CN111174618B

CN111174618B - Heat storage heat exchanger and fresh air system

Info

Publication number: CN111174618B
Application number: CN201911339873.4A
Authority: CN
Inventors: 刘志生; 付长春; 曹兆军; 李翠翠; 郭娟
Original assignee: Qingjian Group Co Ltd
Current assignee: Qingdao Construction Group Co.,Ltd.; Qingjian Group Co Ltd
Priority date: 2019-12-23
Filing date: 2019-12-23
Publication date: 2021-02-02
Anticipated expiration: 2039-12-23
Also published as: CN111174618A

Abstract

The invention provides a heat storage heat exchanger and a fresh air system, which comprise a heat source inlet, a heat source outlet, a cold source inlet, a cold source outlet and a shell, wherein a plurality of heat storage blocks are arranged in the shell of the heat exchanger, the heat storage blocks are stacked together, a first hole and a second hole are arranged in each heat storage block, the first holes and the second holes are not communicated with each other, the first holes of the heat storage blocks form communicated channels, the channels formed by the first holes are used for circulating a heat source, and the second holes form communicated channels for circulating a cold source; the cold source enters from the cold source inlet, passes through the second hole and then is discharged from the cold source outlet. The invention aims to provide a novel heat storage heat exchanger, which can independently store heat and exchange heat by virtue of a heat storage block, omits a heat exchange pipe and can further improve the heat storage and exchange effect.

Description

Heat storage heat exchanger and fresh air system

Technical Field

The invention belongs to the technical field of heat exchangers, and particularly relates to a heat storage heat exchanger and a fresh air system.

Background

With the continuous development of economy and the large consumption of energy sources, energy conservation becomes a global concern, the utilization of renewable energy sources such as solar energy, wind energy, geothermal energy and the like, industrial waste heat and waste heat becomes a key point for research and development of various countries, however, the energy sources have the characteristics of discontinuity and instability, and therefore, the research of an energy storage technology is particularly important. The heat storage technology is one of energy storage technologies, and an important ring in the heat storage technology is the design of a phase change heat storage heat exchanger. The common phase-change heat storage type heat exchanger is formed by sleeving two pipes together, and cold fluid and hot fluid respectively flow through an inner pipe and an outer pipe. The phase change heat storage material is packaged in the phase change heat storage unit with a certain shape and applied to the heat storage box, so that the occupied area of the conventional heat storage box can be reduced, and the defect of discontinuous utilization of waste heat, waste heat and solar energy can be overcome. The flat plate type heat exchanger is a heat exchanger with the highest heat exchange efficiency in various heat exchangers at present, and has the advantages of small occupied space and convenience in mounting and dismounting. The high-pressure resistant staggered circulation structure of the plate heat exchanger is formed by combining concave-convex lines between two adjacent plates in a vacuum welding mode, and the staggered circulation structure enables cold and hot fluid in the plate heat exchanger to generate strong turbulence to achieve a high heat exchange effect.

Solar energy is inexhaustible clean energy and has huge resource amount, and the total amount of solar radiation energy collected on the surface of the earth every year is 1 multiplied by 10¹⁸kW.h, which is ten thousand times of the total energy consumed in the world year. The utilization of solar energy has been used as an important item for the development of new energy in all countries of the world. However, the energy density of the solar radiation reaching the earth is small (about one kilowatt per square meter), and it is also smallIs discontinuous, which brings certain difficulties for large-scale development and utilization. Therefore, in order to widely use solar energy, not only the technical problems should be solved, but also it is necessary to be economically competitive with conventional energy sources.

Aiming at the structure of a heat collector, the prior art has been researched and developed a lot, but the heat collecting capability is not enough on the whole, and the problem that the operation time is long and scaling is easy to happen, so that the heat collecting effect is influenced.

In any form and structure of solar collector, there is an absorption component for absorbing solar radiation, and the structure of the collector plays an important role in absorbing solar energy.

Flat tubes have found widespread use in automotive air conditioning units and residential or commercial air conditioning heat exchangers in recent years. The flat tubes are provided with a plurality of small passages therein through which, in use, a heat exchange fluid flows. Because the flat tube heat exchange area is big, consequently can improve heat transfer effect greatly.

Column ribs: the addition of fins helps to increase the heat exchange area and can enhance the disturbance of the flow field. Enhanced heat exchange by the addition of fins has been widely used in heat exchangers. However, the design cannot consider the heat dissipation effect singly, and from the viewpoint of system economy, the situation that the heat dissipation improvement effect is extremely small due to the fact that the pressure drop is increased sharply after the fins are added is avoided as much as possible. And considering the relatively lower temperature when the refrigerant is imported, no rib is arranged in the central high-flow-velocity area so as to improve the pressure drop of the cold plate, and column ribs are arranged in the peripheral low-flow-velocity area so as to strengthen disturbance and increase the heat exchange area, thereby compensating the loss of the heat dissipation capacity caused by the temperature rise of the refrigerant.

