CN113883003A - Flywheel energy storage device utilizing motor spare driving capability and operation method - Google Patents
Flywheel energy storage device utilizing motor spare driving capability and operation method Download PDFInfo
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- CN113883003A CN113883003A CN202111218127.7A CN202111218127A CN113883003A CN 113883003 A CN113883003 A CN 113883003A CN 202111218127 A CN202111218127 A CN 202111218127A CN 113883003 A CN113883003 A CN 113883003A
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- 238000004146 energy storage Methods 0.000 title claims abstract description 73
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- 238000005381 potential energy Methods 0.000 description 4
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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
- F03D3/00—Wind motors with rotation axis substantially perpendicular to the air flow entering the rotor
- F03D3/005—Wind motors with rotation axis substantially perpendicular to the air flow entering the rotor the axis being vertical
- F03D3/007—Wind motors with rotation axis substantially perpendicular to the air flow entering the rotor the axis being vertical using the Magnus effect
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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
- F03D13/00—Assembly, mounting or commissioning of wind motors; Arrangements specially adapted for transporting wind motor components
- F03D13/20—Arrangements for mounting or supporting wind motors; Masts or towers for wind motors
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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
- F03D3/00—Wind motors with rotation axis substantially perpendicular to the air flow entering the rotor
- F03D3/02—Wind motors with rotation axis substantially perpendicular to the air flow entering the rotor having a plurality of rotors
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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
- F03D3/00—Wind motors with rotation axis substantially perpendicular to the air flow entering the rotor
- F03D3/06—Rotors
- F03D3/062—Rotors characterised by their construction elements
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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
- F03D7/00—Controlling wind motors
- F03D7/06—Controlling wind motors the wind motors having rotation axis substantially perpendicular to the air flow entering the rotor
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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
- F03D9/00—Adaptations of wind motors for special use; Combinations of wind motors with apparatus driven thereby; Wind motors specially adapted for installation in particular locations
- F03D9/10—Combinations of wind motors with apparatus storing energy
- F03D9/12—Combinations of wind motors with apparatus storing energy storing kinetic energy, e.g. using flywheels
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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
- Y02E10/728—Onshore wind turbines
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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
- Y02E10/74—Wind turbines with rotation axis perpendicular to the wind direction
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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
- Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
- Y02E60/16—Mechanical energy storage, e.g. flywheels or pressurised fluids
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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
- Y02E70/00—Other energy conversion or management systems reducing GHG emissions
- Y02E70/30—Systems combining energy storage with energy generation of non-fossil origin
Abstract
The invention relates to a flywheel energy storage device utilizing the vacant driving capability of a motor and an operation method, and the flywheel energy storage device comprises a rotor blade, a motor, an overrunning clutch, a T-shaped bevel gear steering gear, a flywheel, an electromagnetic clutch, a reversing gear, an electromagnetic brake, an energy storage spring and the like; the motor transmits the motion to the T-shaped bevel gear steering gear through the overrunning clutch and then outputs the motion in two paths, wherein one path inputs the motion to the reversing center of the air intake machine, and the other path is connected with the energy storage flywheel. The motor is driven by the separation of the rotor blades, the gap of reduced load drives the flywheel to store energy in an accelerating way, and then the flywheel is connected with the movement of the flywheel in a decelerating way; after the rotor blade is reversed, the energy storage springs and the energy storage amount of the flywheel are sequentially received, the rotating speed of the motor is increased after the rotating speed of the rotor blade is converged with the energy storage flywheel, the overrunning clutch is automatically connected with the driving connection of the rotor blade, and then the motor is accelerated according to the maximum driving capability until the rotor blade obtains the rotating speed of the maximum Magnus effect under the real-time wind speed.
Description
Technical Field
The invention relates to the field of vertical axis wind turbines, in particular to a wheel-rail type vertical axis wind turbine rotor blade driving structure based on the Magnus effect and an operation method thereof.
