CN105006791A - Thermal equilibrium temperature-difference control method based on natural hot-pressing of long vertical enclosed busbar - Google Patents
Thermal equilibrium temperature-difference control method based on natural hot-pressing of long vertical enclosed busbar Download PDFInfo
- Publication number
- CN105006791A CN105006791A CN201510439732.5A CN201510439732A CN105006791A CN 105006791 A CN105006791 A CN 105006791A CN 201510439732 A CN201510439732 A CN 201510439732A CN 105006791 A CN105006791 A CN 105006791A
- Authority
- CN
- China
- Prior art keywords
- coefficient
- value
- enclosed busbar
- bus
- long vertical
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Abstract
The invention discloses a thermal equilibrium temperature-difference control method based on the natural hot-pressing of a long vertical enclosed busbar. The interior temperature difference delta T of the long vertical enclosed busbar, the intensity Q of a heat source, and the vertical height H of the busbar satisfy the following relationship of delta T=a1+a2*H+a3*q+a4*H2+a5*q2, wherein a1 represents a first coefficient, a2 represents a second coefficient, a3 represents a third coefficient, a4 represents a fourth number and a5 represents a fifth coefficient. According to the invention, the numerical calculation and the field measurement are conducted on the thermal equilibrium state and the temperature distribution state of the long vertical enclosed busbar (namely an isolated phase bus, IPB) in the natural ventilation state are conducted for comparative study. In this way, the temperature distribution rule and the temperature distribution characteristics of the long vertical enclosed busbar in a strong heat source restricted space in the natural ventilation state are obtained. Therefore, the temperature-difference control of the IPB during engineering is ensured, and the thermal equilibrium mode can be correctly selected. The temperature distribution for the safe and reliable operation of the IPB is ensured, and an advanced and reliable guidance is provided for the selection of the heat dissipation mode.
Description
Technical field
The invention belongs to Hydraulic and Hydro-Power Engineering field of electromechanical technology, refer to a kind of heat balance temperature difference control method based on the hot pressing of long vertical enclosed busbar nature particularly.
Background technology
The long vertical enclosed busbar Temperature Distribution of Large Underground Power Station and heat dissipation problem are the guarantees of bus security of operation.Along with the fast development of domestic water electrical engineering, the application of long vertical isolated-phase enclosed bus (IPB) in underground power station is also more and more extensive, but the IPB to different capabilities and vertical height, there is no relevant design, manufacturer's standard or regulation.The type of cooling of each underground power station relies on natural draft cooling.Such as Pengshui Hydropower Station, water Bu Ya hydroelectric station, its enclosed busbar rated current is respectively 14kA, 16kA, the vertical IPB of the above-mentioned water power head of a station is a machine one hole lead-out mode, adopts natural draft respectively, the mode of forced ventilation meets the requirement of IPB heat balance.Along with the increase of the specified heat flow of the underground power station vertical enclosed busbar of length and the complicated of arrangement, the heat balance only leaning on natural draft whether still to meet IPB requires that needs carry out the rear judgement of concrete calculating.
According to national standard, isolated-phase enclosed bus should meet temperature increase requirement when rated condition is run, and when adopting aluminium, its conductor allows maximum temperaturerise to be 50K, and shell allows maximum temperaturerise to be 30K, and ambient temperature is 40K.Need it is emphasized that no matter be 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 greater than to a certain degree bus along its length, bus structure design will be affected.In order to reach bus safe operation requirement, the shell at each position of bus, conductor temperature lower than national regulations while also answer relative equilibrium, especially long vertical isolated-phase enclosed bus, all the more so.But at present about under natural hot pressing condition, the temperature controlled research of corresponding different heat sources intensity parameters Down Highway on vertical section length direction belongs to blank.
Summary of the invention
The regulation of bus temperature difference along its length is not provided in order to solve current national standard, and shell at each position of bus, conductor temperature lower than national regulations while also answer the problem of relative equilibrium, the invention provides a kind of heat balance temperature difference control method based on the hot pressing of long vertical enclosed busbar nature.
For achieving the above object, the heat balance temperature difference control method based on the hot pressing of long vertical enclosed busbar nature designed by the present invention, its special character is, in long vertical enclosed busbar, temperature difference T and heat source strength q, bus vertical height H meet relational expression:
ΔT＝a
1+a
2*H+a
3*q+a
4*H
2+a
5*q
2
Wherein: a
1be the first coefficient, a
2be the second coefficient, a
3be the 3rd coefficient, a
4for Quaternary system number, a
5it is the 5th coefficient.
