Low-dew-point heat energy closed-loop energy-saving dehumidification system

Abstract

The invention discloses a low-dew-point heat energy closed-loop energy-saving dehumidification system which comprises a regeneration precooler and a regeneration preheater. The regeneration separator is used for separating the gaseous state and the liquid in the fluid; the regeneration compression pump is used for driving fluid to flow; a first circulating pipeline is arranged between the regeneration precooler and the regeneration preheater; the first circulation pipeline is sequentially communicated with the regeneration precooler, the regeneration separator, the regeneration compression pump, the regeneration preheater and the regeneration precooler to form a closed loop circulation pipeline. Heat energy in front of the return air surface cooler is recycled and transferred to regeneration heating and air supply heating, so that the load and energy consumption of return air surface cooler, regeneration heating and air supply heating are reduced, and the purpose of saving energy is achieved. The flow of the fluid is accurately detected and adjusted in real time through the sensor, the temperature of the fluid flowing in and out of each component is accurately controlled, and heat loss is reduced to the minimum.

Description

Technical Field

[0001] The invention belongs to the technical field of rotary dehumidification, and in particular relates to a low dew point thermal energy closed-loop energy dehumidification system. Background Art

[0002] The fresh air of the low dew point rotary dehumidification system passes through the fresh air filter and is then condensed and dehumidified by the fresh air surface cooler, and then deeply dehumidified by the first-stage rotary wheel; the return air from the drying workshop is mixed with the fresh air after deep dehumidification and filtered, and then the mixed air temperature is lowered by the return air surface cooler, and then further dehumidified by the second-stage rotary wheel, thereby obtaining low dew point air with extremely low dew point. After the air is sent to the drying workshop for temperature adjustment (heating or cooling), it is sent to the drying workshop through the processing fan and is simultaneously drawn back to the dehumidification system; the regeneration air of the dehumidification system It is the low-temperature air taken from the mixed air table after cooling. The low-temperature air can take out the heat attached to the wheel after the high-temperature regeneration of the secondary wheel, thereby raising the wind temperature to 40-45℃ to achieve initial warming (cold blowing). Then the air is heated to 120-130℃ by the heater to regenerate and desorb the secondary wheel. The regenerated exhaust air of the secondary wheel is heated to 120-130℃ by the heater again to regenerate and desorb the primary wheel. The air after regeneration and desorption is discharged to the outside through the regeneration fan.

[0003] In the low dew point rotary dehumidification system, the heat load of the return air cooler is composed of the return air heat load and the fresh air heat load. The return air heat load is the heat load caused by the heat generated by the equipment, personnel and materials in the drying room, and the fresh air heat load is composed of the residual heat load accumulated on the wheel after the regeneration of the first-stage wheel. In the low dew point rotary dehumidification system, after the return air cooler lowers the air temperature, it needs to increase the air temperature by supply air heating to achieve a constant temperature state in the drying room. Therefore, the return air cooler in the low dew point dehumidification system is in a process of offsetting the cold and hot loads.

[0004] The Chinese patent document with publication number CN117588803A discloses a rotary dehumidification system and a rotary dehumidification control method. The system includes: a first-stage rotary wheel and a second-stage rotary wheel; fresh air is sent to the target area after passing through the treatment area of ​​the two-stage rotary wheel in sequence, and the return air of the target area merges with the outlet air of the first-stage rotary wheel treatment area; fresh air or mixed air enters the second-stage rotary wheel regeneration area after being heated by the first condenser and / or the electric heater, and the mixed air is obtained by diversion from the air inlet of the second-stage rotary wheel treatment area; fresh air or exhaust air of the second-stage rotary wheel regeneration area enters the first-stage rotary wheel regeneration area after being heated by the second condenser; the first condenser and the first evaporator are connected to the same refrigerant circulation loop, the second condenser and the second evaporator are connected to the same refrigerant circulation loop, and the first evaporator and the second evaporator are installed in the area with cooling demand.

