CN103940277B - Tube-bundle-free split type solid heat storage heat exchanger - Google Patents
Tube-bundle-free split type solid heat storage heat exchanger Download PDFInfo
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- CN103940277B CN103940277B CN201410184996.6A CN201410184996A CN103940277B CN 103940277 B CN103940277 B CN 103940277B CN 201410184996 A CN201410184996 A CN 201410184996A CN 103940277 B CN103940277 B CN 103940277B
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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
- Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
- Y02E60/14—Thermal energy storage
Abstract
The invention provides a heat storage heat exchanger used for waste heat in the tube-bundle-free cement production process. The heat exchanger comprises a high-temperature flue gas inlet, a high-temperature flue gas outlet, a low-temperature working medium inlet, a low-temperature working medium outlet and a shell. Multiple blocks of heat storage materials are arranged in the shell of the heat exchanger, are solid and are piled up, each block of heat storage material is provided with first holes and a second hole, the first holes and the second hole of each block of heat storage material are arranged in a crossed mode and are not communicated with each other, and the first holes and the second holes of the heat storage materials form communicated channels. Waste heat in the cement production process is fully utilized, so that heat exchange efficiency is maximized, energy is saved, and the aims of environment protection and energy conservation are achieved.
Description
Technical field
The present invention relates to a kind of heat regenerator of high-efficiency cement production process UTILIZATION OF VESIDUAL HEAT IN, belong to the field of heat exchangers of F28d.
Background technology
Along with China's rapid economic development, energy resource consumption increases day by day, and the problem that urban air quality goes from bad to worse is also outstanding all the more, and the problem of economize energy and the discharge of minimizing environment harmful is extremely urgent.In common field of heat energy power, high, the with serious pollution one of the main reasons of energy consumption is that the exhaust gas temperature of flue gas is too high, namely wastes mass energy, causes environmental pollution again.Cement industry is the industry of a highly energy-consuming, high pollution.Cement industry afterheat generating system can carry out recycling to using waste heat from tail gas, realizes the object of energy-saving and emission-reduction.But relevant waste heat has intermittence, the features such as poor quality, makes the efficiency of electricity generation system low, and these problems demand solve.
Application heat-storing material can make discontinuous steam in industry-by-industry production process become continuous steam, is conducive to the efficiency improving afterheat generating system.Such as, at home in existing copper smelting process, melting converter produces a large amount of rich steam, but because load fluctuation is large, large portion directly to sky discharge, causes mass energy to waste, by setting up storage heater, it can be made to become steam turbine and to stablize filling source, take full advantage of Copper making process waste, achieve the cascade utilization of the energy.Storage heater in existing UTILIZATION OF VESIDUAL HEAT IN industry, mainly comprises various types of shell-and-tube heat exchanger, and such as, fountain, light pipe, Needle fin tube, gilled tube, heat pipe etc., also can utilize plate type heat exchanger to realize accumulation of heat and exothermic process.But Problems existing is, accumulation of heat and thermal desorption system complex structure, accumulation of heat and heat release are large with heat exchanger volume, and high in cost of production, the improvement therefore for heat-accumulating process heat transmission equipment is necessary.
The present invention is directed to Problems existing in the thermal storage equipment of existing cement industry UTILIZATION OF VESIDUAL HEAT IN, propose a kind of novel heat regenerator.
Summary of the invention
To achieve these goals, technical scheme of the present invention is as follows: a kind of heat regenerator of cement production process UTILIZATION OF VESIDUAL HEAT IN, described heat exchanger comprises high-temperature flue gas import, high-temperature flue gas exports, cryogenic fluid entrance, cryogenic fluid outlet and housing, polylith heat-storing material is set in described heat exchanger shell, described heat-storing material is solid heat storage material, described polylith heat-storing material is stacked, first hole and the second hole are set in every block heat-storing material, first hole and the second hole arranged in a crossed manner and not connected, first hole of described polylith heat-storing material forms the passage be communicated with, the flue gas that the passage that described first hole is formed produces for the cement production process that circulates, second hole is for the cryogenic fluid that circulates, described flue gas enters from high-temperature flue gas entry, and through the first hole, then discharge from high-temperature flue gas outlet, cryogenic fluid enters from cryogenic fluid entrance, through the second hole, then discharges from cryogenic fluid outlet.
