CN116025510A - Speed regulating device for wind driven generator and wind driven generator set - Google Patents
Speed regulating device for wind driven generator and wind driven generator set Download PDFInfo
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- CN116025510A CN116025510A CN202310159986.6A CN202310159986A CN116025510A CN 116025510 A CN116025510 A CN 116025510A CN 202310159986 A CN202310159986 A CN 202310159986A CN 116025510 A CN116025510 A CN 116025510A
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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
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- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
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- Y02E10/72—Wind turbines with rotation axis in wind direction
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Abstract
The invention relates to the technical field of wind power generation, and particularly discloses a speed regulating device for a wind power generator and a wind power generator set, wherein the speed regulating device comprises a differential planetary speed regulating gear box, at least one speed regulating motor gearbox and at least one speed regulating motor, the differential planetary speed regulating gear box comprises a gear ring, the speed regulating motor gearbox is connected with the gear ring, the speed regulating motor gearbox comprises a first transmission path used for generating electricity and a second transmission path used for electric power, the first transmission path comprises a first gear and a second gear which are meshed, the first gear is connected with the gear ring, the second gear is connected with the speed regulating motor, and the number of teeth of the first gear is larger than that of the second gear. According to the invention, different transmission paths are adopted by bidirectional transmission between the gear ring and the speed regulating motor, so that the torque of the speed regulating motor in a power generation state is reduced, and the size and weight of the speed regulating motor are reduced.
Description
Technical Field
The invention relates to the technical field of wind power generation, in particular to a speed regulating device for a wind power generator and a wind power generator set.
Background
In recent years, the gradually developed power grid friendly wind power technology takes a front stepless speed regulation technology as a core, and adopts a constant-speed synchronous generator to ensure that the rotating speed of the generator is always kept near the synchronous rotating speed. The prepositive stepless speed regulating technology mainly comprises three technologies of hydraulic torque variable speed regulation, electromagnetic coupling speed regulation and differential gear speed regulation. In the differential planetary gear speed regulation technology commonly used in the prior art, differential gear speed regulation mainly utilizes the principle of motion synthesis to synthesize two input motions into one output motion. Specifically, the wind wheel drives a planet carrier of the differential planetary speed regulating gearbox to rotate through the speed increasing gearbox, and the input rotation speed is the input rotation speed; the speed regulating motor drives the gear ring of the differential planetary speed regulating gear box to rotate, and the speed regulating speed is the speed regulating rotating speed; the planetary gears of the differential planetary speed regulating gear box combine the input rotation speed and the speed regulating rotation speed to form the constant rotation speed of the sun gear of the differential planetary speed regulating gear box, and the constant rotation speed is output to the synchronous generator.
The speed regulating motor has an electric state and a power generation state; when the external wind speed is smaller than a certain value, the rotation after the wind wheel is accelerated is insufficient to enable the rotation speed of the synchronous generator to reach the set rotation speed of grid-connected power generation after being changed by the differential gear speed regulating box, the speed regulating motor is in an electric state, and the speed regulating motor drives the gear train in the differential gear speed regulating box to rotate so as to drive the synchronous generator to rotate. When the external wind speed is greater than a certain value, the rotation after the wind wheel is accelerated is changed in speed by the differential gear speed regulating box, so that the rotation speed of the synchronous generator exceeds the set rotation speed of the grid-connected power generation, at the moment, the speed regulating motor is in a power generation state, and a part of rotation provided by the wind wheel is output to the speed regulating motor through the differential gear speed regulating box to drive the speed regulating motor to generate power.
In the prior art, when the speed regulating motor is in an electric state, the speed regulating motor can reach high rotating speed and low torque; when the speed regulating motor is in a power generation state, the speed regulating motor can reach low rotation speed and high torque. The rotating speed change range of the speed regulating motor is wider, and the torque fluctuation is large. The size and the weight of the speed-adjusting motor are mainly determined by the torque, if the high torque is required to be met, the speed-adjusting motor with larger size is required to be selected, and the weight is larger, so that the speed-adjusting motor has high cost and poor economical efficiency. The inventor aims at searching a method capable of reducing the size of the existing speed regulating motor so as to reduce the cost of the motor.
Disclosure of Invention
The invention aims to overcome the defect of high cost of a speed regulating motor caused by large size and heavy weight of the speed regulating motor in the prior art, and provides a speed regulating device for a wind driven generator and a wind driven generator set.
