Bearing lubricating and sealing device and wind power gear box

Abstract

The bearing lubricating and sealing device comprises a high-speed shaft, a bearing, a distance ring, an impeller and a bearing seat, the bearing and the distance ring are assembled on the high-speed shaft through a locking nut, the impeller is arranged between the bearing and the distance ring, the high-speed shaft penetrates through the bearing seat, and the bearing and the distance ring are both located in an annular area of the bearing seat; the outer wall of the distance ring makes contact with the inner wall of the bearing seat, a first oil hole is formed in the side wall of the distance ring, a lubricating main oil way is arranged in the bearing seat, and the first oil hole communicates with the lubricating main oil way and faces the impeller. The impeller comprises a plurality of blades which are spirally unfolded with the axis of the impeller as the center line. The section of each blade is in an arc shape with the bent cambered surface facing the bearing. A first oil return channel communicated with the inner bearing chamber is further arranged in the bearing seat, and the communication area of the first oil return channel in the bearing chamber is located on the side, back to the bearing, of the impeller. The bearing is fully lubricated and cooled in an impeller oil feeding and impeller negative pressure air suction mode, and the service life of the gearbox is prolonged.

Description

Technical Field

[0001] The present invention relates to the technical field of wind power generation equipment, and in particular to a bearing lubrication and sealing device and a wind power gear box. Background Art

[0002] In a wind turbine gearbox, the output shaft in the front gearbox is connected to a coupling, on which a brake disc is provided. During lubrication of the internal components of the gearbox, the brake disc will form a negative pressure environment at the output end and absorb oil from the high-speed shaft due to the centrifugal effect of its close proximity to the high-speed shaft and high-speed rotation, which will cause leakage of lubricating oil and poor lubrication efficiency of the internal components of the gearbox. At the same time, the bearings of the high-speed shaft mostly use lubrication holes facing the bearings to spray oil on the rolling elements in the bearings, which will cause most of the lubricating oil to be blocked by the rolling elements and flow directly through the rolling elements to the bottom of the bearing chamber and flow away through the return oil channel connected to the bottom of the chamber, making it difficult to fully lubricate and cool the bearings, thus affecting the operating stability and service life of the gearbox.

[0003] Therefore, how to improve the lubrication and heat dissipation efficiency of the internal components of the gearbox is a technical problem that needs to be solved urgently by those skilled in the art. Summary of the invention

[0004] In view of this, an object of the present invention is to provide a bearing lubrication and sealing device to improve the lubrication and heat dissipation efficiency of the internal components of the gear box.

[0005] Another object of the present invention is to provide a wind power gearbox including the bearing lubrication and sealing device.

[0006] To achieve the above object, the present invention provides the following technical solutions:

[0007] A bearing lubrication and sealing device, characterized in that it comprises a high-speed shaft, a bearing, a distance ring, an impeller and a bearing seat, wherein the bearing and the distance ring are assembled on the high-speed shaft through a locking nut, the impeller is arranged between the bearing and the distance ring, the high-speed shaft passes through the bearing seat, and the bearing and the distance ring are both located in an annular area of ​​the bearing seat;

[0008] The outer wall of the distance ring contacts the inner wall of the bearing seat, and the side wall of the distance ring is provided with a first oil hole, a main lubrication oil circuit is provided in the bearing seat, the first oil hole is connected to the main lubrication oil circuit and is provided toward the impeller; the impeller comprises a plurality of spirally expanded blades with its axis as the center line, and the cross section of the blade is an arc with a curved arc surface facing the bearing; the bearing seat is also provided with a first oil return channel connected to the internal bearing chamber thereof, and the connecting area of ​​the first oil return channel in the bearing chamber is located on the side of the impeller facing away from the bearing.

[0009] Preferably, in the above-mentioned bearing lubrication and sealing device, the distance ring includes an annular web, the web is coaxial with the impeller and is arranged toward the impeller, and the outer wall of the web is provided with a first annular oil passage and a second annular oil passage at intervals along the axial direction, and the second annular oil passage is closer to the impeller than the first annular oil passage;

[0010] A groove is provided on one side of the web facing the impeller, and the first annular oil channel and the second annular oil channel are respectively connected to the side of the web facing the impeller, the first annular oil channel is connected to the first oil return channel, and the second annular oil channel is connected to the bearing lubrication oil channel provided on the bearing seat, and the bearing lubrication oil channel is connected to the middle area of ​​the bearing in the axial direction.

[0011] Preferably, in the above-mentioned bearing lubrication and sealing device, a primary oil groove, a secondary oil groove and a tertiary oil groove are provided on the side of the web facing the impeller, the primary oil groove and the secondary oil groove are both arc-shaped and have equal diameters, and the tertiary oil groove is annular and has a groove body depth greater than that of the secondary oil groove;

[0012] The primary oil groove is connected to the tertiary oil groove in radial direction through oil holes, and the tertiary oil groove is connected to the first annular oil passage through a first radial oil hole; the secondary oil groove is connected to the second annular oil passage through a second radial oil hole.