Background
The wind turbines are divided into two categories, namely a horizontal axis wind turbine and a vertical axis wind turbine according to the geometric relationship between a rotating shaft of the wind turbines and the ground, the horizontal axis wind turbines are developed rapidly in the wind power generation technology, and the wind turbines occupy most of domestic and foreign wind power generation markets. However, the rapid development of the horizontal axis wind turbine technology cannot obviously reduce the operation cost, the wind power grid-connection electricity price is still high, and most wind energy enterprises can survive only by being subsidized by national energy policies. In order to compete with the traditional energy, the development of the wind turbine generator system towards large-scale is selected, and the wind power cost is reduced by improving the wind energy conversion efficiency. Unfortunately, the development of large-scale horizontal axis wind turbine does not significantly reduce the manufacturing and operating costs of the horizontal axis wind turbine, and the relatively high efficiency of the horizontal axis wind turbine is still at the cost of high cost in the present view, because the huge structural size almost reaches the development limit of the horizontal axis wind turbine, the cost of blade materials and manufacturing and installation severely restricts the further large-scale horizontal axis wind turbine, and the large-scale horizontal axis wind turbine is the most effective way for reducing the cost of wind power generation — thereby entering a paradox circle. Technically, the horizontal axis wind turbine is limited to further increase in structure by technical bottlenecks such as complicated pitch change, fan mechanism, huge and heavy speed change mechanism and generator body, high-rise installation structure and alternating load of gravity and inertia force when huge blades rotate, accelerated fatigue of blade roots, damage of the blades to migratory birds, running noise and the like.
In the development history of wind power generation technology, a vertical axis wind turbine concept scheme is documented, and the scheme is based on the following scientific phenomena: in a natural flow field, when a fluid bypasses a cylindrical or spherical obstacle body which performs a rotational motion, the rotating body is subjected to a lateral force which is actually a lifting force phenomenon caused by a difference in flow velocity of the fluid on both sides of the cylinder, and is called a magnus effect, and a lateral force generated is called a magnus effect stress or a magnus (lifting) force. For example, "curvy" and "banana" in ball games are phenomena in which the magnus effect stresses caused by the additional rotation of the ball during its advance cause the flight path of the ball to deviate from a predetermined trajectory.
The technical scheme is conceived in 1933 by the American engineer Julius D.Madaras, and the specific scheme is as follows: the power blade capable of generating the Magnus effect stress is a rotating cylindrical drum loaded on a rail trolley, the trolley is placed on a circumferential rail, and when wind blows to the cylindrical drum, the Magnus effect is generated on the rotating cylindrical drum, namely the flowing direction of the wind is the same as the moving direction of the cylindrical drum on one side of the cylinder, so that the flowing speed of fluid on the side is accelerated; the motion direction of the cylindrical barrel on the other side is opposite to the incoming flow direction, the speed of the fluid flowing on the side is blocked, the induced circulation around the rotating cylindrical barrel generates a lift force perpendicular to the wind flowing direction (the lift force direction points to the same side of the motion direction), the resultant force pushes the trolley to move around the annular track, and the wheels of the trolley drive the generator.
The wind power plant of this concept does not achieve the effect of large-scale power generation, the reason being ascribed to its "mechanical complexity": in order to enable the lifting force generated on the cylindrical rotor to continuously drive the trolley to reciprocate on the annular track, the rotating cylinder needs to change the rotating direction once at the joint of each upper air inlet circular arc and each lower air inlet circular arc of the annular track of the trolley; in order to obtain large lift force, the diameter and the rotating speed of the cylindrical barrel are required to be measured to be large as much as possible, so that the rotational inertia of the cylindrical barrel is large, and the driving energy is large. Under the technical conditions of the current time (1933), the change of the rotating speed and the steering of the rotor cylinder can be realized only by a complex pure mechanical system, and the mechanical loss is overlarge; also, because of the difficulty in commutation and the undeveloped influence of other basic techniques, the increase in the rotational speed of the cylinder is greatly limited, and the aerodynamic characteristics of the rotor are not fully exploited, so that the concept is abandoned.
Further analyzing the above technical solutions, one of the most important technical problems is that, in order to obtain favorable aerodynamic characteristics for the wind turbine, the cylindrical rotor needs to have a sufficiently large rotation radius and rotation speed, so that the rotational inertia of the cylindrical rotor is generally large, and the energy required to be consumed when the rotation speed requirement is met is also large; however, even if each rotor which is so heavy obtains ideal aerodynamic lift force, the trolley is driven to run through the semicircular arc of the windward side, after the rotor enters the lower semicircular arc of the leeward side, in order to continuously obtain the magnus force which drives the trolley along the same circumferential direction, the rotation direction of the rotor needs to be changed (otherwise, the magnus force generated by the rotor on the leeward side can block the circular motion of the trolley). That is, each rotor must pass through the change of the rotation direction twice within the range of passing through the circular orbit for one circle, so that the problem of poor rotation energy conversion is solved, a large amount of energy is consumed when the rotor is started reversely, the consumed energy accounts for too much in the electric energy which can be generated by the wind turbine, and the practicability of the technology is seriously influenced.
With the continuous progress of modern technology, the technical problems in the above schemes can be solved by new technical means and methods. Therefore, the wind turbine structure and the operation control method thereof are designed innovatively on the basis of modern industrial technology, and the key technical problems of improving the wind energy utilization efficiency of the wind turbine and redefining the practical value of the wind turbine are solved.
