WO2024230040A1

WO2024230040A1 - Tower-shaped spiral solar receiver

Info

Publication number: WO2024230040A1
Application number: PCT/CN2023/119967
Authority: WO
Inventors: 凌祥; 王旭东; 汤显; 曹冲
Original assignee: 南京工业大学
Priority date: 2023-05-05
Filing date: 2023-09-20
Publication date: 2024-11-14

Abstract

Disclosed is a tower-shaped spiral solar receiver. The tower-shaped spiral solar receiver comprises a metal thermal collector plate, a metal bath cavity, a spiral coil pipe, an inlet flow-dividing manifold, an outlet flow-collecting manifold, etc. Sunlight is accurately focused on an outer plate of the metal thermal collector plate, the metal thermal collector plate absorbs heat to increase the temperature, and internal liquid metal is gasified and then condensed on an inner plate. Heat is unidirectionally transmitted to the metal bath cavity, then evenly transmitted to the spiral coil pipe at a high heat flux density after a heat absorption medium filled in the metal bath cavity is heated and melted, and taken away by a heat exchange medium in the spiral coil pipe. The heat exchange medium flows into the branch coil pipes through the inlet flow-dividing manifold and flows out after being converged in the outlet flow-collecting manifold. By using indirect heat transfer via a "metal bath" in the metal bath cavity, the present application features a high heat conductivity coefficient and temperature equalization, and can achieve efficient heat transfer, homogenize the heat flux density, reduce the thermal stress, and avoid harms such as pipe breaking. According to the present application, the heat exchange medium can be heated to a supercritical state, thus greatly improving the power generation efficiency.

Description

A tower type solar cyclone heat absorber

Technical Field

The invention belongs to the technical field of solar high-temperature heat utilization, and in particular relates to a tower-type solar cyclone heat absorber.

Background Art

With the rapid development of the economy, the demand for energy is increasing. At present, traditional fossil fuels are still the main driving force of global economic growth, but the carbon dioxide released after their combustion will seriously pollute the environment, and the energy crisis and global warming problems are becoming more and more serious. It is crucial to improve the energy structure and vigorously develop renewable clean energy, and the inexhaustible solar energy has received widespread attention. Compared with photovoltaic power generation, solar thermal power generation technology is cleaner in the raw material manufacturing process, and can be used with energy storage systems to generate electricity 24 hours a day. However, due to its low power generation efficiency and high power generation cost, how to improve the efficiency of solar thermal power generation and reduce costs has become a development problem. In the solar thermal power generation system, the tower solar thermal power generation system can achieve a higher operating temperature due to its high concentration ratio, thereby improving the overall power generation efficiency, and is more popular in the future development trend. As the core heat absorption component of the tower solar energy, the absorber reflects the concentrated sunlight directly on the heat absorption plate. It is easy to be heated unevenly under high heat flux load, resulting in dangers such as burst pipe leakage. How to ensure the stable and efficient operation of the absorber has become a key technical issue in the current tower solar thermal power generation system.

Summary of the invention

In view of the deficiencies in the prior art, the present invention provides a tower-type solar cyclone absorber, which has the advantages of unidirectional heat transfer, reduced heat dissipation, high light-to-heat conversion efficiency, uniform temperature, uniform heat, low thermal stress, heat storage and high pressure bearing capacity, and can heat the heat exchange medium to a supercritical or ultra-supercritical state, thereby greatly improving the operating parameters and power generation efficiency.

To achieve the above object, the present invention adopts the following technical solutions:

A tower solar cyclone heat absorber, characterized in that it comprises: a metal heat plate, a metal bath cavity, a spiral coil, an inlet shunt main pipe, an outlet collecting main pipe and a central tube; a plurality of metal heat plates are arranged around the metal bath cavity, a plurality of independent chambers are formed inside the metal heat plates, each chamber is filled with liquid metal, the liquid metal transfers the heat absorbed by the metal heat plate to the metal bath cavity through the process of gasification and condensation, and the metal bath cavity is filled with a heat absorbing medium; the spiral coil is wound around the central tube in a circumferential direction, the spiral coil is immersed in the heat absorbing medium, the outer wall of the spiral coil and the infiltration surface of the heat absorbing medium serve as heat transfer surfaces, the spiral coil flows into the heat exchange medium through the inlet shunt main pipe, and the heat exchange medium flows out through the outlet collecting main pipe.

