CN118278187A - Method, system, equipment and medium for determining brake parameters of wind generating set - Google Patents
Method, system, equipment and medium for determining brake parameters of wind generating set Download PDFInfo
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Abstract
The application discloses a method, a system, equipment and a medium for determining parameters of a brake of a wind generating set, and belongs to the technical field of wind power generation technologies. The method for determining the brake parameters of the wind generating set comprises the following steps: determining aerodynamic peak torque of the wind generating set, and calculating maximum braking torque of a brake according to the aerodynamic peak torque and a gear box speed ratio; calculating the maximum linear speed of the brake disc and the maximum angular speed of the brake disc according to the maximum wind wheel rotating speed and the brake parameter constraint information; setting the ratio of the maximum linear velocity of the brake disc to the maximum angular velocity of the brake disc as the radius of the brake disc; calculating the area of a brake pad according to the maximum braking torque, the maximum angular velocity of the brake disc and the maximum power consumption rate of the unit area of the brake disc; the brake disc radius and the brake pad area are set as brake parameters. According to the application, the parameters of the brake can be reasonably set, and the braking performance of the brake in the wind generating set is improved.
Description
Technical Field
The application relates to the technical field of wind power generation, in particular to a method, a system, equipment and a medium for determining parameters of a brake of a wind generating set.
Background
The wind generating set is a device for converting kinetic energy of wind into electric energy, and comprises a low-speed shaft, a high-speed shaft, a gear box, a generator, a brake and other structures. The brake comprises a brake disc, a brake pad and a caliper, wherein the caliper generates braking force by pressing the brake pad to the brake disc, so that the brake of the high-speed shaft is realized.
In the related art, a brake with fixed parameters is usually arranged in a wind generating set, but the brake cannot effectively brake the wind generating set due to different working parameters of different wind generating sets.
Therefore, how to reasonably set the parameters of the brake and improve the braking performance of the brake in the wind generating set is a technical problem that needs to be solved currently by those skilled in the art.
Disclosure of Invention
The application aims to provide a method for determining the parameters of a brake of a wind generating set, a system for determining the parameters of the brake of the wind generating set, electronic equipment and a storage medium, which can reasonably set the parameters of the brake and improve the braking performance of the brake in the wind generating set.
In order to solve the technical problems, the application provides a method for determining parameters of a brake of a wind generating set, comprising the following steps:
determining aerodynamic peak torque of the wind generating set, and calculating maximum braking torque of a brake according to the aerodynamic peak torque and the gear box speed ratio;
Calculating the maximum wind wheel rotating speed of the wind generating set, and calculating the maximum linear speed of the brake disc and the maximum angular speed of the brake disc according to the maximum wind wheel rotating speed and the brake parameter constraint information; the brake parameter constraint information comprises a unit area maximum power consumption rate of a brake disc, a brake pad friction coefficient and a brake pad maximum pressure;
Setting a ratio of the brake disc maximum linear velocity to the brake disc maximum angular velocity as a brake disc radius;
calculating the area of a brake pad according to the maximum braking torque, the maximum angular velocity of the brake disc and the maximum power consumption rate of the unit area of the brake disc;
the brake disc radius and the brake pad area are set as brake parameters in order to produce a corresponding brake according to the brake parameters.
Optionally, determining an aerodynamic peak torque of the wind generating set, and calculating a maximum braking torque of a brake according to the aerodynamic peak torque and the gearbox speed ratio comprises:
inquiring the rated power and the rated angular speed of the wind generating set, and setting the ratio of the rated power and the rated angular speed of the wind generating set as the aerodynamic peak torque;
Calculating a low-speed shaft torque T Low and low of the wind generating set according to a first formula; wherein the first formula is T Low and low ＝T Pneumatic power ×η Friction of ×η Loss of 1×η Pneumatic power ×η Loss of 2;T Pneumatic power representing aerodynamic peak torque, eta Friction of representing material friction coefficient, eta Loss of 1 representing caliper spring force loss coefficient, eta Pneumatic power representing aerodynamic load coefficient, eta Loss of 2 representing additional air loss coefficient;
the ratio of the low shaft torque to the gearbox speed ratio is set to the maximum braking torque of the brake.
Optionally, calculating the maximum wind wheel rotation speed of the wind generating set includes:
inquiring the rated angular speed and the braking delay time of the wind generating set;
Calculating the maximum wind wheel rotating speed omega Wind wheel of the wind generating set according to a second formula;
Wherein the second formula is omega Wind wheel ＝ω Rated for ×η Loss of 1+Δω Wind wheel ;ω Rated for , eta Loss of 1 is the calliper spring force loss coefficient, delta omega Wind wheel is the wind wheel rotating speed increased in the braking delay time.
Optionally, calculating the maximum linear velocity of the brake disc and the maximum angular velocity of the brake disc according to the maximum wind wheel rotation speed and the constraint information of the brake parameter includes:
Calculating the maximum angular velocity omega brake disc of the brake disc according to a third formula; wherein the third formula is I represents the gear box speed ratio;
Calculating the maximum linear velocity v brake disc of the brake disc according to a fourth formula; wherein the fourth formula is Δq represents the maximum power consumption rate per unit area of the brake disc, μ represents the brake pad friction coefficient, and P represents the brake pad maximum pressure.
Optionally, calculating the area of the brake pad according to the maximum braking torque, the maximum angular velocity of the brake disc and the maximum power consumption rate of the unit area of the brake disc includes:
Setting the product of the maximum braking torque and the maximum angular velocity of the brake disc as a power dissipation value;
setting the ratio of the power dissipation value to the maximum power dissipation rate of the unit area of the brake disc as the total area of the brake pad;
And calculating the area of the single brake pad according to the total area of the brake pads and the number of the brake pads.
Optionally, after setting the ratio of the brake disc maximum linear velocity to the brake disc maximum angular velocity to a brake disc radius, the method further includes:
And setting the ratio of the maximum braking torque to the radius of the brake disc as a caliper braking force, and writing the caliper braking force into a configuration file of the wind generating set so as to apply the braking force to the brake disc according to the caliper braking force after receiving a braking command.
