A cooling system for uniform cooling

Abstract

This invention addresses the problem of uneven bottom cooling air intake and poor cooling effect in existing sinter cooling systems by disclosing a uniform cooling system. It utilizes an airflow regulating mechanism with multiple independently adjustable vents at the air box outlet. Based on real-time airflow distribution differences and resistance differences between the inner and outer sides of the sinter layer, the opening of the vents on both sides of the airflow regulating mechanism is adjusted to uniformly distribute the airflow across the inner and outer sides of the sinter layer, thereby achieving uniform cooling of the sinter and improving its cooling effect. This system boasts advantages such as simple overall structure, low investment cost, ease of operation, high control precision, and good flexibility. It has excellent prospects for large-scale promotion and application.

Description

Technical Field

[0001] This utility model relates to cooling equipment for sintered ore, specifically to a uniform cooling system, and belongs to the field of sintered ore cooling technology. Background Technology

[0002] The equipment system centered around the annular cooler is currently the mainstream equipment for cooling sintered ore. The cooling principle involves blowing cooling air into the lower part of the sintered ore bed via a blower as the trolley transports the sintered ore forward, thereby reducing the temperature of the sintered ore from approximately 700-750 degrees Celsius to 120-150 degrees Celsius. During this process, the uniformity of the cooling air distribution in the lower part of the sintered ore bed significantly affects the cooling effect. It is highly susceptible to regional variations in the cooling air distribution, resulting in some sintered ore receiving better cooling while others fail to meet the cooling requirements. Generally, due to the wide width of the sintered ore bed (typically exceeding 4m), the uniformity of the cooling air distribution is influenced by multiple factors, including the uniformity of the sintered ore bed distribution, the structure of the lower air box, and the air supply duct. In actual operation, uneven distribution of cooling air in the lower part of the material layer in the inner and outer rings is caused by problems such as uneven material distribution in the inner and outer rings of the trolley and unreasonable wind box structure design. This results in a large temperature difference (30-40 degrees Celsius) between the unloading of sinter in the inner and outer rings, making it difficult for some sinter to meet production requirements. For projects already in operation, it is difficult to modify the feeding chute and wind box structure. Therefore, in order to solve the problem of poor local cooling effect caused by uneven cooling air distribution, the engineering site often adopts the method of increasing the air volume of the fan to improve the cooling effect of the sinter. However, this will increase the power consumption of the fan to a certain extent, thereby increasing the operating cost. Utility Model Content

[0003] To address the problem of uneven bottom cooling air intake leading to poor cooling effect in existing sinter cooling systems, this invention provides a uniform cooling system. By installing an airflow regulating mechanism with multiple independently adjustable vents at the air box outlet, the opening of the vents on both sides of the sinter layer can be adjusted based on real-time airflow distribution differences and air resistance differences along the width of the sinter layer. This uniformly distributes the airflow evenly across the inner and outer sides of the sinter layer, thereby achieving uniform cooling of the sinter and improving its cooling effect.

[0004] To achieve the above-mentioned technical objectives, the technical solution adopted by this utility model is as follows:

[0005] A uniform cooling system includes a frame, a trolley, a hot air hood, an air box, and an airflow regulating mechanism. A support rail is mounted on the frame, and the trolley is positioned on and runs along the support rail. The hot air hood covers the trolley, and the air box is positioned below the trolley. The airflow regulating mechanism is located between the trolley and the air box, and has multiple independently adjustable vents along its width. By controlling the opening of each vent in the airflow regulating mechanism, uniform cooling airflow is achieved between the air box and the trolley.

[0006] Preferably, the airflow regulating mechanism comprises multiple vent regulators, each including an adjustment drive and vent blades. The adjustment drive is mounted on a frame on one side of the top of the air box. Multiple vent blades are horizontally arranged at the air outlet of the air box, with one end of each blade connected to the adjustment drive. By adjusting the tilt angle of the vent blades relative to the vertical plane using the adjustment drive, the opening size of the vent regulator is adjusted.

[0007] Preferably, the plurality of vent regulators are arranged side by side in the width direction of the air box, and the vent opening of each of the plurality of vent regulators is adjusted independently.

[0008] Preferably, the air volume regulating mechanism consists of two vent regulators arranged side by side in the width direction of the air box.

[0009] Preferably, the adjustment drive includes an electric cylinder, a push rod, a connecting rod, an adjusting rod, and a rotating shaft. The electric cylinder is mounted on a frame on one side of the top of the air box. One end of the push rod is connected to the electric cylinder, the other end of the push rod is connected to one end of the connecting rod, and the other end of the connecting rod is connected to one end of the adjusting rod. The adjusting rod is horizontally positioned and perpendicular to the air outlet blades. The adjusting rod is connected to multiple air outlet blades via multiple rotating shafts. The electric cylinder drives the adjusting rod to move along its axial direction via the push rod and the connecting rod, thereby causing the rotating shaft to rotate. The rotation of the rotating shaft causes the air outlet blades to rotate, thus adjusting the tilt angle of the air outlet blades relative to the vertical plane.

[0010] Preferably, multiple pressure gauges are also provided on the bottom side of the airflow regulating mechanism. These pressure gauges are evenly distributed along the width of the air box.

