CN204944221U - A kind of square equipment manufacture of cement waste heat recovery system of grate cooler - Google Patents

Abstract

The utility model provides a waste heat recovery system of a grate cooler for square equipment cement production. The grate cooler includes a shell and a clinker channel. An insulating material is arranged between the shell and the clinker channel, and waste heat recovery is arranged in the heat insulating material. Equipment, the waste heat recovery equipment includes at least one cylinder, heat exchange tubes are arranged in the at least one cylinder, the cylinder is rectangular, and the lower part of the cylinder is a plane. The grate cooler of the utility model can not only fully absorb the sensible heat released when the clinker is cooled at a high speed in the cooler, reduce the energy consumption of the clinker, but also effectively improve the utilization rate of waste heat.

Description

A square equipment cement production grate cooler waste heat recovery system

technical field

The utility model relates to a heat recovery system of a grate cooler, in particular to the heat recovery system of a grate cooler in cement production, and belongs to the fields of F27D waste heat utilization and F28D heat exchangers.

Background technique

Grate cooler (referred to as grate cooler) is a major equipment in the cement production process. Its basic functions include: (1) Provide appropriate clinker cooling speed to improve cement quality and clinker grindability; (2) Increase the temperature of secondary air and tertiary air as much as possible, as combustion air, and reduce the temperature of the firing system fuel consumption; (3) heating the waste hot air for waste heat power generation and coal mill drying; (4) crushing the clinker and cooling it to the lowest possible temperature to meet the needs of clinker transportation, storage and cement grinding Require. The grate plate and grate bed structure are the most important parts of the grate cooler, which determines the material layer thickness of the grate bed, and also determines the air supply system and heat recovery efficiency. The main performance of the first, second, third and fourth generation grate cooler products Improvements in the structure of grate plates and grate beds.

The basic structure of the fourth-generation grate cooler commonly used in cement production is shown in Figure 1: grate cooler 4 includes kiln head cover 2, grate cooler shell 3, high-temperature air outlet 5, low-temperature air outlet 6, clinker outlet 7 and Fan 8, wherein the clinker enters the grate cooler 4 from the rotary kiln 1, and then is transported in the transmission channel in the grate cooler 4, and the fan 8 supplies air to the grate cooler 4, and the clinker is reduced by the wind. Temperature, so that the clinker is cooled during the transmission process, and the cooled clinker is output through the clinker outlet 7.

But the main problem that exists in existing grate cooler: clinker cooling degree is insufficient, the clinker temperature of clinker outlet is too high, generally exceeds 200 ℃. The resulting consequence is that the cement production process consumes more energy and affects the quality of the finished cement product.

Therefore, it is necessary to develop a new type of heat recovery device, which can fully absorb the sensible heat released when the clinker is cooled at a high speed in the cooler, reduce the energy consumption of the clinker, and effectively improve the utilization rate of waste heat.

Utility model content

The utility model aims at the main problems existing in the existing grate cooler, and proposes a waste heat recovery system of the grate cooler for square equipment cement production.

In order to achieve the above object, the technical solution of the present utility model is as follows: a waste heat recovery system of grate cooler for square equipment cement production, the grate cooler includes a shell and a clinker channel, and an insulating material is arranged between the shell and the clinker channel , Set waste heat recovery equipment in the insulation material.

Preferably, the waste heat recovery device includes at least one cylinder, and heat exchange tubes are arranged in the cylinder.

Preferably, it also includes a pressure measurement device for measuring the pressure of the cylinder, and the pressure measurement device is connected with the cylinder.

Preferably, the waste heat recovery device includes a plurality of cylinders, the plurality of cylinders are connected through a communication structure, and the pressure measuring device is connected to any one of the plurality of cylinders.

Preferably, the outer surface of the lower part of the cylinder is attached to the heat-insulating material, and the heat exchange tube has a certain distance from the inner surface of the lower part of the cylinder.

Preferably, the cylinder is rectangular, and the lower part of the cylinder is plane.

Preferably, there are multiple heat exchange tubes, and at least two adjacent tube heat tubes are connected together through elbow tubes.

Preferably, the heat exchange tubes have multiple rows, and each row has multiple heat exchange tubes.

Preferably, the cylinder is filled with a porous material for heat conduction or heat storage.

Preferably, the pressure measuring device can be replaced by a temperature measuring device or a humidity measuring device.