Optionally, before producing the corresponding brake according to the brake parameters, the method further comprises:
Calculating a temperature rise curve of the brake disc in the braking process according to the brake parameters;
Judging whether the temperature rise curve meets preset requirements or not;
If yes, a step of producing a corresponding brake according to the brake parameters is carried out;
if not, optimizing the brake parameters.
The application also provides a brake parameter determining system of the wind generating set, which comprises:
the torque calculation module is used for determining aerodynamic peak torque of the wind generating set and calculating the maximum braking torque of a brake according to the aerodynamic peak torque and the gear box speed ratio;
The brake disc size determining module is used for calculating the maximum wind wheel rotating speed of the wind generating set and calculating the maximum linear speed of the brake disc and the maximum angular speed of the brake disc according to the maximum wind wheel rotating speed and brake parameter constraint information; the brake parameter constraint information comprises a unit area maximum power consumption rate of a brake disc, a brake pad friction coefficient and a brake pad maximum pressure; and is further configured to set a ratio of the brake disc maximum linear velocity to the brake disc maximum angular velocity to a brake disc radius;
The brake pad area determining module is used for calculating the area of the brake pad according to the maximum braking torque, the maximum angular speed of the brake disc and the maximum power consumption rate of the unit area of the brake disc;
and the parameter determining module is used for setting the radius of the brake disc and the area of the brake pad as brake parameters so as to produce a corresponding brake according to the brake parameters.
The application also provides a storage medium, on which a computer program is stored, which when being executed implements the steps performed by the method for determining the brake parameters of a wind turbine generator system.
The application also provides electronic equipment, which comprises a memory and a processor, wherein the memory stores a computer program, and the processor realizes the steps executed by the brake parameter determining method of the wind generating set when calling the computer program in the memory.
The application provides a method for determining parameters of a brake of a wind generating set, which comprises the following steps: determining aerodynamic peak torque of the wind generating set, and calculating maximum braking torque of a brake according to the aerodynamic peak torque and the gear box speed ratio; calculating the maximum wind wheel rotating speed of the wind generating set, and calculating the maximum linear speed of the brake disc and the maximum angular speed of the brake disc according to the maximum wind wheel rotating speed and the brake parameter constraint information; the brake parameter constraint information comprises a unit area maximum power consumption rate of a brake disc, a brake pad friction coefficient and a brake pad maximum pressure; setting a ratio of the brake disc maximum linear velocity to the brake disc maximum angular velocity as a brake disc radius; calculating the area of a brake pad according to the maximum braking torque, the maximum angular velocity of the brake disc and the maximum power consumption rate of the unit area of the brake disc; the brake disc radius and the brake pad area are set as brake parameters in order to produce a corresponding brake according to the brake parameters.
According to the application, the maximum braking torque of the brake is calculated according to the aerodynamic peak torque of the wind generating set and the gear box speed ratio, so that the capacity of the brake for bearing the maximum torque under extreme conditions is ensured. The application also calculates the maximum linear speed of the brake disc and the maximum angular speed of the brake disc according to the maximum wind wheel rotating speed and the brake parameter constraint information of the wind generating set, thereby determining the radius of the brake disc so as to reduce heat accumulation of the brake disc in the braking process. The application also calculates the area of the brake pad according to the maximum braking torque, the maximum angular velocity of the brake disc and the maximum power consumption rate of the unit area of the brake disc, thereby ensuring that the brake pad has enough friction area to provide enough braking force and avoiding overheating or damage in the braking process. The application sets the calculated radius of the brake disc and the area of the brake pad as the brake parameters and is used for producing the corresponding brake. The brake parameters are determined based on the actual running conditions and braking requirements of the wind generating set, so that the application can reasonably set the brake parameters and improve the braking performance of the brake in the wind generating set. The application also provides a brake parameter determining system of the wind generating set, a storage medium and an electronic device, which have the beneficial effects and are not repeated herein.
Drawings
For a clearer description of embodiments of the present application, the drawings that are required to be used in the embodiments will be briefly described, it being apparent that the drawings in the following description are only some embodiments of the present application, and other drawings may be obtained according to the drawings without inventive effort for those skilled in the art.
FIG. 1 is a flowchart of a method for determining brake parameters of a wind turbine generator system according to an embodiment of the present application;
FIG. 2 is a schematic diagram of a temperature rise curve according to an embodiment of the present application;
FIG. 3 is a schematic diagram showing the calculation of the change of the brake disc surface temperature with the stop time by the finite element method according to the embodiment of the present application;
Fig. 4 is a schematic structural diagram of a brake parameter determining system of a wind turbine generator system according to an embodiment of the present application.
Detailed Description
For the purpose of making the objects, technical solutions and advantages of the embodiments of the present application more apparent, the technical solutions of the embodiments of the present application will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present application, and it is apparent that the described embodiments are some embodiments of the present application, but not all embodiments of the present application. All other embodiments, which can be made by those skilled in the art based on the embodiments of the application without making any inventive effort, are intended to be within the scope of the application.
Referring to fig. 1, fig. 1 is a flowchart of a method for determining a brake parameter of a wind turbine generator system according to an embodiment of the present application.
The specific steps may include:
S101: determining aerodynamic peak torque of the wind generating set, and calculating maximum braking torque of a brake according to the aerodynamic peak torque and the gear box speed ratio;
the embodiment can be applied to an electronic device having a parameter calculation function and a brake model generation function, so as to determine a brake parameter and perform brake production according to the brake parameter.