The invention solves the technical problems by the following technical scheme:
the speed regulating device comprises a differential planetary speed regulating gearbox, at least one speed regulating motor gearbox and at least one speed regulating motor, wherein the speed regulating motor is connected with the differential planetary speed regulating gearbox through the speed regulating motor gearbox;
the differential planetary speed regulation gear box comprises a gear ring, the speed regulation motor gearbox is connected with the gear ring, the speed regulation motor gearbox comprises a first transmission path and a second transmission path, the gear ring and a motor shaft of the speed regulation motor realize transmission through the first transmission path and the second transmission path,
when the speed regulating motor is in a power generation state, the first transmission path is in a passage state, and the second transmission path is in a disconnection state;
when the speed regulating motor is in an electric state, the first transmission path is in a disconnected state, and the second transmission path is in a passage state;
wherein the first transmission path comprises a first gear set, the first gear set comprises a first gear and a second gear which are meshed, the first gear is engaged with the gear ring, the second gear is connected with the speed regulating motor, and the number of teeth Z of the first gear 42 Greater than the number Z of teeth of the second gear 43 。
In the scheme, when the wind speed is low, the rotating speed of the wind wheel is low, wind energy captured by the wind wheel is low, the rotating speed of a planet carrier of a corresponding differential planetary speed regulating gearbox is also low, the torque required for supplying the differential planetary speed regulating gearbox to a gear ring is low and the rotating speed is high, namely, the speed regulating motor is required to operate in an electric state, and the torque is low and the rotating speed is high; when the wind speed is high, the rotating speed of the wind wheel is high, the wind energy captured by the wind wheel is high, the rotating speed of a corresponding planet carrier of the differential planetary speed regulating gearbox is high, the torque distributed to a gear ring is high, the rotating speed is not high, the speed regulating motor is in a power generation state, if the rotating speed is still according to the original transmission path, the torque of the speed regulating motor is larger than the torque in an electric state, but the rotating speed is not high, therefore, the bidirectional transmission between the speed regulating motor and the gear ring is respectively transmitted through different transmission paths, two gears with different teeth are arranged in a first transmission path for realizing transmission under the power generation state of the speed regulating motor, the first gear with the large teeth is connected with the gear ring, the second gear with the small teeth is connected with the speed regulating motor, the effect of improving the rotating speed and reducing the torque is realized by reducing the transmission ratio between the first gear and the second gear, and the size and the weight of the speed regulating motor are reduced because the power generation state and the path of the electric state are mutually independent, and the rotating speed of the electric state cannot be influenced, and the production cost of the speed regulating motor is reduced.
Preferably, the speed regulating device further comprises a controller, and the controller is used for controlling the on-off of the first transmission path and the second transmission path.
In the scheme, the on-off of the first transmission path and the second transmission path is controlled by the controller, and the control process is automatic.
Preferably, the first transmission path further comprises a first clutch, a first gear shaft and a second gear shaft, the first gear is fixedly sleeved on the first gear shaft, the second gear shaft is connected with the speed regulating motor, the second gear is connected with the second gear shaft through the first clutch, and the controller is electrically connected with the first clutch and used for controlling connection and disconnection of the first clutch;
when the first clutch is in a connection state, the second gear is in transmission communication with the second gear shaft; when the first clutch is in an off state, transmission between the second gear and the second gear shaft is disconnected.
In the scheme, the connection and disconnection of the first clutch are controlled by the controller, so that the transmission on-off between the second gear and the input shaft can be realized, and the on-off of the first transmission path is realized.
Preferably, the second transmission path includes a second gear set including a third gear and a fourth gear meshed with each other, the third gear being connected to the speed motor, the fourth gear being engaged with the ring gear.
In this scheme, through the cooperation between third gear and the fourth gear, realize the transmission.
Preferably, the second transmission path further comprises a second clutch, a third gear shaft and a fourth gear shaft, the third gear is fixedly sleeved on the third gear shaft, the third gear shaft is connected with the speed regulating motor, the fourth gear is connected with the fourth gear shaft through the second clutch, and the controller is electrically connected with the second clutch and used for controlling connection and disconnection of the second clutch;
when the second clutch is in a connection state, the fourth gear is in transmission communication with the fourth gear shaft; when the second clutch is in an off state, transmission between the fourth gear and the fourth gear shaft is disconnected.
In the scheme, the connection and disconnection of the second clutch are controlled by the controller, so that the transmission on-off between the fourth gear and the pinion shaft can be realized, and the on-off of the second transmission path is realized.
Preferably, the first transmission path and the second transmission path each further comprise a pinion, a pinion shaft and an input shaft for connecting the speed regulating motor, the pinion shaft comprises the first gear shaft and the fourth gear shaft, the input shaft comprises the second gear shaft and the third gear shaft, the pinion is connected with the gear ring, and the pinion is fixedly sleeved on the pinion shaft;
the first gear is fixedly sleeved on the pinion shaft, and the second gear is connected with the input shaft through the first clutch; the third gear is fixedly sleeved on the input shaft, and the fourth gear is connected with the pinion shaft through the second clutch.
In this scheme, pinion shaft and input shaft are the shared part of first transmission route and second transmission route, be convenient for connect the dress between speed governing motor gearbox and the speed governing motor, if there is not the pinion, first gear train in the speed governing motor gearbox, second gear train is connected with the ring gear directly, can lead to the input of first transmission route, the output of second transmission route is not on same axis, consequently, can at least one be the same with speed governing motor's motor shaft in the input of first transmission route, the output of second transmission route is different, need through belt drive or chain drive, the structure can be more complicated, this scheme can make the input of first transmission route, the output of second transmission route both be located same axis and connect speed governing motor's motor shaft through setting up the pinion, transmission structure is simpler.
Preferably, the first clutch and the second clutch are both bidirectional transmission clutches.
In the scheme, the first transmission path and the second transmission path can realize bidirectional transmission, and when the first clutch and the second clutch are in a closed state, the first clutch and the second clutch can play a role in braking the gear ring.
Preferably, the number of teeth Z of the third gear 45 Equal to the number Z of teeth of the fourth gear 48 。
In the scheme, when the speed regulating motor is in an electric state, the speed is not increased by a gear when the speed regulating motor is driven to the pinion.