[0011] Preferably, multiple anemometers are also provided on the bottom side of the airflow regulating mechanism. These anemometers are evenly distributed along the width of the air box.

[0012] Preferably, multiple infrared material temperature detectors are also provided at the rear of the hot air hood. These infrared material temperature detectors are evenly distributed along the width of the inner wall of the hot air hood.

[0013] Preferably, the cooling system is an annular cooler. Preferably, each air box has an independent cooling fan at its bottom air inlet. Preferably, an inlet pressure gauge and an outlet pressure gauge are respectively installed at the air inlet and outlet of the cooling fan.

[0014] The process of cooling sintered materials using the cooling system of this invention is as follows:

[0015] 1) The hot material is loaded into the trolley and runs along the support track. During the operation, the hot material in the trolley is cooled by blowing cooling air into the air box.

[0016] 2) During the heat exchange and cooling process, adjust the opening of each vent of the air volume regulating mechanism to ensure that the hot material in the trolley is cooled evenly.

[0017] Preferably, step 2) specifically includes:

[0018] 201) During the heat exchange and cooling process, the average air pressure on both sides of the wind box in the width direction is monitored in real time, and the average air pressure difference is obtained. If the average air pressure difference is not greater than the allowable air pressure difference, the current operating condition is maintained. If the average air pressure difference is greater than the allowable air pressure difference, then proceed to step 202).

[0019] 202) Real-time detection of the average wind speed on both sides of the windbox width direction, and calculation of the actual material thickness, actual air volume, target air volume and target average air pressure on both sides of the windbox width direction based on the measured average wind speed and measured average air pressure on both sides of the windbox width direction.

[0020] 203) Calculate the increase in wind resistance on the side with a thinner material layer based on the target average wind pressure on the side with a thinner material layer in the width direction of the wind box. Reduce the opening of the ventilation opening on the side with a thinner material layer by adjusting the air volume so that the increase in wind resistance on that side meets the working condition requirements.

[0021] Preferably, in step 202), the actual material thickness on the outer side, the actual material thickness on the inner side, the actual air volume on the outer side, the actual air volume on the inner side, the target air volume on the outer side, the target air volume on the inner side, the target average air pressure on the outer side, and the target average air pressure on the inner side in the width direction of the bellows are respectively denoted as h. 外实 (m), h 内实 (m), Q 外实 (m) 3 / h), Q 内实 (m) 3 / h), Q 外目 (m) 3 / h), Q 内目 (m) 3 / h), R 外目 (Pa), R内目 (Pa), then we have:

[0022] h 外实 =R 外实 / (1275×V 外实 1.67 ) (I).

[0023] h 内实 =R 内实 / (1275×V 内实 1.67 (II).

[0024] Q 外实 =V 外实 ×3600E 外 (III).

[0025] Q 内实 =V 内实 ×3600E 内 (IV).

[0026] Q 外目 =(Q 外实 +Q 内实 ) / (1+h 内实 / h 外实 ) (V).

[0027] Q 内目 =(Q 外实 +Q 内实 ) / (1+h 外实 / h 内实 (VI).

[0028] R 外目 =1275×h 外实 ×[Q 外目 / (3600E 外 )] 1.67 (VII).

[0029] R 内目 =1275×h 内实 ×[Q 内目 / (3600E 内 )] 1.67 (VIII).

[0030] In equations (I) to (VIII), R 外实 R represents the measured average wind pressure on the outer side of the bellows along its width direction, in Pa. 内实 V represents the measured average wind pressure on the inner side of the bellows along its width direction, in Pa. 外实 V represents the measured average wind speed on the outer side of the bellows along its width, in m / s. 内实E represents the measured average wind speed on the inner side of the bellows along its width direction, in m / s. 外 The ventilation cross-sectional area on the outer side of the bellows in the width direction is m. 2 E 内 The ventilation cross-sectional area on the inner side of the bellows along its width direction is in meters. 2 .

[0031] Preferably, in step 203), the increase in wind resistance on the side with a thinner material layer in the width direction of the windbox is recorded as △P (Pa).

[0032] If h 外实 =h 内实 Simply adjust the opening and ventilation volume of the vents on both sides of the bellows in the width direction to be consistent.

[0033] If h 外实 <h 内实 Then we have:

[0034] △P=P / [h 外实 ×P / (h 内实 ×R 内目 )]-R 外目 (IX).

[0035] If h 外实 >h 内实 Then we have:

[0036] △P=P / [h 内实 ×P / (h 外实 ×R 外目 )]-R 内目 (X).

[0037] In equations (IX) to (X), P is the total pressure provided by the cooling fan, in Pa.

[0038] The difference between the target air volume and the actual air volume on the side with the thinner material layer in the width direction of the bellows is set to △Q (m). 3 / h). The area of ​​the vent that is obstructed after the airflow resistance increase on the side with a thinner material layer is reduced by the airflow adjustment mechanism to meet the working condition requirements is denoted as A (m). 2 Then we have:

[0039] A = sqrt[△P / (0.5×ρ×C] d ×△Q 2 / 3600 2 )] (XI).