The working parameters of the wind power plant, which require the determination of the brake parameters, may be determined prior to this step, and the aerodynamic peak torque may be determined from the working parameters of the wind power plant. Specifically, the present embodiment may determine a rated power of the wind turbine generator set and a rated angular velocity of the wind turbine generator set, calculate an aerodynamic peak torque, calculate a torque of the low speed shaft according to the aerodynamic peak torque and a correlation coefficient (e.g., a material friction coefficient, a caliper spring force loss coefficient, an aerodynamic load coefficient, an additional air loss coefficient, etc.), and calculate a maximum braking torque of the brake (i.e., a torque of the high speed shaft) according to the torque of the low speed shaft and a gear box speed ratio (i.e., a gear box speed ratio, a ratio of the low speed shaft speed to the high speed shaft speed). The low-speed shaft is connected with the input end of the gear box, and the high-speed shaft is connected with the output end of the gear box.
According to the process, firstly, aerodynamic peak torque which can be generated by the wind generating set at a specific wind speed is determined, and the maximum braking torque which the brake needs to bear is calculated according to the aerodynamic peak torque and the gear box speed ratio. In this way, it is ensured that the brake is able to cope with the maximum torque that the wind turbine generator system generates in extreme cases. The maximum braking torque is a brake design torque.
S102: calculating the maximum wind wheel rotating speed of the wind generating set, and calculating the maximum linear speed of the brake disc and the maximum angular speed of the brake disc according to the maximum wind wheel rotating speed and the brake parameter constraint information;
According to the embodiment, the rated angular speed and the braking delay time of the wind turbine generator set can be determined according to the working parameters of the wind turbine generator set, and then the maximum wind wheel rotating speed of the wind turbine generator set is calculated according to the rated angular speed and the braking delay time of the wind turbine generator set. The maximum wind wheel rotating speed is the maximum rotating speed which can be achieved by the wind wheel at a specific wind speed. And calculating the maximum linear speed and the maximum angular speed of the brake disc according to the maximum wind wheel rotating speed and the brake parameter constraint information (such as the maximum power consumption rate of the unit area of the brake disc, the friction coefficient of the brake disc and the maximum pressure of the brake disc).
S103: setting a ratio of the brake disc maximum linear velocity to the brake disc maximum angular velocity as a brake disc radius;
Wherein, this step can ensure that the brake disc can operate effectively under the maximum operating condition by setting the ratio of the maximum linear velocity of the brake disc to the maximum angular velocity as the radius of the brake disc. The brake disc radius may be the radius that the brake disc can reach at maximum.
S104: calculating the area of a brake pad according to the maximum braking torque, the maximum angular velocity of the brake disc and the maximum power consumption rate of the unit area of the brake disc;
The required area of the brake pad can be calculated after the maximum braking torque of the brake disc, the maximum angular velocity of the brake disc and the maximum power consumption rate of the unit area of the brake disc are obtained, and by the mode, the brake pad can be ensured to provide enough friction force in the braking process, and overheating or damage is avoided.
S105: the brake disc radius and the brake pad area are set as brake parameters in order to produce a corresponding brake according to the brake parameters.
On the basis of obtaining the radius of the brake disc and the area of the brake pad, the radius of the brake disc and the area of the brake pad can be set as brake parameters, and then corresponding brakes can be produced according to the brake parameters. As a possible implementation manner, the present embodiment may also build a brake model according to the brake parameters, and then produce a corresponding brake according to the brake model. The dimensions of the brake discs and brake pads of the resulting brake correspond to the brake parameters generated in the above-described solutions.
The maximum braking torque of the brake is calculated according to the aerodynamic peak torque of the wind generating set and the gear box speed ratio, so that the capacity of the brake for bearing the maximum torque under extreme conditions is ensured. The embodiment also calculates the maximum linear speed of the brake disc and the maximum angular speed of the brake disc according to the maximum wind wheel rotating speed and the brake parameter constraint information of the wind generating set, so as to determine the radius of the brake disc, and reduce heat accumulation of the brake disc in the braking process. The embodiment also calculates the area of the brake pad according to the maximum braking torque, the maximum angular velocity of the brake disc and the maximum power consumption rate of the unit area of the brake disc, thereby ensuring that the brake pad has enough friction area to provide enough braking force and avoiding overheating or damage during the braking process. The present embodiment sets the calculated brake disc radius and brake pad area as brake parameters and is used to produce a corresponding brake. The brake parameters are determined based on the actual running conditions and braking requirements of the wind generating set, so that the embodiment can reasonably set the brake parameters and improve the braking performance of the brake in the wind generating set.
As a further introduction to the corresponding embodiment of fig. 1, the maximum braking torque of the brake may be calculated by: inquiring the rated power and the rated angular speed of the wind generating set, and setting the ratio of the rated power and the rated angular speed of the wind generating set as the aerodynamic peak torque; calculating a low-speed shaft torque T Low and low of the wind generating set according to a first formula; the ratio of the low shaft torque to the gearbox speed ratio is set to the maximum braking torque of the brake.
Wherein the first formula is T Low and low ＝T Pneumatic power ×η Friction of ×η Loss of 1×η Pneumatic power ×η Loss of 2;T Pneumatic power representing aerodynamic peak torque, eta Friction of representing material friction coefficient, eta Loss of 1 representing caliper spring force loss coefficient, eta Pneumatic power representing aerodynamic load coefficient, eta Loss of 2 representing additional air loss coefficient.
As a further introduction to the corresponding embodiment of fig. 1, the maximum rotor speed of a wind turbine may be calculated by: inquiring the rated angular speed and the braking delay time of the wind generating set; and calculating the maximum wind wheel rotating speed omega Wind wheel of the wind generating set according to a second formula.
Wherein the second formula is omega Wind wheel ＝ω Rated for ×η Loss of 1+Δω Wind wheel ;ω Rated for , eta Loss of 1 is the calliper spring force loss coefficient, delta omega Wind wheel is the wind wheel rotating speed increased in the braking delay time.
The embodiment can calculate the maximum linear velocity of the brake disc and the maximum angular velocity of the brake disc according to the maximum wind wheel rotating speed and the constraint information of the brake parameters (the maximum power consumption rate of the unit area of the brake disc, the friction coefficient of the brake pad and the maximum pressure of the brake pad).