Each block heat-storing material described is cube structure, in every block heat-storing material, arrange two ranked first hole and and ranked second hole, second hole is positioned at the centre that two ranked first hole, the plane that often ranked first pore center line place is parallel with cubical outer surface, and the plane that often ranked second pore center line place is parallel with cubical outer surface; Two to ranked first the center line in hole identical with the distance of the center line in middle second hole, between first hole and the second hole, structure is set to 90 degrees, wherein the diameter in the first hole is D1, the diameter in the second hole is D2, distance between the center line in the first hole and the center line in the second hole is L2, the distance in the face of the heat-storing material that the plan range at the center line place in the first hole is nearest is L1, then D1, D2 and L1, and L2 meets following formula:
L1/L2=a*ln(D2/D1)+b，
D2>D1,L2>L1,
Wherein ln is logarithmic function, and a, b are parameter, wherein 1.26<=a<=1.42,0.35<=b<=0.41;
25mm<=D1<=65mm, 25mm<=D2<=65mm,
The unit of L, D1, D2 is mm.
Preferred a=1.32, b=0.39.
Described heat exchanger is vertical structure, and the first hole is vertical direction, and the second hole is horizontal direction, and in the vertical direction arranges multiple dividing plate, and the first hole is divided into multiple independently passage.
The described hole be arranged in the heat-storing material of edge is curved shape, thus makes the second hole form coiled pipe structure in the vertical direction.
Along the direction of flow of flue gas, the heat storage capacity of described heat-storing material reduces gradually.
Along the direction of flow of flue gas, the distance between the center line in the first described hole and the center line in the second hole reduces gradually.
The entrance in the second hole arranges control valve, and for regulating the flow of the medium entering the second hole, set temperature sensor on high-temperature flue gas exit position, for measuring the temperature of the flue gas of heat exchanger exit; Control valve, temperature sensor and central controller carry out data cube computation, and center-control, according to the size of the temperature of temperature sensor measurement, regulates the flow entering the medium in the second hole automatically.
If the temperature measured is lower than the first temperature, then central controller reduces the aperture of control valve automatically, if the temperature measured is higher than the second temperature, then central controller increases the aperture of control valve automatically, and wherein the second temperature is greater than the first temperature.
Described heat storage medium is ceramic material, and the mass component of described ceramic material is as follows: SiO
241%, 3.22%Li
2o, 5.85%TiO
2, 4.3%MgO, 7.1%La
2o
3, 0.5%BaO, remaining is Al
2o
3.
Compared with existing, heat regenerator of the present invention has following advantage:
1) because be provided with the Split type structure of heat-storing material, the present invention is simple by heat regenerator structure, and be easy to manufacture, cost reduces.
2) because be solid heat storage material, so flue gas and cryogenic media directly by carrying out heat exchange in heat-storing material, can not need to arrange pipeline again in heat exchanger, avoiding the corrosion of pipe, having economized pipe.
3) provide a kind of split type regenerative heat exchanger newly, maintain easily, save cost.
4) the present invention has possessed the function of hot tank in conventional hold over system and cold tank, can realize the heat absorption and release function of heat-storing material simultaneously, optimize the structure of hold over system, decrease initial investment and operating cost.
5) heat release while accumulation of heat can also be realized, greatly optimize the utilization of preheating.
6) by test of many times, optimize the optimum structure of heat exchanger, realize the needs that heat exchanger meets heat storage capacity and cost simultaneously.
7) by arranging dividing plate, making overall accumulation of heat even, strengthening convection current simultaneously.
8) by automatically controlling, avoiding cold end corrosion, reaching maximum exhaust heat utilization effect simultaneously.
9) being arranged by the thickness of heat-storing material or the change of heat storage capacity, providing cost savings when meeting accumulation of heat demand.
10) provide a kind of new heat-storing material, meet the demand of the UTILIZATION OF VESIDUAL HEAT IN in manufacture of cement.
