Rotary dehumidification system and its control method

Abstract

This invention relates to the field of air handling equipment technology, and in particular to a rotary dehumidification system and its control method. The rotary dehumidification system includes: at least one rotary wheel, a low-temperature dehumidification side, and a high-temperature regeneration side. The low-temperature dehumidification side has a dehumidification zone and an evaporator, in which a first working fluid flows. The high-temperature regeneration side has at least one gradient condensing heat pump system, each corresponding to one of the rotary wheels, used to gradient-heat the airflow before it enters the regeneration zone of each rotary wheel. The gradient condensing heat pump system includes multiple heat pump systems that sequentially heat the airflow. This invention can simultaneously consider regeneration temperature and system energy consumption, improving the overall energy efficiency and regeneration temperature of the rotary dehumidification system, thus achieving the goal of maximizing energy saving while achieving a high regeneration temperature.

Description

Technical Field

[0001] This invention relates to the field of air handling equipment technology, and in particular to a rotary dehumidification system and its control method. Background Technology

[0002] Rotary dehumidifier units consist of a rotor, a low-temperature dehumidification side, and a high-temperature regeneration side. The rotor includes a regeneration zone and a dehumidification zone. Currently, rotary dehumidifier units typically use electric heating, steam heating, or single-stage heat pumps (single or multiple units) to regenerate the regeneration zone of the rotor. Among these methods, regeneration steam heating or electric heating is energy-intensive; a single-stage heat pump system cannot provide a high regeneration temperature, resulting in low overall system energy efficiency; while using multiple single-stage heat pump systems can increase the regeneration temperature, it leads to high system cost and high energy efficiency. Therefore, existing rotary dehumidifier units suffer from the problem of not being able to simultaneously achieve optimal regeneration temperature and system energy consumption. Summary of the Invention

[0003] In view of the above problems, the present invention is proposed to provide a combined air conditioning unit and its control method that overcomes or at least partially solves the above problems, aiming to solve the problem that existing rotary dehumidification systems cannot simultaneously take into account regeneration temperature and system energy consumption, so as to improve the overall energy efficiency and regeneration temperature of rotary dehumidification systems.

[0004] On one hand, the present invention provides a rotary dehumidification system, comprising:

[0005] At least one impeller, the impeller including a regeneration zone and a dehumidification zone;

[0006] On the low-temperature dehumidification side, the low-temperature dehumidification side is provided with the dehumidification area and the evaporator, and the first working fluid flows in the evaporator;

[0007] On the high-temperature regeneration side, at least one gradient condensation heat pump system is provided. Each gradient condensation heat pump system corresponds to one of the rotors and is used to gradient heat the airflow before it enters the regeneration zone of each rotor. The gradient condensation heat pump system includes multiple heat pump systems that sequentially heat the airflow. The working fluid of the heat pump system that heats the airflow for the first time is the upper-stage working fluid, and the working fluid of the heat pump system that heats the airflow for the next time is the lower-stage working fluid. The lower-stage working fluid exchanges heat with the upper-stage working fluid that releases heat during condensation through a first intermediate heat exchanger when evaporating and absorbing heat. The heat pump system that heats the airflow for the first time uses the first working fluid flowing out of the evaporator to heat the airflow for the first time.

[0008] Optionally, the first intermediate heat exchanger includes a first channel and a second channel, wherein an upper working fluid flows in the first channel and a lower working fluid is contained in the second channel;

[0009] Each of the heat pump systems includes a condenser and a compressor, the condenser being used to heat the airflow;

[0010] The condenser and compressor of the heat pump system that heat the airflow are referred to as the upper condenser and the upper compressor; the upper compressor is used to compress the upper working fluid, and the outlet of the upper compressor is connected to the upper condenser.

[0011] The condenser and compressor of the heat pump system that further heats the airflow are referred to as the lower-stage condenser and the lower-stage compressor; the lower-stage compressor is used to compress the lower-stage working fluid, the inlet of the lower-stage compressor is connected to the second channel corresponding to the first intermediate heat exchanger, and the outlet of the lower-stage compressor is connected to the lower-stage condenser.

[0012] The condenser and compressor of the heat pump system that first heats the airflow are referred to as the first condenser and the first compressor; the first compressor is used to compress the first working fluid; the inlet of the first compressor is connected to the evaporator, and the outlet of the first compressor is connected to the first condenser.

[0013] Optionally, the rotary dehumidification system further includes a second intermediate heat exchanger;

[0014] The second intermediate heat exchanger includes:

[0015] The outlet of the first channel through which the first working fluid flows is connected to the inlet of the return liquid pipe, and the outlet of the first condenser is connected to the inlet of the return liquid pipe. The outlet of the return liquid pipe is connected to the inlet of the evaporator through a first throttling pipe.

[0016] The liquid inlet pipe has its inlet connected to the outlet of the liquid return pipe via a second throttling pipe, and its outlet connected to the inlet of the first compressor. The first working fluid in the liquid inlet pipe, which absorbs heat during evaporation, exchanges heat with the first working fluid in the liquid return pipe, which releases heat during condensation.

[0017] The second intermediate heat exchanger is used to collect the first working fluid cooled by the first intermediate heat exchanger and the first working fluid cooled by the first condenser into the second intermediate heat exchanger for subcooling and cooling, and then enter the evaporator after throttling.

[0018] The heat pump system that initially heats the airflow also includes a control valve for controlling the total flow rate of the working fluid within the heat pump system.

[0019] Optionally, the rotary dehumidification system includes at least two rotary wheels, which are arranged sequentially along the airflow direction, and the high-temperature regeneration side is provided with at least two gradient condensation heat pump systems;

[0020] Each gradient condensing heat pump system is connected to the evaporator;

[0021] The evaporator is located between the dehumidification zones of the two rotors.

[0022] Optionally, a steam heating device is provided between the rotor and the gradient condensation heat pump system to reheat the airflow that has been heated by the gradient condensation heat pump system.

[0023] The present invention also provides a control method for a rotary dehumidification system as described in any one of the above claims, comprising:

[0024] Obtain the actual moisture content of the air outlet side of the dehumidification area of ​​the rotor;

[0025] The frequency of the compressors in each of the heat pump systems shall be controlled at least according to the actual moisture content.