[0013] Preferably, in the above-mentioned bearing lubrication and sealing device, the arc length of the secondary oil groove is greater than the arc length of the primary oil groove.

[0014] Preferably, in the above-mentioned bearing lubrication and sealing device, the outer wall of the distance ring is further provided with an inwardly concave slideway, a valve core is provided in the slideway, a first end of the slideway is connected to the inner wall of the distance ring, and a second end of the slideway is connected to the second annular oil passage;

[0015] When the valve core is in the first position, it is in the right position of the slide and closes the second annular oil passage and the bearing lubricating oil passage; when the valve core is in the second position, it is in the left position of the valve core and the second annular oil passage is connected to the bearing lubricating oil passage.

[0016] Preferably, in the above-mentioned bearing lubrication and sealing device, the outer wall of the distance ring is also provided with a buffer channel, the buffer channel is an arc-shaped groove and is arranged at the second end of the slideway, the second annular oil channel is connected to the buffer channel, and the inlet of the bearing lubrication oil circuit is arranged on the buffer channel.

[0017] Preferably, in the above-mentioned bearing lubrication and sealing device, the first end of the slideway is connected to the inner wall of the distance ring through a wedge-shaped groove, and the smaller side opening of the wedge-shaped groove is located on the inner wall of the distance ring.

[0018] Preferably, in the above-mentioned bearing lubrication and sealing device, the bearing seat is provided with a sodium storage groove in the radial direction corresponding to the wedge groove and the second annular oil channel, and a magnetic screw plug is installed at the bottom of the sodium storage groove.

[0019] Preferably, the above-mentioned bearing lubrication and sealing device also includes an oil flinger ring, and the bearing seat is also provided with a second oil return channel. The lubricating oil passing through the gap between the distance ring and the impeller is flung toward the inner wall of the end cover on one side of the bearing chamber by the centrifugal action of the oil flinger ring, and flows to the second oil return channel at the bottom; a plurality of labyrinth seals are arranged between the oil flinger ring and the end cover.

[0020] Preferably, in the above-mentioned bearing lubrication and sealing device, the bearing comprises a first bearing portion and a second bearing portion arranged along the same axis, and a bearing distance ring arranged between the first bearing portion and the second bearing portion.

[0021] Preferably, in the above-mentioned bearing lubrication and sealing device, an oil baffle plate is provided between the outlet end of the first oil return channel and the gear area of ​​the high-speed shaft; and an oil baffle ring is provided between the bearing and the gear area of ​​the high-speed shaft.

[0022] A wind power gearbox comprises the bearing lubrication and sealing device described in any one of the above embodiments.

[0023] It can be seen from the above technical scheme that the bearing lubrication and sealing device provided by the present invention can guide the lubricating oil to the top of the impeller through the main lubrication oil circuit and the first oil hole for the high-speed shaft under normal operating conditions, and then can break up and drive the lubricating oil through the structure in which the blades and the axis of the high-speed shaft are spirally arranged, so as to achieve full lubrication of the bearing by the lubricating oil. Compared with the lubrication method of directly adding lubricating oil to the bearing, it can improve the utilization efficiency of the lubricating oil and improve the uniform lubrication of various areas of the bearing; at the same time, due to the high-speed rotation of the impeller, affected by the Bernoulli effect, the lubricating oil and air can enter the impeller position from two channels, and flow to the bearing side through the impeller drive. Due to the closed space, all the lubricating oil is used for bearing lubrication, thereby improving the utilization rate of the lubricating oil, and the external low-temperature air is absorbed and passed into the bearing, which can accelerate the heat dissipation of the bearing and improve the heat dissipation efficiency of the bearing, thereby improving the operating stability and life of the bearing. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0025] Figure 1 A schematic diagram of the exploded structure of a bearing lubrication and sealing device provided in an embodiment of the present invention;

[0026] Figure 2 It is a schematic diagram of the assembly cross-sectional structure of the bearing lubrication and sealing device;

[0027] Figure 3 for Figure 2 Detailed view of the bottom area of ​​;

[0028] Figure 4 is a schematic diagram of the structure of the impeller;

[0029] Figure 5 It is a structural schematic diagram when the impeller rotates forward;

[0030] Figure 6 is a schematic diagram of the cross-sectional structure of the bearing seat;

[0031] Figure 7 It is a schematic diagram of the cross-sectional structure of the bearing seat at another cutting depth;

[0032] Figure 8 It is a structural diagram when the impeller is reversed;

[0033] Fig. 9 Schematic diagram of the cross-sectional structure of the distance ring;

[0034] Fig.10 This is a side view of the web of the distance ring;