To optimize the above technical solutions, the specific measures taken also include:

Furthermore, the metal hot plate includes a heat absorbing plate, a top plate on the hot plate, a bottom plate on the hot plate, an inner wall, a side sealing plate and a partition; the heat absorbing plate, the top plate on the hot plate, the bottom plate on the hot plate, the inner wall and the side sealing plate are spliced to form a sealed cavity, and a plurality of inclined partitions are evenly distributed in the sealed cavity and divide the sealed cavity into a plurality of independent chambers. The heat absorbing plate is used to absorb sunlight. The inner wall surface forms the heat absorbing wall surface of the metal bath cavity.

Furthermore, the metal bath cavity is formed by splicing an inner wall surface, a bath cavity upper cover plate, a bath cavity lower cover plate and a central tube. The bath cavity upper cover plate and the bath cavity lower cover plate are arranged opposite to each other, and both the bath cavity upper cover plate and the bath cavity lower cover plate are provided with holes corresponding to the spiral coil.

Furthermore, the spiral coil is welded and fixed to the upper cover plate of the bath chamber and the lower cover plate of the bath chamber, and the spiral coil is not in direct contact with the central tube.

Furthermore, the spiral coil is composed of a plurality of coil branches arranged in an arrangement, and the spiral coil is installed on the central tube through a limiting pad. The bottom of the limiting pad is axially fixed on the central tube, and the surface of the limiting pad is provided with a plurality of arc-shaped grooves corresponding to the plurality of coil branches, and the coil branches can be movably installed in the arc-shaped grooves.

Furthermore, the number of the spiral coils is more than one, and a plurality of spiral coils are stacked and wound circumferentially on the central tube, each group of spiral coils corresponds to a limiting pad, and the limiting pads are connected by flat pads.

Furthermore, the metal hot plate, the metal bath chamber and the spiral coil are made of P91 steel or P92 steel.

Furthermore, the heat absorbing medium is pure metal or mixed metal.

Furthermore, the heat exchange medium is water, purified and pressurized air, or purified and pressurized carbon dioxide.

Furthermore, the metal hot plate is designed by the following formula:

Where, ΔP _v is the pressure loss of metal vapor in the metal hot plate, μ _v is the dynamic viscosity of metal vapor in the metal hot plate, ρ _v is the density of metal vapor in the high-temperature hot plate, θ is the angle between the partition and the horizontal plane, L is the vertical distance between the two partitions, d is the distance between the heat absorbing plate and the inner wall, f is the Fanning drag coefficient, d _e is the equivalent diameter, and ξ is the local drag coefficient.

The beneficial effects of the present invention are:

1) The indirect and efficient heat transfer method is adopted to avoid direct sunlight exposure, solve the problems of thermal fatigue and thermal ratchet caused by thermal stress caused by direct heat transfer, and greatly extend the service life of the heat absorber;

2) A metal hot plate (high-temperature hot plate) is used to absorb and transfer heat, achieving one-way heat transfer, solving the problem of heat loss during heat transfer, and improving the light-to-heat conversion efficiency of the absorber; an innovative structure of a baffle and an independent cavity is proposed, and a specific design scheme for the metal hot plate is proposed, taking full account of the condensation and evaporation process of the liquid metal and the economic safety of the overall structure, and the Fanning formula is used to calculate and limit the various parameters in the metal hot plate;

3) The heat transfer medium with high thermal conductivity and the high specific surface area of the spiral coil can quickly transfer heat to the heat exchange medium; and the flowing heat absorbing medium can evenly transfer heat to the spiral coil, making the metal bath cavity have excellent Uniform temperature performance, able to withstand high heat flux density heat load. Different from the model formed by splicing multiple independent tube banks/heat exchange channels, the integrated heat absorbing medium makes the heat distribution more uniform;

4) The multi-tube and multi-layer spiral coils are arranged in parallel, which greatly improves the flux and heat transfer capacity of the heat exchange medium, and can effectively prevent the risk of local overheating and tube burst caused by rapid temperature rise; the low thermal stress technology is adopted, and the spiral coils are welded to the upper and lower cover plates, but not to the center tube, so that the spiral coils can expand and contract freely under heat, reducing thermal stress;

5) Limiting pads and flat pads that are compatible with the installation of the spiral coil are designed, so that the spiral coil can freely expand and contract in a high temperature environment, thereby significantly reducing thermal stress and improving the safety, reliability and service life of the equipment.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a schematic diagram of the appearance of a tower-type solar cyclone heat absorber of the present invention.

