CN204944221U - A kind of square equipment manufacture of cement waste heat recovery system of grate cooler - Google Patents
A kind of square equipment manufacture of cement waste heat recovery system of grate cooler Download PDFInfo
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- CN204944221U CN204944221U CN201520747884.7U CN201520747884U CN204944221U CN 204944221 U CN204944221 U CN 204944221U CN 201520747884 U CN201520747884 U CN 201520747884U CN 204944221 U CN204944221 U CN 204944221U
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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
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Abstract
The utility model provides a kind of square equipment manufacture of cement waste heat recovery system of grate cooler, described grate-cooler comprises shell, grog passage, between described shell and grog passage, insulation material is set, in insulation material, waste heat recovery apparatus is set, described waste heat recovery apparatus comprises at least one cylindrical shell, arrange heat exchanger tube at least one cylindrical shell described, described cylindrical shell is rectangle, and cylindrical shell bottom is plane.Grate-cooler of the present utility model fully can either absorb the sensible heat of grog release during very fast cooling in cooler, reduces grog energy consumption, effectively can promote utilization rate of waste heat again.
Description
Technical field
The utility model relates to a kind of heat recovery system of grate cooler, especially relates to the grate cooler heat recovery system in manufacture of cement, belongs to the field of heat exchangers of F27D UTILIZATION OF VESIDUAL HEAT IN, F28D.
Background technology
Grate cooler (abbreviation grate-cooler) is a kind of capital equipment in cement production process.Its basic function comprises: (1) provides suitable clinker cooling speed, to improve the grindability of cement quality and grog; (2) improve Secondary Air and tertiary air temperature as far as possible, as combustion air, reduce firing system fuel consumption; (3) by remaining Hot-blast Heating, dry for cogeneration and coal mill; (4) grog is in addition broken and be cooled to alap temperature, to meet the requirement of clinker conveyor, storage and cement grinding.Grate plate and grate structure are the most important parts of grate-cooler, which determine the thickness of feed layer of grate, determine again air feed system and heat recovery efficiency, one, two, three, four generation grate-cooler product be mainly manifested in the improvement of the structure of grate plate and grate.
In manufacture of cement, the basic structure of conventional forth generation grate-cooler as shown in Figure 1: grate-cooler 4 comprises kiln head cover 2, grate-cooler shell 3, high warm air outlet 5, low warm air outlet 6, grog outlet 7 and blower fan 8, wherein grog enters grate-cooler 4 from rotary kiln 1, then transmit in the transmission channel in grate-cooler 4, blower fan 8 is blown in grate-cooler 4, the temperature of grog is reduced by wind, thus clinker cooling is carried out in transmitting procedure, cooled grog is exported by grog outlet 7.
But the subject matter existed in existing grate-cooler: clinker cooling degree is not enough, the clinker temperature of grog outlet is too high, generally more than 200 DEG C.The consequence caused thus is that cement production process energy consumption is higher, affects again the quality of finished cement simultaneously.
Therefore be necessary to research and develop a kind of novel heat reclaim unit, fully can either absorb the sensible heat of grog release during very fast cooling in cooler, reduce grog energy consumption, effectively can promote utilization rate of waste heat again.
Utility model content
The utility model, for the subject matter existed in existing grate-cooler, proposes a kind of square equipment manufacture of cement waste heat recovery system of grate cooler.
To achieve these goals, the technical solution of the utility model is as follows: a kind of square equipment manufacture of cement waste heat recovery system of grate cooler, described grate-cooler comprises shell, grog passage, arranges insulation material, in insulation material, arrange waste heat recovery apparatus between described shell and grog passage.
As preferably, described waste heat recovery apparatus comprises at least one cylindrical shell, arranges heat exchanger tube in described cylindrical shell.
As preferably, also comprise the device for pressure measurement measuring barrel pressure, described device for pressure measurement is connected with cylindrical shell.
As preferably, described waste heat recovery apparatus comprises multiple cylindrical shell, and be communicated with by connectivity structure between described multiple cylindrical shell, described device for pressure measurement is connected with any one of multiple cylindrical shell.
As preferably, outer surface and the insulation material of the bottom of described cylindrical shell stick together, and the inner surface of the bottom of described heat exchanger tube and cylindrical shell has certain distance.