[0035] Fig.11 for Fig.10 A schematic cross-sectional structure diagram of ;

[0036] Fig.12 for Fig.10 A schematic diagram of a cross-sectional structure at another depth in the axial direction;

[0037] Fig.13 It is a schematic diagram of the cross-sectional structure of the assembly structure of the impeller and the distance ring;

[0038] Fig.14 It is a structural schematic diagram of the valve core being located at the first position in the slideway;

[0039] Fig.15 It is a structural schematic diagram of the valve core being located at the second position in the slideway;

[0040] Fig.16 It is a side view of the slideway and buffer channel;

[0041] Fig.17 is a schematic diagram of the connecting structure between the first oil return channel and the first annular oil channel;

[0042] Fig.18It is a schematic diagram of the connection between the second oil return channel and the bearing lubricating oil circuit when the gear box is reversed;

[0043] Fig.19 This is a front view of the slide position.

[0044] Among them, 10-high-speed shaft; 110-gear area; 20-bearing; 210-first bearing part; 220-second bearing part; 230-bearing distance ring; 30-distance ring; 310-first oil hole; 320-web; 3210-first annular oil passage; 3220-second annular oil passage; 3230-first oil groove; 3240-secondary oil groove; 3250-third oil groove; 3260-first radial oil hole; 3270-second radial Oil hole; 330- slideway; 340- valve core; 350- buffer channel; 360- wedge groove; 40- impeller; 410- blade; 50- bearing seat; 510- lubrication main oil circuit; 520- bearing lubrication oil circuit; 530- sodium storage tank; 540- magnetic plug; 550- second oil return channel; 560- first oil return channel; 60- locking nut; 70- oil thrower ring; 80- end cover; 910- oil baffle plate; 920- oil baffle ring. DETAILED DESCRIPTION

[0045] The core of the present invention is to disclose a bearing lubrication and sealing device to improve the lubrication and heat dissipation efficiency of the internal components of the gear box.

[0046] Another core of the present invention is to provide a wind power gearbox including the above-mentioned bearing lubrication and sealing device.

[0047] In order to make the technical personnel in this field better understand the scheme of the present invention, the embodiments of the present invention are described below with reference to the accompanying drawings. In addition, the embodiments shown below do not limit the content of the invention recorded in the claims. In addition, the entire contents of the structures represented by the following embodiments are not limited to those necessary for the solutions of the invention recorded in the claims.

[0048] like Figure 1-19 As shown, the bearing lubrication and sealing device provided by the embodiment of the present invention mainly includes a high-speed shaft 10, a bearing 20, a distance ring 30, an impeller 40 and a bearing seat 50, wherein the high-speed shaft 10 is a power output shaft, one end of which is connected to a coupling to achieve power transmission, and the bearing 20 and the distance ring 30 are assembled on the high-speed shaft 10 through a locking nut 60, and the bearing 20 and the distance ring 30 are both sleeved and installed, and the locking nut 60 is preferably a ring-shaped nut structure with an external thread to maintain the stability of the connection. The impeller 40 is arranged between the bearing 20 and the distance ring 30, and it should be noted that the impeller 40 is fixedly arranged on the outer periphery of the high-speed shaft 10 so that during the rotation of the high-speed shaft 10, the impeller 40 rotates synchronously with the high-speed shaft 10.

[0049] The bearing seat 50 is an outer protective structure, which is a cylindrical component so that the oil circuit and other structures can be processed on the side wall surface and the internal structural components can be protected. The high-speed shaft 10 is arranged through the bearing seat 50, and it should be noted that the axial length of the high-speed shaft 10 is longer than the bearing seat 50. The gear area 110 on the high-speed shaft 10 is located on one side of the bearing seat 50, and the bearing 20 and the distance ring 30 are located in the annular area of ​​the bearing seat 50. At the same time, the outer wall of the distance ring 30 contacts the inner wall of the bearing seat 50, and the outer wall of the bearing 20 also contacts the inner wall of the bearing seat 50. In the axial direction of the high-speed shaft 10, the bearing 20 abuts against the distance ring 30, so that the bearing 20 can operate stably and be lubricated in a relatively closed environment.

[0050] On the basis of the above structure, the bearing seat 50 is provided with a lubricating main oil passage 510 in its side wall area. One side opening of the lubricating main oil passage 510 is connected to the side wall of the bearing seat 50 in the axial direction, and external lubricating oil is injected through the opening position of the lubricating main oil passage 510, while the other side opening of the lubricating main oil passage 510 is connected to the bearing chamber, that is, the area surrounded by the inner wall surface of the bearing seat 50 for the operation of the bearing 20. Correspondingly, a first oil hole 310 is opened in the side wall of the distance ring 30. The distance ring 30 is connected to the lubricating main oil passage 510 through the first oil hole 310 through the fitting structure between its outer wall and the inner wall of the bearing seat 50, so as to receive the lubricating oil injected into the lubricating main oil passage 510; and the other end opening of the first oil hole 310 is arranged toward the impeller 40. It should be noted that, in some embodiments of the present invention, the distance ring 30 is a variable cross-section structure, that is, its inner diameter in the axial direction of the high-speed shaft 10 is a stepped configuration, and the impeller 40 is arranged in an annular structure in an area with a larger inner diameter of the distance ring 30. Correspondingly, the first oil hole 310 is also arranged in an annular structure in an area with a larger inner diameter of the distance ring 30, so that the lubricating oil flowing out of the first oil hole 310 can drip vertically onto the impeller 40 under the action of gravity.