FIG. 2 is a top view of the tower-type solar cyclone heat absorber of the present invention.

FIG. 3 is a partial exploded schematic diagram of the metal hot plate of the present invention.

FIG. 4 is a schematic diagram of filling the liquid metal in the metal hot plate of the present invention.

FIG. 5 a is a schematic diagram of a coil branch pipe interface of the present invention.

FIG. 5 b is a schematic diagram of an inlet manifold and an outlet manifold of the present invention.

FIG. 6 is a partial exploded schematic diagram of the metal bath chamber of the present invention.

FIG. 7 a is a schematic diagram of a limiting pad strip and a protecting pad strip of the present invention.

FIG. 7 b is a schematic diagram of each coil branch pipe of the present invention being installed in a limiting pad.

FIG8 is a schematic diagram of the working process of the tower type solar cyclone heat absorber of the present invention.

FIG. 9 is a schematic diagram showing the change of sodium vapor flow loss in the independent chamber of the metal hot plate of the present invention with the inclination angle of the partition.

The accompanying drawings are marked as follows: 1. Metal hot plate; 1.1. Heat absorbing plate; 1.2. Upper cover plate of hot plate; 1.3. Lower cover plate of hot plate; 1.4. Inner wall surface; 1.5. Side sealing plate; 1.6. Partition; 2. Metal bath chamber; 2.1. Upper cover plate of bath chamber; 2.2. Lower cover plate of bath chamber; 3. Spiral coil; 3.1. Coil branch pipe; 4. Inlet diversion main pipe; 5. Outlet collecting main pipe; 6. Center tube; 6.1. Limiting pad; 6.2. Flat pad; 6.3. Arc groove; 7. Liquid metal; 8. Heat absorbing medium.

DETAILED DESCRIPTION

The present invention will now be described in further detail with reference to the accompanying drawings.

Embodiment 1

In this embodiment, a tower solar cyclone heat absorber as shown in FIG. 1 and FIG. 2 is proposed, which is composed of a metal heat plate 1, a metal bath chamber 2, a spiral coil 3, an inlet flow distribution main pipe 4, an outlet flow collection main pipe 5 and a central tube 6. The metal heat plates 1 are independent of each other, and multiple metal heat plates 1 are assembled in a circle. The sunlight is reflected by the heliostat field and concentrated on the heat absorbing plate 1.1 of the metal heat plate 1. The metal heat plate 1 absorbs the heat of the sunlight and transfers the heat to the metal bath chamber 2 in one direction, so that the heat filled in the metal bath chamber 2 The heat absorbing medium 8 inside heats up and melts, and then transfers the heat to the spiral coil 3. The spiral coil 3 is immersed in the heat absorbing medium 8, and the outer wall of the spiral coil 3 and the infiltration surface of the heat absorbing medium 8 serve as the heat transfer surface. The heat exchange medium flows into each spiral coil 3 through the inlet branch main pipe 4, and flows out after being gathered through the outlet collecting main pipe 5. The heat absorber of the present invention adopts an indirect heat transfer method, which can effectively solve the problems of thermal stress, thermal fatigue, etc. caused by the huge temperature difference caused by direct heat transfer.

As shown in Figures 3 and 4, the metal hot plate 1 is polygonal, and is composed of a heat absorbing plate 1.1, a cover plate 1.2 on the hot plate, a lower cover plate 1.3 on the hot plate, an inner wall surface 1.4, a side sealing plate 1.5 and a partition 1.6. The partition 1.6 divides the interior of the metal hot plate 1 into multiple independent chambers, and each chamber is evacuated and heated to maintain a high temperature environment and filled with liquid metal. The liquid metal can be pure metals such as potassium, sodium and lithium, but not limited to potassium, sodium and lithium, and metal mixtures. Sunlight is reflected on the heat absorbing plate 1.1, and the temperature rises after absorbing heat, so that the liquid metal inside the chamber is vaporized and then condensed on the inner wall surface 1.4. The liquid metal 7 in each chamber transfers heat to the inner wall surface 1.4 in a unidirectional and efficient manner through the cycle of evaporation, condensation and gravity reflux. The metal hot plate 1 used in the heat absorber of the present invention can transfer heat in one direction and reduce heat loss during heat transfer, and can effectively improve the light-heat conversion efficiency of the heat absorber.

