CN111396455A - Wind power generation main shaft system - Google Patents
Wind power generation main shaft system Download PDFInfo
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- CN111396455A CN111396455A CN202010347218.XA CN202010347218A CN111396455A CN 111396455 A CN111396455 A CN 111396455A CN 202010347218 A CN202010347218 A CN 202010347218A CN 111396455 A CN111396455 A CN 111396455A
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- bearing
- main shaft
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- static pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0629—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion
- F16C32/064—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion the liquid being supplied under pressure
- F16C32/0651—Details of the bearing area per se
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03D—WIND MOTORS
- F03D15/00—Transmission of mechanical power
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03D—WIND MOTORS
- F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
- F03D80/70—Bearing or lubricating arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0629—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0629—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion
- F16C32/064—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion the liquid being supplied under pressure
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/70—Wind energy
- Y02E10/72—Wind turbines with rotation axis in wind direction
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Sustainable Energy (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Sliding-Contact Bearings (AREA)
- Wind Motors (AREA)
- Support Of The Bearing (AREA)
Abstract
The invention discloses a wind power generation main shaft system, which belongs to the field of wind power generation and comprises a wind power main shaft, wherein a main shaft shell is sleeved outside the wind power main shaft, a conical dynamic and static pressure sliding bearing is arranged between the main shaft shell and the wind power main shaft, an oil inlet channel is arranged on the main shaft shell, and the oil inlet channel is connected with the conical dynamic and static pressure sliding bearing. The outer layer of the outer ring of the conical static pressure sliding bearing is a steel ring, the middle part of the outer ring is a copper alloy layer, and the inner layer of the outer ring of the conical static pressure sliding bearing is a friction coating. The bearing oil of the hydraulic system has medium pressure and high pressure. The outer ring of the conical dynamic and static pressure bearing is formed by three parts, the rigidity and the strength of the whole bearing can be increased by taking the bearing outer ring as steel, the elastic modulus can be reduced by copper alloy, the elastic deformation is easy, the offset load of the bearing is reduced, and the self-adaptive function is realized. Compared with a rolling bearing, the conical dynamic and static pressure sliding bearing is smaller in volume and lower in cost.
Description
Technical Field
The invention relates to the field of wind power generation, in particular to a wind power generation main shaft system.
Background
Wind turbine generators work in the field all the year round, and have severe working conditions, large temperature and humidity changes and complex loading conditions, so that wind turbine bearings are required to have good impact resistance, sealing and lubricating properties, long service life and high reliability. The wind power bearing is an important supporting component of the wind turbine generator and plays an important role in the service life, performance and reliability of the whole generator.
The main shaft of the wind turbine mainly bears the weight load of the blades and the hub of the wind turbine, the dead weight load of the main shaft, the supporting force and the thrust force of the main shaft bearing, the inertial load and the pneumatic load of the wind acting on the main shaft through the blades and the hub, and the like, so that the main shaft needs to bear the radial force and the axial force generated by the wind. In addition, due to the particularity of the working environment of the fan, axial impact can be generated along with sudden change of the wind speed. The bearing inner ring of the fan main shaft is arranged with the fan main shaft through interference fit, the bearing outer ring is fixed on a special support of the frame, and the axial force born by the bearing inner ring is applied on the end surface of the bearing inner ring by the shaft shoulder of the main shaft
Only a portion of the rollers in a running bearing are typically loaded at the same time, and the region where the rollers are located is referred to as the load-bearing region of the bearing. The bearing bears the load and the running clearance has influence on the bearing area. If the load bearing zone is too small, the rollers are prone to slipping during actual operation.
The rotating speed of the input shaft of the wind power gear box is generally 10-20 rpm, and the oil film of the input shaft bearing, namely the planet carrier supporting bearing, is difficult to form due to the low rotating speed.
With the increasing capacity of a single machine of the wind turbine generator and the diameter of the main shaft and the balance consideration of the cost performance of the generator, the price of the main shaft bearing is very high.
Disclosure of Invention
In order to solve the problems in the prior art, the invention provides a wind power generation main shaft system.