[0026] Optionally, controlling the frequency of the compressors in each of the heat pump systems at least according to the actual moisture content includes:

[0027] When the actual moisture content is continuously higher than the first preset moisture content within a first preset time, the temperature of the air heated by each of the heat pump systems is obtained and recorded as the first actual temperature.

[0028] If each of the first actual temperatures is less than its respective first preset temperature, then the frequency of the compressor of each of the heat pump systems shall be increased at least.

[0029] Optionally, a steam heating device is provided between the rotor and the gradient condensation heat pump system;

[0030] If each of the first actual temperatures is less than its respective first preset temperature, then at least the frequency of the compressor of each of the heat pump systems is increased, and then the process further includes:

[0031] Once the frequency of the compressor is increased to the maximum frequency, the airflow temperature on the inlet side of the regeneration zone of the impeller is obtained and recorded as the inlet temperature.

[0032] If the inlet temperature remains lower than the target temperature for a second preset time period, the steam heating device will be turned on until the inlet temperature is greater than or equal to the target temperature, at which point the steam heating device will be turned off.

[0033] Optionally, controlling the frequency of the compressors in each of the heat pump systems at least according to the actual moisture content includes:

[0034] When the actual moisture content is continuously less than the second preset moisture content within a third preset time period, the frequency of the compressor of each heat pump system shall be reduced at least.

[0035] When the actual moisture content is less than or equal to the second preset moisture content and less than or equal to the first preset moisture content, the frequency of the compressor is reduced.

[0036] Wherein, the first preset moisture content is greater than the second preset moisture content.

[0037] Optionally, a steam heating device is provided between the rotor and the gradient condensation heat pump system;

[0038] Controlling the frequency of the compressors in each of the heat pump systems at least according to the actual moisture content includes:

[0039] If the actual moisture content remains lower than the second preset moisture content for a third preset time period, reduce the heating power of the steam heating device or turn off the steam heating device, and reduce the frequency of the compressor.

[0040] When the actual moisture content is less than or equal to the second preset moisture content and less than or equal to the first preset moisture content, the frequency of the compressor is stopped from decreasing, and the heating power of the steam heating device is maintained or increased, or the steam heating device is turned on.

[0041] Wherein, the first preset moisture content is greater than the second preset moisture content.

[0042] In the rotary dehumidification system of this invention, a gradient condensation heat pump system is installed on the air inlet side of the regeneration zone of each rotor, and each gradient condensation heat pump system includes multiple heat pump systems. A first intermediate heat exchanger is provided between adjacent heat pump systems. Under the action of the first intermediate heat exchanger, the lower-stage working fluid can absorb heat from the upper-stage working fluid, thereby increasing the heating temperature of the heat pump system that heats the airflow for the next time to a higher temperature than the heat pump system that heats the airflow for the previous time. In use, multiple heat pump systems heat the airflow multiple times, achieving gradient condensation heating and increasing the regeneration temperature of the regenerated air. Compared with existing technologies that only use electric heating or only use steam heating, this invention reduces energy consumption and achieves a higher regeneration temperature; compared with existing single-stage heat pump systems, this invention increases the regeneration temperature while having lower energy consumption; compared with existing multi-stage heat pump systems, it reduces energy consumption and achieves maximum energy saving. In summary, the present invention can simultaneously take into account regeneration temperature and system energy consumption, improve the overall energy efficiency and regeneration temperature of the rotary dehumidification system, and thus achieve the goal of maximizing energy saving while achieving a high regeneration temperature.

[0043] Furthermore, compared with existing technologies, under the same conditions, this invention also has the advantage of low operating costs. This invention can also achieve automatic control, remote monitoring, and unattended operation, and has the advantage of simple maintenance.

[0044] Therefore, those skilled in the art will more readily understand the above and other objects, advantages and features of the present invention from the following detailed description of specific embodiments of the invention in conjunction with the accompanying drawings. Attached Figure Description

[0045] The following sections will describe some specific embodiments of the invention in detail by way of example and not limitation, with reference to the accompanying drawings. The same reference numerals in the drawings denote the same or similar parts or portions. Those skilled in the art should understand that these drawings are not necessarily drawn to scale. In the drawings:

[0046] Figure 1 This is a schematic diagram of a rotary dehumidification system according to an embodiment of the present invention;

[0047] Figure 2 This is a schematic flowchart of a control method for a rotary dehumidification system according to an embodiment of the present invention;

[0048] Figure 3 This is a schematic flowchart of a control method for a rotary dehumidification system according to an embodiment of the present invention;

[0049] Figure 4 This is a schematic flowchart of a control method for a rotary dehumidification system according to an embodiment of the present invention;

[0050] Figure 5 This is a schematic flowchart of a control method for a rotary dehumidification system according to an embodiment of the present invention;

[0051] Figure 6 This is a schematic flowchart of a control method for a rotary dehumidification system according to an embodiment of the present invention;

[0052] Figure 7 This is a schematic flowchart of a control method for a rotary dehumidification system according to an embodiment of the present invention. Detailed Implementation

[0053] The following reference Figures 1 to 7 This invention describes a rotary dehumidification system and its control method according to embodiments of the present invention. The terms "front," "rear," "upper," "lower," "top," "bottom," "inner," "outer," and "lateral," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. These are used only for the convenience of describing the invention and for simplification, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on the invention.

[0054] The terms "first," "second," etc., are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined as "first," "second," etc., may explicitly or implicitly include at least one of that feature, that is, include one or more of that feature. In the description of this invention, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified. When a feature "includes or contains" one or more of the features it encompasses, unless otherwise specifically stated, this indicates that other features are not excluded and may be further included.

[0055] Unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," "fixing," and "coupling," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise expressly limited. Those skilled in the art should be able to understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0056] Figure 1 This is a schematic diagram of a rotary dehumidification system according to an embodiment of the present invention, which provides a rotary dehumidification system.

[0057] A rotary dehumidification system includes at least one rotary wheel 100, a low-temperature dehumidification side, and a high-temperature regeneration side.