As shown in FIG6 , the inner wall surfaces 1.1 of the plurality of metal hot plates 1 constitute an integral heat-absorbing wall surface of the metal bath cavity 2, and the heat-absorbing medium 8 can flow freely in the metal bath cavity 2, which has better stability and heat-dissipating performance during operation, and largely avoids the problem of uneven heating under high heat flux density load.

As shown in FIG6 , the metal bath chamber 2 is polygonal in shape, and is composed of an inner wall surface 1.4, a bath chamber upper cover plate 2.1, a bath chamber lower cover plate 2.2 and a central tube 6. The metal bath chamber 2 is filled with a heat absorbing medium 8. The heat absorbing medium 8 can be made of metal tin, aluminum, etc., but is not limited to tin, aluminum, other metals and metal mixtures. When the heat absorber is working, the metal melts, and the spiral coil 3 is immersed in the liquid metal. The outer wall of the tube and the wetted surface of the liquid metal are used as the heat transfer surface. The "metal bath" heat transfer method is adopted, which has the function of equalizing the temperature. On the one hand, the metal has a high thermal conductivity, which can stably enhance the heat exchange effect of the spiral coil 3; on the other hand, the flowing liquid metal can transfer heat evenly to the spiral coil 3, avoiding the concentrated sunlight directly reflected on the spiral coil 3 to cause local overheating and other hazards.

As shown in Fig. 5a, Fig. 5b, Fig. 7a and Fig. 7b, a new fixing structure is designed for the installation and support of the spiral coil 3 in this embodiment. In order to achieve efficient thermal stress management, low thermal stress technology is adopted, wherein the bath chamber upper cover plate 2.1 and the bath chamber lower cover plate 2.2 are both provided with holes matching the spiral coil 3, and the spiral coil 3 is fixed to the bath chamber upper cover plate 2.1 and the bath chamber lower cover plate 2.2 by welding, and at the same time avoids welding with the central tube 6, but by setting a limit pad 6.1 and a flat pad 6.2, the spiral coil 3 is limited to a relatively fixed position. The spiral coil 3 is composed of a plurality of coil branches 3.1 arranged in an arrangement, the bottom of the limit pad 6.1 is fixed to the central tube 6 along the axial direction, and the surface of the limit pad 6.1 is provided with a plurality of arc grooves 6.3 corresponding to the plurality of coil branches 3.1, and the coil branches 3.1 can be movably installed in the arc grooves 6.3. This design enables the spiral coil 3 to freely expand and contract in a high temperature environment, thereby significantly reducing thermal stress and improving the safety of the equipment. Reliability and service life.

As shown in Figures 5a, 5b, 6, 7a and 7b, the heat exchange medium under supercritical pressure enters each spiral coil 3 through the inlet shunt main pipe 4, and the generated supercritical state heat exchange medium flows out after being gathered through the outlet header 5. The overall pipeline sealing of the system and the materials of the pipeline have very strict standards. The metal hot plate 1, the metal bath chamber 2, the spiral coil 3, the inlet shunt main pipe 4 and the outlet header 5 are all made of existing high temperature resistant pressure bearing materials such as P91 and P92.

As shown in Figures 2, 6, 7a, 7b and 8, several coil branch interfaces (W1-Wn) are opened on the bath chamber upper cover plate 2.1 and the bath chamber lower cover plate 2.2, each interface is connected to a separate heat exchange medium flow channel, and each coil branch 3.1 constitutes a heat exchange medium flow channel return. The specific number of spiral coils can be increased or decreased according to actual needs. The spiral coil 3 is made of high thermal conductivity and high temperature and pressure resistant materials (including but not limited to P91, P92, etc.) to ensure efficient heat conduction. At the same time, the spiral shape of the spiral coil 3 can achieve enhanced heat exchange effect and improve the heat exchange efficiency between the heat absorbing fluid and the liquid metal in the metal bath chamber. The return of the heat exchange medium flow channel is limited in the limiting pad 6.1 and is separated from the return of the upper layer of the heat exchange medium flow channel by the flat pad 6.2, which enhances the stability of the spiral coil 3. The upper layer of flat pads 6.2 is directly fixed on the lower layer of limiting pads 6.1, and the bottom layer of limiting pads 6.1 is directly fixed on the central tube 6. The limiting pads 6.1 and the flat pads 6.2 are made of P91 or P92 high temperature resistant steel.