The technical scheme of the invention is as follows: the utility model provides a wind power generation main shaft system, includes the wind-powered electricity generation main shaft, the wind-powered electricity generation main shaft overcoat is equipped with main shaft housing, be equipped with toper hybrid slide bearing between main shaft housing and the wind-powered electricity generation main shaft, the last oil feed passageway that is equipped with of main shaft housing, the oil feed passageway is connected with toper hybrid slide bearing.
The conical dynamic and static pressure sliding bearing is divided into a bearing inner ring and a bearing outer ring, the outer layer of the bearing outer ring is a steel ring, the middle part of the bearing outer ring is a copper alloy layer, and the inner surface of the bearing outer ring is a friction layer and a coating.
And one or more oil inlet cavities and a middle ring groove are arranged on the conical dynamic and static pressure sliding bearing, each oil inlet cavity is connected with the middle ring groove, and the oil inlet cavities are communicated with the bearing inner ring of the conical dynamic and static pressure sliding bearing and the matching gap of the bearing outer ring.
And a disc spring is arranged between the conical dynamic and static pressure sliding bearing and the main shaft shell.
The outer ring friction surface of the conical sliding bearing is concave micro arc-shaped.
The end parts of the main shaft shell and the wind power main shaft are sealed through end covers.
The oil inlet channel is connected with a hydraulic control system, the hydraulic control system comprises an oil tank, an oil pump, a cooler, an oil filter, a secondary pressure control valve, a first overflow valve and a first lubricating oil outlet, the oil tank is connected with the oil pump, the oil pump is connected with the cooler, the cooler is connected with the oil filter, the oil filter is connected with the secondary pressure control valve, the secondary pressure control valve is connected with the first lubricating oil outlet, the first lubricating oil outlet is connected with the oil inlet channel, and the first overflow valve is connected between the secondary pressure control valve and the first lubricating oil outlet.
The second-stage pressure control valve is connected with a second lubricating oil outlet, the second lubricating oil outlet is connected with the gear box, and a second overflow valve is connected between the second-stage pressure control valve and the second lubricating oil outlet.
The front end of the wind power main shaft is connected with a hub, the main shaft shell is integrated with the mounting support, the rear end of the wind power main shaft is connected with a planet carrier through a bolt and a pin, a planet shaft is arranged on the planet carrier, and the planet shaft is connected with a gear box.
The bearing capacity of the oil film of the conical dynamic and static pressure sliding bearing meets the following requirements:
P＝F2＝F+F1，
P1＝Psinβ，
P2＝Pcosβ，
p is the bearing capacity of the oil film of the conical dynamic and static pressure sliding bearing,
P1is the axial force of the oil film of the conical dynamic and static pressure sliding bearing,
P2is the radial force of the oil film of the conical dynamic and static pressure sliding bearing,
f is the static pressure, and F is the static pressure,
F1is the bearing capacity of the conical dynamic pressure sliding bearing,
F2is the bearing capacity of the oil film of the conical dynamic and static pressure sliding bearing,
wherein L is the width of bearing, A is correction coefficient, and A is A1A2；A1A is a pressure end leakage coefficient of the bearing, and A is more than or equal to 0.91≤1.0；A2For the correction of the coefficient of elastic deformation of the bearing, A21.0; psi ═ e/is the relative eccentricity of the bearing; omega is the pressure intensity amplitude and the pressure intensity amplitude,
μ is dynamic viscosity.
The outer ring of the conical dynamic and static pressure bearing adopted by the invention is composed of three parts, the rigidity and the strength of the whole bearing can be increased due to the fact that the outer ring of the bearing is made of steel, the elastic modulus can be reduced due to copper alloy, the elastic deformation is easy, the unbalance loading of the bearing is reduced, the self-adaptive function is realized, the inner concave micro-arc shape modification is adopted for the outer ring friction surface of the bearing, an oil film is not easy to leak, and compared with a rolling bearing, the conical dynamic and static pressure bearing is smaller in. The secondary pressure control valve can control to generate medium-pressure oil pressure and high-pressure oil pressure, and can select proper oil pressure according to the wind speed to ensure that the bearing has proper bearing capacity.