[0058] Rotor 100 includes a regeneration zone and a dehumidification zone.

[0059] The low-temperature dehumidification side is equipped with a dehumidification area and an evaporator 200, in which a first working fluid flows.

[0060] The high-temperature regeneration side is equipped with a regeneration zone and at least one gradient condensation heat pump system. Each gradient condensation heat pump system corresponds to one rotor 100 and is used to perform gradient heating on the airflow before it enters the regeneration zone of each rotor 100.

[0061] The gradient condensation heat pump system includes multiple heat pump systems that sequentially heat the airflow. The working fluid of the heat pump system that heats the airflow for the first time is the upper working fluid, and the working fluid of the heat pump system that heats the airflow for the next time is the lower working fluid. The lower working fluid exchanges heat with the upper working fluid that releases heat during condensation through the first intermediate heat exchanger 400 when it absorbs heat during evaporation. The heat pump system that heats the airflow for the first time uses the first working fluid flowing out of the evaporator 200 to heat the airflow for the first time.

[0062] In this embodiment, the gradient condensation heat pump system may include two, three, four, or five heat pump systems. The number of heat pump systems in each gradient condensation heat pump system can be set as needed. A first intermediate heat exchanger 400 is provided between each pair of adjacent heat pump systems.

[0063] Specifically, the heat pump system that first heats the airflow is denoted as the upper-level heat pump system. The heat pump system that second heats the airflow is denoted as the lower-level heat pump system. The heat pump system that first heats the airflow is denoted as the first heat pump system 310. The terms "upper-level heat pump system" and "lower-level heat pump system" are relative, as are "upper-level working fluid" and "lower-level working fluid".

[0064] For example, when a gradient condensation heat pump system includes two heat pump systems, the two systems are a first heat pump system 310 and a second heat pump system 320. The first heat pump system 310 is the superior heat pump system of the second heat pump system 320, and the second heat pump system 320 is the inferior heat pump system of the first heat pump system 310. A first working fluid flows in the first heat pump system 310, and a second working fluid flows in the second heat pump system 320. The first working fluid is the superior working fluid of the second working fluid, and the second working fluid is the inferior working fluid of the first working fluid. A first intermediate heat exchanger 400 between the first heat pump system 310 and the second heat pump system 320 exchanges heat between the first and second working fluids, with the second working fluid absorbing heat from the first working fluid. The working process of the rotary dehumidification system is as follows: the first working fluid flows out from the outlet (high-temperature side) of the evaporator 200 and then enters the first heat pump system 310. The first heat pump system 310 uses the first working fluid to initially heat the airflow. The second heat pump system 320 uses a second working fluid to heat the airflow a second time. After passing through the regeneration zone of the rotor 100, the airflow forms regeneration airflow, i.e., regeneration wind.

[0065] For example, when a gradient condensation heat pump system includes three heat pump systems, these three systems are a first heat pump system 310, a second heat pump system 320, and a third heat pump system. The first heat pump system 310 is the superior heat pump system of the second heat pump system 320, the second heat pump system 320 is the inferior heat pump system of the first heat pump system 310, the second heat pump system 320 is the superior heat pump system of the third heat pump system, and the third heat pump system is the inferior heat pump system of the second heat pump system 320. A first working fluid flows within the first heat pump system 310, a second working fluid flows within the second heat pump system 320, and a third working fluid flows within the third heat pump system. The first working fluid is the superior working fluid of the second working fluid, the second working fluid is the inferior working fluid of the first working fluid, the second working fluid is the superior working fluid of the third working fluid, and the third working fluid is the superior working fluid of the first working fluid. A first intermediate heat exchanger 400 between the first heat pump system 310 and the second heat pump system 320 exchanges heat between the first working fluid and the second working fluid, with the second working fluid absorbing heat from the first working fluid. The first intermediate heat exchanger 400 between the second heat pump system 320 and the third heat pump system exchanges heat between the second working fluid and the third working fluid, with the third working fluid absorbing heat from the second working fluid. The working process of the rotary dehumidification system is as follows: the first working fluid flows out from the outlet (high-temperature side) of the evaporator 200 and then enters the first heat pump system 310. The first heat pump system 310 uses the first working fluid to heat the airflow for the first time. The second heat pump system 320 uses the second working fluid to heat the airflow for the second time. The third heat pump system uses the third working fluid to heat the airflow for the third time.

[0066] In this embodiment, each rotor 100 has a gradient condensation heat pump system installed on the air inlet side of its regeneration area. Each gradient condensation heat pump system includes multiple heat pump systems, and a first intermediate heat exchanger 400 is provided between adjacent heat pump systems. Under the action of the first intermediate heat exchanger 400, the lower-stage working fluid can absorb heat from the upper-stage working fluid, thereby making the heating temperature of the heat pump system that heats the airflow for the next time higher than the heating temperature of the heat pump system that heats the airflow for the previous time. In use, multiple heat pump systems heat the airflow multiple times, realizing gradient condensation heating and increasing the regeneration temperature of the regenerated air. Compared with the prior art of electric heating or steam heating only, this invention reduces energy consumption and has a higher regeneration temperature; compared with the prior art of a single-stage heat pump system, this invention increases the regeneration temperature while having lower energy consumption; compared with the prior art of multiple single-stage heat pump systems, it reduces energy consumption and achieves the goal of maximizing energy saving. In summary, the present invention can simultaneously take into account regeneration temperature and system energy consumption, improve the overall energy efficiency and regeneration temperature of the rotary dehumidification system, and thus achieve the goal of maximizing energy saving while achieving a high regeneration temperature.

[0067] Furthermore, compared with existing technologies, under the same conditions, this invention also has the advantage of low operating costs. This invention can also achieve automatic control, remote monitoring, and unattended operation, and has the advantage of simple maintenance.

[0068] In some embodiments of the present invention, the first intermediate heat exchanger 400 includes a first channel and a second channel, wherein an upper working fluid flows in the first channel and a lower working fluid is contained in the second channel.

[0069] Each heat pump system includes a condenser and a compressor. The condenser is used to heat the airflow. The condensers are arranged along the direction of airflow.