Preferably, the differential planetary speed regulation gearbox and the speed regulation motor gearbox adopt an integrated box body structure.
In this scheme, integral type box structure is more convenient for split type structure, installs, need not to separately transport and assembles again.
Preferably, the speed-regulating motor gearboxes are arranged on two sides of the differential planetary speed-regulating gearbox, and the speed-regulating motor is arranged corresponding to the speed-regulating motor gearboxes.
In this scheme, set up a plurality of buncher and buncher, fault-tolerant rate is higher.
The invention also provides a wind generating set, which comprises a wind wheel, a synchronous generator and the speed regulating device for the wind generator, wherein the wind wheel is connected with the input end of the differential planetary speed regulating gearbox, and the synchronous generator is connected with the output end of the differential planetary speed regulating gearbox.
The invention has the positive progress effects that: according to the invention, different transmission paths are adopted through bidirectional transmission between the gear ring and the speed regulating motor, so that the torque requirement of the speed regulating motor in a power generation state is reduced, and the size and weight of the speed regulating motor are reduced.
Drawings
Fig. 1 is a schematic structural view of a wind turbine generator system according to embodiment 1 of the present invention.
Fig. 2 is an enlarged view of the differential planetary speed gearbox and speed motor gearbox of fig. 1.
Fig. 3 is a schematic structural diagram of a wind turbine generator system of the prior art.
Fig. 4 is an enlarged view of the differential planetary speed gearbox of fig. 3.
Fig. 5 is a graph of captured power versus rotational speed characteristics of a wind turbine of an original design.
Fig. 6 is a graph showing the variation characteristic of the rotation speed of the planet carrier with the wind speed according to the original design.
Fig. 7 is a graph showing the variation of the rotational speed of the ring gear with the wind speed according to the original design.
Fig. 8 is a characteristic curve of the torque variation of the speed regulating motor with the wind speed according to the original design.
Fig. 9 is a graph of the speed-torque characteristic of the conventionally designed motor.
FIG. 10 is a graph showing the rotation speed-torque characteristic of the motor according to embodiment 1 of the present invention
Fig. 11 is a schematic diagram of an applied structure of a differential planetary speed change gear box and a speed change motor gearbox according to embodiment 2 of the present invention.
The reference numerals include:
example 1:
Speed increasing gear box 2
Differential planetary speed-regulating gearbox 3
Speed-regulating motor gearbox 4
First clutch 41
Main brake 6
Example 2:
Differential planetary speed-regulating gearbox 3
Speed-regulating motor gearbox 4
Second coupling 6
Compressor or pump load 7
Detailed Description
The invention is further illustrated by means of the following examples, which are not intended to limit the scope of the invention.
Example 1
Referring to fig. 1 and 2, the present embodiment provides a wind generating set, which includes a wind wheel 1, a speed increasing gearbox 2, a speed adjusting device, a coupling 7 and a synchronous generator 8.
The speed regulating device comprises a differential planetary speed regulating gearbox 3, at least one speed regulating motor 5 and at least one speed regulating motor gearbox 4, wherein the speed regulating motor 5 is connected with the differential planetary speed regulating gearbox 3 through the speed regulating motor gearbox 4.
The number of the speed regulating motors 5 and the speed regulating motor gearboxes 4 can be one or more, and the speed regulating motors 5 and the speed regulating motor gearboxes 4 are the same in number and are arranged in a one-to-one correspondence manner. In this embodiment, the number of the speed-adjusting motors 5 is two, and correspondingly, the number of the speed-adjusting motor gearboxes 4 is also two, and the two speed-adjusting motor gearboxes 4 are respectively arranged at two sides of the differential planetary speed-adjusting gearbox 3. The capacity of a single speed motor 5 can be reduced by providing two speed motors 5 so that a more versatile, lower cost speed motor 5 is used. In other embodiments, the speed adjusting motor 5 may be provided in one, three, or another number, not limited to the present embodiment.
The differential planetary speed adjusting gearbox 3 includes a differential speed adjusting gearbox housing, a ring gear 32 rotatably provided in the differential speed adjusting gearbox housing, a sun gear 33 rotatably provided in the ring gear 32, planetary gears 34 rotatably provided between the sun gear 33 and an inner ring of the ring gear 32, and a carrier 31 for supporting the planetary gears 34.
The wind wheel 1 is connected with the input end of the speed increasing gear box 2, the planet carrier 31 of the differential planetary speed adjusting gear box 3 is connected with the output end of the speed increasing gear box 2, the sun gear 33 of the differential planetary speed adjusting gear box 3 is connected with the synchronous generator 8 through the coupler 7, and the main brake 6 is arranged between the sun gear and the coupler 7. Under the condition that the rotating speed of the wind wheel 1 is lower, the rotation of the wind wheel 1 is input from the input end of the speed increasing gear box 2 at a lower rotating speed and is increased through the speed increasing gear box 2, and the output end of the speed increasing gear box 2 outputs to the differential planetary speed regulating gear box 3 at a higher rotating speed, so that the rotating speed of the rotation input into the differential planetary speed regulating gear box 3 when the rotating speed of the wind wheel 1 is lower can also reach the required rotating speed.
