CN109737368B - Steam heat exchanger with steady flow structure - Google Patents
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- CN109737368B CN109737368B CN201810674825.XA CN201810674825A CN109737368B CN 109737368 B CN109737368 B CN 109737368B CN 201810674825 A CN201810674825 A CN 201810674825A CN 109737368 B CN109737368 B CN 109737368B
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Abstract
The invention provides a steam heat exchanger which comprises a header and a steam pipe, wherein a flow stabilizer is arranged in the steam pipe, the flow stabilizer is of a sheet structure, and the sheet structure is arranged on the cross section of the steam pipe; the flow stabilizing device is composed of a square through hole and a regular octagonal through hole, the side length of the square through hole is equal to that of the regular octagonal through hole, four sides of the square through hole are respectively sides of four different regular octagonal through holes, and four mutually spaced sides of the regular octagonal through hole are respectively sides of four different square through holes. Compared with the current stabilizer in the prior art, the current stabilizer further improves the current stabilizing effect, enhances heat transfer and is simple to manufacture.
Description
Technical Field
The invention relates to the field of boiler technology and heat exchangers, in particular to an intelligently controlled evaporator and a steam heat exchanger thereof.
Background
A vaporizer is a mechanical device that uses the heat energy of a fuel or other energy source to heat water into steam. The evaporator has wide application field and is widely applied to places such as clothing factories, dry cleaning shops, restaurants, bunkers, canteens, restaurants, factories and mines, bean product factories and the like. The steam generating system comprises an evaporator, the steam generated by which is generally applied to the steam utilization device, but there is a lack of corresponding intelligent control regulation between the steam utilization device and the evaporator, for example, to control the steam generation of the evaporator according to the conditions of the steam utilization device. The present invention is therefore primarily directed to improvements in the intelligent control of steam generation systems.
Furthermore, steam-water mixtures are present in the typical piping in steam-utilizing plants. The heat exchange tube is in the evaporation process, and inevitable can carry liquid to in the steam pipe, simultaneously because the heat release condensation of condensation end to there is liquid in making the condensation end, liquid inevitable entering steam pipe, thereby make the fluid in the heat exchange tube be the vapour-liquid mixture, the vapour-liquid mixture exists and leads to the vapour to mix into a whole, and heat transfer capacity between with the liquid descends, great influence the efficiency of heat transfer.
Disclosure of Invention
The invention provides an intelligently controlled evaporator aiming at the defects in the prior art, and simultaneously provides an evaporator utilizing device with a novel structure, and the evaporator has the functions of rapid heating, uniform temperature distribution, automatic power control, safety and reliability, and improves the heating efficiency.
In order to achieve the purpose, the invention adopts the following technical scheme:
a steam heat exchanger comprises a header and a steam pipe, wherein the steam pipe extends upwards from the header, the header is provided with a steam inlet and a condensate outlet, steam enters the header and then flows upwards from the header to enter the steam pipe, the steam pipe exchanges heat with the outside to form condensate, then returns to the header under the action of gravity and then flows out from a water return port at the lower part of the header, a flow stabilizing device is arranged in the steam pipe, the flow stabilizing device is of a sheet structure, and the sheet structure is arranged on the cross section of the steam pipe; the flow stabilizing device is composed of a square through hole and a regular octagonal through hole, the side length of the square through hole is equal to that of the regular octagonal through hole, four sides of the square through hole are respectively sides of four different regular octagonal through holes, and four mutually spaced sides of the regular octagonal through hole are respectively sides of four different square through holes.
Preferably, the heat exchanger is a medicinal material dryer, and the medicinal material is arranged on the connecting plate, so that a multi-layer medicinal material drying plate is formed.
Preferably, the cross-section of the steam tube is square.
Preferably, a plurality of flow stabilizers are arranged in the steam pipe, the distance between every two adjacent flow stabilizers is M1, the side length of each square through hole is B1, and the side length of the steam pipe is B2, so that the following requirements are met:
M1/B2=a*Ln(B1/B2) +b
wherein a, b are parameters, wherein 1.725< a <1.733,4.99< b < 5.01;
11<B2<46mm；
1．9<B1<3.2mm；
18<M1<27mm。
further preferably, a is smaller and B is larger as B1/B2 is increased.
Preferably, a =1.728, b = 4.997;
preferably, the flow stabilizer includes at least one of a square central flow stabilizer with a square through hole at the center of the steam pipe and a regular octagonal central flow stabilizer with a regular octagonal through hole at the center of the steam pipe.
Preferably, the adjacently arranged flow stabilizers are of different types.
Preferably, a plurality of flow stabilizers are arranged in the steam pipe, the distance from the inlet of the steam pipe is H, the distance between every two adjacent flow stabilizers is S, and S = F1(H) The following requirements are met:
S’<0, S”>0。
preferably, a plurality of flow stabilizers are arranged in the steam pipe, the distance from the steam pipe inlet is H, the side length of a square through hole of each flow stabilizer is D, and D = F3(H) The following requirements are met:
D’<0, D”>0。
preferably, the inner wall of the steam pipe is provided with a groove, the shell of the flow stabilizer is arranged in the groove, and the inner wall of the shell is aligned with the inner wall of the steam pipe.
The invention has the following advantages:
1) the invention provides a novel flow stabilizer with a novel structure combining a square through hole and a regular octagon through hole, wherein the included angles formed by the edges of the formed square hole and the regular octagon hole are both larger than or equal to 90 degrees through the square and the regular octagon, so that fluid can fully flow through each position of each hole, and the short circuit of the fluid flow is avoided or reduced. The two-phase fluid is separated into the liquid phase and the gas phase by the flow stabilizer with the novel structure, the liquid phase is divided into small liquid masses, the gas phase is divided into small bubbles, the backflow of the liquid phase is inhibited, the gas phase is enabled to flow smoothly, the flow stabilizing effect is achieved, the vibration and noise reducing effect is achieved, and the heat exchange effect is improved. Compared with the current stabilizer in the prior art, the current stabilizer further improves the current stabilizing effect, strengthens heat transfer and is simple to manufacture.
2) Because the fluid continuously releases heat along with the upward flow of the fluid, and the heat release in different heat collecting pipes is more and more uneven along with the continuous heat release of the fluid, the pressure balance can be ensured to be achieved as soon as possible in the flowing process of the fluid through the arrangement.