[0005] In the above patent solution, two condensers and two evaporators are arranged between the secondary rotor and the primary rotor in the regeneration stage, which can balance the cooling capacity gap, provide sufficient heat for the regeneration air, and reduce the use of electric heaters to a certain extent. However, in the dehumidification stage, the return air and the fresh air are mixed between the primary rotor and the secondary rotor. The mixed air needs to be cooled before entering the secondary rotor, and the air coming out of the secondary rotor needs to be reheated. Thus, the alternating cold and heat exchange results in a large amount of energy loss and a huge energy consumption. Summary of the invention

[0006] In order to overcome the technical problem in the prior art that the air entering the secondary wheel needs to be cooled, while the air coming out of the secondary wheel needs to be heated, and the reciprocating heat exchange is performed, which will cause a lot of energy loss; one purpose of the present invention is to provide a low dew point thermal energy closed-loop energy-saving dehumidification system, which reduces the load of the return air cooler by transferring the heat energy recovered before the return air cooler to regeneration heating and supply air heating, that is, reduces the energy consumption of refrigeration; at the same time, after the heat energy is transferred to regeneration heating and supply air heating, the heating energy consumption of regeneration heating and supply air heating is also reduced.

[0007] In order to achieve the above-mentioned purpose, the present invention adopts the following technical scheme: a low dew point thermal energy closed-loop energy-saving dehumidification system, including a regenerative precooler, the regenerative precooler is arranged between the first-level rotor and the second-level rotor, the fresh air passing through the first-level rotor and the return air passing through the second-level rotor are mixed to form a mixed fluid, and the mixed fluid passes through the regenerative precooler and the return air surface cooler in sequence to enter the processing area and the auxiliary regeneration area of ​​the second-level rotor; a regenerative preheater, the fluid passing through the auxiliary regeneration area of ​​the second-level rotor passes through the regenerative preheater, the first regenerative heater, and the regeneration area of ​​the second-level rotor in sequence; a regenerative separator, the regenerative separator is used to separate the gas and liquid in the fluid; a regenerative compression pump, the regenerative compression pump is used to drive the fluid to flow; wherein a first circulation pipeline is arranged between the regenerative precooler and the regenerative preheater; the first circulation pipeline is connected to the regenerative precooler, the regenerative separator, the regenerative compression pump, the regenerative preheater, and the regenerative precooler in sequence to form a closed-loop circulation pipeline.

[0008] Further, a first temperature sensor and a pressure sensor are provided on the first circulation pipeline between the regenerative precooler and the regenerative separator; an electronic throttle valve is provided on the first circulation pipeline between the regenerative preheater and the regenerative precooler;

[0009] Specifically, the electronic throttle valve adjusts its opening according to superheat; when the actual superheat is greater than the preset superheat, the opening of the electronic throttle valve increases; when the actual superheat is less than the preset superheat, the opening of the electronic throttle valve decreases; the superheat = the temperature of the liquid after vaporization in the first circulation pipeline after absorbing heat detected by the first temperature sensor - the temperature corresponding to the saturated pressure of the liquid after vaporization in the first circulation pipeline after absorbing heat detected by the pressure sensor.

[0010] Specifically, the preset superheat of the electronic throttle valve is 4-6K.

[0011] Furthermore, it includes an air supply precooler, and the fluid passing through the regenerative precooler passes through the air supply precooler and the return air surface cooler in sequence and then flows to the secondary rotor; an air supply separator, and the air supply separator is used to separate the gas and liquid in the fluid; an air supply compression pump, and the air supply compression pump is used to drive the fluid flow; an air supply heater, and the air supply heater is used to adjust the temperature of the fluid flowing out of the secondary rotor processing area; wherein a second circulation pipeline is arranged between the regenerative precooler and the air supply heater; the second circulation pipeline is connected with the air supply precooler, the air supply separator, the air supply compression pump, the air supply heater, and the air supply precooler in sequence to form a closed-loop circulation pipeline.

[0012] Specifically, a second temperature sensor is provided on the second circulation pipeline between the supply air precooler and the supply air separator; and a mechanical throttle valve is provided on the second circulation pipeline between the supply air heater and the supply air precooler.

[0013] Specifically, the second temperature sensor detects the temperature of the liquid in the second circulation pipeline after absorbing heat and vaporizing, and transfers the heat of the temperature to the inside of the mechanical throttle valve to push the valve needle to open larger or smaller.

[0014] Specifically, the size of the mechanical throttle valve is designed according to the standard superheat of 5K; when the actual superheat is less than 5K, the opening of the mechanical throttle valve is reduced; when the actual superheat is greater than 5K, the opening of the mechanical throttle valve is increased.

[0015] Furthermore, the return air surface cooler uses chilled water or Freon as a cooling source.

[0016] Furthermore, the temperature of air passing through the return air cooler is less than 12°C.