[0051] Furthermore, the impeller 40 is a structure that rotates synchronously with the high-speed shaft 10, and includes a plurality of blades 410 in the circumference thereof. Preferably, the plurality of blades 410 are evenly arranged in the circumference of the impeller 40, and the blades 410 are in a spirally unfolded configuration with the axis of the annular impeller 40 as the center line. The cross-sectional profile of the blades 410 is an arc-shaped structure so as to be able to guide the lubricating oil to slide, and at the same time, the curved surface of the blades 410 faces the direction of the bearing 20. It should be noted that the curved surface of the blades 410 facing the bearing 20 here specifically means that the center of the curved surface of the blades 410 is arranged closer to the bearing 20 than the blades 410, so as to guide the lubricating oil. In the above structure, in normal operation, that is, when the high-speed shaft 10 of the wind turbine gearbox rotates forward and the impeller 40 rotates forward synchronously, the lubricating oil entering the upper part of the impeller 40 through the first oil hole 310 from the lubricating main oil path 510 will flow into the blade 410 structure of the impeller 40. Since the structure of the blade 410 is a spirally unfolded configuration with the axis of the annular impeller 40 as the center line, and the curved arc surface faces the direction of the bearing 20, it will be scattered and drive the lubricating oil to rotate under high-speed rotation conditions, and squeeze the lubricating oil to one side of the bearing 20. The lubricating oil will be partially atomized and flow to the bearing 20 along the axial direction of the high-speed shaft 10 to lubricate the bearing 20. Compared with the lubrication method of directly adding lubricating oil to the position of the bearing 20, it can make the lubricating oil enter the bearing 20 more fully, and can reduce the amount of lubricating oil directly dripping to the bottom of the bearing chamber through the blocking effect of the blade 410, thereby improving the utilization rate of the lubricating oil.

[0052] In order to further optimize the above technical solution, a first oil return channel 560 is further provided in the bearing seat 50. The first oil return channel 560 connects the bearing chamber inside the bearing seat 50, that is, the space in the bearing seat 50 for arranging the bearing 20, and the external area of ​​the bearing seat 50. The first oil return channel 560 is used to discharge the lubricating oil accumulated in the bearing chamber. It should be noted that the connecting area of ​​the first oil return channel 560 in the bearing chamber is preferably located on the side of the impeller 40 facing away from the bearing 20. In the above embodiment, during the synchronous forward rotation of the impeller 40 and the high-speed shaft 10, the impeller 40 can blow air toward the bearing 20 and form a negative pressure on the side facing away from the bearing 20 under the action of the rotation in a relatively sealed space. On the one hand, it can accelerate the absorption of lubricating oil from the first oil hole 310 to accelerate the lubrication of the bearing 20; on the other hand, it can absorb air from the outside of the bearing seat 50 from the first oil return channel 560, and blow air with a lower external temperature to the bearing 20 to achieve heat exchange with the bearing 20, thereby accelerating the cooling of the bearing 20 and improving the running stability of the bearing 20. The negative pressure environment can effectively prevent the lubricating oil from leaking through the radial gap between the distance ring 30 and the impeller 40, and the negative pressure formed by the impeller 40 is much higher than the negative pressure formed by the centrifugal effect of the brake disc of the outer coupling on the air, thereby playing an effective sealing role.

[0053] The above structure guides the lubricating oil to the top of the impeller 40 through the main lubricating oil passage 510 and the first oil hole 310 for the high-speed shaft 10 under normal operating conditions, and then the lubricating oil can be dispersed and driven through the structure in which the blades 410 are spirally arranged with the axis of the high-speed shaft 10, so as to achieve full lubrication of the bearing 20 by the lubricating oil. Compared with the lubrication method of directly adding lubricating oil to the bearing 20, the utilization efficiency of the lubricating oil can be improved and the lubrication of various areas of the bearing 20 can be improved. At the same time, due to the high-speed rotation of the impeller 40, under the influence of the Bernoulli effect, the lubricating oil and air can enter the impeller 40 position from two channels, and flow to the side of the bearing 20 driven by the impeller 40. Due to the closed space, all the lubricating oil is used to lubricate the bearing 20, thereby improving the utilization rate of the lubricating oil. Moreover, the external low-temperature air is sucked and passed into the bearing 20, which can accelerate the heat dissipation of the bearing 20 and improve the heat dissipation efficiency of the bearing 20, thereby improving the operating stability and life of the bearing 20.