In the embodiment, the speed increasing gear box 2 and the differential planetary speed regulating gear box 3 are designed in a split way, and the speed increasing gear box 2 can be detached from the differential planetary speed regulating gear box 3 so as to be convenient for transportation. In other embodiments, the speed increasing gear box 2 and the differential planetary speed adjusting gear box 3 may be combined and designed as a whole according to the circumstances, and the speed increasing gear box 2 and the differential planetary speed adjusting gear box 3 form a one-piece gear box, which is not limited to the present embodiment.
In the embodiment, the differential planetary speed-regulating gearbox 3 and each speed-regulating motor gearbox 4 are designed into an integral structure, and the differential planetary speed-regulating gearbox 3 and the speed-regulating motor gearboxes 4 form an integral gearbox. In other embodiments, the differential planetary speed-adjusting gearbox 3 and the speed-adjusting motor gearboxes 4 may be designed separately according to the situation, and each speed-adjusting motor gearbox 4 may be detached from the differential planetary speed-adjusting gearbox 3 for transportation, which is not limited to the present embodiment.
The speed-adjusting motor 5 has an electric state and a power generation state. Specifically, when the external wind speed is smaller than a certain value, the rotation of the wind wheel 1 after speed increasing is insufficient to enable the rotation speed of the synchronous generator 8 to reach the set rotation speed of grid-connected power generation after speed changing through the differential gear speed regulating box 3, the speed regulating motor 5 is in an electric state, and the speed regulating motor 5 drives the gear train in the differential gear speed regulating box 3 to rotate so as to drive the synchronous generator 8 to rotate. When the external wind speed is greater than a certain value, the rotation of the wind wheel 1 after speed increasing is changed through the differential gear speed regulating box 3, so that the rotation speed of the synchronous generator 8 exceeds the set rotation speed of grid-connected power generation, at the moment, the speed regulating motor 5 is in a power generation state, and part of the rotation provided by the wind wheel 1 is output to the speed regulating motor 5 through the differential gear speed regulating box 3 to drive the speed regulating motor 5 to generate power. The external wind speed makes a certain value to be reached by the change state of the speed regulating motor 5 not be a specific value, and the specific value needs to be designed according to factors such as power of a wind generating set.
The speed-adjusting motor gearbox 4 comprises a speed-adjusting gearbox shell, a first transmission path and a second transmission path which are arranged in the speed-adjusting gearbox shell, and transmission is realized between the gear ring 32 and a motor shaft of the speed-adjusting motor 5 through the first transmission path and the second transmission path. Specifically, the first transmission path is used to realize transmission between the ring gear 32 and the motor shaft of the speed motor 5 when the speed motor 5 is in the power generation state. The second transmission path is used for realizing transmission between the gear ring 32 and the motor shaft of the speed regulating motor 5 when the speed regulating motor 5 is in an electric state. When the speed regulating motor 5 is in a power generation state, the first transmission path is in a passage state, and the second transmission path is in a disconnection state; when the speed regulating motor 5 is in an electric state, the first transmission path is in a disconnected state, and the second transmission path is in a passage state. In this embodiment, the bidirectional transmission between the speed-adjusting motor 5 and the gear ring 32 is respectively transmitted through different transmission paths, so that the transmission paths of the speed-adjusting motor 5 in two states are mutually independent and do not interfere with each other.
As shown in fig. 1 and 2, the first transmission path includes a pinion gear 44, a pinion shaft, a first gear set, a first clutch 41, and an input shaft 46. The pinion gear 44 is engaged with the outer ring of the ring gear 32, the pinion gear 44 is fixedly sleeved on a pinion shaft, and two ends of the pinion shaft are rotatably connected to the inner wall of the gearbox housing. One end of the input shaft 46 is located in the gearbox housing and is rotatably connected to the inner wall of the gearbox housing, and the other end extends out of the gearbox housing and is connected to the motor shaft of the speed regulating motor 5. The first gear set includes a first gear 42 and a second gear 43, which are engaged with each other, the first gear 42 is fixedly sleeved on the pinion shaft, and the second gear 43 is connected with the input shaft 46 through the first clutch 41. The first clutch 41 in this embodiment is a two-way transmission clutch, and in other alternative embodiments, it may be a clutch of other configurations.
The present embodiment realizes on-off of the transmission between the second gear 43 and the input shaft 46 by controlling the connection and disconnection of the first clutch 41, thereby realizing on-off of the first transmission path. Specifically, when the first clutch 41 is in the connected state, the second gear 43 is in transmission communication with the input shaft 46, the first transmission path is in communication, and the speed motor 5 can be in the power generation mode. When the first clutch 41 is in the off state, the transmission between the second gear 43 and the input shaft 46 is disconnected, the first transmission path is disconnected, and the speed motor 5 is not in the power generation mode.
Wherein the first gear setMiddle gear tooth number Z 42 ＞Z 43 ，Z 42 For the number of teeth, Z, of the first gear 42 43 The number of teeth of the second gear 43.
In this embodiment, the pinion gear 44 is directly meshed with the outer race of the ring gear 32, and in other embodiments, the pinion gear 44 may be indirectly meshed with the outer race of the ring gear 32 through a plurality of intermediate gears, or the pinion gear 44 may be meshed with the inner race of the ring gear 32 and connected to the pinion shaft through a plurality of intermediate gears. Whether the pinion gear 44 is engaged with the outer ring or the inner ring of the ring gear 32, the pinion gear may be directly engaged with or indirectly engaged with the outer ring or the inner ring of the ring gear 32, and the pinion gear shaft may be rotated by rotating the ring gear 32.