As a preference, the grate cooler also has a clinker outlet temperature detection device for detecting the clinker temperature at the clinker outlet. The temperature automatically controls the opening of the valve, thereby controlling the flow of fluid entering the heat exchange tube; when the detected temperature of the clinker outlet is too high, the control system automatically increases the opening of the valve to increase the flow of fluid entering the heat exchange tube , if the temperature of the detected clinker outlet is too low, the control system will automatically adjust the opening of the valve to reduce the flow of fluid entering the heat exchange tube.

Preferably, the control method of the control system is as follows: the outlet temperature T indicates that the clinker temperature condition for cement production is met, and the fluid flow rate V entering the waste heat recovery equipment at temperature T, the above-mentioned outlet temperature T and flow rate V are standard data, so The standard data described above are stored in the control system;

When the outlet temperature becomes t, the flow v changes as follows:

v=b*V*(t/T) ^a , wherein a is a parameter, 1.06<a<1.10; preferably, a=1.08;

b is an adjustment coefficient, (t/T)>1,0.97<b<1.00; preferably 0.98;

(t/T)<1, 1.00<b<1.04; preferably 1.02;

(t/T)=1, b=1;

0.85<t/T<1.15.

In the above formula, temperature T, t is the absolute temperature, the unit is K, the flow rate V, the unit of v is m/s, which is the total flow rate entering the waste heat utilization equipment.

Preferably, the water in the heat exchange tube can be directly transported to the heating radiator, or through an intermediate heat exchanger, the heat is transferred to the heating water, and then the heating water enters the heating radiator for heating. The device comprises an upper header and a lower header and a heat dissipation pipe with a triangular section between the upper header and the lower header. The heat dissipation pipe includes a base pipe and cooling fins positioned on the periphery of the base body. The cross section of the base pipe is An isosceles triangle, the heat sink includes a first heat sink and a second heat sink, the first heat sink extends outward from the corner of the isosceles triangle, and the second heat sink includes two fins from the isosceles triangle The plurality of cooling fins extending outward facing the waist and the plurality of cooling fins extending outward from the first cooling fins, the second cooling fins extending in the same direction are parallel to each other, and the first cooling fins and the second cooling fins extend The end of the base pipe forms a second isosceles triangle; the base pipe is provided with a first fluid channel, and the first heat sink is provided with a second fluid channel, and the first fluid channel communicates with the second fluid channel; the first fluid channel communicates with the second fluid channel; The two heat sinks are mirror-symmetrical to the plane where the center line of the first heat sink is located, the distance between the adjacent second heat sinks is L1, the base length of the isosceles triangle is W, and the second isosceles triangle The length of the waist is S, which satisfies the following formula:

L1/S*100＝A*Ln(L1/W*100)+B*(L1/W)+C, where Ln is a logarithmic function, A, B, and 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 apex angle of an isosceles triangle is a, 110°<a<160°.

The length of the base pipe is L, 0.02<W/L<0.08, 800mm<L<2500mm.

Compared with the prior art, the waste heat recovery system of the utility model has the following advantages:

1) This utility model provides a new type of waste heat recovery system for the grate cooler, which can fully absorb the sensible heat released when the clinker is cooled at a high speed in the cooler, so that the outlet temperature of the clinker can be changed to 100°C, reducing tons of clinker The energy consumption of materials can be reduced, and the utilization of waste heat can be effectively improved.

2) The utility model has insulation materials between the waste heat recovery equipment and the clinker channel, which can prevent the high temperature airflow in the channel from directly washing the waste heat recovery device, and prevent the waste heat recovery device from bursting or being damaged due to high temperature washing.

3) By setting up a pressure measuring device, when the heat exchange tube bursts, the fluid flowing into the heat exchange tube is shut off in time.

4) By setting the cylinder, it is possible to perform radiative heat exchange to the heat exchange tube through the cylinder or conduct heat exchange through the heat transfer medium, which avoids direct contact between the heat exchange tube and the high-temperature insulation material, and avoids the occurrence of excessive temperature of the heat exchange tube. squib.

5) An intelligent control method for automatically adjusting the fluid flow in the heat exchange tube according to the outlet temperature of the clinker is provided, which meets the needs of production and saves energy.

6) The frequency of the fan is automatically adjusted according to the clinker outlet temperature of the grate cooler, so as to achieve the purpose of saving energy and realizing intelligent production.