Drawings
FIG. 1 is a schematic structural view of the present invention;
FIG. 2 is a schematic structural view of the present invention;
FIG. 3 is a schematic structural view of the present invention;
FIG. 4 is a side view of FIG. 3;
FIG. 5 is a schematic structural view of a conical dynamic-static pressure sliding bearing;
FIG. 6 is a schematic structural diagram of an outer ring of a conical dynamic-static pressure sliding bearing;
FIG. 7 is a schematic structural diagram of an outer ring of a conical dynamic-static pressure sliding bearing;
FIG. 8 is a schematic structural diagram of an inner ring of a conical dynamic-static pressure sliding bearing;
FIG. 9 is a structural schematic diagram of the friction surfaces of the outer ring and the inner ring of the conical dynamic-static pressure sliding bearing;
FIG. 10 is a schematic diagram of the hydraulic control system;
FIG. 11 is a schematic diagram of the pressure curve of the oil film of the conical dynamic-static pressure sliding bearing;
in the figure: 1-wind power main shaft, 2-main shaft shell, 3-conical dynamic and static pressure sliding bearing, 4-disc spring, 5-planet carrier, 6-planet shaft, 7-gear box, 8-propeller hub, 9-mounting bracket, 10-end cover, 11-oil inlet channel, 12-steel ring, 13-copper alloy layer, 14-friction layer and coating, 15-bearing inner ring, 16-oil tank, 17-oil pump, 18-cooler, 19-oil filter, 20-two-stage pressure control valve, 21-first lubricating oil outlet, 22-first overflow valve, 23-oil inlet chamber, 24-second lubricating oil outlet, 25-second overflow valve, 26-outer ring friction surface, 27-inner ring friction surface and 28-bolt.
Detailed Description
The invention is further described below with reference to the accompanying drawings:
as shown in fig. 1-4, a wind power generation main shaft system comprises a wind power main shaft 1, a main shaft shell 2 is sleeved outside the wind power main shaft 1, two conical dynamic and static pressure sliding bearings 3 are arranged between the main shaft shell 2 and the wind power main shaft 1, an oil inlet channel 11 is arranged on the main shaft shell 2, and the oil inlet channel 11 is connected with the conical dynamic and static pressure sliding bearings 3. The end parts of the spindle housing 2 and the wind-powered spindle 1 are sealed by an end cover 10. A disc spring 4 can be arranged between the conical dynamic and static pressure sliding bearing 3 and the main shaft shell 2, and the disc spring 4 plays a role in automatically adjusting the bearing oil clearance. The front end of the wind power main shaft 1 is connected with a propeller hub 8, the main shaft shell 2 and a mounting bracket 9 are integrated, and the mounting bracket 9 is a circular flange. The rear end of the wind power main shaft 1 is connected with a planet carrier 5 through a bolt 28 or a pin shaft (for a semi-direct drive unit), a planet shaft 6 is arranged on the planet carrier 5, the planet shaft 6 is connected with a gear box 7, and the gear box 7 is connected with a generator. The rear end of the wind power main shaft 1 is connected with a generator flange (for a direct drive unit). During assembly, firstly, the left conical dynamic and static pressure sliding bearing 3 is installed on the wind power main shaft 1, then the main shaft shell 2 is installed, then the right conical dynamic and static pressure sliding bearing 3 is installed, and finally the planet carrier 5 is installed. The wind power main shaft 1 is a hollow short shaft cast by high-strength nodular cast iron or high-strength alloy steel, the diameter is large, the weight is light, the rigidity is large, two ends of the wind power main shaft 1 are supported by conical dynamic and static pressure sliding bearings, the excircle of the bearing is supported on a main shaft shell, a disk spring 4 is used for pre-tightening and damping, and the bearing clearance is determined by design calculation and wind load.