The flow guide structure comprises: in order to avoid the flowing dead zone in the convective heat exchange process of the refrigerant and the cold plate, a baffle plate widely adopted in a heat exchanger is used for reference, a plurality of long and straight vertical plates are distributed in the cold plate to be used as a flow guide structure, and the flow direction of the refrigerant is changed in some areas of a flow field so as to improve the flow field distribution of the refrigerant in the cold plate.

For the above analysis, the following technical problems exist in the prior art: for the heat storage heat exchanger, the structure is complex, a heat exchange pipe needs to be arranged independently, and the heat utilization efficiency is low; the heat collecting efficiency of the heat collecting pipe is low; the new trend system needs to be improved.

Disclosure of Invention

The invention aims to provide a novel heat accumulator, a heat collector and a novel air system thereof, which improve the heat exchange performance.

In order to achieve the purpose, the technical scheme of the invention is as follows:

a heat storage heat exchanger comprises a heat source inlet, a heat source outlet, a cold source inlet, a cold source outlet and a shell, wherein a plurality of heat storage blocks are arranged in the shell of the heat exchanger, the heat storage blocks are stacked together, a first hole and a second hole are formed in each heat storage block, the first holes and the second holes are not communicated with each other, the first holes of the heat storage blocks form communicated channels, the channels formed by the first holes are used for circulating a heat source, and the second holes form communicated channels for circulating a cold source; the cold source enters from the cold source inlet, passes through the second hole and then is discharged from the cold source outlet.

Preferably, the heat storage block is a ceramic heat storage block.

The utility model provides a new trend system, includes heat collector, heat accumulation heat exchanger, cold source module, the heat collector absorbs solar energy, then transmits for heat accumulation material through heat accumulation heat exchanger, and the cold source module includes the cold source passageway, the cold source passageway carries out the heat transfer with heat accumulation material, gives the cold source in the cold source passageway with the heat transfer, the cold source be the air, the air heating after carry in the building room to form new trend system, its characterized in that, heat accumulation heat exchanger just preceding heat accumulation heat exchanger.

Preferably, the heat collector comprises a heat collecting tube and a reflecting mirror, the heat collecting tube is a flat tube, the lower flat surface of the flat tube is opposite to the reflecting surface of the reflecting mirror, the flat tube comprises a lower bottom plate and an upper cover, the upper cover and the bottom plate are assembled together to form a cavity of the flat tube, fluid flows in the cavity, the bottom plate comprises a plurality of heat exchange areas, each heat exchange area comprises a vertical plate and a column rib, and the vertical plate comprises a first vertical plate located in the center of the heat exchange area, a second vertical plate surrounding the first vertical plate and a third vertical plate surrounding the second vertical plate;

the first vertical plates comprise four, intervals are arranged between every two adjacent first vertical plates, the adjacent first vertical plates are in a vertical relation, and extension lines of the four first vertical plates form a first square;

the second vertical plates comprise four, intervals are arranged between every two adjacent second vertical plates, the adjacent second vertical plates are in a vertical relation, extension lines of the four second vertical plates form a second square, and the extension line of each first vertical plate passes through the middle points of the two second vertical plates;

the third vertical plates comprise four, intervals are arranged between every two adjacent third vertical plates, the adjacent third vertical plates are in a vertical relation, extension lines of the four third vertical plates form a third square, and the extension line of each second vertical plate passes through the middle points of the two third vertical plates;

a plurality of column ribs are arranged between the second vertical plate and the third vertical plate;

the bottom plate also comprises four vertical plates arranged outside the third vertical plates, the four vertical plates are arranged in parallel, and the extension lines of the two third vertical plates pass through the middle point of one fourth vertical plate;

the flat tube includes a plurality of fluid inlets provided on the upper cover, one fluid inlet provided for each heat exchange area, and the fluid inlets provided at the center of each heat exchange area.

Preferably, the upper cover includes an upper wall surface and a side wall surface extending downward along a side portion of the upper wall surface, and the side wall surface covers an upper portion of the bottom plate to form the cavity of the flat tube.

The invention has the following advantages:

1) the invention provides a novel heat storage heat exchanger which can independently store heat and exchange heat by virtue of a heat storage block, saves a heat exchange pipe and can further improve the heat storage and exchange effect.

2) The invention develops a novel flat heat collecting tube structure, wherein a plurality of heat exchange areas are arranged on a flat tube, a refrigerant in each heat exchange area flows in from the central area of an upper cover, when the refrigerant just enters a cold plate, the temperature is still low, the temperature difference between the refrigerant and the heat exchange areas is large, the cooling capacity is strong, and the temperature of the heat exchange areas can be more effectively controlled.

