CN116909126B - Water cooling flow PID control method based on flywheel heat dissipation model - Google Patents
Water cooling flow PID control method based on flywheel heat dissipation model Download PDFInfo
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- 230000017525 heat dissipation Effects 0.000 title claims abstract description 49
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Abstract
The invention discloses a water cooling flow PID control method based on a flywheel heat dissipation model, and belongs to the field of flywheel heat exchange. The method models the heat generation, heat dissipation and water cooling heat exchange processes of the flywheel, establishes an output equation of a heat dissipation energy flow model of the flywheel and a heat transfer process of the flywheel, thereby calculating the heat energy of a water cooling heat exchange surface in a dynamic process and improving the calculation accuracy of the heat generation of the flywheel; PID control is carried out on the flow opening of the cooling water valve based on the difference value between the heat energy of the water-cooling heat exchange surface and the heat energy standard value, and the flow of cooling water is timely adjusted, so that the heat dissipation of the flywheel is controlled.
Description
Technical Field
The invention relates to the field of flywheel heat exchange, in particular to a water cooling flow PID control method based on a flywheel heat dissipation model.
Background
With the improvement of the duty ratio of renewable energy sources in an energy structure, more and more renewable energy sources are connected with the grid, so that the problem of randomness and fluctuation is brought, and the stable operation of the power system is challenged.
Establishing large-scale energy storage is a key technology for coping with the randomness and fluctuation of renewable energy sources and supporting renewable energy source grid connection. The current energy storage technology comprises pumped storage, chemical battery energy storage and flywheel energy storage. The flywheel energy storage is a hotspot for large-scale energy storage in the current power grid due to the characteristics of high reliability, flexible configuration, long service life, environmental protection and the like. In research and development projects of flywheel energy storage at home and abroad, a series of projects such as wind power flywheel combined frequency modulation power stations, large flywheel energy storage power stations and the like are developed, and a plurality of generator sets are also provided with flywheel energy storage devices with different capacities.
However, with the increase of the power density of the flywheel energy storage system, the problem of temperature rise caused by loss and heating becomes one of the bottlenecks of development of the flywheel energy storage system. The flywheel energy storage system generates heat mainly by motor and electromagnetic bearing, and the motor generates heat mainly from stator core loss, winding copper loss, rotor eddy current loss and rotor mechanical loss, and electromagnetic bearing generates heat mainly by iron loss and copper loss constitution. At present, a great deal of research is carried out on how to establish rules and models of flywheel rotor bearing heating, temperature field distribution and flywheel energy storage system heat dissipation, but the design problem of a water cooling heat dissipation control strategy and the basic problem of multi-target cooperative control are required to be further studied in the aspects of fine characterization of heat generation and heat transfer characteristics of a magnetic levitation flywheel energy storage system. It is necessary to build a finer flywheel heat exchange, water-cooling heat dissipation heat exchange model and a corresponding cooperative control strategy.
Disclosure of Invention
The invention aims to provide a water-cooling flow PID control method based on a flywheel heat dissipation model, which can accurately calculate heat generation of a flywheel, timely adjust the flow of cooling water and control heat dissipation of the flywheel.
In order to achieve the above object, the present invention provides the following solutions:
a water cooling flow PID control method based on a flywheel heat dissipation model comprises the following steps:
selecting a flywheel heat exchange surface according to a heat diffusion direction, and establishing a flywheel heat dissipation physical model according to the selected flywheel heat exchange surface;
simplifying the flywheel heat dissipation physical model into a flywheel heat dissipation energy flow model;
establishing a state space equation according to the flywheel heat dissipation energy flow model;
constructing an output equation of the flywheel heat transfer process;
determining flywheel body parameters;
according to the flywheel body parameters, utilizing the output equation and the state space equation to obtain the heat energy of the water-cooling heat exchange surface;
and PID control is carried out on the flow opening of the cooling water valve based on the difference value between the heat energy of the water-cooling heat exchange surface and the heat energy standard value.