Preferably, the computing formula of described heat source strength q is:
q＝Q
S/[S
Q－π*(D
L 2/4)*n]
Wherein, Q
sfor shaft height direction caloric value, S
qfor vertical shaft efficiently radiates heat sectional area, D
lfor bus shell external diameter, n is bus group number in vertical shaft.
Preferably, when the span of described heat source strength q is 150W/m
3≤ q < 260W/m
3, bus vertical height H span when being 60m≤H < 100m, described first coefficient a
1value be ﹣ 8.3399, described second coefficient a
2value be 0.18336, described 3rd coefficient a
3value be 0.4559, described Quaternary system number a
4value be 6.7559 × 10
﹣ 4, described 5th coefficient a
5value be 7.7898 × 10
﹣ 6.
Preferably, when the span of described heat source strength q is 260W/m
3≤ q < 400W/m
3, bus vertical height H span when being 60m≤H < 100m, described first coefficient a
1value be 14.5349, described second coefficient a
2value be 0.01656, described 3rd coefficient a
3value be 0.1521, described Quaternary system number a
4value be 2.9100 × 10
﹣ 4, described 5th coefficient a
5value be ﹣ 6.3164 × 10
﹣ 6.
Preferably, when the span of described heat source strength q is 75W/m
3≤ q < 200W/m
3, bus vertical height H span when being 100m≤H < 180m, described first coefficient a
1value be ﹣ 2.9452, described second coefficient a
2value be 0.08397, described 3rd coefficient a
3value be 0.04767, described Quaternary system number a
4value be ﹣ 2.2651 × 10
﹣ 4, described 5th coefficient a
5value be 2.0157 × 10
﹣ 6.
Preferably, when the span of described heat source strength q is 200W/m
3≤ q < 300W/m
3, bus vertical height H span when being 100m≤H < 180m, described first coefficient a
1value be 15.4622, described second coefficient a
2value be 0.00572, described 3rd coefficient a
3value be ﹣ 0.1769, described Quaternary system number a
4value be ﹣ 0.01072 × 10
﹣ 4, described 5th coefficient a
5value be 5.8279 × 10
﹣ 6.
The present invention carries out numerical computations and field measurement comparative study to heat balance and Temperature Distribution under the long vertical enclosed busbar natural draft condition of Large Underground Power Station heat-flash stream, temperature distributing rule and feature under the natural draft condition of acquisition in the restricted clearance of heat-flash source, and analyze vertical shaft size, the factors such as heat source strength, bus height on the impact of IPB Temperature Distribution, and find out the heat radiation strategy its Temperature Distribution being played to the sex parameter of crucial control and reply different situations.The temperature difference controlling value of superelevation bus on vertical section length direction under corresponding different heat sources intensity parameters is proposed.
The present invention is different according to the bus distribution in isolated-phase enclosed bus vertical shaft, the local temperature of the diverse location bus in restricted clearance and be different Variation Features along the temperature distributing rule in vertical height direction, by complete three-dimensional numerical simulation, under providing the condition of different operational factor, analyze the long vertical isolated-phase enclosed bus temperature field of big current, diverse location single bus vertical temperature distribution rule, import and export difference variation rule, and then explore and the hot-fluid in the long vertical isolated-phase enclosed bus vertical shaft of big current under understanding mixed ventilation pattern and Temperature Distribution performance, and different operational factor flows to it and the affecting laws of heat exchange.
The present invention is directed to the long heat-flash stream of vertical enclosed busbar of large-scale power station and the complexity of layout, adopt Fluid Mechanics Computation (computational fluid dynamics, CFD), according to the heat source strength of different IP B, the factor labors such as different shaft height calculate, finding systematic IPB heat balance rule, for ensureing in engineering that the IPB temperature difference controls, selecting properly heat balance mode, ensureing that the Temperature Distribution of IPB safe and reliable operation and the reliable radiating mode of advanced person provide guidance.
Embodiment
Below in conjunction with specific embodiment, the present invention is described in further detail.
1) heat balance in IPB vertical shaft
The heat radiation of IPB conductor is undertaken by the thermal radiation between conductor and shell, shell inner air convection, and shell is then mainly by the heat loss through convection of thermal radiation, shell outer air.Thermal radiation determines do not have difference in IPB vertical direction by radiation coefficient (for constant), therefore affects the convection current of the IPB inside and outside air of mainly IPB of Temperature Distribution in vertical direction.