[0070] In this heat pump system, the condenser and compressor that heat the airflow are referred to as the upper-stage condenser and the upper-stage compressor. The upper-stage compressor is used to compress the upper-stage working fluid, and its outlet is connected to the upper-stage condenser.

[0071] The condenser and compressor of the heat pump system that heats the airflow again are referred to as the lower-stage condenser and the lower-stage compressor. The lower-stage compressor is used to compress the lower-stage working fluid. The inlet of the lower-stage compressor is connected to the second channel of the corresponding first intermediate heat exchanger 400, and the outlet of the lower-stage compressor is connected to the lower-stage condenser.

[0072] The heat pump system that first heats the airflow is referred to as the first heat pump system 310. The condenser and compressor of the first heat pump system 310 are referred to as the first condenser 311 and the first compressor 312. The first compressor 312 is used to compress the first working fluid. The inlet of the first compressor 312 is connected to the evaporator 200, and the outlet of the first compressor 312 is connected to the first condenser 311.

[0073] Specifically, when the gradient condensation heat pump system includes two heat pump systems, the two heat pump systems are the first heat pump system 310 and the second heat pump system 320. The condenser and compressor of the second heat pump system 320 are denoted as the second condenser 321 and the second compressor 322. A second working fluid flows within the second heat pump system 320. The inlet of the first channel of the first heat exchanger is connected to the outlet of the first compressor 312. In operation, the gaseous first working fluid flows out from the outlet of the evaporator 200 and then flows into the first compressor 312 for compression. A portion of the first working fluid then enters the first condenser 311 for condensation. The gaseous airflow requiring regeneration absorbs heat as it passes through the condenser, achieving the first temperature increase. Another portion of the first working fluid flowing out of the outlet of the first compressor 312 enters the first channel of the first intermediate heat exchanger 400. Under the action of the first intermediate heat exchanger 400, the second working fluid in the second channel absorbs the heat from the first working fluid in the first channel. The second working fluid after absorbing heat flows into the second compressor 322 for compression. Then the second working fluid enters the second condenser 321 for condensation. When the gas flow that needs to be regenerated passes through the second condenser 321, it will absorb heat and achieve a second temperature rise.

[0074] When the gradient condensation heat pump system includes three heat pump systems, these three systems are designated as a first heat pump system 310, a second heat pump system 320, and a third heat pump system. A first intermediate heat exchanger 400 between the first heat pump system 310 and the second heat pump system 320 is denoted as first intermediate heat exchanger A, and a first intermediate heat exchanger 400 between the second heat pump system 320 and the third heat pump system is denoted as first intermediate heat exchanger B. A third working fluid flows within the third heat pump system. The operating principles of the first heat pump system 310 and the second heat pump system 320 are the same as those in the above embodiments and will not be repeated here. The following focuses on the coordination relationship between the second heat pump system 320 and the third heat pump system. In use, the second working fluid flowing out of the outlet of the second compressor 322 flows partly into the second condenser 321 and partly into the first channel of the first intermediate heat exchanger B. Under the action of the first intermediate heat exchanger B, the third working fluid in the second channel of the first intermediate heat exchanger B absorbs heat from the second working fluid in the first channel. The heat-absorbing third working fluid flows into the second compressor 322 for compression. Then the second working fluid enters the third condenser for condensation. The gas flow that needs to be regenerated will absorb heat when it passes through the third condenser, achieving a third temperature rise.

[0075] In this embodiment, the gradient condensation heat pump system can achieve multiple cascade compression and gradient condensation, which is more conducive to increasing the regeneration temperature and maximizing energy saving.

[0076] In some embodiments of the invention, the heat pump system for further heating the airflow also includes a throttling device located between the outlet of the lower-stage condenser and the inlet of the second channel. For example, the throttling device of the second heat pump system 320 is located between the outlet of the second condenser 321 and the inlet of the second channel.

[0077] In some embodiments of the present invention, the rotary dehumidification system further includes a second intermediate heat exchanger 500.

[0078] The second intermediate heat exchanger includes a return pipe and an inlet pipe.

[0079] The outlet of the first channel through which the first working fluid flows is connected to the inlet of the return liquid pipe, and the outlet of the first condenser 311 is connected to the inlet of the return liquid pipe. The outlet of the return liquid pipe is connected to the inlet of the evaporator 200 through the first throttling pipe.

[0080] The inlet of the liquid inlet pipe is connected to the outlet of the liquid return pipe through the second throttling pipe, and the outlet of the liquid inlet pipe is connected to the inlet of the first compressor 312; the first working fluid in the liquid inlet pipe, which absorbs heat during evaporation, and the first working fluid in the liquid return pipe, which releases heat during condensation, exchange heat.

[0081] The second intermediate heat exchanger 500 is used to collect the first working fluid cooled by the corresponding first intermediate heat exchanger 400 and the first working fluid cooled by the first condenser 311 into the second intermediate heat exchanger 500 for subcooling, and then enter the evaporator 200 after throttling.

[0082] After absorbing heat, the first working fluid in the inlet pipe flows out from the outlet of the inlet pipe and then into the first compressor 312. This arrangement is more conducive to increasing the heating temperature of the first heat pump system 310 and also to saving energy.

[0083] Specifically, a throttling device is installed on the first throttling pipeline. A throttling device is also installed on the second throttling pipeline.

[0084] In this embodiment, by setting up a second intermediate heat exchanger 500, the first working fluid can be subcooled. After being subcooled, the first working fluid returns to the evaporator 200 and can better absorb heat from the air on the low-temperature dehumidification side.

[0085] In some embodiments of the present invention, the rotary dehumidification system includes a rotary wheel 100 and a gradient condensation heat pump system.

[0086] In some embodiments of the present invention, the rotary dehumidification system includes at least two rotors 100 (e.g., two rotors 100, three rotors 100, or four rotors 100), the at least two rotors 100 being arranged sequentially along the airflow direction, and at least two gradient condensation heat pump systems being provided on the high-temperature regeneration side. The evaporator 200 is located between the dehumidification zones of the two rotors 100.