The patent provides a wheel-rail type vertical axis wind turbine structure based on the Magnus effect and an operation method thereof, which can effectively reduce energy consumption of a rotating cylindrical rotor during rotation and reversing and improve the generating efficiency of wind power. Researches show that the rotary cylinder with the Magnus effect can obtain higher lift force than other wing profiles, the manufacturing cost is low, and the vertical axis wind turbine has good application prospect.
Disclosure of Invention
The technical problem is as follows: the invention provides a driving mode of a rotor blade of a wheel-rail type vertical axis wind turbine, when the rotor blade needs to change the rotating direction in order to obtain the Magnus effect stress of the continuous operation of the wind turbine, particularly during the reversing period when the rotor blade is separated from the driving of a motor, the idle state of the load reduction of the motor is utilized to provide energy storage energy for an energy storage flywheel, and when the rotor blade is started reversely, the energy of the energy storage flywheel is transmitted to the rotor blade, so that the rotating speed of the rotor blade is improved; after the flywheel energy storage is transmitted, the driving of the motor is automatically switched in, so that the energy consumption of the rotor during reversing can be effectively reduced, and the generating efficiency of the wind turbine is improved.
The technical scheme is as follows: the implementation of the technical scheme of the invention relates to a driving mode and an operation method of a wheel-rail type vertical axis wind turbine rotor blade. With reference to the description in the above technical background, the following description is further provided for the working process of the wheel-rail type vertical axis wind turbine after the cooperative work with the technical solution of the present invention: the annular steel rails are laid on the horizontal ground and are connected end to form a complete circular track (in order to obtain higher wind speed, an overhead track higher than the ground can be made); a plurality of small rail cars are arranged on the track, and wheels of the small rail cars are limited by a bogie of the small car and a limiter to roll only along the track and can not be separated from the track; the rail trolley is connected with a wheel platform through a bogie, and wheels advancing along a rail and a small generator driven by a wheel shaft are arranged on the wheel platform;
a cylindrical rotor (equivalent to a blade of a wind turbine and also called a rotor blade) for generating Magnus effect stress and a rotor blade driving system driven by a speed-regulating motor are arranged on a platform of the small rail car;
the structure composition and the working process of the rotor blade driving system are as follows: the output shaft of the driving motor transmits power to a single-input double-output gear mechanism (such as a commercially available T-shaped bevel gear steering gear) through a special overrunning clutch (hereinafter referred to as a flywheel energy storage overrunning clutch), the power of the motor is divided into two parts, one path is transmitted to an energy storage flywheel (generally connected to a vertical shaft), and the other path is transmitted to a reversing center of a wind turbine;
the overrunning clutch has the effects that when the rotating speed of the motor is higher than the rotating speed of the driven load, the clutch works in an 'on' state, and the load is really driven by the motor; when the load rotating speed exceeds the electric rotating speed, or the rotating speed of the motor is lower than the load rotating speed, the clutch is in an off state, the load is not driven and controlled by the motor at the moment, the rotating speeds of the motor and the load are not constrained with each other until the rotating speed of the motor is equal to and has a trend higher than the load rotating speed, the clutch is automatically restored to be on, and the motor drives the load effectively again;
3 groups of electromagnetic clutches, 1 group of overrunning clutches, 1 group of electromagnetic brakes and 1 group of gear sets for reversing in positive and negative rotation are arranged in the reversing center;
the electromagnetic clutch comprises 3 groups of electromagnetic clutches, wherein 1 group of electromagnetic clutches are arranged on an input shaft of a motor power entering a reversing center and are responsible for power connection between the aspects of 'separating and combining' the motor and a flywheel and the reversing center (hereinafter referred to as driving electromagnetic clutches); the other 2 groups of electromagnetic clutches are matched with a positive and negative rotation reversing gear set (hereinafter referred to as reversing electromagnetic clutches 1 and 2), the rotation direction between two shafts is changed by adding or subtracting an externally meshed intermediate gear between two transmission shafts A and B at the reversing center, namely, the rotation of the shaft A is transmitted to the shaft B through a pair of externally meshed gears and then drives rotor blades through the connection of the 1 st electromagnetic clutch (the upper gear and the transmission shaft form an integral body through the clutch) and the connection of the other 1 electromagnetic clutch (the upper gear and the transmission shaft form an idle rotation relationship), so that the positive rotation of the shaft A at the reversing center is changed into the rotation opposite to the rotation of the shaft A after being