CN221277934U - Lubrication structure of bearing and lubricating oil distribution system for bearing - Google Patents

Abstract

The present disclosure provides a lubrication structure of a bearing, including: the bearing is provided with an inner ring, an inner ring and rolling bodies arranged between the inner ring and the inner ring, and a clearance space exists between the outer wall of the inner ring and the inner wall of the inner ring; at least one input channel disposed in the inner ring and leading from an outer surface of the inner ring to the clearance space; a lubrication distribution pipe is arranged in the clearance space in the circumferential direction and has an inlet and an outlet for supplying lubrication oil towards the rolling bodies, a first set of inlet channels of the at least one inlet channel being for the inlet of liquid lubrication oil or for the inlet of a two-phase oil-gas mixture flow or for the inlet of oil mist, and the inlet of the lubrication distribution pipe being connected to said first set of inlet channels. The present disclosure also provides a lubrication oil distribution system for a bearing, in particular for providing lubrication oil to a lubrication structure as described above.

Description

Lubrication structure of bearing and lubricating oil distribution system for bearing

Technical Field

The present disclosure relates to a lubrication structure of a bearing and a lubrication oil distribution system for the bearing.

Background

Now, a non-Chang Duofeng force generator is installed in the world, and a pitch bearing is an important part of a pitch system of the wind driven generator. The function of the pitch bearing is to connect the blade to the hub and transfer the load on the blade to the hub. When the wind speed is too high or too low, the attack angle of the air flow to the blades is changed by adjusting the pitch of the blades, so that the aerodynamic torque obtained by the wind generating set is changed, and the power output is kept stable. The blade pitch function, pitch bearing are therefore extremely important for safe production and reliable operation of the wind turbine.

Because the bearing is very complex in stress, the pitch shaft is subjected to loads caused by aerodynamic forces, gravity, centrifugal forces and yaw transmitted from the blades during operation, and these forces are transmitted to the pitch bearing through the blades, which are manifested as axial forces, radial forces and overturning moments. Meanwhile, the vibration force acts on the pitch bearing due to the coupling of various loads received in the running process, and the vibration force is easy to cause fretting friction and abrasion, namely fretting abrasion, fretting fatigue and fretting corrosion.

In particular, when the inner rolling body of the pitch bearing is relative to the raceway surface, the pitch-variable bearing can only perform extremely small-distance reciprocating motion, fretting wear is extremely easy to occur in the small-distance reciprocating motion to form fretting wear particles, and if the fretting wear particles enter the contact area of the rolling body and the raceway, the wearing particles form abrasive particle wear, so that the wearing of the pitch bearing is further aggravated, and the bearing fails in advance, so that the wearing particles generated in the contact area of the rolling body and the raceway are timely removed, and the anti-fretting wear particles have a positive effect on reducing the abrasive particle wear occurring in the pitch bearing. Further development of fretting wear can lead to fretting fatigue and fretting corrosion of the pitch bearing.

In the case of good lubrication, the occurrence and development of these fretting wear can be suppressed as much as possible. However, in the absence of a lubricant or poor lubrication, it can easily cause the pitch bearing to fail, causing the pitch system to fail. When serious, the bearing outer ring is cracked, and even a serious accident that the blades fall down occurs.

In normal operation of the pitch bearing, the pitch adjustment angle is typically 0 ° -30 °, although the adjustment frequency may sometimes be relatively high, but the speed of the rolling bodies of the pitch bearing relative to the raceway surface is very low. However, under most operating conditions, the pitch action is relatively small, and the relative speed between the rolling elements of the pitch bearing and the friction pairs such as the raceway surface is almost zero (even if not zero) during operation of the fan, so that it is impossible to form a sufficiently thick fluid lubrication film, i.e. to separate the friction pairs inside the bearing from each other. Therefore, lubrication in the bearing is in a boundary lubrication state, and ensuring that a sufficient amount of lubricant is present in the contact area of the rolling elements and the raceway to form a boundary lubrication film is very important for lubrication of the pitch bearing.

At present, most of variable pitch bearings of wind driven generators are lubricated by adopting a centralized lubricating oil distribution system, and the lubricating agent is lubricating grease. After the operation time of the pitch bearing is a period of time, the lubricating grease in the bearing continuously acts under the gravity and the centrifugal force; the shearing action of the rolling bodies and the retainers, the vibration caused by the response of the blades to wind and the accumulation action of time factors, and the phenomenon that excessive base oil is lost due to lubricating grease. The oil content in the lubricating grease is insufficient, the lubricating capability is reduced, the lubricating grease is hardened, and even the bearing can have grease discharging faults. Waste grease cannot be timely discharged from the bearing cavity, the grease can be filled and blocked in the bearing cavity, the pressure in the cavity is higher and higher along with the continuous filling of the grease, and the bearing sealing ring is broken and extruded by excessive pressure, so that the grease is leaked and the inside of the hub of the wind driven generator is polluted. Waste grease is accumulated in the bearing cavity, metal abrasive dust and other pollutants generated in the running process of the bearing are added, the oil filling hole and the grease discharging hole can be blocked, new grease cannot be pumped in, the waste grease cannot be discharged out, the abrasion speed of a raceway and rolling bodies in the bearing is further increased, the service life of the pitch bearing is shortened, and the reliable running of a pitch system and a wind driven generator is greatly influenced.

In addition, many studies have shown that the iron content of grease discharged from pitch bearings in service is very high, and that some pitch bearing grease samples have iron contents even exceeding 1% iron content. The metal particles in the lubricating grease are too high in content, so that the oxidation, hardening and hardening of the lubricating grease can be accelerated, the fiber structure of the lubricating grease is damaged, the base oil in the lubricating grease cannot be locked, the oil content in the lubricating grease is greatly reduced, and the problem of poor lubrication of a pitch bearing is caused, so that a pitch system cannot work normally. If the pitch bearing is replaced due to failure of the pitch bearing, this will bring about a huge economic loss for the maintenance units and owners of the wind turbine, especially for offshore wind turbines, where the replacement of the pitch bearing will bring about a larger economic loss.

In other fields, bearings having similar working conditions and lubricated by grease also face the above-mentioned problems. Thus, if the grease lubrication of such bearings can be replaced with a grease lubrication, there is a great benefit to the friction pair in such bearings (especially wind-powered pitch bearings).

Disclosure of utility model

In view of the above-mentioned problems and needs, the present disclosure proposes a novel technical solution, which solves the above-mentioned problems and brings about other technical effects due to the following technical features.

The present disclosure provides a lubrication structure of a bearing, including: the bearing is provided with an inner ring, an inner ring and rolling bodies arranged between the inner ring and the inner ring, wherein a clearance space exists between the outer wall of the inner ring and the inner wall of the inner ring; at least one input channel disposed in the inner ring and leading from an outer surface of the inner ring to the clearance space; a lubricant distribution pipe provided in the clearance space in the circumferential direction and having an inlet and an outlet for supplying lubricant toward the rolling bodies; wherein a first set of at least one inlet channel is used for inputting liquid lubricating oil or a two-phase oil-gas mixed flow or inputting oil mist, and an inlet of a lubricating oil distributing pipe is connected with the first set of inlet channels.

