CN105006791B - Thermal balance temperature difference control method based on the natural hot pressing of long vertical enclosed busbar - Google Patents
Thermal balance temperature difference control method based on the natural hot pressing of long vertical enclosed busbar Download PDFInfo
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Abstract
The invention discloses the thermal balance temperature difference control method based on the natural hot pressing of long vertical enclosed busbar, temperature difference T meets relational expression with heat source strength q, bus vertical height H in long vertical enclosed busbar：Δ T=a1+a2*H+a3*q+a4*H2+a5*q2, wherein：a1For the first coefficient, a2For the second coefficient, a3For the 3rd coefficient, a4For the 4th coefficient, a5For the 5th coefficient.The present invention carries out numerical computations and field measurement comparative study to thermal balance under the conditions of vertical enclosed busbar (IPB) gravity-flow ventilation of Large Underground Power Station heat-flash stream length and Temperature Distribution, obtain temperature distributing rule and feature under the conditions of the gravity-flow ventilation in the restricted clearance of heat-flash source, to ensure the control of the IPB temperature difference, correct selection thermal balance mode in engineering, it is ensured that the Temperature Distribution of IPB safe and reliable operations and advanced reliable radiating mode provide guidance.
Description
Technical field
It is natural based on long vertical enclosed busbar in particular to one kind the invention belongs to Hydraulic and Hydro-Power Engineering field of electromechanical technology
The thermal balance temperature difference control method of hot pressing.
Background technology
The vertical enclosed busbar Temperature Distribution of Large Underground Power Station length and heat dissipation problem are the guarantees of bus run safety.With
Domestic hydroelectric project fast development, application of the long vertical isolated-phase enclosed bus (IPB) in underground power station is also more and more extensive,
But to different capabilities and the IPB of vertical height, without relevant design, manufacturer's standard or regulation.The cooling of each underground power station
Mode is cooled down by gravity-flow ventilation.Such as Pengshui Hydropower Station, water cloth a strip of land between hills power station, its enclosed busbar rated current is respectively
14kA, 16kA, the vertical IPB of the above-mentioned water power head of a station be the hole lead-out mode of a machine one, and gravity-flow ventilation, forced ventilation is respectively adopted
Mode meets the requirement of IPB thermal balances.Increase and arrangement with the specified heat flow of the vertical enclosed busbar of underground power station length
Complication, only by gravity-flow ventilation whether still conform to IPB thermal balance require need carry out specifically calculate after judge.
According to national standard, isolated-phase enclosed bus should meet temperature increase requirement when declared working condition is run, during using aluminium, its
Conductor allows maximum temperaturerise to be 50K, and shell allows maximum temperaturerise to be 30K, and environment temperature is 40K.Need it is emphasized that no matter
It is level or vertically arranged bus, national standard does not all provide the regulation of bus temperature difference along its length.But according to
The manufacturing experience of enclosed busbar, when temperature difference is more than to a certain degree bus along its length, will influence bus structure to design.
In order to reach bus safe operation requirement, shell, conductor temperature at each position of bus also answer phase while being less than national regulations
To equilibrium, vertical isolated-phase enclosed bus is especially grown, it is even more so.But at present under natural hot pressing condition, correspondence is different
Temperature controlled research of the heat source strength parameter Down Highway on vertical section length direction belongs to blank.
The content of the invention
In order to solve the regulation that current national standard does not provide bus temperature difference along its length, and at each position of bus
Shell, conductor temperature is while be less than national regulations the problem of also answer relative equilibrium, the present invention provides a kind of based on long vertical
The thermal balance temperature difference control method of enclosed busbar nature hot pressing.
To achieve the above object, the thermal balance temperature difference control based on the natural hot pressing of long vertical enclosed busbar designed by the present invention
Method processed, it is characterized in that, temperature difference T is met with heat source strength q, bus vertical height H in long vertical enclosed busbar closes
It is formula：
Δ T=a1+a2*H+a3*q+a4*H2+a5*q2
Wherein：a1For the first coefficient, a2For the second coefficient, a3For the 3rd coefficient, a4For the 4th coefficient, a5For the 5th coefficient.
Preferably, the calculation formula of the heat source strength q is：
Q=QS/[SQ- π * (DL 2/4)*n]
Wherein, QSFor shaft height direction caloric value, SQEffectively radiated sectional area, D for vertical shaftLFor bus shell external diameter, n
For bus group number in vertical shaft.