[0054] Furthermore, when the gearbox is in operation under normal working conditions, the impeller 40 and the high-speed shaft 10 maintain forward high-speed rotation, while the gearbox may reverse under certain working conditions. At this time, the load is small, the power is low, and the running time is short. The impeller 40 runs in the reverse direction. When the gearbox reverses, the bearing 20 still needs to be lubricated. However, due to its small load and low power, the demand for lubricating oil is different from that during forward rotation. Therefore, in some embodiments of the present invention, in order to enable the bearing lubrication and sealing device to adapt to various working conditions of the gearbox, the distance ring 30 also includes The annular web 320, specifically, the web 320 is coaxially arranged with the impeller 40, and the web 320 is arranged toward the impeller 40, specifically, a part of the web 320 can overlap with a part of the impeller 40 in the axial direction, as described in the above embodiment, the distance ring 30 is a variable cross-section structure, that is, its inner diameter in the axial direction of the high-speed shaft 10 is a stepped configuration, and the impeller 40 is arranged in the annular structure of the area with a larger inner diameter of the distance ring 30, and the web 320 is an annular area with a smaller inner diameter of the distance ring 30. On this basis, the outer wall surface of the web 320, that is, the outer wall surface position of the distance ring 30, is further provided with a first annular oil passage 3210 and a second annular oil passage 3220, the first annular oil passage 3210 and the second annular oil passage 3220 are arranged in parallel and at intervals, and the second annular oil passage 3220 is arranged closer to the impeller 40 than the first annular oil passage 3210.

[0055] The first annular oil passage 3210 and the second annular oil passage 3220 are used to guide the lubricating oil at different positions, and correspondingly, a groove for collecting the lubricating oil is opened on the side surface of the web 320 facing the impeller 40, and the first annular oil passage 3210 and the second annular oil passage 3220 are respectively connected to the side of the web 320 facing the impeller 40, and at the same time, the first annular oil passage 3210 is connected to the first oil return passage 560. When the impeller 40 reverses, the impeller 40 will drive the lubricating oil injected from the top of the impeller 40 toward the side facing away from the bearing 20, and collect the lubricating oil through the groove on the side of the web 320 facing the impeller 40. The lubricating oil entering the first annular oil passage 3210 through the groove structure can flow into the first oil return passage 560 to be recovered by the oil tank.

[0056] At the same time, a bearing lubricating oil passage 520 is also opened on the bearing seat 50, and the second annular oil passage 3220 is connected to the bearing lubricating oil passage 520 opened on the bearing seat 50, and the groove collects the lubricating oil, and the lubricating oil entering the second annular oil passage 3220 through the groove structure can enter the bearing lubricating oil passage 520, and the other end of the bearing lubricating oil passage 520 is connected to the middle area of ​​the bearing 20 in its axial direction, so that the lubricating oil can enter the bearing 20 and achieve a lubrication effect.

[0057] It should be noted that, in the above embodiment, the bearing 20 is actually lubricated by the lubricating oil collected in the second annular oil channel 3220, and the first annular oil channel 3210 is used for oil leakage, that is, when the working load is small and the demand for lubricating oil is small, part of the lubricating oil is returned to the oil tank through the first annular oil channel 3210, so as to avoid the problem of oil stirring and heating of the bearing 20 due to the accumulation of lubricating oil, thereby improving the lubrication effect of the bearing 20 under the gearbox reversal condition.

[0058] On the basis of the above embodiment, in order to achieve effective connection between the groove opened on the side of the web 320 facing the impeller 40 and the first annular oil channel 3210 and the second annular oil channel 3220, a primary oil groove 3230, a secondary oil groove 3240 and a tertiary oil groove 3250 are further opened on the side of the web 320 facing the impeller 40, wherein the primary oil groove 3230 and the secondary oil groove 3240 are separately arranged, both of which are arc-shaped structures, and the radii of the primary oil groove 3230 and the secondary oil groove 3240 are equal, and the tertiary oil groove 3250 is a complete annular structure. It should be noted that the secondary oil groove 3240 is the structure with the shallowest groove body depth among the three oil groove structures for oil collection and guidance; and the groove body depths of the primary oil groove 3230 and the tertiary oil groove 3250 are greater than those of the secondary oil groove 3240, and the groove body depths of the primary oil groove 3230 and the tertiary oil groove 3250 can be the same or different to achieve a layered structure. It should be noted that the multi-stage oil grooves with different depths are provided to meet the communication with the first annular oil passage 3210 and the second annular oil passage 3220 provided at different positions in the axial direction of the web 320. Correspondingly, the web 320 is provided with oil holes in its radial direction. Since the secondary oil groove 3240 is provided closer to the bearing 20 in the axial direction of the web 320, the secondary oil groove 3240 is communicated with the second annular oil passage 3220 with a shallower groove body depth through the second radial oil hole 3270. The primary oil groove 3230 and the tertiary oil groove 3250 are firstly communicated in the radial direction through the oil hole, and then the bottom area of ​​the groove body of the tertiary oil groove 3250, that is, the deeper area, is communicated with the first annular oil passage 3210 through the first radial oil hole 3260, thereby realizing the communication setting of the first annular oil passage 3210 and the second annular oil passage 3220 at different positions in the axial direction through one side of the web 320.