transmitted to the rotor blades through the shaft B; the motion of the shaft A is transmitted to the shaft C through a pair of external meshing gears by the 'off' of the 1 st electromagnetic clutch and is transmitted to the shaft B through the (intermediate) external meshing gear on the shaft C, the forward rotation of the shaft A at the reversing center changes the transmission direction through two times of external meshing gears and is converted into the forward rotation of the rotor blade, and thus, the rotation of the rotor blade in the forward and reverse directions can be obtained by controlling the alternative use of the two reversing special electromagnetic clutches at the reversing center, and the unidirectional driving of the input shaft at the reversing center can also transmit the rotation of the rotor blade in the forward and reverse directions to the input shaft at the reversing center;
the 1 group of overrunning clutches in the reversing center are used for one-way energy storage transmission of the spring energy storage device (hereinafter referred to as the spring energy storage overrunning clutch, which is described in detail below); 1 group of electromagnetic brakes is used for braking and stopping the blade rotor;
the electromagnetic clutch is in friction type transmission and can complete clutch action in motion;
the commutation center has 3 input and output channels which have rotation energy transmission with the outside, and the channel 1 is the rotation input channel of the motor and the energy storage flywheel; the channel 2 is a connecting channel between the reversing center and the cylindrical rotor, is used for outputting power input into the reversing center to drive the cylindrical rotor to rotate, and is also used for reversely transmitting the residual rotating energy before the rotor blade stops to the reversing center;
the 3 rd channel of the reversing center is connected with an energy storage spring, a spring energy storage overrunning clutch which is movably connected with the energy storage spring is arranged on an input shaft provided with a driving electromagnetic clutch and is used for transmitting the residual rotation energy of the rotor blade back and storing the residual rotation energy in a torsion energy storage spring, releasing the energy storage of the spring when the rotor blade is started reversely, and transmitting the initial starting energy after the rotation direction is changed to the cylindrical rotor through different combination states of the 2 groups of reversing electromagnetic clutches;
after the rotation of the motor is transmitted to the reversing center, the automatic control system of the wind turbine changes the unidirectional rotation of the motor into the rotation of the cylinder rotor in the preset direction by controlling the electromagnetic clutch combination of the preset sequence and drives the rotor blades to carry out variable-frequency speed regulation according to the preset acceleration, and the aim is to ensure that the rotor blades obtain the optimal Magnus effect so as to generate the maximum Magnus lift force under the condition of specific wind speed;
the magnus lift gained by the rotor blades described above will drive the trolley along the track via the trolley platform supporting the rotor.
The advancing trolley wheels roll on the track, the wheels transmit the motion to the rotor of the vehicle-mounted generator, and the generator generates electricity.
The circular track of the trolley consists of a windward semicircular arc (the direction of the arc bulge is opposite to the half circumference of the windward direction) and a leeward semicircular arc (the direction of the arc bulge is opposite to the half circumference of the leeward direction) in a wind field. When the small rail car drives the cylindrical rotor to run on the windward semi-arc track, the cylindrical rotor needs to enter the leeward semi-arc track to continue to run annularly. Similarly, the trolley runs on the leeward semi-arc track and then enters the windward semi-arc of the next running period to continue running, and the wheels drive the generator to continuously rotate to generate power in such a way repeatedly.
After the trolley is driven by the rotor blades and enters the leeward semicircular arc track from the windward semicircular arc, the magnus lifting force action direction generated on the rotor blades needs to be changed reversely to drive the trolley to continuously push the trolley to perform continuous circular motion, so that the original rotation direction of the carried cylindrical rotor needs to be changed to change the magnus lifting force direction on the cylindrical rotor, and the trolley can obtain the driving force for continuously running along the fixed annular direction.
Therefore, in the range of one circle of the circular track, the cylinder rotor needs to change the rotation direction once at two intersection points of the windward half arc and the leeward half arc.
Because the rotor blade driving system has certain mass and rotational inertia, the cylindrical rotor commutation needs to be completed in a specified range (commutation zone) near the front and the rear of the junction point of the two circular arc tracks (rotor commutation point).
The generators arranged on the wheel sides are distributed generation layout, the number of the generators participating in actual power generation can be timely adjusted according to the real-time wind speed of a wind field and the actual acquired Magnus force of the rotor blades, and accordingly starting of the wind turbine and maximum utilization of wind energy are facilitated.