Specifically, in this embodiment, the maximum angular velocity ω brake disc of the brake disc may be calculated according to a third formula; wherein the third formula isI represents the gear box speed ratio;
Specifically, in this embodiment, the maximum linear velocity v brake disc of the brake disc may be calculated according to a fourth formula; wherein the fourth formula is Δq represents the maximum power consumption rate per unit area of the brake disc, μ represents the brake pad friction coefficient, and P represents the brake pad maximum pressure.
As a further introduction to the corresponding embodiment of fig. 1, the brake pad area may be calculated by: setting the product of the maximum braking torque and the maximum angular velocity of the brake disc as a power dissipation value; setting the ratio of the power dissipation value to the maximum power dissipation rate of the unit area of the brake disc as the total area of the brake pad; and calculating the area of the single brake pad according to the total area of the brake pads and the number of the brake pads.
As a further introduction to the corresponding embodiment of fig. 1, after setting the ratio of the maximum linear velocity of the brake disc to the maximum angular velocity of the brake disc to a brake disc radius, it is also possible to set the ratio of the maximum brake torque to the brake disc radius to a caliper braking force and to write the caliper braking force into a profile of the wind park in order to apply the braking force to the brake disc in accordance with the caliper braking force after receiving a braking command.
As a further introduction to the corresponding embodiment of fig. 1, the temperature rise profile of the brake disc during braking may also be calculated from the brake parameters before the corresponding brake is produced according to the brake parameters; judging whether the temperature rise curve meets preset requirements or not; if yes, a step of producing a corresponding brake according to the brake parameters is carried out; if not, optimizing the brake parameters. Specifically, in this embodiment, the temperature rise curve may be calculated by a finite element method or an empirical formula.
The flow described in the above embodiment is explained below by way of an embodiment in practical application.
The mechanical braking mechanism is an auxiliary braking mechanism of a wind generating set safety protection system. There are two ways of performing mechanical braking: one is spring force braking, hydraulic force releases braking, so that braking effect under the condition of power failure of a power grid can be ensured; the other is hydraulic pressure braking, the spring force releases the brake, so that controllable flexible mechanical braking can be realized, but if the power grid is cut off for a long time, the mechanical braking can be released.
Variable speed constant frequency wind generating sets commonly adopt a variable pitch system of an independent actuating mechanism, namely multiple protection is realized by aerodynamic braking completely, but even so, a stop braking device is required to meet the needs of maintenance personnel. In the above-mentioned case, the parking brake device may be made small as long as it has a capability of rotating the impeller from a low speed to a complete stop, and in order to prevent the impeller from rotating due to a high wind speed in a parking state, a locking device is generally provided on the low speed shaft, that is, a locking disc with a bolt hole is provided on the low speed shaft, and a bolt can be used to lock the housing. The mechanical brake mechanism consists of a brake disc mounted on the high-speed shaft and brake calipers arranged around the brake disc. The brake calipers are fixed and the brake disc rotates with the high speed shaft, but the relevant standard requires that the mechanical brake is able to bring the rotor to a complete stop at a wind speed 5m/s higher than the maximum wind speed maintained or repaired by the manufacturer. The brake caliper has a pre-loaded spring braking force and the hydraulic pressure opens the brake caliper by means of a piston in the hydraulic cylinder. As a standby braking mechanism, the pre-pressing spring braking force of mechanical braking is generally required to ensure the safe shutdown of the wind generating set when the wind generating set is off-line under rated load. However, in the case of a normal stop, the hydraulic force is not completely released, i.e. only a part of the spring force acts during braking. For this purpose, a special relief valve and an accumulator are provided in the hydraulic system to ensure that the braking force of the spring is not completely provided during braking.
For a fixed-pitch constant-speed wind generating set, a mechanical braking mechanism is required to independently brake the off-grid wind generating set under the condition of pneumatic braking failure. Therefore, the braking torque of the mechanical brake is large enough, and in the worst case, when the unit generates electricity with rated load at a speed higher than the rated wind speed, the sudden load shedding machine is stopped after the power grid fault happens suddenly, and in this case, if the pitch mechanism is blocked, the mechanical brake system is put into operation as an emergency braking mechanism. This situation causes a significant transient load on the transmission system, and the design of all components of the transmission system must take into account the braking torque of the mechanical brake, but too much braking torque is undesirable, which can lead to a significant increase in the cost of the overall transmission system.
During braking of the mechanical brake system, the kinetic energy of the wind wheel and the drive train and the additional energy fed by the aerodynamic moment are dissipated in the form of heat in the brake disc and the brake pads, resulting in a rapid initial temperature rise near the surface of the brake disc. The energy dissipation ratio is equal to the product of the braking torque and the rotational speed of the brake disc, so that the energy dissipation ratio cannot be reduced while maintaining a high surface temperature in the latter stages of braking.
The friction coefficient of the resin-based brake pad is maintained at 0.4at a temperature of 250 ℃ and is reduced to 0.25 at 400 ℃ with 300 ℃ generally being the upper temperature limit of the resin-based pad; the friction coefficient of the sintered metal brake pad was about 0.4at 400 ℃ and was reduced to 0.33 at 750 ℃; since the temperature of the ductile iron brake disc itself is limited to 600 ℃, such a temperature is not practically achievable. Sintered metal brake pads allow the brake disc to absorb more energy, and sintered metal is a more efficient thermal conductor than resin-based materials, so it is often necessary to incorporate insulation in the caliper design to prevent the oil in the hydraulic cylinder from overheating. In theory, the brake can be designed according to the upper temperature rise limit of the brake disc, but in practice, the varying torque complicates the calculation and cannot quantify the margin of error for uncontrolled braking torque loss. Mechanical brake system design is limited by the following factors: (1) centrifugal stress of the brake disc; (2) number and size of brake pads; (3) power consumption per unit area of the brake pad; (4) brake disc temperature rise.