[0059] It should be noted that the arc length of the secondary oil groove 3240 is preferably greater than the arc length of the primary oil groove 3230, so that the secondary oil groove 3240 has a sufficient collection area, and the secondary oil groove 3240 with a longer arc length passes through the lowest point of the annular structure, thereby ensuring that a certain amount of lubricating oil can be stored when the gearbox is reversed, so as to form pressure and enter the bearing lubricating oil circuit 520, thereby preventing the lubricating oil from directly connecting to the return oil channel structure and losing the lubrication effect.

[0060] The above structure realizes effective oil supply when the gearbox rotates forward by designing the impeller 40 and the oil circuit. At the same time, by arranging a multi-stage oil groove on the web 320, the lubricating oil is collected and guided, and the oil is drained and dissipated when the gearbox is reversed, thereby meeting the different degrees of heat dissipation requirements of the bearing 20 under different operating conditions, and effectively improving the operating stability and service life of the bearing 20.

[0061] In order to improve the stability of the first annular oil channel 3210 and the second annular oil channel 3220 in different operating conditions of the lubricating oil and avoid affecting the lubricating oil during forward transmission of the gearbox, in some embodiments of the present invention, the outer wall of the distance ring 30 is further provided with a concave slide 330, and the length direction of the slide 330 is along the axial direction of the distance ring 30. A valve core 340 is provided inside the slide 330. The valve core 340 can slide along the length direction of the slide 330 to switch the conduction state of the slide 330. Specifically, the first end of the slide 330, that is, the end of the slide 330 close to the bearing 20, is connected to the inner wall of the distance ring 30 so as to receive the lubricating oil from the inner wall position of the distance ring 30 and drive the valve core 340 inside the slide 330. The second end of the slide 330, that is, the end of the slide 330 away from the bearing 20, is connected to the second annular oil channel 3220; and the sliding path of the valve core 340 in the slide 330 can at least pass through the first position and the second position. When the valve core 340 is in the first position, it is in the right position of the slide 330, that is, the end of the slide 330 away from the bearing 20. At this time, the valve core 340 isolates and closes the second annular oil channel 3220 and the bearing lubricating oil channel 520, as well as the connecting port between the bearing lubricating oil channel 520 and the slide 330 and the inner wall of the distance ring 30, and the lubricating oil cannot flow between the bearing lubricating oil channel 520 and the second annular oil channel 3220.

[0062] It should be noted that when the gearbox rotates forward, there will be lubricating oil in the bearing chamber. At the same time, the lubricating oil will flow into the interior of the slide 330 through the connection between the first end of the slide 330 and the bearing chamber, and at the same time push the valve core 340 from the left side of the slide 330 to the right side, that is, push the valve core 340 to the first position to close the second annular oil channel 3220 and the bearing lubricating oil channel 520, thereby maintaining the airtightness of the interior of the bearing chamber and reducing the risk of lubricating oil leakage.

[0063] When the valve core 340 is in the second position, it is in the left position of the valve core 340. At this time, the second annular oil channel 3220 is connected with the bearing lubricating oil circuit 520, so that the lubricating oil in the second annular oil channel 3220 can reach the position of the bearing 20 through the bearing lubricating oil circuit 520. It should also be noted that under the condition of gearbox reversal, the second annular oil channel 3220 can collect lubricating oil through the groove set on the side wall of the web 320. The lubricating oil entering the second annular oil channel 3220 will reach the position of the slide 330 and push the valve core 340 from the right side of the slide 330 to the left side, that is, push the valve core 340 to move to the second position, so as to realize the connection between the second annular oil channel 3220 and the bearing lubricating oil circuit 520, and meet the lubrication of the bearing 20 under the corresponding working condition of the gearbox.