Specifically, the second transmission path includes a pinion gear 44, a pinion shaft, a second gear set including a meshed third gear 45 and a fourth gear 48, a second clutch 47, and an input shaft 46, the third gear 45 being fixedly connected coaxially with the input shaft 46, the fourth gear 48 being connected with the pinion shaft through the second clutch 47. The second clutch 47 in this embodiment is a two-way transmission clutch, and in other alternative embodiments, it may be a clutch of other configurations.
The present embodiment realizes on-off of transmission between the fourth gear 48 and the pinion shaft by controlling connection and disconnection of the second clutch 47, thereby realizing on-off of the second transmission path. Specifically, when the second clutch 47 is in the connected state, the fourth gear 48 is in transmission communication with the pinion shaft, the second transmission path is in communication, and the speed motor 5 is in an electric state. When the second clutch 47 is in the off state, the transmission between the fourth gear 48 and the pinion shaft is disconnected, the second transmission path is disconnected, and the speed motor 5 is not in the electric state.
Wherein the number of gear teeth Z in the second gear set 45 ＝Z 48 ，Z 45 For the number of teeth of the third gear 45, Z 48 The number of teeth of the fourth gear 48.
That is, the pinion gear 44, the pinion shaft, and the input shaft 46 are all common portions of the first transmission path and the second transmission path.
In other embodiments, the first and second transmission paths may not include common portions of the pinion gear 44, the pinion shaft, and the input shaft 46. The specific arrangement is as follows:
the first transmission path only comprises a first gear set and a first clutch 41, the first gear set comprises a first gear 42 and a second gear 43 which are meshed, the first gear 42 is meshed with the outer ring of the gear ring 32, a first gear shaft is fixedly connected in a gear hole of the first gear 42, two ends of the first gear shaft are rotatably connected to the inner wall of the speed changing box shell, a second gear shaft is movably connected in a gear hole of the second gear 43, one end of the second gear shaft is positioned in the speed changing box shell and rotatably connected to the inner wall of the speed changing box shell, and the other end of the second gear shaft extends out of the speed changing box shell and is connected to a motor shaft of the speed changing motor 5. The second gear shaft is connected with the second gear 43 through a first clutch 41, and the first clutch 41 is used for realizing the on-off of transmission between the second gear 43 and the second gear shaft.
The second transmission path only comprises a second gear set and a second clutch 47, the second gear set comprises a third gear 45 and a fourth gear 48 which are meshed with each other, the fourth gear 48 is also meshed with the outer ring of the gear ring 32, a third gear shaft is fixedly connected in a gear hole of the third gear 45, one end of the third gear shaft is positioned on the gearbox shell and is rotatably connected on the inner wall of the gearbox shell, and the other end of the third gear shaft extends out of the gearbox shell and is connected to a motor shaft of the speed regulating motor 5. A fourth gear shaft is movably connected in the gear hole of the fourth gear 48, two ends of the fourth gear shaft are rotatably connected to the inner wall of the gearbox shell, the fourth gear shaft is connected with the fourth gear 48 through a second clutch 47, and the second clutch 47 is used for realizing the on-off of transmission between the fourth gear 48 and the fourth gear shaft.
In these embodiments, since the second gear shaft and the third gear shaft are not on the same axis, the connection between the second gear shaft and the third gear shaft and the motor shaft of the speed-adjusting motor 5 can be made by the existing transmission structure such as chain transmission, belt transmission, etc., only the number of teeth Z of the first gear 42 needs to be ensured 42 Greater than the number Z of teeth of the second gear 43 43 (i.e., the gear ratio between the first gear 42 and the second gear 43 is less than 1). The number of teeth Z of the third gear 45 45 Number of teeth Z with fourth gear 48 48 The ratio of the two is preferably 1, and other values can be designed according to actual conditions.
The pinion shaft in this embodiment includes the first gear shaft and the fourth gear shaft, that is, the pinion shaft serves as both the first gear shaft for connecting the first gear 42 and the fourth gear shaft for connecting the fourth gear 48 as described above, and the integrated pinion shaft structure simplifies the structure as well as makes the first gear shaft and the fourth gear shaft coaxial. In other alternative embodiments, the first gear shaft and the fourth gear shaft may be of a split type structure.
The input shaft 46 in the present embodiment includes the second gear shaft and the third gear shaft, that is, the input shaft 46 serves as both the second gear shaft for connecting the second gear 43 and the third gear shaft for connecting the third gear 45 as described above, and the integrated input shaft 46 has a structure that both simplifies the structure and makes the second gear shaft and the third gear shaft coaxial. In other alternative embodiments, the second gear shaft and the third gear shaft may be of a split type structure.
The speed regulating device of the present embodiment further includes a controller electrically connected to the first clutch 41 and the second clutch 47, and the controller controls on/off of the first transmission path and the second transmission path by controlling connection and disconnection of the first clutch 41 and the second clutch 47.
When the speed-adjusting motor 5 is in the power generation state, that is, in the process of transmitting power from the ring gear 32 to the speed-adjusting motor 5, the first clutch 41 is in the closed state and the second clutch 47 is in the open state, so that the first transmission path is in the passage state and the second transmission path is in the open state, and the power transmission process in the process is as follows: gear ring 32→first gear 42→second gear 43→first clutch 41→input shaft 46.