As preferably, described cylindrical shell is rectangle, and cylindrical shell bottom is plane.
As preferably, described heat exchanger tube is many, and two at least adjacent pipe heat pipes are linked together by swan neck.
As preferably, arrange described heat exchanger tube has more, often arrange heat exchanger tube and there are many.
As preferably, in cylindrical shell, fill heat conduction or accumulation of heat porous material.
As preferably, described device for pressure measurement can serviceability temperature measurement mechanism or humidity measuring instrument replace.
As preferably, grate-cooler also has grog outlet temperature checkout gear, for detecting the clinker temperature of grog outlet, described temperature-detecting device and control system data cube computation, the aperture of the clinker temperature autocontrol valve that described control system detects according to outlet temperature checkout gear, thus control the flow entering the fluid of heat exchanger tube; When the temperature of the grog outlet detected is too high, the then aperture of the automatic intensifying valve of control system, increases the flow entering the fluid of heat exchanger tube, if the temperature of the grog outlet detected is too low, then control system turns valve opening down automatically, reduces the flow entering heat exchanger tube fluid.
As preferably, described control system control mode is as follows: outlet temperature T represents the clinker temperature condition meeting manufacture of cement, enter the fluid flow V of waste heat recovery apparatus during temperature T, above-mentioned outlet temperature T, flow V are normal data, and described normal data stores in the controls;
When outlet temperature becomes t time, flow v changes as follows:
V=b*V* (t/T)
a, wherein a is parameter, 1.06<a<1.10; Preferably, a=1.08;
B is regulation coefficient, (t/T) >1,0.97<b<1.00; Be preferably 0.98;
(t/T) <1,1.00<b<1.04; Be preferably 1.02;
(t/T)＝1,b＝1；
0.85<t/T<1.15。
In above-mentioned formula, temperature T, t are absolute temperature, and unit is K, and flow V, v unit is m/s, for entering the total flow of waste heat utilization equipment.
As preferably, water in described heat exchanger tube can be delivered directly in convector, or pass through Intermediate Heat Exchanger, transfer heat to heating water, then heating water enters in convector and heats, described convector comprises the radiating tube of upper header and lower collector pipe and the triangular-section between upper header and lower collector pipe, described radiating tube comprises base tube and is positioned at the fin of matrix periphery, the cross section of described base tube is isosceles triangle, described fin comprises the first fin and the second fin, described first fin stretches out from isosceles triangle drift angle, described second fin comprises multiple fin of stretching from the facing epitaxy at two waist places of isosceles triangle and from the outward extending multiple fin of the first fin, the second fin extended to same direction is parallel to each other, described first fin, the end that second fin extends forms the second isosceles triangle, described substrate tube arranges first fluid passage, and described first fin inside arranges second fluid passage, described first fluid passage and second fluid channel connection, described second fin is relative to the face specular at the first fin center line place, and the distance of adjacent the second described fin is L1, and the base length of described isosceles triangle is W, and the length of the waist of described second isosceles triangle is S, meets following formula:
L1/S*100=A*Ln (L1/W*100)+B* (L1/W)+C, wherein Ln is logarithmic function, A, B, C are coefficients, 0.68<A<0.72,22<B<26,7.5<C<8.8;
0.09<L1/S<0.11,0.11<L1/W<0.13
4mm<L1<8mm
40mm<S<75mm
45mm<W<85mm
The drift angle of isosceles triangle is a, 110 ° of <a<160 °.
Base tube length is L, 0.02<W/L<0.08,800mm<L<2500mm.
Compared with prior art, the utility model residual neat recovering system has following advantage:
1) the utility model provides a kind of novel waste heat recovery system of grate cooler, fully can either absorb the sensible heat of grog release during very fast cooling in cooler, make the outlet temperature of grog become 100 DEG C, reduce ton grog energy consumption, effectively can promote again the utilization of waste heat.
2) the utility model has insulation material between waste heat recovery apparatus and grog passage, and the air-flow of high temperature in passage can be avoided directly to wash away waste-heat recovery device, avoids waste-heat recovery device booster or damage because of washing away of high temperature.
3) by arranging device for pressure measurement, the fluid of closing waste heat recovery apparatus when heat exchanger tube generation booster in time flows into heat exchanger tube.