According to the specific embodiment provided by the invention, the invention discloses the following technical effects:
the invention discloses a water cooling flow PID control method based on a flywheel heat dissipation model, which models the processes of heat generation, heat dissipation and water cooling heat exchange of a flywheel, establishes an output equation of the flywheel heat dissipation energy flow model and the flywheel heat transfer process, thereby calculating the heat energy of a water cooling heat exchange surface in the dynamic process and improving the calculation accuracy of the flywheel heat generation; PID control is carried out on the flow opening of the cooling water valve based on the difference value between the heat energy of the water-cooling heat exchange surface and the heat energy standard value, and the flow of cooling water is timely adjusted, so that the heat dissipation of the flywheel is controlled.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions of the prior art, the drawings that are needed in the embodiments will be briefly described below, it being obvious that the drawings in the following description are only some embodiments of the present invention, and that other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.
FIG. 1 is a flow chart of a water cooling flow PID control method based on a flywheel heat dissipation model provided by an embodiment of the invention;
FIG. 2 is a schematic diagram of a flywheel and a water cooling device model according to an embodiment of the present invention;
FIG. 3 is a schematic diagram of a flywheel heat dissipation physical model according to an embodiment of the present invention;
FIG. 4 is a schematic diagram of a flywheel heat dissipation energy flow model according to an embodiment of the present invention;
fig. 5 is a schematic diagram of flow control of a water-cooled valve according to an embodiment of the present invention.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present invention, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
The invention models the flywheel heat generation, heat dissipation and water cooling heat exchange processes based on the heat flow theory, and designs the water cooling heat dissipation control strategy based on the model.
In order that the above-recited objects, features and advantages of the present invention will become more readily apparent, a more particular description of the invention will be rendered by reference to the appended drawings and appended detailed description.
As shown in fig. 1, an embodiment of the present invention provides a water cooling flow PID control method based on a flywheel heat dissipation model, including:
step 1: and selecting a flywheel heat exchange surface according to the heat diffusion direction, and establishing a flywheel heat dissipation physical model according to the selected flywheel heat exchange surface.
The heat exchange surface is selected in the direction of heat diffusion, referring to fig. 2, the contact surface of the flywheel rotor and the axial filling gas is a first heat exchange surface, and the contact wall from the axial filling gas to the water cooling liquid is a second heat exchange surface.
And a flywheel heat dissipation physical model is established by combining a heat exchange link of water cooling heat dissipation, as shown in figure 3. The water cooling wall in fig. 3 corresponds to the water cooling heat exchange wall in fig. 2, and the cooling water D1 and the cooling water D2 in fig. 3 correspond to the two cooling water pipelines in fig. 2 respectively. In fig. 3, the cooling water flows into the location of the cold fluid through the valve.
Step 2: and simplifying the flywheel heat dissipation physical model into a flywheel heat dissipation energy flow model.
When the heat storage performance and the water cooling heat exchange capacity of the flywheel are evaluated, the energy stored on the gas filled in the flywheel and the water cooling heat exchange wall plays a crucial role in the process, so that a model can be assumed:
1) The content, flow and temperature of the gas-filled working medium in the flywheel are kept unchanged in a short time scale;
2) The energy stored by the flywheel is mainly filled with air and heat exchange wall parts, and other parts can be ignored;
3) The wall between the filling gas and the water-cooling liquid in the flywheel is equivalent to a heat exchanger with a certain length and thickness;
4) The cooling water feed pump is assumed to be a feed water process with a certain pressure, temperature and flow.
The flywheel heat dissipation energy flow model is shown in fig. 4. The flywheel heat dissipation energy flow model comprises: flywheel axial filling gas equivalent thermal fluid thermal resistance R h,1 Equivalent cold fluid thermal resistance R of flywheel axial filling gas c,1 Equivalent thermal fluid thermal resistance R of flywheel cooling water heat exchange wall h,2 Equivalent cold fluid thermal resistance R of flywheel cooling water heat exchange wall c,2 The first capacitor, the second capacitor, the first power supply, the second power supply, the third power supply, the fourth power supply and the fifth power supply.