[0087] Specifically, the evaporator 200 can be positioned between any two rotors 100.

[0088] In this embodiment, by setting at least two rotors 100, the dehumidification performance of the rotor dehumidification system can be improved.

[0089] In some embodiments of the present invention, the rotary dehumidification system includes at least two rotors 100 (e.g., two, three, or four rotors 100), arranged sequentially along the airflow direction, and at least two gradient condensing heat pump systems are provided on the high-temperature regeneration side. An evaporator 200 is located between the dehumidification zones of the two rotors 100. Each gradient condensing heat pump system is connected to an evaporator 200. Specifically, the first heat pump system 310 of each gradient condensing heat pump system is connected to the same evaporator 200. In some alternative embodiments, at least two parallel evaporators 200 are provided between the dehumidification zones of the two rotors 100, with each evaporator 200 corresponding to a gradient condensing heat pump system. The first heat pump system 310 of each gradient condensing heat pump system is connected to a different evaporator 200.

[0090] In this embodiment, the first heat pump system 310 of multiple gradient condensing heat pump systems shares a single evaporator 200, which not only reduces production costs but also further reduces energy consumption. Therefore, this embodiment is beneficial for maximizing energy savings.

[0091] In some embodiments of the present invention, a steam heating device 700 is provided between the rotor 100 and the gradient condensation heat pump system for reheating the airflow heated by the gradient condensation heat pump system.

[0092] In this embodiment, the steam heating device 700 is provided to further increase the regeneration temperature.

[0093] In some embodiments of the present invention, the first heat pump system 310 includes a plurality of first compressors 312, which are connected in parallel. For example, the first heat pump system 310 includes two first compressors 312 connected in parallel; or, the first heat pump system 310 includes three first compressors 312 connected in parallel.

[0094] In this embodiment, by setting up multiple first compressors 312 connected in parallel, it is beneficial to improve the heating temperature and heating efficiency of the first heat pump system 310.

[0095] In some alternative embodiments, the first heat pump system 310 may also include only a first compressor 312.

[0096] In some embodiments of the present invention, such as Figure 1 As shown, the rotary dehumidification system includes two rotors 100, a low-temperature dehumidification side, and a high-temperature regeneration side. The high-temperature regeneration side is equipped with two gradient condensation heat pump systems. Each gradient condensation heat pump system comprises two heat pump systems: a first heat pump system 310 and a second heat pump system 320. A first working fluid flows through the first heat pump system 310, and a second working fluid flows through the second heat pump system 320. The first heat pump system 310 is used for initial heating of the airflow, and the second heat pump system 320 is used for secondary heating of the airflow. A first intermediate heat exchanger 400 is provided between the first heat pump system 310 and the second heat pump system 320. A second intermediate heat exchanger 500 is provided between the first intermediate heat exchanger 400 and the evaporator 200. The evaporator 200 is located between the dehumidification zones of the two rotors 100.

[0097] The low-temperature dehumidification side is equipped with three surface coolers 600, namely the first surface cooler, the second surface cooler, and the third surface cooler. Specifically, the two rotors 100 are the first-stage rotor and the second-stage rotor, respectively. Along the airflow direction, the low-temperature dehumidification side is arranged with the first surface cooler, the dehumidification area of ​​the first-stage rotor, the evaporator 200, the second surface cooler, the dehumidification area of ​​the second-stage rotor, and the third surface cooler in sequence.

[0098] The first heat pump system 310 also includes two control valves 313, which are used to control the total flow rate of the working fluid within the heat pump system. Specifically, the two control valves 313 are a first control valve and a second control valve, respectively. A first control valve is provided between the inlet of the first condenser 311 and the outlet of the first compressor 312; a second control valve is provided between the inlet of the first channel of the first intermediate heat exchanger 400 and the outlet of the first compressor 312.

[0099] Outdoor fresh air is pre-treated by the first surface cooler 600. After the first cooling and dehumidification, it enters the first-stage dehumidifier 100 for the first deep dehumidification. The dehumidified and heated low-humidity dry airflow enters the evaporator 200 for the second cooling. The cooled dry airflow is split into two streams and enters different zones of the second-stage dehumidifier 100. One part of the airflow enters the dehumidification pre-regeneration zone of the second-stage dehumidifier 100 for pre-regeneration. The other part of the airflow enters the dehumidification zone of the second-stage dehumidifier 100 for the second deep dehumidification. The ultra-low humidity dry airflow after deep dehumidification and heating enters the third surface cooler 600 for the third cooling and is finally sent into the drying room.

[0100] The airflow that needs to be regenerated is heated by the gradient condensation heat pump system corresponding to the first-stage rotor 100 to become a high-temperature airflow. It then enters the regeneration area of ​​the first-stage rotor 100 and heats and regenerates the regeneration area of ​​the first-stage rotor 100. After regeneration, the exhaust air (regeneration air) is discharged from the regeneration port.

[0101] The airflow that needs to be regenerated is heated by the gradient condensation heat pump system corresponding to the second-stage rotor 100 to become a high-temperature airflow, which enters the regeneration area of ​​the second-stage rotor 100 and heats and regenerates the regeneration area of ​​the second-stage rotor 100. After regeneration, the exhaust air is discharged from the regeneration port.

[0102] The gas flow temperature after heating by the first condenser 311 is 65℃, the gas flow temperature after heating by the second condenser 321 is 130℃, and the gas flow temperature after heating by the steam heating device 700 is 130℃.

[0103] like Figure 2-7 As shown, the present invention also provides a control method for the rotary dehumidification system described in any of the above embodiments.

[0104] The control method includes the following steps:

[0105] Step S100: Obtain the actual moisture content of the air outlet side of the dehumidification zone of the rotor 100.

[0106] Step S200: Control the frequency of the compressors in each heat pump system at least according to the actual moisture content.

[0107] Specifically, step S100 allows us to obtain the actual dehumidification effect of the rotor 100. Step S200 allows us to control the frequency of the compressors in each heat pump system based on the actual dehumidification effect of the rotor 100, which helps to achieve better dehumidification and maximize energy savings in the system.