The present disclosure also provides a lubrication oil distribution system for a bearing for providing lubrication oil to a lubrication structure as described above, characterized in that the lubrication oil distribution system comprises: a lubricant oil tank; a pressurized air source; a multi-pipe swivel is fluidly coupled to the bearing, the lubrication oil tank, and the source of pressurized air to provide lubrication oil from the lubrication oil tank and pressurized air from the source of pressurized air to the bearing such that the pressurized air causes lubrication oil within the bearing to flow and drain.

The present disclosure also provides a lubrication oil distribution system for a bearing for providing lubrication oil to a lubrication structure as described above, characterized in that the lubrication oil distribution system comprises: a lubricant oil tank; a pressurized air source; a multi-line swivel coupled to the lubrication oil tank and the pressurized air source to receive lubrication oil from the lubrication oil tank and pressurized air from the pressurized air source; an oil and gas mixer is fluidly coupled between the multi-conduit swivel and the bearing, receives lubrication oil and pressurized air from the multi-conduit swivel, thereby producing a two-phase oil and gas mixture stream, and provides the two-phase oil and gas mixture stream to the bearing.

The present disclosure also provides a lubrication oil distribution system for a bearing for providing lubrication oil to a lubrication structure as described above, characterized in that the lubrication oil distribution system comprises: a lubricant oil tank; a pressurized air source; an oil mist generating unit that receives the lubricating oil from the lubricating oil tank and the pressurized air from the pressurized air source, thereby generating a lubricating oil mist; a multi-pipe swivel is fluidly coupled to the bearing and the oil mist generating unit to provide lubricating oil mist from the oil mist generating unit to the bearing.

The wind power variable pitch bearing unit is lubricated through a trace amount of circulating oil lubricating oil distribution system, the lubricating oil is supplied to bearings and seals in the bearing unit by a pumping system, and the lubricating oil in the bearing unit is sucked back to an oil tank by compressed air and a vacuum system, so that trace amount of circulating oil lubrication is realized. In areas with lower ambient temperature, the heat preservation and heat tracing belt are needed to be carried out on the lubricating oil pipeline and the oil return pipeline so as to ensure that the lubricating oil in the pipeline is in a reasonable temperature range, so that the lubricating oil can have good fluidity, can be sucked back into the vacuum cylinder by the vacuum system, and is pumped into the oil tank by the pump to realize circulating oil lubrication.

Drawings

FIG. 1 is a schematic illustration of a bearing lubrication structure according to a preferred embodiment of the present disclosure;

FIG. 2 is an enlarged view of portion A of FIG. 1;

FIGS. 3A, 3B, 3C, and 3D are cross-sectional views showing the lubricating oil distribution tube and its surrounding structure at different locations in FIG. 1, respectively;

FIG. 4 is an enlarged view of portion B of FIG. 1;

FIG. 5 is a schematic illustration of a bearing lubrication structure according to an alternative preferred embodiment of the present disclosure;

FIG. 6 is an enlarged view of portion B of FIG. 5;

FIG. 7 is a schematic illustration of a lubricating oil dispensing system according to a preferred embodiment of the present disclosure;

FIG. 8 is a schematic illustration of a lubricating oil dispensing system according to another preferred embodiment of the present disclosure;

FIG. 9 is a schematic view of a lubricating oil dispensing system according to yet another preferred embodiment of the present disclosure;

Detailed Description

In order to make the objects, technical solutions and advantages of the technical solutions of the present disclosure more clear, the technical solutions of the embodiments of the present disclosure will be clearly and completely described below with reference to the drawings of the specific embodiments of the present disclosure. Like reference numerals in the drawings denote substantially identical structural and functional components. It should be noted that the described embodiments are some, but not all embodiments of the present disclosure. All other embodiments, which can be made by one of ordinary skill in the art without the need for inventive faculty, are within the scope of the present disclosure, based on the described embodiments of the present disclosure.

Possible implementations within the scope of the present disclosure may have fewer components, have other components not shown in the drawings, different components, differently arranged components, differently connected components, etc., than the examples shown in the drawings. Furthermore, two or more of the elements in the figures may be implemented in a single element or a single element shown in the figures may be implemented as multiple separate elements.

Unless defined otherwise, technical or scientific terms used herein should be given the ordinary meaning as understood by one of ordinary skill in the art to which this disclosure belongs. The terms "first," "second," and the like in the description and in the claims, do not denote any order, quantity, or importance, but rather are used to distinguish one element from another. Where the number of components is not specified, the number of components may be one or more; likewise, the terms "a," "an," "the," and the like do not necessarily denote a limitation of quantity. The word "comprising" or "comprises", and the like, means that elements or items preceding the word are included in the element or item listed after the word and equivalents thereof, but does not exclude other elements or items. The terms "mounted," "configured," "connected," or "connected" and the like are not limited to physical or mechanical mounting, configuration, connection, but may include electrical mounting, configuration, connection, whether direct or indirect. "upper", "lower", "left", "right", etc. are used merely to denote relative positional relationships when the apparatus is in use or positional relationships shown in the drawings, and when the absolute position of the object to be described is changed, the relative positional relationships may be changed accordingly.

For ease of description, the direction of the rotational axis of the bearing will be referred to herein as the axial direction, the direction perpendicular to the axial direction will be referred to as the radial direction, and the direction along the rotational direction will be the circumferential direction. The term "inner/inward" refers to along the direction toward the interior of the bearing, and conversely, the term "outer/outward" refers to toward the exterior of the bearing. In addition, in different embodiments, the same reference numerals are used to refer to components having the same or similar structures and functions.

Bearing lubrication structure

The present disclosure provides a bearing lubrication structure that makes it possible to use lubricating oil instead of grease for bearings in the background art (particularly wind power pitch bearings). It is understood that the rolling elements of the bearing may be balls, cylindrical rollers, tapered rollers, etc.

Referring to fig. 1, the present disclosure is described hereinafter by taking a pitch bearing of a wind turbine as an example. In this wind turbine, a pitch bearing 4 (hereinafter referred to as bearing 4) connects the blades of the wind turbine and a hub (neither of which is shown).

The bearing lubrication structure according to the present disclosure includes: a bearing 4, at least one inlet channel 44, a lubrication distribution pipe 2. Specifically, the bearing has an inner ring 41, an outer ring 42, and rolling elements 43 provided between the inner ring 41 and the outer ring 42. In the case of a wind power pitch bearing, three rows of rolling elements 43 distributed in the axial direction are provided in the bearing 4. The inner ring 41 of the bearing 4 is used for mounting the blades and also as a gear wheel, and therefore comprises teeth 410; the outer race 42 of the bearing 4 is used to mount the hub. It will be appreciated that in cases where a pitch bearing is not used, the bearing may not be used as a gear, i.e. it does not include teeth.

In the pitch bearing mounting, the blades are mounted on the inner ring 41 of the bearing 4 through bolt holes 418. The hub of the wind turbine is mounted on the opposite side of the blade through bolt holes 428. If pitch control is performed by the bearing 4 as a gear, the output gear of the pitch device meshes with the teeth 410 on the bearing 4, thereby rotating the inner ring 41 of the pitch bearing. The inner ring 41 of the pitch bearing rotates to drive the blades fixed on the inner ring to rotate, thereby realizing the pitch function.