Preferably, when the span of the heat source strength q is 150W/m3≤ q ＜ 260W/m3, bus vertical height H
When span is 60m≤H ＜ 100m, the first coefficient a1Value be ﹣ 8.3399, the second coefficient a2Value be
0.18336, the 3rd coefficient a3Value be 0.4559, the 4th coefficient a4Value be 6.7559 × 10﹣ 4, the described 5th is
Number a5Value be 7.7898 × 10﹣ 6。
Preferably, when the span of the heat source strength q is 260W/m3≤ q ＜ 400W/m3, bus vertical height H
When span is 60m≤H ＜ 100m, the first coefficient a1Value be 14.5349, the second coefficient a2Value be
0.01656, the 3rd coefficient a3Value be 0.1521, the 4th coefficient a4Value be 2.9100 × 10﹣ 4, the described 5th is
Number a5Value be ﹣ 6.3164 × 10﹣ 6。
Preferably, when the span of the heat source strength q is 75W/m3≤ q ＜ 200W/m3, bus vertical height H takes
When being worth scope for 100m≤H ＜ 180m, the first coefficient a1Value be ﹣ 2.9452, the second coefficient a2Value be
0.08397, the 3rd coefficient a3Value be 0.04767, the 4th coefficient a4Value be ﹣ 2.2651 × 10﹣ 4, the described 5th
Coefficient a5Value be 2.0157 × 10﹣ 6。
Preferably, when the span of the heat source strength q is 200W/m3≤ q ＜ 300W/m3, bus vertical height H
When span is 100m≤H ＜ 180m, the first coefficient a1Value be 15.4622, the second coefficient a2Value be
0.00572, the 3rd coefficient a3Value be ﹣ 0.1769, the 4th coefficient a4Value be ﹣ 0.01072 × 10﹣ 4, described
Five coefficient a5Value be 5.8279 × 10﹣ 6。
The present invention is to thermal balance under the conditions of the vertical enclosed busbar gravity-flow ventilation of Large Underground Power Station heat-flash stream length and temperature point
Cloth carries out numerical computations and field measurement comparative study, obtains temperature point under the conditions of the gravity-flow ventilation in the restricted clearance of heat-flash source
Cloth rule and feature, and analyze vertical shaft size, the influence of the factor to IPB Temperature Distributions such as heat source strength, bus height, and find out
The parameter of crucial controlling influence and the radiating strategy of reply different situations are played on its Temperature Distribution.Propose correspondence different heat sources
Temperature difference controlling value of the superelevation bus on vertical section length direction under intensive parameter.
The present invention is distributed different, the diverse location bus in restricted clearance according to the bus in isolated-phase enclosed bus vertical shaft
Local temperature and temperature distributing rule along vertical height direction be in different Variation Features, pass through complete three-dimensional Numerical-Mode
Intend, provide under conditions of different operational factors, analyze the vertical isolated-phase enclosed bus temperature field of high current length, the single mother of diverse location
Line vertical temperature distribution rule, imports and exports difference variation rule, and then the high current explored and recognized under mixed ventilation pattern is long
Hot-fluid and Temperature Distribution performance in vertical isolated-phase enclosed bus vertical shaft, and its different operational factors flow the shadow with heat exchange to it
Ring rule.
The present invention is for the heat-flash stream of the vertical enclosed busbar of large-scale power station length and the complexity of arrangement, using calculating fluid force
Learn (computational fluid dynamics, CFD), according to different IPB heat source strength, different shaft height etc. because
Plain labor is calculated, and finds systematic IPB thermal balances rule, is to ensure that the control of the IPB temperature difference, correct selection heat are flat in engineering
Weighing apparatus mode, it is ensured that the Temperature Distribution of IPB safe and reliable operations and advanced reliable radiating mode provide guidance.
Embodiment
Below in conjunction with specific embodiment, the present invention is described in further detail.
1) thermal balance in IPB vertical shafts
The radiating of IPB conductors is carried out by the heat radiation between conductor and shell, shell inner air convection, and shell is then led
If passing through the heat loss through convection of air outside heat radiation, shell.Heat radiation is determined by radiation coefficient (being constant), in IPB vertical direction
Upper no difference, therefore the convection current of the influence IPB mainly inside and outside air of IPB of Temperature Distribution in vertical direction.