[0108] Based on the actual moisture content of the air outlet side of the dehumidification zone of each rotor 100, the heat pump systems of the corresponding gradient condensation heat pump system are controlled to adjust the dehumidification capacity of the dehumidification zone of each rotor 100.

[0109] In this embodiment, the frequency of the compressors in each heat pump system is controlled by the actual moisture content of the air outlet side of the dehumidification zone of the rotor 100, which helps to balance the dehumidification effect, regeneration temperature, and system energy consumption. In other words, the present invention can better improve the overall energy efficiency of the system while ensuring the dehumidification and regeneration effects.

[0110] like Figure 3 As shown, in some optional embodiments of the present invention, step S200, controlling the frequency of the compressors of each heat pump system at least according to the actual moisture content, includes the following steps:

[0111] Step S201: When the actual humidity content is continuously higher than the first preset humidity content within a first preset time period, the temperature of the air heated by each heat pump system is obtained and recorded as the first actual temperature.

[0112] Step S202: If each first actual temperature is less than its respective first preset temperature, then increase the frequency of the compressor of each heat pump system.

[0113] Furthermore, the first preset moisture content = target moisture content + deviation moisture content, where the deviation moisture content is greater than 0. The first preset temperature = set temperature value - deviation temperature value, where the deviation temperature value is greater than 0.

[0114] During operation of the rotary dehumidification system, if the actual moisture content remains higher than the first preset moisture content within a first preset time period, it indicates that the dehumidification capacity of the rotary wheel 100 has not met the set requirements. If the first temperature corresponding to each heat pump system is simultaneously lower than or below the first preset temperature, it indicates that the heating effect of each heat pump system on the airflow is poor. In this case, increasing the compressor frequency is beneficial to increasing the regeneration temperature and also to improving the dehumidification effect.

[0115] Furthermore, in some embodiments of the present invention, the first heat pump system 310 further includes a control valve 313 for controlling the total flow rate of the working fluid within the heat pump system.

[0116] Specifically, control valve 313 includes a first control valve and a second control valve. A first control valve is provided between the inlet of the first condenser 311 and the outlet of the first compressor 312; a second control valve 313 is provided between the inlet of the first channel of the first intermediate heat exchanger 400 and the outlet of the first compressor 312.

[0117] like Figure 4 As shown, step S200, controlling the compressor frequency of each heat pump system based at least on the actual moisture content, includes the following steps:

[0118] Step S201: When the actual humidity content is continuously higher than the first preset humidity content within a first preset time period, the temperature of the air heated by each heat pump system is obtained and recorded as the first actual temperature.

[0119] In step S203, if each first actual temperature is less than its respective first preset temperature, the frequency of the compressor of each heat pump system is increased, and the opening degree of the control valve 313 is increased.

[0120] Specifically, "increasing the opening degree of control valve 313" refers to increasing the opening degree of the first control valve and the second control valve to increase the total flow rate of the working fluid in the first heat pump system 310, thereby improving the heating effect of the first condenser 311 on the airflow that needs to be regenerated, and at the same time improving the cooling effect of the evaporator 200 on the low-temperature dehumidification side air, thereby improving the dehumidification effect of the air.

[0121] In this embodiment, when the dehumidification capacity of the rotor 100 does not meet the set requirements and the heating effect of each heat pump system on the airflow is not good, increasing the frequency of the compressor and the opening of the control valve 313 at the same time is more conducive to increasing the regeneration temperature and also more conducive to improving the dehumidification effect.

[0122] In some embodiments of the present invention, a steam heating device 700 is provided between the rotor 100 and the gradient condensation heat pump system.

[0123] like Figure 3 and Figure 4 As shown, if each first actual temperature is lower than its respective first preset temperature, then the compressor frequency is increased at least, followed by the following steps:

[0124] Step S204: After the compressor frequency is increased to the maximum frequency, the airflow temperature on the inlet side of the regeneration area of ​​the rotor 100 is obtained and recorded as the inlet temperature.

[0125] Step S205: If the inlet temperature remains lower than the target temperature for a second preset time, turn on the steam heating device 700 until the inlet temperature is greater than or equal to the target temperature, then turn off the steam heating device 700.

[0126] Specifically, the second preset time can be set as needed. For example, the second preset time can be 3 minutes, 4 minutes, or 5 minutes, etc.

[0127] In this embodiment, the steam heating device 700 is used to increase the regeneration temperature, which in turn improves heating efficiency. Furthermore, when controlling each heat pump system alone is insufficient to increase the regeneration temperature, adjusting the steam heating device 700 further enhances the heating effect, reducing energy consumption and maximizing energy savings.

[0128] In some embodiments of the present invention, controlling the frequency of the compressors of each heat pump system based at least on the actual moisture content includes the following steps:

[0129] Step S201: When the actual humidity content is continuously higher than the first preset humidity content within a first preset time period, the temperature of the air heated by each heat pump system is obtained and recorded as the first actual temperature.

[0130] Step S206: If each first actual temperature is less than its respective first preset temperature, while meeting the system pressure and temperature safety range, increase the operating frequency of each heat pump system compressor by 10% per sampling cycle (the frequency increase value can be set as needed), and at the same time increase the opening of the corresponding valve until each compressor runs at full frequency.

[0131] In the above embodiments, the first preset time can be set as needed. For example, the first preset time can be 3 minutes, 4 minutes, or 5 minutes, etc.

[0132] like Figure 5 As shown, in some embodiments of the present invention, controlling the frequency of the compressors of each heat pump system based at least on the actual moisture content includes the following steps:

[0133] Step S211: When the actual moisture content is continuously less than the second preset moisture content within the third preset time period, reduce the frequency of the compressors of each heat pump system.

[0134] Step S212: When the actual moisture content is less than or equal to the second preset moisture content and less than or equal to the first preset moisture content, stop reducing the compressor frequency; wherein, the first preset moisture content is greater than the second preset moisture content.

[0135] Specifically, the third preset time can be set as needed, for example, it can be 3 minutes, 4 minutes, or 5 minutes, etc. The first preset moisture content = target moisture content + deviation moisture content; the second preset moisture content = target moisture content - deviation moisture content, where the deviation moisture content is greater than 0.