[0040] In equation (XI), ρ is the cooling air density, kg / m³. 3 C dThe blade resistance coefficient at the airflow regulating mechanism's vent is 0.3~0.9. The increase in air resistance on the side with a thinner material layer in the width direction of the air box is calculated as ΔP according to formula (IX) or formula (X). The opening of the vent on the side with a thinner material layer is reduced by the airflow regulating mechanism to achieve the target of ΔP, so that the obstructed area of ​​the vent on that side is the calculated value A of formula (XI).

[0041] Preferably, the rotation angle of the air outlet blades is adjusted by controlling the running time of the regulating drive, thereby increasing the air resistance on the side of the airflow regulating mechanism with a thinner material layer by ΔP. Wherein:

[0042] t=arcsin{sqrt[(0.5×ρ×C d ×△Q 2 / 3600 2 ) / (△P×h 2 ×b 2 ×n 2 )]} / (57.3u)(XII)。

[0043] In equation (XII), t is the pushing time of the push rod, s; ​​h is the length of a single air outlet blade, m; b is the width of a single air outlet blade, m; n is the number of air outlet blades, blades; and u is the axial pushing speed of the push rod, m / s. The running time of the adjustment drive on the side of the thinner material layer of the airflow control mechanism is the calculated value t in equation (XII) above, which in turn causes the wind resistance on the side of the thinner material layer to increase by ΔP.

[0044] It should be noted that all formulas in this utility model are obtained by the inventor based on experiments and engineering applications, and all calculations are obtained by converting values ​​according to the specified units and substituting the converted values ​​into the formulas (after converting the units, only the values ​​are substituted into the formulas for calculation, not the units; the units are only used to adjust the size of the values).

[0045] In existing technologies, during the forced-air cooling process of sinter, the uniformity of cooling air distribution from the lower part of the material layer is easily affected by multiple factors, such as the material layer distribution state (material distribution uniformity), the structure of the lower air box, and the air supply pipeline. This results in uneven cooling air distribution on both sides of the lower part of the material layer (referring to the two sides perpendicular to the material running direction, i.e., the two sides in the width direction of the material layer) during actual forced-air cooling, leading to a large temperature difference in the unloading of sinter on both sides of the material layer. However, modifying the material distribution chute and air box structure to achieve uniform material distribution and air supply is difficult and costly for existing projects. To address this problem, this invention introduces a specially structured airflow regulating mechanism between the trolley and its bottom air box. This mechanism adjusts the intake airflow of cooling air from the air box, allowing for control of the cooling airflow in the width direction based on the current material distribution status. This ensures a uniform distribution of airflow entering the material layer in the width direction, thereby achieving uniform cooling of the sinter.

[0046] In this invention, the airflow regulating mechanism is a multi-ventilation structure with multiple independently adjustable openings in the width direction. Specifically, the airflow regulating mechanism divides the top air outlet of the wind box into multiple independently adjustable air outlet areas in the width direction. When the upper sintered ore layer changes, the thinner material layer in the width direction allows cooling air to pass more easily, resulting in relatively lower wind resistance and a higher wind speed (i.e., larger airflow) in that area compared to other areas. Therefore, the airflow regulating mechanism can reduce the opening of the vent in that area, thereby increasing the wind resistance and reducing the wind speed (generally, with a fixed airflow from the blower of the annular cooler, reducing the wind speed on the thinner side is equivalent to increasing the wind speed on the thicker side, thus making the cooling efficiency of the material more uniform). This reduces and unifies the wind speed difference in the width direction of the wind box.

[0047] In this invention, the airflow regulating mechanism consists of multiple vent regulators, each with an independently adjustable vent opening. This means that the cooling airflow area can be divided into multiple zones along the width direction. Furthermore, based on real-time changes in the material distribution in each zone, the opening of the corresponding vent regulator can be controlled, resulting in a relatively uniform airflow along the width direction, which is beneficial for the uniform cooling of the sinter. In a preferred embodiment of this invention, the airflow regulating mechanism consists of two vent regulators arranged side-by-side along the width direction of the air box, effectively dividing the air box outlet into two vents (referred to as the outer vent and the inner vent) along the width direction.

[0048] In this invention, the vent regulator includes an adjustment drive and vent blades. The adjustment drive includes an electric cylinder, a push rod, a connecting rod, an adjusting rod, and a rotating shaft. The electric cylinder, push rod, connecting rod, adjusting rod, rotating shaft, and vent blades are connected in series. That is, the electric cylinder drives the push rod to move along its axial direction. The adjusting rod is parallel to the push rod. The connecting rod is perpendicularly connected to both the push rod and the adjusting rod. When the push rod moves along its axial direction, it can drive the adjusting rod to move axially synchronously through the connecting rod. The rotating shaft is perpendicularly connected to the adjusting rod, and the axial movement of the adjusting rod can drive the rotating shaft to rotate (for example, the bottom side of the adjusting rod has an axial rack design, and one end of the rotating shaft is a gear design that meshes with the rack and pinion of the adjusting rod. Alternatively, the adjusting rod and the rotating shaft can be designed with a ball screw). The other end of the rotating shaft is connected to one end of the vent blades, and the vent blades are located at the air outlet of the air box. It should be noted that the air outlet of the bellows is generally equipped with multiple air vent blades. Each air vent blade is connected to an adjusting rod via a rotating shaft, and the rotation of all air vent blades associated with the same adjusting rod is synchronized. It should also be noted that the air vent regulator is initially in a fully open state, meaning the angle between the air vent blade and the vertical direction is 0 degrees (the air vent blade surface is vertical). Conversely, when the angle between the air vent blade and the vertical direction is 90 degrees (the air vent blade surface is horizontal), the air vent is in a fully closed state. In other words, by varying the angle between the air vent blade and the vertical direction between 0 and 90 degrees, the opening degree of the corresponding air vent can be adjusted.

