CN115751737A - Disc type heat collection heater for solar thermal power generation system and design method - Google Patents
Disc type heat collection heater for solar thermal power generation system and design method Download PDFInfo
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- CN115751737A CN115751737A CN202310028426.7A CN202310028426A CN115751737A CN 115751737 A CN115751737 A CN 115751737A CN 202310028426 A CN202310028426 A CN 202310028426A CN 115751737 A CN115751737 A CN 115751737A
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/40—Solar thermal energy, e.g. solar towers
- Y02E10/44—Heat exchange systems
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/40—Solar thermal energy, e.g. solar towers
- Y02E10/46—Conversion of thermal power into mechanical power, e.g. Rankine, Stirling or solar thermal engines
Abstract
The embodiment of the invention provides a disc type heat collection heater for a solar thermal power generation system and a design method, and relates to the field of solar heat collection heater structures. The disc-type heat collection heater comprises a shell, a plurality of heating pipes, an air inlet collection chamber and an air inlet pipe, wherein the shell is provided with a heat collection cavity and a light gathering port, the heat collection cavity is communicated with the light gathering port, the plurality of heating pipes are uniformly arranged in the heat collection cavity along the circumferential direction, and the air inlet pipe is communicated with the air inlet collection chamber, the air inlet collection chamber and all the heating pipes. And the air inlet collection chamber is positioned outside a light condensation area defined by the edge of the light condensation port, the collection chamber is used for conveying heat conduction working media to the heating pipe, and solar energy enters the heat collection cavity through the light condensation port and heats the heat conduction working media in the air inlet collection chamber and the heating pipe. Because the heat-conducting working medium is heated in the air inlet and collecting chamber, the solar energy entering the heat collecting cavity can carry out secondary heating on the heat-conducting working medium in the heating pipe, thereby improving the heat collecting efficiency of the disc type heat collecting heater.
Description
Technical Field
The invention relates to the field of solar heat collection heater structures, in particular to a disc type heat collection heater for a solar thermal power generation system and a design method.
Background
The disc-type Stirling solar thermal power generation system utilizes the technical characteristics of small size, high temperature and high efficiency of a Stirling heat engine to directly connect the Stirling engine and the disc-type heat collector, and the Stirling engine is arranged at the focus of the disc-type heat collector and tracks solar energy together with the light condensing system. The solar heat power generation efficiency of over 30 percent is obtained by utilizing the advantages of high disc type light condensation and heat collection efficiency and high Stirling engine efficiency without a heat transfer and storage system. But the heat transfer and heat storage device is not configured, so that the application of generating power by replacing the conventional energy source with the renewable energy source of the current power system is limited. The heat reservoir of the solar thermal power generation system is very large in size, is difficult to be arranged on the light-gathering bracket to track the movement of the sun and can only be arranged on the ground. Therefore, the solar energy must be transmitted to the ground heat storage tank through high-temperature heat collection and high-temperature heat conduction working medium. The market application of the high-temperature solar thermal power generation technology capable of storing energy can be realized.
The disc type solar light and heat collecting device is a solar light and heat collecting system with the highest efficiency. The light and heat collecting efficiency is as high as more than 90%, which is far higher than that of tower type and groove type light and heat collecting systems. Is an ideal solar heat collecting technology with high temperature light gathering. The disc type solar heat collector needs to utilize a high-temperature heat conducting working medium to conduct long-distance high-temperature heat conducting operation, so that the disc type solar heat collector in the prior art has the problems of serious heat energy loss and low heat collecting efficiency.
Disclosure of Invention
The invention provides a disc type heat collection heater for a solar thermal power generation system and a design method thereof, which can improve the heat collection efficiency of the disc type heat collection heater for the solar thermal power generation system and reduce the loss of heat energy.
Embodiments of the invention may be implemented as follows:
an embodiment of the present invention provides a dish type heat collecting heater for a solar thermal power generation system, including:
the shell is provided with a heat collection cavity and a light gathering port, and the heat collection cavity is communicated with the light gathering port;
the heating pipes are uniformly arranged in the heat collection cavity along the circumferential direction;
the air inlet collection chamber is connected with all the heating pipes, is positioned outside a light condensation area defined by the edge of the light condensation opening, and is used for primarily heating a heat conduction working medium and conveying the heat conduction working medium to the heating pipes;
the air inlet pipe is connected with the air inlet collection chamber;
the solar energy enters the heat collection cavity through the light gathering port and heats the air inlet collection chamber and the heat conducting working medium in the heating pipe.
Optionally, the plurality of heating pipes together form an annular structure, and the plurality of heating pipes are all symmetrically arranged and evenly distributed along a center line of the housing.
Optionally, the portions of all the heating pipes connected with the intake plenum are continuously and uniformly curved toward directions away from each other.
Optionally, the gap between two adjacent heating tubes ranges from 0.05mm to 0.1 mm.
Optionally, the disc type heat collection heater for the solar thermal power generation system further comprises a plurality of flow deflectors, and the plurality of flow deflectors are arranged in the air intake collection chamber at intervals.
Optionally, the air intake collection chamber is annular, two side walls of the air intake collection chamber are both connected with the flow deflectors, and the flow deflectors on different side walls are arranged in a staggered manner.
Optionally, the disc type heat collection heater for the solar thermal power generation system further comprises a flow regulating valve, and the flow regulating valve is arranged in the air inlet pipe.
Optionally, the disc type heat collection heater for the solar thermal power generation system further comprises an air outlet assembly, the air outlet assembly is located in a light gathering area surrounded by the edge of the light gathering port, and the air outlet assembly is connected with the heating pipe.
Optionally, the air outlet assembly comprises an air outlet collection chamber and an air outlet pipe, the air outlet collection chamber is connected with all the heating pipes, and the air outlet collection chamber is connected with the air outlet pipe.
Optionally, the housing includes a front baffle, a bottom plate and a side plate, one side edge of the side plate is connected to the front baffle, the other side edge of the side plate is connected to the bottom plate, the light gathering port is disposed on the front baffle, and the air outlet pipe penetrates through the bottom plate.
Optionally, the front baffle is provided with a connecting hole, and one end of the adapter section connected with one end of the air inlet and collection chamber is arranged in the connecting hole.
Optionally, the disc type heat collection heater for the solar thermal power generation system further comprises a heat insulation layer, and the heat insulation layer is arranged between the outer shell and the heating pipe.