P
M＝Q
MF+Q
MD
P
M+P
K＝Q
KF+Q
KD
P
mfor the power loss of conductor, W/ (m phase);
Q
mFfor IPB is to the heat loss through radiation of shell;
Q
mDfor the convective heat transfer between conductor and shell;
P
kfor the power loss of conductor, shell, W/ (m phase);
Q
kFfor the heat loss through radiation of shell;
Q
kDfor the heat loss through convection of shell and shell outer air.
The heating of IPB itself is because the loss of conductor and shell causes, and conductor and shell directly exist convection current, its mechanism of radiant heat transfer is comparatively complicated, therefore needs model to carry out following simplification:
(1) owing to considering hot property, the viscosity of air, therefore consider that 100% heat is passed to shell by conductor, and ignore the loss of conductor itself and gas at the length direction of conductor.
(2) at IPB vertical direction each section of conductor, housing, hole wall only in this section of object generation heat transfer, without heat transfer between each section, ignore the thermal conduction resistance of IPB conductor, case material.
2) physical model of IPB vertical shaft
IPB and vertical shaft thereof can be reduced to the enclosure space that heat-generating cylindrical body is placed in vertical shaft formation, form the restricted clearance heat exchange models that has endogenous pyrogen.
3) Mathematical Modeling of IPB vertical shaft
The heat dissipation problem of underground power station IPB is a complicated heat transfer process, if adopt conventional method to solve, not only formula is complicated, and needs to make a large amount of simplification and hypothesis to Mathematical Modeling, and result of calculation must be caused to depart from reality.Along with the development of computer technology, carry out for adopting numerical computation method under complex situations solving and can increasing substantially computational accuracy.
Concrete steps comprise:
1) according to mass conservation law, the law of conservation of momentum and law of conservation of energy, governing equation is set up to the thermal balance state of each point in shaft space:
Continuity equation:
The equation of momentum:
Energy equation:
In formula: u
i: air average speed components in the vertical direction; u
j: air average speed components in the horizontal direction; x
i: vertical height: t: time; ρ: atmospheric density; P: pressure; V: the laminar flow coefficient of viscosity; v
t: turbulence factor; g
i: vertical direction acceleration of gravity; β: air thermal expansion coefficient; T: hoistway entrance place and exit mean temperature; T
∞: ambient temperature; T: actual temperature; Γ: generalized diffusion process coefficient; I: radiation intensity;
2) value of pressure p is supposed, solve the air average speed components u in the vertical direction in the equation of momentum
i;
3) value of the pressure p of hypothesis is revised, make the air average speed components u in the vertical direction drawn
imeet continuity equation;
4) by revised pressure p and air average speed components u in the vertical direction
ivalue substitute into energy equation, solve actual temperature T;
5) step 1 is repeated) ~ 4) until calculate the actual temperature T of each point in vertical shaft.
Wherein, step 1) energy equation in, generalized diffusion process coefficient Γ and Prandtl number P
rwith σ
tthere is following relational expression:
Γ＝v/Pr+v
t/σ
T
In formula: v: the laminar flow coefficient of viscosity; v
t: turbulence factor; σ
t: empirical, get 0.9 ~ 1; P
r: Prandtl number.
Prandtl number Pr can according to formula Pr=c
pv/ λ obtains, in formula: c
pfor specific heat at constant pressure, λ is conductive coefficient.
The essence of underground power station IPB heat dissipation problem is actual is have with under the non-isothermal turbulent-flow heat-exchanging of endogenous pyrogen, externally thermal radiation comprehensive function, and the temperature field of the air in vertical shaft restricted clearance, velocity field reach the process of corresponding balance.Air-flow in this restricted clearance is by adding the thermal current effect from bottom to top that thermogenetic buoyancy lift is power through IPB shell.Numerical simulator adopts the K – ε two-equation model considering buoyancy lift, and wall adopts Standard law of wall method.Application SIMPLE Algorithm for Solving discrete, discrete equation adopts QUICK form to prevent pseudo-diffusion, have employed multi-surface radiation (S2S) model and carries out radiation calculating.