Further, referring to fig. 2, a clearance space 40 exists between the outer wall of the inner ring 41 and the inner wall of the outer ring 42 of the bearing 4, and the lubricating oil distribution pipe 2 is disposed in the clearance space 40 in the circumferential direction.

The at least one input channel 44 is provided in the outer ring 42 and leads from an outer surface 421 of the outer ring 42 to the clearance space 40. The input channel 44 may be machined into the outer race 42, for example, by a drilling process. It should be appreciated that the number of input channels 44 may be suitably set as desired.

The lubricating oil distribution pipe 2 is arranged in the clearance space 40 in the circumferential direction and has an inlet 21 and an outlet 22 for supplying lubricating oil towards the rolling bodies (see fig. 3A-3D). For example, the inlet 21 may be a small length of tubing protruding from the lubrication distribution tube 2 that is inserted into the outlet of the corresponding inlet channel 44 to receive lubrication from the inlet channel, which may be sealingly connected, such as by interference fit, adhesive bonding, welding, or the like. Furthermore, the lubrication distribution tube 2 may be fixed to the outer ring 4 in any suitable manner. The outer ring 4 is typically stationary so that the lubrication distribution tube 2 does not move during bearing operation.

Further, a first group of the at least one input channel 44 is used for inputting a liquid lubricating oil or a two-phase oil-gas mixture flow or oil mist (as described later), and the inlet 21 of the lubricating oil distribution pipe 2 is connected to the first group of input channels. It will be appreciated that there may be only one inlet channel 44, which itself constitutes a group and is connected to the inlet 21 of the lubricating oil distribution pipe 2; when there are a plurality of input channels 44, some or all of the plurality of input channels 44 may be used as a first set of input channels as needed to connect with the inlet 21 of the lubrication distribution pipe 2.

Compared with the prior art that the bearing can only be lubricated by lubricating grease, by adopting the scheme of the present disclosure for directly providing lubricating oil for various friction pair cycles inside the bearing, each rolling body, each rolling surface and each pair of friction pair in the bearing can be well lubricated, and after adopting the lubricating mechanism, the supply quantity of the lubricating oil can be regulated and controlled as required, so as to realize micro cycle lubrication, thereby greatly improving the running stability and the service life of the bearing.

According to a preferred embodiment, when the clearance space between the inner and outer rings of the bearing is small, in order to accommodate the arrangement and installation of the lubrication distribution pipe 2, the outer wall of the inner ring 41 may further comprise a first groove 411, and the inner wall of the outer ring 42 may further comprise a second groove 422 corresponding to the first groove 411, the first groove 411 and the second groove 422 forming a space for accommodating the lubrication distribution pipe 2, as shown in fig. 2.

It will be appreciated that any suitable number of lubrication distribution pipes 2 may be provided on both axial sides of each row of rolling bodies 43, depending on the lubrication requirements. As shown in fig. 1, four sets of lubricating oil distribution pipes 2 are provided for three rows of rolling elements 43. Fig. 3A-3D show four sets of lubrication distribution pipes 2 from top to bottom in fig. 1, respectively, in particular, the lubrication distribution pipes 2 of fig. 3A have outlets 22 directed downward, the lubrication distribution pipes 2 of fig. 3B and 3C have outlets 22 directed obliquely upward and obliquely downward, and the lubrication distribution pipes 2 of fig. 3D have outlets 22 directed upward, so that the lubrication distribution pipes 2 are provided on both axial sides of the three rows of rolling bodies 43 in fig. 1, whereby lubrication oil can be supplied to all friction pairs in the bearing also when the position changes due to the pitch axis operation, ensuring sufficient lubrication of the rolling bodies.

Preferably, the number of the inlet 21 and the outlet 22 of the lubricating oil distribution pipe 2 may be appropriately set as required. Preferably, the lubricating oil distribution pipe 2 may be a metallic material or a long-life polymer material. Preferably, the lubricating oil distribution pipe 2 may be one complete annular pipe or a plurality of arcuate pipes arranged in the circumferential direction.

In order to accommodate the circulating flow of the lubricating oil, oil drain holes may be provided at appropriate positions of the bearings to drain the lubricating oil out of the bearings. For example, the oil drain hole may be provided in an appropriate position of the outer race, or on a seal as described later.

It is further preferable that in the case of supplying liquid lubricating oil to the bearing, in order to facilitate supply and recovery of the liquid lubricating oil to the rolling bodies, the outer race 42 is provided with a plurality of input passages 44, and the plurality of input passages 44 are divided into the first group of input passages for inputting the liquid lubricating oil (as described above) and the second group of input passages which may be connected with a pressurized air source (described later) outside the bearing to input pressurized air into the clearance space 40. Thus, the pressurized air inputted into the clearance space 40 through the second group of input passages makes the clearance space 40 exhibit positive pressure with respect to the outside, causing the liquid lubricating oil to flow not only inside the bearing but also to the oil discharge hole, to achieve supply and discharge of the lubricating oil. In this case, the number of the second group of input channels may be smaller than the number of the first group of input channels, and preferably, may also be uniformly dispersed between the first group of input channels at appropriate intervals.

In the case of a two-phase oil-gas mixture flow or oil mist, it is not necessary to introduce additional pressurized air into the interstitial space 40 because of the pressure of the two-phase oil-gas mixture flow or oil mist itself, so that the plurality of input channels 44 may all be used as a first set of input channels for inputting the two-phase oil-gas mixture flow or oil mist.

Thus, the plurality of input channels provided on the outer ring may be adapted to be fed with lubricating oil or with pressurized air, as desired, by merely adjusting the division of the first and second sets of input channels.

According to a preferred embodiment, the lubrication oil inlet pipe 20 may be provided for some or all of the first set of inlet channels. Preferably, the lubrication oil inlet pipe 20 may be connected between the outlet of the respective inlet channel and the inlet 21 of the lubrication oil distribution pipe 2 by means of a sealing thread or an interference fit.

For example, the lubrication oil input pipe 20 may be a small length of piping connected to the outlet of the respective input channel and the inlet 21 of the lubrication oil distribution pipe 2 to input lubrication oil from the respective input channel into the lubrication oil distribution pipe 2; or as shown in fig. 3A-3D, the lubrication oil input pipe 20 is inserted from the outer surface 421 of the outer ring 42 into the corresponding input channel 44 and connected to the inlet 21 of the lubrication oil distribution pipe 2 (in this case, the inlet 21 may be provided as a through hole and connected to the outlet of the lubrication oil distribution pipe 2 in an appropriate manner), and the gap between the lubrication oil input pipe 20 and the corresponding input channel 44 is sealed by a sealing ring (not shown). That is, the lubrication oil input pipe 20 may be a separate long dedicated pipe which is inserted from outside the outer ring 42 through the input channel 44 directly into the clearance space 40 and connected to the lubrication oil distribution pipe 2.