The embodiment of the invention also provides a design method of the disc type heat collecting heater for the solar thermal power generation system, which is used for designing the disc type heat collecting heater for the solar thermal power generation system and comprises the following steps:
determining a characteristic angle alpha of the condenser;
determining the characteristic angle a of the disc type heat collecting heater and the diameter d of the light gathering port 0 ；
According to the characteristic angle alpha of the condenser, the characteristic angle a of the disc type heat collection heater and the diameter d of the light gathering port 0 Determining the characteristic length of the heat collection cavity and the inner diameter d of the air inlet collection chamber 1 ；
Determining the total heat energy loss of the disc type heat collecting heater;
and circulating the steps to obtain a plurality of total heat losses, and selecting a group of data with the minimum total heat loss to determine the structural parameters of the disc type heat collection heater.
The disc type heat collection heater for the solar thermal power generation system and the design method thereof provided by the embodiment of the invention have the beneficial effects that:
this a dish formula thermal-arrest heater for solar thermal power generation system includes the shell, a plurality of heating pipes, the collection chamber and the intake pipe of admitting air, the shell is equipped with thermal-arrest chamber and spotlight mouth, thermal-arrest chamber and spotlight mouth intercommunication, a plurality of heating pipes evenly set up in the thermal-arrest intracavity along circumference, the collection chamber and all heating pipes of admitting air are connected, the collection chamber that admits air is located the outside of the spotlight region that the edge that gathers the light mouth encloses, the collection chamber that admits air is used for carrying out the primary heating and carrying heat conduction working medium to the heating pipe with heat conduction working medium, the intake pipe is connected with the collection chamber that admits air, solar energy gets into the thermal-arrest chamber through spotlight mouth, and heat conduction working medium in collection chamber and the heating pipe of admitting air. When the disc type heat collection heater for the solar thermal power generation system is used, the disc type heat collection heater for the solar thermal power generation system can collect solar energy to form a conical light spot, so that the sunlight entering the heat collection cavity has an inclination angle, one part of the solar energy entering the heat collection cavity falls on the air inlet collection chamber to heat the heat conducting working medium, the other part of the solar energy falls on the heating pipe connected with the air inlet collection chamber to heat the heat conducting working medium in the heating pipe, and the heat conducting working medium is heated in the air inlet collection chamber, so that the solar energy entering the heat collection cavity can secondarily heat the heat conducting working medium in the heating pipe, thereby improving the heat collection efficiency and the heating temperature of the disc type heat collection heater for the solar thermal power generation system, and reducing the loss of the heat energy.
According to the design method of the disc type heat collecting heater for the solar thermal power generation system, through multiple times of design calculation, an optimal structure of the disc type heat collecting heater can be designed after a group of data with the minimum heat loss is selected.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings that are required to be used in the embodiments will be briefly described below, it should be understood that the following drawings only illustrate some embodiments of the present invention and therefore should not be considered as limiting the scope, and for those skilled in the art, other related drawings can be obtained according to the drawings without inventive efforts.
Fig. 1 is a schematic structural diagram of a first view angle of a dish type heat collection heater for a solar thermal power generation system according to an embodiment;
FIG. 2 isbase:Sub>A cross-sectional view taken along A-A of FIG. 1;
fig. 3 is an enlarged view of a portion a in fig. 1.
Icon: 1-heating a tube; 2-a housing; 21-a bottom plate; 22-a front baffle; 23-side plate; 3-a heat insulation layer; 41-air intake collection chamber; 42-an air inlet pipe; 5, an air outlet component; 51-air outlet collection chamber; 52-an air outlet pipe; 6-flow regulating valve; 7-bolt; 8-a light-gathering port; 9-flow deflectors; 100-disc type heat collecting heater for solar thermal power generation system.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are some, but not all embodiments of the present invention. The components of embodiments of the present invention generally described and illustrated in the figures herein may be arranged and designed in a wide variety of different configurations.
Thus, the following detailed description of the embodiments of the present invention, presented in the figures, is not intended to limit the scope of the invention, as claimed, but is merely representative of selected embodiments of the invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
It should be noted that: like reference numbers and letters refer to like items in the following figures, and thus, once an item is defined in one figure, it need not be further defined and explained in subsequent figures.
In the description of the present invention, it should be noted that, if the terms "upper", "lower", "inner", "outer", etc. are used to indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings or the orientation or positional relationship which the product of the present invention is used to usually place, it is only for convenience of description and simplification of the description, but it is not intended to indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present invention.
Furthermore, the appearances of the terms "first," "second," and the like, if any, are used solely to distinguish one from another and are not to be construed as indicating or implying relative importance.
It should be noted that the features of the embodiments of the present invention may be combined with each other without conflict.
Before describing the technical solutions of the embodiments of the present application, the technical terms and application scenarios related to the embodiments of the present application will be described and explained first.
A solar thermal power generation system using a water medium as a working medium and using heat transfer oil as a heat transfer and storage medium is called a first generation solar thermal power generation technology. At present, a plurality of power stations are operated internationally. The solar thermal power generation system using water as working medium and molten salt as heat transfer and storage medium is called as the second generation solar thermal power generation technology. At present, a plurality of power stations are operated internationally. The working medium temperature of the first generation solar thermal power station is below 400 ℃. The power generation efficiency is generally lower than 15%. The working medium temperature of the second generation solar thermal power station can reach 550 ℃. The generating efficiency can reach 18 percent. The solar thermal power generation system using gas as working medium (hydrogen, helium, carbon dioxide, air, etc.) and gas or solid (carbon dioxide, ceramics, etc.) as heat transfer and storage medium is called as third generation solar thermal power generation technology, and the power generation efficiency can reach more than 30%. At present, a third-generation solar thermal power generation system is in the stages of technical innovation and product development.
The third generation solar thermal power generation adopts a high-temperature solar thermal power generation technology, and faces significant technical innovation and breakthrough in the aspects of solar heat collection, heat energy transportation, storage, a heat engine and the like. At present, the disc type Stirling solar thermal power generation technology is more successful.