As shown in fig. 5-9, the tapered dynamic-static pressure sliding bearing 3 is a low-speed tapered dynamic-static pressure sliding bearing, the tapered dynamic-static pressure sliding bearing 3 is divided into a bearing inner ring and a bearing outer ring, the bearing inner ring and the bearing outer ring are used in cooperation, the outer layer of the bearing outer ring is a steel ring 12, the middle part is a copper alloy layer 13, and the inner surface is a friction layer and a coating 14. The friction layer is made of friction materials, such as babbitt metal, polytetrafluoroethylene, composite materials and the like; the coating is a coating for increasing friction performance, such as molybdenum-based material (molybdenum disulfide), polytetrafluoroethylene and the like, and is used for preventing abrasion caused by excessive friction generated when an oil film is too thin, or playing a role of protecting a friction layer when a hydraulic system fails, and the bearing inner ring is made of alloy steel. The inner surface of the bearing outer ring can be specifically designed as follows: 1. the aluminum-zinc alloy is a friction material, and the molybdenum-based material or the polytetrafluoroethylene is a coating; 2. babbitt metal is a friction material, and polytetrafluoroethylene is a coating. The bearing outer ring is made of steel, so that the rigidity and the strength of the whole bearing can be improved, and the copper alloy is used for reducing the elastic modulus, is easy to elastically deform, reduces the offset load of the bearing and has a self-adaptive function. The conical dynamic and static pressure bearing can bear axial force and radial force.
Be equipped with one or more oil feed chamber 15 and middle annular on toper hybrid sliding bearing 3's the bearing inner race, each oil feed chamber 15 communicates each other through middle annular, oil feed chamber 15 is linked together with toper hybrid sliding bearing 3's bearing inner race and bearing inner race's fit clearance.
The advantages of using the composite bearing structure are: compared with a radial cylindrical bearing, when a main shaft is subjected to bending moment, the cylindrical bearing is subjected to unbalance loading, one side of a gap between the main shaft and the bearing is large, the other side of the gap is small, high-pressure oil is easy to leak, oil film pressure is not easy to build, and energy consumption is high; the intermediate layer of the bearing outer ring is made of copper alloy, so that the elastic modulus is relatively small, the bearing outer ring is easy to elastically deform, and the bearing unbalance loading is reduced.
The outer ring friction surface 26 of the conical sliding bearing 3 adopts an inward concave micro arc modification. The arc is designed according to the optimal value of bearing deformation. The bearing can deform after being stressed, and the internal oil inlet film also needs space. The bearing is just in a straight line after being subjected to load deformation, and an oil film in the bearing is not easy to leak out.
The price of the large rolling bearing is very high, and the relative price of the dynamic and static pressure sliding bearing is much lower. The conical dynamic and static pressure sliding bearing can save space and is smaller than a rolling bearing, so that the main shaft system is small in overall size. The hydraulic system can be shared with the wind power gear box.
As shown in fig. 10, the oil feed passage 11 is connected to a hydraulic control system including an oil tank 16, an oil pump 17, a cooler 18, an oil filter 19, a secondary pressure control valve 20, a first relief valve 22, and a first lube oil outlet 21, the oil tank 16 is connected to the oil pump 17, the oil pump 17 is connected to the cooler 18, the cooler 18 is connected to the oil filter 19, the oil filter 19 is connected to the secondary pressure control valve 20, the secondary pressure control valve 20 is connected to the first lube oil outlet 21, the first lube oil outlet 21 is connected to the oil feed passage 11, and the first relief valve 22 is connected between the secondary pressure control valve 20 and the first lube oil outlet 21. The hydraulic control system can use a wind power gear box body as an oil pool, and can also be externally hung with an oil tank, a high-pressure gear pump is used as an oil pump, a cooler is air-cooled or water-cooled, the filter is the same as a wind power conventional filter, a secondary pressure control valve is electrically controlled and accords with wind power standards, the secondary pressure control valve controls two oil pressures (high pressure and medium pressure), a