3) The invention provides a steam utilization device with a novel structure, which can enlarge the heat exchange area of a steam pipe and achieve the purpose of enhancing heat transfer by arranging the steam pipe and a connecting sheet.
4) According to the invention, through reasonable layout, the square and regular octagonal through holes are uniformly distributed, so that the fluid on the whole cross street is uniformly divided, and the problem of nonuniform division of the annular structure along the circumferential direction in the prior art is avoided.
5) The large holes and the small holes are uniformly distributed on the whole cross section through the uniform distribution of the square holes and the regular octagonal holes, and the separation effect is better through the position change of the large holes and the small holes of the adjacent flow stabilizing devices.
6) According to the invention, the flow stabilizer is of a sheet structure, so that the flow stabilizer is simple in structure and low in cost.
7) According to the invention, the optimal relation size of the parameters is researched by setting the regular changes of the parameters such as the distance between the adjacent flow stabilizers, the side length of the holes of the flow stabilizers, the pipe diameter of the heat absorption pipes, the pipe spacing and the like in the height direction of the heat absorption pipes, so that the flow stabilizing effect is further achieved, the noise is reduced, and the heat exchange effect is improved.
8) According to the invention, the heat exchange rule caused by the change of each parameter of the flow stabilizer is widely researched, and the optimal relational expression of the heat exchange effect is realized under the condition of meeting the flow resistance.
Description of the drawings:
FIG. 1 is a schematic diagram of an evaporator system of the present invention.
FIG. 2 is a schematic view of the evaporator of the present invention.
Fig. 3 is a schematic view of a control structure of the evaporator of fig. 2.
Fig. 4 is a schematic front cut-away view of a vapor heat exchanger of the present invention.
Fig. 5 is a schematic side cut view of a vapor heat exchanger of the present invention.
Fig. 6 is another detailed structural schematic diagram of the steam heat exchanger of the present invention.
Fig. 7 is a schematic view of the construction of the communicating tubes and the connecting plate of the vapor heat exchanger of the present invention.
FIG. 8 is a schematic cross-sectional view of a flow stabilizer of the present invention;
fig. 9 is a schematic view of another cross-sectional configuration of a flow stabilizer of the present invention;
FIG. 10 is a schematic view of the placement of the flow stabilizer of the present invention within the steam tube;
FIG. 11 is a schematic cross-sectional view of the placement of a flow stabilizer of the present invention within a steam tube
Fig. 12 is a schematic view of the upper part of fig. 4.
Fig. 13 is a schematic view of the upper portion of fig. 6.
In the figure: 1. the device comprises an evaporator, 11, a steam chamber, 12, a water replenishing tank, 13, an electric heating device, 14 water inlet pipelines, 15 steam outlet pipelines, 16 water pumps, 2 steam utilization equipment, 21 steam inlet pipes, 22 steam pipes, 23 connecting plates, 24 headers, 25 water outlet pipes, 3 communicating pipes, 4 flow stabilizers, 41 square through holes, 42 regular octagon through holes, 43 sides and 5 controllers.
Detailed Description
An evaporator system includes an evaporator 1 and a steam utilizing device 2. The steam generated by heating in the evaporator 1 enters the steam utilization device 2 through the steam inlet pipe 21, and is recycled to the evaporator 1 for heating after being fully utilized in the steam utilization device through heat exchange.
The evaporator structure is as shown in fig. 1, and comprises a steam chamber 11, a water replenishing tank 12 and a water pump 16, wherein the water replenishing tank 12 is connected with the water pump 16 through a pipeline, the water pump 16 is connected with the steam chamber 11 through a pipeline, an electric heating device 13 is arranged in the steam chamber 11, a steam outlet pipeline 15 is arranged on the upper part of the steam chamber 11, and the steam chamber 11 is provided with a water inlet pipeline 14.
From the replenishing tank 12, the water is fed by means of a water pump 16 into the steam chamber 11, where it is heated by means of an electric heating device 13, and the steam produced is discharged through a steam outlet line 15.
Preferably, the steam discharged from the steam outlet line 15 is recycled by entering the steam chamber 11 through the water inlet line 14.
Preferably, the replenishing tank 12 is provided with an inlet pipeline, and the inlet pipeline is connected with a tap water pipe for replenishing water through the tap water pipe. Preferably, a purifying device is arranged between the tap water pipe and the water replenishing tank 12 to purify tap water, so that the heating effect is prevented from being influenced by scaling of an electric heating device in the water replenishing tank.
Preferably, the steam chamber 11 has a circular cross-section.
Preferably, the electric heating device 13 is provided in plurality. The electric heating device is an electric heating pipe. The electrical heater 13 is vertically disposed from the bottom wall of the steam chamber 11 upward, as shown in fig. 1.
The invention can realize the following control:
temperature control
Preferably, a temperature sensor is provided in the steam inlet pipe 21 for measuring the temperature of the steam in the steam inlet pipe 21. The temperature sensor and the electric heating device 13 are in data connection with the controller 5, and the controller 5 automatically controls the heating power of the electric heating device 13 according to the temperature measured by the temperature sensor.
Preferably, the controller controls the electric heating device to increase the heating power if the temperature measured by the temperature sensor is lower than a certain temperature. If the temperature measured by the temperature sensor is higher than a certain temperature, the controller controls the electric heating device to reduce the heating power in order to avoid heat waste.
Through control heating power, guarantee that the entry temperature meets the demands, avoid the entry temperature too high, cause calorific loss, the entry temperature is crossed lowly, causes the unsatisfied actual requirement of heat.
Preferably, the controller 5 automatically increases the heating power of the electric heating means 13 if the detected temperature data is lower than a first value, and the controller 5 automatically decreases the heating power of the electric heating means 13 if the measured temperature data is higher than a second value, which is higher than the first value.
Preferably, when the measured temperature is lower than the first temperature, the electric heating device 13 heats at a first power; when the measured temperature is lower than a second temperature lower than the first temperature, the electric heating device 13 heats at a second power higher than the first power; when the measured temperature is lower than a third temperature lower than the second temperature, the electric heating device 13 heats at a third power higher than the second power; when the measured temperature is lower than a fourth temperature lower than the third temperature, the electric heating device 13 heats at a fourth power higher than the third power; when the measured temperature is lower than a fifth temperature lower than the fourth temperature, the electric heating device 13 heats at a fifth power higher than the fourth power.
Preferably, the first temperature is higher than the second temperature by 2-3 ℃, the second temperature is higher than the third temperature by 2-3 ℃, the third temperature is higher than the fourth temperature by 2-3 ℃, and the fourth temperature is higher than the fifth temperature by 2-3 ℃.
Further preferably, the first temperature is 5.5-6 ℃ higher than the second temperature, the second temperature is 2.5 ℃ higher than the third temperature, the third temperature is 2.5 ℃ higher than the fourth temperature, and the fourth temperature is 2.5 ℃ higher than the fifth temperature.
Preferably, the fifth power is 1.08 to 1.18 times the fourth power, the fourth power is 1.08 to 1.18 times the third power, the third power is 1.08 to 1.18 times the second power, and the second power is 1.08 to 1.18 times the first power.
Preferably, the fifth power is 1.14 times the fourth power, the fourth power is 1.14 times the third power, the third power is 1.14 times the second power, and the second power is 1.14 times the first power.
By optimizing the temperature and power, especially by setting the heating power and temperature difference in a differentiated manner, the heating efficiency can be further improved, and the time can be saved. Experiments show that the heating efficiency can be improved by about 10-15%.
Preferably, the temperature sensor is a plurality of temperature sensors, and the controller controls the operation of the evaporator according to the temperature data measured by the plurality of temperature sensors.
(II) Water level control
Preferably, a water level sensor is arranged in the steam chamber 11, the water level sensor, the electric heater 13 and the water pump 16 are in data connection with the controller 5, and the controller 5 automatically controls the power of the water pump 16 according to the measured water level in the steam chamber 11.
Preferably, the controller increases the flow rate of water into the steam chamber 11 by controlling to increase the power of the water pump 16 if the water level is lowered, and decreases the flow rate of water into the steam chamber 11 or stops the supply of water into the steam chamber 11 by decreasing the power of the water pump 16 or turning off the water pump 16 if the water level is too high.
Through foretell setting, avoided on the one hand that the water level crosses the steam output rate that leads to the fact low and electric heater unit's dry combustion method, cause electric heater unit's damage and produce the incident, on the other hand, avoided because the water level is too high and the water yield that leads to the fact is too big to it is low excessively to cause the steam output rate.
Preferably, when the measured water level is lower than the first water level, the controller 5 controls the water pump 16 to supplement water at the first power; when the measured water level is lower than a second water level lower than the first water level, the controller 5 controls the water pump 16 to supplement water at a second power higher than the first power; when the measured water level is lower than a third water level lower than the second water level, the controller 5 controls the water pump 16 to supplement water at a third power higher than the second power; when the measured water level is lower than a fourth water level lower than the third water level, the controller 5 controls the water pump 16 to supplement water at a fourth power higher than the third power; when the measured water level is lower than a fifth water level lower than the fourth water level, the controller 5 controls the water pump 16 to supplement water at a fifth power higher than the fourth power.
Preferably, the first water level is 1.08 to 1.18 times the second water level, the second water level is 1.08 to 1.18 times the third water level, the third water level is 1.08 to 1.18 times the fourth water level, and the fourth water level is 1.08 to 1.18 times the fifth water level.
Preferably, the first water level is 1.1 to 1.15 times the second water level, the second water level is 1.15 to 1.2 times the third water level, the third water level is 1.2 to 1.25 times the fourth water level, and the fourth water level is 1.25 to 1.3 times the fifth water level.
Preferably, the fifth power is 1.7-1.9 times the fourth power, the fourth power is 1.6-1.8 times the third power, the third power is 1.5-1.7 times the second power, and the second power is 1.3-1.5 times the first power.
Through the preferred of above-mentioned water level and water pump power, especially through the settlement of the water level of differentiation and water pump power, can be quick realize the invariant of water level, improve steam output rate, save time. Experiments show that the steam yield can be improved by about 12-16%.
(III) control of heating power according to water level
Preferably, a water level sensor is arranged in the steam chamber 11, the water level sensor and the electric heater 6 are in data connection with the controller 5, and the controller 5 automatically controls the heating power of the electric heater according to the measured water level in the steam chamber 11.
Preferably, if the water level is too low, the controller controls to reduce the power of the electric heater 6 or directly turn off the heating of the electric heater 6, thereby preventing the water level from being further reduced due to too high steam generation caused by too high heating power, and if the water level is too high, the controller increases the steam generation by increasing the heating power of the electric heater 6, thereby reducing the water level.
Through foretell setting, avoided the water level to hang down the dry combustion method who causes electric heater unit excessively on the one hand, caused electric heater unit's damage and produced the incident, on the other hand, avoided because the water level is too high and the indoor water yield of steam that causes is too big to it is low excessively to cause steam output rate.
Preferably, when the measured water level is lower than the first water level, the controller 5 controls the electric heating device 13 to heat at the first power; when the measured water level is lower than a second water level lower than the first water level, the controller 5 controls the electric heating device 13 to heat at a second power lower than the first power; when the measured water level is lower than a third water level lower than the second water level, the controller 5 controls the electric heating device 13 to heat at a third power lower than the second power; when the measured water level is lower than a fourth water level lower than the third water level, the controller 5 controls the electric heating device 13 to heat at a fourth power lower than the third power; when the measured water level is lower than a fifth water level lower than the fourth water level, the controller 5 controls the electric heating device to heat at a fifth power lower than the fourth power; when the measured water level is lower than a sixth water level lower than the fifth water level, the controller 5 controls the electric heating device to stop heating.
Preferably, the first water level is 1.08 to 1.18 times the second water level, the second water level is 1.08 to 1.18 times the third water level, the third water level is 1.08 to 1.18 times the fourth water level, and the fourth water level is 1.08 to 1.18 times the fifth water level.
Preferably, the first water level is 1.1 to 1.15 times the second water level, the second water level is 1.15 to 1.2 times the third water level, the third water level is 1.2 to 1.25 times the fourth water level, and the fourth water level is 1.25 to 1.3 times the fifth water level.
Preferably, the first power is 1.6 to 1.7 times the second power, the second power is 1.5 to 1.6 times the third power, the third power is 1.4 to 1.5 times the fourth power, and the fourth power is 1.3 to 1.4 times the fifth power.
Through the optimization of the water level and the power of the electric heating device, especially through the setting of the differentiated water level and the power of the electric heating device, the water level can be quickly positioned at a preset safety position, the steam output rate can be ensured when the water level is too high, and the time is saved.
(IV) pressure control
Preferably, a pressure sensor is provided on the steam inlet pipe 21 of the steam utilizing apparatus for measuring the pressure in the steam inlet pipe 21. The pressure sensor and the electric heating device 13 are in data connection with the controller 5, and the controller 5 automatically controls the heating power of the electric heating device 13 according to the pressure measured by the pressure sensor.
Preferably, the controller 5 controls the electric heating device 13 to start heating if the pressure measured by the pressure sensor is lower than a certain pressure. If the temperature measured by the pressure sensor is higher than the upper limit pressure, the controller controls the electric heating device 13 to stop heating in order to avoid danger caused by excessive pressure.
Through so setting up, can come the heating power of adjusting according to the pressure of steam inlet pipe 21 to guarantee that the heat transfer volume of steam utilization equipment reaches the requirement, under the condition of maximize steam output, guarantee the safety of evaporimeter simultaneously.
Preferably, the controller 5 controls the electric heating device 13 to increase the heating power if the pressure measured by the pressure sensor is below a certain value. If the temperature measured by the pressure sensor is higher than a certain value, the controller controls the electric heating device 13 to reduce the heating power in order to avoid the danger caused by the excessive pressure.
Preferably, when the measured pressure is higher than the first pressure, the controller 5 controls the heating power of the electric heating device 13 to be reduced to the first power for heating; when the measured pressure is higher than a second pressure higher than the first pressure, the controller 5 controls the heating power of the electric heating device 13 to be reduced to a second power lower than the first power for heating; when the measured pressure is higher than a third pressure higher than the second pressure, the controller 5 controls the heating power of the electric heating device 13 to be reduced to a third power lower than the second power for heating; when the measured pressure is higher than a fourth pressure higher than the third pressure, the controller 5 controls the heating power of the electric heating device 13 to be reduced to a fourth power higher than the third power for heating; when the measured pressure is higher than a fifth pressure higher than the fourth pressure, the controller 5 stops the heating of the electric heating device 13.
Preferably, the fourth power is 0.4 to 0.6 times the third power, the third power is 0.6 to 0.8 times the second power, and the second power is 0.7 to 0.9 times the first power.
Further preferably, the fourth power is 0.5 times the third power, the third power is 0.7 times the second power, and the second power is 0.8 times the first power.
The fifth pressure is the upper limit pressure.
Preferably, the pressure sensor is a plurality of pressure sensors, and the controller controls the operation of the evaporator according to the pressure data measured by the plurality of pressure sensors.
(V) steam flow control
Preferably, a flow sensor is arranged on the steam inlet pipe 21 of the steam utilization device and used for measuring the steam flow entering the steam utilization device per unit time, and the flow sensor and the electric heater 6 are in data connection with the controller 5. The controller 5 automatically controls the power of the electric heater according to the measured steam flow.
Preferably, the controller 5 controls the electric heating device 13 to increase the heating power if the measured steam flow is below a certain value. If the temperature measured by the pressure sensor is higher than a certain value, the controller controls the electric heating device 13 to decrease the heating power.
Through so setting up, can adjust heating power according to the steam quantity that gets into, guarantee the invariant of the steam quantity that gets into, avoid the quantity too big or undersize, cause steam quantity not enough or extravagant.
Preferably, when the measured flow rate is higher than the first flow rate, the controller 5 controls the heating power of the electric heating device 13 to be reduced to the first power for heating; when the measured flow rate is higher than a second flow rate higher than the first flow rate, the controller 5 controls the heating power of the electric heating device 13 to be reduced to a second power lower than the first power for heating; when the measured flow rate is higher than a third flow rate higher than the second flow rate, the controller 5 controls the heating power of the electric heating device 13 to be reduced to a third power lower than the second power for heating; when the measured flow rate is higher than a fourth flow rate higher than the third flow rate, the controller 5 controls the heating power of the electric heating device 13 to be reduced to a fourth power higher than the third power for heating; when the measured flow rate is higher than the fifth flow rate, which is higher than the fourth flow rate, the controller 5 stops the heating of the electric heating device 13.
Preferably, the fourth power is 0.4 to 0.6 times the third power, the third power is 0.6 to 0.8 times the second power, and the second power is 0.7 to 0.9 times the first power.
Further preferably, the fourth power is 0.5 times the third power, the third power is 0.7 times the second power, and the second power is 0.8 times the first power.
Further preferably, the fifth flow rate is 1.1 to 1.2 times the fourth flow rate, the fourth flow rate is 1.2 to 1.3 times the third flow rate, the third flow rate is 1.3 to 1.4 times the second flow rate, and the second flow rate is 1.4 to 1.5 times the first flow rate.
By optimizing the flow rate and the power of the electric heating device, especially by setting the flow rate and the power of the electric heating device in a differentiated manner, the flow rate can be quickly kept constant, and time can be saved.
(VI) temperature control of water outlet pipeline
Preferably, a temperature sensor is arranged on the water outlet pipeline 21 of the steam utilization equipment and used for measuring the temperature of the water after heat exchange, and the temperature sensor and the electric heater 6 are in data connection with the controller 5. The controller 5 automatically controls the heating power of the electric heater according to the temperature measured by the temperature sensor. Through control heating power, guarantee that the temperature after the heat transfer satisfies the demands, avoid the temperature too high, cause calorific loss, the temperature is crossed lowly, causes the unsatisfied actual requirement of heat.
Preferably, the controller controls the electric heating device to increase the heating power if the temperature measured by the temperature sensor is lower than a certain temperature. If the temperature measured by the temperature sensor is higher than a certain temperature, for example, causing heat waste, the controller controls the electric heating device to reduce heating in order to avoid the heat waste. By reducing the heating power, the steam output is low, so that waste is avoided.
Preferably, the controller 5 automatically increases the heating power of the electric heating means 13 if the detected temperature data is lower than a first value, and the controller 5 automatically decreases the heating power of the electric heating means 13 if the measured temperature data is higher than a second value, which is higher than the first value.
Preferably, when the measured temperature is lower than the first temperature, the electric heating device 13 heats at a first power; when the measured temperature is lower than a second temperature lower than the first temperature, the electric heating device 13 heats at a second power higher than the first power; when the measured temperature is lower than a third temperature lower than the second temperature, the electric heating device 13 heats at a third power higher than the second power; when the measured temperature is lower than a fourth temperature lower than the third temperature, the electric heating device 13 heats at a fourth power higher than the third power; when the measured temperature is lower than a fifth temperature lower than the fourth temperature, the electric heating device 13 heats at a fifth power higher than the fourth power.
Preferably, the first temperature is higher than the second temperature by 2-3 ℃, the second temperature is higher than the third temperature by 2-3 ℃, the third temperature is higher than the fourth temperature by 2-3 ℃, and the fourth temperature is higher than the fifth temperature by 2-3 ℃.
Further preferably, the first temperature is greater than the second temperature by 2.5 degrees centigrade, the second temperature is greater than the third temperature by 2.5 degrees centigrade, the third temperature is greater than the fourth temperature by 2.5 degrees centigrade, and the fourth temperature is greater than the fifth temperature by 2.5 degrees centigrade.
Preferably, the fifth power is 1.08 to 1.18 times the fourth power, the fourth power is 1.08 to 1.18 times the third power, the third power is 1.08 to 1.18 times the second power, and the second power is 1.08 to 1.18 times the first power.
Preferably, the fifth power is 1.14 times the fourth power, the fourth power is 1.14 times the third power, the third power is 1.14 times the second power, and the second power is 1.14 times the first power.
By optimizing the temperature and power, especially by setting the heating power and temperature difference in a differentiated manner, the heating efficiency can be further improved, and the time can be saved. Experiments show that the heating efficiency can be improved by about 10-15%.
Preferably, the temperature sensor is a plurality of temperature sensors, and the controller controls the operation of the system according to the temperature data measured by the plurality of temperature sensors 12.
(VII) steam Chamber temperature control
Preferably, a temperature sensor is provided in the steam chamber for measuring the temperature of the steam in the steam chamber. The temperature sensor and the electric heating device 13 are in data connection with the controller 5, and the controller 5 automatically controls the heating power of the electric heating device 13 according to the temperature measured by the temperature sensor.
Preferably, the controller controls the electric heating device to increase the heating power if the temperature measured by the temperature sensor is lower than a certain temperature. If the temperature measured by the temperature sensor is above a certain temperature, for example above a dangerous critical temperature, the controller controls the electric heating device to stop heating in order to avoid overheating.
Preferably, the controller 5 automatically increases the heating power of the electric heating means 13 if the detected temperature data is lower than a first value, and the controller 5 automatically decreases the heating power of the electric heating means 13 if the measured temperature data is higher than a second value, which is higher than the first value.
Preferably, when the measured temperature is lower than the first temperature, the electric heating device 13 heats at a first power; when the measured temperature is lower than a second temperature lower than the first temperature, the electric heating device 13 heats at a second power higher than the first power; when the measured temperature is lower than a third temperature lower than the second temperature, the electric heating device 13 heats at a third power higher than the second power; when the measured temperature is lower than a fourth temperature lower than the third temperature, the electric heating device 13 heats at a fourth power higher than the third power; when the measured temperature is lower than a fifth temperature lower than the fourth temperature, the electric heating device 13 heats at a fifth power higher than the fourth power.
Preferably, the first temperature is higher than the second temperature by 2-3 ℃, the second temperature is higher than the third temperature by 2-3 ℃, the third temperature is higher than the fourth temperature by 2-3 ℃, and the fourth temperature is higher than the fifth temperature by 2-3 ℃.
Further preferably, the first temperature is greater than the second temperature by 2.5 degrees centigrade, the second temperature is greater than the third temperature by 2.5 degrees centigrade, the third temperature is greater than the fourth temperature by 2.5 degrees centigrade, and the fourth temperature is greater than the fifth temperature by 2.5 degrees centigrade.
Preferably, the fifth power is 1.08 to 1.18 times the fourth power, the fourth power is 1.08 to 1.18 times the third power, the third power is 1.08 to 1.18 times the second power, and the second power is 1.08 to 1.18 times the first power.
Preferably, the fifth power is 1.14 times the fourth power, the fourth power is 1.14 times the third power, the third power is 1.14 times the second power, and the second power is 1.14 times the first power.
By optimizing the temperature and power, especially by setting the heating power and temperature difference in a differentiated manner, the heating efficiency can be further improved, and the time can be saved. Experiments show that the heating efficiency can be improved by about 10-15%.
Preferably, the temperature sensor is disposed on a bottom wall of the steam chamber.
Preferably, the temperature sensor is a plurality of temperature sensors, and the controller controls the operation of the evaporator according to the temperature data measured by the plurality of temperature sensors 12.
Preferably, the steam utilization device 2 is a steam heat exchanger. The steam heat exchanger includes a header 24 and steam tubes 22, the steam tubes 22 extending upwardly from the header. As shown in fig. 5 and 6, the steam pipes 22 are a plurality of pipes, the steam pipes 22 are arranged in a matrix and have parallel rows and columns, and connecting plates 23 are provided between the steam pipes to connect the rows and columns of steam pipes together through the connecting plates 23. The steam generated by the evaporator 1 enters the header 24 and then flows upward from the header 24 into the steam pipe 22. The steam pipe 22 forms condensed water by heat exchange with the outside, and returns to the header tank 24 by gravity, and then returns to the evaporator 1 from a return port at the lower portion of the header tank 24.
Preferably, the steam inlet pipe 21 is provided at one or both ends of the header 24.
Through setting up connecting plate 23 for expand heat transfer area, play the effect like the fin.
Preferably, the web 23 is provided in a plurality of layers along the height direction of the steam pipe 22. The distance of the connection plate 23 in the height direction becomes smaller along the height direction of the steam pipe 22. Mainly because the research shows that the hot steam all goes to the upper part, so the heat exchange capability is stronger and stronger along with the continuous increase of the height. Through the change of the distance of the connecting plate 23 in the height direction, the whole heat exchange is uniform, and the local temperature is prevented from being too high or too low.
Preferably, the distance of the connection plate 23 in the height direction is increased in a smaller and smaller range along the height direction of the steam pipe 22. The above rule change is a conclusion obtained through a large number of experiments and researches, and through the change of the above range, the whole heat exchange is more uniform, and the local temperature is further prevented from being too high or too low.
Alternatively, as shown in fig. 6 and 13, a communicating pipe 3 is provided between the steam pipes. A communication pipe 3 is provided between at least two adjacent steam pipes 22. In the research, it is found that in the process of heat release of the evaporation tubes, the heat release amount of the heat release tubes at different positions is different, so that the pressure or temperature between the steam tubes 22 is different, which may cause over-high temperature of some steam tubes 22 and shortened service life, and once a problem occurs in one steam tube 22, the problem that the whole heat tube cannot be used may occur. According to the invention, through a great deal of research, the communicating pipes 3 are arranged on the adjacent steam pipes, so that under the condition that the steam pipes are heated differently to cause different pressures, the fluid in the steam pipe 22 with large pressure can rapidly flow to the steam pipe 22 with small pressure, thereby keeping the overall pressure balance and avoiding local overheating or overcooling.
Fig. 13 shows that the communicating pipes are arranged only in the horizontal row, but the present application is not limited to the horizontal row, and may be arranged only in the vertical row or in a combined horizontal row and vertical row.
Preferably, a plurality of communication pipes 3 are provided between adjacent steam pipes 22 from the lower portion of steam pipe 22 to the upper portion of steam pipe 22. Through setting up a plurality of communicating pipes, can make the continuous balanced pressure of fluid in the heat absorption evaporation process, guarantee the pressure balance in the whole steam pipe.
Preferably, the distance between adjacent communication tubes 3 decreases from the lower portion of steam pipe 22 to the upper portion of steam pipe 22. The purpose is to arrange more communicating pipes, because the fluid continuously releases heat along with the upward flow of the fluid, and the heat release in different heat collecting pipes is more and more uneven along with the continuous heat release of the fluid, so that the pressure balance can be achieved as soon as possible in the flowing process of the fluid through the arrangement.
Preferably, the distance between adjacent communication pipes is decreased from the lower portion of steam pipe 22 to the upper portion of steam pipe 22 to be larger. Experiments show that the arrangement can ensure that the pressure balance is achieved more optimally and more quickly in the fluid flowing process. This is also the best way of communicating by extensively studying the law of change of the pressure distribution.
Preferably, the diameter of communication pipe 3 increases from the lower portion of steam pipe 22 to the upper portion of steam pipe 22. The purpose is to ensure a larger communication area, because the fluid continuously releases heat along with the upward flow of the fluid, and the temperature and pressure in different heat collecting pipes are more and more uneven along with the continuous heat release of the steam, so that the pressure balance can be ensured to be achieved as soon as possible in the flowing process of the fluid through the arrangement.
Preferably, the diameter of communication pipe 3 increases from the lower portion of steam pipe 22 to the upper portion of steam pipe 22. Experiments show that the arrangement can ensure that the pressure balance is achieved more optimally and more quickly in the fluid flowing process. This is also the best way of communicating by extensively studying the law of change of the pressure distribution.
Preferably, as shown in fig. 13, connection plate 23 connects adjacent communication tubes 3.
Preferably, the heat exchanger is a medicinal material dryer, and the medicinal material is arranged on the connecting plate 23, so that a multi-layer medicinal material drying plate is formed.
Preferably, the heat exchanger is a chemical liquid heat exchanger, and the steam pipe is inserted into the chemical liquid in the tank to heat the chemical liquid.
Preferably, the heat exchanger is a health product heat exchanger, and the steam pipe extends into the health product in the box body and is used for heating the health product.
Because the heat transfer of steam in the steam pipe for vapour-liquid two-phase flow appears in the steam pipe, on the one hand, the steam pipe is in the evaporation process, inevitable can carry liquid to in the steam pipe, simultaneously because the exothermic condensation of condensation end, thereby make to have liquid in the condensation end, liquid inevitable entering steam pipe, thereby make the fluid in the steam pipe be vapour-liquid mixture, simultaneously the steam pipe can be because of the incondensable gas of ageing production in the operation process, the incondensable gas generally rises to the condensation end on steam pipe upper portion, the existence of incondensable gas leads to the pressure increase in the steam pipe condensation end, pressure makes liquid flow to in the steam pipe. Greatly influencing the heat exchange efficiency. Therefore, the present invention adopts a new structure to separate vapor phase and liquid phase, so that the heat exchange is enhanced.
The steam pipe is internally provided with a flow stabilizer 4, and the structure of the flow stabilizer 4 is shown in figures 8 and 9. The flow stabilizer 4 is a sheet structure which is arranged on the cross section of the steam pipe 3; the flow stabilizer 4 is composed of a square structure and a regular octagonal structure, so that a square through hole 41 and a regular octagonal through hole 42 are formed. The side length of the square through-hole 41 is equal to the side length of the regular octagonal through-hole 42 as shown in fig. 1, the four sides 43 of the square through-hole are the sides 43 of four different regular octagonal through-holes, respectively, and the four mutually spaced sides 43 of the regular eight deformed through-hole are the sides 43 of four different square through-holes, respectively.
The invention adopts the current stabilizer with a novel structure, and has the following advantages:
1) the invention provides a novel flow stabilizer with a novel structure combining a square through hole and a regular octagon through hole, wherein the included angles formed by the edges of the formed square hole and the regular octagon hole are both larger than or equal to 90 degrees through the square and the regular octagon, so that fluid can fully flow through each position of each hole, and the short circuit of the fluid flow is avoided or reduced. The two-phase fluid is separated into the liquid phase and the gas phase by the flow stabilizer with the novel structure, the liquid phase is divided into small liquid masses, the gas phase is divided into small bubbles, the backflow of the liquid phase is inhibited, the gas phase is enabled to flow smoothly, the flow stabilizing effect is achieved, the vibration and noise reducing effect is achieved, and the heat exchange effect is improved. Compared with the current stabilizer in the prior art, the current stabilizer further improves the current stabilizing effect, strengthens heat transfer and is simple to manufacture.
2) According to the invention, through reasonable layout, the square and regular octagonal through holes are uniformly distributed, so that the fluid on the whole cross street is uniformly divided, and the problem of nonuniform division of the annular structure along the circumferential direction in the prior art is avoided.
3) According to the invention, the large holes and the small holes are uniformly distributed on the whole cross section through the uniform distribution of the square holes and the regular octagonal through holes at intervals, and the separation effect is better through the position change of the large holes and the small holes of the adjacent flow stabilizers.
4) According to the invention, the flow stabilizer is of a sheet structure, so that the flow stabilizer is simple in structure and low in cost.
By arranging the annular flow stabilizing device, the invention equivalently increases the internal heat exchange area in the steam exchange pipe, strengthens the heat exchange and improves the heat exchange effect.
The invention divides the gas phase and the liquid phase at all cross section positions of all steam exchange pipes, thereby realizing the contact area of the division of the gas-liquid interface and the gas phase boundary layer and the cooling wall surface on the whole steam exchange pipe section and enhancing the disturbance, greatly reducing the noise and the vibration and strengthening the heat transfer.
Preferably, the flow stabilizers are of two types, as shown in fig. 8 and 9, the first type being a square central flow stabilizer, the square being located in the center of the steam or condensation tube, as shown in fig. 9. The second is a regular octagonal central flow stabilizer, the regular octagon being located in the center of the steam or condensation tube, as shown in fig. 8. Preferably, the two types of flow stabilizers are arranged adjacently, i.e. the types of flow stabilizers arranged adjacently are different. Namely, the regular octagonal central current stabilizer is adjacent to the square central current stabilizer, and the square central current stabilizer is adjacent to the regular octagonal central current stabilizer. According to the invention, the square holes and the regular octagon holes are uniformly distributed at intervals, so that the large holes and the small holes are uniformly distributed on the whole cross section, and through the position change of the large holes and the small holes of the adjacent flow stabilizing devices, the fluid passing through the large holes next passes through the small holes, and the fluid passing through the small holes next passes through the large holes to be further separated, so that the mixing of vapor and liquid is promoted, and the separating and heat exchanging effects are better.
Preferably, the steam pipe 3 is square in cross section.
Preferably, the diameter of the steam pipe 3 is continuously reduced in the direction of fluid flow. The main reasons are as follows: the flowing resistance can be increased by increasing and reducing the pipe diameter of the steam pipe, so that the evaporated steam in the steam pipe moves towards the direction of increasing the pipe diameter, the heat exchange uniformity of the whole steam pipe is further promoted, and the heat is prevented from being concentrated on the upper part of the steam pipe for heat exchange.
Preferably, the diameter of the steam pipe 3 is continuously increased more and more in the direction of fluid flow. The amplitude change of the pipe diameter is a result obtained by a large number of experiments and numerical simulation by the applicant, and through the arrangement, the circulating flow of the loop steam pipe can be further promoted, so that the heat exchange is integrally uniform.
Preferably, a plurality of flow stabilizers are provided in the steam pipe, and the interval between the flow stabilizers is gradually reduced from the lower portion of the steam pipe 22 to the upper portion of the steam pipe 22. Setting the distance from the steam pipe inlet to be H, the distance between adjacent current stabilizers to be S, S = F1(H) I.e. S is a function of the height H as a variable, S' is the first derivative of S, satisfying the following requirements:
S’<0;
the main reason is that the vapor in the vapor pipe carries liquid in the rising process, and the vapor is continuously concentrated towards the upper part in the rising process, so that the vapor in the gas-liquid two-phase flow is more and more, the vapor phase in the vapor-liquid two-phase flow is more and more, the heat exchange capacity in the vapor pipe is relatively weakened along with the increase of the vapor phase, and the vibration and the noise thereof are also continuously increased along with the increase of the vapor phase. The distance between adjacent flow stabilizers needs to be set shorter and shorter.
Through the experiment discovery, through foretell setting, both can reduce vibrations and noise to the at utmost, can improve the heat transfer effect simultaneously.
Further preferably, the distance between the adjacent flow stabilizers is gradually decreased from the lower portion of the steam pipe 22 to the upper portion of the steam pipe 22. I.e. S "is the second derivative of S, the following requirements are met:
S”>0;
through the experiment, the vibration and the noise of about 7% can be further reduced, and the heat exchange effect of about 8% is improved.
Preferably, a plurality of flow stabilizers are provided in the steam pipe, and the side length of the square is gradually reduced from the lower portion of the steam pipe 22 to the upper portion of the steam pipe 22. The distance from the steam pipe inlet is H, the side length of the square is C, and C = F2(H) And C' is the first derivative of C, and meets the following requirements:
C’<0;
further preferably, the side length of the square is gradually decreased from the lower portion of the steam pipe 22 to the upper portion of the steam pipe 22. C' is the second derivative of C, and meets the following requirements:
C”>0。
see previous variations in the flow stabilizer spacing for specific reasons.
Preferably, the distance between adjacent flow stabilizers remains constant.
Preferably, the inner wall of the steam pipe is provided with a gap, and the outer end of the flow stabilizer is arranged in the gap.
Preferably, the steam pipe is formed by welding a multi-section structure, and a flow stabilizer is arranged at the joint of the multi-section structure.
Through analysis and experiments, the distance between the flow stabilizers cannot be too large, the vibration and noise reduction and separation effects are poor due to the fact that the distance is too large, meanwhile, the distance cannot be too small, the resistance is too large due to the fact that the distance is too small, and similarly, the side length of a square cannot be too large or too small, the vibration and noise reduction effects are poor or the resistance is too large, so that the vibration and noise reduction is optimized under the condition that normal flow resistance (the total pressure bearing is less than 2.5Mpa, or the on-way resistance of a single steam pipe is less than or equal to 5 Pa/M) is preferentially met through a large number of experiments, and the optimal relation of all parameters is arranged.
Preferably, the distance between adjacent flow stabilizers is M1, the side length of a square through hole is B1, the riser is a square section, and the side length of the square section of the riser is B2, so that the following requirements are met:
M1/B2=a*Ln(B1/B2) +b
wherein a, b are parameters, wherein 1.725< a <1.733,4.99< b < 5.01;
11<B2<46mm；
1．9<B1<3.2mm；
18<M1<27mm。
further preferably, a is smaller and B is larger as B1/B2 is increased.
Preferably, a =1.728, b = 4.997;
preferably, the side length B1 of the square through hole is the average of the inner side length and the outer side length of the square through hole, and the side length B2 of the square cross section of the ascending tube is the average of the inner side length and the outer side length of the ascending tube.
Preferably, the outer length of the square through hole is equal to the inner length of the square section of the riser.
Preferably, as B2 increases, B1 also increases. However, as B2 increases, the magnitude of the increase in B1 becomes smaller and smaller. The change of the rule is obtained through a large amount of numerical simulation and experiments, and the heat exchange effect and the noise are further improved and reduced through the change of the rule.
Preferably, as B2 increases, M1 decreases. However, as B2 increases, the magnitude of the decrease in M1 becomes smaller and smaller. The change of the rule is obtained through a large amount of numerical simulation and experiments, and the heat exchange effect and the noise are further improved and reduced through the change of the rule.
Learn through analysis and experiment, the interval of tedge also satisfies certain requirement, for example can not too big or undersize, no matter too big or undersize can lead to the heat transfer effect not good, because set up current stabilizer in this application tedge moreover, consequently current stabilizer also has certain requirement to the tedge interval. Therefore, through a large number of experiments, under the condition that the normal flow resistance (the total pressure bearing is less than 2.5MPa, or the on-way resistance of a single ascending pipe is less than or equal to 5 Pa/M) is preferentially met, the damping and noise reduction are optimized, and the optimal relation of each parameter is arranged.
The distance between adjacent flow stabilizers is M1, the side length of a square is B1, the ascending pipe is a square section, the side length of the ascending pipe is B2, and the distance between the centers of the adjacent ascending pipes is M2, so that the following requirements are met:
M2/B2=d*(M1/B2)2+e+f*(M1/B2)3-h*(M1/B2)；
wherein d, e, f, h are parameters,
1.239<d<1.240,1.544<e<1.545,0.37<f<0.38,0.991<h<0.992；
11<B2<46mm；
1．9<B1<3.2mm；
18<M1<27mm。
16<M2<76mm。
the spacing between the centers of adjacent risers of M2 is referred to as the distance between the centerlines of the risers.
Further preferably, d =1.2393, e =1.5445, f =0.3722, h = 0.9912;
preferably, d, e, f are larger and h is smaller as M1/B2 is increased.
Preferably, as B2 increases, M2 increases, but as B2 increases, the magnitude of the increase in M2 becomes smaller and smaller. The change of the rule is obtained through a large amount of numerical simulation and experiments, and the heat exchange effect can be further improved through the change of the rule.
Preferably, the steam pipe length L is between 2000 and 2500 mm. More preferably, 2200 to 2300 mm.
By optimizing the optimal geometric dimension of the formula, the optimal effect of shock absorption and noise reduction can be achieved under the condition of meeting the normal flow resistance.
For other parameters, such as the wall thickness of the pipe and the wall thickness of the shell, the parameters are set according to normal standards.
Preferably, the pipe diameter of the steam pipe is larger than that of the return pipe. The resistance of the return pipe is mainly increased, and the resistance of the steam pipe is reduced, so that steam flows from the evaporation part more easily, and circulation is formed better by the loop steam pipe.
Although the present invention has been described with reference to the preferred embodiments, it is not limited thereto. Various changes and modifications may be effected therein by one skilled in the art without departing from the spirit and scope of the invention as defined in the appended claims.
Claims (4)
1. A steam heat exchanger for a medicinal material dryer comprises a collecting box and a steam pipe, wherein the steam pipe extends upwards from the collecting box, the collecting box is provided with a steam inlet and a condensate outlet, steam enters the collecting box and then flows upwards from the collecting box to enter the steam pipe, the steam pipe exchanges heat with the outside to form condensate water, then returns to the collecting box under the action of gravity and then flows out from a water return port at the lower part of the collecting box, and the steam heat exchanger is characterized in that a flow stabilizing device is arranged in the steam pipe, the flow stabilizing device is of a sheet structure, and the sheet structure is arranged on the cross section of the steam pipe; the flow stabilizer consists of a square through hole and a regular octagonal through hole, the side length of the square through hole is equal to that of the regular octagonal through hole, four sides of the square through hole are respectively sides of four different regular octagonal through holes, and four mutually spaced sides of the regular octagonal through hole are respectively sides of four different square through holes; the heat exchanger is a medicinal material dryer, a connecting plate is arranged among the steam pipes, and the medicinal materials are arranged on the connecting plate, so that a multilayer medicinal material drying plate is formed.
2. The steam heat exchanger of claim 1 wherein the steam tube is square in cross-section.
3. The steam heat exchanger of claim 2, the flow stabilizers comprising at least one of a first type being a square central flow stabilizer with a square through hole in the center of the steam tube and a second type being a regular octagonal central flow stabilizer with a regular octagonal through hole in the center of the steam tube.
4. A steam heat exchanger according to claim 3 wherein the flow stabilizers are of two types and the adjacently disposed flow stabilizers are of different types.
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| WO2015185589A1 (en) * | 2014-06-05 | 2015-12-10 | BSH Hausgeräte GmbH | Evaporator |
| CN107044789A (en) * | 2017-04-21 | 2017-08-15 | 青岛金玉大商贸有限公司 | A kind of porous constant-current stabilizer heat pipe |
| CN107327821A (en) * | 2017-08-31 | 2017-11-07 | 青岛科技大学 | A kind of steam generator of intelligent control vapor (steam) temperature |
| CN107966051A (en) * | 2017-04-21 | 2018-04-27 | 青岛金玉大商贸有限公司 | A kind of condensable porous type constant-current stabilizer heat exchanger of spacing change |
| CN107976093A (en) * | 2017-04-21 | 2018-05-01 | 青岛金玉大商贸有限公司 | A kind of non-condensable gas porous type constant-current stabilizer heat exchanger of spacing change |
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Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2015185589A1 (en) * | 2014-06-05 | 2015-12-10 | BSH Hausgeräte GmbH | Evaporator |
| CN107044789A (en) * | 2017-04-21 | 2017-08-15 | 青岛金玉大商贸有限公司 | A kind of porous constant-current stabilizer heat pipe |
| CN107966051A (en) * | 2017-04-21 | 2018-04-27 | 青岛金玉大商贸有限公司 | A kind of condensable porous type constant-current stabilizer heat exchanger of spacing change |
| CN107976093A (en) * | 2017-04-21 | 2018-05-01 | 青岛金玉大商贸有限公司 | A kind of non-condensable gas porous type constant-current stabilizer heat exchanger of spacing change |
| CN107327821A (en) * | 2017-08-31 | 2017-11-07 | 青岛科技大学 | A kind of steam generator of intelligent control vapor (steam) temperature |
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