4) by arranging cylindrical shell, can radiation heat transfer be carried out by cylindrical shell to heat exchanger tube or carry out conduction heat exchange by heat-conducting medium, avoid heat exchanger tube and directly directly contact with the insulation material of high temperature, avoid the too high generation booster of heat exchanger tube temperature.
5) provide the intelligent control method that a kind of outlet temperature according to grog regulates fluid flow in heat exchanger tube automatically, meet the needs of production, saved the energy.
6) automatically adjust the frequency of blower fan according to grate-cooler grog outlet temperature, thus reach the object of economize energy, to realize the intellectuality of producing.
7) the utility model provides the radiating tube that a kind of new residual heat system uses, and rationally arranges the fin of radiating tube, can arrange more fin, therefore have good radiating effect.
Accompanying drawing explanation
Fig. 1 is the schematic diagram of grate-cooler;
Fig. 2 is grate-cooler waste heat recovery apparatus scheme of installation;
Fig. 3 is the schematic diagram of waste heat recovery apparatus structure;
Fig. 4 is the main TV structure schematic diagram of radiator in residual neat recovering system;
Fig. 5 is the fluid passage relative position schematic diagram of radiator in residual neat recovering system;
Fig. 6 is the schematic diagram that the right side of Fig. 4 is observed.
Reference numeral is as follows:
1, rotary kiln, 2, kiln head cover, 3, shell, 4, grate-cooler, 5, high warm air outlet, 6, low warm air outlet, 7, grog exports, 8, blower fan, 9, grog passage, 10, insulation material, 11, waste heat recovery apparatus, 12, connectivity structure, 13, pipe plug, 14, cylindrical shell, 15, heat exchanger tube, 16, device for pressure measurement, 17, porous material, 18, swan neck, 19, base tube, 20, first fluid passage, 21, first fin, 22, second fin, 23, second fin, 24, first waist, 25, second waist, 26, second fluid passage, 27, base, 28, valve.
Detailed description of the invention
Below in conjunction with accompanying drawing, detailed description of the invention of the present utility model is described in detail.
A kind of manufacture of cement waste heat recovery system of grate cooler, comprise grate-cooler, Fig. 1 illustrates a kind of manufacture of cement grate-cooler 4, grate-cooler 4 comprises kiln head cover 2, grate-cooler shell 3, high warm air outlet 5, low warm air outlet 6, grog outlet 7 and blower fan 8, wherein grog enters grate-cooler 4 from rotary kiln 1, then transmit in the grog passage 9 in grate-cooler 4, blower fan 8 is blown in grate-cooler 4, the temperature of grog is reduced by wind, thus clinker cooling is carried out in transmitting procedure, cooled grog is exported by grog outlet 7.
Grog from rotary kiln 1 transports in grate-cooler grog passage 9, and the wind carried by blower fan is cooled, and arranges insulation material 10 between described shell 3 and grog passage 9, as shown in Figure 2, arranges waste heat recovery apparatus 11 in insulation material 10.
Certainly, the blower fan in Fig. 1 is only schematic diagram, and blower fan transports cooling air along grog channel bottom to blowing up, to cool the grog in grog passage.
Be in insulation material, waste heat recovery apparatus is set, main cause is the discovery that is in operation, the clinker temperature exporting out from grog is too high, thus affect the quality of finished cement, but also cause the energy consumption in cement production process too high, therefore by arrange waste heat recovery apparatus reclaim Cement Cold but in heat, reduce further the energy consumption of manufacture of cement, improve the quality of finished cement.
As preferably, insulation material 10 is insulating bricks.
As preferably, between described waste heat recovery apparatus 11 and grog passage, there is insulation material 10.As shown in Figure 2, two-layer insulating brick is set between waste heat recovery apparatus 11 and grog passage 9.Why insulation material is set, main cause avoids waste heat recovery apparatus 11 directly contact with the high-temperature flue gas in grog passage 9 or directly washed away by high-temperature flue gas, cause waste heat recovery apparatus temperature too high, or directly washing away easy damage, also can avoiding the heat-exchanging tube bundle in waste heat recovery apparatus because high temperature causes booster with washing away.
As shown in Figure 2, as preferably, described waste heat recovery apparatus comprises at least one cylindrical shell 14, arranges heat exchanger tube 15 at least one cylindrical shell described.