The disc-type Stirling solar thermal power generation system utilizes the technical characteristics of small size, high temperature and high efficiency of a Stirling heat engine to directly connect the Stirling engine and the disc-type heat collector, and the Stirling engine is arranged at the focus of the disc-type heat collector and tracks solar energy together with the light condensing system. The advantages of high efficiency of disc type light condensation and heat collection and high efficiency of the Stirling engine are utilized, and the solar thermal power generation efficiency of over 30 percent is obtained without a heat transfer and storage system. But the heat transfer and heat storage device is not configured, so that the application of generating power by replacing the conventional energy source with the renewable energy source of the current power system is limited. The heat reservoir of the solar thermal power generation system is very large in size, is difficult to be arranged on the light-gathering bracket to track the movement of the sun and can only be arranged on the ground. Therefore, the solar energy must be transmitted to the ground heat storage tank through high-temperature heat collection and high-temperature heat conduction working medium. The market application of the high-temperature solar thermal power generation technology capable of storing energy can be realized.
The disc type solar light and heat collecting device is a solar light and heat collecting system with the highest efficiency. The light and heat collecting efficiency is as high as more than 90%, which is far higher than that of tower type and groove type light and heat collecting systems. Is an ideal solar heat collecting technology with high temperature light gathering. The disc type solar heat collector needs to utilize a high-temperature heat conducting working medium to conduct long-distance high-temperature heat conducting operation, so that the disc type solar heat collector in the related technology has the problems of serious heat energy loss and low heat collecting efficiency.
Referring to fig. 1 to 3, the present embodiment provides a dish type heat collecting heater 100 for a solar thermal power generation system. The disc type heat collection heater 100 for the solar thermal power generation system can effectively solve the above-mentioned technical problems, improve the heat collection efficiency of the heat collection heater, and reduce the loss of heat energy.
The applied disc type solar thermal power generation system comprises but is not limited to an engine and a disc type heat collecting heater 100 used for the solar thermal power generation system, the engine generates power by using high-temperature heat energy collected by the disc type heat collecting heater, the engine is arranged on the ground and is connected with the engine by a high-pressure high-temperature pipe, the heat energy collected by the disc type heat collecting heater can also be conducted to a heat storage tank arranged on the ground by using a high-temperature heat conducting pipe for storing heat energy, and continuous power generation is carried out when no solar light exists. The heat collecting device has the technical characteristics of high pressure resistance, high temperature resistance and high efficiency, and solves the problems of high temperature, high efficiency collection and heat transmission of heat energy required by disc type energy storage and continuous power generation.
The applied disc type solar thermal power generation system comprises but is not limited to a condenser, a disc type heat collection heater 100 for the solar thermal power generation system is arranged at the focus of the condenser and moves along with the condenser to track the sun, and sunlight enters the disc type heat collection heater 100 for the solar thermal power generation system for heat collection after being reflected and condensed by the condenser.
Referring to fig. 1, the disc type heat collecting heater 100 for a solar thermal power generation system includes a housing 2, a plurality of heating pipes 1, an air intake collection chamber 41 and an air intake pipe 42, the housing 2 is provided with a heat collection cavity and a light gathering port 8, the heat collection cavity is communicated with the light gathering port 8, the plurality of heating pipes 1 are uniformly arranged in the heat collection cavity along a circumferential direction, the air intake collection chamber 41 is connected to all the heating pipes 1, the air intake collection chamber 41 is located outside a light gathering region surrounded by the edge of the light gathering port 8, the air intake collection chamber 41 is used for primarily heating a heat conducting working medium and delivering the heat conducting working medium to the heating pipes 1, and the air intake pipe 42 is connected to the air intake collection chamber 41, wherein solar energy enters the heat collection cavity through the light gathering port 8 and heats the heat conducting working medium in the air intake collection chamber 41 and the heating pipes 1.
Specifically, the disc type heat collecting heater for the solar thermal power generation system in the prior art is directly connected with the engine, but cannot store energy and continuously generate power. In order to solve the above problems, high temperature heat energy must be collected and conducted to the ground, but the collection and conduction of high temperature heat energy to the ground causes a great loss of heat energy. In order to reduce the heat energy consumption, two methods are generally adopted, one is to adopt high-performance heat insulation materials. The other is to use a high-temperature heat pipe with a smaller diameter, namely to increase the heat flux density of the heat transfer pipe. However, the reduction in the diameter of the heat conductive pipe increases the flow rate, resulting in an increase in pressure loss. Neither method can improve the heat collection efficiency well. In order to solve the technical problem, the solution adopted by the embodiment is as follows: firstly, a high-temperature-resistant and high-pressure-resistant high-efficiency heat collector is adopted for high-efficiency collection of heat energy. And secondly, supercritical carbon dioxide with special performance is used as a heat-conducting medium to realize high-temperature and high-efficiency transmission of heat energy. When the disc type heat collecting heater 100 for the solar thermal power generation system is used, as the disc type heat collecting heater 100 for the solar thermal power generation system can collect solar energy to form a conical light spot, the sunlight entering the heat collecting cavity has an inclination angle, one part of the solar energy entering the heat collecting cavity falls on the air inlet air collecting chamber 41 to heat the heat conducting working medium in the air inlet air collecting chamber 41, and then the other part of the solar energy falls on the heating pipe 1 connected with the air inlet air collecting chamber 41 to heat the heat conducting working medium in the heating pipe 1, and as the heat conducting working medium is heated in the air inlet air collecting chamber 41, the solar energy entering the heat collecting cavity can secondarily heat the heat conducting working medium in the heating pipe 1, so that the heat collecting efficiency and the heating temperature of the disc type heat collecting heater 100 for the solar thermal power generation system are improved, and the loss of the heat energy is reduced.
It should be noted that the heat conducting working medium adopted in this embodiment is supercritical carbon dioxide.
Specifically, the critical pressure of the supercritical carbon dioxide is as high as 7.38MPa, the system pressure of the supercritical carbon dioxide can be as high as more than 15MPA (far higher than the critical pressure of the supercritical carbon dioxide of 7.38 MPa), and the temperature can also be as high as more than 700 ℃. The density of the supercritical carbon dioxide exceeds 220kg/m 3 Its density is close to that of liquid, however its flow pressure loss is equivalent to that of gas, and its specific heat capacity is up to 1.25kj/kg. deg.C. Therefore, the supercritical carbon dioxide has the advantages of high density, high density of carried heat energy and small flow loss. Is an ideal medium for transmitting and storing heat energy. The application of supercritical carbon dioxide as a heat-conducting working medium in the disc type heat collection heater 100 for the solar thermal power generation system is an effective technical approach for realizing solar thermal high-temperature transportation and high-temperature storage and further realizing solar thermal high-temperature high-efficiency power generation.