3) The invention develops a novel flat heat collecting tube structure, and a flow guide structure is arranged in a cold plate of each heat exchange area, so that the flow dead zone of a refrigerant is effectively reduced, and the temperature uniformity of a hot flow surface is further improved; the column ribs are adopted, so that disturbance of a convection field is enhanced, the heat exchange area is expanded, and the heat exchange is favorably strengthened.

4) Each heat exchange area of the heat collection pipe adopts a single-inlet and double-outlet flow mode, so that the phenomenon that the temperature is gradually increased along the flow direction due to the conventional single-inlet and single-outlet flow mode is improved, and the temperature uniformity of heat dissipation is further improved.

5) According to the invention, the heat pipe structure is simulated through a large amount of researches, formulas such as the Knoop number of the structure are determined for the first time, and the heat dissipation performance and the pumping power consumption of the flat pipe can be estimated through the formulas.

6) The invention provides a fresh air system which meets the air supply requirement of a building.

7) The fresh air system can automatically control the removal effect of PM10 and PM2.5, and further improve the quality of fresh air.

Description of the drawings:

the accompanying drawings, which are incorporated in and constitute a part of this application, illustrate embodiments of the application and, together with the description, serve to explain the application and are not intended to limit the application.

FIG. 1 is a schematic diagram of a solar energy system;

FIG. 2 is a schematic diagram of a solar collector system;

FIG. 3 is a schematic top view of a preferred collector tube;

FIG. 4 is a schematic structural diagram of a bottom plate of a preferred heat collecting tube;

FIG. 5 is a structural depiction of a heat exchange area;

FIG. 6 is a schematic view of the upper cover structure;

FIG. 7 is a front view of the base plate;

FIG. 8 is a schematic diagram of a regenerative heat exchanger;

FIG. 9 is a schematic view of a heat storage block;

fig. 10 is a schematic flow diagram of an air supply system or a heating system.

In the figure: 1. the heat collector, 2 heat utilization devices (heat storage exchangers), 3 heat exchange areas, 4 fluid inlets, 41-44 vertical plates, 51-52 fluid outlets, 501 column ribs, 502 column ribs, 10 bottom plates, 11 reflectors, 12 heat collecting pipes (flat pipes), 13 first holes, 14 heat storage blocks, 15 second holes, 20 upper covers and 21 buildings.

Detailed Description

The present disclosure is further described with reference to the following detailed description of illustrative embodiments and accompanying drawings.

Fig. 1 shows a solar collector system, which comprises a collector 1 and a heat utilization device 2 thereof, wherein the collector 1 is connected with the heat utilization device 2 through a pipeline.

The heat collector structure is shown in fig. 2, and comprises a heat collecting tube 12 and a reflector 11, wherein the heat collecting tube 12 is a flat tube. As shown in fig. 3, the lower flat surfaces of the flat tubes face the reflecting surfaces of the reflecting mirrors 11, and the focal points of the reflecting mirrors 11 are located between the upper flat surfaces and the lower flat surfaces, preferably on the surfaces on which the axes of the upper flat surfaces and the axes of the lower flat surfaces of the flat tubes 12 in the longitudinal direction are located.

A flat tube 12 as shown in fig. 3 to 7, comprising a lower base plate 10 and an upper cover 20, the upper cover 20 and the base plate 10 being assembled together to form a cavity of the flat tube 12 in which a fluid flows, the base plate 10 comprising a plurality of heat exchange regions 3 each comprising a riser 41-44 including a first riser 41 located at the center of the heat exchange region 3, a second riser 42 surrounding the first riser 41, and a third riser 43 surrounding the second riser 42, and

column ribs

501, 502;

preferably, as shown in fig. 4-5, the first vertical plates 41 include four first vertical plates 41, a space is provided between adjacent first vertical plates 41, the adjacent first vertical plates 41 are in a perpendicular relationship, and extension lines of the four first vertical plates 41 form a first square;

the second vertical plates 42 comprise four, an interval is arranged between every two adjacent second vertical plates 42, the adjacent second vertical plates 42 are in a vertical relation, the extension lines of the four second vertical plates 42 form a second square, and the extension line of each first vertical plate 41 passes through the middle points of the two second vertical plates 42;

the third vertical plates 43 comprise four, a gap is formed between every two adjacent third vertical plates 43, the adjacent third vertical plates 43 are in a vertical relation, the extension lines of the four third vertical plates 43 form a third square, and the extension line of each second vertical plate 42 passes through the middle points of the two third vertical plates 43;

a plurality of column ribs 501 are arranged between the second riser 42 and the third riser 43;

the bottom plate further comprises four vertical plates 44 arranged outside the third vertical plates 43, the four vertical plates 44 are arranged in parallel, and the extension lines of the two third vertical plates 43 pass through the middle point of one fourth vertical plate 44;

the flat tube 12 includes a plurality of fluid inlets 4 provided on the upper cover 20, one fluid inlet 4 is provided for each heat exchange area, the fluid inlet 4 is provided at a central position of each heat exchange area, the flat tube 12 includes a plurality of

fluid outlets

51, 52 provided on both sides of the flat tube 12 at both sides of the connecting portion of the adjacent heat exchange area 3 and/or both ends of the flat tube 12, the

fluid outlets

51, 52 are provided at outer positions of parallel lines formed by the two fourth risers 44.