By arranging cylindrical shell 14, avoiding heat exchanger tube directly to contact with insulation material, making heat exchanger tube by the radiation of cylindrical shell 14 or by porous material heat conduction, avoiding heat exchanger tube, because temperature is too high, booster occurs.
By arranging cylindrical shell, Another reason is once there is booster, then avoid fluid to leak, destroy insulation material.
As preferably, have certain space between cylindrical shell 14 and heat exchanger tube 15, described space is as the porous material 17 being preferably filled to heat conduction or accumulation of heat.
As preferably, also comprise the device for pressure measurement 16 measuring barrel pressure.Described device for pressure measurement 16 is connected to cylindrical shell 14, by measuring the pressure in cylindrical shell 14, check whether heat exchanger tube 15 booster occurs, once there is booster, then the measurement data of device for pressure measurement 16 will be abnormal, then close the Fluid valve entered in heat exchanger tube 15 in time.
As preferably, described system also comprises control system and valve 28, and described control system and valve 28 carry out data cube computation, for the opening and closing of by-pass valve control 28 and the size of valve 28 flow.Described control system and device for pressure measurement 16 carry out data cube computation, for the pressure of detected pressures measurement mechanism 16.Once the pressure of the device for pressure measurement 16 of control system detection exceedes predetermined value, then show pressure anomaly, probably there is booster in heat exchanger tube 15, and now control system by-pass valve control 28 is closed automatically.By above-mentioned automatic control function, monitor procedure is made to realize automation.
As preferably, described waste heat recovery apparatus 11 comprises multiple cylindrical shell 14, is communicated with between described cylindrical shell 14 by connectivity structure 12, and described device for pressure measurement 16 is connected with any one of multiple cylindrical shell 14.
By arranging connectivity structure 12, multiple cylindrical shell 14 is communicated with, once some cylindrical shell generation boosters, then because the reason be communicated with, device for pressure measurement 14 also can detect pressure anomaly at any time, then also can automatically control fluid valve closing, avoid fluid to enter into heat exchanger tube.The quantity of device for pressure measurement 16 can be reduced like this, only by one or the few device for pressure measurement of quantity, thus realize the pressure detecting of multiple cylindrical shell.
As preferably, outer surface and the insulation material of the bottom of described cylindrical shell 14 stick together, and described heat exchanger tube 15 has certain distance with the inner surface of the bottom of cylindrical shell 14.
Sticked together by the outer surface of the bottom of cylindrical shell 14 and insulation material, the heat trnasfer between cylindrical shell 14 outer surface and insulation material can be ensured, ensure that heat is delivered to cylindrical shell from insulation material by the mode of heat trnasfer.Heat exchanger tube 15 has certain distance with the inner surface of the bottom of cylindrical shell 14, realizes radiation heat transfer, avoids heat exchanger tube and cylindrical shell directly to contact and cause temperature too high, thus cause booster phenomenon to occur.
As preferably, described cylindrical shell 14 is rectangle, and cylindrical shell bottom is plane.
As preferably, described heat exchanger tube 15 is many, and two at least adjacent pipe heat pipes are linked together by swan neck 18.As preferably, connected by swan neck 18 between the heat exchanger tube in each cylindrical shell, thus make the series connection of the heat exchanger tube 15 in each cylindrical shell 14 be a heat exchanger tube.
As preferably, arrange described heat exchanger tube 15 has more, often arrange heat exchanger tube and there are many.Such as, as shown in Figure 2, two row's heat exchanger tubes are set perpendicular to grog channel direction.
As preferably, the multiple heat exchanger tubes in each cylindrical shell 14 are a heat exchanger tube 15 by elbow series connection, have independent entrance and exit, and the heat exchanger tube 15 in multiple cylindrical shell 14 are parallel-connection structure.Like this, the heat exchanger tube of each cylindrical shell 14 arranges separately a valve, and by arranging valve separately, control system can control separately each valve, thus controls separately the flow entering the fluid of each cylindrical shell.
Certainly, as preferably, each cylindrical shell can arrange separately a device for pressure measurement 16, automatically the pressure in each cylindrical shell is detected by device for pressure measurement 16, when certain cylinder internal pressure of detection is abnormal, then automatically close the valve of this cylindrical shell, stop fluid to enter the heat exchanger tube of this cylindrical shell.