PM=QMF+QMD
PM+PK=QKF+QKD
PMFor the power attenuation of conductor, W/ (m phases)；
QMFFor heat loss through radiation of the IPB to shell；
QMDFor the convection heat transfer' heat-transfer by convection between conductor and shell；
PKFor the power attenuation of conductor, shell, W/ (m phases)；
QKFFor the heat loss through radiation of shell；
QKDFor the heat loss through convection of air outside shell and shell.
The heatings of IPB in itself are due to that the loss of conductor and shell is caused, and conductor and shell directly have convection current, radiation
Its mechanism of conducting heat is complex, it is therefore desirable to which model carries out following simplify：
(1) due to consideration that the hot property of air, viscosity, thus consider conductor by 100% heat transfer to shell, and
The length direction of conductor ignores loss of the conductor with gas in itself.
(2) only occur in each section of conductor of IPB vertical direction, housing, hole wall in this section of object between heat transfer, each section without heat
Conduction, ignores the thermal conduction resistance of IPB conductors, case material.
2) physical model of IPB vertical shafts
IPB and its vertical shaft can be reduced to heat-generating cylindrical body and be placed in the closing space of vertical shaft formation, and forming one has
The restricted clearance heat exchange models of endogenous pyrogen.
3) mathematical modeling of IPB vertical shafts
Underground power station IPB heat dissipation problem is a complicated heat transfer process, if solved using conventional method, no
Only formula is complicated, and needs to make mathematical modeling a large amount of simplified and it is assumed that necessarily cause result of calculation deviation actual.With
The development of computer technology, calculating essence can be increased substantially for carrying out solution using numerical computation method under complex situations
Degree.
Specific steps include：
1) according to mass conservation law, the law of conservation of momentum and law of conservation of energy, to each point in shaft space
Thermal balance state sets up governing equation：
Continuity equation：
The equation of momentum：
Energy equation：
In formula：ui：Average speed components of the air in vertical direction；uj：The average speed components of air in the horizontal direction；
xi：Vertical height：t：Time；ρ：Atmospheric density；p：Pressure；v：The laminar flow coefficient of viscosity；vt：Turbulence factor；gi：Vertical direction weight
Power acceleration；β：Air thermal expansion coefficient；T：At hoistway entrance and exit mean temperature；T∞：Environment temperature；T：Actual temperature
Degree；Γ：Generalized diffusion process coefficient；I：Radiation intensity；
2) value to pressure p is carried out it is assumed that solving average speed components u of the air in the equation of momentum in vertical directioni；
3) value of pair pressure p assumed is modified so that average speed components u of the air gone out in vertical directioniIt is full
Sufficient continuity equation；
4) by revised pressure p and air vertical direction average speed components uiValue substitute into energy equation, ask
Solve actual temperature T；
5) repeat step 1)~4) until calculating the actual temperature T of each point in vertical shaft.
Wherein, step 1) energy equation in, generalized diffusion process coefficient Γ and Prandtl number PrWith σTThere are following relational expressions：
Γ=v/Pr+vt/σT
In formula：v：The laminar flow coefficient of viscosity；vt：Turbulence factor；σT：Empirical, takes 0.9~1；Pr：Prandtl number.
Prandtl number Pr can be according to formula Pr=cpV/ λ are obtained, in formula：cpFor specific heat at constant pressure, λ is thermal conductivity factor.
The essence of underground power station IPB heat dissipation problems is really to have with the non-isothermal turbulent-flow heat-exchanging of endogenous pyrogen, external heat radiation
Under comprehensive function, the temperature field of the air in vertical shaft restricted clearance, velocity field reach the process accordingly balanced.This limited sky
Interior air-flow is by by the effect of thermal current from bottom to top of IPB shells plus thermogenetic buoyancy lift for power.Numerical-Mode
Analog model uses Standard law of wall method using the K-ε two-equation models for considering buoyancy lift, wall.Using SIMPLE Algorithm for Solving
Discrete, discrete equation uses QUICK forms to prevent pseudo- diffusion, employs the progress of multilist surface radiation (S2S) model
Radiation is calculated.
Radiation intensity I computation model is：
In formula：Position vector；s：Vertical length；Direction vector；a：Absorption coefficient；σs：Scattering coefficient；n：Refraction
Coefficient；σ：Stefan ﹣ Boltzmann constants；T：Actual temperature；Φ：Phase function；Ω'：Space multistory angle.Space multistory angle
The parameters such as Ω ', absorption coefficient a have model structure and material character to determine.