[0049] In this invention, multiple pressure gauges (used to determine whether there is a significant difference in resistance between the inner and outer sides due to uneven material distribution, thus affecting the distribution of airflow in the lower part of the material layer) and multiple wind speed gauges (used, on the one hand, to determine whether there is a difference in airflow between the inner and outer sides due to unreasonable design of the air box and air supply branch pipe structure, and on the other hand, to verify the adjustment effect of the airflow adjustment mechanism) are also provided on both sides of the bottom width direction of the airflow adjustment mechanism. For example, an outer pressure gauge, an inner pressure gauge, an outer wind speed gauge, and an inner wind speed gauge are respectively provided on both sides of the bottom width direction of the airflow adjustment mechanism. The pressure gauges and wind speed gauges monitor the wind speed and wind pressure changes in the bottom width direction of the airflow adjustment mechanism in real time, thereby providing a basis for adjusting the opening of the ventilation outlets of the ventilation outlet regulators in different areas of the airflow adjustment mechanism, and thus achieving precise control of airflow.

[0050] In this invention, the main reason for the uneven distribution of cooling air is the difference in air supply resistance between the inner and outer sides of the wind box in the width direction due to the uneven distribution of the material layer. This leads to a difference in the flow rate of the cooling air between the inner and outer sides (i.e., different flow rates per unit time). Therefore, the air outlet of the wind box is divided into multiple ventilation openings of equal size and independently adjustable openings in the width direction. The opening of each ventilation opening can be adjusted according to the difference in flow rate and pressure of the cooling air in each area in the width direction, thereby achieving uniform air supply in each area in the width direction. Taking an annular cooler as an example, an inner ventilation opening (or inner ring ventilation opening) and an outer ventilation opening (or outer ring ventilation opening) are respectively set in the width direction on the bottom side of its material layer. That is, two ventilation opening regulators are arranged side by side along the width direction at the air outlet at the top of the wind box. In actual engineering, the control process is as follows:

[0051] (S1) During the initial operation, keep both ventilation outlets of the air volume regulating mechanism fully open (i.e., the initial state is fully open by default); obtain the unloading temperature monitoring data of the inner and outer rings of the annular cooler after a period of operation, and take the average value T. w and T n The calculation yields ΔT=T w -T n If |ΔT|≥20℃, the air volume adjustment mechanism needs to be activated for adjustment.

[0052] (S2) Obtain the cooling air supply pressure monitoring data of the outer and inner rings in the width direction of the air box, obtained by the pressure detectors at the outer and inner rings of the ring cooler during a period of operation, and record the average value as R. 外实 and R 内实 The calculation yields ΔR = R 外实 -R 内实 If |△R|≤200Pa, it indicates that there is no significant difference in the distribution of the inner and outer ring material layers (no adjustment is needed). If |△R|>200Pa, it indicates that there is a difference in the distribution of the inner and outer ring material layers, then proceed to the next step.

[0053] (S3) Calculate the standard values ​​of air volume distribution in the inner and outer rings (i.e., the target values ​​for subsequent regulation) based on the pressure monitoring data of the inner and outer rings. The calculation process is as follows:

[0054] First, determine the target airflow required to achieve consistent cooling effects between the inner and outer rings, and the change in airflow compared to the current state:

[0055] With the airflow regulator fully open, the pressure measured by the pressure gauges on both sides of the air box (4) in the width direction is the flow resistance value of the fluid passing through the bed. Based on the relationship between the material bed resistance and the material bed height and surface wind speed obtained during actual operation, R=1275hV 1.67 The height values ​​of the inner and outer bed layers can be calculated separately:

[0056] h 外实 =R 外实 / (1275×V 外实 1.67 ) (I).

[0057] h 内实 =R 内实 / (1275×V 内实 1.67 (II).

[0058] Due to the material layer height h 外实 and h 内实 With sinter quantity K 外 and K 内 The amount of sintered ore is directly proportional to the target air volume Q required for the inner and outer rings to achieve the cooling requirements. 外目 and Q 内目 Proportional, then in the total air volume Q 总 Assuming that the conditions remain unchanged, then we have

[0059] h 外实 :h 内实 =Q 外目 :Q 内目 .

[0060] Q 外目 +Q 内目 =Q 总 .

[0061] The cooling air delivery speed data of the inner and outer rings of the air box were obtained by using an anemometer during a period of operation of the annular cooler, and the average value V was taken. 外实 and V 内实 And calculate the actual flow rate Q of the current air volume based on the ventilation cross-sectional area (E, which is generally the same on the inside and outside). 外实 and Q 内实 The calculation formula is:

[0062] Q 外实 =V w ×3600E.