One end of the first capacitor is respectively filled with equivalent thermal fluid thermal resistance R of gas in the axial direction of the flywheel h,1 Is equivalent to the thermal resistance R of cold fluid filled with gas axially in one end and flywheel c,1 The other end of the first capacitor is grounded; flywheel axial filling gas equivalent thermal fluid thermal resistance R h,1 The other end of the flywheel is connected with the positive electrode of the first power supply, and the flywheel is axially filled with gas equivalent cold fluid thermal resistance R c,1 The other end of the first power supply is connected with the negative electrode of the second power supply.
One end of the first capacitor and the flywheel are axially filled with equivalent thermal fluid thermal resistance R of gas h,1 Is equivalent to the thermal resistance R of cold fluid filled with gas axially in one end and flywheel c,1 Corresponds to the flywheel bearing temperature T at the connection point of one end of (2) w1 Flywheel axial filling gas equivalent thermal fluid thermal resistance R h,1 The other end of the flywheel is corresponding to the axial filling gas temperature T of the flywheel h1,in Equivalent cold fluid thermal resistance R of flywheel axial filling gas c,1 The other end of the water heater corresponds to the inlet temperature T of the first section of cooling water c1,in 。
One end of the second capacitor is respectively equivalent to the thermal fluid thermal resistance R of the flywheel cooling water heat exchange wall h,2 Equivalent cold fluid thermal resistance R of one end of (2) and flywheel cooling water heat exchange wall c,2 The other end of the second capacitor is grounded; equivalent thermal fluid thermal resistance R of flywheel cooling water heat exchange wall h,2 The other end of the flywheel cooling water heat exchange wall equivalent cold fluid thermal resistance R is connected with the positive electrode of the third power supply c,2 The other end of the first power supply is respectively connected with the negative electrode of the fourth power supply and the negative electrode of the fifth power supply; the positive pole of the second power supply is connected with the positive pole of the fourth power supply.
One end of the second capacitor is equivalent to the flywheel cooling water heat exchange wallThermal fluid thermal resistance R h,2 Equivalent cold fluid thermal resistance R of one end of (2) and flywheel cooling water heat exchange wall c,2 Corresponds to the wall temperature T of the flywheel container w2 Equivalent thermal fluid thermal resistance R of flywheel cooling water heat exchange wall h,2 The other end of the water tank corresponds to the temperature T of the cooling water of the flywheel h2,in Equivalent cold fluid thermal resistance R of flywheel cooling water heat exchange wall c,2 The other end of the water tank corresponds to the inlet temperature T of the second section of cooling water c2，in 。
The temperature T of the cooling water outlet of the first section corresponds to the connection line of the positive electrode of the second power supply and the positive electrode of the fourth power supply c1.out The anode of the fifth power supply corresponds to the outlet temperature T of the second section of cooling water c2.out The negative pole of the third power supply corresponds to the temperature T of the cooling water outlet of the flywheel h2.out 。
Step 3: and establishing a state space equation according to the flywheel heat dissipation energy flow model.
According to the flywheel heat dissipation energy flow model shown in fig. 3, a state space equation is established as follows:
wherein x is a state variable, c p Specific heat capacity of water-cooled heat exchange wall of flywheel, M 1 And M 2 The metal masses of the two sections of heat exchange walls are respectively.
One important reason for establishing the state space equation is that the heat accumulating capacity of each link of the flywheel can be accurately represented, and the heat accumulating capacity is corrected according to historical data, so that the accurate heat energy of the heat exchange surface is obtained in real time.
Step 4: and constructing an output equation of the flywheel heat transfer process.