7) The utility model provides a new heat dissipation pipe used in the waste heat system, and rationally arranges the heat dissipation fins of the heat dissipation pipe, so that more heat dissipation fins can be arranged, so it has a good heat dissipation effect.

Description of drawings

Fig. 1 is the schematic diagram of grate cooler;

Figure 2 is a schematic diagram of the installation of the waste heat recovery equipment of the grate cooler;

Fig. 3 is a schematic diagram of the structure of waste heat recovery equipment;

Figure 4 is a schematic diagram of the front view of the radiator in the waste heat recovery system;

Fig. 5 is a schematic diagram of the relative positions of the fluid channels of the radiator in the waste heat recovery system;

FIG. 6 is a schematic diagram viewed from the right side of FIG. 4 .

The reference signs are as follows:

1. Rotary kiln, 2. Kiln head cover, 3. Shell, 4. Grate cooler, 5. High temperature air outlet, 6. Low temperature air outlet, 7. Clinker outlet, 8. Fan, 9. Clinker channel, 10 , thermal insulation material, 11, waste heat recovery equipment, 12, connecting structure, 13, pipe plug, 14, cylinder body, 15, heat exchange tube, 16, pressure measuring device, 17, porous material, 18, elbow pipe, 19 , base tube, 20, first fluid channel, 21, first heat sink, 22, second heat sink, 23, second heat sink, 24, first waist, 25, second waist, 26, second fluid channel , 27, bottom edge, 28, valve.

detailed description

Below in conjunction with accompanying drawing, specific embodiment of the present utility model is described in detail.

A grate cooler waste heat recovery system for cement production, including a grate cooler. Figure 1 shows a grate cooler 4 for cement production. The grate cooler 4 includes a kiln head cover 2, a grate cooler shell 3, a high-temperature air outlet 5, Low-temperature air outlet 6, clinker outlet 7 and fan 8, wherein the clinker enters the grate cooler 4 from the rotary kiln 1, and then is transported in the clinker channel 9 in the grate cooler 4, and the fan 8 flows to the grate cooler 4 The air is supplied in the air, and the temperature of the clinker is lowered by the wind, so that the clinker is cooled during the transmission process, and the cooled clinker is output through the clinker outlet 7.

The clinker from the rotary kiln 1 is transported in the clinker channel 9 of the grate cooler, and is cooled by the wind delivered by the fan. An insulating material 10 is arranged between the shell 3 and the clinker channel 9, as shown in FIG. 2 . A waste heat recovery device 11 is arranged inside the material 10 .

Certainly, the fan in Fig. 1 is only a schematic diagram, and the fan conveys cooling air and blows upwards along the bottom of the clinker channel to cool the clinker in the clinker channel.

The reason why waste heat recovery equipment is installed in the insulation material is mainly because it is found during operation that the temperature of the clinker coming out of the clinker outlet is too high, which affects the quality of cement products, and also causes excessive energy consumption in the cement production process. Therefore, by setting up waste heat recovery equipment to recover the heat in cement cooling, the energy consumption of cement production can be further reduced, and the quality of cement products can be improved.

Preferably, the insulating material 10 is an insulating brick.

Preferably, there is an insulating material 10 between the waste heat recovery device 11 and the clinker channel. As shown in FIG. 2 , two layers of insulating bricks are arranged between the waste heat recovery equipment 11 and the clinker channel 9 . The main reason for setting the thermal insulation material is to avoid direct contact between the waste heat recovery equipment 11 and the high-temperature flue gas in the clinker channel 9 or being directly washed by the high-temperature flue gas. Avoid the heat exchange tube bundle in the waste heat recovery equipment from bursting due to high temperature and erosion.

As shown in FIG. 2 , preferably, the waste heat recovery device includes at least one cylinder body 14 , and a heat exchange tube 15 is arranged in the at least one cylinder body.

By setting the cylinder 14, the direct contact between the heat exchange tube and the insulation material is avoided, so that the heat exchange tube passes through the radiation of the cylinder 14 or conducts heat through the porous material, and prevents the heat exchange tube from bursting due to excessive temperature.

By setting the cylinder, another reason is to avoid fluid leakage and damage to the insulation material in the event of a pipe burst.

Preferably, there is a certain space between the cylinder body 14 and the heat exchange tube 15, and the space is preferably filled with a porous material 17 for heat conduction or heat storage.