Furthermore, according to a preferred embodiment, the bearing lubrication structure further comprises a seal 45 sealing the clearance space 40 between the inner ring 41 and the outer ring 42 from the axially outer side of the bearing, i.e. two seals 45 are provided at the axially outer sides of the bearing 4, respectively, as indicated by blocks B and C in fig. 1. It should be understood that the seal 45 in block C of fig. 1 has substantially the same structure and mounting as the seal 45 in block B shown in fig. 4, and therefore, the seal is described hereinafter by way of example as the seal in block B.

As shown in fig. 4, the seal 45 includes a seal housing 450 having a first end and a second end.

The first end is sealingly and fixedly connected to an axially outer end face 423 of the outer race 42. Preferably, the first end of seal 45 is secured to outer race 42 by screw 455 and sealing ring 456 is disposed between the first end and outer surface 423 of outer race 42. Seal 456 may be molded or machined. If the seal 456 is machined, it can be integral or can be multi-segment spliced.

The second end has a seal lip 451 in contact with an axially outer end face 413 of the inner ring 41, and the seal housing has an oil drain hole 452 to drain the lubricating oil in the clearance space 40. Multiple oil drain holes may be required depending on the particular oil drain situation. The discharged lubricating oil may be recovered or fed into a lubricating oil circulation system (described later).

Preferably, the seal 45 may further include a sealing flap 453 secured to the second end of the seal 45 by a screw 454 to securely retain the sealing lip 451 in the seal 45.

In addition, depending on the outer ring structure, for example, in the case of the wind power generator of fig. 1, the outer ring includes the bolt holes 428 as described above, and thus, the first end of the seal 45 may also be fixed to the outer ring by bolts (not shown) inserted into the bolt holes 428. Alternatively, as shown in fig. 1, in the case where the outer ring 42 is assembled from two outer ring portions 42A and 42B, the first end of the seal may also be fixed to the outer ring by bolts (not shown) for assembling the two outer ring portions 42A and 42B.

It will be appreciated that the mounting position of the seal may also be reversed left-right, i.e. the first end of the seal may be fixed to the axially outer end face of the inner ring and the sealing lip may contact the axially outer end face of the outer ring.

The present disclosure has been described above in relation to a bearing 4 comprising cylindrical rolling bodies, it being understood that the present disclosure is also applicable to bearings comprising other types of rolling bodies. According to a preferred embodiment as shown in fig. 5, the bearing 4 may comprise two rows of balls 430 as rolling bodies, and similar to the previous embodiment, the lubricating oil distribution pipes 2 are provided on both upper and lower sides of each row of balls 430. Also, for example, in the case of fig. 5, when the clearance space between the inner and outer rings is sufficient to accommodate the lubricating oil distribution pipe 2, the grooves 411 and 422 as described above may not be provided on the inner and outer rings.

In addition, the preferred embodiment also includes modifications to the seal, as indicated by blocks B and C in fig. 5. Referring to fig. 6, the improvement made is described by taking the seal in block B as an example. In the preferred embodiment, the axially outer end face 423 of the outer race 42 includes an outwardly projecting protrusion 424 that includes a recess 426, and a first end of the housing 460 of the seal 46 is inserted into the recess 426, such as by an interference fit, adhesive bonding, or the like, thereby eliminating the screw and seal ring for mounting the first end in the embodiment of fig. 4. In addition, the housing 460 also includes an inwardly projecting projection 465 at the second end that cooperates with the sealing flap 467 to better secure the sealing lip 461 between the projection 465 and the sealing flap 467. The seal 46 also includes an oil drain hole 452. It should be appreciated that the seal 46 in block C of fig. 5 has substantially the same structure and mounting as the seal 46 in block B of fig. 6, and will not be described in detail herein.

Lubricating oil distribution system

As mentioned before, some conventional bearings (in particular pitch bearings for wind turbines) are lubricated by grease. The present disclosure proposes to lubricate such bearings by means of lubricating oil, and thus the present disclosure further proposes a lubricating oil dispensing system for bearings, particularly adapted to provide lubricating oil to bearing lubrication structures as previously described.

According to a preferred embodiment, referring to fig. 7, the lubricating oil dispensing system of the present disclosure comprises: a lubricant oil tank 600; a pressurized air source 100; multi-pipe rotary joint 200, is fluidly coupled with a bearing, lubricant tank 600, and pressurized air source 100 to provide lubricant from lubricant tank 600 and pressurized air from pressurized air source 100 to the bearing, whereby the pressurized air causes lubricant within the bearing to flow and drain.

It should be understood that the multi-pipe rotary joint 200 may be an intermediate connection device designed as needed for communicating a plurality of pipes, and thus its input, output ports, internal communication channels, etc. may be flexibly designed as needed as long as the functions described below can be achieved. It is also to be understood that the term "coupled" as used herein and hereinafter includes direct coupling or indirect coupling via intermediate members.

The lubrication distribution system according to the present disclosure will be described below by way of example with respect to a lubrication distribution system designed for three bearings 401, 402, 403 in a wind turbine. For example, the bearings 401, 402, 403 may each be a bearing 4 having a bearing lubrication structure according to the present disclosure as previously described.

FIG. 7 illustrates a lubrication oil distribution system according to a preferred embodiment of the present disclosure. In the figureIndicating the direction of the air flow,Indicating the direction of flow of the lubricating oil,Indicating the direction of flow of the air and lubricant mixture.

Specifically, in fig. 7, the pressurized air line 800 connected to the pressurized air source 100 is a pressurized air supply line upstream of the multi-line rotary joint 200, the pressurized air line 801 is a pressurized air distribution line downstream of the multi-line rotary joint 200, and the pressurized air lines 800, 801 communicate with each other through the multi-line rotary joint 200. The pressurized air line 801 is connected to a pressurized air branch line 802, a pressurized air branch line 803, and a pressurized air line branch 804, respectively, and these branch lines 802, 803, 804 respectively introduce pressurized air into the bearings 401, 402, 403, so that the pressurized air entering the respective bearings can build up air pressure in the respective bearings, and lubricating oil in the bearings 401, 402, 403 can smoothly flow and be discharged. Preferably, if the lubrication distribution system is used in offshore or off-shore wind turbines, the pressurized air source requires desalination, water removal to prevent adverse effects from binding the lubrication distribution system and bearings.

In fig. 7, a lubrication oil line 805 connected to the oil tank 600 is a lubrication oil supply line upstream of the multi-pipe swivel 200, a lubrication oil line 806 is a lubrication oil distribution line downstream of the multi-pipe swivel 200, and the lubrication oil lines 805, 806 communicate with each other via the multi-pipe swivel 200. The lubrication oil piping 806 is connected to the lubrication oil branch piping 807, the lubrication oil branch piping 808, and the lubrication oil branch piping 809, respectively, to introduce lubrication oil into the bearings 401, 402, 403. Preferably, the oil tank 600 may also share an oil tank with other lubrication oil lubricated components, such as a gearbox and/or a lubrication oil distribution system of a main shaft bearing.