Illustratively, the output equation construction process is as follows:
4.1 input vector u
u＝[G 1，c ，G 2，c ，G 1，h ，G 2，h ] T The vector u is the heat capacity flow of each section of cold and hot fluid, and is calculated by the formula (2). The flow is obtained through a flywheel control platform flow real-time database. Wherein G is 1，c For the first stage of cold fluid heat capacity flow, G 1，c ＝c p D 1，c ，D 1，c Cold fluid flow for the first stage; g 2，c For the second stage cold fluid heat capacity stream, G 2，c ＝c p D 2，c ，D 2，c Cold fluid flow for the second stage; g 1，h For the first section of heat capacity flow of heat fluid, G 1，h ＝c p D 1，h ，D 1，h The first section of hot fluid flow; g 2，h For the second-stage heat capacity flow of heat fluid, G 2，h ＝c p D 2，h ，D 2，h Is the second section of hot fluid flow.
4.2 state variable x, the value of which is obtained by the flywheel state monitoring platform.
x＝[T w1 ，T w2 ] T (3)
4.3 output variable computation
To evaluate the heat transfer process, Q is selected 1 ，Q 2 ，Q 3 ，Q 4 As an output variable of the multi-stage segmentation system to form an output vector y.
y＝[Q 1 ，Q 2 ，Q 3 ，Q 4 ] T (4)
Q i Representing the heat exchange quantity of each section of cold fluid; i.e.)>
Qi+2 TableShowing working medium and metal heat accumulation in each section. I.e.)>
The above is written as the output equation:
y＝Cx+D (5)
wherein,
c and D describe the change in output variable caused by the change in input and state variables.
Step 5: and determining flywheel body parameters.
5.1 on-line calculating the pressure and temperature of the filling gas in the flywheel according to the enthalpy value, p s 、T c1，in By the internal energy formula of the object:
U＝njRT c1，in /2 (6)
where n is the amount of the object substance, j is the degree of freedom, j is the number of molecular atoms, R is a constant= 8,T and is the filling gas temperature, and the internal energy U is determined. Then through an enthalpy value formula:
h in ＝U+p s G in (7)
wherein p is s To fill the gas pressure, G in For the input side gas flow, determining the enthalpy value h of the gap filling working medium entering the flywheel rotor in As flywheel rotor side energy, formula (8):
Q 0 ＝h in *m in (8)
h in and m in Respectively an input side enthalpy value and a mass flow rate.
5.2, determining quality and length parameters of the filling working medium and the water-cooling heat exchange wall in the flywheel according to a flywheel product manual; for calculating the thermal resistance of each segment, as in formula (9):
wherein k is i，h 、k i，c The heat transfer coefficient parameters of the heat exchange wall of the hot fluid and the cold fluid are respectively A i，h 、A i，c The surface area parameters of the hot fluid and cold fluid heat exchange surfaces are obtained by the length parameters respectively.
Step 6: and obtaining the heat energy of the water-cooling heat exchange surface by utilizing the output equation and the state space equation according to the flywheel body parameters.
The heat transfer system is described by a state equation and an output equation, and can be simplified into
The formula (6) can represent the heat capacity flow and state variable of each section of cold and hot fluid as input, and the relation of heat output can be obtained by substituting the measured input quantity and the monitored platform parameter, so that the water cooling flow can be adjusted according to the heat.
And finally, the water-cooling heat exchange surface heat energy (water-cooling heat exchange surface heat energy Q) is in the final step:
Q＝Q 0 +Q 1 +Q 2 +Q 3 +Q 4 (11)
q represents redundant heat energy of the flywheel after cooling in real time.
Step 7: and PID control is carried out on the flow opening of the cooling water valve based on the difference value between the heat energy of the water-cooling heat exchange surface and the heat energy standard value.
The calculated Q is compared with a given standard value Q b (thermal energy standard value) and feedback control is performed on the flow opening of the cooling water valve according to the difference, as shown in fig. 5.