[0136] If the actual moisture content remains lower than the second preset moisture content within the third preset time period, it indicates that the dehumidification capacity of the rotor 100 is excessive. In this case, the compressor frequency should be reduced at least. On the one hand, this not only reduces the heating capacity of each condenser on the airflow requiring regeneration, but also reduces the cooling effect of the evaporator 200 on the low-temperature dehumidification side air, thereby reducing the dehumidification capacity. On the other hand, it is more conducive to maximizing energy saving.

[0137] In some embodiments of the present invention, the first heat pump system 310 further includes a control valve 313 for controlling the total flow rate of the working fluid within the heat pump system. Specifically, the control valve 313 includes a first control valve 313 and a second control valve 313. A first control valve 313 is disposed between the inlet of the first condenser 311 and the outlet of the first compressor 312; a second control valve 313 is disposed between the inlet of the first channel of the first intermediate heat exchanger 400 and the outlet of the first compressor 312.

[0138] like Figure 6 As shown, the frequency of the compressor in each heat pump system should be controlled at least according to the actual moisture content, including the following steps:

[0139] In step S213, when the actual moisture content is continuously less than the second preset moisture content within the third preset time period, the frequency of the compressors of each heat pump system is reduced and the opening degree of the control valve 313 is reduced.

[0140] Step S214: When the actual moisture content is less than or equal to the second preset moisture content and less than or equal to the first preset moisture content, stop reducing the frequency of the compressor; wherein, the first preset moisture content is greater than the second preset moisture content.

[0141] Specifically, "reducing the opening degree of control valve 313" refers to reducing the opening degree of the first control valve 313 and the second control valve 313 to reduce the total flow rate of the working fluid in the first heat pump system 310, thereby reducing the heating effect of the first condenser 311 on the airflow that needs to be regenerated, and at the same time reducing the cooling effect of the evaporator 200 on the low-temperature dehumidification side air, thereby reducing the dehumidification effect of the air.

[0142] In this embodiment, when the dehumidification capacity of the rotor 100 is excessive, reducing the frequency of the compressor and the opening of the control valve 313 simultaneously can meet the dehumidification needs while maximizing energy saving.

[0143] In some embodiments of the present invention, a steam heating device 700 is provided between the rotor 100 and the gradient condensation heat pump system.

[0144] like Figure 7 As shown, the frequency of the compressor in each heat pump system should be controlled at least according to the actual moisture content, including the following steps:

[0145] In step S215, when the actual moisture content is continuously less than the second preset moisture content within the third preset time period, the heating power of the steam heating device 700 is reduced or the steam heating device 700 is turned off, and the frequency of the compressor is reduced.

[0146] Step S216: When the actual moisture content is less than or equal to the second preset moisture content and less than or equal to the first preset moisture content, stop reducing the frequency of the compressor and maintain or increase the heating power of the steam heating device 700 or turn on the steam heating device 700.

[0147] The first preset moisture content is greater than the second preset moisture content.

[0148] Furthermore, in step S215, while reducing the frequency of the compressor, the opening degree of the control valve 313 is reduced.

[0149] In this embodiment, when the dehumidification capacity of the rotor 100 is excessive, it is more conducive to reducing energy consumption, thereby maximizing energy saving. Preferably, the heating power of the steam heating device 700 is reduced or the steam heating device 700 is turned off.

[0150] In some embodiments of the present invention, the frequency of the compressor of each heat pump system is controlled at least according to the actual moisture content, including the following steps: Step S220, when the actual moisture content is less than or equal to the second preset moisture content and less than or equal to the first preset moisture content within a fourth preset time period, the existing frequency of the compressor of each heat pump system is maintained.

[0151] If the actual moisture content is less than or equal to the second preset moisture content and less than or equal to the first preset moisture content within the fourth preset time period, it indicates that the dehumidification capacity of the impeller 100 meets the requirements. The fourth preset time can be set as needed; for example, it can be 3 minutes, 4 minutes, or 5 minutes, etc.

[0152] In some embodiments of the present invention, the rotary dehumidification system further includes a plurality of surface coolers 600, which are disposed on the low-temperature dehumidification side and arranged sequentially along the air flow direction.

[0153] The control method also includes the following steps:

[0154] Step S300: Obtain the temperature at the outlet side of each surface cooler 600 and record it as the actual outlet temperature.

[0155] In step S400, the water valves of each surface cooler 600 are controlled according to the actual outlet temperature.

[0156] Specifically, the actual outlet temperature of each surface cooler 600 is compared with the corresponding set outlet temperature, and the water valve of each surface cooler 600 is controlled according to the comparison result.

[0157] In this embodiment, the above-described settings facilitate quick adjustment of the dehumidification capacity of the rotor 100.

[0158] In some embodiments of the present invention, step S400, controlling the water valves of each surface cooler 600 according to the actual outlet temperature, includes:

[0159] Step S401: If the actual outlet temperature is greater than the corresponding first set outlet temperature within the fifth preset time period, then increase the opening of the water valve of each surface cooler 600. For example, increase the water valve by 10% in each sampling cycle until the water valve is fully open. First set outlet temperature = target outlet temperature + T.

[0160] In step S402, if the actual outlet temperature is lower than the corresponding second set outlet temperature within the fifth preset time period, then reduce the opening of the water valve of each surface cooler 600. For example, reduce the water valve opening by 10% in each sampling cycle until the actual outlet temperature meets the target outlet temperature ±T deviation for 3 minutes. Second set outlet temperature = target outlet temperature - T.

[0161] In step S403, if the actual outlet temperature of each device is greater than or equal to the corresponding second set outlet temperature and less than or equal to the corresponding first set outlet temperature within the fifth preset time, then the water valve opening of each surface cooler 600 is maintained.

[0162] Specifically, the fifth preset time is 3 minutes, but it can also be 4 minutes or 5 minutes. In other words, the fifth preset time can be set as needed.

[0163] This embodiment provides a scientific method for controlling the water valve of the surface cooler 600.