Preferably, a pressure measuring device 16 for measuring cylinder pressure is also included. The pressure measuring device 16 is connected to the cylinder body 14, and by measuring the pressure in the cylinder body 14, it is checked whether the heat exchange tube 15 has exploded. Once a pipe explosion occurs, the measurement data of the pressure measuring device 16 will be abnormal, and Close the fluid valve entering the heat exchange tube 15 in time.

Preferably, the system further includes a control system and a valve 28, and the control system is connected to the valve 28 in data, and is used to control the opening and closing of the valve 28 and the flow rate of the valve 28. The control system is in data connection with the pressure measuring device 16 for detecting the pressure of the pressure measuring device 16 . Once the pressure of the pressure measuring device 16 detected by the control system exceeds a predetermined value, it indicates that the pressure is abnormal, and it is likely that the heat exchange tube 15 has exploded. At this time, the control system controls the valve 28 to close automatically. Through the above-mentioned automatic control function, the monitoring process is automated.

Preferably, the waste heat recovery device 11 includes a plurality of cylinders 14 , and the cylinders 14 communicate with each other through a communication structure 12 , and the pressure measuring device 16 is connected to any one of the plurality of cylinders 14 .

By setting the communication structure 12, multiple cylinders 14 are connected. Once a certain cylinder bursts, the pressure measurement device 14 will detect abnormal pressure at any time due to the connection, and the fluid valve will be automatically controlled to close. , to prevent the fluid from entering the heat exchange tube. In this way, the number of pressure measuring devices 16 can be reduced, and only one or a small number of pressure measuring devices can be used to realize the pressure detection of multiple cylinders.

Preferably, the outer surface of the lower part of the cylinder body 14 is pasted together with the thermal insulation material, and the heat exchange tube 15 has a certain distance from the inner surface of the lower part of the cylinder body 14 .

The outer surface of the lower part of the cylinder body 14 is attached to the insulation material to ensure heat transfer between the outer surface of the cylinder body 14 and the insulation material, and ensure that heat is transferred from the insulation material to the cylinder body through heat transfer. There is a certain distance between the heat exchange tube 15 and the inner surface of the lower part of the cylinder body 14 to realize radiation heat exchange, and avoid the direct contact between the heat exchange tube and the cylinder body to cause the temperature to be too high, thereby causing the tube explosion phenomenon to occur.

Preferably, the cylinder body 14 is rectangular, and the lower part of the cylinder body is a plane.

Preferably, there are multiple heat exchange tubes 15 , and at least two adjacent tube heat tubes are connected together through elbow tubes 18 . Preferably, the heat exchange tubes in each cylinder are connected by elbow pipes 18, so that the heat exchange tubes 15 in each cylinder 14 are connected in series as one heat exchange tube.

Preferably, the heat exchange tubes 15 have multiple rows, and each row has multiple heat exchange tubes. For example, as shown in Figure 2, two rows of heat exchange tubes are arranged perpendicular to the direction of the clinker channel.

Preferably, multiple heat exchange tubes in each cylinder 14 are connected in series through an elbow to form a heat exchange tube 15 with a separate inlet and outlet, while the heat exchange tubes 15 in multiple cylinders 14 are in a parallel structure. In this way, the heat exchange tubes of each cylinder 14 are individually provided with a valve, and by setting the valves individually, the control system can individually control each valve, thereby individually controlling the flow of fluid entering each cylinder.

Of course, as a preference, each cylinder can be provided with a pressure measuring device 16 independently, and the pressure in each cylinder can be automatically detected through the pressure measuring device 16, and when the pressure in a certain cylinder is detected to be abnormal, the valve of the cylinder is automatically closed , to prevent fluid from entering the heat exchange tubes of the cylinder.

Preferably, because the communication structure 12 is provided, a small number of pressure measuring devices can be provided, for example, only one. At this time, when the control system detects that the pressure is abnormal, it can control to close all valves or the main valve.

Preferably, a temperature measuring device can be used instead of the pressure measuring device 16 . The temperature measuring device is connected with the control system for data. When the detected temperature is lower than a certain value, that is, the measurement data will be abnormal, and the control system will close the fluid valve entering the heat exchange tube 15 in time.

Preferably, a humidity measuring device can be used instead of the pressure measuring device 16 . The humidity measuring device is connected with the control system for data. When the detected humidity is higher than a certain value, that is, the measurement data will be abnormal, and the control system will close the fluid valve entering the heat exchange tube 15 in time.