One key parameter to be selected in brake design is the design braking torque. Due to factors such as interlayer and pollution of the brake pad, the friction coefficient is quantified in terms of changing torque and error margin of uncontrolled braking torque loss, and the designed braking torque calculated according to the nominal friction value is 1.78 times of the maximum aerodynamic torque according to GL (Germanischer Lloyd) stipulation.
According to the embodiment, the design torque of the brake is deduced, the diameter of a brake disc and the size of a brake pad are reasonably selected, and the braking force of a caliper is reduced to a reasonable level, so that a method for rapidly designing a braking system of a wind generating set is provided; the temperature rise of the brake disc is calculated respectively through a finite element method and an empirical formula, and the surface temperature of the brake disc obtained through the two methods is compared with a brake moment change curve; and finally, according to the pneumatic torque and rotating speed curve, performing simulation calculation on the highest temperature which can be reached by the surface of the brake disc, and verifying the rationality of the design of the mechanical brake system.
The embodiment provides a method for rapidly designing a wind generating set braking system, which is applied to a wind generating set with the diameter of 49 meters and the stall adjustment of 0.75MW for designing a high-speed shaft brake, and the wind generating set can realize the shutdown of the wind generating set at the wind speed of 20m/s under the condition that 10% overspeed occurs after a power grid is lost and with or without the help of an aerodynamic braking system. The low shaft rated speed is 22.6rpm, the generator slip is ignored, and the brake delay time is assumed to be 0.5 seconds. The method comprises the following steps:
step 1: the design torque of the brake is deduced.
One key parameter to be selected in brake design is torque at the high speed mechanical brake system (i.e., maximum braking torque). This step makes it possible to determine the relation between the rotational speed and the aerodynamic torque at a prescribed wind speed of 20 m/s. The coefficient of friction may vary significantly above and below the design value due to factors such as the sandwich and contamination of the brake pads, and therefore the design braking torque calculated from the nominal friction value must be increased by a suitable material factor. Aerodynamic peak torque occurs when the maximum rotational speed is reached before the mechanical brake is applied.
The aerodynamic peak torque is calculated as follows:
T Pneumatic power is peak aerodynamic torque; p Rated for is the rated power of the unit; omega Rated for is the rated rotational speed of the unit. The calculation mode of the rated rotating speed of the unit is as follows: ω Rated for =low-speed shaft rated rotational speed×2pi/60.
The design torque T Low and low (i.e., low-speed shaft torque) of the low-speed shaft mechanical brake system is calculated as follows:
T Low and low ＝T Pneumatic power ×η Friction of ×η Loss of 1×η Pneumatic power ×η Loss of 2＝380.5×1.2×1.1×1.35×1.05＝712.0kNm。
T Low and low is the design torque of the mechanical brake system of the low-speed shaft; GL guidelines (GERMANISCHER LLOYD) specify a material coefficient η Friction of =1.2 of friction coefficient; caliper spring force loss coefficient η Loss of 1 =1.1; aerodynamic load coefficient η Pneumatic power =1.35; the extra air loss coefficient η Loss of 2 =1.05. In this way, it is ensured that the rotor remains stationary without a very large temperature rise when η Friction of 、η Loss of 1、η Pneumatic power and η Loss of 2 defined by GL are completely eroded.
The torque at the high speed mechanical brake system (i.e., the maximum braking torque of the brake) T Manufacturing process is converted into:
The above i represents the gearbox ratio.
Step 2: the brake disc diameter is selected.
There is a 0.5 second delay before the mechanical brake system is put into operation, during which the rotor speed increases by about 1rpm, at which time the maximum rotor speed ω Wind wheel is:
ω Wind wheel ＝ω Rated for ×η Loss of 1+Δω Wind wheel ＝22.6×1.1+1＝25.9rpm；
The caliper spring force loss coefficient eta Loss of 1＝1.1;Δω Wind wheel of the mechanical braking system is the rotational speed of the wind wheel increased during the delay period of the mechanical braking system input; converting to the maximum rotating speed of the high-speed shaft to obtain the maximum angular speed omega brake disc of the brake disc;
The sintered metal brake pad can accept a friction speed of up to 115m/s, while the allowable friction speed of the resin-based brake pad is only about 30 m/s; in order to keep the power consumption rate deltaq per unit area of the brake pad at a sufficiently low level and to have satisfactory braking performance at high friction speeds, sintered metal is used as a preferred brake pad material, and the maximum linear speed of the brake disc is obtained by the following formula:
v brake disc is the linear speed of the brake disc, and is determined by the power consumption rate delta Q of unit area, the friction coefficient mu of the brake pad and the pressure P of the brake pad; wherein, the Ferodo standard requires that DeltaQ is less than or equal to 11.6MW/m 2; the friction coefficient of the sintered metal brake pad is mu=0.4; p is the pressure of the brake pad, and the requirement is reduced to below 275kN/m 2.
Thus, the maximum allowable brake disc radius for centrifugal stress is:
r is the maximum allowable brake disc radius of centrifugal stress, wherein the diameter of the brake disc of 1.2m is selected to minimize the temperature rise, and v brake disc is the linear speed of the brake disc.
Step 3: the brake pad size is selected.
The total area of the brake pad needs to keep the maximum power consumption per unit area of the brake pad below Δq=11600 kW/m 2. Thus, the power dissipation reaches a maximum at the start of braking, and the power dissipation value P Consumption of is the product of the maximum braking torque T Manufacturing process and the maximum angular speed ω brake disc of the brake disk, i.e.:
P Consumption of ＝T Manufacturing process ×ω brake disc ＝10.55×182.4＝1924.7kW；
therefore, the total area S Is required to of the brake pad is:
S Is required to is the total area of the brake pad which is required to be minimum; p Consumption of is the dissipation value of the power consumption and Δq is the maximum power consumption rate per unit area of the brake disc.
Step 4: and calculating the braking force of the caliper.
The braking force required by the mechanical brake system caliper is as follows:
F Braking system is the required braking force friction, calculated from the maximum braking torque T Manufacturing process divided by the brake disc radius R.