[0063] Q 内实 =V n ×3600E.

[0064] Where 3600 is the conversion ratio between hours and seconds (because the unit of cooling airflow in this utility model is m³ / s). 3 / h (cooling air velocity is in m / s). The formula for calculating the target airflow is:

[0065] Q 外目 =(Q 外实 +Q 内实 ) / (1+h内实 / h 外实 ) (V).

[0066] Q 内目 =(Q 外实 +Q 内实 ) / (1+h 外实 / h 内实 (VI).

[0067] The required reduction in airflow on the side with the thinner material layer (assuming it's the outer side) is:

[0068] △Q 外 =Q 外实 -Q 外目 =V 外实 ×3600E-(V 外实 ×3600E+V n实 ×3600E) / (1+h 内实 / h 外实 ).

[0069] Secondly, calculate the flow resistance corresponding to the target air volume:

[0070] When the airflow rates of the inner and outer rings change, the corresponding flow resistance of the fluid through the bed will also change. Since the bed distribution remains unchanged during one revolution of the annular cooler, the flow resistance R corresponding to the target airflow rate can be calculated based on the calculated bed height and target airflow rate. 外目 and R 内实 :

[0071] R 外目 =1275×h 外实 ×[Q 外目 / (3600E 外 )] 1.67 (VII).

[0072] R 内目 =1275×h 内实 ×[Q 内目 / (3600E 内 )] 1.67 (VIII).

[0073] Finally: Calculate the pressure adjustment value ΔP (i.e., the increase in air resistance on the side with the thinner material layer, in Pa):

[0074] For the flow state of a fluid in a porous medium, the relationship between flow rate and pressure can be characterized by the following formula:

[0075] Q = P / R.

[0076] In the above formula, P is the difference between the inlet and outlet pressures of the fluid under the drive of the fan. Since the outlet pressure is basically slightly negative or zero, it is generally considered to be zero. Therefore, P is the total pressure provided by the fan (the measured value, the actual drive provided by the fan, i.e., the difference between the fan outlet pressure and the inlet pressure). R is the flow resistance, which is related to the bed height, porosity, etc. As previously obtained:

[0077] h 外实 :h 内实 =Q 外目 :Q 内目 .

[0078] Then we have:

[0079] P / (R 外目 +△P)=h 外实 ×P / (h 内实 ×R 内目 ).

[0080] Furthermore, the formula for calculating the adjustment amount of the air volume regulator and the relationship between the change in the opening degree of the air volume regulator and the change in the material layer resistance ΔP is as follows:

[0081] △P=0.5×ρ×C d ×△Q w 2 / (3600A) 2 .

[0082] (S4) Adjust the opening of the vent regulator on the side with a thinner material layer (assuming it's the outer side) to increase the resistance of the cooling air passing through the vent regulator on that side, and the increased resistance value is ΔP. ​​The adjustment method of the vent regulator on this side is as follows:

[0083] (S401) The vent regulator includes an adjustment drive and vent blades. The adjustment drive includes an electric cylinder, a push rod, a connecting rod, an adjustment rod, and a rotating shaft (the specific connection relationship is as described above and will not be repeated here). During the operation of this vent regulator, the axial movement distance of the push rod is set to w (m), the axial movement speed of the push rod is u (m / s), the axial movement time of the push rod is t (s), the rotation angle of the vent blade is α (°), the length of a single vent blade is h (m), the width of a single vent blade is b (m), the number of vent blades is n (blades), and the cooling air density is ρ (kg / m³). 3 The blade drag coefficient is C. d The current obstructed area of ​​the air outlet blades of the vent regulator on the side with the thinner material layer is A (m²). 2 );in:

[0084] w = u × t.

[0085] α = w × 57.3.

[0086] A = n × h × b × sinα.

[0087] △P=0.5×ρ×C d ×△Q w 2 / (3600A) 2 .

[0088] During the adjustment of the vent regulator on this side, the wind resistance ΔP is mainly adjusted by the axial movement time of the push rod driven by the electric cylinder. Therefore, by combining the above equations, we can obtain:

[0089] t=arcsin{sqrt[(0.5×ρ×C d ×△Q 2 / 3600 2 ) / (△P×h 2 ×b 2 ×n 2 )]} / (57.3u)(XII)。

[0090] That is, starting the electric cylinder causes the push rod to move axially for a time equal to the calculated value t of equation (XII), which in turn increases the wind resistance on the side with the thinner material layer by ΔP. 57.3 is the conversion factor for converting radians to angles.

[0091] In addition, after completing the above adjustments, further testing and verification can be performed. The verification process is as follows:

[0092] (S5) Obtain the cooling air delivery speed monitoring data of the outer and inner rings of the air box detected by the anemometer at the outer ring and the anemometer at the inner ring during a period of operation of the annular cooler, and record the average value as V. 外实 and V 内实 The calculation yields ΔV = V 外实 -V 内实 If |△V|≤0.1m / s, no adjustment is needed; if |△V|>0.1m / s, proceed to the next step.