In fig. 7, the lubrication oil lines 810, 811, 812 are oil return lines for discharging a mixture of lubrication oil and air from the bearings 401, 402, 403, for example, installed in the hub of the wind turbine, which are connected to the relevant lines through the multi-line swivel 200. That is: upstream line 810 communicates with downstream line 813 through multi-line swivel 200. The upstream line 811 communicates with the downstream line 814 through the multi-line swivel 200, and the upstream line 812 communicates with the downstream line 815 through the multi-line swivel 200. In addition, line 817 is a vacuum line. Line 818 is a line that pumps lubricant from vacuum tank 503 back to the tank. It will be appreciated that lines 813, 814, 815 may also be combined into a single overall line, as desired.

Preferably, to ensure good fluidity of the lubricating oil in the low temperature environment in the pipes 805, 806, 807, 808, 809, 810, 811, 812, 813, 814, 815, 818, etc., these pipes 805, 806, 807, 808, 809, 810, 811, 812, 813, 814, 815, 818, etc. may be wrapped around the heat tracing band and/or the insulation layer as the case may be so that the temperature of the lubricating oil in the lubricating oil pipe is treated to a reasonable extent, especially the oil return pipe. In addition, in the case of use in a wind turbine, the piping and components within the dashed box 900 rotate as the hub rotates. In this case, the portion of the multi-pipe rotary joint 200 for coupling to the pipe inside the dashed box 900 is designed to be rotatable with the hub.

In fig. 7, the piping 819 is the piping of the bypass filtration system, primarily to ensure that the lubricant cleanliness levels in the lubricant distribution system are within reasonable limits.

In fig. 7, the lubricating oil in the oil tank 600 is sucked by the pump 301 through the coarse oil inlet filter 300, passes through the valve 302, the fine filter 306, the valve 307 and the flow meter 309 to the multi-pipe rotary joint 200. To prevent the fine filter 306 from being blocked, a bypass check valve 308 is provided, when the fine filter 306 reaches a certain pressure difference, to prevent the filter element of the fine filter 306 from being damaged, the bypass check valve 308 is opened to protect the filter element in the fine filter 306, and simultaneously prevent pollutant particles in the filter element from invading a pipeline system of lubricating oil after the filter element in the fine filter 306 is damaged, and damage bearings 401, 402, 403 and other relevant parts. Meanwhile, the valve 304 and the particle counter 305 are used for detecting the cleanliness of the lubricating oil pumped out of the oil tank, and on-line monitoring of the cleanliness of the lubricating oil is realized in use. If the cleanliness of the lubricant detected by the particle counter 305 exceeds the limit value, the pump 701 is started to perform bypass filtration purification until the cleanliness detected by the particle counter is within the required range. The differential pressure change-over switch 303 monitors the differential pressure of the fine filter 306, and when the differential pressure of the two sides of the fine filter 306 exceeds a set value range, the differential pressure change-over switch 303 sends an alarm signal to the main control, and the main control reports the fault. Filters 707, 708 are 1 for 1, and are switched during use by the signal from the differential pressure switch 705. The oil tank 600 may also be shared with other lubrication components, and may in principle be shared with the lubrication distribution system of the gearbox and/or main shaft bearings. Because of the difficulty in controlling the cleanliness of the lubricating oil to a high cleanliness level during operation of the gear oil, it is not generally recommended to share a tank with the gearbox.

In fig. 7, the lubricating oil passes through a flow rate transmitter 309 with a digital display function and then reaches the multi-pipe rotary joint 200. After the lubrication oil passes through the multi-pipe swivel 200, the lubrication oil pipe is split into three lubrication points into the 3 bearings 401, 402, 403. That is, after passing through the flow transmitter 310 with the digital display function, one path enters the lubrication point in the bearing 401 through the distributor 311. The second path passes through the flow transmitter 312 with digital display function and then enters the lubrication point in the bearing 402 through the distributor 313. The third path, after passing through the digitally-enabled flow transmitter 314, passes through the distributor 315 and into the lubrication point within the bearing 403 (e.g., through a corresponding input channel connected to the bearing cup in the bearing lubrication structure as previously described). The digitally enabled flow transmitters 309, 310, 312, 314 may, for example, transmit flow signals to a PLC system and may display and monitor flow values from a central control system (DCS) and/or transmit flow signals to other control systems, such as SCADA (Supervisory Control And Data Acquisition) systems or wind generators. The dispensers 311, 313, 315 may be of various types of lubricant dispensers, such as progressive, plunger, etc. types of dispensers.

Furthermore, in the present preferred embodiment and the preferred embodiment described later with reference to fig. 8 and 9, the multi-pipe rotary joint 200 may also be fluidly coupled with the oil drain hole of the bearing. Further, the lubrication oil distribution system may further include an oil/gas separation system fluidly coupled to the multi-pipe rotary joint 200 to receive a mixture of lubrication oil and air discharged from the oil discharge holes of the bearings and separate the lubrication oil from the air in the mixture.

Specifically, referring to fig. 7, in the case of a wind power generator, a mixture of lubricating oil and air in bearings 401, 402, 403 therein enters the multi-pipe rotary joint 200 through pipes 810, 811, 812 connected to oil drain holes (e.g., the aforementioned oil drain holes 452) of the bearings, respectively, under gravity change, centrifugal force, pressurized air pressure, and vacuum suction provided by a vacuum pump 512, under hub operation conditions, and then enters the vacuum buffer tank 503 through pipes 813, 814, 815. The air in the real buffer tank 503 enters an automatic oil separator 509 through a valve 507 to remove oil, and is discharged to the atmosphere through a valve 511 by a vacuum pump 512. The lubricating oil separated in the automatic oil separator 509 flows to the vacuum buffer tank 503 through the pipe 816 through the automatic oil discharge valve 508. The valve 504 is a vacuum transmitter 505 with a digital display function, and can transmit a vacuum degree signal in the vacuum tank 503 to the PLC system, and can display and monitor the vacuum degree signal from a central control system (DCS), and/or transmit the vacuum degree signal to a SCADA system or other control systems of a wind power generator, so as to monitor the vacuum degree. 510 is a vent valve. To ensure the oil-gas separation effect, a plurality of oil-gas separators, such as a cyclone type, electrostatic type, agglomeration type and other separators, can be arranged to ensure that no oil mist is discharged to the environment to the greatest extent possible. Meanwhile, in order to ensure that the bearings 401, 402, 403 are operated under the condition of micro positive pressure, and prevent the vacuum degree in the bearings 401, 402, 403 from being pumped too high due to the operation of the vacuum pump 512, the air pressure in the bearings 401, 402, 403 and the sealing thereof needs to be controlled to ensure that the internal pressure is slightly higher than the external atmospheric pressure. Such as 10Pa, preferably 15Pa, above the atmospheric pressure outside the bearings 401, 402, 403.