Considering that the front surface and the rear surface of the brake caliper apply braking force to the brake disc, in order to ensure that the stress on the two sides of the brake disc is uniform during braking, the brake calipers are required to be symmetrically arranged on the two sides of the brake disc, so that the number of the brake pads is a multiple of 4; the number of the brake blocks is limited by the size of the installation coupler on the brake disc, the convenience of the installation and maintenance of the brake blocks and other factors, and the area of each brake block is required to be as small as possible; as a possible embodiment, the number of brake pads n=32, i.e. 8 brake pads are mounted on each caliper.
S Single sheet is the area of a single brake pad; n is the number of the brake pads and can be a multiple of 4.
Step 5: the brake disc temperature rise was calculated by the finite element method.
Assuming that the heat generated enters the brake disc at a uniform intensity over the swept-out area of the brake pad as the brake disc rotates, the temperature rise is calculated by the finite element method over a time interval Δt taking into account the slice x of the brake disc closest to the brake disc surface, the thickness Δx and the cross-sectional area a, the element thickness Δx being given by:
x is the slice closest to the brake disc surface, Δx is the slice thickness; t is the initial time before the braking of the brake disc, and delta t is the time interval;
θ is temperature, thermal conductivity k=36W/m/K, specific heat capacity C p =502J/kg/K, and density ρ=7085 kg/m 3 of 450-grade spheroidal graphite cast iron, and thermal diffusivity can be obtained If the time increment Δt is selected at 0.025 seconds and the cell thickness is 1.005mm, the above formula is reduced to:
θ(x,t+△t)＝θ(x，t)+0.25[θ(x+Δx,t)+θ(x-Δx,t)-2θ(x,t)]；
This equation can be used to calculate the temperature distribution across the brake disc, starting from a uniform distribution, and applying the appropriate increment to the braking surface at the boundary.
Step 6: and calculating the temperature rise of the brake disc by using an empirical formula.
The maximum temperature rise of the brake disc can be estimated by the following empirical formula:
Wherein, theta 0 is the initial temperature of the brake disc; θ max is the highest temperature reached in the automatic process of the brake disc; e is the total energy dissipated in joules, t is the duration of the stop in seconds, s=pi (D-w) w, S is the area of the brake disc surface swept by the brake pad, D is the disc diameter, and w is the brake disc width.
Step 7: a brake disc surface temperature-braking torque curve is generated.
Referring to fig. 2, fig. 2 is a schematic diagram of a temperature rise curve provided by the embodiment of the application, and the diagram shows the change of the surface temperature of a brake disc along with the braking moment when the stall-regulated wind turbine generator system is braked emergently after overspeed.
The continuous solid line in fig. 2 calculates the surface temperature rise of the brake disc for the finite element method; the dashed line is the temperature rise estimated by empirical formula. When the ratio of brake torque to maximum aerodynamic torque is about 1.6, the brake disc surface temperature rise is minimal. When the ratio falls below this value, the extension of the stop time will result in more energy being absorbed from the wind, and thus the temperature starts to rise rapidly. However, the maximum brake temperature is relatively insensitive to increases in ratios above 1.6. The temperature rise curve generation conditions shown in fig. 2 are: rated rotational speed
22.6Rpm, brake delay = 0.5s, maximum aerodynamic torque = 380.5kNm, diameter of brake disc
=1.2M, single brake pad area=53.1 cm 2. In FIG. 2, the ratio of braking torque to maximum aerodynamic torque is plotted on the abscissa, and the temperature rise (. Degree. C.) is plotted on the ordinate.
Step 8: the surface temperature of the brake disc is calculated in a simulation manner.
Referring to fig. 3, fig. 3 is a schematic diagram showing a change of a brake disc surface temperature with a stop time calculated by a finite element method according to an embodiment of the present application. In fig. 3, the abscissa indicates time(s), the ordinate indicates torque (kNm) corresponding to the pneumatic torque curve, the ordinate indicates rotational speed (rpm) corresponding to the rotational speed curve, and the ordinate indicates temperature rise (c) corresponding to the brake disc surface temperature curve. The curve generation conditions shown in fig. 3 are: rated rotation speed=22.6 rpm, rated power=75 kW, braking delay=0.5 s, braking torque= 712.0kNm, maximum starting torque= 380.5kNm, diameter of brake disc 1.2m, number of calipers
=32, Single brake pad area 53.1cm 2. As can be seen from fig. 3, after stopping to half, the surface temperature reached a maximum of 440 c, which lasted 4.7 seconds from the start of braking. This temperature is well below the limit of the sintered bond pad.
Referring to fig. 4, fig. 4 is a schematic structural diagram of a brake parameter determining system of a wind turbine generator system according to an embodiment of the present application, where the system may include:
A torque calculation module 401, configured to determine an aerodynamic peak torque of the wind generating set, and calculate a maximum braking torque of a brake according to the aerodynamic peak torque and the gearbox speed ratio;
A brake disc size determining module 402, configured to calculate a maximum wind wheel rotational speed of the wind generating set, and calculate a brake disc maximum linear speed and a brake disc maximum angular speed according to the maximum wind wheel rotational speed and brake parameter constraint information; the brake parameter constraint information comprises a unit area maximum power consumption rate of a brake disc, a brake pad friction coefficient and a brake pad maximum pressure; and is further configured to set a ratio of the brake disc maximum linear velocity to the brake disc maximum angular velocity to a brake disc radius;
a brake pad area determining module 403, configured to calculate a brake pad area according to the maximum braking torque, the maximum angular velocity of the brake disc, and the maximum power consumption rate per unit area of the brake disc;
and the parameter determining module 404 is used for setting the radius of the brake disc and the area of the brake pad as brake parameters so as to produce corresponding brakes according to the brake parameters.