[0093] (S6) Adjust the vent regulator on the side with a thinner material layer. Each time it is adjusted, the rotation angle of the vent blades on that side is 0.1 to 0.5 degrees. After the adjustment is completed, keep the ring cooler running for a period of time and determine whether the difference in cooling air speed between the inner and outer rings, |△V|, is within the target range. If it is, the adjustment is successful. If not, continue to adjust. The adjustment method is the same as described in step (S4).

[0094] In this invention, the width of the bellows is 0.5-20m, preferably 1-15m, and more preferably 3-10m. The number of vents in the airflow regulating mechanism is 1-30, preferably 2-20, and more preferably 2-10. The number of air vent blades in any vent regulator is 1-100, preferably 5-80, and more preferably 10-60.

[0095] Compared with the prior art, the beneficial technical effects of this utility model are as follows:

[0096] 1. This utility model creatively proposes to set up an air volume adjustment mechanism with independent adjustment function of multiple ventilation ports between the wind box and the trolley. In this way, without changing the original structure of the wind box or the material distribution mechanism, the cooling air from the wind direction can be adjusted in real time according to the change of the material distribution state, thereby achieving uniform air supply in the width direction of the material layer and significantly improving the cooling effect of sinter.

[0097] 2: The cooling system provided by this utility model has a simple overall structure, low investment cost, easy operation, high control precision, and good flexibility, and has excellent prospects for large-scale promotion and application. Attached Figure Description

[0098] Figure 1 This is a schematic diagram of the cooling system described in this utility model.

[0099] Figure 2 This is a top view schematic diagram of the air volume adjustment structure described in this utility model.

[0100] Figure 3 This is a schematic diagram of the structure of one of the ventilation openings of the air volume regulating device when the ventilation opening is half open.

[0101] Reference numerals in the attached drawings: 1: Frame; 101: Support rail; 2: Trolley; 3: Hot air hood; 4: Air box; 5: Air volume adjustment mechanism; 51: Ventilation outlet regulator; 511: Adjustment drive; 5111: Electric cylinder; 5112: Push rod; 5113: Connecting rod; 5114: Adjusting rod; 5115: Rotating shaft; 512: Air outlet blade; 6: Pressure gauge; 7: Anemometer; 8: Infrared material temperature sensor. Detailed Implementation

[0102] The technical solution of this utility model is illustrated below. The scope of protection of this utility model includes, but is not limited to, the following embodiments.

[0103] A uniform cooling system includes a frame 1, a trolley 2, a hot air hood 3, an air box 4, and an airflow regulating mechanism 5. A support rail 101 is mounted on the frame 1, and the trolley 2 is placed on and runs along the support rail 101. The hot air hood 3 covers the trolley 2, and the air box 4 is located below the trolley 2. The airflow regulating mechanism 5 is positioned between the trolley 2 and the air box 4, and has multiple independently adjustable vents in its width direction. By controlling the opening size of each vent in the airflow regulating mechanism 5, uniform cooling air delivery between the air box 4 and the trolley 2 is achieved.

[0104] Preferably, the airflow regulating mechanism 5 consists of multiple air vent regulators 51, each air vent regulator 51 including an adjustment drive 511 and air vent blades 512. The adjustment drive 511 is mounted on a frame 1 on one side of the top of the air box 4. Multiple air vent blades 512 are horizontally laid at the air outlet of the air box 4, and one end of each air vent blade 512 is connected to the adjustment drive 511. By adjusting the tilt angle of the air vent blades 512 relative to the vertical plane through the adjustment drive 511, the opening size of the air vent regulator 51 can be adjusted.

[0105] Preferably, the plurality of ventilation outlet regulators 51 are arranged side by side in the width direction of the air box 4, and the ventilation opening of each of the plurality of ventilation outlet regulators 51 is adjusted independently.

[0106] Preferably, the air volume regulating mechanism 5 consists of two vent regulators 51 arranged side by side in the width direction of the air box 4.

[0107] Preferably, the adjustment drive 511 includes an electric cylinder 5111, a push rod 5112, a connecting rod 5113, an adjusting rod 5114, and a rotating shaft 5115. The electric cylinder 5111 is mounted on the frame 1 on one side of the top of the air box 4. One end of the push rod 5112 is connected to the electric cylinder 5111, the other end of the push rod 5112 is connected to one end of the connecting rod 5113, and the other end of the connecting rod 5113 is connected to one end of the adjusting rod 5114. The adjusting rod 5114 is horizontally positioned and perpendicular to the air outlet blades 512. The adjusting rod 5114 is connected to multiple air outlet blades 512 via multiple rotating shafts 5115. The electric cylinder 5111 drives the adjusting rod 5114 to move along its axis through the push rod 5112 and the connecting rod 5113, which in turn drives the rotating shaft 5115 to rotate. The rotation of the rotating shaft 5115 drives the air outlet blade 512 to rotate, thereby realizing the adjustment of the tilt angle of the air outlet blade 512 relative to the vertical plane.

[0108] Preferably, a plurality of pressure gauges 6 are also provided on the bottom side of the air volume regulating mechanism 5. The plurality of pressure gauges 6 are evenly distributed along the width direction of the air box 4.