Preferably, the cylinder body 14 is filled with a porous material 17 for heat conduction or heat storage. By setting the porous material 17, excess heat can be stored, and at the same time, the heat can be transferred to the heat exchange tube 15 through heat conduction.

Preferably, a fluid communication channel is set in the porous medium 17 to detect internal fluid pressure.

The structure of the cylinder 14 shown in FIG. 3 , one end of the cylinder 14 is closed, and the other end is provided with a pipe plug 13 , and the pipe is a U-shaped pipe structure.

Of course, preferably, the plurality of tubes in the barrel 14 may be in parallel structure, for example, headers are arranged at the fluid inlet and outlet of the heat exchange tubes 15, similar to the headers of a heating radiator.

Preferably, the tubes between multiple cylinders 14 may be in series structure, that is, the heat exchange tubes 15 between adjacent cylinders 14 are connected in series through connecting pipes. This requires only one valve.

Preferably, in this case, the outer surface of the heat exchange tube 15 is coated with a heat absorbing material to enhance the absorption of radiation.

Preferably, along the direction of clinker transportation, the heat absorption capacity of the heat-absorbing materials of the heat exchange tubes 15 of different cylinders 14 is gradually enhanced, and further preferably, the range of enhanced heat absorption capacity is gradually increased. Through experiments, it is found that the waste heat absorption capacity can be increased by about 15% by setting in this way. Moreover, by setting in this way, the overall heat absorption of the heat exchange tubes can be made uniform, and the temperature difference becomes small, so as to ensure the overall life of the heat exchange tubes and avoid excessive temperature of some heat exchange tubes, resulting in constant and frequent replacement.

Preferably, along the transport direction of clinker, the thermal conductivity of the different cylinders 14 heat exchange tubes 15 and the porous materials 17 gradually increase, and further preferably, the degree of enhancement of the thermal conductivity gradually increases. Through experiments, it is found that by setting in this way, the residual heat absorption capacity can be provided by about 16%. The main reasons are similar to the previous ones.

Preferably, along the transportation direction of the clinker, the heat storage capacity of the different cylinders 14 heat exchange tubes 15 and the porous materials 17 gradually increase, and further preferably, the degree of heat storage capacity enhancement gradually increases. The main reasons are similar to the previous ones.

In this solution, by arranging porous material layers 17 of the same material and different thermal conductivity at different positions, different enhancements of the heat absorption capacity of the heat exchange tubes 15 at different positions can be achieved. Porous material layers 17 of different materials can also be directly selected to obtain different heat absorption capabilities.

Preferably, an endothermic material is provided on the outer surface of the barrel 14 . The main reason is that part of the heat exchange between the insulating material and the cylinder body 14 also has radiation heat exchange, so it is necessary to install a heat storage material to increase the heat absorption.

Preferably, along the conveying direction of the clinker, the heat-absorbing capabilities of the heat-absorbing materials on the surfaces of different cylinders 14 are gradually enhanced, and further preferably, the range of enhanced heat-absorbing capabilities gradually increases. The main reasons are similar to the previous ones.

Preferably, protrusions are provided on the outside of the cylinder body 14 . The heights of the protrusions on the surface of different cylinders are different. Along the transportation direction of the clinker, the heights of the protrusions on the surface of different cylinders gradually increase, and further preferably, the increase range gradually increases. The main reasons are similar to the previous ones.

Preferably, protrusions are provided on the outside of the cylinder body 14 . The density of protrusions on the surface of different cylinders is different. Along the transportation direction of the clinker, the density of the protrusions on the surface of different cylinders increases gradually, and further preferably, the increase range gradually increases. The main reasons are similar to the previous ones.

As a preference, the grate cooler further includes a clinker outlet temperature detection device for detecting the clinker temperature at the clinker outlet. The temperature detection device is connected with the control system data. The control system automatically controls the opening of the valve according to the detected clinker temperature, thereby controlling the flow of fluid entering the heat exchange tube.

When the detected temperature of the clinker outlet is too high, the opening of the valve will be automatically increased to increase the flow of fluid entering the heat exchange tube. If the detected temperature is too low, the opening of the valve will be automatically reduced to reduce the flow of fluid entering the heat exchange tube. fluid flow. By automatically adjusting the flow rate of the fluid, the quantity of the fluid involved in the heat exchange can be automatically adjusted, thereby realizing the adjustment of the temperature of the clinker at the clinker outlet, meeting the needs of production, and ensuring the quality of cement.