[0064] Furthermore, in order to reduce the design difficulty of the slide 330, in some embodiments of the present invention, a buffer channel 350 is further provided on the outer wall of the distance ring 30. The buffer channel 350 is an arc groove structure arranged along the circumference of the distance ring 30, and the buffer channel 350 intersects with the slide 330 at the second end of the slide 330 to structurally expand the slide 330 through the buffer channel 350. At the same time, the second annular oil channel 3220 is connected to the buffer channel 350 position, and the entrance of the bearing lubrication oil circuit 520 is arranged on the buffer channel 350. When the valve core 340 is in the first position, the connecting area between the second annular oil channel 3220 and the buffer channel 350, as well as the buffer channel 350 and the first end of the slide 330, that is, the area where the slide 330 and the bearing chamber are connected are isolated through its double-layer sealing gasket structure; and when the valve core 340 is in the second position, it moves to the left to connect the second annular oil channel 3220 with the buffer channel 350.

[0065] Furthermore, in some embodiments of the present invention, the first end of the slide 330 is connected to the inner wall of the distance ring 30 through the wedge-shaped groove 360, and the smaller side opening of the wedge-shaped groove 360 ​​is located on the inner wall of the distance ring 30. The structure of the wedge-shaped groove 360 ​​can meet the needs of collecting the lubricating oil into the slide 330, so that the gear box can drive the valve core 340 under the forward rotation condition, and at the same time, reduce the overflow of the lubricating oil from the wedge-shaped groove 360 ​​through its smaller side opening.

[0066] Furthermore, in order to improve the cleanliness of the lubricating oil and improve its lubricating effect on the bearing 20, the embodiment of the present invention is further provided with a sodium storage tank 530, which is opened at least at a position corresponding to the wedge groove 360 ​​and the second annular oil passage 3220 in the radial direction of the bearing seat 50, so as to collect iron filings and other particles that may exist in the sodium storage lubricating oil, clean the oil path, prevent the valve core 340 from getting stuck, and improve the cleanliness of the lubricating oil. Preferably, a magnetic screw plug 540 is installed at the bottom of the sodium storage tank 530 to remove metal particles in the lubricating oil through the cooperation of gravity and magnetic attraction.

[0067] In addition, it should be noted that in some embodiments of the present invention, the bearing lubrication and sealing device further includes an oil slinger 70, and correspondingly, a second oil return channel 550 is also provided in the bearing seat 50. Specifically, the oil slinger 70 is provided between the distance ring 30 and the end cover 80, and the lubricating oil flowing through the gap between the distance ring 30 and the impeller 40 will reach the position of the oil slinger 70, and the oil slinger 70 rotates synchronously with the high-speed shaft 10 to sling the lubricating oil to the inner wall position of the end cover 80 under the centrifugal action, and the lubricating oil flows to the bottom along the inner wall of the end cover 80, and is collected through the second oil return channel 550 connected to the bottom of the bearing chamber. It should also be noted that multiple labyrinth seals are provided between the oil slinger 70 and the end cover 80 to prevent the reverse leakage of the lubricating oil.

[0068] Furthermore, in some embodiments of the present invention, the bearing 20 includes a first bearing portion 210 and a second bearing portion 220 arranged along the same axis, and a bearing distance ring 230 arranged between the first bearing portion 210 and the second bearing portion 220, so that each structural part of the bearing 20 can be individually designed and assembled to adapt to different gearbox operating conditions.

[0069] It should also be noted that an oil baffle plate 910 is provided between the outlet end of the first oil return channel 560 and the gear area 110 of the high-speed shaft 10. The oil baffle plate 910 provided between the outlet of the first oil return channel 560 and the high-speed shaft 10 can provide enclosure protection for the outlet of the first oil return channel 560, so as to effectively prevent the lubricating oil from splashing into the gear area 110 of the high-speed shaft 10, and the high-temperature lubricating oil formed by the meshing and extrusion of the gears and then entering the oil return channel. At the same time, an oil baffle ring 920 is provided between the bearing 20 and the gear area 110 of the high-speed shaft 10, and the oil baffle ring 920 is provided in the bearing chamber to prevent the lubricating oil from leaking from the inside of the bearing chamber to the gear area 110 of the high-speed shaft 10.

[0070] Furthermore, an embodiment of the present invention also provides a wind turbine gearbox, which includes a bearing lubrication and sealing device provided by any of the above embodiments. Since the bearing lubrication and sealing device has the technical effects provided by the above embodiments, the wind turbine gearbox also has the above technical effects, which will not be repeated herein.

[0071] The terms "first", "second", "left side" and "right side" in the specification and claims of the present invention and the above drawings are used to distinguish different objects rather than to describe a specific order. In addition, the terms "including" and "having" and any variations thereof are intended to cover non-exclusive inclusions. For example, a process, method, system, product or device including a series of steps or units is not limited to the listed steps or units, but may include steps or units that are not listed.

[0072] The above description of the disclosed embodiments enables one skilled in the art to implement or use the present invention. Various modifications to these embodiments will be apparent to one skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the present invention. Therefore, the present invention will not be limited to the embodiments shown herein, but rather to the widest scope consistent with the principles and novel features disclosed herein.