[0109] Preferably, a plurality of anemometers 7 are also provided on the bottom side of the airflow regulating mechanism 5. The plurality of anemometers 7 are evenly distributed along the width direction of the air box 4.

[0110] Preferably, a plurality of infrared material temperature detectors 8 are also provided at the rear of the hot air hood 3. The plurality of infrared material temperature detectors 8 are evenly distributed along the width direction of the inner wall of the hot air hood 3.

[0111] Preferably, the cooling system is an annular cooler. Preferably, each air box 4 has an independent cooling fan at its bottom air inlet. Preferably, an inlet pressure gauge and an outlet pressure gauge are respectively installed at the air inlet and outlet of the cooling fan.

[0112] Example 1

[0113] like Figure 1-3 As shown, a uniform cooling system includes a frame 1, a trolley 2, a hot air hood 3, an air box 4, and an airflow regulating mechanism 5. A support rail 101 is mounted on the frame 1, and the trolley 2 is placed on and runs along the support rail 101. The hot air hood 3 covers the trolley 2, and the air box 4 is located below the trolley 2. The airflow regulating mechanism 5 is located between the trolley 2 and the air box 4, and has multiple independently adjustable vents in its width direction. By controlling the opening size of each vent in the airflow regulating mechanism 5, uniform cooling air delivery between the air box 4 and the trolley 2 is achieved.

[0114] Example 2

[0115] The embodiment 1 is repeated, except that the airflow regulating mechanism 5 consists of multiple air vent regulators 51, each air vent regulator 51 including an regulating drive 511 and air vent blades 512. The regulating drive 511 is mounted on a frame 1 on one side of the top of the air box 4. Multiple air vent blades 512 are horizontally laid at the air outlet of the air box 4, and one end of each air vent blade 512 is connected to the regulating drive 511. By adjusting the tilt angle of the air vent blades 512 relative to the vertical plane through the regulating drive 511, the opening size of the air vent regulator 51 is adjusted.

[0116] Example 3

[0117] Example 2 is repeated, except that the plurality of ventilation outlet regulators 51 are arranged side by side in the width direction of the air box 4, and the ventilation opening of each of the plurality of ventilation outlet regulators 51 is adjusted independently.

[0118] Example 4

[0119] The embodiment 3 is repeated, except that the air volume regulating mechanism 5 is composed of two vent regulators 51 arranged side by side in the width direction of the air box 4.

[0120] Example 5

[0121] The embodiment 4 is repeated, except that the adjustment drive 511 includes an electric cylinder 5111, a push rod 5112, a connecting rod 5113, an adjusting rod 5114, and a rotating shaft 5115. The electric cylinder 5111 is mounted on the frame 1 on one side of the top of the air box 4. One end of the push rod 5112 is connected to the electric cylinder 5111, and the other end of the push rod 5112 is connected to one end of the connecting rod 5113. The other end of the connecting rod 5113 is connected to one end of the adjusting rod 5114. The adjusting rod 5114 is horizontally positioned and perpendicular to the air outlet blades 512. The adjusting rod 5114 is connected to multiple air outlet blades 512 via multiple rotating shafts 5115. The electric cylinder 5111 drives the adjusting rod 5114 to move along its axis through the push rod 5112 and the connecting rod 5113, which in turn drives the rotating shaft 5115 to rotate. The rotation of the rotating shaft 5115 drives the air outlet blade 512 to rotate, thereby realizing the adjustment of the tilt angle of the air outlet blade 512 relative to the vertical plane.

[0122] Example 6

[0123] Example 5 is repeated, except that multiple pressure gauges 6 are also provided on the bottom side of the airflow regulating mechanism 5. The multiple pressure gauges 6 are evenly distributed along the width direction of the air box 4.

[0124] Example 7

[0125] The embodiment 6 is repeated, except that multiple anemometers 7 are also provided on the bottom side of the airflow regulating mechanism 5. The multiple anemometers 7 are evenly distributed along the width direction of the air box 4.

[0126] Example 8

[0127] The embodiment 7 is repeated, except that multiple infrared material temperature detectors 8 are also provided at the tail end of the hot air hood 3. The multiple infrared material temperature detectors 8 are evenly distributed along the width direction of the inner wall of the hot air hood 3.

[0128] Example 9

[0129] Repeat Example 8, except that the cooling system is an annular cooler.

[0130] Example 10

[0131] Repeat Example 9, except that each air box 4 has an independent cooling fan at its bottom air inlet. An inlet pressure gauge and an outlet pressure gauge are respectively installed at the air inlet and outlet of the cooling fan.

[0132] The process of cooling sintered materials using the above system is as follows: Hot sintered ore is loaded into the trolley 2 and runs along the support track 101. During operation, all ventilation openings of the airflow regulating mechanism 5 are fully opened, and cooling air is blown into the air box 4 to cool the hot sintered ore in the trolley 2. The cooled sintered ore is then discharged from the discharge port. An infrared material temperature detector 8 installed in the hot air hood 3 detects whether the average temperature of the material discharged from the inner ring of the annular cooler meets the operating requirements (i.e., the temperature difference between the inner and outer rings is less than the set value). If it meets the requirements, the current operating conditions are maintained; otherwise, subsequent operations are performed.