[0017] Compared with the prior art, the beneficial effect of the present invention is that the present invention not only reduces the refrigeration load and energy consumption of the return air cooler, but also reduces the load and energy consumption of the regenerative heating and the supply air heating by transferring the heat energy recovery before the return air cooler to the regenerative heating and the supply air heating, thereby achieving the purpose of energy saving. At the same time, the temperature of the first circulation pipeline and the second circulation pipeline is accurately detected by the sensor, the flow rate of the fluid is adjusted in real time, and the temperature of the fluid entering and exiting each component is accurately controlled, so as to minimize the heat loss and further achieve energy saving. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Figure 1 This is the process flow chart of the low dew point rotary dehumidification system in the existing design;

[0019] Figure 2 It is a process flow chart of the low dew point thermal energy arm link energy dehumidification system of the present invention;

[0020] Figure 3 The process flow chart of the present invention is different from the prior art;

[0021] Figure 4 is a process flow chart of the first circulation pipeline of the present invention;

[0022] Figure 5 is a process flow chart of the second circulation pipeline of the present invention;

[0023] Figure 6 It is a schematic diagram of the working area distribution of the secondary rotor of the present invention.

[0024] In the figure: 11, fresh air filter; 12, fresh air surface cooler; 13, primary rotor; 21, treatment fan wheel; 22, return air filter; 23, return air surface cooler; 24, secondary rotor; 241, treatment area; 242, auxiliary regeneration area; 243, regeneration area; 31, first regeneration heater; 32, second regeneration heater; 33, regeneration fan; 34, supply air heater; 35, drying workshop; 41, regeneration precooler; 42, regeneration separator; 43, regeneration compression pump; 44, regeneration preheater; 45, throttle valve controller; 46, first temperature sensor; 47, pressure sensor; 48, electronic throttle valve; 51, supply air precooler; 52, supply air separator; 53, supply air compression pump; 54, mechanical throttle valve; 55, second temperature sensor. DETAILED DESCRIPTION

[0025] The present invention is further described below in conjunction with the accompanying drawings and specific implementation methods. It should be noted that, under the premise of no conflict, the various embodiments or technical features described below can be arbitrarily combined to form a new embodiment.

[0026] In the description of the present invention, it should be noted that directional words, such as the terms "center", "lateral", "longitudinal", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", etc., indicating directions and positional relationships are based on the directions or positional relationships shown in the accompanying drawings, which are only for the convenience of narrating the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and cannot be understood as limiting the specific scope of protection of the present invention.

[0027] In addition, the terms "first" and "second" are used for descriptive purposes only and cannot be understood as indicating or implying relative importance or implicitly indicating the number of technical features. Therefore, the definition of "first" and "second" features can explicitly or implicitly include one or more of the features. In the description of the present invention, the meaning of "several" is two or more, unless otherwise clearly and specifically defined.

[0028] In the present invention, unless otherwise specified and limited, the terms "setting", "installation" and the like should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can also be a mechanical connection; it can be directly connected, or it can be connected through an intermediate medium, or the two elements can be internally connected. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0029] See also Figure 1-Figure 6 A low dew point thermal energy closed-loop energy-saving dehumidification system includes a fresh air filter 11, a fresh air surface cooler 12, a primary rotor 13, a processing fan wheel 21, a return air filter 22, a regeneration precooler 41, a supply air precooler 51, a return air surface cooler 23, and a secondary rotor 24, which are arranged in sequence according to the flow direction of the fluid. The fluid flowing out of the return air surface cooler 23 is divided into two paths, one of which flows to the processing area 241 of the secondary rotor 24, and the other flows to the auxiliary regeneration area 242 of the secondary rotor 24.

[0030] The fluid flowing out of the treatment area 241 flows to the air supply heater 34, enters the drying workshop 35, and flows to the treatment fan wheel 21. The fluid flowing out of the auxiliary regeneration area 242 flows to the regeneration preheater 44, the first regeneration heater 31, the regeneration area 243 of the secondary rotor 24, the second regeneration heater 32, the primary rotor 13, and the regeneration fan 33 in sequence and is discharged outward.

[0031] The fluid passing through the regenerative precooler 41 also flows to the regenerative separator 42, the regenerative compression pump 43, and the regenerative preheater 44 in sequence; the fluid of the regenerative preheater 44 also flows to the regenerative precooler 41, thereby forming a closed-loop first circulation pipeline.

[0032] A first temperature sensor 46 and a pressure sensor 47 are provided on the first circulation pipeline between the regeneration precooler 41 and the regeneration separator 42; an electronic throttle valve 48 and a throttle valve controller 45 are provided on the first circulation pipeline between the regeneration preheater 44 and the regeneration precooler 41.