4) thermal equilibrium analysis of IPB vertical shafts
Under the conditions of gravity-flow ventilation, calculating analysis is carried out by the IPB Temperature Distributions to multiple Large Underground Power Stations and drawn,
Temperature in some underground power station IPB surface temperatures and vertical shaft gradually rises, and maximum occurs in the first half, and in outlet section
Temperature decreases on the contrary causes temperature that the high distribution curve in the low centre in two ends is presented, its temperature difference within control range, and its
Significantly " chimney " effect is not presented in rule；But the underground power station IPB surface temperatures also having progressively are carried with height increase
Height, IPB vertical shafts do not have temperature to be stepped up also with height increase, with obvious " chimney " effect.
When IPB vertical shaft endogenous pyrogen intensity q is relatively low, the gravity-flow ventilation that the hot pressing that its IPB is produced as endogenous pyrogen is formed is changed
Heat energy power can meet thermal balance requirement, and the thermal buoyancy effect caused in outlet section is not enough to overcome outside IPB exit sites room relatively
Cryogenic air is influenceed, and strong convection heat transfer is produced in exit, is substantially reduced outlet block temperature and while is influenceed IPB tops close
The surface temperature and hoistway temperature of outlet so that IPB " chimney " effect is not obvious.As heat source strength q increases, in limited sky
The interior gravity-flow ventilation produced is not enough to take away the heat that IPB is distributed, and is also gradually risen with the increase air themperature of height,
This further weakens heat-exchange capacity and causes gradually rising for IPB surface temperatures, therefore when the increasing of the heat source strength q in IPB
Plus the altitude temperature difference effect that IPB is imported and exported is stepped up so that IPB " chimney " effect is stepped up.
Heat source strength q calculation formula is：
Q=QS/[SQ- π * (DL 2/4)*n]
Wherein, QSFor shaft height direction caloric value, SQEffectively radiated sectional area, D for vertical shaftLFor bus shell external diameter, n
For bus group number in vertical shaft.
By substantial amounts of simulation work and engineering measurement, thermal balance in the vertical enclosed busbar restricted clearance of Large Copacity length is grasped
Restricting relation between mechanism and its each influence factor, obtain heat source strength q in the temperature difference △ T and IPB under gravity-flow ventilation and
Bus vertical height H Multi-parameter data piecewise fitting correlation.
Δ T=a1+a2*H+a3*q+a4*H2+a5*q2
Wherein：a1For the first coefficient, a2For the second coefficient, a3For the 3rd coefficient, a4For the 4th coefficient, a5For the 5th coefficient.
When heat source strength q span is 150W/m3≤ q ＜ 260W/m3, bus vertical height H span be
During 60m≤H ＜ 100m, the first coefficient a1Value be ﹣ 8.3399, the second coefficient a2Value be 0.18336, the 3rd coefficient a3Value
For 0.4559, the 4th coefficient a4Value be 6.7559 × 10﹣ 4, the 5th coefficient a5Value be 7.7898 × 10﹣ 6.Then Δ T=﹣
8.3399+0.18336H+0.4559q+(6.7559×10﹣ 4)H2+(7.7898×10﹣ 6)q2。
When heat source strength q span is 260W/m3≤ q ＜ 400W/m3, bus vertical height H span be
During 60m≤H ＜ 100m, the first coefficient a1Value be 14.5349, the second coefficient a2Value be 0.01656, the 3rd coefficient a3Value
For 0.1521, the 4th coefficient a4Value be 2.9100 × 10﹣ 4, the 5th coefficient a5Value be ﹣ 6.3164 × 10﹣ 6.Then Δ T=
14.5349+0.01656H+0.1521q+(2.9100×10﹣ 4)H2- (6.3164 × 10﹣ 6)q2。
When heat source strength q span is 75W/m3≤ q ＜ 200W/m3, bus vertical height H span be
During 100m≤H ＜ 180m, the first coefficient a1Value be ﹣ 2.9452, the second coefficient a2Value be 0.08397, the 3rd coefficient a3Value
For 0.04767, the 4th coefficient a4Value be ﹣ 2.2651 × 10﹣ 4, the 5th coefficient a5Value be 2.0157 × 10﹣ 6.Then Δ T=﹣
2.9452+0.08397H+0.04767q- (2.2651 × 10﹣ 4)H2+(2.0157×10﹣ 6)*q2。
When heat source strength q span is 200W/m3≤ q ＜ 300W/m3, bus vertical height H span be
During 100m≤H ＜ 180m, the first coefficient a1Value be 15.4622, the second coefficient a2Value be 0.00572, the 3rd coefficient a3Value
For ﹣ 0.1769, the 4th coefficient a4Value be ﹣ 0.01072 × 10﹣ 4, the 5th coefficient a5Value be 5.8279 × 10﹣ 6.Then Δ T=
15.4622+0.00572H-0.1769q- (0.01072 × 10﹣ 4)H2+5.8279×10﹣ 6)*q2。
Different heat sources intensity q, bus vertical height H bus temperature difference controlling value reference value are shown in Table 1 under the conditions of gravity-flow ventilation
It is shown：
The gravity-flow ventilation condition Down Highway temperature difference controlling value table of table 1
The content not being described in detail in specification belongs to prior art known to professional and technical personnel in the field.