[0133] The average wind pressure on both sides of the inner and outer rings is detected by a pressure sensor 6 located at the bottom of the trolley 2, and the average wind speed on both sides of the inner and outer rings is detected by a wind speed sensor 7 located at the bottom of the trolley 2. By adjusting the opening of the vent of the airflow regulating mechanism 5 on the side with thinner material layer, the wind resistance on that side is increased, thus improving the cooling effect on both sides of the inner and outer rings. Specifically, adjusting the opening of the vent of the airflow regulating mechanism 5 is achieved by the electric cylinder 5111 driving the adjusting rod 5114 to extend outward along its axial direction via the push rod 5112 and the connecting rod 5113, which in turn drives the rotating shaft 5115 to rotate. The rotation of the rotating shaft 5115 drives the air outlet blades 512 to rotate, thereby reducing the tilt angle of the air outlet blades 512 relative to the vertical plane. Conversely, if the opening of the airflow regulating mechanism 5 is increased, the adjusting rod 5114 retracts inward along its axial direction, thereby increasing the tilt angle of the air outlet blades 512 relative to the vertical plane.

Claims

1. A cooling system for uniform cooling, characterized in that: The cooling system includes a frame (1), a trolley (2), a hot air hood (3), a wind box (4), and an air volume regulating mechanism (5). A support rail (101) is provided on the frame (1), and the trolley (2) is placed on the support rail (101) and runs along the support rail (101). The hot air hood (3) is placed above the trolley (2), and the wind box (4) is placed below the trolley (2). The air volume regulating mechanism (5) is placed between the trolley (2) and the wind box (4), and the air volume regulating mechanism (5) has multiple independently adjustable ventilation openings in the width direction. By controlling the size of the opening of each ventilation opening of the air volume regulating mechanism (5), the uniform delivery of cooling air between the wind box (4) and the trolley (2) can be achieved.

2. The cooling system according to claim 1, characterized in that: The air volume regulating mechanism (5) consists of multiple air vent regulators (51), each air vent regulator (51) including an regulating drive (511) and air vent blades (512); the regulating drive (511) is mounted on a frame (1) on one side of the top of the air box (4); multiple air vent blades (512) are laid horizontally at the air outlet of the air box (4), and one end of all air vent blades (512) is connected to the regulating drive (511); the air vent blades (512) are adjusted by the regulating drive (511) to adjust the tilt angle of the blade surface of the air vent blades (512) relative to the vertical plane, thereby realizing the adjustment of the air vent opening size of the air vent regulator (51).

3. The cooling system according to claim 2, characterized in that: Multiple ventilation opening regulators (51) are arranged side by side in the width direction of the air box (4), and the ventilation opening of each of the multiple ventilation opening regulators (51) is adjusted independently.

4. The cooling system according to claim 3, characterized in that: The air volume regulating mechanism (5) consists of two vent regulators (51) laid side by side in the width direction of the air box (4).

5. The cooling system according to claim 2, characterized in that: The adjustment drive (511) includes an electric cylinder (5111), a push rod (5112), a connecting rod (5113), an adjusting rod (5114), and a rotating shaft (5115); the electric cylinder (5111) is mounted on the frame (1) on one side of the top of the bellows (4); one end of the push rod (5112) is connected to the electric cylinder (5111), the other end of the push rod (5112) is connected to one end of the connecting rod (5113), and the other end of the connecting rod (5113) is connected to one end of the adjusting rod (5114); the adjusting rod (5114) is connected to the electric cylinder (5111). The air vent blades (512) are set flat and perpendicular to each other. The adjusting rod (5114) is connected to multiple air vent blades (512) through multiple rotating shafts (5115). The electric cylinder (5111) drives the adjusting rod (5114) to move along its axial direction through the push rod (5112) and the connecting rod (5113), thereby driving the rotating shaft (5115) to rotate. The rotation of the rotating shaft (5115) drives the air vent blades (512) to rotate, thereby realizing the adjustment of the tilt angle of the air vent blades (512) relative to the vertical plane.

6. The cooling system according to any one of claims 1-5, characterized in that: Multiple pressure gauges (6) are also provided on the bottom side of the air volume regulating mechanism (5); the multiple pressure gauges (6) are evenly distributed along the width direction of the air box (4).

7. The cooling system according to any one of claims 1-5, characterized in that: Multiple anemometers (7) are also provided on the bottom side of the air volume regulating mechanism (5); the multiple anemometers (7) are evenly distributed along the width direction of the air box (4).

8. The cooling system according to any one of claims 1-5, characterized in that: Multiple infrared material temperature detectors (8) are also provided at the tail of the hot air hood (3); the multiple infrared material temperature detectors (8) are evenly distributed along the width direction of the inner wall of the hot air hood (3).

9. The cooling system according to any one of claims 1-5, characterized in that: The cooling system is an annular cooler.

10. The cooling system according to claim 9, characterized in that: Each air box (4) has an independent cooling fan installed at the bottom air inlet.

11. The cooling system according to claim 10, characterized in that: An inlet pressure gauge and an outlet pressure gauge are installed at the air inlet and outlet of the cooling fan, respectively.

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