Preferably, the

outlets

51, 52 are provided at lower positions on the side portions of the flat tubes 12.

Preferably, as shown in fig. 6, the upper cover includes an upper wall surface and a side wall surface extending downward along a side portion of the upper wall surface, and the side wall surface covers an upper portion of the bottom plate to form a cavity of the flat tube 12.

Preferably, the

outlets

51 and 52 are provided at lower positions of the sidewall surfaces, and the

outlets

51 and 52 are formed by forming holes at the lower positions.

In the structure, because of the heat collection effect of the reflector 11, the temperature of the central position of the heat exchange area of the flat tube is highest, and by the structure, fluid flows in from the central area of the heat exchange area.

The utility model provides a flat intraduct is equipped with the water conservancy diversion structure, especially through setting up the multilayer riser for the fluid flow scope is extensive, effectively reduces the fluid flow dead zone, further improves the temperature uniformity of hot flow face.

In the heat exchanger of this application, through at second and third riser, set up the post rib between third and the fourth riser, do not set up the post rib inside the first riser and between first and the second riser, make the flow resistance in the region that the inner space is little (inside the first riser and between first and the second riser) little, the disturbance is strengthened in the outer space increase region, the disturbance to the flow field has been strengthened promptly, and heat transfer area has been expanded, do benefit to the intensive heat transfer, it is too big also to avoid the flow resistance, accommodation is extensive.

Preferably, the rib shape is cylindrical.

According to the heat exchanger, each heat exchange area adopts a single-inlet and double-outlet flow mode, so that cold fluid flows from the middle to two sides, the phenomenon that the temperature gradually rises along the flow direction due to the single-inlet and single-outlet flow mode in the prior art is improved, and the heat-dissipation temperature uniformity is further improved.

The risers 41-44 are flow directing structures that can be considered as longer straight fins of larger size. Through setting up these risers, also can play the vortex and strengthen the effect of heat transfer.

Preferably, the fluid inlet 4 is located at a position intermediate the two

fluid outlets

51, 52. Through the arrangement, the fluid distribution is more uniform, and the heat dissipation performance is more uniform.

Preferably, the base plate 10 and the upper cover 20 are of a rectangular structure.

Preferably, the heat exchange area is a square area.

Preferably, the bottom plate 10 is provided with a groove, the upper cover is provided with a convex column, and the bottom plate and the upper cover are connected through the matching of the groove and the convex column.

Preferably, the recesses are located diagonally in the base 10, outside the parallel lines formed by the two fourth risers 44.

Preferably, the recess is a hole.

Preferably, the convex column is provided with a threaded hole. The upper cover 10 and the base plate 20 are coupled by means of screw-coupling.

Preferably, the lower portion of the sidewall of the upper cover 20 is provided with an outward extension perpendicular to the sidewall, and the extension is provided with a screw hole to match with a screw hole at a corresponding position on the bottom plate.

Each heat exchange region is located farther from the center of the base plate, the farther between adjacent column ribs 501, between the second riser and the third riser. Mainly along with being more far away from the center of bottom plate, be close to the third riser more, fluidic flow space is less, and the velocity of flow can be fast relatively, and is far away more between 501 through setting up adjacent post for the fluid velocity of flow keeps relative stability, makes whole heat transfer can reach relative even, avoids local inhomogeneous, causes local premature damage.

Further preferably, the distance between the adjacent column ribs 501 increases continuously from the center of the floor to the outside of the center of the floor, the farther the distance between the second riser and the third riser is from the center of the floor. The distribution also accords with the distribution rule change of fluid flow and heat exchange, and the heat exchange efficiency can be further improved through numerical simulation and experimental discovery.

Between the third riser and the fourth riser, the farther from the center of the floor, the closer the adjacent column ribs 501 are from the center of the floor. Mainly along with being farther away from the center of bottom plate, the fluidic flow space is big more, and the velocity of flow can slow down relatively, and is more near between 501 through setting up adjacent post for the fluid velocity of flow keeps relative stability, makes whole heat transfer can reach relative even, avoids local inhomogeneous, causes local too early damage.

Further preferably, the closer the distance between the adjacent column ribs 501 increases continuously between the third riser and the fourth riser from the center of the floor outward, the farther from the center of the floor. The distribution also accords with the distribution rule change of fluid flow and heat exchange, and the heat exchange efficiency can be further improved through numerical simulation and experimental discovery.