The computation model of radiation intensity I is:
In formula:
position vector; S: vertical length;
direction vector; A: absorption coefficient; σ
s: scattering coefficient; N: refraction coefficient; σ: Si Difen ﹣ Boltzmann constant; T: actual temperature; Φ: phase function; Ω ': space multistory angle.The parameters such as space multistory angle Ω ', absorption coefficient a have model structure and material character to determine.
4) thermal equilibrium analysis of IPB vertical shaft
Under natural draft condition, draw by carrying out computational analysis to the IPB Temperature Distribution of multiple Large Underground Power Station, temperature in some underground power stations IPB surface temperature and vertical shaft raises gradually, and there is maximum at the first half, and decrease on the contrary at outlet block temperature and make temperature present the high distribution curve in low centre, two ends, its temperature difference is within control range, and its rule does not present significantly " chimney " effect; But the underground power station IPB surface temperature also had progressively improves along with highly increasing, IPB vertical shaft does not have temperature along with highly increase progressively raises yet, and has significantly " chimney " effect.
When IPB vertical shaft endogenous pyrogen intensity q is lower, the natural draft exchange capability of heat that the hot pressing that its IPB produces as endogenous pyrogen is formed can meet heat balance requirement, cause and be not enough to overcome the outdoor relative low temperature air impact in IPB outlet position at the thermal buoyancy effect of outlet section, strong convection heat transfer is produced in exit, greatly reduce outlet block temperature and affect IPB top near the surface temperature exported and hoistway temperature simultaneously, making IPB " chimney " effect not obvious.Along with heat source strength q increases, the natural draft produced in limited space is not enough to take away the heat that IPB distributes, and along with height increase air themperature also raise gradually, this weakens the rising gradually that heat-exchange capacity causes IPB surface temperature further, and the altitude temperature difference effect therefore imported and exported as the increase IPB of the heat source strength q in IPB progressively increases IPB " chimney " effect is progressively increased.
The computing formula of heat source strength q is:
q＝Q
S/[S
Q－π*(D
L 2/4)*n]
Wherein, Q
sfor shaft height direction caloric value, S
qfor vertical shaft efficiently radiates heat sectional area, D
lfor bus shell external diameter, n is bus group number in vertical shaft.
By a large amount of simulation work and engineering measurement, to grasp in the long vertical enclosed busbar restricted clearance of Large Copacity restricting relation between heat balance mechanism and each influencing factor thereof, obtain the Multi-parameter data piecewise fitting correlation of heat source strength q in temperature difference △ T and IPB under natural draft and bus vertical height H.
ΔT＝a
1+a
2*H+a
3*q+a
4*H
2+a
5*q
2
Wherein: a
1be the first coefficient, a
2be the second coefficient, a
3be the 3rd coefficient, a
4for Quaternary system number, a
5it is the 5th coefficient.
When the span of heat source strength q is 150W/m
3≤ q < 260W/m
3, bus vertical height H span when being 60m≤H < 100m, the first coefficient a
1value be ﹣ 8.3399, the second coefficient a
2value be the 0.18336, three coefficient a
3value be 0.4559, Quaternary system number a
4value be 6.7559 × 10
﹣ 4, the 5th coefficient a
5value be 7.7898 × 10
﹣ 6.Then Δ T=﹣ 8.3399+0.18336H+0.4559q+ (6.7559 × 10
﹣ 4) H
2+ (7.7898 × 10
﹣ 6) q
2.
When the span of heat source strength q is 260W/m
3≤ q < 400W/m
3, bus vertical height H span when being 60m≤H < 100m, the first coefficient a
1value be the 14.5349, second coefficient a
2value be the 0.01656, three coefficient a
3value be 0.1521, Quaternary system number a
4value be 2.9100 × 10
﹣ 4, the 5th coefficient a
5value be ﹣ 6.3164 × 10
﹣ 6.Then Δ T=14.5349+0.01656H+0.1521q+ (2.9100 × 10
﹣ 4) H
2-(6.3164 × 10
﹣ 6) q
2.
When the span of heat source strength q is 75W/m
3≤ q < 200W/m
3, bus vertical height H span when being 100m≤H < 180m, the first coefficient a
1value be ﹣ 2.9452, the second coefficient a
2value be the 0.08397, three coefficient a
3value be 0.04767, Quaternary system number a
4value be ﹣ 2.2651 × 10
﹣ 4, the 5th coefficient a
5value be 2.0157 × 10
﹣ 6.Then Δ T=﹣ 2.9452+0.08397H+0.04767q-(2.2651 × 10
﹣ 4) H
2+ (2.0157 × 10
﹣ 6) * q
2.