Has the advantages that: the problem of energy consumption for driving the blades of the wheel-rail type vertical axis wind turbine is one of the core technical problems, and the practical value of the wind turbine is determined. Because the wind turbine can obtain the peripheral speed for directly driving the generator to generate electricity by virtue of the technical characteristic of large radius of the track, the cost that the wind turbine driven by a central shaft can drive the generator to generate electricity only after the rotating speed of the wind turbine is accelerated by the accelerating gearbox is saved; the wheels of the power generation trolley can independently drive the distributed small generators, and the number of the generators participating in power generation can be selected according to the field wind speed during operation, so that the applicable wind speed range and the wind power conversion efficiency of wind power generation are expanded; according to the actual wind speed on site, the rotating speed of the rotor blade of the wind turbine is driven in a variable speed mode, so that unnecessary energy consumption is reduced and the generating efficiency of the wind turbine is improved on the premise that the maximum wind power benefit can be obtained, and therefore the invention is very important for improving the technology of the wind turbine.
Drawings
FIG. 1 is a schematic diagram of an overall structure of a wheel-track type vertical axis wind turbine;
FIG. 2 is a schematic view of a wind turbine rotor blade drive system;
FIG. 3 is a schematic structural diagram of a flywheel energy storage device;
FIG. 4 is a schematic view of Magnus lift on a cylindrical rotor blade and driving a power generation cart forward.
In the above figures: 1-ring track, 2-power generation trolley, 3-trolley connecting frame, 4-cylinder rotor blade, 5-rotor blade driving motor, 6-flywheel energy storage overrunning clutch, 7-T-shaped bevel gear steering device 1, 8-flywheel, 9-main driving chain wheel, 10-reversing central input shaft, 11-driving electromagnetic clutch, 12-spring energy storage overrunning clutch, 13-inter-shaft driving chain wheel, 14-electromagnetic clutch and reversing gear 1, 15-electromagnetic clutch and reversing gear 2, 16-reversing intermediate gear, 17-reversing central output shaft, 18-T-shaped bevel gear steering device 2, 19-cylinder rotor blade, 20-electromagnetic brake, 21-energy storage spring, 22-energy storage driving chain wheel and 23-trolley steering frame, and 24, a wheel power generation device.
Detailed Description
The embodiment of the invention provides a wheel-rail type vertical axis wind turbine rotor blade driving structure and an operation method thereof, and the wheel-rail type vertical axis wind turbine rotor blade driving structure comprises an annular rail, a power generation trolley, a trolley connecting frame, a cylindrical rotor blade, a rotor blade driving motor, a flywheel energy storage overrunning clutch, a T-shaped bevel gear steering gear 1, a flywheel, a main driving chain wheel, a reversing center input shaft, a special driving electromagnetic clutch, a spring energy storage overrunning clutch, an inter-shaft driving chain wheel, an electromagnetic clutch and reversing gear 1, an electromagnetic clutch and reversing gear 2, a reversing intermediate gear, a reversing center output shaft, a T-shaped bevel gear steering gear 2, an electromagnetic brake, an energy storage spring, an energy storage driving chain wheel, a trolley steering frame, a wheel power generation device and the like.
The technical solutions in the embodiments of the present invention will be clearly described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. Based on the embodiments of the present invention, other embodiments obtained by a person of ordinary skill without creative efforts belong to the protection scope of the present invention.
Fig. 1 shows an overall structural layout of a wheel-rail type vertical axis wind turbine formed by three power generation trolleys 2 and trolley connecting frames 3 uniformly distributed on an annular track 1, and a cylindrical rotor blade 4 is a power blade for the wind turbine to rotate along the track.
The wind turbine structure principle and the control method and the process in operation are detailed as follows:
3 rail power generation trolleys 2 loaded with cylindrical rotors are uniformly distributed on the plane annular rail 1, the trolleys are connected with each other through trolley connecting frames 3 to form an integral framework of the wheel-rail type vertical axis wind turbine, and an electric control and power transmission component of the wind turbine is arranged at the central part of the integral framework of the wind turbine (not shown in the figure);
as shown in fig. 1 and 4, when the wind speed in the wind field is stable and meets the requirement of normal operation of the wind turbine, a certain trolley 2 forming the wind turbine is operating on a windward (or leeward) semicircular arc track, and a cylindrical rotor 4 thereon is driven by a driving motor 5 to rotate at a predetermined rotation direction and a predetermined rotation speed;
as shown in fig. 4, it is assumed that the rotation of the rotor blades 4 in the wind field obtains sufficient magnus lift force, the direction of the lift force is perpendicular to the wind force and complies with the fluid mechanics principle, the trolley is pushed to move forward along the track, the wheels roll to drive the generator to generate electricity, and the output electric energy is output through the power transmission component (not shown in the figure).