As preferably, because arrange connectivity structure 12, therefore can the few device for pressure measurement of magnitude setting, such as only arrange one.Now, it is abnormal that control system detects that pressure occurs, then can control closeall valve or total valve.
As preferably, device for pressure measurement 16 can be replaced by serviceability temperature measurement mechanism.Temperature measuring equipment and control system carry out data cube computation, and when the temperature detected is lower than certain numerical value, namely measurement data will be abnormal, then control system closes the Fluid valve entered in heat exchanger tube 15 in time.
As preferably, humidity measuring instrument can be used to replace device for pressure measurement 16.Humidity measuring instrument and control system carry out data cube computation, and when the humidity detected is higher than certain numerical value, namely measurement data will be abnormal, then control system closes the Fluid valve entered in heat exchanger tube 15 in time.
As preferably, in cylindrical shell 14, fill heat conduction or accumulation of heat porous material 17.By arranging porous material 17, unnecessary heat storage can be made, heat exchanger tube 15 can be transferred heat to by the mode of heat conduction simultaneously.
As preferably, in described porous media 17, fluid flow passageway is set, to detect internal fluid pressure.
The structure of cylindrical shell 14 as shown in Figure 3, cylindrical shell 14 one end is closed, and the other end arranges pipe plug 13, and pipe is U-shaped tubular construction.
Certainly, as preferably, many pipes in cylindrical shell 14 can be parallel-connection structures, and such as, arrange collector at the fluid inlet of heat exchanger tube 15 and outlet, the collector of similar convector is such.
As preferably, the pipe between multiple cylindrical shell 14 can be cascaded structure, and the heat exchanger tube 15 namely between adjacent cylindrical shell 14 connects the structure for series connection by tube connector.So only need a valve.
As preferably, in such cases, the outer surface heat-absorbing material of described heat exchanger tube 15, to strengthen the absorption to radiation.
As preferably, along the transporting direction of grog, the heat absorption capacity of heat exchanger tube 15 heat-absorbing material of different cylindrical shell 14 strengthens gradually, and be further used as preferably, the amplitude that heat absorption capacity strengthens increases gradually.Found through experiments, by setting like this, exhaust-heat absorption ability about 15% can be improved.And by so arranging, the heat absorption of heat exchanger tube entirety can be made even, and temperature contrast diminishes, and ensures heat exchanger tube bulk life time, avoids part heat exchanger tube temperature too high, cause and constantly change frequently.
As preferably, along the transporting direction of grog, the capacity of heat transmission of different cylindrical shell 14 heat exchanger tube 15 porous material 17 strengthens gradually, and be further used as preferably, the amplitude that the capacity of heat transmission strengthens increases gradually.Found through experiments, by setting like this, exhaust-heat absorption ability can be provided to provide about 16%.Before main cause is similar.
As preferably, as preferably, along the transporting direction of grog, the heat storage capacity of different cylindrical shell 14 heat exchanger tube 15 porous material 17 strengthens gradually, and be further used as preferably, the amplitude that heat storage capacity strengthens increases gradually.Before main cause is similar.
In this programme, can by arranging identical material at different parts, the porous material layer 17 of different thermal conductivity factor, the difference that can realize the absorption heat energy power of different parts heat exchanger tube 15 strengthens.Also directly can select the porous material layer 17 of unlike material, obtain different heat absorption capacities.
As preferably, the outer surface of cylindrical shell 14 arranges heat-absorbing material.Main cause is because the heat exchange between insulation material and cylindrical shell 14 also exists a part of radiation heat transfer, therefore needs to arrange heat-storing material to increase caloric receptivity.
As preferably, along the transporting direction of grog, the heat absorption capacity of the surperficial heat-absorbing material of different cylindrical shells 14 strengthens gradually, and be further used as preferably, the amplitude that heat absorption capacity strengthens increases gradually.Before main cause is similar.
As preferably, cylindrical shell 14 outer setting is protruding.The height of different drum surface projection is different, and along the transporting direction of grog, the height of different drum surface projection increases gradually, and be further used as preferably, the amplitude of increase increases gradually.Before main cause is similar.