When the span of heat source strength q is 200W/m
3≤ q < 300W/m
3, bus vertical height H span when being 100m≤H < 180m, the first coefficient a
1value be the 15.4622, second coefficient a
2value be the 0.00572, three coefficient a
3value be ﹣ 0.1769, Quaternary system number a
4value be ﹣ 0.01072 × 10
﹣ 4, the 5th coefficient a
5value be 5.8279 × 10
﹣ 6.Then Δ T=15.4622+0.00572H-0.1769q-(0.01072 × 10
﹣ 4) H
2+ 5.8279 × 10
﹣ 6) * q
2.
Under natural draft condition, the bus temperature difference controlling value reference value of different heat sources intensity q, bus vertical height H is shown in Table 1:
Table 1 natural draft condition Down Highway temperature difference controlling value table
The content be not described in detail in specification belongs to the known prior art of professional and technical personnel in the field.
Claims (6)
1. based on the heat balance temperature difference control method of long vertical enclosed busbar nature hot pressing, it is characterized in that: in long vertical enclosed busbar, temperature difference T and heat source strength q, bus vertical height H meet relational expression:
ΔT＝a
1+a
2*H+a
3*q+a
4*H
2+a
5*q
2
Wherein: a
1be the first coefficient, a
2be the second coefficient, a
3be the 3rd coefficient, a
4for Quaternary system number, a
5it is the 5th coefficient.
2. the heat balance temperature difference control method based on the hot pressing of long vertical enclosed busbar nature according to claim 1, is characterized in that: the computing formula of described heat source strength q is:
q＝Q
S/[S
Q－π*(D
L 2/4)*n]
Wherein, Q
sfor shaft height direction caloric value, S
qfor vertical shaft efficiently radiates heat sectional area, D
lfor bus shell external diameter, n is bus group number in vertical shaft.
3. the heat balance temperature difference control method based on the hot pressing of long vertical enclosed busbar nature according to claim 1 and 2, is characterized in that: when the span of described heat source strength q is 150W/m
3≤ q < 260W/m
3, bus vertical height H span when being 60m≤H < 100m, described first coefficient a
1value be ﹣ 8.3399, described second coefficient a
2value be 0.18336, described 3rd coefficient a
3value be 0.4559, described Quaternary system number a
4value be 6.7559 × 10
﹣ 4, described 5th coefficient a
5value be 7.7898 × 10
﹣ 6.
4. the heat balance temperature difference control method based on the hot pressing of long vertical enclosed busbar nature according to claim 1 and 2, is characterized in that: when the span of described heat source strength q is 260W/m
3≤ q < 400W/m
3, bus vertical height H span when being 60m≤H < 100m, described first coefficient a
1value be 14.5349, described second coefficient a
2value be 0.01656, described 3rd coefficient a
3value be 0.1521, described Quaternary system number a
4value be 2.9100 × 10
﹣ 4, described 5th coefficient a
5value be ﹣ 6.3164 × 10
﹣ 6.
5. the heat balance temperature difference control method based on the hot pressing of long vertical enclosed busbar nature according to claim 1 and 2, is characterized in that: when the span of described heat source strength q is 75W/m
3≤ q < 200W/m
3, bus vertical height H span when being 100m≤H < 180m, described first coefficient a
1value be ﹣ 2.9452, described second coefficient a
2value be 0.08397, described 3rd coefficient a
3value be 0.04767, described Quaternary system number a
4value be ﹣ 2.2651 × 10
﹣ 4, described 5th coefficient a
5value be 2.0157 × 10
﹣ 6.