When the trolley 2 carries the cylindrical rotor 4 to move to a specified range close to the intersection point (a reversing point in figure 4) of the windward semi-arc and the leeward semi-arc, the control center of the wind turbine sends out an instruction, the driving electromagnetic clutch 11 'off' of the reversing center in figure 3 cuts off the driving connection between the motor and the cylindrical rotor, and the cylindrical rotor 4 freely rotates under the action of inertia;
then, the wind turbine control system determines the current rotation direction of the cylindrical rotor according to a rotation speed sensor (not shown in the figure), if the rotor blade is in a counterclockwise (set to be in a forward) direction as shown in fig. 4, which indicates that the trolley 2 is close to a 'reversing point' below the trolley 4, the electromagnetic clutch and the reversing gear 14 are enabled to work, and the electromagnetic clutch and the reversing gear 15 are kept disconnected, so that the forward free rotation of the cylindrical rotor 4 is uniformly converted into the rotation of the reversing center input shaft 10 in the direction opposite to the motor input rotation direction; similarly, if the rotor blade is in the clockwise direction (set to reverse direction) as shown in fig. 4, which indicates that the trolley 2 is already approaching to the "reversing point" above fig. 4, the electromagnetic clutch and the reversing gear 15 are made to work, and the electromagnetic clutch and the reversing gear 14 are kept disconnected, the reverse free rotation of the cylindrical rotor 4 is uniformly converted into the rotation of the reversing center input shaft 10 in the direction opposite to the motor input rotation direction;
because the driving electromagnetic clutch 11 installed on the input shaft 10 is already in the 'off' state, the motion is not in motion connection with the electric motor 5 and the energy storage flywheel 8, and the reverse rotation of the input shaft drives the energy storage spring 21 to twist and store energy through the 'on' of the spring energy storage overrunning clutch 12, and further drives the energy storage spring 21 to twist and store energy through the energy storage transmission chain wheel 22 (the ordinary bicycle flywheel shaft and the pedal shaft have the motion relation of the similar 'overrunning clutch', when the bicycle flywheel shaft (rear wheel) rotates reversely, the pedal shaft must be driven to rotate reversely together, and the pedal shaft at the moment is equivalent to the energy storage spring rotating shaft at the moment, so the reverse rotation of the input shaft 10 must drive the energy storage spring 21 to twist, and the residual inertia energy of the cylindrical rotor is converted into elastic potential energy to be stored;
the cylinder rotor 4 stops after the inertia energy of the cylinder rotor is completely converted into elastic potential energy, and after a control center detects a stop signal of the rotor 4 (the rotation speed sensor is not marked in the figure), the electromagnetic brake 20 is controlled to brake, the rotor brakes, and the elastic potential energy stored by a spring is latched;
on the other hand, after the motor 5 is disconnected from the motion connection with the input shaft 10 by the driving electromagnetic clutch 11, the whole load is reduced, and in order to exert the driving capability of the motor, the motor is started to carry out variable frequency acceleration, the flywheel energy storage overrunning clutch 6 is closed, and the flywheel 8 is driven to rotate in an accelerated way to store energy;
after the motor 5 drives the flywheel 8 to accelerate to a specified speed (theoretically, the higher the speed that can be achieved, the better, but practically limited by various conditions, which can be determined by calculation and field tests), the motor 5 then decelerates to N in a frequency-down manner1(for explanation, see the following), at this time, the rotating speed of the flywheel 8 is higher than that of the motor 5, the overrunning clutch is in the 'off' state, and the flywheel 8 rotates freely under the action of inertia and is not influenced by the reduction of the rotating speed of the motor 5;
on the other hand, after the trolley 2 carries the cylinder rotor 4 which is already stopped to reach and pass through the appointed turning point, the braking instruction is cancelled, the latched spring rotating shaft outputs the positive driving torque which is the same as the turning direction of the motor 5 and the flywheel to the reversing center input shaft 10 through the overrunning clutch 12 (similar to the fact that the back wheel which is at rest is inevitably driven to rotate towards the advancing direction by the positive rotation of the pedal shaft of the bicycle), the elastic potential energy is selected through one of the 2 reversing electromagnetic clutches 15 or 14 (the principle is shown in the specification), the torque is transmitted to the cylinder rotor 4 according to the preset direction to be used as the starting torque which is converted towards the new turning direction, and the spring rotating shaft stops rotating until the spring energy is completely released; at this time, the cylindrical rotor 4 is started, after the rotating speed exceeds the spring rotating shaft, the spring energy storage overrunning clutch 12 is changed from 'on' to 'off', and the forward rotation of the input shaft 10 is not influenced by the energy storage spring rotating shaft any more (similar to the forward rotation of the bicycle is not influenced by the stop of the pedal shaft once the rotating speed of the rear wheel exceeds the driving rotating speed of the pedal plate when the bicycle moves forward);
after the control center receives a stop signal transmitted by a spring rotating shaft rotating speed sensor (not shown in the figure), the control center instructs to drive the electromagnetic clutch 11 to be switched on, because the rotating speed of the motor is far lower than the rotating speed of the energy storage flywheel 8 at the moment, the flywheel is in a free rotating state under the action of the flywheel energy storage overrunning clutch 6, the switching-on of the clutch 11 enables the cylinder rotor 4 to only absorb the rotating energy of the flywheel 8, the rotating speed of the rotor is increased, the rotating speed of the flywheel is reduced, and the final rotating speed is converged to the initial rotating speed N of the rotor related to the system inertia, the characteristics of the energy storage spring and the flywheel and the like0；
Initial speed N of the rotor0A relatively stable value is set for a built system (such as a certain rotor speed, rotational inertia, elastic energy storage parameters and the like), and the range of the system can be roughly determined through calculation or experiments;
the motor is decelerated to N1Should be less than or equal to N0That is, in the stage of starting the drum rotor 4 in reverse rotation, after the energy released from the energy storage spring 21 and the flywheel 8 is obtained, the real-time initial speed of the rotor still "overruns" the real-time rotating speed of the motor 5, and because the flywheel energy storage overrunning clutch 6 is in the "off" state under this condition, the motor 5 does not participate in the actual driving of the drum rotor 4 at this time.