As preferably, cylindrical shell 14 outer setting is protruding.The density of different drum surface projection is different, and along the transporting direction of grog, the density of different drum surface projection increases gradually, and be further used as preferably, the amplitude of increase increases gradually.Before main cause is similar.
As preferably, described grate-cooler also comprises grog outlet temperature checkout gear, for detecting the clinker temperature of grog outlet.Described temperature-detecting device and control system data cube computation.Described control system according to the aperture of the clinker temperature autocontrol valve detected, thus controls the flow entering the fluid of heat exchanger tube.
When the temperature of the grog outlet detected is too high, then the aperture of automatic intensifying valve, increases the flow entering the fluid of heat exchanger tube, if the temperature detected is too low, then automatically turns valve opening down, reduces the flow entering heat exchanger tube fluid.By automatically regulating fluid flow, thus automatically regulate the quantity of the fluid participating in heat exchange, thus realize, to the adjustment of grog outlet clinker temperature, meeting the needs on producing, ensureing cement quality.
Described control system can realize adjusting flow automatically according to outlet temperature.Control mode is as follows: during outlet temperature T, flow V, represents the clinker temperature condition meeting manufacture of cement.Above-mentioned outlet temperature T, flow V are normal data.Described normal data stores in the controls.
When outlet temperature becomes t time, flow v changes as follows:
V=b*V* (t/T)
a, wherein a is parameter, 1.06<a<1.10; Preferably, a=1.08;
B is regulation coefficient, (t/T) >1,0.97<b<1.00; Be preferably 0.98;
(t/T) <1,1.00<b<1.04; Be preferably 1.02;
(t/T)＝1,b＝1；
0.85<t/T<1.15。
In above-mentioned formula, temperature T, t are absolute temperature, and unit is K, and flow V, v unit is m/s, for entering the total flow of waste heat recovery apparatus.
As preferably, when the heat exchanger tube 15 of multiple cylindrical shell 14 is parallel-connection structures time, time flow carries out adjusting, the increase of the heat exchanger tube flow of each cylindrical shell or the ratio of minimizing identical.
As preferably, the ratio that heat exchanger tube 15 flow of each cylindrical shell 14 increases or reduces is different, and along the transporting direction of grog, the ratio increasing or reduce is more and more less.Further preferably, the amplitude of increase or minimizing ratio is more and more less.Found through experiments, the setting changed by flowrate amplitude, the data of control can be made more accurate, and error is less, can reduce by the error of about 30%.
By above-mentioned formula, the intellectuality adjusting flow according to outlet temperature automatically can be realized, save and can transport, improve production efficiency.
As preferably, can input in the controls and organize normal data more.When under appearance two groups or many group reference data situations, the interface of the reference data that user can be provided to select, preferably, control system can be selected (1-t/T) automatically
2minimum one of value.
As preferably, described control system comprises blower fan frequency regulation arrangement, can control blower fan frequency, thus regulate the flow of the wind entering cooling grog in grate-cooler according to the clinker temperature of grog outlet.When temperature is too high, then automatically tune up the frequency of blower fan, increase air output, if the temperature detected is too low, then automatically reduce blower fan frequency, reduce air output.
Certainly blower fan FREQUENCY CONTROL and fluid flow can be controlled to combine, control grog outlet temperature together.
As preferably, the fluid of heating in heat exchanger tube 15 is used for Waste Heat Generation and uses.
As preferably, heat exchanger tube 15 connects convector, thus the water of heating is used for heating.
As preferably, the water in heat exchanger tube 15 can be delivered directly in convector, and also can pass through heat exchanger, transfer heat to heating water, then heating water enters in convector and heats.Described radiator comprises upper header and lower collector pipe and is positioned at the radiating tube of upper header and lower collector pipe.