In fig. 7, the pressurized air source 100, after passing through the valve 101, enters the pressurized air buffer tanks 102, 103 as valves, and 104 as a pressure transmitter with digital display function mounted on the pressurized air buffer tank 102, can transmit pressure signals to a PLC system, can display pressure values and monitor from a central control system (DCS), and/or transmit pressure signals to a SCADA system or other control system of a wind power generator, to monitor the pressure. 105 are valves, preferably automatic drain valves, mounted on the pressurized air buffer tank 102 to prevent moisture in the pressurized air from affecting lubrication of the bearings 401, 402, 403. After the pressurized air passes through the automatic drain filter 106 from the buffer tank 102, the pressurized air enters the precision filter 107 and enters the pressurized air dryer 108, and the dew point of the pressurized air is reduced to below-25 ℃, so that the pressurized air is prevented from forming free water by condensation in the lubricating oil distribution system and the bearings 401, 402 and 403, and adverse effects are caused on the friction pair and each equipment component. The pressurized air reenters the pressure relief valve 109 to control the maximum pressure and flow rate of the downstream pressurized air lines 801, 802, 803, 804. The pressure transmitter 110 with digital display can display the pressure on the pipeline after depressurization, transmit the pressure signal to the PLC system, display the pressure value from the central control system (DCS) and monitor, and/or transmit the pressure signal to the SCADA system or other control systems of the wind power generator to monitor the pressure.

As shown in fig. 7, the adjustable throttle valves 111, 113, 115 are adjusting valves for adjusting the flow rate of the pressurized air to be supplied to the bearings 401, 402, 403, respectively.

In fig. 7, the lubricating oil in the oil tank 600 is pumped by the pump 701 through the valve 700, and the valve 702 and the pressure transmitter 703 with digital display function are used for measuring and detecting the effect of the internal pressure in the outlet line of the pump 701. The pressure transmitter 703 with digital display function can transmit pressure signals to the PLC system and can display pressure values from the central control system (DCS) and monitor and/or transmit pressure signals to the SCADA system or other control systems of the wind power generator to monitor the pressure. The lubricating oil passes through filters 707 and 708 and returns to the oil tank 600 after passing through a valve 709, thereby realizing bypass filtration purification of the lubricating oil. After the filters 707, 708 are plugged, the one-way valve 706 is opened, preventing damage to the pump 701. The differential pressure change-over switch 705 monitors the differential pressure of the filters 707 and 708, and when the differential pressure across the filters 707 and 708 exceeds a set value range, the differential pressure change-over switch 705 transmits a signal to the PLC system, sends an alarm signal to the PLC system, and a central control system (DCS) reports the fault and/or transmits the differential pressure signal to a SCADA system or other control system of the wind power generator to monitor the differential pressure.

In fig. 7, a magnetic filter 601 is mounted in the oil return position. The heater 602 functions to heat the oil in the oil tank 600 when the oil temperature in the oil tank is lower than a set value to ensure that the temperature of the lubricating oil in the oil tank 600 is in a reasonable range. Control of heater 602 by temperature controller 603. And 604 is a thermometer, which displays the oil temperature in the oil tank. 606 is an oil level gauge that displays the level of oil within the oil tank 600. 607 is an oil level transmitter which functions to display the oil level height and to transmit oil level height signals to the PLC system and to display and monitor the oil level height values from the central control system (DCS) and/or to transmit oil level signals to the SCADA system or other control systems of the wind power generator for monitoring the oil level. The temperature transmitter 608 with the digital display function is used for converting the temperature of the lubricating oil measured in the oil tank 600 into a digital signal, transmitting the digital signal to the PLC system, displaying the temperature value of the lubricating oil from a central control system (DCS) and monitoring the temperature, and/or transmitting the temperature signal to a SCADA system or other control systems of the wind power generator to monitor the temperature.

In addition, for wind turbine applications, biodegradable lubricating oils have been proposed because of the problems associated with the efficiency of the removal of the mixture of lubricating oil and air in the present lubrication system. Lubricating oils typically produced with ester-based oils, particularly those formulated with polyol ester-based oils, reduce the negative environmental impact of the very small amounts of oil mist that are discharged.

The lubricating oil distribution system can realize a lubricating mode of micro-circulating oil, is particularly suitable for lubricating a variable pitch bearing structure of a wind driven generator, and can be changed into the lubricating mode of lubricating oil and air circulation according to the bearing lubricating structure disclosed by the invention for the existing variable pitch bearing structure operated by the installed machine so as to improve the lubricating efficiency and reliability of the variable pitch bearing and prolong the service life of the bearings.

FIG. 8 illustrates a lubrication oil distribution system according to another preferred embodiment of the present disclosure. It should be appreciated that the lubrication oil distribution system depicted in fig. 8 includes the same or similar devices or units as the lubrication oil distribution system depicted in fig. 7, and that these devices or units will not be described in detail. In the figureIndicating the direction of the air flow,Indicating the direction of flow of the lubricating oil,Indicating the direction of flow of the two-phase hydrocarbon mixture stream. The particulars of the lubricating oil distribution system of fig. 8 will be mainly described hereinafter.

The lubricating oil distribution system shown in fig. 8 includes: a lubricant oil tank 600; a pressurized air source 100; a multi-line swivel 200 fluidly coupled to the lubrication oil tank 600 and the pressurized air source 100 to receive lubrication oil from the lubrication oil tank 600 and pressurized air from the pressurized air source 100; the oil and gas mixer 3101 is fluidly coupled between the multi-circuit rotary joint 200 and the bearing, receives lubricating oil and pressurized air from the multi-circuit rotary joint 200, thereby generating a two-phase oil and gas mixture stream, and provides the two-phase oil and gas mixture stream to the bearing.

In fig. 8, pressurized air in pressurized air line 801 disposed downstream of multi-line swivel joint 200 enters oil and gas mixer 3101; the lubricating oil from the lubricating oil line 806 enters the oil-gas mixer 3101, where it is mixed with the pressurized air from the pressurized air line 801 in the oil-gas mixer 3101 to form a two-phase oil-gas mixture stream. It will be appreciated that the lubrication oil and the pressurized air in this two-phase oil-gas mixture flow are relatively independent two-phase flows in the same passage, as compared with the case of the liquid lubrication oil and air input into the bearing interior in fig. 7 described above, for example, after the lubrication oil and air form a two-phase oil-gas mixture flow in the oil-gas mixer 3101 and are input into the aforementioned first group of input passages 44, the lubrication oil adheres to the inner wall of the passages and is blown forward by the pressurized air to reach the bearing interior.

Further, the oil and gas branches 802, 803, 804 from the oil and gas mixer 3101 are connected to three oil and gas distributors 3111, 3121, 3131 for lubricating lubrication points within the three bearings 401, 402, 403, respectively. That is, the first oil and gas branch 802 enters the oil and gas distributor 3111, and then enters the lubrication point in the bearing 401 after being distributed. The second hydrocarbon leg 803 enters the hydrocarbon distributor 3121 and is distributed to lubrication points within the bearing 402. The third oil and gas branch 804 enters the oil and gas distributor 3131, and after being distributed, enters the lubrication point in the bearing 403. It will be appreciated that the above-described branches may be connected to corresponding input channels at the outer race of the bearing in the bearing lubrication arrangement as described previously. Thus, although the air and the lubricating oil form a two-phase oil-gas mixture flow in the oil-gas mixer 3101, when the two-phase oil-gas mixture flow is supplied into the bearings 401, 402, 403, the two-phase oil-gas mixture flow can still build up sufficient pressure in the bearings to enable the two-phase oil-gas mixture flow in the bearings 401, 402, 403 to flow back while preventing the vacuum pump 512 from drawing the inside of the bearings 401, 402, 403 into negative pressure, which adversely affects the bearings.