[0033] The electronic throttle valve 48 adjusts its opening according to the superheat; when the actual superheat is greater than the preset superheat, the opening of the electronic throttle valve 48 increases; when the actual superheat is less than the preset superheat, the opening of the electronic throttle valve 48 decreases; the superheat = the temperature of the liquid vaporized in the first circulation pipeline after the first temperature sensor 46 detects the heat absorption - the temperature corresponding to the saturated pressure of the liquid vaporized in the first circulation pipeline after the heat absorption detected by the pressure sensor 47. The preset superheat of the electronic throttle valve 48 is 4-6K, preferably 5K.

[0034] The fluid passing through the air supply precooler 51 also flows to the air supply separator 52, the air supply compression pump 53, and the air supply heater 34 in sequence; the fluid of the air supply heater 34 also flows to the air supply precooler 51, thereby forming a closed-loop second circulation pipeline.

[0035] A second temperature sensor 55 is provided on the second circulation pipeline between the air supply precooler 51 and the air supply separator 52; a mechanical throttle valve 54 is provided on the second circulation pipeline between the air supply heater 34 and the air supply precooler 51. The second temperature sensor 55 detects the temperature of the liquid in the second circulation pipeline after absorbing heat and vaporizes, and transfers the heat of the temperature to the inside of the mechanical throttle valve 54 to push the valve needle to open or close. The size of the mechanical throttle valve 54 is designed according to the standard superheat degree 5K; when the actual superheat degree is less than 5K, the opening degree of the mechanical throttle valve 54 is reduced; when the actual superheat degree is greater than 5K, the opening degree of the mechanical throttle valve 54 is increased.

[0036] Solution description: In the low dew point rotary dehumidification system, the temperature of the mixed return air is generally between 25-40℃. This air is cooled to below 12℃ by the return air cooler 23; the supply air heater 34 heats the outlet air of the secondary rotary wheel 24 from 13-14℃ to 20-25℃. The first regeneration heater 31 of the secondary rotary wheel 24 heats the cold outlet air of 40-45℃ to 120-130℃.

[0037] The heat energy before the return air cooler 23 is recovered and transferred to the first regeneration heater 31 and the supply air heater 34, so as to reduce the load of the return air cooler 23. The reduction of the load of the return air cooler 23 can save energy in refrigeration. At the same time, after the heat energy is transferred to the first regeneration heater 31 and the supply air heater 34, the heating energy consumption of regeneration heating and supply air heating can be greatly reduced. The heat energy in the drying workshop 35 does not need to be offset by refrigeration. This part of the heat energy forms a closed-loop utilization of heat energy in the low dew point dehumidification system.

[0038] Specifically, the heat load of the return air cooler 23 of the low dew point rotary dehumidification system is divided into three parts. The regenerative precooler 41 absorbs the return air heat, and the regenerative compression pump 43 transfers the heat to the regenerative preheater 44 through the fluid inside the first circulation pipeline. The regenerative preheater 44 has an air outlet temperature of 80-85°C or above. The regenerative precooler 41 absorbs the heat in the air and reduces the air temperature. The regenerative separator 42 separates the gaseous and liquid states in the fluid. The electronic throttle valve 48 is used to intercept and reduce the pressure of the high-pressure liquid in the first circulation pipeline. The opening of the electronic throttle valve 48 is automatically adjusted by the electronic throttle valve controller 45 by collecting temperature and pressure. In this system process, the heat of the return air is transferred to the regenerative preheater 44, and the first regenerative heater 31 is heated from 40-45°C to 120-130°C, realizing the heating from 80-85°C to 120-130°C. In this process, only a small amount of compression pump power is consumed, but a large amount of regenerative heating energy consumption is saved.

[0039] The air supply precooler 51 absorbs the heat of the air after the regeneration precooler 41 cools down. The air supply compression pump 53 transfers the heat to the air supply heater 34 through the fluid inside the second circulation pipeline. The air outlet of the air supply heater 34 reaches 20-25°C. The air supply precooler 51 absorbs the heat in the air and lowers the air temperature. The air supply separator 52 separates the gaseous and liquid states in the fluid. The mechanical throttle valve 54 is used to intercept and reduce the pressure of the high-pressure liquid in the second circulation pipeline. The opening of the throttle valve is automatically adjusted by the expansion of the liquid inside the second temperature sensor 55. In this system process, part of the heat of the return air is transferred to the air supply heater 34, and the air supply heater 34 consumes only a small amount of compression pump power.