high-pressure oil and a medium-pressure oil are generated at an oil inlet of the control valve, and the high-pressure oil and the medium-pressure oil are used for providing a dynamic and static; the bearings are lubricated with high pressure oil at high wind speeds and with medium pressure oil at low wind speeds. Each lubricating oil port at the oil outlet of the control valve is provided with a throttle valve and an overflow valve to generate low pressure oil to lubricate the bearings and gears of the gear box when the unit is in normal operation. When the wind turbine generator is influenced by high wind speed, high-pressure oil generated by the secondary pressure control valve 20 enters the oil inlet cavity of the conical dynamic and static pressure sliding bearing 3 through the oil inlet channel 11 and then enters the space between the bearing outer ring and the bearing inner ring to form an oil film to play a role in resisting impact and lubricating. When the wind turbine generator is influenced by low wind speed, the secondary pressure control valve 20 can generate medium pressure oil, so that the fit clearance between the bearing outer ring and the bearing inner ring is proper in size, the phenomenon of slipping in operation can be prevented, and energy consumption is reduced. The secondary pressure control valve 20 is connected with a second lubricating oil outlet 24, the second lubricating oil outlet 24 is connected with the gear box 7, a second overflow valve 25 is connected between the secondary pressure control valve 20 and the second lubricating oil outlet 24, and the second overflow valve 25 can also generate low-pressure oil to lubricate bearings and gears of the gear box 7 when the unit operates normally.
As shown in fig. 11, the bearing capacity of the oil film of the conical dynamic-static pressure sliding bearing 3 satisfies the following requirements:
P＝F2＝F+F1，
P1＝Psinβ，
P2＝Pcosβ，
p is the bearing capacity of the oil film of the conical dynamic and static pressure sliding bearing,
P1is the axial force of the oil film of the conical dynamic and static pressure sliding bearing,
P2is a conical dynamic and static pressure sliding shaftThe radial force of the oil film of the bearing,
f is the static pressure, and F is the static pressure,
F1is the bearing capacity of the conical dynamic pressure sliding bearing,
F2is the bearing capacity of the oil film of the conical dynamic and static pressure sliding bearing,
wherein L is the width of bearing, A is correction coefficient, and A is A1A2；A1A is a pressure end leakage coefficient of the bearing, and A is more than or equal to 0.91≤1.0；A2For the correction of the coefficient of elastic deformation of the bearing, A21.0; psi ═ e/is the relative eccentricity of the bearing; omega is the pressure intensity amplitude and the pressure intensity amplitude,
μ is dynamic viscosity.
Claims (10)
1. A wind power generation main shaft system comprises a wind power main shaft (1), and is characterized in that: the wind power main shaft (1) overcoat is equipped with main shaft housing (2), be equipped with toper hybrid slide bearing (3) between main shaft housing (2) and wind power main shaft (1), be equipped with oil feed passageway (11) on main shaft housing (2), oil feed passageway (11) are connected with toper hybrid slide bearing (3).
2. A wind power spindle system according to claim 1, wherein: the conical dynamic and static pressure sliding bearing (3) is divided into a bearing inner ring and a bearing outer ring, the outer layer of the bearing outer ring is a steel ring (12), the middle part of the bearing outer ring is a copper alloy layer (13), and the inner surface of the bearing outer ring is a friction layer and a coating (14).
3. A wind power spindle system according to claim 1, wherein: be equipped with oil feed chamber (15) and middle annular on the bearing inner race of toper hybrid slide bearing (3), oil feed chamber (15) and middle annular communicate mutually, oil feed chamber (15) are linked together with the bearing inner race of toper hybrid slide bearing (3) and the fit clearance of bearing inner race.
4. A wind power spindle system according to claim 1, wherein: and a disc spring (4) is arranged between the conical dynamic and static pressure sliding bearing (3) and the main shaft shell (2).
5. A wind power spindle system according to claim 1, wherein: and an outer ring friction surface (26) of the conical sliding bearing (3) is subjected to inward concave micro arc modification.
6. A wind power spindle system according to claim 1, wherein: an end cover (10) is arranged at the end part of the main shaft shell (2) and the wind-driven main shaft (1).