Claims

1. A bearing lubrication and sealing device, characterized in that: It comprises a high-speed shaft, a bearing, a distance ring, an impeller and a bearing seat, wherein the bearing and the distance ring are assembled on the high-speed shaft through a locking nut, the impeller is arranged between the bearing and the distance ring, the high-speed shaft passes through the bearing seat, and the bearing and the distance ring are both located in the annular area of ​​the bearing seat; The outer wall of the distance ring contacts the inner wall of the bearing seat, and the side wall of the distance ring is provided with a first oil hole, a main lubrication oil circuit is provided in the bearing seat, the first oil hole is connected to the main lubrication oil circuit and is provided toward the impeller; the impeller comprises a plurality of spirally expanded blades with its axis as the center line, and the cross section of the blade is an arc with a curved arc surface facing the bearing; the bearing seat is also provided with a first oil return channel connected to the internal bearing chamber thereof, and the connecting area of ​​the first oil return channel in the bearing chamber is located on the side of the impeller facing away from the bearing.

2. The bearing lubrication and sealing device according to claim 1, characterized in that: The distance ring includes an annular web, the web is coaxial with the impeller and is arranged toward the impeller, and the outer wall of the web is provided with a first annular oil passage and a second annular oil passage at intervals along the axial direction, and the second annular oil passage is closer to the impeller than the first annular oil passage; A groove is provided on one side surface of the web facing the impeller, and the first annular oil channel and the second annular oil channel are respectively connected to the side of the web facing the impeller, the first annular oil channel is connected to the first oil return channel, and the second annular oil channel is connected to the bearing lubrication oil channel provided on the bearing seat, and the bearing lubrication oil channel is connected to the middle area of ​​the bearing in the axial direction.

3. The bearing lubrication and sealing device according to claim 2, characterized in that: The side of the web facing the impeller is provided with a primary oil groove, a secondary oil groove and a tertiary oil groove, the primary oil groove and the secondary oil groove are arc-shaped and have equal diameters, the tertiary oil groove is annular and has a groove body depth greater than that of the secondary oil groove; The primary oil groove is connected to the tertiary oil groove in radial direction through oil holes, and the tertiary oil groove is connected to the first annular oil passage through a first radial oil hole; the secondary oil groove is connected to the second annular oil passage through a second radial oil hole.

4. The bearing lubrication and sealing device according to claim 3, characterized in that: The arc length of the secondary oil groove is greater than the arc length of the primary oil groove.

5. The bearing lubrication and sealing device according to claim 2, characterized in that: The outer wall of the distance ring is also provided with a concave slideway, a valve core is provided in the slideway, a first end of the slideway is connected to the inner wall of the distance ring, and a second end of the slideway is connected to the second annular oil passage; When the valve core is in the first position, it is in the right position of the slide and closes the second annular oil passage and the bearing lubricating oil passage; when the valve core is in the second position, it is in the left position of the valve core and the second annular oil passage is connected to the bearing lubricating oil passage.

6. The bearing lubrication and sealing device according to claim 5, characterized in that: The outer wall of the distance ring is also provided with a buffer channel, which is an arc-shaped groove and passes through the second end of the slideway. The second annular oil channel is connected to the buffer channel, and the inlet of the bearing lubrication oil circuit is arranged on the buffer channel.

7. The bearing lubrication and sealing device according to claim 5, characterized in that: The first end of the slideway is connected to the inner wall of the distance ring through a wedge-shaped groove, and a smaller opening of the wedge-shaped groove is located on the inner wall of the distance ring.

8. The bearing lubrication and sealing device according to claim 7, characterized in that: The bearing seat is provided with a sodium storage groove in the radial direction corresponding to the wedge groove and the second annular oil passage, and a magnetic screw plug is installed at the bottom of the sodium storage groove.

9. The bearing lubrication and sealing device according to claim 6, characterized in that: It also includes an oil slinger ring, and the bearing seat is also provided with a second oil return channel. The lubricating oil passing through the gap between the distance ring and the impeller is spun toward the inner wall of the end cover on one side of the bearing chamber by the centrifugal action of the oil slinger ring, and flows to the second oil return channel at the bottom; a plurality of labyrinth seals are arranged between the oil slinger ring and the end cover.

10. The bearing lubrication and sealing device according to claim 1, characterized in that: The bearing includes a first bearing portion and a second bearing portion arranged along the same axis, and a bearing distance ring arranged between the first bearing portion and the second bearing portion.

11. The bearing lubrication and sealing device according to claim 1, characterized in that: An oil baffle plate is arranged between the outlet end of the first oil return channel and the gear area of ​​the high-speed shaft; and an oil baffle ring is arranged between the bearing and the gear area of ​​the high-speed shaft.

12. A wind power gearbox, characterized in that: The invention comprises a bearing lubrication and sealing device as described in any one of claims 1 to 11.

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