[0040] The air cooled by the air supply precooler 51 is finally cooled by the return air cooler 23 to a process temperature condition of 12°C or less before entering the secondary rotor 24. In the low dew point rotary dehumidification system, the fresh air cooler 12 and the return air cooler 23 can use chilled water as the cooling source, or Freon direct cooling can be used as the cooling source.

[0041] The above description is only a specific embodiment of the present invention, but the technical features of the present invention are not limited thereto. Any changes or modifications made by any technician in the field of the present invention are included in the patent scope of the present invention.

Claims

1. A low dew point thermal energy closed loop energy dehumidification system, characterized in that: It includes a regenerative precooler, which is arranged between the primary rotor and the secondary rotor. The fresh air passing through the primary rotor and the return air passing through the secondary rotor are mixed to form a mixed fluid. The mixed fluid passes through the regenerative precooler and the return air cooler in sequence and enters the processing area and the auxiliary regeneration area of ​​the secondary rotor; a regenerative preheater, the fluid passing through the auxiliary regeneration area of ​​the secondary rotor passes through the regenerative preheater, the first regeneration heater, and the regeneration area of ​​the secondary rotor in sequence; A regeneration separator, the regeneration separator is used to separate gas and liquid in the fluid; A regenerative compression pump, the regenerative compression pump is used to drive the fluid to flow; Among them, a first circulation pipeline is arranged between the regenerative precooler and the regenerative preheater; the first circulation pipeline sequentially connects the regenerative precooler, the regenerative separator, the regenerative compression pump, the regenerative preheater, and the regenerative precooler to form a closed-loop circulation pipeline.

2. The dehumidification system according to claim 1, characterized in that: A first temperature sensor and a pressure sensor are provided on the first circulation pipeline between the regeneration precooler and the regeneration separator; an electronic throttle valve is provided on the first circulation pipeline between the regeneration preheater and the regeneration precooler.

3. The dehumidification system according to claim 2, characterized in that: The electronic throttle valve adjusts its opening according to the superheat; when the actual superheat is greater than the preset superheat, the opening of the electronic throttle valve increases; when the actual superheat is less than the preset superheat, the opening of the electronic throttle valve decreases; the superheat = the temperature of the liquid after vaporization in the first circulation pipeline after absorbing heat detected by the first temperature sensor - the temperature corresponding to the saturated pressure of the liquid after vaporization in the first circulation pipeline after absorbing heat detected by the pressure sensor.

4. The dehumidification system according to claim 3, characterized in that: The preset superheat degree of the electronic throttle valve is 4-6K.

5. The dehumidification system according to any one of claims 1 to 4, characterized in that: It includes a supply air precooler, and the fluid passing through the regenerative precooler sequentially passes through the supply air precooler and the return air surface cooler and then flows to the secondary rotor; An air supply separator, the air supply separator is used to separate gas and liquid in the fluid; An air supply compression pump, the air supply compression pump is used to drive the fluid to flow; The air supply heater is used to adjust the temperature of the fluid flowing out of the secondary wheel processing area; wherein a second circulation pipeline is arranged between the regeneration precooler and the air supply heater; the second circulation pipeline sequentially connects the air supply precooler, the air supply separator, the air supply compression pump, the air supply heater, and the air supply precooler to form a closed-loop circulation pipeline.

6. The dehumidification system according to claim 5, characterized in that: A second temperature sensor is provided on the second circulation pipeline between the air supply precooler and the air supply separator; and a mechanical throttle valve is provided on the second circulation pipeline between the air supply heater and the air supply precooler.

7. The dehumidification system according to claim 6, characterized in that: The second temperature sensor detects the temperature of the liquid in the second circulation pipeline after absorbing heat and transfers the heat of the temperature to the inside of the mechanical throttle valve to push the valve needle to open larger or smaller.

8. The dehumidification system according to claim 7, characterized in that: The size of the mechanical throttle valve is designed according to the standard superheat of 5K; when the actual superheat is less than 5K, the opening of the mechanical throttle valve is reduced; when the actual superheat is greater than 5K, the opening of the mechanical throttle valve is increased.

9. The dehumidification system according to any one of claims 1 to 4, characterized in that: The return air surface cooler uses chilled water or Freon as a cooling source.

10. The dehumidification system according to any one of claims 1 to 4, characterized in that: The temperature of air passing through the return air cooler is less than 12°C.

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