7. A wind power spindle system according to claim 1, wherein: the oil inlet channel (11) is connected with a hydraulic control system, the hydraulic control system comprises an oil tank (16), an oil pump (17), a cooler (18), an oil filter (19), a secondary pressure control valve (20), a first overflow valve (22) and a first lubricating oil outlet (21), the oil tank (16) is connected with an oil pump (17), the oil pump (17) is connected with a cooler (18), the cooler (18) is connected to an oil filter (19), the oil filter (19) is connected to a secondary pressure control valve (20), the secondary pressure control valve (20) is connected to a first lube oil outlet (21), the first lubricating oil outlet (21) is connected with the oil inlet channel (11), a first overflow valve (22) is connected between the second-stage pressure control valve (20) and the first lubricating oil outlet (21), the secondary pressure control valve (20) can be controlled to generate both medium and high oil pressures.
8. A wind power spindle system according to claim 7, wherein: the secondary pressure control valve (20) is connected with a second lubricating oil outlet (24), the second lubricating oil outlet (24) is connected with the gear box (7), and a second overflow valve (25) is connected between the secondary pressure control valve (20) and the second lubricating oil outlet (24).
9. A wind power spindle system according to claim 1, wherein: the front end of the wind power main shaft (1) is connected with a hub (8), the main shaft shell (2) and the mounting bracket (9) are integrated, the rear end of the wind power main shaft (1) is connected with the planet carrier (5) through a bolt and a pin, and the planet carrier (5) is connected with the gear box (7).
10. A wind power spindle system according to claim 1, wherein: the bearing capacity of the oil film of the conical dynamic and static pressure sliding bearing (3) meets the following requirements:
P＝F2＝F+F1，
P1＝Psinβ，
P2＝Pcosβ，
p is the bearing capacity of the oil film of the conical dynamic and static pressure sliding bearing,
P1is the axial force of the oil film of the conical dynamic and static pressure sliding bearing,
P2is the radial force of the oil film of the conical dynamic and static pressure sliding bearing,
f is the static pressure, and F is the static pressure,
F1is the bearing capacity of the conical dynamic pressure sliding bearing,
F2is the bearing capacity of the oil film of the conical dynamic and static pressure sliding bearing,
wherein L is the width of bearing, A is correction coefficient, and A is A1A2；A1A is a pressure end leakage coefficient of the bearing, and A is more than or equal to 0.91≤1.0；A2For the correction of the coefficient of elastic deformation of the bearing, A21.0; psi ═ e/is the relative eccentricity of the bearing; omega is the pressure intensity amplitude and the pressure intensity amplitude,
μ is dynamic viscosity.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010347218.XA CN111396455A (en) | 2020-04-27 | 2020-04-27 | Wind power generation main shaft system |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010347218.XA CN111396455A (en) | 2020-04-27 | 2020-04-27 | Wind power generation main shaft system |
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| CN111396455A true CN111396455A (en) | 2020-07-10 |
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| CN202010347218.XA Pending CN111396455A (en) | 2020-04-27 | 2020-04-27 | Wind power generation main shaft system |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115111345A (en) * | 2022-08-22 | 2022-09-27 | 太原科技大学 | A wind power speed-increasing gearbox with radial/thrust sliding bearing combined support structure |
| CN115163658A (en) * | 2022-07-22 | 2022-10-11 | 中国华能集团清洁能源技术研究院有限公司 | Sliding main bearing and its assembly method, wind turbine transmission system |
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2020
- 2020-04-27 CN CN202010347218.XA patent/CN111396455A/en active Pending
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115163658A (en) * | 2022-07-22 | 2022-10-11 | 中国华能集团清洁能源技术研究院有限公司 | Sliding main bearing and its assembly method, wind turbine transmission system |
| CN115163658B (en) * | 2022-07-22 | 2024-08-09 | 中国华能集团清洁能源技术研究院有限公司 | Sliding main bearing and assembly method thereof, and wind turbine transmission system |
| CN115111345A (en) * | 2022-08-22 | 2022-09-27 | 太原科技大学 | A wind power speed-increasing gearbox with radial/thrust sliding bearing combined support structure |
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