The lubrication oil distribution system further includes digital display pressure transmitters 314, 315, 316 mounted between the oil and gas mixer 3101 and the oil and gas distributors 3111, 3121, 3131, which can transmit pressure signals to the PLC system and can display and monitor pressure values from the central control system (DCS) and/or transmit pressure signals to the SCADA system or other control system of the wind power generator. The oil and gas distributors 3111, 3121, 3131 are typically progressive distributors.

FIG. 9 illustrates a lubrication oil distribution system according to yet another preferred embodiment of the present disclosure. It should be appreciated that the lubrication oil distribution system shown in fig. 9 includes the same or similar devices or units as the lubrication oil distribution system shown in fig. 7 and 8, and these devices or units will not be described in detail. In the figureIndicates the air flow direction, "→" indicates the lubricant flow direction,Indicating the flow direction of the oil mist. The particulars of the lubricating oil distribution system of fig. 9 will be mainly described hereinafter.

The lubricating oil distribution system shown in fig. 9 includes: a lubricant oil tank 600; a pressurized air source 100; an oil mist generation unit 901 that receives the lubricating oil from the lubricating oil tank 600 and the pressurized air from the pressurized air source 100, thereby generating a lubricating oil mist; the multi-pipe rotary joint 200 is fluidly coupled to the bearing and the oil mist generating unit 901 to supply the lubricating oil mist from the oil mist generating unit 901 to the bearing. Preferably, the oil mist generating unit 90 mainly includes an oil mist generator 117, an oil mist generating unit oil tank 611, and the like.

In fig. 9, the pressurized air line 801A is a pressurized air line after passing through a pressure reducing valve 1151. The oil mist lubrication line 801 is an oil mist lubrication line from the oil mist generator 117 to the multi-line rotary joint 200, and the oil mist lubrication line 801 and the oil mist lubrication line 806 communicate with each other through the multi-line rotary joint 200.

Pressurized air exits surge tank 102 through valve 1061 and enters automatic drain filter 1071. From the automatic drain filter 1071, through valve 1081, into the fine filter 1091, and through valve 1101, into the pressurized air dryer 1111, the dew point of the pressurized air is reduced to a lower temperature (e.g., below-25 ℃) to prevent condensation of the pressurized air in the lubrication oil distribution system and bearings 401, 402, 403, free water formation, and adverse effects on friction pairs and various equipment components. Pressurized air then passes through valve 112 and into pressurized air heater 1131 to heat the pressurized air, thereby facilitating the atomization of the lubricant in mist generator 1171 to form a mist (the droplets of lubricant in such mist have a very small diameter, on the order of a few tenths of a micron to a few microns), and improving the atomization efficiency of the lubricant. After being heated by heater 1131, the pressurized air enters pressure reducing valve 1151 through valve 114 to control the highest pressure and flow rate in the subsequent pressurized air lines (e.g., lines 801A, 802, 803, 804, etc.). The pressure transmitter 116 with digital display may display the pressure in the pipeline after being depressurized by the depressurization valve 1151, and transmit the pressure signal to the PLC system, and may display and monitor the pressure value from the central control system (DCS), and/or transmit the pressure signal to the SCADA system or other control system of the wind power generator, to monitor the pressure value.

In fig. 9, the oil mist generator 1171 of the oil mist generating unit 901 functions to generate oil mist to form an oil mist fluid. The oil mist generation unit oil tank 611 further includes: an in-tank heater 612 for heating the lubricating oil in the oil tank 611 to facilitate atomization; and a temperature controller 613 for controlling the heater 612 to ensure that the lubricant processing in the oil tank 611 is within a control temperature range. In addition, 614 is a thermometer; 616 is an oil level gauge of the oil tank 611, which shows the level of the oil in the oil tank 611. 617 is an oil level transmitter which functions to display the oil level height and to transmit oil level height signals to a PLC system and to display and monitor oil level height values from a central control system (DCS) and/or to transmit oil level signals to a SCADA system or other control system of a wind power generator for oil level monitoring. The temperature transmitter 618 with the digital display function is used for converting the temperature of the lubricating oil measured in the oil tank 611 into a digital signal, transmitting the digital signal to the PLC system, displaying the temperature value of the lubricating oil from the central control system (DCS) and monitoring the temperature, and/or transmitting the temperature signal to the SCADA system or other control systems of the wind power generator to monitor the temperature. When the oil level in the oil tank 611 is measured by the oil level transmitter 617 to be lower than the limit value, a signal is sent to the control system, the pump 301 is started to operate, oil is supplied to the oil tank 611, and when the oil level in the oil tank 611 reaches the maximum oil level limit value, a signal is sent to the control system, and the pump 301 is stopped to operate.

In fig. 9, oil mist from the oil mist generator 1171 enters the pipe 806 after passing through the pipe 801 and entering the multi-pipe rotary joint 200. The oil mist in the line 806 is divided into 3 lines, the first line being the line 802, which in turn is divided into a plurality of lines into the bearing 401, which lubricates the friction pair in the bearing 401. The second path is line 803, which in turn splits into multiple branches into bearings 402, lubricating friction pairs in bearings 402. The third path is a pipe 804 which in turn divides into a plurality of branches into the bearings 403, lubricating the friction pairs in the bearings 403. It will be appreciated that the aforementioned branches may be connected to corresponding input channels of the bearing outer race in the bearing lubrication arrangement as previously described.

A flow transmitter (not shown in fig. 9) may be provided for each of the oil mist branches entering the bearings 401, 402, 403 to enable detection and detection of oil mist in each of the oil mist branches entering the bearings, and the measured oil mist flow values may be converted into digital signals for transmission to the PLC system, and the oil mist flow values and monitoring of each of the oil mist branches may be displayed from the central control system (DCS), and/or the oil mist flow signals may be transmitted to the SCADA system or other control systems of the wind power generator for monitoring of the oil mist flow.

In order to ensure good fluidity of the lubricating oil in the pipes 801, 806, 810, 811, 812, 813, 814, 815, 818, etc. in a low temperature environment, the lubricating oil pipes 801, 806, 810, 811, 812, 813, 814, 815, 818, etc. should be wound with heat tracing bands and/or heat insulating layers according to circumstances so that the lubricating oil temperature in the lubricating oil pipes is treated to a reasonable extent, particularly the oil return pipes.

In fig. 1, the lubricating oil in bearings 401, 402, 403 enters multi-pipe rotary joint 200 through pipes 810, 811, 812 under the change of gravity, centrifugal force, pressurized air pressure in the oil mist fluid, and vacuum suction force provided by vacuum pump 512 under the hub operation condition, and then enters vacuum buffer tank 503 through pipes 813, 814, 815. The air in the real buffer tank 503 enters the automatic oil mist separator 509 through the valve 507 to remove oil, and is discharged to the atmosphere through the valve 511 by the vacuum pump 512. The lubricating oil separated in the automatic oil mist separator 509 flows to the vacuum buffer tank 503 through the automatic oil discharge valve 508 via the pipe 816. The valve 504 is a vacuum transmitter 505 with a digital display function, and can transmit a vacuum degree signal in the vacuum tank 503 to the PLC system, and can display and monitor the vacuum degree signal from a central control system (DCS), and/or transmit the vacuum degree signal to a SCADA system or other control systems of a wind power generator, so as to monitor the vacuum degree. 510 is a vent valve. To ensure the oil mist separation effect, a plurality of oil mist separators, such as a cyclone type, electrostatic type, agglomeration type, or the like, may be provided as a combined separator to ensure that no oil mist is discharged to the environment as much as possible.