[0164] While this invention provides several exemplary embodiments, many other variations or modifications consistent with the principles of this invention can be directly determined or derived from the disclosure of this invention without departing from its spirit and scope. Therefore, the scope of this invention should be understood and recognized as covering all such other variations or modifications.

Claims

1. A rotary dehumidification system, characterized in that, include: At least one impeller, the impeller including a regeneration zone and a dehumidification zone; On the low-temperature dehumidification side, the low-temperature dehumidification side is provided with the dehumidification area and the evaporator, and the first working fluid flows in the evaporator; On the high-temperature regeneration side, at least one gradient condensation heat pump system is provided. Each gradient condensation heat pump system corresponds to one of the rotating impellers and is used to gradient-heat the airflow before it enters the regeneration zone of each impeller. The gradient condensation heat pump system includes multiple heat pump systems that sequentially heat the airflow. The working fluid of the heat pump system that initially heats the airflow is the upper-stage working fluid, and the working fluid of the heat pump system that subsequently heats the airflow is the lower-stage working fluid. The lower-stage working fluid exchanges heat with the upper-stage working fluid, which releases heat during evaporation, through a first intermediate heat exchanger. The heat pump system that initially heats the airflow utilizes the first working fluid flowing out of the evaporator to initially heat the airflow. The first intermediate heat exchanger includes a first channel and a second channel, wherein an upper working fluid flows in the first channel and a lower working fluid is contained in the second channel; Each of the heat pump systems includes a condenser and a compressor, the condenser being used to heat the airflow; The condenser and compressor of the heat pump system that heat the airflow are referred to as the upper condenser and the upper compressor; the upper compressor is used to compress the upper working fluid, and the outlet of the upper compressor is connected to the upper condenser. The condenser and compressor of the heat pump system that further heats the airflow are referred to as the lower-stage condenser and the lower-stage compressor; the lower-stage compressor is used to compress the lower-stage working fluid, the inlet of the lower-stage compressor is connected to the second channel corresponding to the first intermediate heat exchanger, and the outlet of the lower-stage compressor is connected to the lower-stage condenser. The condenser and compressor of the heat pump system that first heats the airflow are referred to as the first condenser and the first compressor; the first compressor is used to compress the first working fluid; the inlet of the first compressor is connected to the evaporator, and the outlet of the first compressor is connected to the first condenser. The rotary dehumidification system also includes a second intermediate heat exchanger; The second intermediate heat exchanger includes: The outlet of the first channel through which the first working fluid flows is connected to the inlet of the return liquid pipe, and the outlet of the first condenser is connected to the inlet of the return liquid pipe. The outlet of the return liquid pipe is connected to the inlet of the evaporator through a first throttling pipe. The liquid inlet pipe has its inlet connected to the outlet of the liquid return pipe via a second throttling pipe, and its outlet connected to the inlet of the first compressor. The first working fluid in the liquid inlet pipe, which absorbs heat during evaporation, exchanges heat with the first working fluid in the liquid return pipe, which releases heat during condensation. The heat pump system that initially heats the airflow also includes a control valve for controlling the total flow rate of the working fluid within the heat pump system.

2. The rotary dehumidification system according to claim 1, characterized in that, The rotary dehumidification system includes at least two rotary wheels, which are arranged sequentially along the airflow direction. The high-temperature regeneration side is equipped with at least two gradient condensation heat pump systems. Each gradient condensing heat pump system is connected to the evaporator; The evaporator is located between the dehumidification zones of the two rotors.

3. The rotary dehumidification system according to claim 1, characterized in that, A steam heating device is provided between the rotor and the gradient condensation heat pump system to reheat the airflow that has been heated by the gradient condensation heat pump system.

4. A control method for a rotary dehumidification system as described in any one of claims 1-3, characterized in that, include: Obtain the actual moisture content of the air outlet side of the dehumidification area of ​​the rotor; The frequency of the compressors in each of the heat pump systems shall be controlled at least according to the actual moisture content.

5. The control method for the rotary dehumidification system according to claim 4, characterized in that, Controlling the frequency of the compressors in each of the heat pump systems at least according to the actual moisture content includes: When the actual moisture content is continuously higher than the first preset moisture content within a first preset time, the temperature of the air heated by each of the heat pump systems is obtained and recorded as the first actual temperature. If each of the first actual temperatures is less than its respective first preset temperature, then the frequency of the compressor of each of the heat pump systems shall be increased at least.

6. The control method for the rotary dehumidification system according to claim 5, characterized in that, A steam heating device is provided between the rotor and the gradient condensation heat pump system; If each of the first actual temperatures is less than its respective first preset temperature, then at least the frequency of the compressor of each of the heat pump systems is increased, and then the process further includes: Once the frequency of the compressor is increased to the maximum frequency, the airflow temperature on the inlet side of the regeneration zone of the impeller is obtained and recorded as the inlet temperature. If the inlet temperature remains lower than the target temperature for a second preset time period, the steam heating device will be turned on until the inlet temperature is greater than or equal to the target temperature, at which point the steam heating device will be turned off.

7. The control method for the rotary dehumidification system according to claim 4, characterized in that, Controlling the frequency of the compressors in each of the heat pump systems at least according to the actual moisture content includes: When the actual moisture content is continuously less than the second preset moisture content within a third preset time period, the frequency of the compressor of each heat pump system shall be reduced at least. When the actual moisture content is less than or equal to the second preset moisture content and less than or equal to the first preset moisture content, the frequency of the compressor is reduced. Wherein, the first preset moisture content is greater than the second preset moisture content.

8. The control method for the rotary dehumidification system according to claim 4, characterized in that, A steam heating device is provided between the rotor and the gradient condensation heat pump system; Controlling the frequency of the compressors in each of the heat pump systems at least according to the actual moisture content includes: If the actual moisture content remains lower than the second preset moisture content for a third preset time period, reduce the heating power of the steam heating device or turn off the steam heating device, and reduce the frequency of the compressor. When the actual moisture content is less than or equal to the second preset moisture content and less than or equal to the first preset moisture content, the frequency of the compressor is stopped from decreasing, and the heating power of the steam heating device is maintained or increased, or the steam heating device is turned on. Wherein, the first preset moisture content is greater than the second preset moisture content.

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