ΔQ＝Q b -Q (12)
Wherein k is coolingThe up-down range change rate of the opening of the water valve,or->Determined by Δq:
if the heat energy of the water-cooling heat exchange surface is greater than or equal to the heat energy standard value, controlling the flow valve to change at a rate of up-down travel according to the opening of the cooling water valveClosing; wherein T is D And (5) adding the time constant of the control link for the opening degree of the valve.
If the heat energy of the water-cooling heat exchange surface is smaller than the heat energy standard value, controlling the opening of the flow valve to be as follows the change rate of the upper and lower strokes of the opening of the cooling water valvePerforming enlargement; wherein T is C The time constant of the control link is reduced for the valve opening.
The invention aims to establish a dynamic energy flow model based on a flywheel heat dissipation process, an energy flow process from a flywheel rotor to filling gas and then to a water cooling wall, and particularly a dynamic change process. The filling of gas and water-cooled heat exchange wall in the flywheel is the main link of the flywheel heat dissipation process. In the invention, the method calculates the heat of the working fluid in the dynamic process, and improves the accuracy of the energy of the working medium. According to the calculation method, the heat generated by the flywheel can be accurately calculated, and the cooling water flow can be timely adjusted to control the heat dissipation of the flywheel.
In the present specification, each embodiment is described in a progressive manner, and each embodiment is mainly described in a different point from other embodiments, and identical and similar parts between the embodiments are all enough to refer to each other.
The principles and embodiments of the present invention have been described herein with reference to specific examples, the description of which is intended only to assist in understanding the methods of the present invention and the core ideas thereof; also, it is within the scope of the present invention to be modified by those of ordinary skill in the art in light of the present teachings. In view of the foregoing, this description should not be construed as limiting the invention.
Claims (3)
1. The water cooling flow PID control method based on the flywheel heat dissipation model is characterized by comprising the following steps of:
selecting a flywheel heat exchange surface according to a heat diffusion direction, and establishing a flywheel heat dissipation physical model according to the selected flywheel heat exchange surface;
simplifying the flywheel heat dissipation physical model into a flywheel heat dissipation energy flow model;
establishing a state space equation according to the flywheel heat dissipation energy flow model;
constructing an output equation of the flywheel heat transfer process;
determining flywheel body parameters;
according to the flywheel body parameters, utilizing the output equation and the state space equation to obtain the heat energy of the water-cooling heat exchange surface;
PID control is carried out on the flow opening of the cooling water valve based on the difference value between the heat energy of the water-cooling heat exchange surface and the heat energy standard value;
the assumption conditions for simplifying the flywheel heat dissipation physical model into a flywheel heat dissipation energy flow model include:
the content, flow and temperature of the gas-filled working medium in the flywheel are kept unchanged within a preset time scale;
the flywheel energy storage component is only filled with air and a heat exchange wall;
the wall between the filling gas and the water-cooling liquid in the flywheel is equivalent to a heat exchanger with a certain length and thickness;
the cooling water feed pump has a water feed process with certain pressure, temperature and flow;
the flywheel dissipates heat energy flowThe model comprises: flywheel axial filling gas equivalent thermal fluid thermal resistance R h,1 Equivalent cold fluid thermal resistance R of flywheel axial filling gas c,1 Equivalent thermal fluid thermal resistance R of flywheel cooling water heat exchange wall h,2 Equivalent cold fluid thermal resistance R of flywheel cooling water heat exchange wall c,2 The first capacitor, the second capacitor, the first power supply, the second power supply, the third power supply, the fourth power supply and the fifth power supply;
one end of the first capacitor is respectively filled with equivalent thermal fluid thermal resistance R of gas in the axial direction of the flywheel h,1 Is equivalent to the thermal resistance R of cold fluid filled with gas axially in one end and flywheel c,1 The other end of the first capacitor is grounded; flywheel axial filling gas equivalent thermal fluid thermal resistance R h,1 The other end of the flywheel is connected with the positive electrode of the first power supply, and the flywheel is axially filled with gas equivalent cold fluid thermal resistance R c,1 The other end of the first power supply is connected with the negative electrode of the second power supply;
one end of the first capacitor and the flywheel are axially filled with equivalent thermal fluid thermal resistance R of gas h,1 Is equivalent to the thermal resistance R of cold fluid filled with gas axially in one end and flywheel c,1 Corresponds to the flywheel bearing temperature T at the connection point of one end of (2) w1 Flywheel axial filling gas equivalent thermal fluid thermal resistance R h,1 The other end of the flywheel is corresponding to the axial filling gas temperature T of the flywheel h1,in Equivalent cold fluid thermal resistance R of flywheel axial filling gas c,1 The other end of the water heater corresponds to the inlet temperature T of the first section of cooling water c1,in ；
One end of the second capacitor is respectively equivalent to the thermal fluid thermal resistance R of the flywheel cooling water heat exchange wall h,2 Equivalent cold fluid thermal resistance R of one end of (2) and flywheel cooling water heat exchange wall c,2 The other end of the second capacitor is grounded; equivalent thermal fluid thermal resistance R of flywheel cooling water heat exchange wall h,2 The other end of the flywheel cooling water heat exchange wall equivalent thermal fluid thermal resistance R is connected with the positive electrode of a third power supply h,2 The other end of the flywheel cooling water heat exchange wall equivalent cold fluid thermal resistance R is also connected with the negative electrode of the first power supply c,2 The other end of the first power supply is respectively connected with the negative electrode of the fourth power supply and the negative electrode of the fifth power supply; the positive electrode of the second power supply is connected with the positive electrode of the fourth power supply;
one end of the second capacitor is connected with the flywheelEquivalent thermal fluid thermal resistance R of cooling water heat exchange wall h,2 Equivalent cold fluid thermal resistance R of one end of (2) and flywheel cooling water heat exchange wall c,2 Corresponds to the wall temperature T of the flywheel container w2 Equivalent thermal fluid thermal resistance R of flywheel cooling water heat exchange wall h,2 The other end of the water tank corresponds to the temperature T of the cooling water of the flywheel h2,in Equivalent cold fluid thermal resistance R of flywheel cooling water heat exchange wall c,2 The other end of the water tank corresponds to the inlet temperature T of the second section of cooling water c2,in ；
The temperature T of the cooling water outlet of the first section corresponds to the connection line of the positive electrode of the second power supply and the positive electrode of the fourth power supply c1.out The anode of the fifth power supply corresponds to the outlet temperature T of the second section of cooling water c2.out The negative pole of the third power supply corresponds to the temperature T of the cooling water outlet of the flywheel h2.out ；
The state space equation is:
wherein x is a state variable, c p Specific heat capacity of water-cooled heat exchange wall of flywheel, M 1 And M 2 The metal masses of the two sections of heat exchange walls are respectively;
the method for constructing the output equation of the flywheel heat transfer process specifically comprises the following steps:
defining an input vector u as: u= [ G ] 1,c ,G 2,c ,G 1,h ,G 2,h ] T The method comprises the steps of carrying out a first treatment on the surface of the Wherein G is 1,c For the first stage of cold fluid heat capacity flow, G 1,c ＝c p D 1,c ，D 1,c Cold fluid flow for the first stage; g 2,c For the second stage cold fluid heat capacity stream, G 2，c ＝c p D 2，c ，D 2，c Cold fluid flow for the second stage; g 1，h For the first section of heat capacity flow of heat fluid, G 1，h ＝c p D 1，h ，D 1,h The first section of hot fluid flow; g 2，h For the second-stage heat capacity flow of heat fluid, G 2，h ＝c p D 2，h ，D 2，h The second section of hot fluid flow;
the preset state variable x is x= [ T ] w1 ，T w2 ] T ；