In the designed center diffusion type flat tube, fluid enters a cavity of the flat tube from an inlet of a center area of the upper cover, passes through the bottom plate flow guide structure, gradually flows to the periphery of the cavity of the flat tube from the center inlet area, carries out convection heat exchange with the surfaces of flow channels (including column ribs) in the flowing process, and finally flows out from outlets on two sides of the flat tube after being mixed at a position connected with the heat exchange area, thereby carrying out heat exchange.

Compared with the traditional heat collecting tube plate, the center diffusion type flat tube changes the flow mode of fluid in a single inlet and single outlet mode, and replaces the single inlet and double outlet mode, so that in the design, outlets are processed on two sides of the flat tube, and the temperature uniformity of the heat flow surface of the flat tube can be effectively improved.

Further, the diversion structure, actually be some risers, can be regarded as the long straight type fin of bigger size, for reducing the flow resistance, to the fillet is handled to the diversion structure. Fluid flows in from the upper cover of the central diffusion type flat tube, passes through the flow guide structure and gradually flows to corner areas, so that dead flowing areas of the four corner areas of the flat tube can be avoided.

Further, the stud ribs are disposed in low flow rate, high temperature regions of the flat tube cavities. In this time of flat tube structural design, the column ribs are uniformly designed as cylindrical column ribs. The height of the column ribs is set to 4.7mm, and the arrangement mode of the column ribs is determined to be staggered or in-line according to the general flow direction of the fluid in each area needing to be provided with the ribs.

When the system is operated, water flows into the flat tubes from the flat tube inlets 4, is divided by the symmetrically distributed vertical plates (the vertical plates are distributed symmetrically about the central axis of the flat tubes, the lower part is the same) 41, and flows to the periphery from four directions in a divergent manner; when the water flows through the risers 42, the water is divided again and guided to the areas of the column ribs 501 (the column ribs are also symmetrically distributed about the central axis of the flat tube) by the

risers

42 and 43, after passing through the risers 43, the water flowing out from the horizontal direction is divided at the risers 44 on the left and right sides, and the water flowing out from the vertical direction is divided at the inner wall of the upper cover, and after passing through the area of the column ribs 502, the water flows to the corner areas of the four outermost peripheries of the flat tube, so that the flow dead area is effectively reduced. Finally, the water is converged outside the right and left risers 44, and then flows out of the flat tubes through the two

outlets

51, 52 of the upper cover. In the process of flowing inside the flat tube, water absorbs heat conducted to the flat tube from the solar heat collector through the heat flow surface, and finally the heat is taken away together with the water flowing out of the flat tube. The water flowing out of the flat tubes is cooled again to the required temperature through the external heat exchanger, and flows into the flat tubes again to participate in heat exchange, so that a cycle is completed.

Preferably, the heat utilization device 2 is a heat storage heat exchanger 2, a fluid channel and a cold source channel are arranged in the heat storage heat exchanger, fluid in the heat collector transfers heat to the heat storage material through the fluid channel, and the cold source flows through the cold source channel to absorb heat of the heat storage material.

Preferably, the solar heat collection device forms a heat storage system, and the heat storage system comprises a heat collector (with a structure shown in fig. 2), a heat storage heat exchanger 2 and a cold source module, wherein the heat collector absorbs solar energy and then transfers the solar energy to a heat storage material through the heat storage heat exchanger, the cold source module comprises a cold source channel, and the cold source channel exchanges heat with the heat storage material and transfers heat to a cold source in the cold source channel.

Preferably, the cold source channel is an air inlet channel and/or an air inlet channel. Further preferably, the air inlet channel and/or the water inlet channel is an air pipe and/or a water pipe.

Preferably, the heat sink is air, and the air is heated and then delivered into the room of the building 21, thereby forming an air supply system.

Preferably, the cold source is water, and the water is heated and then delivered to the room of the building 21 for heating, so as to form a heating system. Preferably, the heat is supplied in a floor heating mode.

The heat storage heat exchanger structure is shown in fig. 8. The heat exchanger comprises a fluid inlet 6, a fluid outlet 7, a cold source inlet 9, a cold source outlet 8 and a shell, wherein a plurality of heat storage blocks 14 are arranged in the shell of the heat exchanger, the heat storage blocks 14 are stacked together, a first hole 13 and a second hole 15 are arranged in each heat storage block 14, the first holes 13 and the second holes 15 are arranged in a crossed mode and are not communicated with each other, the first holes 13 of the heat storage blocks form communicated channels, the channels formed by the first holes 13 are used for flowing fluid, and the second holes 15 form communicated channels for flowing the cold source; the fluid enters from the fluid inlet 6, passes through the first hole 13, and then exits from the fluid outlet 7, and the cold source enters from the cold source inlet 9, passes through the second hole 15, and then exits from the cold source outlet 8.

The heat accumulation block is divided into a plurality of blocks, so that the heat accumulation block can be conveniently carried and maintained, and is convenient to replace when a certain heat accumulation block loses heat accumulation capacity. Because the heat accumulation piece is the solid heat accumulation piece, does not take place the phase transition among the heat transfer process, therefore the fluid can directly pass the first hole in the heat accumulation piece, need not set up the tube bank alone in first hole, has saved the tube bank. Also, because the cold source flows in the second hole and the fluid flows in the first hole, the fluid and the cold source cannot be directly mixed, the second pipe is saved, and the cost is saved.

Preferably, the heat storage block is a ceramic heat storage block. Therefore, the ceramic heat storage block is adopted, and because the ceramic has corrosion resistance, compared with the traditional tube bundle, the ceramic heat storage block can simultaneously prevent tail gas from corroding the tube bundle.

When the fluid passes through the first hole 13, the heat storage block absorbs heat in the fluid, and then the heat storage medium transfers the absorbed heat to the cold source of the second hole, thereby completing the heat exchange process.

The fluid and the cold source can flow simultaneously, and the heat storage block absorbs the heat of the fluid and transfers the heat to the cold source.

Of course, as another alternative, the fluid and the cold source may exchange heat with the thermal storage medium separately at different time periods. In the heat absorption process, the high-temperature fluid releases heat in the first hole, and the heat storage block stores heat; when the stored heat is required to be utilized, the heat of the heat storage medium is absorbed through the cold source in the second hole. For example, when the high-temperature fluid stops intermittently, the heat storage block and the cold source in the second hole perform exothermic reaction, so that the heat energy is stored and utilized, and the utilization rate of the energy is improved.

As shown in fig. 9, as a preferable mode, each heat storage block 14 is of a cubic structure, two rows of first holes 13 and one row of second holes 15 are arranged in each heat storage block 14, the second holes 15 are located in the middle of the two rows of first holes 13, a plane where the center lines of the first holes 13 of each row are located is parallel to the outer surface of the cube, and a plane where the center lines of the second holes 15 of each row are located is parallel to the outer surface of the cube; the distance between the central line of the two rows of first holes 13 and the central line of the middle second hole is the same, and the first holes and the second holes are arranged at 90 degrees.

Preferably, the second holes are formed in a manner that a plurality of parallel serpentine tubes are arranged in parallel to each other in a vertical direction, and the low-temperature working medium flows in the vertical direction, but the arrangement of the second holes is not limited to the form shown in fig. 8. As another arrangement, the second holes are a plurality of parallel holes parallel to each other in the horizontal direction, and the holes may be in the form of serpentine tubes, that is, the second holes in the same plane are connected together at the ends by the heat storage blocks in a bent structure, and are in a serial structure, and the second holes in different planes are in a parallel structure. Of course, the tubes may also be provided without bends, i.e. with all tubes in the plane and in the vertical direction in a parallel configuration.

As one preference, the diameter of the second hole 15 is continuously reduced along the direction in which the hot water flows. The main reason is along the direction that hot water flows, the continuous decline of hydrothermal temperature, the heat that the heat accumulation piece stored is also less and less, consequently through reducing the pipe diameter, reduce the flow of the low temperature working medium that flows through the heat accumulation piece, thereby make along the fluidic flow direction, the holistic temperature rise difference of low temperature working medium is not big, make the temperature of the low temperature working medium after the heating before mixing keep unanimous basically, the inhomogeneous of the temperature of heating has been avoided, also can avoid the second hole to be heated inhomogeneous and lead to local high temperature simultaneously, influence its life.

Preferably, the solar air supply system further comprises a filtering module, wherein the filtering module is arranged between the fluid module and the heat storage module and used for filtering inlet air, or arranged in the fluid module and preferably arranged in the air inlet channel, and the filtering module is sequentially provided with a primary filter, an electrostatic dust collector, an activated carbon filter and a high-efficiency filter.

Preferably, the primary filter is one or more of non-woven fabric, nylon mesh, fluffy glass fiber felt, plastic mesh or metal wire mesh. Preferably, the primary filter is of a composite structure at least comprising two layers, and the arrangement directions of the skeleton structure fibers of the filter screen in the composite structure of the two adjacent layers are mutually perpendicular, so that the filtering effect can reach medium-efficiency filtering.

The electrostatic dust collector comprises an electrostatic dust collection section, the electrostatic dust collection section comprises two stages, the two stages are a first stage and a second stage along the flowing direction of wind, and the electric field intensity of the first stage is different from that of the second stage. Further preferably, the electric field strength in the second stage is smaller than the electric field strength in the first stage. Mainly because the large particles contained in the air are reduced by the dust removal in the first stage, and therefore by reducing the electric field strength, it is possible to achieve substantially the same effect with less energy.

Preferably, a plurality of dust collecting polar plates are arranged in each stage, and the dust collecting polar plates are parallel to each other; a plurality of corona electrodes are uniformly arranged between the dust collecting polar plates.

Preferably, the system further comprises a controller, the inlet of the electrostatic dust removal section is provided with a PM10 dust detector for detecting the concentration of PM10 at the inlet position, the PM10 dust detector is in data connection with the controller, and the controller automatically controls the strength of the electric field according to the detected concentration of PM 10.

The controller automatically increases the intensity of the electric field if the detected concentration of PM10 becomes high, and automatically decreases the intensity of the electric field if the detected concentration of PM10 becomes low.

Through foretell intelligent control, the size of electric field is controlled according to particulate matter concentration automatically to realize the intelligent operation of system, but also can reach the requirement of energy saving, further improve the pollutant desorption effect of flue gas.

Preferably, the first stage inlet and the second stage inlet are respectively provided with a PM10 dust detector, and the controller independently controls the electric field intensity in the first stage and the second stage according to the data detected by the PM10 dust detectors of the first stage inlet and the second stage inlet.

The electrostatic precipitator comprises an electrostatic/ultrasonic coupling precipitation section, and preferably, the electrostatic/ultrasonic coupling precipitation section is divided into two stages. An ultrasonic wave generating end is arranged in the device and is connected with an ultrasonic generator to establish an ultrasonic field.

Preferably, a pm2.5 detector is arranged at the inlet section of the electrostatic/ultrasonic coupling dust removal section and used for detecting the concentration of pm2.5 at the inlet position, the pm2.5 detector is in data connection with a controller, and the controller automatically controls the power of the ultrasonic generator according to the detected pm2.5 concentration.

The controller automatically boosts the power of the sonotrode if the detected PM2.5 concentration becomes high, and automatically reduces the power of the sonotrode if the detected PM2.5 concentration becomes low.

Through the intelligent control, the power of the ultrasonic generator is automatically controlled according to the concentration of the particulate matters, so that the intelligent operation of the system is realized, the requirement of saving energy can be met, and the pollutant removal effect of the flue gas is further improved.

Preferably, the electrostatic/ultrasonic coupling dust removal section is divided into two stages, PM2.5 detectors are respectively arranged at inlets, and the controller respectively and independently controls the power of the ultrasonic generators in the third stage and the fourth stage according to data detected by the PM2.5 detectors at the inlets of the two stages.

Preferably, the activated carbon filter comprises a catalyst MnO capable of catalytically decomposing ozone₂/CuO、CuO/Ni、MnO₂/Pt、Fe₃O₄/CuO、Ag/Fe₂O₃、Ni/SiO₂One or more of (a).

Preferably, the high-efficiency filter is made of one or more of PP filter paper, glass fiber paper and PET filter paper.

Preferably, the solar thermal storage system further comprises a control module, and the control module is connected with the electrostatic dust collector to control the electrostatic dust collector. For example, the amount of power includes opening and closing.

Preferably, the solar heat storage system further comprises a detection module, the detection module is used for detecting the concentration of particles in the fresh air, the fine particle data exceed a set threshold value, the fine particle data send signals to the control module, the electrostatic dust collector in the filtering module is started at the moment, and the filtering times of the fresh air are increased. When meeting the better weather of air quality, detection module receives and judges that fine particles data in the new trend is less than the threshold value that sets up, and its send signal gives control module, closes the electrostatic precipitator among the filter module, reduces the consumption of electric quantity.

The invention further researches the structure and the heat exchange condition of the structure. The study of the heat exchange condition of this application is carried out to every heat exchange area.

The length of the first riser is set toL ₁And the length of the second riser is set toL ₂And the length of the third riser is set toL ₃The length of the fourth riser is set toL ₄And the thicknesses of all the vertical plates are consistent and are uniformly set to bew；

A plurality of column ribs are arranged between the second vertical plate and the third vertical plate and between the third vertical plate and the fourth vertical plate, and the diameters are uniformly set todThe column rib between third riser and the fourth riser so sets up: multiple rows of column ribs, adjacent rows all adopt fork rows, and the distance between the central axes of the column ribs of the same row of adjacent column ribsS ₁Distance between central axes of adjacent rows of column ribsS ₂；

The post rib between second riser and the third riser so sets up: multiple rows of column ribs are arranged between two opposite third vertical plates and are arranged in parallel with the third vertical plates, adjacent rows all adopt fork rows, and the distance between the central axes of the column ribs of the same row of adjacent column ribsS ₁Distance between central axes of adjacent rows of column ribsS ₂ 。

S ₁、S ₂And the remaining structural dimensional parameters are labeled as shown in fig. 5. When in useS ₁、S ₂When it is changed, i.e. not a fixed value, adoptS ₁、S ₂Average value of (a).

The relationship between the flowing heat exchange performance of the cold plate and the size parameters of the flat tube runner structure is obtained by fitting through simulation calculation:

in the above formulas:Nu _fis the average number of knoop-sels,Dp _wis the pressure drop of the inlet and the outlet of the cold plate,Reis the Reynolds number of the inlet of the refrigerant,D _eis the equivalent diameter of the vertical plate,N _baffle、P _bafflein order to correct the factor(s),S ₁，S ₂，d，L ₁，L ₂，L ₃，L ₄，wthe relative structural dimensions of the cold plate flow passage are as described above; the respective physical quantities are defined as follows:

in formula 5ρIn order to obtain the heat transfer fluid (water) density,uin order to obtain the inlet velocity of the heat exchange fluid,d ₁is the pipe diameter of a heat exchange fluid inlet,μis a heat exchange hydrodynamic viscosity; the baffle is a vertical plate;

in the above-mentioned formula 7, the,hin order to obtain an average heat transfer coefficient,λheat conductivity coefficient of the heat exchange fluid;

in formula 8QThe power consumption is designed for the heat collector,Ain the formula fitting process, the temperature difference definition mode adopts the difference between the highest temperature of the cold plate and the temperature of the inlet refrigerant:

the heat dissipation performance and the pumping power consumption of the flat tube can be estimated according to the types.

The invention also discloses a building roof on which the solar energy system is arranged.

This application has still carried out optimal design to the structure of thermal-collecting tube. Numerical simulation and experiments show that the size of the vertical plates, the size of the column ribs and the distance between the column ribs have great influence on the heat exchange effect, the adjacent distance is too small due to the overlarge size of the vertical plates, the flow resistance is increased, the heat exchange effect is poor, and the reinforced heat transfer effect of the segmented fluid cannot be achieved due to the undersize of the vertical plates; similarly, the size and spacing of the ribs also have the same problem. Therefore, the invention obtains the optimal size relation through a large amount of numerical simulation and experimental research.

The length L3 of the third riser 43, the length of the side of the third square formed by the extension lines of the four third risers 43 is L, the distance between the centers of two adjacent column ribs is S, and the diameter of each column rib is D, so that the following requirements are met:

L3/L-a-b LN (D/S), where LN is a logarithmic function, 0.2435< a <0.2440, 0.6780< b < 0.6785;

further preferably, a =0.2437 and b = 0.6783.

The spacing of the centers of adjacent columnar ribs is S, which is the average spacing of the

columnar ribs

501, 502.

Preferably, the length L of the third square is based on a square formed by extending the center axis of the third riser 43.

The ratio of the length of the first vertical plate to the side length of the first square, the ratio of the length of the second vertical plate to the side length of the second square, and the ratio of the length of the third vertical plate to the side length of the third square are all the same. Are all L3/L.

Preferably, 0.45< L3/L < 0.90; 0.39< D/S < 0.85;

preferably, the length of the fourth riser is 35-45 cm; the third riser is 25-35 cm in length.

Preferably, D is 1-2 cm.

Through the layout of the structure optimization of the heat exchange components, the whole heat exchange effect can reach the best heat exchange effect on the basis of ensuring that the pressure meets the requirement.

Although the present invention has been described with reference to the preferred embodiments, it is not limited thereto. Various changes and modifications may be effected therein by one skilled in the art without departing from the spirit and scope of the invention as defined in the appended claims.

Claims

1. A fresh air building system comprises a heat collector, a heat storage heat exchanger and a cold source module, wherein the heat collector absorbs solar energy and transmits the solar energy to a heat storage material through the heat storage heat exchanger, the cold source module comprises a cold source channel, the cold source channel exchanges heat with the heat storage material and transmits heat to a cold source in the cold source channel, the cold source is air, and the air is heated and then conveyed into a room of a building to form the fresh air system. The second hole forms a communicated channel for circulating the cold source; the cold source enters from the cold source inlet, passes through the second hole and then is discharged from the cold source outlet; the heat collector comprises a heat collecting pipe and a reflecting mirror, the heat collecting pipe is a flat pipe, the lower flat surface of the flat pipe is opposite to the reflecting surface of the reflecting mirror, the flat pipe comprises a lower bottom plate and an upper cover, the upper cover and the bottom plate are assembled together to form a cavity of the flat pipe, fluid flows in the cavity, the bottom plate comprises a plurality of heat exchange areas, each heat exchange area comprises a vertical plate and a column rib, and the vertical plate comprises a first vertical plate located in the center of the heat exchange area, a second vertical plate surrounding the first vertical plate and a third vertical plate surrounding the second vertical plate;

2. The fresh air building system of claim 1 wherein the heat storage blocks are ceramic heat storage blocks.

3. The fresh air building system as claimed in claim 1 wherein the top cover includes a top wall and a side wall extending downwardly along the edge of the top wall, the side wall covering the top of the base to form the cavity of the flat tube.