阅读说明：本技术 太阳能吸热器热效率的测试方法 (Method for testing thermal efficiency of solar heat absorber ) 是由 肖刚 聂婧 倪明江 岑可法 于 2020-06-15 设计创作，主要内容包括：本发明涉及太阳能热发电技术领域,公开了一种太阳能吸热器热效率的测试方法,包括如下步骤：在第一时间段内,稳定运行太阳能吸热器；在以规定比例N升高或者降低入射功率后的第二时间段内,稳定运行太阳能吸热器,其中,在第一时间段内和第二时间段内,太阳能吸热器的进出口传热工质状态一致；根据太阳能吸热器在第一时间段内和在第二时间段内的输出功率P-(outpA)、P-(outpB)以及N,确定热效率。本发明提供的太阳能吸热器热效率的测试方法,只需测量测试期间内吸热器进出口温度、压力和流量,即可测试太阳能吸热器的热效率,对电站运行的干扰小、测试成本低,能够实现对太阳能吸热器性能的验收工作,并可为以后的优化运行提供指导。(The invention relates to the technical field of solar thermal power generation, and discloses a method for testing the thermal efficiency of a solar heat absorber, which comprises the following steps: in a first time period, stably operating the solar heat absorber; in a second time period after the incident power is increased or reduced by a specified proportion N, stably operating the solar heat absorber, wherein in the first time period and the second time period, the states of heat transfer working media of an inlet and an outlet of the solar heat absorber are consistent; according to the output power P of the solar heat absorber in the first time period and the second time period outpA 、P outpB And N, determining the thermal efficiency. The method for testing the thermal efficiency of the solar heat absorber provided by the invention can test the thermal efficiency of the solar heat absorber by only measuring the inlet and outlet temperature, pressure and flow of the heat absorber during the test period, has small interference on the operation of a power station and low test cost, can realize the acceptance work of the performance of the solar heat absorber and can provide guidance for the subsequent optimized operation.)

1. A method for testing the thermal efficiency of a solar heat absorber is characterized by comprising the following steps:

in a first time period, stably operating the solar heat absorber;

in a second time period after the incident power is increased or reduced by a specified proportion N, stably operating the solar heat absorber, wherein in the first time period and the second time period, the states of heat transfer working media of an inlet and an outlet of the solar heat absorber are consistent;

according to the output power P of the solar heat absorber in the first time period and the second time period_outpA、P_outpBAnd specifying the ratio N to determine the thermal efficiency.

2. The method for testing the thermal efficiency of the solar thermal absorber according to claim 1, wherein the output power P is_outpThe calculation formula of (2) is as follows:

wherein the content of the first and second substances,the unit is t/h, and is the mass flow of the heat absorber; h is_inExpressing the enthalpy value of the heat transfer working medium at the inlet of the heat absorber, wherein the unit is kJ/kg; h is_outExpressing the enthalpy value of the heat transfer working medium at the outlet of the heat absorber, wherein the unit is kJ/kg;

thermal efficiency eta of solar heat absorber in first time period and second time period_A、η_BThe calculation formula of (2) is as follows:

wherein alpha is_rcvIs the absorption rate of the heat absorber; p_outpAAnd P_outpBThe output power of the heat sink in the first time period and the second time period, respectively, is given in units of W.

And according to the results of multiple tests, obtaining the thermal efficiency of the heat absorber under the rated working condition in an interpolation mode.

3. The method for testing the thermal efficiency of the solar heat absorber according to claim 1 or 2, wherein the value of N is changed by changing the number of solar collectors in the solar collector field irradiating the solar heat absorber.

4. The method for testing the thermal efficiency of the solar thermal absorber according to claim 3, wherein the first time period and the second time period are symmetrical time periods of the same day with respect to the local true solar time at noon of 12: 00.

5. The method for testing the thermal efficiency of the solar thermal absorber according to claim 3, further comprising the step of

A step of grouping solar concentrators in a solar concentrator field, wherein,

different sets of heliostat layouts are staggered with respect to the solar thermal absorber.

6. The method for testing the thermal efficiency of the solar thermal absorber according to claim 1 or 2, further comprising the step of

And determining the prescribed ratio N according to the ratio between the DNI value in the first time period and the DNI value in the second time period.

7. The method for testing the thermal efficiency of the solar heat absorber is characterized in that the incident power is increased or decreased by changing the cleaning rate of the solar condenser, and the specified ratio N is determined according to the ratio of the cleaning rate to the cleaning rate.

8. The method for testing the thermal efficiency of the solar thermal absorber according to claim 6 or 8, wherein the first time period and the second time period are corresponding time periods in two days in which the attitude angle of the solar condenser does not change more than 3%.

9. The method for testing the thermal efficiency of the solar heat absorber according to claim 1, wherein the consistency of the states of the heat transfer working media at the inlet and the outlet of the heat absorber is that the temperature difference of the heat transfer working media at the inlet and the outlet of the heat absorber is within +/-5 ℃ in the first time period and the second time period corresponding to the heat absorber with the heat transfer working media being liquid and particles;

corresponding to the heat absorber with the gaseous heat transfer working medium, the consistent states of the heat transfer working medium at the inlet and the outlet mean that the temperature difference of the heat transfer working medium at the inlet and the outlet of the heat absorber is within +/-5 ℃ and the pressure difference of the heat transfer working medium at the outlet of the heat absorber is within +/-5 kPa in the first time period and the second time period.

10. The method for testing the thermal efficiency of the solar heat absorber according to claim 1, wherein the stable operation of the solar heat absorber corresponds to the heat absorber with the heat transfer working medium in liquid state and particles, and means that the temperature fluctuation range of the heat transfer working medium at the inlet and the outlet of the heat absorber is within +/-2 ℃ within any 2 minutes in the first time period and the second time period;

the stable operation of the solar heat absorber corresponding to the heat absorber with the gaseous heat transfer working medium means that the temperature fluctuation range of the heat transfer working medium at the inlet and the outlet of the heat absorber is within +/-2 ℃ and the pressure fluctuation range of the heat transfer working medium at the outlet of the heat absorber is within +/-1 kPa within any 2 minutes in the first time period and the second time period.

Technical Field

The invention relates to the technical field of solar thermal power generation, in particular to a method for testing the thermal efficiency of a solar heat absorber.

Background

The utilization form of the solar thermal power generation technology mainly refers to a light-gathering solar thermal power generation system. The system focuses solar radiation by using the light-gathering and heat-collecting device to heat the heat transfer working medium, has the characteristics of large installed capacity, high conversion efficiency, high-temperature energy storage and the like, can generate high-temperature steam, and generates electricity which is consistent with the parameters of a conventional thermal power plant, so that matched equipment is easy to obtain.

The light-gathering solar thermal power generation system mainly comprises a light-gathering system, a heat collection system, a heat storage system, a power generation system and the like. According to different light-gathering forms, the light-gathering solar thermal power generation system is mainly divided into a groove type solar thermal power generation system, a tower type solar thermal power generation system, a disc type solar thermal power generation system and a linear Fresnel type solar thermal power generation system. The trough solar thermal power generation system adopts a parabolic trough reflector surface, and the radiation energy of the sun is focused on a heat collecting pipe through the focusing of the reflector. The heat collecting system of the tower system mainly comprises a plurality of collecting mirrors and a heat absorber positioned at the top of the heat absorbing tower; each condensing lens adopts a double-shaft tracking structure, tracks the position of the sun in real time and reflects solar radiation to the heat absorber. The dish system adopts a dish-shaped paraboloidal mirror to collect solar radiation energy, the dish-shaped paraboloidal mirror is a more compact independent power generation unit, a receiver is arranged at the focus of a rotary paraboloidal condenser, and incident sunlight is absorbed by a heat absorber after being reflected and focused by the condenser. The linear Fresnel emission type solar light-gathering and heat-collecting system mainly comprises a primary reflector field, a secondary reflector, a heat absorber, a tracking device and the like, wherein the primary reflector field comprises a plane mirror or a slightly bent strip reflector, and the primary reflector provides single-axis tracking and reflects and concentrates incident solar radiation light onto the heat absorber.

The heat absorber is a core device of a solar thermal power generation system and is a key for realizing the conversion from solar energy to heat energy of a heat transfer working medium. The heat absorber can be divided into a tubular heat absorber, a positive displacement heat absorber and a particle heat absorber according to the structure of the heat absorber. For the tubular heat absorber, a heat transfer working medium flows in a metal or ceramic tube, the outer wall of the tube is coated with a high-temperature-resistant selective absorption coating, the temperature of the outer wall surface of the tube is raised by focusing incident solar energy in a radiation mode, and then the heat is transferred to the heat transfer working medium in the tube through the tube wall in a heat conduction and convection mode. The positive-displacement heat absorber generally uses a densely woven mesh-shaped or honeycomb-shaped porous material as a heat absorber, the porous heat absorber absorbs solar energy reflected and focused, and when air flows through the heat absorber, the air and the heat absorber generate heat convection and heat exchange and then are heated to high temperature. The particle heat absorber generally absorbs heat based on a particle layer, the particle layer is heated by focused sunlight and continuously heated, and solar energy is continuously collected along with the flow of the particle layer.

The thermal efficiency of the heat sink is the ratio of the output power of the heat sink to the incident power of the heat sink. In engineering practice, the total incident power cannot be accurately measured due to different sizes and shapes of the heat absorbers, uneven light condensation distribution and real-time change; if the incident power of the heat absorber is estimated by adopting a calculation simulation result of the solar energy condensation system, the precision is difficult to guarantee and measure, and the thermal efficiency cannot be calculated.

Disclosure of Invention

The invention aims to provide a method for testing the thermal efficiency of a solar heat absorber, which adjusts the incident power of the heat absorber by selecting different working conditions, further changes the output power of the heat absorber, offsets the influence of the incident power of the heat absorber on the result in the thermal efficiency calculation by reasonably setting preconditions, and can calculate the thermal efficiency of the heat absorber by measuring the inlet and outlet temperature, pressure and flow of the heat absorber in the testing period. The testing method has small influence on the normal operation of the optothermal power station and is easy for field operation.

Specifically, the invention provides a method for testing the thermal efficiency of a solar heat absorber, which comprises the following steps:

in a first time period, stably operating the solar heat absorber;

and in a second time period after the incident power is increased or decreased by the specified ratio N, stably operating the solar heat absorber, wherein,

in the first time period and the second time period, the states of heat transfer working media of an inlet and an outlet of the solar heat absorber are consistent;

according to the output power P of the solar heat absorber in the first time period and the second time period_outpA、P_outpBAnd specifying the ratio N to determine the thermal efficiency.

When the heat absorber operates stably and the states of the inlet and outlet heat transfer working media are consistent in different time periods, the heat dissipation loss of the heat absorber is basically unchanged, and the relation between incident powers in different time periods can be established. Based on another relation between the incident powers provided by N in different time periods, the influence of the incident powers on the thermal efficiency can be counteracted in a numerical operation mode, so that the thermal efficiency can be measured and calculated based on the output power.

Compared with the prior art, the method for testing the thermal efficiency of the solar heat absorber, provided by the invention, can determine the thermal efficiency of the solar heat absorber only by testing some physical quantities which are easy to measure without measuring or calculating and simulating the incident power of the heat absorber, and has the advantages of low test cost and less interference to the operation of the heat absorber.

The incident power of the heat absorber is changed in the first time period and the second time period to determine the heat efficiency, so that the heat absorber heat exchanger is suitable for different types of heat absorbers and different types of heat transfer working media, and is wide in audience range and strong in adaptability.

Preferably, the output power P_outpThe calculation formula of (2) is as follows:

wherein the content of the first and second substances,the unit is t/h, and is the mass flow of the heat absorber; h is_inExpressing the enthalpy value of the heat transfer working medium at the inlet of the heat absorber, wherein the unit is kJ/kg; h is_outExpressing the enthalpy value of the heat transfer working medium at the outlet of the heat absorber, wherein the unit is kJ/kg;

thermal efficiency eta of solar heat absorber in first time period and second time period_A、η_BThe calculation formula of (2) is as follows:

wherein alpha is_rcvIs the absorption rate of the heat absorber; p_outpAAnd P_outpBThe output power of the heat sink in the first time period and the second time period, respectively, is given in units of W.

Further, as a priority, according to the results of multiple tests, the thermal efficiency of the heat absorber under the rated working condition is obtained through an interpolation mode.

According to the optimal scheme, a more accurate thermal efficiency result can be obtained through reasonable formula calculation, and the test precision is higher.

Further, it is preferable that the value of N is changed by changing the number of solar collectors in the solar collector field that irradiate the solar heat absorber.

According to the preferred scheme, the value of the specified proportion N is calculated according to the change of the number of the solar energy collecting lenses, so that the method is more convenient, quicker and more accurate.

Further, preferably, the first time period and the second time period are time periods on the same day that are symmetrical about 12:00 am, the local true solar time.

According to the preferred scheme, the two time periods which are symmetrical to the local true solar time and 12:00 noon are symmetrical, so that the radiation intensity in the first time period and the radiation intensity in the second time period are similar, and the influence of solar irradiance change on the incident power ratio N is effectively avoided.

Further, preferably, the method for testing the thermal efficiency of the solar thermal absorber further comprises the step of grouping the solar concentrators in the solar concentrator field, wherein the different groups of heliostat layouts are staggered with respect to the solar thermal absorber. Through grouping the solar condenser lenses, the solar condensing field effect rates among different groups are basically the same, so that the influence of the solar condensing field effect rate on the incident power ratio N is effectively avoided.

Further, preferably, the method for testing the thermal efficiency of the solar thermal absorber further comprises the step of determining the prescribed ratio N according to the ratio between the DNI value in the first time period and the DNI value in the second time period.

The DNI value is used as an influencing parameter of the incident power ratio N, and on the one hand, is a relatively easy-to-measure quantity, and on the other hand, a change in weather conditions is directly reflected in a change in DNI value, and causes a change in incident power, which is also a quantity that is easy to change.

Further, it is preferable to use a method of changing the cleaning rate of the solar condenser, to increase or decrease the incident power, and the prescribed ratio N is determined based on the ratio before and after the cleaning rate is changed.

According to the preferred embodiment, the value of the prescribed ratio N can be changed in various ways, and the thermal efficiency test mode is flexible and various. In addition, the comparison and calculation can be carried out through calculation results of various modes, and a more accurate thermal efficiency result can be obtained.

Further, it is preferable that the first time period and the second time period are corresponding time periods in two days in which the attitude angle of the solar condenser changes by not more than 3%.

According to the preferred scheme, the time interval between the first time period and the second time period corresponds to the change of the attitude angle of the solar condenser lens not more than 3%, and the test time periods in the two days are the same, so that the aiming point positions of the solar condenser lens fields in different test time periods are almost the same, the difference of the solar condensing field efficiency is almost negligible, and the influence of the solar condensing field efficiency on the incident power ratio N can be reduced.

Here, the "time period corresponding to two days" means a time period in which the starting point and the ending point are equal in value according to the 24-hour timekeeping method.

In addition, preferably, the heat absorbers with liquid and granular heat transfer working media correspond to the heat absorbers with the inlet and outlet heat transfer working media in consistent states, namely the temperature difference of the heat transfer working media at the inlet and the outlet of the heat absorber is within +/-5 ℃ in the first time period and the second time period;

corresponding to the heat absorber with the gaseous heat transfer working medium, the consistent states of the heat transfer working medium at the inlet and the outlet mean that the temperature difference of the heat transfer working medium at the inlet and the outlet of the heat absorber is within +/-5 ℃ and the pressure difference of the heat transfer working medium at the outlet of the heat absorber is within +/-5 kPa in the first time period and the second time period.

According to the preferred scheme, due to the influence of weather factors and field operation, the inlet temperature and the outlet temperature of the heat absorber in the first time period and the second time period are not necessarily the same, and the outlet pressure of the gas heat transfer working medium is also different. The test requirements can be met as long as the temperature variation range of the heat transfer working medium at the inlet and the outlet of the heat absorber is within +/-5 ℃ and the pressure variation range of the gas heat transfer working medium is within +/-5 kPa in two time periods, and the conditions of actual operation are also met.

In addition, as the optimization, the heat absorber which corresponds to the heat absorber with the heat transfer working medium in liquid state and particles stably operates means that the temperature fluctuation range of the heat transfer working medium at the inlet and the outlet of the heat absorber is within +/-2 ℃ within any 2 minutes in the first time period and the second time period;

the stable operation of the solar heat absorber corresponding to the heat absorber with the gaseous heat transfer working medium means that the temperature fluctuation range of the heat transfer working medium at the inlet and the outlet of the heat absorber is within +/-2 ℃ and the pressure fluctuation range of the heat transfer working medium at the outlet of the heat absorber is within +/-1 kPa within any 2 minutes in the first time period and the second time period.

According to the preferred scheme, due to the influences of normal direct irradiance, temperature and wind speed fluctuation in a test time period and a field control strategy, the inlet and outlet temperatures of the heat absorber and the outlet pressure of the gaseous heat transfer working medium can fluctuate. The stable operation can be regarded as long as the temperature fluctuation range of the heat transfer working medium at the inlet and the outlet of the heat absorber is not more than +/-2 ℃ and the pressure fluctuation range of the gas heat transfer working medium is not more than +/-1 kPa within any 2 minutes in two time periods.

Drawings

FIG. 1 is a molten salt system flow diagram;

FIG. 2 is a schematic diagram illustrating a solar concentrator field division according to a first embodiment of the present invention;

fig. 3 shows the thermal efficiency testing procedure of the heat absorber in the first embodiment of the present invention;

fig. 4 shows the thermal efficiency testing procedure of the heat absorber in the second embodiment of the present invention;

fig. 5 shows the thermal efficiency testing procedure of the heat absorber in the third embodiment of the present invention.

Description of reference numerals:

1. a cold salt tank; 2. a cold salt pump; 3. a flow meter; 4. an inlet buffer tank; 5. an inlet temperature sensor; 6. an inlet pressure sensor; 7. a solar concentrator field; 8. a heat sink; 9. an outlet pressure sensor; 10. an outlet temperature sensor; 11. an outlet buffer tank; 12. a valve; 13. and (4) a hot salt tank.

Detailed Description

The present invention will be described in further detail with reference to the accompanying drawings. The structure and the like for testing the thermal efficiency of the solar heat absorber are schematically and simply shown in the attached drawings.

In the description of the present invention, it is to be understood that the terms "upper", "lower", "front", "rear", "left", "right", "top", "bottom", "inner", "outer", and the like, indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, are merely for convenience in describing the present invention and simplifying the description, and do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be construed as limiting the present invention.

Implementation mode one

In a first embodiment of the present invention, a method for testing thermal efficiency of a solar heat absorber is provided, fig. 1 shows a flow chart of a molten salt system, and in other embodiments, taking a molten salt system as an example, molten salt flows in a cold salt tank 1, an inlet buffer tank 4, a heat absorber 8, an outlet buffer tank 11 and a hot salt tank 13 in sequence, and a solar condenser field 7 focuses and reflects solar radiation to the heat absorber 8.

More specifically, an inlet buffer tank 4 is arranged between the cold salt tank 1 and the heat absorber 8, and the outlet end of the cold salt tank 1 utilizes the cold salt pump 2 to provide power for circulating the molten salt towards the heat absorber 8. A flowmeter 3 is arranged between the cold salt tank 1 and the inlet buffer tank 4, and detects the flow rate of the molten salt flowing out of the cold salt tank 1 in real time. An inlet temperature sensor 5 and an inlet pressure sensor 6 are sequentially arranged between the inlet buffer tank 4 and the heat absorber 8, and are used for respectively detecting the temperature and the pressure of the molten salt at the inlet end of the heat absorber 8. The solar energy focusing mirror field 7 focuses the solar energy to the heat absorber 8, and the molten salt flowing to the heat absorber 8 absorbs the radiation and raises the temperature.

The circulating molten salt flows from the heat absorber 8 to the hot salt tank 13, an outlet buffer tank 11 is arranged between the heat absorber 8 and the hot salt tank 13, an outlet pressure sensor 9 and an outlet temperature sensor 10 are sequentially arranged between the heat absorber 8 and the outlet buffer tank 11, and the temperature and the pressure of the molten salt at the outlet end of the heat absorber 8 are respectively detected. A valve 12 is provided between the outlet buffer tank 11 and the hot salt tank 13.

Fig. 3 shows a schematic division diagram of a solar concentrator field in the first embodiment, in which a plurality of solar concentrators are staggered around a heat absorber. And, in each circle of the condenser, every other one of the condenser lenses is marked as black, and the rest of the condenser lenses are marked as white. The black marked collection mirrors make up group 1 and the white marked collection mirrors make up group 2. Therefore, the difference between the field efficiency of the two groups of solar condensing lenses can be ignored, and the difference of the incident power can be reduced proportionally when a certain group of solar condensing lenses is closed, for example, N is 0.5.

Taking a molten salt system as an example, in the first embodiment, a pair of thermal efficiency process tests is performed in a grouping manner, and the test steps are shown in fig. 3 and are as follows:

step 1: the difference of the incident power of the heat absorber is only related to the change of the number of the projected solar energy collecting mirrors. The test times are symmetrical about the true solar time at noon of 12:00 at the location of the solar thermal power plant. The incident power of the heat absorber is changed through the grouping and control strategy of the solar condenser field, and the influence of weather is small. The test time is symmetrical about the local true solar time at noon of 12:00, and the influence of the field efficiency of the solar condenser on the incident power ratio N is effectively avoided.

Before the test is started, field operators should determine that the heat absorber 8 does not have the phenomenon of salt blockage, and the test instruments 3, 5, 6, 9 and 10 and the solar condenser field 7 work normally. After the solar condenser field 7 is started, the heat absorber 8 is preheated, and salt is added after the wall of the heat absorber meets the requirement. After salting, the molten salt system can be kept in low load operation for a period of time, i.e., the heat sink outlet temperature sensor 10 reading is maintained below 400 ℃, to observe the conditions of system operation. And if the system stably and normally operates, slowly increasing the temperature of the molten salt. 20 minutes before the start of the test, the positions of the solar energy collecting lenses are uniformly distributed, the number of the solar energy collecting lenses is more than 80% of the total number of the solar energy collecting lenses, the reading of a heat absorber outlet temperature sensor 10 is more than 500 ℃, and the time of molten salt temperature rise after the start of the formal test is reduced. At this time, the molten salt directly enters the hot salt tank 13, the inlet temperature of the heat absorber does not fluctuate greatly any more, and the corresponding inlet temperature of the heat absorber can be established.

Step 2: testing the working condition A: before the real solar time noon is 12:00, namely in the first time period, the two groups of solar energy collecting lenses of the 1 st group and the 2 nd group are in the sun-chasing working state.

And step 3: and the operator of the molten salt system utilizes the cold salt pump 2 to regulate the mass flow of the molten salt in a frequency conversion manner, so that the temperature reading at the outlet of the heat absorber in the test time period reaches the test temperature. And the testing temperature is determined according to the testing working condition, and if the thermal efficiency of the solar heat absorber under the rated working condition is to be tested, the temperature is the rated temperature of the outlet of the heat absorber.

And 4, step 4: a steady state is considered to be achieved when the range of fluctuations in the readings from the absorber inlet temperature sensor 5 and the absorber outlet temperature sensor 10 do not exceed ± 2 ℃ within 2 minutes. At this time, the molten salt system operator records normal direct irradiance, wind speed, temperature, heat absorber flowInlet temperature T_inOutlet temperature T_outInlet pressure P_inAnd an outlet pressure P_outAnd so on.

And 5: and testing working condition B: after 12 am when the local real solar time, that is, in the second time period, the 2 nd group of solar energy collecting lenses (or the 1 st group of solar energy collecting lenses) are removed, and only one group of the solar energy collecting lenses is in the sun-following working state.

Step 6: and (5) repeating the step (3). The reading of the inlet temperature sensor 5 and the outlet temperature sensor 10 of the heat absorber under the working condition B and the reading change range of the inlet temperature sensor 5 and the outlet temperature sensor 10 under the working condition A are within +/-5 ℃.

And 7: and (4) repeating the step.

And 8: and respectively calculating the output power of the heat absorber 8 under the test working condition A and the test working condition B according to the recorded data. And calculating the thermal efficiency of the heat absorber 8 under the test working condition A and the test working condition B according to the output power of the heat absorber 8.

Output power P_outpThe calculation method comprises the following steps:

wherein:the unit is t/h, and is the mass flow of the heat absorber; h is_inExpressing the enthalpy value of the heat transfer working medium at the inlet of the heat absorber, wherein the unit is kJ/kg; h is_outExpressing the enthalpy value of the heat transfer working medium at the outlet of the heat absorber, and the unit is kJ/kg.

The heat efficiency calculation method of the heat absorber comprises the following steps:

wherein eta is_AAnd η_BThe thermal efficiency of the heat absorber is respectively working condition A and working condition B; alpha is alpha_rcvIs the absorption rate of the heat absorber; p_outpAAnd P_outpBThe output power of the heat absorber in the first time period and the second time period respectively is W; and N is the ratio of the incident power of the heat absorber in the first time period to the incident power of the heat absorber in the second time period.

As an optimization, the intrinsic efficiency of the heat absorber is defined as:

the efficiency of the absorber is the intrinsic efficiency of the absorber multiplied by the absorption rate of the absorber, which reflects the ratio of the absorber output power to the energy of the solar radiation absorbed by the absorber.

For the first working condition control strategy, N should be 0.5.

And by correcting DNI, ambient temperature and wind speed under the test condition and the rated working condition, the efficiency of the heat absorber under the rated working condition can be calculated through the efficiencies of the working condition A and the working condition B.

The specific calculation process of the formula is as follows:

according to the first law of thermodynamics, under a steady state condition, the incident power of the heated surface of the heat absorber has the following relationship with the power reflected by the heat absorber, the output power and the heat loss power:

P_inc＝ρP_inc+P_outp+P_loss (1)

the absorption rate of the heat absorber is alpha, since the transmission of the heat absorber is negligible_rcvAnd heat absorber reflectivity ρ_rcvHas the following relationship:

ρ_rcv＝1-α_rcv (2)

then:

α_rcvP_inc＝P_outp+P_loss (3)

when the heat absorber operates stably, under the conditions of constant inlet and outlet temperatures and wind speed, the correlation between the temperature distribution of the surface of the heat absorber and the whole heat absorber and incident power is small, and the heat dissipation loss of the heat absorber is basically unchanged. The following relationship is then obtained:

α_rcvP_incA＝P_outpA+P_loss (4)

α_rcvP_incB＝P_outpB+P_loss (5)

according to the working condition control, the incident power of the working condition A and the incident power of the working condition B have the following relation:

P_incA＝NP_incB (6)

thus, we obtain:

P_outpA+P_loss＝NP_outpB+NP_loss (7)

the heat loss can be expressed as:

the heat sink output power can be expressed as:

wherein:the unit is t/h, and is the mass flow of the heat absorber; h is_inExpressing the enthalpy value of the heat transfer working medium at the inlet of the heat absorber, wherein the unit is kJ/kg; h is_outExpressing the enthalpy value of the heat transfer working medium at the outlet of the heat absorber, and the unit is kJ/kg.

The thermal efficiency is defined as:

the thermal efficiency corresponding to the working condition A and the working condition B can be obtained by the derivation:

the heat absorber is an external heat absorber, a cavity type heat absorber, a positive displacement heat absorber or a particle heat absorber, and the heat transfer working medium is fused salt, water/steam, air and supercritical CO₂Heat transfer oil or particles.

The aforementioned heat transfer medium states are different for different states of the heat transfer medium.

If the heat transfer working medium is liquid or granular, the state of the heat transfer working medium comprises the inlet and outlet temperature of the heat absorber, and the enthalpy value h of the heat transfer working medium has the calculation formula as follows:

h＝U+PV

wherein U is the internal energy of the heat transfer working medium and the unit is J; the outlet pressure of the liquid and particle heat transfer working medium is generally normal pressure, and the influence on the calculation of the output power of the heat absorber is small.

For the heat absorber with the heat transfer working medium in a liquid state or particles, the consistent state of the heat transfer working medium means that the temperature variation ranges of the heat transfer working medium at the inlet and the outlet of the heat absorber are within +/-5 ℃ in the first and second time periods. The inlet temperature and the outlet temperature of the heat absorber in the two test periods are not necessarily the same due to the influence of weather factors and field operation; therefore, the temperature variation range is set within +/-5 ℃, so that the test requirement can be ensured, and the actual operation condition is met.

As optimization, the stable heat transfer working medium state of the inlet and the outlet of the heat absorber means that the fluctuation range of the temperature of the inlet and the outlet of the heat absorber does not exceed +/-2 ℃ within 2 minutes. Due to the DNI, the fluctuation of the temperature and the wind speed in the testing time period and the influence of a field control strategy, the temperature of the inlet and the outlet of the heat absorber may fluctuate, and the temperature fluctuation range is regarded as being stably consistent with the actual operation condition when the temperature fluctuation range does not exceed +/-2 ℃.

Second embodiment

The second embodiment of the present invention provides a method for testing thermal efficiency of a solar heat absorber, and the second embodiment is a further improvement of the first embodiment, and parts not specifically described include reference numerals and text descriptions, which are the same as those of the first embodiment, and are not described herein again.

Taking an air system as an example, the second embodiment adopts a working condition control strategy to test two pairs of thermal efficiencies, the test steps are shown in fig. 4, and the steps are as follows:

step 1: the difference of the incident power of the heat absorber is only related to the change of the normal direct irradiance (hereinafter referred to as DNI). The DNI variation is caused by cloud or sand weather factors. Setting the day when the DNI changes as a working condition A, namely a first time period; and a clear day in which the change of the attitude angle of the solar energy condenser corresponding to the working condition A is not more than 3% is a working condition B, namely a second time period. The test time periods of the working condition A and the working condition B are consistent, the states of the solar condenser field of the working condition A and the solar condenser field of the working condition B are the same, and DNI in the respective test time periods is kept stable.

Before the test begins, the field operator should determine that the test instruments 3, 5, 6, 9, 10 and the solar concentrator field 7 are working properly. After the solar condenser field 7 is started, the heat absorber 8 is preheated, and gas heat absorbing medium is introduced after the wall of the heat absorber meets the requirement. After venting the gas heat absorption medium, the brayton cycle system can be kept in low load operation for a period of time, i.e. the heat absorber outlet temperature sensor 10 reading is maintained at around 400 ℃, to observe the system operating conditions. If the system is stably and normally operated, the temperature of the air is slowly increased. 20 minutes before the start of the test, the positions of the solar energy collecting lenses are uniformly distributed, the number of the solar energy collecting lenses is more than 80% of the total number of the solar energy collecting lenses, the reading of the temperature sensor 10 at the outlet of the heat absorber is more than 700 ℃, and the time for heating the gas heat absorbing medium after the start of the formal test is shortened. At the moment, air directly enters the turbine to do work, the inlet temperature of the heat absorber does not fluctuate greatly any more, and the corresponding inlet temperature of the heat absorber can be determined.

Step 2: testing the working condition A: in a first time period, in the light-gathering state of the solar condenser field 7, the attitude angle of the solar condenser field 7, the input position and number of the solar condenser and the aiming point are determined and recorded.

And step 3: the air system operator adjusts the mass flow of air by adjusting the system load or turbine speed to bring the heat absorber outlet temperature reading to the test temperature during the test period. And the testing temperature is determined according to the testing working condition, and if the thermal efficiency of the solar heat absorber under the rated working condition is to be tested, the temperature is the rated temperature of the outlet of the heat absorber.

And 4, step 4: and when the fluctuation range of the readings of the heat absorber inlet temperature sensor 5 and the heat absorber outlet temperature sensor 10 is not more than +/-2 ℃ and the fluctuation range of the heat absorber inlet pressure sensor 6 and the heat absorber outlet pressure sensor 9 is not more than +/-1 kPa within 2 minutes, the stability can be considered to be reached. At this time, the air system operator records DNI, wind speed, temperature, heat absorber flowInlet temperature T_inOutlet temperature T_outInlet pressure P_inAnd an outlet pressure P_outAnd so on.

And 5: and testing working condition B: and in a second time period, determining and recording the attitude angle of the solar condenser field, putting the solar condensers with the same positions and quantity as the working condition A, and setting the aiming points as the working condition A. The same aiming point position can eliminate the difference between the truncation efficiency and the shadow shielding efficiency caused by the aiming point.

Step 6: and (5) repeating the step (3). The reading of the heat absorber inlet temperature sensor 5 and the reading of the heat absorber outlet temperature sensor 10 in the working condition B and the reading change ranges of the heat absorber inlet temperature sensor 5 and the heat absorber outlet temperature sensor 10 in the working condition A are within +/-5 ℃, and the reading of the heat absorber inlet pressure sensor 6 and the reading change ranges of the heat absorber outlet pressure sensor 9 in the working condition B and the reading change ranges of the heat absorber inlet pressure sensor 6 and the heat absorber outlet pressure sensor 9 in the working condition A are within +/-5 kPa.

And 7: and (4) repeating the step.

And 8: and respectively calculating the output power of the heat absorber 8 under the test working condition A and the test working condition B according to the recorded data. And calculating the thermal efficiency of the heat absorber 8 under the test working condition A and the test working condition B according to the output power of the heat absorber 8.

Output power P_outpThe calculation method comprises the following steps:

wherein:the unit is t/h, and is the mass flow of the heat absorber; h is_inExpressing the enthalpy value of the heat transfer working medium at the inlet of the heat absorber, wherein the unit is kJ/kg; h is_outExpressing the enthalpy value of the heat transfer working medium at the outlet of the heat absorber, and the unit is kJ/kg.

The heat efficiency calculation method of the heat absorber comprises the following steps:

wherein alpha is_rcvIs the absorption rate of the heat absorber; p_outpAAnd P_outpBThe output power of the heat absorber in the first time period and the second time period respectively is W; and N is the ratio of the incident power of the heat absorber in the first time period to the incident power of the heat absorber in the second time period.

For the present operating mode control strategy two, N-DNI_A/DNI_BThe value is 0.5 to 0.8.

And by correcting DNI, ambient temperature and wind speed under the test condition and the rated working condition, the efficiency of the heat absorber under the rated working condition can be calculated through the efficiencies of the working condition A and the working condition B.

Third embodiment

A third embodiment of the present invention provides a method for testing thermal efficiency of a solar thermal absorber, where the third embodiment is a further improvement on the first or second embodiment, and parts not specifically described include reference numerals and text descriptions, which are the same as those in the first or second embodiment, and are not described herein again.

Taking the particle system as an example, the third embodiment adopts a grouping mode to perform three pairs of thermal efficiency process tests, the test steps are shown in fig. 5, and the steps are as follows:

step 1: the difference of the incident power of the heat absorber is only equal to the mirror surface cleaning rate eta_{c ln}Is relevant. Cleaning rate eta_{c ln}The variation of (a) is achieved by cleaning the solar concentrator or spraying a dust or fog onto the surface of the solar concentrator. Setting the working condition A as the cleaning rate eta of the solar condenser_{c ln}The changed day is sunny, namely a first time period; setting the working condition B as the cleaning rate eta of the solar condenser_{c ln}The day of sunny before the change, i.e. the second time period. The day difference between the working condition A and the working condition B corresponds to that the attitude angle of the solar condenser changes by no more than 3%, the test time periods of the working condition A and the working condition B are consistent, the states of the solar condenser fields of the working condition A and the working condition B are the same, and DNI in the respective test time periods is kept stable. The cleaning rate eta of the solar condenser can be obviously changed by cleaning the solar condenser or spraying the surface of the solar condenser with water_{c ln}The operation is also simpler. And if the test time periods of the working condition A and the working condition B are the same, the DNI in the test time of the working condition A and the test time of the working condition B are basically the same. And the change of the attitude angle of the solar condenser is very small, the field efficiency of the solar condenser in two test time periods is only equal to the cleaning rate eta_{c ln}It is related.

Before the test is started, the field operating personnel should determine that the particle layer in the particle heat absorber 8 can continuously and stably flow, each test instrument 5, 6, 9 and 10 and the heliostat field 7 work normally, and the valve is closed after the test is finished. And (3) heating a particle layer in the particle heat absorber 8 after the heliostat field 7 is started, and opening an inlet and outlet control valve of the heat absorber after the surface temperature of the particles meets the requirement, so that the particles start to flow. After opening the control valve, the particulate heat absorber can be kept in low load operation for a period of time, i.e., the particulate heat absorber outlet temperature sensor 10 reading is maintained below 400 c, to observe system operation. If the system is stably and normally operated, slowly increasing the temperature of the particle layer. 20 minutes before the start of the test, the positions of the solar energy collecting lenses are uniformly distributed, the number of the solar energy collecting lenses is more than 80% of the total number of the solar energy collecting lenses, the reading of a heat absorber outlet temperature sensor 10 is more than 800 ℃, and the time of molten salt temperature rise after the start of the formal test is reduced. At this point, the particles enter the hot tank 13 directly, and the absorber inlet temperature no longer fluctuates significantly, and the corresponding absorber inlet temperature can be established.

Step 2: testing the working condition A: in a first time period, in the light-gathering state of the solar condenser field 7, the attitude angle of the solar condenser field 7, the input position and number of the solar condenser and the aiming point are determined and recorded.

And step 3: the operator of the particle system adjusts the electric valve 2 to control the mass flow of the particles, so that the temperature reading at the outlet of the heat absorber in the testing time period reaches the testing temperature. And the testing temperature is determined according to the testing working condition, and if the thermal efficiency of the solar heat absorber under the rated working condition is to be tested, the temperature is the rated temperature of the outlet of the heat absorber.

And 4, step 4: a steady state is considered to be achieved when the range of fluctuations in the readings from the absorber inlet temperature sensor 5 and the absorber outlet temperature sensor 10 do not exceed ± 2 ℃ within 2 minutes. At this point, the particle system operator records DNI, wind speed, temperature, heat sink flow, inlet temperature, outlet temperature, inlet pressure, and outlet pressure data.

And 5: and testing working condition B: and in a second time period, determining and recording the attitude angle of the solar condenser field, putting the solar condensers with the same positions and quantity as the working condition A, and setting the aiming points as the working condition A. The same aiming point position can eliminate the difference between the truncation efficiency and the shadow shielding efficiency caused by the aiming point.

Step 6: and (5) repeating the step (3). The reading of the heat absorber inlet temperature sensor 5 and the outlet temperature sensor 10 in the working condition B and the reading change range of the inlet temperature sensor 5 and the outlet temperature sensor 10 in the working condition A are within +/-5 ℃.

And 7: and (4) repeating the step.

And 8: and respectively calculating the output power of the heat absorber 8 under the test working condition A and the test working condition B according to the recorded data. And calculating the thermal efficiency of the heat absorber 8 under the test working condition A and the test working condition B according to the output power of the heat absorber 8.

Output power P_outpThe calculation method comprises the following steps:

wherein:the unit is t/h, and is the mass flow of the heat absorber; h is_inExpressing the enthalpy value of the heat transfer working medium at the inlet of the heat absorber, wherein the unit is kJ/kg; h is_outExpressing the enthalpy value of the heat transfer working medium at the outlet of the heat absorber, and the unit is kJ/kg.

The heat efficiency calculation method of the heat absorber comprises the following steps:

wherein alpha is_rcvIs the absorption rate of the heat absorber; p_outpAAnd P_outpBThe output power of the heat absorber in the first time period and the second time period respectively is W; and N is the ratio of the incident power of the heat absorber in the first time period to the incident power of the heat absorber in the second time period.

For the present grouping scheme three, N ═ η_{c ln A}/η_{c ln B}The value is 0.6 to 0.8, where eta_{c ln} Indicating the cleaning rate of the solar concentrator.

And by correcting DNI, ambient temperature and wind speed under the test condition and the rated working condition, the efficiency of the heat absorber under the rated working condition can be calculated through the efficiencies of the working condition A and the working condition B.

The state of the solar condenser field in the second and third embodiments is the same, including the position and number of the solar condensers for tracking the day, the tracking attitude of each solar condenser, and the position of the aiming point. The solar energy collecting mirrors in the same positions and quantity can eliminate the difference of the efficiency of the solar energy collecting mirrors in different positions, and the efficiency of the whole mirror field in two testing time periods is ensured to be the same.

The groove type, the disc type, the linear Fresnel type or the combined light-gathering type can be used for testing the heat absorber according to the second embodiment and the third embodiment.

In some embodiments, the power P is output_outpThe enthalpy value in (1) is converted into a value that can be actually measured, thereby converting the calculation formula into:

wherein the content of the first and second substances,the unit is t/h, and is the mass flow of the heat absorber; cp_inThe specific heat capacity of the heat transfer working medium at the inlet of the heat absorber is expressed in J/(kg.K); cp_outThe specific heat capacity of the heat transfer working medium at the outlet of the heat absorber is expressed in J/(kg.K); t is_inThe temperature of heat transfer working media at the inlet of the heat absorber is respectively, and the unit is; t is_outThe temperature of the heat transfer working medium at the outlet of the heat absorber is respectively in the unit of ℃.

It will be appreciated by those of ordinary skill in the art that in the embodiments described above, numerous technical details are set forth in order to provide a better understanding of the present application. However, the technical solutions claimed in the claims of the present application can be basically implemented without these technical details and various changes and modifications based on the above-described embodiments. Accordingly, in actual practice, various changes in form and detail may be made to the above-described embodiments without departing from the spirit and scope of the invention.