The control system can automatically adjust the flow rate according to the outlet temperature. The control method is as follows: when the outlet temperature is T, the flow rate V indicates that the clinker temperature condition for cement production is satisfied. The above outlet temperature T and flow rate V are standard data. The standard data are stored in the control system.

When the outlet temperature becomes t, the flow v changes as follows:

v=b*V*(t/T) ^a , wherein a is a parameter, 1.06<a<1.10; preferably, a=1.08;

b is an adjustment coefficient, (t/T)>1,0.97<b<1.00; preferably 0.98;

(t/T)<1, 1.00<b<1.04; preferably 1.02;

(t/T)=1, b=1;

0.85<t/T<1.15.

In the above formula, temperature T, t is the absolute temperature, the unit is K, the flow rate V, the unit of v is m/s, which is the total flow rate entering the waste heat recovery equipment.

Preferably, when the heat exchange tubes 15 of a plurality of cylinders 14 are connected in parallel, when the flow rate is adjusted, the rate of increase or decrease of the flow rate of the heat exchange tubes of each cylinder is the same.

Preferably, the flow rates of the heat exchange tubes 15 of each cylinder 14 increase or decrease in different proportions, and along the direction of clinker transportation, the increase or decrease proportions become smaller and smaller. Further preferably, the range of increasing or decreasing ratio becomes smaller and smaller. It is found through experiments that the control data can be made more accurate and the error is smaller through the setting of the change of the flow amplitude, and the error can be reduced by about 30%.

Through the above formula, it is possible to realize the intelligence of automatically adjusting the flow rate according to the outlet temperature, saving energy and improving production efficiency.

As an advantage, multiple sets of standard data can be entered into the control system. When there are two or more sets of benchmark data, an interface for user-selected benchmark data can be provided. Preferably, the control system can automatically select the one with the smallest value of (1−t/T) ² .

Preferably, the control system includes a fan frequency adjusting device, which can control the fan frequency according to the clinker temperature at the clinker outlet, so as to adjust the flow of wind entering the grate cooler to cool the clinker. When the temperature is too high, the fan frequency will be automatically increased to increase the air supply volume. If the detected temperature is too low, the fan frequency will be automatically reduced to reduce the air supply volume.

Of course, fan frequency control and fluid flow control can be combined to control clinker outlet temperature together.

Preferably, the fluid heated in the heat exchange tube 15 is used for power generation by the waste heat boiler.

Preferably, the heat exchange pipe 15 is connected to a heating radiator, so that the heated water is used for heating.

Preferably, the water in the heat exchange tube 15 can be directly transported to the heating radiator, or can pass through the heat exchanger to transfer heat to the heating water, and then the heating water enters the heating radiator for heating. The radiator includes an upper header and a lower header and cooling pipes located on the upper header and the lower header.

As shown in Figures 4 and 5, the radiating tube used by the radiator includes a base tube 19 and cooling fins 21-23 positioned at the periphery of the base tube, as shown in Figures 4 and 5, the base tube The cross section is an isosceles triangle, and the radiating fins include a first radiating fin 21, a second radiating fin 22, and a second radiating fin 23, and the first radiating fin 21 extends outward from the vertex of the isosceles triangle, so The second cooling fins include a plurality of second cooling fins 22 extending outward from the two sides of the isosceles triangle and a plurality of second cooling fins 23 extending outward from the first cooling fins. The second cooling fins 22 and the second cooling fins 23 are parallel to each other. Parallel, the second cooling fins 22 and the second cooling fins 23 extending outward from the first waist 24 of the isosceles triangle (i.e. the waist on the right side) are parallel to each other, the first cooling fins 21, the second cooling fins 22, the second cooling fins The extended end of fin 23 forms a second isosceles triangle, as shown in Figure 4, the length of the waist of the second isosceles triangle is S; the first fluid channel 20 is set inside the base pipe 19, and the first heat dissipation A second fluid channel 26 is arranged inside the sheet 21 , and the first fluid channel 21 communicates with the second fluid channel 26 . For example, as shown in FIG. 4 , it is connected at the vertices of an isosceles triangle.