6. the heat balance temperature difference control method based on the hot pressing of long vertical enclosed busbar nature according to claims 1 or 2, is characterized in that: when the span of described heat source strength q is 200W/m
3≤ q < 300W/m
3, bus vertical height H span when being 100m≤H < 180m, described first coefficient a
1value be 15.4622, described second coefficient a
2value be 0.00572, described 3rd coefficient a
3value be ﹣ 0.1769, described Quaternary system number a
4value be ﹣ 0.01072 × 10
﹣ 4, described 5th coefficient a
5value be 5.8279 × 10
﹣ 6.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510439732.5A CN105006791B (en) | 2015-07-23 | 2015-07-23 | Thermal balance temperature difference control method based on the natural hot pressing of long vertical enclosed busbar |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510439732.5A CN105006791B (en) | 2015-07-23 | 2015-07-23 | Thermal balance temperature difference control method based on the natural hot pressing of long vertical enclosed busbar |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105006791A true CN105006791A (en) | 2015-10-28 |
| CN105006791B CN105006791B (en) | 2017-07-21 |
Family
ID=54379358
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510439732.5A Active CN105006791B (en) | 2015-07-23 | 2015-07-23 | Thermal balance temperature difference control method based on the natural hot pressing of long vertical enclosed busbar |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN105006791B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109818260A (en) * | 2019-03-28 | 2019-05-28 | 星凯电气有限公司 | A kind of GGD bus of low-voltage switch cabinet contact temperature control device |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5251591A (en) * | 1975-10-24 | 1977-04-25 | Hitachi Ltd | Cooling equipment for phase separated enclosed bus bars |
| 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 |
-
2015
- 2015-07-23 CN CN201510439732.5A patent/CN105006791B/en active Active
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5251591A (en) * | 1975-10-24 | 1977-04-25 | Hitachi Ltd | Cooling equipment for phase separated enclosed bus bars |
| 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 |
Non-Patent Citations (1)
| Title |
|---|
| 梁波等: "Seitevare水电站长垂直封闭母线设计考察与研究", 《人民长江》 * |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109818260A (en) * | 2019-03-28 | 2019-05-28 | 星凯电气有限公司 | A kind of GGD bus of low-voltage switch cabinet contact temperature control device |
Also Published As
| Publication number | Publication date |
|---|---|
| CN105006791B (en) | 2017-07-21 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| Kent | Numerical analysis of laminar natural convection in isosceles triangular enclosures for cold base and hot inclined walls | |
| Al-Kayiem et al. | Mathematical analysis of the influence of the chimney height and collector area on the performance of a roof top solar chimney | |
| Vaz et al. | Experimental and numerical analysis of an earth–air heat exchanger | |
| Tingzhen et al. | Numerical simulation of the solar chimney power plant systems coupled with turbine | |
| Gan | Simulation of buoyancy-driven natural ventilation of buildings—Impact of computational domain | |
| Zogou et al. | Flow and heat transfer inside a PV/T collector for building application | |
| Marc et al. | Modeling and experimental validation of the solar loop for absorption solar cooling system using double-glazed collectors | |
| Farea et al. | CFD modeling for natural ventilation in a lightwell connected to outdoor through horizontal voids | |
| Li et al. | A new solution for thermal interference of vertical U-tube ground heat exchanger for cold area in China | |
| Mei et al. | Thermal buoyancy driven flows inside the industrial buildings primarily ventilated by the mechanical fans: Local facilitation and infiltration | |
| Lu et al. | Experimental investigation into the positive effects of a tri-blade-like windbreak wall on small size natural draft dry cooling towers | |
| Acikgoz | A novel evaluation regarding the influence of surface emissivity on radiative and total heat transfer coefficients in radiant heating systems by means of theoretical and numerical methods | |
| Acikgoz et al. | Experimental and numerical investigation of the correlation between radiative and convective heat-transfer coefficients at the cooled wall of a real-sized room | |
| CN105087882A (en) | Partitioning method for heat treatment stages of vertical quenching furnace | |
| Merabtine et al. | Semi-analytical model for thermal response of anhydrite radiant slab | |
| Haghighi et al. | A study of vaulted roof assisted evaporative cooling channel for natural cooling of 1-floor buildings | |
| Mahdi et al. | Numerical investigations of turbulent natural convection heat transfer within a wind turbine nacelle operating in hot climate | |
| Piña-Ortiz et al. | Thermal analysis of a finned receiver for a central tower solar system | |
| Alshammari et al. | Thermal energy simulation of the building with heating tube embedded in the wall in the presence of different PCM materials | |
| CN105138727A (en) | Modeling method based on isolated phase bus natural hot pressing for underground power plant | |
| CN105006791A (en) | Thermal equilibrium temperature-difference control method based on natural hot-pressing of long vertical enclosed busbar | |
| CN106529010A (en) | Method for designing housing of anti-condensation ring main unit by using finite element model | |
| Chen et al. | Experimental investigation on the thermal performance of an enhanced convection-radiant heating wall panel with orifices | |
| CN105116727B (en) | Optimal control method based on long vertical enclosed busbar force ventilation amount | |
| Bayareh | Numerical simulation of a solar chimney power plant in the southern region of Iran |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant |