Low-energy-consumption cooling system of pressure vessel and control method of low-energy-consumption cooling system

Abstract

The invention belongs to the field of boiler pressure vessels, and discloses a low-energy-consumption cooling system of a pressure vessel, which comprises an air cooling device for mixing cold air into exhausted gas to reduce the temperature of the exhausted gas; the air cooling device comprises an outer cylinder, a conical air inlet nozzle and an inner cylinder; the inner diameter of the conical air inlet nozzle is gradually reduced in the direction away from the exhaust pipeline; annular plates are fixedly connected between two ends of the inner cylinder and the inner wall of the outer cylinder; an air inlet cavity is formed between the annular plate and the conical air inlet nozzle; a clamping cavity is formed between the inner cylinder and the outer cylinder; a communicating hole is formed in the annular plate; an air inlet hole is formed in the wall of the outer cylinder; the refrigerant inlet pipe comprises a supply section, a coil pipe section and a guide-out section which are sequentially communicated, and the coil pipe section is located in the clamping cavity and wound on the outer wall of the inner barrel. According to the invention, full cooling of high-temperature gas is realized in a mode of combining liquid cooling and air cooling, and compared with liquid cooling, the cooling device has the advantage of low energy consumption. The invention correspondingly discloses a control method of the low-energy-consumption cooling system of the pressure vessel.

Description

Technical Field

[0001] The invention belongs to the technical field of boiler pressure vessels, and particularly relates to a low-energy consumption cooling system for a pressure vessel and a control method thereof. Background Art

[0002] Boiler pressure vessels are the full names of boilers and pressure vessels. Because they belong to special equipment, they play an important role in production and life.

[0003] At present, the exhaust pipes of boiler pressure vessels on the market are usually designed as single layers, with poor overall heat insulation and corrosion resistance, low service life, and easy to generate large noises during use. When the pressure is too high, the pipeline is prone to rupture. At the same time, the existing exhaust pipes do not have a cooling effect, the temperature of the discharged gas is relatively high, which is easy to cause environmental pollution and poor environmental protection. Therefore, those skilled in the art have provided an exhaust pipe for a boiler pressure vessel to solve the problems raised in the above background art.

[0004] In the related art, CN212537795U discloses an exhaust pipe for a boiler pressure vessel. The exhaust pipe body is composed of an outer shell and an inner shell. An aggregation area is arranged inside the inner shell, a dispersion area is arranged above the aggregation area, and an exhaust valve is arranged between the aggregation area and the dispersion area. A silencing area is arranged above the dispersion area. The exhaust pipe is designed as a double-layer structure, effectively improving its heat insulation and corrosion resistance and extending the service life of the exhaust pipe. At the same time, three layers of structures, namely an aggregation area, a dispersion area, and a silencing area, are arranged inside the inner shell. The aggregation area is a conical structure from bottom to top, which can aggregate the gas on the exhaust valve, control the automatic opening or closing of the exhaust valve. At the same time, this design can extend the residence time of the gas in the inner shell, improve the gas cooling effect, and has the effect of silencing and noise reduction.

[0005] In this cooling and temperature reduction method, continuous and efficient circulating cooling water is required during the exhaust peak period, and the energy consumption for cooling is relatively high. Moreover, there is a problem of low heat transfer efficiency in the circulating water cooling, and the temperature of the gas discharged at the end of the pipeline may still be relatively high. As the gas flows along the pipeline, the temperature becomes lower and lower towards the end. The decrease in temperature difference makes the heat transfer and cooling efficiency of the coolant tend to decrease. To completely cool down, it is necessary to increase the length of the high-temperature gas flow path, or increase the amount of coolant introduced, or extend the heat exchange time between the gas and the coolant. Obviously, extending the pipeline will increase the equipment cost, and increasing the coolant flow rate requires the coolant pumping system to work for a longer time, resulting in increased energy consumption. Summary of the Invention

[0006] The purpose of the present invention is to provide a low-energy consumption cooling system for a pressure vessel and a control method thereof, which have low energy consumption and can completely cool down the discharged gas.

[0007] To achieve the above purpose, the specific technical solutions provided by the present invention are as follows:

[0008] A low - energy - consumption cooling system for a pressure vessel, comprising an exhaust pipe for discharging high - temperature gas; the exhaust pipe includes an inner pipe, an outer pipe, and a refrigerant coil disposed between the inner pipe and the outer pipe for circulating coolant, and both ends of the refrigerant coil are respectively connected to a refrigerant inlet pipe and a refrigerant outlet pipe; the end of the exhaust pipe is connected to an air - cooling device for mixing cold air into the discharged gas to reduce the exhaust temperature.

[0009] The air - cooling device includes,

[0010] An outer cylinder, which is fixedly connected to the end of the exhaust pipe;

[0011] A conical air inlet nozzle disposed inside the outer cylinder, the conical air inlet nozzle is connected to one end of the outer cylinder close to the exhaust pipe and the inner diameter gradually decreases in the direction away from the exhaust pipe;

[0012] And an inner cylinder disposed inside the outer cylinder, the length of the inner cylinder is less than that of the outer cylinder, and annular plates are fixedly connected between the outer edges of both ends and the inner wall of the outer cylinder; an air inlet cavity is formed between the annular plate and the conical air inlet nozzle, and a clamping cavity is formed between the outer circumferential side wall of the inner cylinder and the inner circumferential side wall of the outer cylinder; a number of communication holes for communicating the air inlet cavity and the clamping cavity are opened on the annular plate, and a number of air inlet holes for communicating the clamping cavity are opened on the barrel wall of the outer cylinder.

[0013] The refrigerant inlet pipe includes a supply section, a coil section, and a lead - out section that are sequentially connected, wherein the coil section is located in the clamping cavity and is wound around the outer wall of the inner cylinder.

[0014] By adopting the above - mentioned technical solution, an air - cooling device is arranged at the end of the exhaust pipe, which can further cool the gas that has been cooled by heat exchange with the coolant, so that the temperature of the finally discharged gas is close to room temperature, and the high - temperature gas discharged from the pressure vessel is cooled more thoroughly. The specific structure of the air - cooling device enables the gas to enter the inner cylinder from the air jet nozzle, the air flow speed increases and the air pressure decreases, so that the outside low - temperature air is sucked in and mixed evenly through the air inlet cavity, the communication holes, the clamping cavity and the air inlet holes to achieve the cooling purpose. This cooling method does not require an additional gas circulation supply system, improving the cooling effect of the discharged gas without increasing energy consumption. Among them, the coil section of the refrigerant pipe is arranged in the clamping cavity, which is conducive to reducing the temperature of the air entering the air inlet cavity and conducive to giving full play to the air - cooling effect. At the same time, it should be noted that the gas temperature at the inlet side of the exhaust pipe is high and the density is small. If the air - cooling device is arranged at the inlet side of the exhaust pipe, the effect of introducing outside cold air may be poor due to the small gas density. Therefore, it is better to arrange the air - cooling device at the end of the exhaust pipe to ensure the smooth and stable operation of the air - cooling device.

[0015] Further, it further includes an air inlet cover covering the air inlet holes on the outer cylinder. The air inlet cover is communicated with an air supply pipe, and the air supply pipe includes a visible pipe section and a buried pipe section buried underground. With the help of the air inlet cover and the air supply pipe, low-temperature air can be supplied to the clamping cavity. The buried pipe section buried underground can reduce heat exchange, and the temperature of the air introduced into the clamping cavity is close to or lower than the room temperature, and the cooling effect is better.

[0016] Further, the outer cylinder includes a fixed section and an adjustable section connected by threads. The ring plate and the inner cylinder are both arranged in the adjustable section. According to the high or low exhaust temperature, the relative positions of the fixed end and the adjustable section can be adjusted, that is, the size of the air inlet cavity or the depth of the conical air inlet nozzle inserted into the inner cylinder can be changed, so as to adjust the air mixing and cooling effect.

[0017] Further, the aperture of the communication hole is smaller than that of the air inlet hole, which is more conducive to smoothly introducing cold air and realizing air-cooling.

[0018] Further, a heat insulation material layer is provided on the outer wall of the inner cylinder.

[0019] Further, the coil pipe section includes a plurality of independent spiral branch pipes, and the plurality of spiral branch pipes are equidistantly distributed around the axis of the inner cylinder.

[0020] Further, the refrigerant coil pipe includes a plurality of independent refrigerant branch pipes, and the plurality of refrigerant branch pipes are equidistantly distributed around the axis of the exhaust pipe.

[0021] Further, a grille plate is fixedly provided at one end of the outer cylinder away from the exhaust pipe, and the aperture of the mesh holes on the grille plate gradually increases from the center of the grille plate to the periphery.

[0022] Further, the refrigerant inlet pipe further includes an intermediate pipe section arranged in parallel with the coil pipe section. According to actual needs, the amount of coolant introduced between the inner pipe and the outer pipe can be increased by means of the intermediate pipe section, so as to maintain the temperature of the gas entering the air-cooling device at a relatively stable level and prevent the air-cooling effect from fluctuating due to large fluctuations in the gas temperature.

[0023] Further, a proportional solenoid valve is installed on the coil pipe section. The proportional solenoid valve is connected to a controller, and the controller is connected to a temperature sensor; the temperature sensor is arranged in the exhaust pipe and is located on the air inlet side of the exhaust pipe. The controller can be a PLC, a microcontroller, etc. Based on the temperature sensor, the controller and the proportional solenoid valve, the flow rate of the coolant flowing through the clamping cavity can be dynamically adjusted according to the temperature change, so as to ensure the best cooling effect.

[0024] On the other hand, the present invention provides a control method for a low-energy consumption cooling system applied to the aforementioned pressure vessel, and the steps are as follows:

[0025] S1. The temperature sensor detects the temperature of the gas in the exhaust pipe and outputs a corresponding temperature signal, and the output temperature signal is connected to the analog input port of the controller;

[0026] S2. The controller calculates and outputs a corresponding control signal according to the temperature signal, and the control signal output by the controller is connected to the drive circuit of the proportional solenoid valve;

[0027] S3. The proportional solenoid valve adjusts the spool position according to the magnitude of the input control signal, thereby regulating the flow rate; if the temperature is higher than the set value, the output signal of the controller increases and the proportional solenoid valve increases; if the temperature is lower than the set value, the output signal of the controller decreases and the proportional solenoid valve decreases.

[0028] The present invention has the following beneficial effects:

[0029] First, on the basis of cooling the refrigerant coil, the present invention further sets up an air-cooling device, which uses a high-speed air flow to inhale low-temperature air and mix it quickly to achieve further cooling of the gas after being cooled by the refrigerant, and the cooling is complete;

[0030] Second, the air-cooling device can directly introduce low-temperature air without adding an additional air supply system, and the energy consumption is low; the refrigerant inlet pipe includes a coil section arranged in the clamping cavity, which can pre-cool the air and is conducive to giving full play to the air-cooling effect;

[0031] Third, in the preferred solution, the temperature sensor, the controller and the proportional solenoid valve can be used to regulate the magnitude of the coolant flow rate flowing through the clamping cavity, and dynamically distribute the coolant flow rate for refrigerant cooling and air-cooling, so as to adapt to the fluctuating change of the temperature of the gas discharged from the pressure vessel. Description of the Drawings

[0032] Figure 1 is a schematic structural diagram of the low-energy consumption cooling system of the pressure vessel in Embodiment 1 of the present invention Figure 1 ;

[0033] Figure 2 is a schematic structural diagram of the low-energy consumption cooling system of the pressure vessel in Embodiment 1 of the present invention Figure 2 ;

[0034] Figure 3 is a cross-sectional view of the exhaust pipe and the air-cooling device in Embodiment 1 of the present invention;

[0035] Figure 4 is a schematic structural diagram of the grille plate in Embodiment 1 of the present invention;

[0036] Figure 5 is a cross-sectional view of the air-cooling device in Embodiment 2 of the present invention;

[0037] Figure 6 is a cross-sectional view of the air-cooling device in Embodiment 3 of the present invention.

[0038] Description of reference numerals:

[0039] 1. Container body; 2. Exhaust duct; 21. Inner tube; 22. Outer tube; 23. Connecting flange; 3. Refrigerant coil; 31. Refrigerant inlet pipe; 311. Supply section; 312. Coil section; 313. Lead-out section; 314. Intermediate pipe section; 32. Refrigerant outlet pipe; 4. Air cooling device; 41. Outer tube; 411. Fixed section; 412. Adjustable section; 4121. Air inlet hole; 413. Grille plate; 42. Inner tube; 43. Conical air inlet nozzle; 44. Ring plate; 441. Connecting hole; 45. Air inlet cavity; 46. Clamp cavity; 5. Air inlet hood; 51. Air supply pipe; 511. Open pipe section; 512. Concealed pipe section; 6. Proportional solenoid valve; 7. Controller; 8. Temperature sensor. DETAILED DESCRIPTION

[0040] In order to enable those skilled in the art to better understand the technical solutions of the present invention, the present application will be further described in detail below in conjunction with the accompanying drawings.

[0041] Example 1

[0042] Reference Figure 1 A low energy consumption cooling system for a pressure vessel is used to cool down the high temperature gas discharged from the container body 1 and then discharge it, and it includes an exhaust pipe 2 and an air cooling device 4. When installed, the exhaust pipe 2 is in a vertical state, and its lower end opening is directly connected to the gas outlet of the container body 1 or connected through a pipeline.

[0043] Reference Figure 2 and Figure 3 , the exhaust pipe 2 includes an inner pipe 21 and an outer pipe 22 arranged coaxially, and connecting flanges 23 are provided at both ends of the exhaust pipe 2. The outer wall of the inner pipe 21 is wound with a refrigerant coil 3 located in the interlayer between the inner pipe 21 and the outer pipe 22. The two ends of the refrigerant coil 3 are respectively connected with a refrigerant inlet pipe 31 and a refrigerant outlet pipe 32. Water or other coolants can be used for cooling. The coolant enters the refrigerant coil 3 from the refrigerant inlet pipe 31, and after heat exchange with the high-temperature gas flowing through the inner pipe 21 in the interlayer, it is discharged from the refrigerant outlet pipe 32; the temperature of the high-temperature gas in the inner pipe 21 is greatly reduced, and the initial cooling is completed. In order to improve the cooling efficiency, the coolant is introduced in a countercurrent manner, that is, the coolant flows through the refrigerant coil 3 in the opposite direction of the high-temperature gas. In other embodiments, multiple parallel refrigerant branches can also be provided; multiple refrigerant branches are spaced around the axis of the inner pipe 21, which can improve the uniformity and efficiency of cooling.

[0044] Reference Figure 2 and Figure 3, the top end of the exhaust pipe 2 is fixedly connected and communicated with an air cooling device 4 through a connecting flange 23. The air cooling device 4 includes an outer cylinder 41 and an inner cylinder 42 arranged coaxially. The length of the inner cylinder 42 is less than that of the outer cylinder 41. Annular plates 44 are provided at the peripheries of both ends of the inner cylinder 42, and the outer edges of the annular plates 44 are fixed to the inner wall of the outer cylinder 41. An air inlet cavity 45 is formed between the annular plate 44 close to the exhaust pipe 2 and the inlet of the outer cylinder 41. The inner cylinder 42, the outer cylinder 41 and the annular plates 44 at both ends enclose a clamping cavity 46.

[0045] Refer to Figure 2 and Figure 3 , a plurality of communication holes 441 are opened on the annular plate 44 close to the exhaust pipe 2, and the communication holes 441 communicate the clamping cavity 46 and the air inlet cavity 45. A plurality of air inlet holes 4121 are uniformly distributed on the outer wall of the outer cylinder 41. The aperture of the air inlet holes 4121 is larger than that of the communication holes 441, and the clamping cavity 46 is communicated with the outside.

[0046] Refer to Figure 2 and Figure 3 , a conical air inlet nozzle 43 is provided in the air inlet cavity 45. The caliber of the conical air inlet nozzle 43 gradually decreases from one end of the exhaust pipe 2 towards the direction close to the inner cylinder 42. Its large-caliber end is fixed to the inner wall of the outer cylinder 41, and its small-caliber end extends into the inner cylinder 42. In this way, the gas with residual temperature discharged from the exhaust pipe 2 is sprayed into the inner cylinder 42 through the conical air inlet nozzle 43. The air flow velocity increases and the air pressure decreases, forming a pressure difference. Thus, the low-temperature cold air from the outside is introduced into the inner cylinder 42 through the air inlet cavity 45, the communication holes 441, the clamping cavity 46 and the air inlet holes 4121, and is mixed evenly with the waste heat gas in the inner cylinder 42, realizing further cooling of the waste heat gas.

[0047] Refer to Figure 2 , Figure 3 and Figure 4 , a grille plate 413 is provided at the end of the outer cylinder 41. The aperture of the mesh holes on the grille plate 413 gradually increases from the center to the periphery, and the distribution density of the mesh holes on the grille plate 413 gradually increases from the center to the periphery. In this way, the gas discharged from the end of the inner cylinder 42 is further mixed before being discharged, solving the problem of incomplete cooling by pure coolant in the prior art. In addition, since the air cooling device 4 cools by means of room temperature air and is self-suction, there is no need to be equipped with an additional power transmission mechanism, and it has the advantage of low energy consumption.

[0048] Refer to Figure 2 and Figure 3, in order to give full play to the cooling effect of the air-cooling device 4, the refrigerant inlet pipe 31 is set as a supply section 311, a coil section 312, and a lead-out section 313 that are connected in sequence. The supply section 311 is connected to a refrigerant supply device, such as a cooling water pump, etc. The refrigerant supply device is a conventional means and will not be elaborated here; the end of the lead-out section 313 is connected to the refrigerant coil 3, and the coil section 312 is wound around the outer wall of the inner cylinder 42 and is located in the clamping cavity 46. In this way, before the coolant enters the refrigerant coil 3, it can pre-cool the air entering the clamping cavity 46, which is conducive to giving full play to the air-cooling effect. Further, an insulating material layer is formed on the outer wall of the inner cylinder 42 by coating with an insulating paint, which blocks or slows down the heat transfer between the clamping cavity 46 and the inner cylinder 42, so that the air can maintain a low temperature as much as possible before being mixed into the high-temperature gas.

[0049] Refer to Figure 2 and Figure 3 , in order to dynamically adjust the refrigerant flow rate flexibly according to the gas temperature change and minimize the amount of coolant introduced on the premise of ensuring that the final exhaust temperature is reduced to the required temperature, so as to save the cooling energy consumption, a temperature sensor 8 is provided in the intake pipe in this embodiment. The temperature sensor 8 is provided on the inner pipe 21 and is near the intake port of the inner pipe 21. The temperature sensor 8 is connected to the controller 7. A proportional solenoid valve 6 (Proportional Solenoid Valve) is installed on the coil section 312, and the proportional solenoid valve 6 is connected to the controller 7 (such as a PID controller, etc.). At the same time, the refrigerant inlet pipe 31 further includes an intermediate pipe section 314 that is parallel to the coil section 312, and a proportional solenoid valve 6 connected to the controller 7 is also installed on the intermediate pipe section 314.

[0050] The method for dynamically regulating the refrigerant flow rate based on the temperature sensor 8, the controller 7, and the proportional solenoid valve 6 is as follows:

[0051] S1. The temperature sensor 8 detects the gas temperature in the exhaust pipe 2 and outputs a corresponding temperature signal, and the output temperature signal is connected to the analog input port of the controller 7;

[0052] S2. The controller 7 calculates and outputs a corresponding control signal according to the temperature signal, and the control signal (such as PWM or analog voltage / current) output by the controller 7 is connected to the drive circuit of the proportional solenoid valve 6;

[0053] S3. The proportional solenoid valve 6 adjusts the spool position according to the magnitude of the input control signal, thereby regulating the flow rate; if the temperature is higher than the set value, the signal output by the controller 7 increases, and the proportional solenoid valve 6 increases; if the temperature is lower than the set value, the signal output by the controller 7 decreases, and the proportional solenoid valve 6 decreases.

[0054] Based on the foregoing control method, the flow rate of the coolant flowing through the intermediate pipe section 314 and the coil pipe section 312 can be adjusted to dynamically adapt to the change of the gas temperature, minimize the energy consumption required for cooling as much as possible, and ensure that the final exhaust temperature reaches the predetermined requirements.

[0055] Embodiment 2

[0056] Embodiment 2 is based on Embodiment 1, with reference to Figure 5 , and the difference is only that: the volume of the air inlet cavity 45 is adjustable, or the depth of the conical air inlet nozzle 43 inserted into the inner cylinder 42 is adjustable.

[0057] Specifically, the outer cylinder 41 includes two parts, a circular tubular fixed section 411 and an adjustable section 412, which are threadedly connected between them. The inner cylinder 42 and the ring plate 44 are both arranged in the adjustable section 412; the fixed end is fixed to the end of the exhaust pipe 2 through the connecting flange 23. By rotating, the relative position between the fixed section 411 and the adjustable section 412 in the axial direction can be changed, so as to adjust the volume of the air inlet cavity 45 or the depth of the conical air inlet nozzle 43 inserted into the inner cylinder 42, so that the introduced low-temperature air can be mixed with the high-temperature gas in a better proportion and give full play to the cooling effect.

[0058] Embodiment 3

[0059] Embodiment 3 is based on Embodiment 1, with reference to Figure 6 , and the difference is only that: an air inlet hood 5 covering all the air inlet holes 4121 is arranged on the outer cylinder 41, and the air inlet hood 5 is hermetically arranged with the outer cylinder 41. The air inlet hood 5 is communicated with a gas supply pipe 51, and the gas supply pipe 51 includes a visible pipe section 511 exposed to the air and a buried pipe section 512 buried underground. The buried pipe section 512 can reduce the temperature of the air introduced into the clamping cavity 46 to a certain extent, which is beneficial to the exertion of the cooling effect of the air cooling device 4.

[0060] The above are all the preferred embodiments of this application, and the protection scope of this application is not limited accordingly. Therefore, all equivalent changes made according to the structure, shape, and principle of this application should be covered within the protection scope of this application.

Claims

1. A low energy consumption cooling system for a pressure vessel, comprising an exhaust pipe (2) for exhausting high temperature gas; the exhaust pipe (2) comprises an inner pipe (21), an outer pipe (22) and a refrigerant coil (3) arranged between the inner pipe (21) and the outer pipe (22) for circulating a cooling liquid, wherein the two ends of the refrigerant coil (3) are respectively connected with a refrigerant inlet pipe (31) and a refrigerant outlet pipe (32), wherein: The end of the exhaust pipe (2) is connected to an air cooling device (4) for mixing cold air into the exhaust gas to reduce the exhaust temperature; The air cooling device (4) comprises: An outer cylinder (41), the outer cylinder (41) is fixedly connected to the end of the exhaust pipe (2); A conical air inlet nozzle (43) is arranged in the outer cylinder (41), the conical air inlet nozzle (43) is connected to one end of the outer cylinder (41) close to the exhaust pipe (2) and the inner radial direction of the conical air inlet nozzle (43) gradually decreases away from the exhaust pipe (2); and an inner cylinder (42) arranged in the outer cylinder (41); the inner cylinder (42) is shorter than the outer cylinder (41) and has an annular plate (44) fixedly connected between the outer edges of both ends and the inner wall of the outer cylinder (41); an air intake cavity (45) is formed between the annular plate (44) and the conical air intake nozzle (43); a clamping cavity (46) is formed between the outer circumferential side wall of the inner cylinder (42) and the inner circumferential side wall of the outer cylinder (41); a plurality of connecting holes (441) connecting the air intake cavity (45) and the clamping cavity (46) are formed on the annular plate (44); a plurality of air intake holes (4121) connecting the clamping cavity (46) are formed on the wall of the outer cylinder (41); The refrigerant inlet pipe (31) comprises a supply section (311), a coil section (312) and a discharge section (313) which are connected in sequence, wherein the coil section (312) is located in the clamping cavity (46) and is wound around the outer wall of the inner tube (42).

2. The low energy consumption cooling system for a pressure vessel according to claim 1, characterized in that: The outer cylinder (41) comprises a fixed section (411) and an adjustable section (412) connected by threads, and the ring plate (44) and the inner cylinder (42) are both arranged in the adjustable section (412).

3. The low energy consumption cooling system for a pressure vessel according to claim 1, characterized in that: The diameter of the connecting hole (441) is smaller than that of the air inlet hole (4121).

4. The low energy consumption cooling system for a pressure vessel according to claim 1, characterized in that: The outer wall of the inner cylinder (42) is provided with a heat insulation material layer.

5. The low energy consumption cooling system for a pressure vessel according to any one of claims 1 to 4, characterized in that: The coil section (312) includes a plurality of independent spiral branch pipes, and the plurality of spiral branch pipes are evenly spaced and distributed around the axis of the inner tube (42).

6. The low energy consumption cooling system for a pressure vessel according to claim 5, characterized in that: The refrigerant coil (3) comprises a plurality of independent refrigerant branch pipes, and the plurality of refrigerant branch pipes are distributed at equal intervals around the axis of the exhaust pipe (2).

7. The low energy consumption cooling system for a pressure vessel according to any one of claims 1 to 4, characterized in that: A grille plate (413) is fixedly provided at one end of the outer cylinder (41) away from the exhaust pipe (2), and the diameter of the mesh holes on the grille plate (413) gradually increases from the center of the grille plate (413) to the periphery.

8. The low energy consumption cooling system for a pressure vessel according to any one of claims 1 to 4, characterized in that: The refrigerant inlet pipe (31) further includes an intermediate pipe section (314) arranged in parallel with the coil section (312).

9. The low energy consumption cooling system for a pressure vessel according to claim 8, characterized in that: The coil section (312) is equipped with a proportional solenoid valve (6), the proportional solenoid valve (6) is connected to a controller (7), and the controller (7) is connected to a temperature sensor (8); the temperature sensor (8) is arranged in the exhaust pipe (2) and is located on the air intake side of the exhaust pipe (2).

10. A control method for a low energy consumption cooling system of a pressure vessel according to claim 9, characterized in that: The steps are as follows, S1, the temperature sensor (8) detects the gas temperature in the exhaust pipe (2) and outputs a corresponding temperature signal, and the output temperature signal is connected to the analog input port of the controller (7); S2, the controller (7) calculates and outputs a corresponding control signal according to the temperature signal, and the control signal output by the controller (7) is connected to the drive circuit of the proportional solenoid valve (6); S3, the proportional solenoid valve (6) adjusts the valve core position according to the size of the input control signal, thereby adjusting the flow rate; if the temperature is higher than the set value, the controller (7) output signal increases, and the proportional solenoid valve (6) increases; if the temperature is lower than the set value, the controller (7) output signal decreases, and the proportional solenoid valve (6) decreases.

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