When the speed-adjusting motor 5 is in an electric state, that is, power is transmitted to the gear ring 32 by the speed-adjusting motor 5, the first clutch 41 is in an open state, and the second clutch 47 is in a closed state, so that the first transmission path is in an open state, and the second transmission path is in a path state, and in this process, the power transmission process is as follows: input shaft 46→third gear 45→fourth gear 48→second clutch 47→pinion gear 44→ring gear 32.
The speed regulating device for the wind driven generator in the embodiment has the advantages of being capable of reducing the size and the weight of a speed regulating motor, and is specifically analyzed as follows:
fig. 3 and 4 show a schematic structural view of a wind power plant of another form of applicant design. The pinion 44' of the wind turbine generator is directly connected with the speed regulating motor 5', the wind wheel 1' is input into the planet carrier 31' of the differential planetary speed regulating gear box 3' after being accelerated by the speed increasing gear box 2' (the speed increasing ratio is 56.54), the rotating speed of the planet carrier 31' is the rotating speed of the wind wheel 1' after being accelerated by the speed increasing gear box 2', and the rotating speed of the wind wheel 1' corresponding to different wind speeds can be found according to the wind wheel capturing power and rotating speed characteristic curve of the wind turbine generator shown in fig. 5, so that the rotating speed of the planet carrier 31' corresponding to different wind speeds is calculated. The characteristic curve of the rotation speed of the planet carrier 31 'along with the wind speed can be obtained by taking the wind speed as the abscissa axis and the rotation speed of the planet carrier 31' as the ordinate axis (as shown in fig. 6).
For the differential planetary speed gearbox 3', the relationship between the ring gear 32' speed (speed) and the carrier 31' speed is:
wherein: k is the ratio of the number of teeth of the gear ring 32 'to the number of teeth of the sun gear 33', n pc For the speed of rotation of the planet carrier 31', n r For the gear ring 32' speed, n s Is the sun gear 33' rotational speed.
Let k be 2.3, n s The rotation speed input to the synchronous generator 8' is a constant value, and 1500 is a value, and the rotation speed of the ring gear 32' corresponding to different wind speeds can be calculated from the equation and the rotation speed of the carrier 31 '. The characteristic curve of the rotational speed of the ring gear 32 'with the wind speed (as shown in fig. 7) can be obtained by taking the wind speed as the abscissa axis and the rotational speed of the ring gear 32' as the ordinate axis.
For the differential planetary speed gearbox 3', the torque relationship of the components is:
wherein: k is the ratio of the number of teeth of the gear ring 32 'to the number of teeth of the sun gear 33', T C For torque input to the carrier 31', T R Output torque for ring gear 32', T s Torque is output for the sun gear 33'.
From this and the input torque of the carrier 31', the output torque T of the ring gear 32' at different wind speeds can be calculated R The carrier 31' inputs torque T C The input power of the planet carrier 31' is the captured power of the wind wheel 1 (the captured power of the wind wheel corresponding to different wind speeds can be found from the wind wheel captured power and the rotation speed characteristic curve of the wind turbine generator set in fig. 5), thereby calculating the torque T output by the gear ring 32 R Since the present embodiment has two speed adjusting motors 5', the torque of each speed adjusting motor 5' is half of the output torque of the ring gear 32', thereby calculating the corresponding torque of the speed adjusting motor 5' at different wind speeds. The characteristic curve of the torque of the speed regulating motor 5 'along with the wind speed can be obtained by taking the wind speed as an abscissa axis and the torque of the speed regulating motor 5' as an ordinate (as shown in figure 8). The rotation speed of the speed regulating motor 5 'at different wind speeds is taken as an abscissa axis, the torque of the speed regulating motor 5' at corresponding wind speeds is taken as an ordinate axis, and a rotation speed-torque characteristic curve (shown in fig. 9) of the speed regulating motor 5 'can be obtained, wherein the rotation speed of the speed regulating motor 5' is the rotation speed of the gear ring 32 'after the speed is increased by the pinion 44', and the rotation speed of the speed regulating motor 5 'is 6 times the rotation speed of the gear ring 32' when the speed ratio of the pinion 44 'to the gear ring 32' is set to be 6.
According to the rotation speed-torque characteristic curve of the speed-regulating motor 5 'of the original design, when the speed-regulating motor 5' is in an electric state, the maximum torque is 4.65kNm, and when the speed-regulating motor 5 'is in a power generation state, the maximum torque is 12.5kNm, so that the maximum torque of the speed-regulating motor 5' is 12.5kNm.
And can be seen from the speed-torque characteristic of the speed-regulating motor 5': when the speed regulating motor 5 'is in an electric state, the torque of the speed regulating motor 5' is relatively small and the fluctuation is relatively stable; when the speed-adjusting motor 5' is in a power generation state, the torque of the speed-adjusting motor 5' is larger than that of the speed-adjusting motor 5' in an electric mode, and larger fluctuation can occur at a smaller rotating speed.
According to the motor size and torque characteristic formula:
D 2 ·l＝C A ·T
wherein: d is the diameter of the motor rotor, l is the length of the motor rotor, and C A Is a motor constant, and T is a motor torque.
According to this characteristic, the size and weight of the motor are determined by torque rather than power, and the torque of the motor 5 'is reduced to reduce the size of the motor 5'.
The first gear set, the first clutch 41, the second gear set and the second clutch 47 are added between the pinion 44 and the speed-adjusting motor 5 on the basis of the original design, so that the pinion 44 is driven through a first driving path (the speed-adjusting motor 5 is in a power generation state) when driven to the speed-adjusting motor 5, and the speed-adjusting motor 5 is driven through a second driving path (the speed-adjusting motor 5 is in an electric state) when driven to the pinion 44.
And due to Z 45 ＝Z 48 When the speed regulating motor 5 is in an electric state, the rotating speed of the speed regulating motor 5 is kept consistent with the original design; when the speed-adjusting motor 5 is in the power generation state, the pinion gear 44 and the first gear 42 are coaxial, and thus the rotational speeds of both are the same, and Z is the same 42 ＞Z 43 Therefore, the speed is increased through the second gear 43 and then transmitted to the speed-adjusting motor 5, and the torque of the speed-adjusting motor 5 in the power generation state is reduced. Specifically, the present embodiment provides Z 42 /Z 43 Because of this, the rotational speed of the variable speed motor 5 in the power generation state in the present embodiment is changed to 1/4 of the rotational speed of the variable speed motor 5 in the power generation state in the original design, thereby greatly reducing the torque of the variable speed motor 5 in the power generation state. The speed-torque characteristic curve of the speed motor in the present embodiment (as shown in fig. 10) can be obtained with the rotation speed of the speed motor 5 as the abscissa axis and the torque of the speed motor 5 as the ordinate axis.
According to the speed-torque characteristic curve of the speed-adjusting motor in the present embodiment, since the steering of the speed-adjusting motor 5 in the electric state and the power generation state is opposite, the present embodiment will be described taking the example in which the speed value of the speed-adjusting motor 5 in the electric state is negative and the speed value in the power generation state is positive. When the speed-adjusting motor 5 is in an electric state, as the outside wind speed increases, the absolute value of the rotational speed value of the speed-adjusting motor 5 decreases until reaching 0 (i.e., the rotational speed value becomes large until reaching 0 in fig. 10), the torque of the speed-adjusting motor 5 increases, and the maximum torque thereof is 4.65kNm. When the speed-adjusting motor 5 is in the power generation state, the rotation speed value of the speed-adjusting motor 5 is increased with further increase of the external wind speed, the torque of the speed-adjusting motor 5 is increased, and the maximum torque is 3.11kNm, so that the maximum torque of the speed-adjusting motor is 4.65kNm. The maximum torque of the speed regulating motor 5 is reduced to 4.65kNm from 12.5kNm of the original design, the size and the weight of the speed regulating motor 5 are greatly reduced, and the cost of the speed regulating motor 5 and a corresponding converter is further reduced.
This embodiment also has the following advantages:
(1) Since two clutches are used, the brake at the speed regulating motor 5 can be omitted, and both the first clutch 41 and the second clutch 47 are set to be in a closed state, because of Z 42 /Z 43 =4, and Z 45 ＝Z 48 The first gear set and the second gear set form interlocking, so that braking of the gear ring 32 can be realized, and braking of the wind wheel 1 can be realized by locking the main brake 6. The design brings great convenience for single-blade hoisting, wind locking wheel and fan braking and stopping.
(2) When the single blade is hoisted or the wind inlet wheel is needed, the main brake 6 is locked, the first clutch 41 and the second clutch 47 are controlled to be in a closed state or an open state (namely, one of the first transmission path and the second transmission path is controlled to be in a passage state) according to the required torque, the wind wheel 1 is driven to rotate through the speed regulating motor 5 and is rotated to a specified position, the first clutch 41 and the second clutch 47 are both set to be closed to play a role of locking the wind wheel, and simultaneously, the main wind wheel is conveniently locked to the hole.
Example 2
The differential planetary speed regulation gear box 3 in the embodiment is used for driving a large compressor or pump load, so that the purposes of saving cost and energy and improving efficiency are achieved.
As shown in fig. 11, the synchronous generator 1 of the present embodiment transmits power to the carrier of the differential planetary speed adjusting gearbox 3 at synchronous rotational speed through the first coupling 5, the speed adjusting motor 2 adjusts rotational speed of the ring gear of the differential planetary speed adjusting gearbox 3 through the speed adjusting motor gearbox 4, and finally outputs power to the compressor or pump type load 7 through the male wheel of the differential planetary speed adjusting gearbox 3 and the second coupling 6. The speed regulating motor 2 changes the rotating speed and the running mode according to the load characteristic, thereby achieving the purposes of saving cost, saving energy and enhancing efficiency.
While specific embodiments of the invention have been described above, it will be appreciated by those skilled in the art that this is by way of example only, and the scope of the invention is defined by the appended claims. Various changes and modifications to these embodiments may be made by those skilled in the art without departing from the principles and spirit of the invention, but such changes and modifications fall within the scope of the invention.