For comparison, the air pressure in a typical air turbine is about 1.5MPa, corresponding to an air density of 19.35kg/m 3 The specific heat capacity is 1.05kj/kg. ℃. The heat energy carried by the supercritical carbon dioxide is 13.5 times that of the air. The pipe diameter of the supercritical carbon dioxide used when the same heat energy is transmitted is about 1/4 of the diameter of the air pipe, for example: for a model of 100m 2 The diameter of the air conduit required for the concentrator dish system is about phi 90mm, while the diameter of the supercritical carbon dioxide conduit is phi 25. This can greatly reduce the heat conduction loss. Saving steel and heat insulating material. The thermal conductivity of the supercritical carbon dioxide is 0.15w/m DEG C,the heat conductivity of the air is 0.245w/m DEG C, which has a certain influence on the heat transfer zone, but because the density of the supercritical carbon dioxide is far greater than that of the air, the Reynolds number of the supercritical carbon dioxide is far greater than that of the air under the condition of the same structure, and the comprehensive heat exchange capacity of the supercritical carbon dioxide is greater than that of the air. The viscosity of the supercritical carbon dioxide is about 0.22 x 10 5 pa.s, viscosity of air 1.9 x 10 5 pa.s, the viscosity of the supercritical carbon dioxide is slightly higher than that of air, and the pressure loss can be effectively reduced by adopting a smaller air flow speed.
In the present embodiment, the light-gathering port 8 has a circular shape.
In the present embodiment, the light-condensing area defined by the edge of the light-condensing opening 8 refers to an area defined by the edges of the light-condensing opening 8 extending in the axial direction. Of course, in other embodiments, the light-gathering area defined by the edges of the light-gathering openings 8 refers to the area defined by the edges of the light-gathering openings 8 extending radially outward.
It will be appreciated that the inlet plenum 41 is located outside the region enclosed by the edges of the light collection port 8 extending axially.
In the present embodiment, the plurality of heating pipes 1 together form an annular structure, and the plurality of heating pipes 1 are all symmetrically disposed and uniformly arranged along the center line of the housing 2.
All the parts of the heating pipes 1 connected with the air inlet collection chambers 41 are continuously and uniformly bent towards the directions far away from each other. An included angle is formed between the section of the heating pipe 1 provided with the air inlet collection chamber 41 and the other sections of the heating pipe 1, and when sunlight can irradiate the other sections of the heating pipe 1, part of the sunlight can be reflected on the section of the heating pipe 1 provided with the air inlet collection chamber 41.
Specifically, the heat collecting tube in this embodiment is a high temperature alloy tube.
More, the shape of each heating tube 1 is the same.
In order to obtain the maximum heating surface, the uniform gap between the adjacent heating pipes 1 must be ensured, the close arrangement of the plurality of heating pipes 1 along the circumferential direction can be realized, the gap between the adjacent heating pipes 1 can be reduced to the minimum, the light energy leakage in the gap is reduced, and the high-density energy on the heating surface is utilized to heat the heat-conducting working medium to the maximum extent.
In the present embodiment, the gap between two adjacent heating tubes 1 ranges from 0.05mm to 0.1 mm. Specifically, the gap between two adjacent heating pipes 1 may be 0.05mm, 0.07mm, or 0.09mm, etc. And is not particularly limited herein.
More, heating pipe 1 is the continuous smooth curved shape of multistage. The heating pipe 1 of the continuous smooth crooked of multistage can prolong the runner on the one hand, promote the heat conduction working medium in the runner to thermal absorption, on the other hand, the close packing heating pipe 1 of the continuous smooth crooked form of multistage is structurally owing to can fully release inside thermal expansion stress, and between adjacent heating pipe 1 because the zigzag form contacts between each other the supporting effect better under high temperature for whole heating pipe 1 structure is more stable, can resist the deformation that high temperature high pressure medium brought effectively.
Specifically, the heating pipe 1 and the intake plenum 41 are welded.
In order to guide the heat-conducting working medium and increase the turbulence and the heat transfer area, so as to achieve the purpose of enhancing heat transfer, the disc heat collection heater 100 for the solar thermal power generation system further comprises a plurality of flow deflectors 9, the plurality of flow deflectors 9 are arranged in the air intake collection chamber 41 at intervals, and the design of the plurality of flow deflectors 9 enables the heat-conducting working medium to flow in a turbulent state, so that the heat energy of the air intake collection chamber 41 can be absorbed more effectively.
In this embodiment, the air intake collection chamber 41 is annular, two side walls of the air intake collection chamber 41 are both connected with the flow deflectors 9, and the flow deflectors 9 located on different side walls are arranged in a staggered manner.
More, the guide vanes 9 are arranged along the circumferential direction of the intake plenum 41.
The baffle 9 is arranged inside the air inlet collection chamber 41, so that the strength and rigidity of the air inlet collection chamber 41 can be increased, and the high pressure resistance requirement can be met.
In the present embodiment, the guide vane 9 is annular. In other embodiments, the guide vanes 9 may also be helical. And is not particularly limited herein.
In addition, the disc type heat collecting heater 100 for the solar thermal power generation system further includes a flow control valve 6, and the flow control valve 6 is disposed at the air inlet pipe 42. The flow regulating valve 6 regulates the flow of the heat conducting working medium to adapt to different working conditions and meet the temperature requirement of the output working medium.
Specifically, when the solar light intensity changes, the light energy entering the light gathering port 8 changes, so that the temperature of the working medium outlet changes, the flow of the working medium is increased or decreased through the flow adjusting valve 6, the temperature of the working medium at the outlet can be decreased or increased, and the temperature constancy is ensured. Or when the temperature of the working medium required by the system is changed, the requirement of output temperature can be met by adjusting the flow regulating valve 6.
In the present embodiment, the flow rate adjustment valve 6 is a proportional type high-pressure flow rate adjustment valve.
In this embodiment, the disc type heat collecting heater 100 for the solar thermal power generation system further includes an air outlet assembly 5, the air outlet assembly 5 is located in a light gathering area surrounded by the edge of the light gathering port 8, and the air outlet assembly 5 is connected to the heating pipe 1.
Specifically, the air outlet assembly 5 comprises an air outlet plenum chamber 51 and an air outlet pipe 52, the air outlet plenum chamber 51 is connected with all the heating pipes 1, and the air outlet plenum chamber 51 is connected with the air outlet pipe 52.
More, the gas outlet chamber 51 and the heating pipe 1 are welded.
Besides, the housing 2 includes a front baffle 22, a bottom plate 21 and a side plate 23, one side edge of the side plate 23 is connected to the front baffle 22, the other side edge of the side plate 23 is connected to the bottom plate 21, the light gathering port 8 is disposed on the front baffle 22, and the air outlet pipe 52 penetrates through the bottom plate 21.
The front baffle 22 is provided with a connection hole in which one end of the adapter section connected to one end of the intake plenum 41 is disposed.
More, the adapter section connected with one end of the intake air collecting chamber 41 is connected by welding.
Specifically, the air outlet collection chamber 51 is mounted on the bottom plate 21 through a fixing bolt 7, the air inlet pipe 42 is mounted on the side plate 23 through the fixing bolt 7, the air inlet pipe 42 penetrates through the side plate 23, and the heating pipe 1 is supported in a connecting hole of the front baffle 22 through a switching section. The mounting structure can allow the heating pipe 1, the air inlet collection chamber 41 and the air outlet collection chamber 51 to move along the axial direction under the high-temperature working condition, so that the thermal stress is reduced.
In the present embodiment, the housing 2 is of a cylindrical configuration.
It should be further noted that, in order to reduce the energy loss of the disc type heat collecting heater 100 for the solar thermal power generation system, the disc type heat collecting heater 100 for the solar thermal power generation system further includes a heat insulating layer 3, and the heat insulating layer 3 is disposed between the outer shell 2 and the heating pipe 1.
In this embodiment, it can be known from theoretical analysis and experiments that the focusing light spot of the disc-type heat collection heater is an approximately conical light spot, and in order to obtain higher heat collection efficiency, the axis of the conical light spot should coincide with the axis of the disc-type heat collection heater (i.e., the light collection central axis), the small end face of the cone is located at the light collection port 8, and the large end face of the cone is located in the heat collection cavity. The light energy density at the center of the light spot is the largest, and the light energy density is correspondingly reduced along with the increase of the radius of the conical light spot, so that the whole air intake collection chamber 41 in the embodiment is of a concave cylindrical structure relative to the light gathering port 8, the whole body formed by the plurality of heating pipes 1 is of a conical structure, after the light spot passes through the light gathering port 8, most of light energy is absorbed by the air intake collection chamber 41 and the plurality of heating pipes 1 on the whole, and the energy of the light spot is prevented from escaping from the light gathering port 8 again to the greatest extent.
The heat absorbing surface of the ideal disc type heat collecting heater is arranged at the large end surface and has a certain conical inclination angle, and the ideal disc type heat collecting heater is called a first heat receiving surface. In fact, a part of the light energy entering the light gathering port 8 falls on the cylindrical surface between the light gathering port 8 and the first heated surface, namely, the side wall of the cylindrical light gathering area surrounded by the edge of the light gathering port 8 mentioned in this embodiment and the outside of the cylindrical light gathering area, which is called the second heated surface. Meanwhile, due to the reflection action, part of solar energy irradiated on the first heated surface is reflected to the second heated surface, and part of solar energy irradiated on the second heated surface is reflected on the first heated surface. The light energy entering the light gathering port 8 heats the heat conducting working medium into effective heat energy through the two heat absorbing surfaces. Meanwhile, because the temperature of the heat absorbing surface of the heat absorber is very high, if the actually measured temperature of the first heating surface is as high as 900 ℃, and the actually measured temperature of the second heating surface (on which the air inlet collection chamber 41 is mainly arranged) is as high as 800 ℃, one part of heat energy is radiated into the air through the light gathering port 8, the other part of heat energy is radiated into the air through the heat insulation layer 3 and the shell 2, and the two parts are ineffective heat energy. Therefore, the ideal heat absorber structure should increase the effective heat energy and reduce the ineffective heat energy as much as possible. In the disc-type heat collection heater 100 for the solar thermal power generation system provided by this embodiment, the air intake chamber 41 is disposed on the second heating surface, the heating pipe 1 is disposed on the first heating surface and the second heating surface at the same time, and the heat conducting medium is heated by using the first heating surface and the second heating surface, so that the heat collection efficiency of the disc-type heat collection heater 100 for the solar thermal power generation system is significantly improved.
More, the included angle between the extension line of the heating pipe 1 and the central axis is 60-80 degrees, and the facula half-cone angle (the included angle between the generatrix and the central axis) is about 40-70 degrees. When the angle is satisfied, on one hand, the escape of the light energy from the light-gathering port 8 can be reduced as much as possible, and on the other hand, the structure of the heating section is relatively stable. It should be further noted that the heating pipe 1, the air inlet chamber 41, the air outlet chamber 51, the air inlet pipe 42, and the air outlet pipe 52 provided in this embodiment are all made of high-strength high-temperature alloy materials. Specifically, incnel625 nickel-base superalloy may be employed.
In the present embodiment, the diameter d of the light-gathering port 8 0 The inner diameter d of the intake plenum 41 1 The characteristic length (i.e. the axial distance from the light-gathering port 8 to the joint surface between the first heating surface and the second heating surface) L of the heat-collecting cavity needs to satisfy the following formula:
tga=（d 1 -d 0 ）/L
wherein a is the characteristic angle of the reflected light of the condenser, namely the included angle between the reflected light of the condenser and the central axis, and the diameter of the light-gathering opening 8 of the heat-collecting heater is d 0 The inner diameter of the air inlet collection chamber 41 is d 1 The characteristic length of the heat collecting cavity is L.
The specific calculation process is as follows:
(1) Determining the output heat Q of the heat collecting heater and the working medium outlet temperature t of the heat collecting heater 2 Inlet temperature t of working medium 0 ；
Wherein the parameters are determined according to the user target.
(2) Determining the flow m of the working medium according to the following formula:
m=Q/(C P （t 2 -t 0 ） （1）
in the formula C P : working medium specific heat.
(3) The condenser effective area a is determined as follows:
A= Q/（η 1 η 2 I） （2）
in the formula: eta 1 The light-gathering efficiency is generally 0.89-0.93; eta 2 The efficiency of the heat collector is generally 0.94-0.98; i: solar light intensity (DNI).
(4) The concentrator opening diameter D is determined as follows:
D=（4 ΦA/π） 0.5 （3）
in the formula: phi: the influence factor coefficients of the lens gap of the condenser and the sunlight shielding are considered, and the value is generally 1.1-1.3; the structural design of the condenser can be carried out after the diameter of the condenser opening is determined.
(5) The characteristic angle α of reflected light is determined as follows:
tgα= （4D/p）/（4-（D/p） 2 ） （4）
in the formula: p is condenser focal length: and (4) determining the structural design of the condenser.
(6) After the structural design of the condenser is determined, the energy density distribution of a focusing light spot and each point of the light spot can be calculated according to a Monte Carlo ray tracing method, the light energy density of any point on a finite sphere taking a focus as a center can be calculated through the Monte Carlo ray tracing method, the light energy density distribution on a finite plane or a curved surface is given, the approximate light spot diameter on the focal plane is given, and the distribution map of a constant energy density plane is given.
(7) Designing the key structure size of the heat collecting heater and determining the diameter d of the light condensing port 0 The inner diameter d of the intake plenum 41 1 Characteristic length L of heat collection cavity: (axial distance from the light-gathering port to the junction surface of the first and second heated surfaces).
In addition, the heating pipe 1, the air inlet collection chamber 41 and the air outlet collection chamber 51 are designed into an integral welding structure with high pressure resistance, and a plurality of flow deflectors 9 are welded inside the air inlet collection chamber 41, so that heat transfer is enhanced, and strength and rigidity are increased.
As an optimization result, for 80-100 m 2 The disc type heat collecting heater 100 is used for a solar thermal power generation system, the diameter of a light collecting port 8 is 220-240 mm, the distance between the light collecting port 8 and a heating pipe 1 is 250-400 mm, the diameter of the inner wall of an air inlet collection chamber 41 is 370-380 mm, the diameter of the outer wall of the air inlet collection chamber 41 is 430-440, the wall thickness is 6-10 mm, the number of the heating pipes 1 is 40-60, the pipe diameter phi of the heating pipe 1 is 4-phi 6mm, the wall thickness is 0.8-1.2 mm, and the diameter of a shell 2 is 550-650. The temperature of the heat conducting working medium is 20-100 ℃. The temperature of the working medium heated by the air inlet collection chamber 41 is 380-500 ℃, the temperature of the working medium heated by the heating pipe 1 for the second time is 700-800 ℃, the average temperature of the wall surface of the air inlet collection chamber 41 is 350-450 (the highest 600 ℃), the average temperature of the heating pipe 1 is 600-700 ℃ (the highest 900 ℃), and compared with the prior structure, the temperature of the wall surface of the air inlet collection chamber 41 is reduced by 200 ℃.
The embodiment also provides a design method of a disc type heat collecting heater for a solar thermal power generation system, which is used for designing the above mentioned disc type heat collecting heater for the solar thermal power generation system, and the design method comprises the following steps:
(1) Determining the output heat Q of the heat collection heater and the working medium outlet temperature t of the heat collection heater 2 Inlet temperature t of working medium 0 ；
Wherein the parameters are determined according to the user target.
(2) Determining the flow m of the working medium according to the following formula:
m=Q/(C P （t 2 -t 0 ） （1）
in the formula C P : specific heat of working medium.
(3) The condenser effective area a is determined as follows:
A= Q/（η 1 η 2 I） （2）
in the formula: eta 1 The light-gathering efficiency is generally 0.89-0.93; eta 2 Collector efficiency, generally 094-0.98; i: solar light intensity (DNI).
(4) The concentrator opening diameter D is determined as follows:
D=（4 ΦA/π） 0.5 （3）
in the formula: phi: the influence factor coefficients of the lens gap of the condenser and the sunlight shielding are considered, and the value is generally 1.1-1.3; the structural design of the condenser can be carried out after the diameter of the condenser opening is determined.
(5) The characteristic angle α of the reflected light is determined as follows:
tgα= （4D/p）/（4-（D/p） 2 ） （4）
in the formula: p is condenser focal length: and (4) determining the structural design of the condenser.
(6) After the structural design of the condenser is determined, the energy density distribution of a focusing light spot and each point of the light spot can be calculated according to a Monte Carlo ray tracing method, the light energy density of any point on a finite sphere taking a focus as a center can be calculated through the Monte Carlo ray tracing method, the light energy density distribution on a finite plane or a curved surface is given, the approximate light spot diameter on the focal plane is given, and the distribution map of a constant energy density plane is given.
(7) Designing the key structure size of the heat collecting heater and determining the diameter d of the light condensing port 0 The inner diameter d of the intake plenum 41 1 The characteristic length L of the heat collecting cavity (the axial distance from the light gathering port to the joint surface of the first heating surface and the second heating surface).
(8) Calculating a characteristic angle a of the heat collector (namely an included angle between an extension line of the heating pipe 1 and the central axis) according to the following formula;
tga=（d 1 -d 0 ）/L （5）
(9) The initial design can take a = alpha and the diameter d of the light-gathering opening 0 May be determined with reference to the condenser spot calculation.
(10) Designing other structural parameters of the heat collector;
(11) Calculating the heat exchange quantity Q of the second and first heating surfaces by the following formula 1 、Q 2 And t 1 ；
Q 1 = m CP 1 （t 1 -t 0 ） （6）
Q 2 = mCP 2 （t 2 -t 1 ） （7）
Q 1 +Q 2 =Q （8）
In the formula: CP (CP) 1 、CP 2 T is the specific heat of the working fluid (note that although the working fluid is the same, the specific heat will be different due to different temperatures), t 1 The temperature of the working medium at the outlet of the second heating surface.
(12) Calculating the average temperature T of the second and first heating surfaces 1 、T 2 ；
Q 1 =A 1 *α 1 (T 1 -（t 0 +t 1 ）/2) （9）
Q 2 =A 2 *α 2 (T 2 -(t 1 +t 2 ）/2) （10）
In the formula: a. The 1 、A 2 The second heating surface and the first heating surface are opposite to the heat exchange area, alpha 1 、α 2 The average heat exchange coefficient of the second heating surface and the first heating surface is shown.
(13) Calculating the heat energy loss Q of the second heating surface and the first heating surface s1 、Q s2 ；
Q s1 =ε 1 σ A 1 *Ψ s1 (T 1 4 -T 4 c )+A 1 *λ 1 L 1 (T 1 -T c ) （11）
Q s2 =ε 2 σ A 2 *Ψ s2 (T 2 4 -T 4 c )+A 2 *λ 2 L 2 (T 2 -T c ) （12）
In the formula: epsilon 1 、ε 2 Gray scale of the second heated surface, the first heated surface s1 、Ψ s2 The angle coefficients of the second heating surface and the first heating surface to the light gathering port are lambda 1 、λ 2 Is a heat-insulating materialThermal conductivity of (D), L 1 、L 2 Is the thickness of the heat insulating material, T c Is the ambient temperature and σ is the thermal radiation constant.
(14) The total heat energy loss is:
Q s =Q s1 +Q s2 （13）
(15) Readjusting the structural parameters of the heat collector, and repeating the calculation processes (12) to (15) to obtain new heat energy loss Q s 。
(16) After multiple design calculations, multiple calculation results can be obtained, and a group with the minimum heat loss is selected to determine the structural parameters of the heat collector.
The disc type heat collecting heater 100 for the solar thermal power generation system provided by the embodiment has at least the following advantages:
the disc type heat collecting heater used for the solar thermal power generation system in the prior art is directly connected with an engine, but cannot store energy and continuously generate power. In order to solve the above problems, high temperature heat energy must be collected and conducted to the ground, but the collection and conduction of high temperature heat energy to the ground causes a great loss of heat energy. In order to reduce the heat energy consumption, two methods are generally adopted, one is to adopt high-performance heat insulation materials. The other is to use a high-temperature heat pipe with a smaller diameter, namely to increase the heat flux density of the heat transfer pipe. However, the reduction in the diameter of the heat conductive pipe increases the flow rate, resulting in an increase in pressure loss. Neither method can improve the heat collection efficiency well. In order to solve the technical problem, the solution adopted by the embodiment is as follows: firstly, a high-temperature-resistant and high-pressure-resistant high-efficiency heat collector is adopted for high-efficiency collection of heat energy. And secondly, supercritical carbon dioxide with special performance is used as a heat-conducting medium to realize high-temperature and high-efficiency transmission of heat energy. When the disc type heat collection heater 100 for the solar thermal power generation system is used, as the disc type heat collection heater 100 for the solar thermal power generation system can collect solar energy to form a conical light spot, the sunlight entering the heat collection cavity has an inclination angle, a part of the solar energy entering the heat collection cavity falls on the air inlet collection chamber 41 to heat the heat conducting working medium in the air inlet collection chamber 41, and then the other part of the solar energy falls on the heating pipe 1 connected with the air inlet collection chamber 41 to heat the heat conducting working medium in the heating pipe 1, and as the heat conducting working medium is heated in the air inlet collection chamber 41, the solar energy entering the heat collection cavity can carry out secondary heating on the heat conducting working medium in the heating pipe 1. Meanwhile, due to the reflection action, a part of solar energy irradiated on the first heating surface is reflected to the second heating surface, and a part of solar energy irradiated on the second heating surface is also reflected on the first heating surface, so that the heat collection efficiency and the heating temperature of the disc type heat collection heater 100 for the solar thermal power generation system are improved, and the loss of heat energy is reduced.
The disc type heat collecting heater 100 for the solar thermal power generation system is integrally arranged on a mounting arm near the focus of a condenser and tracks the movement of the sun along with the condenser, solar energy collected by the condenser enters a heat collecting cavity through a light collecting port 8 to heat supercritical carbon dioxide in an air inlet collecting chamber 41 and a heating pipe 1, and finally the heated supercritical carbon dioxide is led out through an air outlet collecting chamber 51 and an air outlet pipe 52.
According to the disc type heat collection heater 100 for the solar thermal power generation system, the second heating surface is arranged at the position close to the light gathering port 8, the first heating surface is arranged at the position close to the air outlet assembly 5, the advantage of high energy density at the rear section is fully utilized for high-temperature heating, and the arrangement that the temperature at the front section is low and the temperature at the rear section is high can effectively reduce the loss of light energy escaping from the light gathering port 8.
When the disc type heat collection heater 100 for the solar thermal power generation system is used, when the solar light intensity changes, the light energy entering the light gathering port 8 changes, so that the temperature of the working medium outlet changes, the flow of the working medium is increased or decreased through the flow adjusting valve 6, the temperature of the working medium at the outlet can be decreased or increased, and the constant temperature is ensured. Or when the temperature of the working medium required by the system is changed, the requirement of output temperature can be met by adjusting the flow regulating valve 6.
In summary, the embodiment of the present invention provides a disc heat collecting heater 100 for a solar thermal power generation system and a design method thereof, the disc heat collecting heater 100 for the solar thermal power generation system includes a housing 2, a plurality of heating pipes 1, an air intake collection chamber 41 and an air intake pipe 42, the housing 2 is provided with a heat collection chamber and a light gathering port 8, the heat collection chamber is communicated with the light gathering port 8, the plurality of heating pipes 1 are uniformly arranged in the heat collection chamber along a circumferential direction, the air intake collection chamber 41 is connected with all the heating pipes 1, the air intake collection chamber 41 is located outside a light gathering area surrounded by edges of the light gathering port 8, the air intake collection chamber 41 is used for primarily heating a heat conducting working medium and conveying the heat conducting working medium to the heating pipes 1, the air intake pipe 42 is connected with the air intake collection chamber 41, solar energy enters the heat collection chamber through the light gathering port 8 and heats the heat conducting working medium in the air intake collection chamber 41 and the heating pipes 1. When the disc type heat collecting heater 100 for the solar thermal power generation system is used, as the disc type heat collecting heater 100 for the solar thermal power generation system can collect solar energy to form a conical light spot, sunlight entering a heat collecting cavity has an inclination angle, one part of the solar energy entering the heat collecting cavity falls on the air inlet collection chamber 41 to heat a heat conducting working medium in the air inlet collection chamber 41, and the other part of the solar energy falls on the heating pipe 1 connected with the air inlet collection chamber 41 to heat the heat conducting working medium in the heating pipe 1, and as the heat conducting working medium is heated in the air inlet collection chamber 41, the solar energy entering the heat collecting cavity can carry out secondary heating on the heat conducting working medium in the heating pipe 1. Meanwhile, due to the reflection action, a part of solar energy irradiated on the first heating surface is reflected to the second heating surface, and a part of solar energy irradiated on the second heating surface is also reflected on the first heating surface, so that the heat collection efficiency and the heat collection temperature of the disc type heat collection heater 100 for the solar thermal power generation system are improved, and the loss of heat energy is reduced.
According to the design method of the disc type heat collecting heater for the solar thermal power generation system, through multiple times of design calculation, an optimal structure of the disc type heat collecting heater can be designed after a group of data with the minimum heat loss is selected.
The above description is only for the specific embodiment of the present invention, but the scope of the present invention is not limited thereto, and any changes or substitutions that can be easily conceived by those skilled in the art within the technical scope of the present invention are included in the scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the claims.
Claims (13)
1. A dish heat collection heater for a solar thermal power generation system, comprising:
the solar heat collector comprises a shell (2), wherein the shell (2) is provided with a heat collecting cavity and a light gathering port (8), and the heat collecting cavity is communicated with the light gathering port (8);
the heating pipes (1) are uniformly arranged in the heat collection cavity along the circumferential direction;
the air inlet collection chamber (41) is connected with all the heating pipes (1), the air inlet collection chamber (41) is positioned outside a light gathering area surrounded by the edge of the light gathering port (8), and the air inlet collection chamber (41) is used for primarily heating a heat conduction working medium and conveying the heat conduction working medium to the heating pipes (1);
the air inlet pipe (42), the air inlet pipe (42) is connected with the air inlet collection chamber (41);
solar energy enters the heat collection cavity through the light gathering port (8) and heats the air inlet collection chamber (41) and the heat conducting working medium in the heating pipe (1).
2. The dish type heat collecting heater for solar thermal power generation system according to claim 1, wherein the plurality of heating pipes (1) together form a ring structure, and the plurality of heating pipes (1) are all symmetrically arranged and uniformly arranged along the center line of the outer shell (2).
3. The dish-type heat collection heater for a solar thermal power generation system according to claim 2, wherein all the portions of the heating pipe (1) to which the inlet plenum (41) is connected are continuously and uniformly curved toward directions away from each other.
4. The dish type heat collecting heater for solar thermal power generation system according to claim 2, wherein the gap between two adjacent heating pipes (1) ranges from 0.05mm to 0.1 mm.
5. The dish heat collection heater for a solar thermal power generation system according to claim 1, wherein the dish heat collection heater (100) further comprises a plurality of flow deflectors (9), and the plurality of flow deflectors (9) are arranged in the air intake chamber (41) at intervals.
6. The dish-type heat collection heater for the solar thermal power generation system according to claim 5, wherein the air inlet collection chamber (41) is annular, two side walls of the air inlet collection chamber (41) are both connected with the flow deflectors (9), and the flow deflectors (9) on different side walls are arranged in a staggered manner.
7. The dish type heat collecting heater for a solar thermal power generation system according to claim 1, wherein the dish type heat collecting heater (100) further comprises a flow regulating valve (6), and the flow regulating valve (6) is disposed at the air inlet pipe (42).
8. The dish type heat collecting heater for the solar thermal power generation system according to claim 1, wherein the dish type heat collecting heater (100) further comprises an air outlet component (5), the air outlet component (5) is located in a light gathering area surrounded by the edge of the light gathering port (8), and the air outlet component (5) is connected with the heating pipe (1).
9. The dish-type heat collection heater for the solar thermal power generation system according to claim 8, wherein the air outlet assembly (5) comprises an air outlet collection chamber (51) and an air outlet pipe (52), the air outlet collection chamber (51) is connected with all the heating pipes (1), and the air outlet collection chamber (51) is connected with the air outlet pipe (52).
10. The dish type heat collecting heater for solar thermal power generation system according to claim 9, wherein the outer shell (2) comprises a front baffle (22), a bottom plate (21) and a side plate (23), one side edge of the side plate (23) is connected with the front baffle (22), the other side edge of the side plate (23) is connected with the bottom plate (21), the light gathering port (8) is arranged on the front baffle (22), and the air outlet pipe (52) penetrates through the bottom plate (21).
11. The dish type heat collecting heater for a solar thermal power generation system according to claim 10, wherein the front baffle (22) is provided with a connection hole, and one end of the adapting section connected with one end of the air intake collection chamber (41) is disposed in the connection hole.
12. The dish type heat collecting heater for a solar thermal power generation system according to any one of claims 1 to 11, wherein the dish type heat collecting heater (100) for a solar thermal power generation system further comprises a heat insulating layer (3), and the heat insulating layer (3) is disposed between the outer shell (2) and the heating pipe (1).
13. A design method of a dish type heat collecting heater for a solar thermal power generation system, which is used for designing the dish type heat collecting heater for the solar thermal power generation system according to any one of claims 1 to 12, and is characterized by comprising the following steps:
determining a characteristic angle alpha of the condenser;
determining the characteristic angle a of the disc type heat collection heater and the diameter d of the light-gathering opening (8) 0 ；
According to the characteristic angle alpha of a condenser, the characteristic angle a of the disc type heat collection heater and the diameter d of the light-gathering port (8) 0 Determining the characteristic length of the heat collection cavity and the inner diameter d of the air inlet collection chamber (41) 1 ；
Determining the total heat energy loss of the disc type heat collecting heater;
and circulating the steps to obtain a plurality of total heat losses, and selecting a group of data with the minimum total heat loss to determine the structural parameters of the disc type heat collection heater.
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Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| AU2001261344A1 (en) * | 2000-05-10 | 2001-11-20 | The Board Of Trustees Of The University Of Illinois | Interference suppression techniques |
| CN104006547A (en) * | 2013-02-26 | 2014-08-27 | 浙江同景科技有限公司 | Disc solar thermal power generation system heat collector |
| CN105066478A (en) * | 2015-08-31 | 2015-11-18 | 华南理工大学 | Circular-truncated-cone-shaped cavity type solar heat absorber with double-row multiple tubes |
| CN105222372A (en) * | 2015-11-10 | 2016-01-06 | 国网上海市电力公司 | Concentration solar generating machine and solar collector thereof |
| CN105423576A (en) * | 2015-12-19 | 2016-03-23 | 湖南科技大学 | Overheat protection device and overheat protection method of heat absorber for solar energy photothermal conversion |
-
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Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| AU2001261344A1 (en) * | 2000-05-10 | 2001-11-20 | The Board Of Trustees Of The University Of Illinois | Interference suppression techniques |
| CN104006547A (en) * | 2013-02-26 | 2014-08-27 | 浙江同景科技有限公司 | Disc solar thermal power generation system heat collector |
| CN105066478A (en) * | 2015-08-31 | 2015-11-18 | 华南理工大学 | Circular-truncated-cone-shaped cavity type solar heat absorber with double-row multiple tubes |
| CN105222372A (en) * | 2015-11-10 | 2016-01-06 | 国网上海市电力公司 | Concentration solar generating machine and solar collector thereof |
| CN105423576A (en) * | 2015-12-19 | 2016-03-23 | 湖南科技大学 | Overheat protection device and overheat protection method of heat absorber for solar energy photothermal conversion |
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