The maximum braking torque of the brake is calculated according to the aerodynamic peak torque of the wind generating set and the gear box speed ratio, so that the capacity of the brake for bearing the maximum torque under extreme conditions is ensured. The embodiment also calculates the maximum linear speed of the brake disc and the maximum angular speed of the brake disc according to the maximum wind wheel rotating speed and the brake parameter constraint information of the wind generating set, so as to determine the radius of the brake disc, and reduce heat accumulation of the brake disc in the braking process. The embodiment also calculates the area of the brake pad according to the maximum braking torque, the maximum angular velocity of the brake disc and the maximum power consumption rate of the unit area of the brake disc, thereby ensuring that the brake pad has enough friction area to provide enough braking force and avoiding overheating or damage during the braking process. The present embodiment sets the calculated brake disc radius and brake pad area as brake parameters and is used to produce a corresponding brake. The brake parameters are determined based on the actual running conditions and braking requirements of the wind generating set, so that the embodiment can reasonably set the brake parameters and improve the braking performance of the brake in the wind generating set.
Further, the process of the torque calculation module 401 determining an aerodynamic peak torque of the wind generating set and calculating a maximum braking torque of the brake according to the aerodynamic peak torque and the gearbox speed ratio includes: inquiring the rated power and the rated angular speed of the wind generating set, and setting the ratio of the rated power and the rated angular speed of the wind generating set as the aerodynamic peak torque; calculating a low-speed shaft torque T Low and low of the wind generating set according to a first formula; wherein the first formula is T Low and low ＝T Pneumatic power ×η Friction of ×η Loss of 1×η Pneumatic power ×η Loss of 2;T Pneumatic power representing aerodynamic peak torque, eta Friction of representing material friction coefficient, eta Loss of 1 representing caliper spring force loss coefficient, eta Pneumatic power representing aerodynamic load coefficient, eta Loss of 2 representing additional air loss coefficient; the ratio of the low shaft torque to the gearbox speed ratio is set to the maximum braking torque of the brake.
Further, the process of calculating the maximum rotor speed of the wind generating set by the brake disc size determining module 402 includes: inquiring the rated angular speed and the braking delay time of the wind generating set; calculating the maximum wind wheel rotating speed omega Wind wheel of the wind generating set according to a second formula; wherein the second formula is omega Wind wheel ＝ω Rated for ×η Loss of 1+Δω Wind wheel ;ω Rated for , eta Loss of 1 is the calliper spring force loss coefficient, delta omega Wind wheel is the wind wheel rotating speed increased in the braking delay time.
Further, the process of calculating the maximum linear velocity of the brake disc and the maximum angular velocity of the brake disc by the brake disc size determining module 402 according to the maximum wind wheel rotational speed and the brake parameter constraint information includes:
Calculating the maximum angular velocity omega brake disc of the brake disc according to a third formula; wherein the third formula is I represents the gear box speed ratio;
Calculating the maximum linear velocity v brake disc of the brake disc according to a fourth formula; wherein the fourth formula is Δq represents the maximum power consumption rate per unit area of the brake disc, μ represents the brake pad friction coefficient, and P represents the brake pad maximum pressure.
Further, the process of calculating the area of the brake pad by the brake pad area determining module 403 according to the maximum braking torque, the maximum angular velocity of the brake disc and the maximum power consumption rate per unit area of the brake disc includes: setting the product of the maximum braking torque and the maximum angular velocity of the brake disc as a power dissipation value; setting the ratio of the power dissipation value to the maximum power dissipation rate of the unit area of the brake disc as the total area of the brake pad; and calculating the area of the single brake pad according to the total area of the brake pads and the number of the brake pads.
Further, the method further comprises the following steps:
And the caliper braking force determining module is used for setting the ratio of the maximum linear speed of the brake disc to the maximum angular speed of the brake disc as a caliper braking force after setting the ratio of the maximum braking torque to the radius of the brake disc as the radius of the brake disc, and writing the caliper braking force into a configuration file of the wind generating set so as to apply braking force to the brake disc according to the caliper braking force after receiving a braking command.
Further, the method further comprises the following steps:
The curve generation module is used for calculating a temperature rise curve of the brake disc in the braking process according to the brake parameters before the corresponding brake is produced according to the brake parameters; the temperature rise curve is also used for judging whether the temperature rise curve meets preset requirements; if yes, a step of producing a corresponding brake according to the brake parameters is carried out; if not, optimizing the brake parameters.
Since the embodiments of the system portion and the embodiments of the method portion correspond to each other, the embodiments of the system portion refer to the description of the embodiments of the method portion, which is not repeated herein.
The present application also provides a storage medium having stored thereon a computer program which, when executed, performs the steps provided by the above embodiments. The storage medium may include: a U-disk, a removable hard disk, a Read-Only Memory (ROM), a random access Memory (Random Access Memory, RAM), a magnetic disk, or an optical disk, or other various media capable of storing program codes.
The application also provides an electronic device, which can comprise a memory and a processor, wherein the memory stores a computer program, and the processor can realize the steps provided by the embodiment when calling the computer program in the memory. Of course the electronic device may also include various network interfaces, power supplies, etc.
In the description, each embodiment is described in a progressive manner, and each embodiment is mainly described by the differences from other embodiments, so that the same similar parts among the embodiments are mutually referred. For the system disclosed in the embodiment, since it corresponds to the method disclosed in the embodiment, the description is relatively simple, and the relevant points refer to the description of the method section. It should be noted that it will be apparent to those skilled in the art that various modifications and adaptations of the application can be made without departing from the principles of the application and these modifications and adaptations are intended to be within the scope of the application as defined in the following claims.
It should also be noted that in this specification, relational terms such as first and second, and the like are used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. Moreover, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. Without further limitation, an element defined by the phrase "comprising one … …" does not exclude the presence of other like elements in a process, method, article, or apparatus that comprises the element.