The reason for the above is that: in order to improve the efficiency, the permanent magnet synchronous motor is used for driving the cylindrical rotor blade, the effective torque when the rotor is started is influenced by the cross of a plurality of factors such as spring energy storage feedback, flywheel energy storage feedback and the like in the rotor reversing period, the actual acceleration value is difficult to be accurately determined, and the phenomenon that the synchronous motor is not allowed to run, such as 'locked-rotor' caused by the motor participating in driving or 'over-rotation' caused by the rotor blade 4 driving the motor 5, is easily caused. And after all energy storage feedback is finished, the cylindrical barrel rotor system is independently driven by the motor, and the actual size of the load can be calculated or tested, so that the basis can be provided for the effective driving of the motor.
The variable frequency drive control system controls the rotating speed of the motor 5 to be N1Acceleration in no-load mode to near actual rotor blade speed with over-N0After the trend is reached, the load of the motor is increased, the preset frequency modulation acceleration during driving needs to be determined by a mode of combining calculation and test according to the rated capacity of the driving motor and the actual parameters of a mechanical system, the most reasonable driving capability of the motor is exerted under the condition of avoiding overload of the motor, namely the maximum rotating speed acceleration capable of ensuring normal operation of the motor can be calculated by combining the comprehensive parameters of the rotational inertia, the rated output torque and the like of an actual cylindrical rotor driving system, and the maximum rotating speed acceleration can be used as the theoretical basis of the variable-frequency acceleration control of the motor, the variable-frequency acceleration of the motor is controlled by the preset acceleration, and the cylindrical rotor is driven to rotate in an accelerated mode towards the target capable of obtaining the maximum Magnus lift force.
Recent research shows that the magnus effect stress generated on the cylindrical rotor depends on the incoming flow wind speed and the product of the radius of the rotating drum and the angular speed of the rotating drum, the magnus force is larger when the linear speed of the cylindrical rotor is larger and reaches the maximum value when the product of the angular speed of the rotating drum and the radius of the rotating drum is equal to 4 times of the incoming flow wind speed under the same wind speed, namely the magnus effect of the rotor blade reaches the peak, and the lift force on the rotor blade can not be increased any more when the rotating speed of the rotating drum is increased; on the other hand, the larger the wind speed, the larger the magnus force that can be generated; as shown in fig. 4, the benefit of the magnus force on the rotor blade 4 to the operation of the power generation trolley is also affected by the position of the cylindrical rotor on the circular track changing at any time, that is, in the process that the rotor is driven from the commutation zone to the midpoint of the windward (or leeward) semi-arc, the included angle (pressure angle) between the direction of the magnus force and the tangential direction of the track where the trolley operates is gradually reduced, the mechanical benefit is gradually increased, and in the process of continuously operating to the next commutation zone, the pressure angle is gradually increased, and the mechanical benefit is gradually reduced; by combining the above factors, the wind turbine rotor is accelerated to the operation that the product of the angular speed and the radius of the rotating drum is equal to 4 times of the incoming flow speed according to the sine acceleration curve after being started from a certain reversing point, and good comprehensive benefits can be obtained.