By employing the bearing lubrication structure and/or the lubrication oil distribution system of the present disclosure, some conventional grease lubricated bearings may be lubricated with a lubrication oil.

By taking a variable pitch bearing of a wind driven generator as an example, the state of trace circulating oil can be realized, the lubrication effect becomes very good, the phenomenon of poor lubrication caused by lack of lubricating grease or insufficient oil content can not occur, and the reliability of the variable pitch bearing is greatly improved. The micro-quantity circulating oil lubrication is realized on the variable-pitch bearing, and measures such as cleaning and dewatering of lubricating oil, moisture invasion control, oil quality state monitoring and the like are arranged in a circulating oil system, so that the reliability of the system, the predictability of system faults and the identifiability of the faults are greatly improved. Preventing the occurrence of the early failure of the pitch bearing and facilitating the taking of relevant remedial measures. And the loss caused by the fault of the pitch system is reduced. And the micro-motion wear particles in the variable pitch bearing can be discharged more timely, so that secondary damage to the bearing caused by the micro-motion wear particles is reduced. After adopting the form of circulating oil lubrication, dispose suitable filter in the circulating oil system, just can ensure that circulating oil is in higher cleanliness level to improve its service life and reliability of pitch bearing. Moreover, under the condition of little increase of the bearing mass, the lubricating oil can lubricate, and the lubrication reliability of the pitch bearing is greatly improved.

The exemplary implementation of the present disclosure has been described in detail hereinabove with reference to the preferred embodiments, however, it will be understood by those skilled in the art that various modifications and adaptations to the specific embodiments described above may be made and that various combinations of the technical features and structures set forth in the present disclosure may be practiced without departing from the scope of the present disclosure, which is defined in the appended claims.

Claims (10)

1. A lubrication structure of a bearing, comprising:

A bearing (4) having an inner ring (41), an outer ring (42), and rolling elements (43) provided between the inner ring (41) and the outer ring (42), wherein a gap space (40) is provided between the outer wall of the inner ring (41) and the inner wall of the outer ring (42);

At least one input channel (44) arranged in the outer ring (42) and leading from an outer surface (421) of the outer ring (42) to the clearance space (40);

A lubricating oil distribution pipe (2) which is provided in the clearance space (40) in the circumferential direction and has an inlet (21) and an outlet (22) for supplying lubricating oil toward the rolling bodies;

Wherein a first group of at least one inlet channel (44) is used for inputting liquid lubricating oil or a two-phase oil-gas mixture flow or inputting oil mist, and an inlet (21) of a lubricating oil distribution pipe (2) is connected with the first group of inlet channels.

2. A lubrication structure of a bearing according to claim 1, characterized in that the outer wall of the inner ring (41) comprises a first groove (411), the inner wall of the outer ring (42) comprises a second groove (422) corresponding to the first groove (411), the first groove (411) and the second groove (422) forming a space for accommodating the lubrication distribution pipe (2).

3. A lubrication structure of a bearing according to claim 1, characterized in that the lubrication distribution tube (2) is a complete ring-shaped tube or a plurality of arc-shaped tubes arranged in the circumferential direction.

4. A lubrication structure of a bearing according to claim 1, characterized in that the lubrication oil inlet pipe (20) is arranged for some or all of the channels of the first set of inlet channels such that:

the lubricant inlet pipe (20) is connected between the outlet of the corresponding inlet channel and the inlet (21) of the lubricant distribution pipe (2) by means of sealing threads or interference fit; or (b)

The lubricant inlet pipe (20) is inserted from the outer surface (421) of the outer ring (42) into the corresponding inlet channel and connected with the inlet (21) of the lubricant distribution pipe (2), and the gap between the lubricant inlet pipe (20) and the corresponding inlet channel is sealed by a sealing ring.

5. A lubrication structure of a bearing as claimed in claim 1, further comprising a seal member (45) sealing the clearance space (40) between the inner ring (41) and the outer ring (42) from the axially outer side of the bearing, the seal member comprising a seal housing (450) having a first end and a second end, the first end being in sealing and fixed connection with the axially outer end face of one of the inner ring (41) and the outer ring (42), the second end having a seal lip (451) in contact with the axially outer end face of the other of the inner ring (41) and the outer ring (42), and the seal housing having an oil drain hole (452) to drain lubricating oil in the clearance space (40).

6. A lubrication structure for a bearing according to any one of claims 1-5, characterized in that at least one input channel (44) comprises a plurality of input channels (44), and that a second set of input channels (44) of the plurality of input channels is connected to a source of pressurized air for inputting pressurized air into the interstitial space (40).

7. A lubrication oil distribution system for a bearing for providing lubrication oil to a lubrication structure according to any one of claims 1-6, the lubrication oil distribution system comprising:

A lubricant oil tank (600);

a pressurized air source (100);

A multi-line swivel (200) is fluidly coupled to the bearing, the lubrication oil tank (600) and the pressurized air source (100) to provide lubrication oil from the lubrication oil tank (600) and pressurized air from the pressurized air source (100) to the bearing such that the pressurized air causes lubrication oil within the bearing to flow and drain.

8. A lubrication oil distribution system for a bearing for providing lubrication oil to a lubrication structure according to any one of claims 1-6, the lubrication oil distribution system comprising:

A lubricant oil tank (600);

a pressurized air source (100);

A multi-line swivel (200) fluidly coupled to the lubrication oil tank (600) and the pressurized air source (100) to receive lubrication oil from the lubrication oil tank (600) and pressurized air from the pressurized air source (100);

An oil and gas mixer (3101) fluidly coupled between the multi-pipe rotary joint (200) and the bearing, receives lubrication oil and pressurized air from the multi-pipe rotary joint (200), thereby producing a two-phase oil and gas mixture stream, and provides the two-phase oil and gas mixture stream to the bearing.

9. A lubrication oil distribution system for a bearing for providing lubrication oil to a lubrication structure according to any one of claims 1-6, the lubrication oil distribution system comprising:

A lubricant oil tank (600);

a pressurized air source (100);

An oil mist generation unit (901) that receives the lubricating oil from the lubricating oil tank (600) and the pressurized air from the pressurized air source (100), thereby generating a lubricating oil mist;

A multi-line swivel (200) is fluidly coupled to the bearing and to the oil mist generating unit (901) to provide lubricating oil mist from the oil mist generating unit (901) to the bearing.

10. The lubricating oil dispensing system of any one of claims 7 to 9 wherein,

The multi-pipe rotary joint (200) is also in fluid connection with the oil drain hole of the bearing,

Wherein the lubrication oil distribution system further comprises an oil/gas separation system fluidly coupled to the multi-pipe swivel (200) to receive a mixture of lubrication oil and air discharged from the oil drain holes of the bearings and to separate lubrication oil from air in the mixture.