Claims (10)
1. A method for determining a brake parameter of a wind turbine generator system, comprising:
determining aerodynamic peak torque of the wind generating set, and calculating maximum braking torque of a brake according to the aerodynamic peak torque and a gear box speed ratio;
Calculating the maximum wind wheel rotating speed of the wind generating set, and calculating the maximum linear speed of the brake disc and the maximum angular speed of the brake disc according to the maximum wind wheel rotating speed and the brake parameter constraint information; the brake parameter constraint information comprises a unit area maximum power consumption rate of a brake disc, a brake pad friction coefficient and a brake pad maximum pressure;
Setting a ratio of the brake disc maximum linear velocity to the brake disc maximum angular velocity as a brake disc radius;
calculating the area of a brake pad according to the maximum braking torque, the maximum angular velocity of the brake disc and the maximum power consumption rate of the unit area of the brake disc;
the brake disc radius and the brake pad area are set as brake parameters in order to produce a corresponding brake according to the brake parameters.
2. The method of determining brake parameters of a wind park according to claim 1, wherein determining an aerodynamic peak torque of the wind park and calculating a maximum braking torque of a brake from the aerodynamic peak torque and a gearbox speed ratio comprises:
inquiring the rated power and the rated angular speed of the wind generating set, and setting the ratio of the rated power and the rated angular speed of the wind generating set as the aerodynamic peak torque;
Calculating a low-speed shaft torque T Low and low of the wind generating set according to a first formula; wherein the first formula is T Low and low ＝T Pneumatic power ×η Friction of ×η Loss of 1×η Pneumatic power ×η Loss of 2;T Pneumatic power representing aerodynamic peak torque, eta Friction of representing material friction coefficient, eta Loss of 1 representing caliper spring force loss coefficient, eta Pneumatic power representing aerodynamic load coefficient, eta Loss of 2 representing additional air loss coefficient;
the ratio of the low shaft torque to the gearbox speed ratio is set to the maximum braking torque of the brake.
3. A method of determining a brake parameter of a wind park according to claim 1, wherein calculating a maximum rotor speed of the wind park comprises:
inquiring the rated angular speed and the braking delay time of the wind generating set;
Calculating the maximum wind wheel rotating speed omega Wind wheel of the wind generating set according to a second formula;
Wherein the second formula is omega Wind wheel ＝ω Rated for ×η Loss of 1+Δω Wind wheel ;ω Rated for , eta Loss of 1 is the calliper spring force loss coefficient, delta omega Wind wheel is the wind wheel rotating speed increased in the braking delay time.
4. A method for determining brake parameters of a wind park according to claim 3, wherein calculating a brake disc maximum linear velocity and a brake disc maximum angular velocity based on said maximum wind wheel rotational speed and brake parameter constraint information comprises:
Calculating the maximum angular velocity omega brake disc of the brake disc according to a third formula; wherein the third formula is I represents the gear box speed ratio;
Calculating the maximum linear velocity v brake disc of the brake disc according to a fourth formula; wherein the fourth formula is Δq represents the maximum power consumption rate per unit area of the brake disc, μ represents the brake pad friction coefficient, and P represents the brake pad maximum pressure.
5. The method for determining brake parameters of a wind turbine generator system according to claim 1, wherein calculating a brake pad area based on the maximum brake torque, the maximum angular velocity of the brake disc, and the maximum power consumption rate per unit area of the brake disc comprises:
Setting the product of the maximum braking torque and the maximum angular velocity of the brake disc as a power dissipation value;
setting the ratio of the power dissipation value to the maximum power dissipation rate of the unit area of the brake disc as the total area of the brake pad;
And calculating the area of the single brake pad according to the total area of the brake pads and the number of the brake pads.
6. The method for determining a brake parameter of a wind power plant according to claim 1, further comprising, after setting a ratio of the maximum linear speed of the brake disc to the maximum angular speed of the brake disc as a brake disc radius:
And setting the ratio of the maximum braking torque to the radius of the brake disc as a caliper braking force, and writing the caliper braking force into a configuration file of the wind generating set so as to apply the braking force to the brake disc according to the caliper braking force after receiving a braking command.
7. The method for determining brake parameters of a wind turbine generator system according to claim 1, further comprising, before producing the corresponding brake according to the brake parameters:
Calculating a temperature rise curve of the brake disc in the braking process according to the brake parameters;
Judging whether the temperature rise curve meets preset requirements or not;
If yes, a step of producing a corresponding brake according to the brake parameters is carried out;
if not, optimizing the brake parameters.
8. A brake parameter determination system for a wind turbine generator system, comprising:
The torque calculation module is used for determining aerodynamic peak torque of the wind generating set and calculating the maximum braking torque of a brake according to the aerodynamic peak torque and the gear box speed ratio;
The brake disc size determining module is used for calculating the maximum wind wheel rotating speed of the wind generating set and calculating the maximum linear speed of the brake disc and the maximum angular speed of the brake disc according to the maximum wind wheel rotating speed and brake parameter constraint information; the brake parameter constraint information comprises a unit area maximum power consumption rate of a brake disc, a brake pad friction coefficient and a brake pad maximum pressure; and is further configured to set a ratio of the brake disc maximum linear velocity to the brake disc maximum angular velocity to a brake disc radius;
The brake pad area determining module is used for calculating the area of the brake pad according to the maximum braking torque, the maximum angular speed of the brake disc and the maximum power consumption rate of the unit area of the brake disc;
and the parameter determining module is used for setting the radius of the brake disc and the area of the brake pad as brake parameters so as to produce a corresponding brake according to the brake parameters.
9. An electronic device comprising a memory and a processor, the memory having stored therein a computer program, the processor, when calling the computer program in the memory, implementing the steps of the method for determining brake parameters of a wind park according to any of claims 1-7.
10. A storage medium having stored therein computer executable instructions which, when loaded and executed by a processor, implement the steps of the method for determining brake parameters of a wind park according to any of claims 1 to 7.
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| CN202410373502.2A CN118278187A (en) | 2024-03-29 | 2024-03-29 | Method, system, equipment and medium for determining brake parameters of wind generating set |
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| CN202410373502.2A CN118278187A (en) | 2024-03-29 | 2024-03-29 | Method, system, equipment and medium for determining brake parameters of wind generating set |
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