Therefore, in the actual operation of the wind turbine, the control center of the wind turbine needs to measure the wind direction and the wind speed of the wind turbine on the working site in real time, firstly two reversing points (shown in fig. 3) of the rotor blade are determined on the track 1 according to the wind direction, and a certain range in front of and behind the reversing points is set as a reversing area; and according to the wind speed, calculating the ideal rotor rotation speed N at which the rotor blade can obtain the optimal Magnus force under the real-time wind speed by using a designed control algorithm2And comprehensively giving reasonable frequency modulation acceleration of the motor under the conditions by referring to the position of the rotor on the track and combining the driving capability of the motor and the inertia parameters of an actual mechanical system, namely continuously accelerating by taking the ideal rotating speed as a target on the premise of fully exerting the maximum allowable output torque of the driving motor until N is reached2Then the operation is changed into constant speed operation;
the rail trolley 2 is driven by the magnus force to carry the cylindrical rotor 4 to continuously run along the rail 1 until the next rotor reversing area is entered for the next cycle.
While the wheel-rail vertical axis wind turbine structure and the operation method thereof provided by the present invention have been described in detail, for those skilled in the art, there may be variations in the specific implementation manners and application ranges according to the concepts of the embodiments of the present invention, and in summary, the contents of the present specification should not be construed as limiting the invention.
Claims (4)
1. A flywheel energy storage device utilizing motor spare driving capability and an operation method thereof are disclosed, wherein the flywheel energy storage device is composed of a power generation trolley, a cylindrical rotor blade, a driving motor, a flywheel energy storage overrunning clutch, a T-shaped bevel gear steering gear, an energy storage flywheel, a main transmission chain wheel, a driving electromagnetic clutch, a spring energy storage overrunning clutch, an inter-shaft transmission chain wheel, an electromagnetic clutch and reversing gear 1, an electromagnetic clutch and reversing gear 2, a reversing intermediate gear, an electromagnetic brake, an energy storage spring and an energy storage transmission chain wheel, wherein the driving electromagnetic clutch, the inter-shaft transmission chain wheel, the electromagnetic clutch and reversing gear 1, the electromagnetic clutch and reversing gear 2 and the reversing intermediate gear form a wind turbine reversing center; the energy-storage type air conditioner is characterized in that a driving motor transmits motion to a T-shaped bevel gear steering gear through an overrunning clutch and then outputs the motion in two paths, wherein one path is connected with an energy-storage flywheel, and the other path is input to a reversing center of an air inlet motor through a main transmission chain wheel and a driving electromagnetic clutch.
2. The flywheel energy storage device and the operation method thereof using the vacant driving capability of the motor according to claim 1, characterized in that the driving motor inputs the unidirectional rotation motion into the commutation center through the overrunning clutch and the energy storage flywheel, and then realizes the 'on/off' of the motion through the driving electromagnetic clutch and the input shaft of the commutation center; the electromagnetic clutch and the reversing gear in the reversing center realize reversing in operation, and the unidirectional rotation obtained by the input shaft is converted into time-sharing driving in the positive and negative directions of the rotor blade.
3. The flywheel energy storage device and the operation method thereof using the vacant driving capability of the motor according to claim 1 are characterized in that the cylindrical rotor blade is separated from the gap driven by the driving motor, the motor is accelerated, and the energy storage flywheel is driven by the overrunning clutch to accelerate and store energy; the motor then reduces the rotating speed, and the energy storage flywheel is separated from the motion connection with the motor under the action of the overrunning clutch of the energy storage flywheel; when the rotor blade is reversely started, the energy storage spring is controlled by the electromagnetic brake to release energy to the rotor blade and then stops rotating, the electromagnetic clutch is driven to be switched on, and the energy storage amount of the flywheel is transmitted to the rotor blade, so that the rotor blade fully absorbs the energy of the energy storage spring and the energy storage flywheel, and the rotating speed of the rotor blade after reversing is continuously increased.
4. The flywheel energy storage device and the operation method thereof according to claim 1, wherein the energy storage flywheel releases energy to the rotor blade, and after the rotation speed of the flywheel is equal to the rotation speed of the rotor blade, the flywheel automatically receives the rotation energy transmitted by the driving motor through the overrunning clutch, and drives the rotor blade at an accelerated speed according to the maximum driving capability of the motor until the rotor blade obtains the maximum magnus effect rotation speed at the real-time wind speed.
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| US4446379A (en) * | 1983-02-17 | 1984-05-01 | Borg John L | Magnus effect power generator |
| US20090058091A1 (en) * | 2007-08-02 | 2009-03-05 | Douglas Joel S | Magnus force fluid flow energy harvester |
| CN103717884A (en) * | 2011-07-22 | 2014-04-09 | 清水敦史 | Vertical axis type Magnus wind turbine generator |
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Application publication date: 20220104 |