Claims (11)
1. The speed regulating device for the wind driven generator is characterized by comprising a differential planetary speed regulating gearbox (3), at least one speed regulating motor gearbox (4) and at least one speed regulating motor (5), wherein the speed regulating motor (5) is connected with the differential planetary speed regulating gearbox (3) through the speed regulating motor gearbox (4);
the differential planetary speed regulation gear box (3) comprises a gear ring (32), the speed regulation motor gearbox (4) is connected with the gear ring (32), the speed regulation motor gearbox (4) comprises a first transmission path and a second transmission path, the gear ring (32) and a motor shaft of the speed regulation motor (5) realize transmission through the first transmission path and the second transmission path, wherein,
when the speed regulating motor (5) is in a power generation state, the first transmission path is in a passage state, and the second transmission path is in a disconnection state;
when the speed regulating motor (5) is in an electric state, the first transmission path is in a disconnected state, and the second transmission path is in a passage state;
wherein the first transmissionThe path comprises a first gear set (42, 43), the first gear set (42, 43) comprises a first gear (42) and a second gear (43) which are meshed, the first gear (42) is connected with the gear ring (32), the second gear (43) is connected with the speed regulating motor (5), and the number of teeth Z of the first gear (42) 42 Greater than the number Z of teeth of the second gear (43) 43 。
2. The speed governor device for a wind turbine of claim 1, further comprising a controller for controlling the on-off of the first drive path and the second drive path.
3. The speed regulating device for a wind driven generator according to claim 2, wherein the first transmission path further comprises a first clutch (41), a first gear shaft and a second gear shaft, the first gear (42) is fixedly sleeved on the first gear shaft, the second gear shaft is connected with the speed regulating motor (5), the second gear (43) is connected with the second gear shaft through the first clutch (41), and the controller is electrically connected with the first clutch (41) and used for controlling connection and disconnection of the first clutch (41);
-when the first clutch (41) is in a connected state, a transmission communication between the second gear (43) and the second gear shaft; when the first clutch (41) is in an off state, transmission between the second gear (43) and the second gear shaft is disconnected.
4. A speed regulating device for a wind turbine according to claim 3, wherein the second transmission path comprises a second gear set (45, 48), the second gear set (45, 48) comprising a third gear (45) and a fourth gear (48) in mesh, the third gear (45) being connected to the speed regulating motor (5), the fourth gear (48) being engaged with the ring gear (32).
5. The speed regulating device for a wind driven generator according to claim 4, wherein the second transmission path further comprises a second clutch (47), a third gear shaft and a fourth gear shaft, the third gear (45) is fixedly sleeved on the third gear shaft, the third gear shaft is connected with the speed regulating motor (5), the fourth gear (48) is connected with the fourth gear shaft through the second clutch (47), and the controller is electrically connected with the second clutch (47) and used for controlling connection and disconnection of the second clutch (47);
-when the second clutch (47) is in a connected state, a transmission communication between the fourth gear (48) and the fourth gear shaft; when the second clutch (47) is in an off state, transmission between the fourth gear (48) and the fourth gear shaft is disconnected.
6. The speed regulating device for a wind turbine according to claim 5, wherein the first transmission path and the second transmission path each further comprise a pinion gear (44), a pinion shaft and an input shaft (46) for connecting the speed regulating motor (5), the pinion shaft comprising the first gear shaft and the fourth gear shaft, the input shaft (46) comprising the second gear shaft and the third gear shaft, the pinion gear (44) being coupled to the ring gear (32), the pinion gear (44) being fixedly sleeved on the pinion shaft;
the first gear (42) is fixedly sleeved on the pinion shaft, and the second gear (43) is connected with the input shaft (46) through the first clutch (41); the third gear (45) is fixedly sleeved on the input shaft (46), and the fourth gear (48) is connected with the pinion shaft through the second clutch (47).
7. The speed regulating device for a wind power generator according to claim 5, wherein the first clutch (41) and the second clutch (47) are both bidirectional transmission clutches.
8. The speed regulating device for a wind turbine according to claim 4, wherein the third gear (45) has a number of teeth Z 45 Equal to the number Z of teeth of the fourth gear (48) 48 。
9. The speed regulating device for a wind driven generator according to claim 1, wherein the differential planetary speed regulating gearbox (3) and the speed regulating motor gearbox (4) adopt an integrated box structure.
10. The speed regulating device for a wind driven generator according to claim 1, wherein the speed regulating motor gearboxes (4) are arranged on two sides of the differential planetary speed regulating gearbox (3), and the speed regulating motor (5) is arranged corresponding to the speed regulating motor gearboxes (4).
11. A wind power generator set, characterized by comprising a wind wheel (1), a synchronous generator (8) and a speed regulating device for a wind power generator according to any of claims 1-10, said wind wheel being connected to the input of said differential planetary speed regulating gearbox (3), said synchronous generator (8) being connected to the output of the differential planetary speed regulating gearbox (3).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202310159986.6A CN116025510A (en) | 2023-02-23 | 2023-02-23 | Speed regulating device for wind driven generator and wind driven generator set |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202310159986.6A CN116025510A (en) | 2023-02-23 | 2023-02-23 | Speed regulating device for wind driven generator and wind driven generator set |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN116025510A true CN116025510A (en) | 2023-04-28 |
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ID=86074165
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202310159986.6A Pending CN116025510A (en) | 2023-02-23 | 2023-02-23 | Speed regulating device for wind driven generator and wind driven generator set |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN116025510A (en) |
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2023
- 2023-02-23 CN CN202310159986.6A patent/CN116025510A/en active Pending
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