Defining an output vector y as: y= [ Q ] 1 ，Q 2 ，Q 3 ，Q 4 ] T The method comprises the steps of carrying out a first treatment on the surface of the Wherein Q is 1 、Q 2 The heat exchange amount of the cold fluid of the first section and the second section is respectively,Q 3 、Q 4 the working medium of the first section and the working medium of the second section and the heat accumulation quantity of metal are respectively adopted,
according to the input vector u, the state variable x and the output vector y, an output equation of the flywheel heat transfer process is established as y=cx+d; wherein, C is a proportionality coefficient,d is a constant term, which is a constant term,
determining flywheel body parameters, specifically including:
according to formula Q 0 ＝h in ×m in Determining flywheel rotor side energy; in which Q 0 The flywheel rotor side energy; m is m in Is the input side mass flow; h is a in For input side enthalpy value, h in ＝U+p s G in U is internal energy, u=njrt c1，in 2, n is the amount of the object substance, j is the degree of freedom, R is a constant, p s To fill the gas pressure, G in Is the input side gas flow;
using the formulaDetermining the thermal resistance of the two sections; the thermal resistance of the two sections comprises equivalent thermal fluid thermal resistance R of flywheel axial filling gas h，1 Equivalent cold fluid thermal resistance R of flywheel axial filling gas c，1 Equivalent thermal fluid thermal resistance R of flywheel cooling water heat exchange wall h，2 Equivalent cold fluid thermal resistance R of flywheel cooling water heat exchange wall c，2 The method comprises the steps of carrying out a first treatment on the surface of the Wherein k is i，h 、k i，c The heat transfer coefficient parameters of the heat exchange wall of the hot fluid and the cold fluid are respectively A i，h 、A i，c The surface area parameters of the heat exchange surface of the hot fluid and the cold fluid are obtained by the length parameters respectively; i=1, 2, i represents a segment number;
the flywheel rotor side energy and the thermal resistance of the two sections form flywheel body parameters;
according to the flywheel body parameters, the output equation and the state space equation are utilized to obtain the heat energy of the water-cooling heat exchange surface, and the method specifically comprises the following steps:
according to the thermal resistance of the two sections, calculating to obtain an output vector y by utilizing the output equation and the state space equation;
from the calculated output vector y and flywheel rotor side energy, the formula q=q is used 0 +Q 1 +Q 2 +Q 3 +Q 4 Determining heat energy Q of a water-cooling heat exchange surface;
PID control is carried out on the flow opening of the cooling water valve based on the difference value between the heat energy of the water-cooling heat exchange surface and the heat energy standard value, and the method specifically comprises the following steps:
if the heat energy of the water-cooling heat exchange surface is greater than or equal to the heat energy standard value, controlling the flow valve to change at a rate of up-down travel according to the opening of the cooling water valveClosing; wherein T is D Adding a time constant of a control link for the opening of the valve;
if the heat energy of the water-cooling heat exchange surface is smaller than the heat energy standard value, controlling the opening of the flow valve to be as follows the change rate of the upper and lower strokes of the opening of the cooling water valvePerforming enlargement; wherein T is C The time constant of the control link is reduced for the valve opening.
2. The water cooling flow PID control method based on the flywheel heat dissipation model according to claim 1, wherein the flywheel heat exchange surface comprises: the first heat exchange surface and the second heat exchange surface;
the first heat exchange surface is the contact surface of the flywheel rotor and the axial filling gas;
the second heat exchange surface is a contact wall of the axial filling gas and the water-cooling liquid.
3. The water cooling flow PID control method based on the flywheel heat dissipation model according to claim 1, wherein the flywheel heat dissipation physical model comprises: flywheel rotor and water cooling wall;
the input end of the flywheel rotor is a first section of cooling water inlet, and the output end of the flywheel rotor is a first section of cooling water outlet;
the input end of the water-cooled wall is a second section cooling water inlet, and the output end of the water-cooled wall is a second section cooling water outlet.
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