Accompanying drawing explanation
Fig. 1 is the schematic diagram of heat-absorbing structure in heat regenerator of the present invention;
Fig. 2 is the schematic diagram of heat radiation structure in heat regenerator of the present invention;
Fig. 3 is another schematic diagram of the heat radiation structure of heat regenerator of the present invention;
Fig. 4 is the upper left corner partial enlarged drawing of the heat regenerator of Fig. 3;
Fig. 5 is the schematic diagram of a detailed description of the invention of heat-storing material of the present invention;
Fig. 6 is the schematic diagram of another detailed description of the invention of heat-storing material of the present invention.
reference numeral
1, high-temperature flue gas outlet, 2, heat exchanger shell, the 3, first hole, 4, vertical baffle, 5, high-temperature flue gas import, 6, vertical baffle, 7, vertical baffle, 8, sender property outlet, the 9, second hole, 10, working medium entrance, 11, inlet tube, 12, inlet header, 13, control valve, 14 heat-storing materials.
Detailed description of the invention
Below in conjunction with accompanying drawing, the specific embodiment of the present invention is described in detail.
As shown in Figure 1, a kind of heat regenerator of cement production process UTILIZATION OF VESIDUAL HEAT IN, described heat exchanger comprises high-temperature flue gas import 5, high-temperature flue gas outlet 1, cryogenic fluid entrance 10, cryogenic fluid outlet 8 and housing 2, polylith heat-storing material 14 is set in heat exchanger shell 2, described polylith heat-storing material 14 is stacked, first hole 3 and the second hole 9 is set in every block heat-storing material 14, first hole 3 and the second hole 9 arranged in a crossed manner and do not interconnect, first hole 3 of described polylith heat-storing material forms the passage be communicated with, the flue gas that the passage that described first hole 3 is formed produces for the cement production process that circulates, second hole 9 forms the passage be communicated with, for the cryogenic fluid that circulates, described flue gas enters from high-temperature flue gas 5 entrance, and through the first hole 3, then discharge from high-temperature flue gas outlet 1, cryogenic fluid enters from cryogenic fluid entrance 10, through the second hole 9, then discharges from cryogenic fluid outlet 8.
Heat-storing material is divided into polylith, can conveniently carry, and safeguards, such as, when certain block heat-storing material loses heat storage capacity, is convenient for changing.Because heat-storing material is solid heat storage material, do not undergo phase transition in heat transfer process, therefore flue gas directly through the first hole in heat-storing material, can not need in the first hole, to arrange tube bank separately, saves tube bank.Equally, because cryogenic fluid flows in the second hole, and flue gas flows in the first hole, and flue gas and cryogenic fluid cannot directly mix, and save the second pipe, provide cost savings.
Preferably, heat-storing material is ceramic heat-storing material.Why adopt ceramic heat-storing material, because pottery has corrosion resistance, arrange compared with tube bank with traditional, can prevent tail gas from the effect of corrosion tube bank occurring simultaneously.
Flue gas is through first hole 3 time, and heat-storing material absorbs the heat in flue gas, and then the heat of absorption is passed to the cryogenic fluid in the second hole by heat storage medium, thus completes heat transfer process.
Flue gas and cryogenic fluid can flow simultaneously, and heat-storing material, while absorption flue gas heat, transfers heat to cryogenic fluid.
Certainly alternatively, flue gas and cryogenic fluid can not simultaneously between section carry out heat exchange with heat storage medium respectively.In endothermic process, high-temperature flue gas heat release in the first hole, heat-storing material storing heat; When needing to utilize the heat stored, by cryogenic fluid in the second hole, absorb the heat of heat storage medium.Such as when high-temperature flue gas intermittence stops, the cryogenic fluid in heat-storing material and the second hole carries out exothermic reaction, realizes storage and the utilization of cement production process waste heat, improves the utilization rate of the energy.
As seen in figures 3-6, as one preferably, each block heat-storing material 14 described is cube structure, in every block heat-storing material 14, arrange two ranked first hole 3 and and ranked second hole 9, second hole 9 is positioned at the centre that two ranked first hole 3, the plane that often ranked first center line place, hole 3 is parallel with cubical outer surface, and the plane that often ranked second center line place, hole 9 is parallel with cubical outer surface; Two to ranked first the center line in hole 3 identical with the distance of the center line in middle second hole, and between the first hole and the second hole, structure is set to 90 degrees.As Figure 4-Figure 6, distance wherein between the first hole 3 and the second centerline hole can not be excessive, if excessive, then can there is no enough heats because of flue gas, cause heat-storing material cannot store full heat, cause the waste of heat-storing material, the temperature of outlet 5 flue gas also can be caused too low simultaneously, cause cold end corrosion; If apart from too small, then cause heat-storing material cannot store satisfied enough heats, cause the demand that cannot meet heat exchange, cause the waste of the energy, in like manner, for the result that the first hole is best with the same demand fulfillment of nearest distance one on heat-storing material border.Therefore, the present invention is the size relationship of the heat exchanger heat-storing material of the best summed up by the test data of the heat exchanger of multiple different tube diameters.
As shown in Figure 4, wherein the diameter in the first hole is D1, and the diameter in the second hole is D2, distance between the center line in the first hole and the center line in the second hole is L2, the distance in the face of the heat-storing material that the plan range at the center line place in the first hole is nearest is L1, then D1, D2 and L1, and L2 meets following formula:
L1/L2=a*ln(D2/D1)+b，
D2>D1,L2>L1,
Wherein ln is logarithmic function, and a, b are parameter, wherein 1.26<=a<=1.42,0.35<=b<=0.41;
25mm<=D1<=65mm, 25mm<=D2<=65mm,
The unit of L, D1, D2 is mm.
Preferably, a=1.32, b=0.39.
Distance between the center of circle in same adjacent two holes that ranked first in hole is L3, the distance of L3 can not be excessive, cause heat cannot store completely if cross conference, cause the waste of heat-storing material, if too small, the heat storage capacity of heat-storing material can be caused too low, accumulation of heat demand cannot be met, the loss of waste heat can be caused.By test of many times, the relation between the described L3 determined and the first bore dia D1 meets: 1.5<L3/D1<2.7, preferably, and 1.9<L3/D1<2.1.
In like manner, the proportion of Distance geometry second bore dia between the second hole, preferably between 1.5-2.7, most preferably is between 1.9-2.1.
As preferably, as Figure 1-3, described heat exchanger is vertical structure, first hole 3 is vertical direction setting, second hole 9 is that horizontal direction is arranged, and in the vertical direction arranges multiple dividing plate 4,6,7, holding multiple pieces heat-storing material between dividing plate and between outermost layer dividing plate and the sidewall of housing, be divided into many groups by heat-storing material, by multiple dividing plate, the first hole 3 be divided into multiple independently passage.By dividing plate, be conducive to the convection heat transfer' heat-transfer by convection performance improving flue gas further.
As one preferably, alignment housing both sides in vertical along housing, the distance between dividing plate is more and more less.The distance of the intermediate space that such as described dividing plate is formed is greater than the distance being positioned at housing both sides.As shown in Figure 2, the space that its median septum 4,6 is formed and 6 and 7 spaces formed are greater than the space that dividing plate 4 is formed with left side housing, are greater than the space that dividing plate 7 is formed with right side housing simultaneously.Main cause is because the speed of flue gas of housing both sides is less than middle speed, can be that speed air flow in whole housing is consistent substantially, thus heat-storing material is evenly absorbed heat on the whole by arranging of dividing plate.
As preferably, as shown in Figure 2, the heat-storing material of warp architecture is set between described the second adjacent hole 9 in the vertical direction, thus makes the second hole form coiled pipe structure in the vertical direction.
As one preferably, along the direction of flow of flue gas, the heat storage capacity of described heat-storing material reduces gradually.Main cause is the flow direction along flue gas, and the temperature of flue gas is more and more lower, and the emission capacity of flue gas reduces gradually, does not therefore need the material of high accumulation of heat energy, can save the cost of heat-storing material like this.
In Fig. 2, the second hole is the form of the coiled pipe arranging many parallel connections parallel to each other in vertical direction, and cryogenic fluid vertically flows, but the arrangement mode in the second hole is not limited to the form shown in Fig. 2.As another kind of set-up mode, second hole is the hole of in the horizontal direction many parallel connection parallel to each other, described hole can be the form of coiled pipe, namely the heat-storing material of the second hole in end by warp architecture on same plane links together, for cascaded structure, be parallel-connection structure in the second hole of Different Plane.Certainly, described pipe also can not arrange warp architecture, is namely all parallel-connection structure with all pipes in vertical direction in the plane, as shown in Fig. 3,6, arranges the collector in the second hole in the left and right sides.
For the form shown in Fig. 6, Fig. 6 illustrates four pieces of heat-storing materials.As one preferably, along on the direction of flow of flue gas, the diameter in the second hole 9 constantly reduces.Main cause is because of the direction along flow of flue gas, the temperature of flue gas constantly declines, heat-storing material institute storing heat is also fewer and feweri, therefore by reducing caliber, reduce the flow of the cryogenic fluid flowing through heat-storing material, thus make along on the flow direction of delaying, the temperature rising difference of the entirety of cryogenic fluid is little, cryogenic fluid temperature before combination after heating is consistent substantially, avoid the uneven of the temperature of heating, also the second hole can be avoided to be heated uneven and to cause local temperature too high simultaneously, affect its service life.
As one preferably, along the direction of flow of flue gas, the distance between the center line in the first described hole 3 and the center line in the second hole 9 is that L reduces gradually.Main cause is the flow direction along flue gas, and the temperature of flue gas is more and more lower, and the emission capacity of flue gas reduces gradually, and therefore required heat-storing material is also just fewer and feweri, can save the cost of heat-storing material like this.
For above-mentioned situation, but L numerical value now also meets above-mentioned formula.The numerical value that L constantly changes can be adjusted by the size adjusting a, b two parameters.
As one preferably, the entrance in the second hole 9 arranges control valve 13, for regulating the flow of the medium entering the second hole 9, simultaneously, set temperature sensor (not shown) on 1 position is exported, for measuring the temperature of the flue gas of heat exchanger exit at high-temperature flue gas; Control valve 13, temperature sensor and central controller (not shown) carry out data cube computation, and center-control, according to the size of the temperature of temperature sensor measurement, regulates the flow entering the medium in the second hole 9 automatically.
If the temperature measured is lower than the first temperature, then central controller reduces the aperture of control valve automatically, if the temperature measured is higher than the second temperature, then central controller increases the aperture of control valve automatically, and wherein the second temperature is greater than the first temperature.
Why take above-mentioned measure, main purpose is to prevent cold end corrosion.Because if flue gas exit temperature is too low, flue-gas temperature can be caused lower than dew-point temperature, the cold end corrosion to smoke discharging pipe and heat exchanger can be caused, by reducing the flow of the cryogenic fluid participating in heat exchange, reduce heat exchange amount, improve outlet temperature, the generation of cold end corrosion can be avoided the control of temperature; In like manner, if the temperature measured is higher than uniform temperature, then shows that exhaust gas temperature is too high, can waste be caused, therefore, need the flow increasing fluid, absorb more heat.
Described heat storage medium is ceramic material, and the mass component of described ceramic material is as follows: SiO
240-43%, 3.1-3.3%Li
2o, 5.5-5.8%TiO
2, 4.3%MgO, 7.0-7.3%La
2o
3, 0.45-0.55%BaO, remaining is Al
2o
3.
Preferably, SiO
241%, 3.22%Li
2o, 5.85%TiO
2, 4.3%MgO, 7.1%La
2o
3, 0.5%BaO, remaining is Al
2o
3.
Above-mentioned heat-storing material is the result obtained by test of many times, has very high heat storage capacity, meet the absorbing waste heat in cement production process completely under rotary cement kiln rear temperature degree.
For the situation of heat-storing material heat storage capacity change, the content that can adjust various composition realizes.
Although the present invention discloses as above with preferred embodiment, the present invention is not defined in this.Any those skilled in the art, without departing from the spirit and scope of the present invention, all can make various changes or modifications, and therefore protection scope of the present invention should be as the criterion with claim limited range.
Claims (4)
1. the heat regenerator without tube bank, described heat exchanger comprises high-temperature flue gas import, high-temperature flue gas exports, cryogenic fluid entrance, cryogenic fluid outlet and housing, polylith heat-storing material is set in described heat exchanger shell, described heat-storing material is solid heat storage material, described polylith heat-storing material is stacked, first hole and the second hole are set in every block heat-storing material, first hole and the second hole arranged in a crossed manner and not connected, first hole of described polylith heat-storing material forms with the second hole the passage be communicated with respectively, the flue gas that the passage that described first hole is formed produces for the cement production process that circulates, the passage that second hole is formed is for the cryogenic fluid that circulates, described flue gas enters from high-temperature flue gas entry, and through the passage that the first hole is formed, then discharge from high-temperature flue gas outlet, cryogenic fluid enters from cryogenic fluid entrance, through the passage that the second hole is formed, then discharges from cryogenic fluid outlet,
Each block heat-storing material described is cube structure, in every block heat-storing material, arrange two ranked first hole and and ranked second hole, described one ranked second hole is positioned at the centre that two ranked first hole, the plane that often ranked first pore center line place is parallel with cubical outer surface, and the plane that often ranked second pore center line place is parallel with cubical outer surface; Two to ranked first the center line in hole identical with the distance of the center line in middle second hole, between first hole and the second hole, structure is set to 90 degrees, wherein the diameter in the first hole is D1, the diameter in the second hole is D2, distance between the center line in the first hole and the center line in the second hole is L2, the distance in the face of the heat-storing material that the plan range at the center line place in the first hole is nearest is L1, then D1, D2 and L1, and L2 meets following formula:
L1/L2=a*ln(D2/D1)+b，
D2>D1,L2>L1,
Wherein ln is logarithmic function, and a, b are parameter, wherein 1.26<=a<=1.42,0.35<=b<=0.41;
25mm<=D1<=65mm, 25mm<=D2<=65mm,
The unit of L, D1, D2 is mm.
2. heat exchanger according to claim 1, is characterized in that a=1.32, b=0.39.
3. heat exchanger according to claim 1, is characterized in that: described heat exchanger is vertical structure, and the first hole is vertical direction, and the second hole is horizontal direction, and in the vertical direction arranges multiple dividing plate, and the first hole is divided into multiple independently passage.
4. heat exchanger as claimed in claim 3, is characterized in that, described in the hole be arranged in the heat-storing material of edge be curved shape, thus make the second hole form coiled pipe structure in the vertical direction.
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| CN109708505A (en) * | 2018-12-26 | 2019-05-03 | 东北大学 | A kind of composite solid heat storage |
| CN112033189B (en) * | 2020-01-08 | 2021-09-14 | 中国北方车辆研究所 | Plate heat exchanger cooled by liquid |
| CN112461022B (en) * | 2020-01-08 | 2022-01-25 | 中国北方车辆研究所 | Liquid cooling plate heat exchanger with variable intervals |
| CN112097551B (en) * | 2020-01-08 | 2021-07-06 | 中国北方车辆研究所 | Liquid cooling plate heat exchanger with multiple outlets distributed |
| CN112240716B (en) * | 2020-01-08 | 2021-09-14 | 中国北方车辆研究所 | Structure optimization method of liquid cooling plate type heat exchanger |
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| CN2769822Y (en) * | 2004-11-09 | 2006-04-05 | 陈应忠 | Long-service life combined fireproof heat accumulator |
| CN201057506Y (en) * | 2007-05-22 | 2008-05-07 | 俞琦 | High-temperature energy accumulation device of central air conditioner |
| CN202013127U (en) * | 2011-04-02 | 2011-10-19 | 刘阳 | Solid heat accumulation structure |
| CN102589328A (en) * | 2012-02-10 | 2012-07-18 | 刘小江 | Pure-countercurrent cellular plate-pin heat exchanger and combination thereof |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2769822Y (en) * | 2004-11-09 | 2006-04-05 | 陈应忠 | Long-service life combined fireproof heat accumulator |
| CN201057506Y (en) * | 2007-05-22 | 2008-05-07 | 俞琦 | High-temperature energy accumulation device of central air conditioner |
| CN202013127U (en) * | 2011-04-02 | 2011-10-19 | 刘阳 | Solid heat accumulation structure |
| CN102589328A (en) * | 2012-02-10 | 2012-07-18 | 刘小江 | Pure-countercurrent cellular plate-pin heat exchanger and combination thereof |
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