Through such a structural arrangement, a plurality of cooling fins can be arranged outside the base pipe 19 to increase heat dissipation, and at the same time, a fluid channel is arranged inside the first cooling fin 21, so that the fluid enters the first cooling fin 21 and directly communicates with the first cooling fin. 21 connected to the second heat sink 22 for heat exchange, increasing the heat dissipation capacity.

Generally, heat sinks are installed around or on both sides of the heat pipe, but it is found in the project that the heat sink on the side that is in contact with the wall is generally not effective in convective heat transfer, because the air flow on the wall side is relatively poor, so this The utility model sets the base 27 of the isosceles triangle as a plane, so when installing the heat sink, the plane can be directly in close contact with the wall. Compared with other radiators, the installation space can be greatly saved, and space waste can be avoided. The special heat sink form ensures the best heat dissipation effect.

Preferably, the second heat sink 22 and the second heat sink 23 are mirror-symmetrical to the plane where the midline of the first heat sink 21 is located, that is, to the plane where the midpoint of the apex and the base of the isosceles triangle is located. Surface mirror symmetry.

Preferably, the second cooling fins 22 and the second cooling fins 23 extend perpendicularly to the two waists of the second isosceles triangle.

When the length of the side of the isosceles triangle is constant, the longer the first heat sink 21, the second heat sink 22, and the second heat sink 23, the better the heat exchange effect is in theory. When the cooling fins 21, the second cooling fins 22, and the second cooling fins 23 reach a certain length, the heat exchange effect is not significantly increased, mainly because the first cooling fins 21, the second cooling fins 22, the second cooling fins As the length of the sheet 23 increases, the temperature at the end of the heat sink becomes lower and lower. As the temperature drops to a certain level, the heat exchange effect will not be obvious. On the contrary, the cost of materials and the occupation of the heat sink will be greatly increased. At the same time, during the heat exchange process, if the distance between the second cooling fins is too small, it is easy to cause the deterioration of the heat exchange effect, because as the length of the heat pipe increases, the boundary layer becomes thicker when the air rises, resulting in a relatively The boundary layers between the adjacent heat sinks overlap each other, which deteriorates the heat transfer. The length of the heat pipe is too low or the distance between the second heat sinks is too large, which reduces the heat transfer area and affects the heat transfer. Therefore, the adjacent second heat sink The distance between the fins, the side length of the isosceles triangle, the lengths of the first fin and the second fin and the length of the heat sink base satisfy an optimal dimensional relationship.

Therefore, the utility model is the best size optimization relationship of the radiator summarized through thousands of test data of radiators of different sizes.

The distance between the adjacent second cooling fins is L1, the length of the base of the isosceles triangle is W, and the length of the waist of the second isosceles triangle is S. The relationship between the above three satisfies the following formula:

L1/S*100＝A*Ln(L1/W*100)+B*(L1/W)+C, where Ln is a logarithmic function, A, B, and 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 apex angle of an isosceles triangle is a, 110°<a<160°.

Preferably, the length of the base pipe 19 is L, 0.02<W/L<0.08, 800mm<L<2500mm.

As preferred, A=0.69, B=24.6, C=8.3.

It should be noted that the distance L1 between adjacent second heat sinks is the distance calculated from the center of the second heat sink, as shown in FIG. 1 .

After calculating the results and then conducting experiments, the results obtained by calculating the boundary and intermediate values are basically consistent with the formula, the error is basically within 3.54%, the largest relative error is not more than 3.97%, and the average error is 2.55%.

Preferably, the distances between the adjacent second cooling fins are the same.

Preferably, the width of the first heat sink 21 is greater than the widths of the second heat sink 22 and the second heat sink 23 .

Preferably, the width of the first heat sink 21 is b1, and the widths of the second heat sink 22 and the second heat sink 23 are b2, wherein 2.2*b2<b1<3.1*b2;

Preferably, 0.9mm<b2<1mm, 2.0mm<b1<3.2mm.

Preferably, the width of the second fluid channel 26 is 0.85-0.95 times, preferably 0.90-0.92 times, the width of the second heat sink 22 .

The widths b1 and b2 here refer to the average width of the heat sink.

Although the utility model has been disclosed above with preferred embodiments, the utility model is not limited thereto. Any person skilled in the art can make various changes and modifications without departing from the spirit and scope of the present utility model, so the protection scope of the present utility model should be based on the scope defined in the claims.

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.