As Fig. 4, shown in 5, the radiating tube that described radiator uses, described radiating tube comprises base tube 19 and is positioned at the fin 21-23 of base tube periphery, as Fig. 4, shown in 5, the cross section of described base tube is isosceles triangle, described fin comprises the first fin 21 and the second fin 22, second fin 23, described first fin 21 is outward extending from isosceles triangle drift angle, described second fin comprises multiple second fin 22 of stretching from the facing epitaxy at two waist places of isosceles triangle and from outward extending multiple second fin 23 of the first fin, the second fin 22 extended to same direction, second fin 23 is parallel to each other, such as, as shown in the figure, from outward extending second fin 22 of isosceles triangle second waist 25 (waist on the left side), second fin 23 is parallel to each other, from isosceles triangle first waist 24 (i.e. the waist on the right) outward extending second fin 22, second fin 23 is parallel to each other, described first fin 21, second fin 22, the end that second fin 23 extends forms the second isosceles triangle, as shown in Figure 4, the length of the waist of the second isosceles triangle is S, described base tube 19 inside arranges first fluid passage 20, and described first fin 21 inside arranges second fluid passage 26, and described first fluid passage 21 is communicated with second fluid passage 26.Such as, as described in Figure 4, be communicated with at isosceles triangle corner position.
By vibrational power flow so, the multiple fin of base tube 19 outer setting can be made, increase heat radiation, fluid passage is set in the first fin 21 inside simultaneously, fluid is made to enter in the first fin 21, the second fin 22 be directly connected with the first fin 21 carries out heat exchange, adds heat-sinking capability.
General radiating tube is all that surrounding or both sides arrange fin, but find in engineering, generally heat convection effect is bad for the fin of the side contacted with wall, because air wall side flow relatively poor, therefore isosceles triangle base 27 is set to plane by the utility model, time therefore fin is installed, can directly by plane and wall close contact, compared with other radiator, installing space can be saved greatly, avoid the waste in space, take special fin form simultaneously, ensure to meet best radiating effect.
As preferably, described second fin 22, second fin 23 relative to the face specular at the first fin 21 center line place, namely relative to the face specular at the line place of the summit of isosceles triangle and the mid point at place, base.
As preferably, the second fin 22, second fin 23 extends perpendicular to two waists of the second isosceles triangle.
When the length on the limit of isosceles triangle is certain, first fin 21 and the second fin 22, second fin 23 is longer, then heat transfer effect is better in theory, find in process of the test, when the first fin 21 and the second fin 22, time second fin 23 reaches certain length, then heat transfer effect just increases very not obvious, main because along with the first fin 21 and the second fin 22, second fin 23 length increases, also more and more lower in the temperature of fin end, along with temperature is reduced to a certain degree, heat transfer effect then can be caused not obvious, also add the cost of material on the contrary and considerably increase the space occupied of radiator, simultaneously, in heat transfer process, if the spacing between the second fin is too little, also the deterioration of heat transfer effect is easily caused, because along with the increase of radiating tube length, in air uphill process, boundary layer is thickening, boundary layer between abutting fins is caused to overlap mutually, worsen heat transfer, spacing between too low or the second fin of radiating tube length causes too greatly heat exchange area to reduce, have impact on the transmission of heat, therefore in the distance of the second adjacent fin, the length of side of isosceles triangle, an optimized size relationship is met between the length of the first fin and the second fin and heat sink length.
Therefore, the utility model is the dimensionally-optimised relation of the radiator of the best summed up by thousands of test datas of the radiator of multiple different size.
The distance of described the second adjacent fin is L1, and the base length of described isosceles triangle is W, and the length of the waist of described second isosceles triangle is S, and the relation of above-mentioned three meets following formula:
L1/S*100=A*Ln (L1/W*100)+B* (L1/W)+C, wherein Ln is logarithmic function, A, B, C are coefficients, 0.68<A<0.72,22<B<26,7.5<C<8.8;
0.09<L1/S<0.11,0.11<L1/W<0.13
4mm<L1<8mm
40mm<S<75mm
45mm<W<85mm
The drift angle of isosceles triangle is a, 110 ° of <a<160 °.
As preferably, base tube 19 length is L, 0.02<W/L<0.08,800mm<L<2500mm.
As preferably, A=0.69, B=24.6, C=8.3.
It should be noted that, the distance L1 of adjacent second fin is the distance counted from the center of the second fin, as shown in Figure 1.
By testing after result of calculation, by the numerical value of computation bound and median, the result of gained matches with formula substantially, and error is substantially within 3.54%, and maximum relative error is no more than 3.97%, and mean error is 2.55% again.
Preferably, the distance of described the second adjacent fin is identical.
As preferably, the width of the first fin 21 is greater than the width of the second fin 22, second fin 23.
Preferably, the width of the first fin 21 is b1, and the width of the second fin 22, second fin 23 is b2, wherein 2.2*b2<b1<3.1*b2;
As preferably, 0.9mm<b2<1mm, 2.0mm<b1<3.2mm.
As preferably, the width of second fluid passage 26 be the 0.85-0.95 of the width of the second fin 22 doubly, be preferably 0.90-0.92 doubly.
Width b1, b2 herein refer to the mean breadth of fin.
Although the utility model discloses as above with preferred embodiment, the utility model is not defined in this.Any those skilled in the art, not departing from spirit and scope of the present utility model, all can make various changes or modifications, and therefore protection domain of the present utility model should be as the criterion with claim limited range.
Claims (8)
1. a square equipment manufacture of cement waste heat recovery system of grate cooler, described grate-cooler comprises shell, grog passage, it is characterized in that, between described shell and grog passage, insulation material is set, in insulation material, arrange waste heat recovery apparatus, described waste heat recovery apparatus comprises at least one cylindrical shell, arranges heat exchanger tube at least one cylindrical shell described, described cylindrical shell is rectangle, and cylindrical shell bottom is plane.
2. residual neat recovering system as claimed in claim 1, is characterized in that having insulation material between described waste heat recovery apparatus and grog passage.
3. residual neat recovering system as claimed in claim 1 or 2, is characterized in that, also comprise the device for pressure measurement measuring barrel pressure, described device for pressure measurement is connected with cylindrical shell.
4. residual neat recovering system as claimed in claim 3, it is characterized in that, described waste heat recovery apparatus comprises multiple cylindrical shell, and be communicated with by connectivity structure between described multiple cylindrical shell, described device for pressure measurement is connected with any one of multiple cylindrical shell.
5. residual neat recovering system as claimed in claim 1, it is characterized in that, described heat exchanger tube is many, and two at least adjacent pipe heat pipes are linked together by swan neck.
6. residual neat recovering system as claimed in claim 1, is characterized in that, fills heat conduction or accumulation of heat porous material in cylindrical shell.
7. residual neat recovering system as claimed in claim 1, it is characterized in that, grate-cooler also has grog outlet temperature checkout gear, for detecting the clinker temperature of grog outlet, described temperature-detecting device and control system data cube computation, the aperture of the clinker temperature autocontrol valve that described control system detects according to outlet temperature checkout gear, thus control the flow entering the fluid of heat exchanger tube; When the temperature of the grog outlet detected is too high, the then aperture of the automatic intensifying valve of control system, increases the flow entering the fluid of heat exchanger tube, if the temperature of the grog outlet detected is too low, then control system turns valve opening down automatically, reduces the flow entering heat exchanger tube fluid.
8. residual neat recovering system as claimed in claim 7, it is characterized in that, described control system control mode is as follows: outlet temperature T represents the clinker temperature condition meeting manufacture of cement, the fluid flow V of waste heat recovery apparatus is entered during temperature T, above-mentioned outlet temperature T, flow V are normal data, and described normal data stores in the controls;
When outlet temperature becomes t time, flow v changes as follows:
V=b*V* (t/T)
a, wherein a is parameter, 1.06<a<1.10;
B is regulation coefficient, during (t/T) >1, and 0.97<b<1.00;
(t/T) during <1,1.00<b<1.04;
(t/T) when=1, b=1;
0.85<t/T<1.15；
In above-mentioned formula, temperature T, t are absolute temperature, and unit is K, and flow V, v unit is m/s, for entering the total flow of waste heat utilization equipment.
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| CN201520747884.7U CN204944221U (en) | 2015-09-24 | 2015-09-24 | A kind of square equipment manufacture of cement waste heat recovery system of grate cooler |
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| CN201520747884.7U CN204944221U (en) | 2015-09-24 | 2015-09-24 | A kind of square equipment manufacture of cement waste heat recovery system of grate cooler |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105066724A (en) * | 2015-09-24 | 2015-11-18 | 山东大学 | Waste heat recovery system for cement production grate cooler employing square equipment |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105066724A (en) * | 2015-09-24 | 2015-11-18 | 山东大学 | Waste heat recovery system for cement production grate cooler employing square equipment |
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