After the heat exchange medium enters each spiral coil from the inlet shunt main pipe 4, it flows in a swirl. The larger specific surface area of the spiral coil 3 and the unique swirl phenomenon formed by the heat exchange medium in the spiral coil 3 improve the heat transfer capacity of the heat exchange medium. In addition, the spiral structure can also realize the long-distance transfer of heat in the spiral coil 3, and improve the power generation efficiency of the heat exchange medium in the supercritical state. After absorbing heat, the heat exchange medium flows out from the outlet header 5. A part of it directly enters the expander to expand and drive the generator to generate electricity, and the other part cooperates with the energy storage system to store energy.

Embodiment 2

The tower solar cyclone absorber proposed in the first embodiment innovatively proposes a partition and an independent cavity structure in the metal hot plate 1, but the specific design scheme of the metal hot plate 1 is not limited to this, and it is also necessary to fully consider the condensation and evaporation process of the liquid metal 7 and the economic safety of the overall structure. Therefore, a design method for a metal hot plate is proposed in this embodiment, and various parameters in the metal hot plate 1 are calculated and limited.

Compared with traditional heat pipes, the steam of high-temperature metal hot plates flows in the thickness direction, the flow path is short, and the steam is all in the adiabatic section, and the wall boundary has little effect on the steam volume. According to different flow modes, laminar flow formula and turbulent flow formula can be selected.

The Hagen-Poiseuille formula is only used for laminar flow:

Where ΔP is the pressure drop, Pa; l is the pipe length, m; μ is the dynamic viscosity, N·s/m ² ; m is the mass flow rate, kg/s; A is the pipe cross-sectional area, mm ² ; R is the pipe radius, mm; ρ is the fluid density, kg/m ³ .

Fanning's formula applies to both laminar and turbulent flows:

Where ξ is the local resistance coefficient; d _e is the equivalent diameter, m; u is the fluid flow rate, m/s; f is the Fanning resistance coefficient, which is related to the Reynolds number Re. When Re＜2100, f＝16/Re, and when 2100＜Re＜10 ⁵ , f＝0.0791/Re ^0.25 .

Calculate the steam flow rate in the steam chamber as:

Where _mv is the mass flow rate of steam, kg/s; _ρv is the steam density, kg/m3; s is the heat transfer circumference of a single chamber, m.

The Fanning formula is used to calculate the steam flow loss in the steam chamber, and the steam pressure drop is:

In the above formula Each quantity is a fixed value under specific experimental conditions, so it can be regarded as a constant factor, denoted as K. Therefore, the above formula becomes:

Wherein, _ΔPv is the pressure loss of metal vapor in the metal hot plate, _μv is the dynamic viscosity of metal vapor in the metal hot plate, _ρv is the density of metal vapor in the high-temperature hot plate, θ is the inclination angle (i.e. the angle between the partition and the horizontal plane), L is the vertical distance between the two partitions, and d is the width of the metal hot plate (i.e. the distance between the heat absorbing plate and the inner wall).

Figure 9 shows the change of sodium vapor flow loss in the steam chamber with the inclination angle of the partition. As the inclination angle increases, the metal vapor flow pressure loss decreases. Theoretically, the inclination angle of the partition can be further increased, but when the angle is too large, the required manufacturing process requirements are greatly increased. Too large an angle will also affect the overall strength, and the demand for sodium filling will also increase, increasing the manufacturing cost and difficulty. Therefore, when designing a metal hot plate, calculation data analysis should be combined to ensure both the condensation and evaporation process of the liquid metal and the safety and economy of the overall structure.

It should be noted that the terms such as "upper", "lower", "left", "right", "front", "back", etc. cited in the invention are only for the convenience of description and are not used to limit the scope of implementation of the present invention. Changes or adjustments in their relative relationships should be regarded as the scope of implementation of the present invention without substantially changing the technical content.

The above are only preferred embodiments of the present invention, and the protection scope of the present invention is not limited to the above embodiments. All technical solutions under the concept of the present invention belong to the protection scope of the present invention. It should be pointed out that for ordinary technicians in this technical field, some improvements and modifications without departing from the principle of the present invention should be regarded as the protection scope of the present invention.

Claims

A tower solar cyclone heat absorber, characterized in that it comprises: a metal heat plate (1), a metal bath cavity (2), a spiral coil (3), an inlet flow distribution main pipe (4), an outlet flow collection main pipe (5) and a central tube (6); a plurality of metal heat plates (1) are arranged around the metal bath cavity (2), a plurality of independent chambers are formed inside the metal heat plates (1), each chamber is filled with liquid metal (7), the liquid metal (7) transfers the heat absorbed by the metal heat plate (1) to the metal bath cavity (2) through the process of gasification and condensation, and the metal bath cavity (2) is filled with a heat absorbing medium (8); the spiral coil (3) is wound around the central tube (6) in a circumferential direction, the spiral coil (3) is immersed in the heat absorbing medium (8), the outer wall of the spiral coil (3) and the infiltration surface of the heat absorbing medium (8) serve as heat transfer surfaces, the spiral coil (3) flows into the heat exchange medium through the inlet flow distribution main pipe (4), and flows out of the heat exchange medium through the outlet flow collection main pipe (5).
A tower solar cyclone absorber as claimed in claim 1, characterized in that: the metal hot plate (1) comprises a heat absorbing plate (1.1), a cover plate (1.2) on the hot plate, a lower cover plate (1.3) on the hot plate, an inner wall surface (1.4), a side sealing plate (1.5) and a partition plate (1.6); the heat absorbing plate (1.1), the cover plate (1.2) on the hot plate, the lower cover plate (1.3) on the hot plate, the inner wall surface (1.4) and the side sealing plate (1.5) are spliced to form a sealed cavity, a plurality of inclined partition plates (1.6) are evenly distributed in the sealed cavity and divide the sealed cavity into a plurality of independent chambers, the heat absorbing plate (1.1) is used to absorb heat from sunlight, and the inner wall surface (1.4) forms the heat absorbing wall surface of the metal bath cavity (2).
A tower-type solar cyclone absorber as described in claim 2, characterized in that: the metal bath chamber (2) is formed by splicing an inner wall surface (1.4), a bath chamber upper cover plate (2.1), a bath chamber lower cover plate (2.2) and a central tube (6), the bath chamber upper cover plate (2.1) and the bath chamber lower cover plate (2.2) are arranged opposite to each other, and the bath chamber upper cover plate (2.1) and the bath chamber lower cover plate (2.2) are both provided with holes corresponding to the spiral coil (3).
A tower type solar cyclone absorber as claimed in claim 3, characterized in that the spiral coil (3) is welded and fixed to the bath chamber upper cover plate (2.1) and the bath chamber lower cover plate (2.2), and the spiral coil (3) is not in direct contact with the central tube (6).
A tower solar cyclone heat absorber as described in claim 1, characterized in that: the spiral coil (3) is composed of a plurality of coil branches (3.1) arranged in an arrangement, the spiral coil (3) is installed on the central tube (6) through a limiting pad (6.1), the bottom of the limiting pad (6.1) is axially fixed to the central tube (6), the surface of the limiting pad (6.1) is provided with a plurality of arc grooves (6.3) corresponding to the plurality of coil branches (3.1), and the coil branches (3.1) can be movably installed in the arc grooves (6.3).
A tower-type solar cyclone heat absorber as described in claim 5, characterized in that: the number of the spiral coils (3) is more than one, and a plurality of spiral coils (3) are stacked and wound circumferentially on the central tube (6), each group of spiral coils (3) corresponds to a limiting pad (6.1), and the limiting pads (6.1) are connected by flat pads (6.2).
A tower type solar cyclone heat absorber as claimed in claim 1, characterized in that: the metal heat plate (1), The metal bath chamber (2) and the spiral coil (3) are made of P91 steel or P92 steel.
The tower type solar cyclone heat absorber according to claim 1, characterized in that the heat absorbing medium (8) is pure metal or mixed metal.
A tower solar cyclone heat absorber as described in claim 1, characterized in that the heat exchange medium is water, purified and pressurized air or purified and pressurized carbon dioxide.
A tower type solar cyclone heat absorber as claimed in claim 3, characterized in that: the metal heat plate (1) is designed according to the following formula:

Where, ΔP v is the pressure loss of metal vapor in the metal hot plate, μ v is the dynamic viscosity of metal vapor in the metal hot plate, ρ v is the density of metal vapor in the high-temperature hot plate, θ is the angle between the partition and the horizontal plane, L is the vertical distance between the two partitions, d is the distance between the heat absorbing plate and the inner wall, f is the Fanning drag coefficient, d e is the equivalent diameter, and ξ is the local drag coefficient.