Claims (5)
1. the thermal balance temperature difference control method based on the natural hot pressing of long vertical enclosed busbar, it is characterised in that：Long vertical closing is female
Temperature difference T meets relational expression with heat source strength q, bus vertical height H in line：
Δ T=a1+a2*H+a3*q+a4*H2+a5*q2
Wherein：a1For the first coefficient, a2For the second coefficient, a3For the 3rd coefficient, a4For the 4th coefficient, a5It is described for the 5th coefficient
Temperature difference T is the temperature difference of the bus on vertical section length direction in long vertical enclosed busbar, unit for DEG C, the heat source strength q
For the heat source strength in IPB, unit is W/m3, the unit of the bus vertical height H is m；
The calculation formula of the heat source strength q is：
Q=QS/[SQ- π * (DL 2/4)*n]
Wherein, QSFor shaft height direction caloric value, SQEffectively radiated sectional area, D for vertical shaftLFor bus shell external diameter, n is perpendicular
Bus group number in well.
2. the thermal balance temperature difference control method according to claim 1 based on the natural hot pressing of long vertical enclosed busbar, it is special
Levy and be：When the span of the heat source strength q is 150W/m3The W/m of≤q ＜ 2603, bus vertical height H span
During for 60m≤H ＜ 100m, the first coefficient a1Value be ﹣ 8.3399, the second coefficient a2Value be 0.18336, it is described
3rd coefficient a3Value be 0.4559, the 4th coefficient a4Value be 6.7559 × 10﹣ 4, the 5th coefficient a5Value be
7.7898×10﹣ 6。
3. the thermal balance temperature difference control method according to claim 1 based on the natural hot pressing of long vertical enclosed busbar, it is special
Levy and be：When the span of the heat source strength q is 260W/m3The W/m of≤q ＜ 4003, bus vertical height H span
During for 60m≤H ＜ 100m, the first coefficient a1Value be 14.5349, the second coefficient a2Value be 0.01656, it is described
3rd coefficient a3Value be 0.1521, the 4th coefficient a4Value be 2.9100 × 10﹣ 4, the 5th coefficient a5Value be ﹣
6.3164×10﹣ 6。
4. the thermal balance temperature difference control method according to claim 1 based on the natural hot pressing of long vertical enclosed busbar, it is special
Levy and be：When the span of the heat source strength q is 75W/m3The W/m of≤q ＜ 2003, bus vertical height H span
During for 100m≤H ＜ 180m, the first coefficient a1Value be ﹣ 2.9452, the second coefficient a2Value be 0.08397, it is described
3rd coefficient a3Value be 0.04767, the 4th coefficient a4Value be ﹣ 2.2651 × 10﹣ 4, the 5th coefficient a5Value be
2.0157×10﹣ 6。
5. the thermal balance temperature difference control method according to claim 1 based on the natural hot pressing of long vertical enclosed busbar, it is special
Levy and be：When the span of the heat source strength q is 200W/m3The W/m of≤q ＜ 3003, bus vertical height H span
During for 100m≤H ＜ 180m, the first coefficient a1Value be 15.4622, the second coefficient a2Value be 0.00572, it is described
3rd coefficient a3Value be ﹣ 0.1769, the 4th coefficient a4Value be ﹣ 0.01072 × 10﹣ 4, the 5th coefficient a5Value be
5.8279×10﹣ 6。
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| CN202178540U (en) * | 2011-03-14 | 2012-03-28 | 刘忠 | phase enclosing bus |
| CN103050914A (en) * | 2012-12-11 | 2013-04-17 | 河南省电力公司商丘供电公司 | Closed insulating bus |
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