Heat modulation dehumidification system
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Solution Overview
Problem
Current dehumidifiers are inefficient in various respects, particularly in applications requiring rapid humidity reduction in fire and flood restoration, and they do not effectively maintain desired humidity levels in structures.
Innovation Solution
A dehumidification system with a secondary evaporator and condenser, which causes refrigerant to evaporate and condense twice in a single refrigeration cycle, utilizing two evaporators, two condensers, and a modulating valve to dynamically manage refrigerant flow, enhancing efficiency and capacity without additional power.
Engineering Contradictions & Design Principles
Engineering Contradiction Analysis
1Productivity
If a conventional single evaporator and condenser system is used, then the device complexity is low, but the dehumidification capacity and efficiency are insufficient
Solution Approach 1:
The system divides the refrigeration cycle into two separate loops: a primary loop with a first evaporator and first condenser, and a secondary loop with a second evaporator and second condenser. This segmentation allows each evaporator to independently process airflow, effectively doubling the dehumidification capacity while maintaining manageable system complexity through modular architecture
Solution Approach 2:
The refrigerant circulation system serves multiple functions simultaneously: it provides cooling through both evaporators for enhanced dehumidification, enables heat recovery through the heat exchanger coupling the two loops, and maintains flexible operational modes (full dehumidification, partial dehumidification, or cooling-only modes) through the controllable flow communication between loops
2Productivity
If refrigerant flow is increased to boost dehumidification capacity, then the dehumidification efficiency improves, but the energy consumption increases
Solution Approach 1:
The system dynamically adjusts refrigerant flow parameters between the primary and secondary loops based on operational demands. The controllable flow communication allows the system to optimize the distribution of refrigerant flow, enabling high dehumidification capacity when needed while reducing energy consumption during lower-demand periods by operating in partial dehumidification or cooling-only modes
Solution Approach 2:
The system transitions from a static single-loop configuration to a dynamic dual-loop system where refrigerant flow can be continuously adjusted between loops. This dynamic flexibility allows the system to match dehumidification capacity with actual demand, avoiding unnecessary energy consumption while maintaining the capability for high-performance operation when required
3Measurement precision
If the dehumidified airflow temperature is reduced to maintain desired humidity levels, then the humidity control precision improves, but the compressor workload increases
Solution Approach 1:
By segmenting the cooling process into two separate evaporators operating in parallel, each evaporator handles a portion of the total airflow required for dehumidification. This division allows the system to achieve the desired low airflow temperature and precise humidity control without overloading a single compressor, as the cumulative cooling effect is distributed across two evaporative processes
Solution Approach 2:
The heat exchanger coupling the primary and secondary loops acts as an intermediary that facilitates heat transfer between the two refrigeration circuits. This intermediary mechanism enables the system to optimize temperature control in the dehumidified airflow by allowing thermal interaction between loops, thereby achieving precise humidity control while managing compressor workload through coordinated heat exchange
Applied Scientific Principles
This section explains which scientific principles are used to turn an abstract innovation direction into a practical engineering solution.
Function Achieved in This Case
This configuration increases compressor capacity and overall efficiency, allowing for greater dehumidification per kilowatt of power used, effectively reducing humidity and maintaining desired airflow temperatures.
Implementation Method 1
the first airflow generated by transferring heat from the inlet airflow to the flow of refrigerant as the inlet airflow passes through the secondary evaporator
Implementation Method 2
the second airflow generated by transferring heat from the first airflow to the flow of refrigerant as the first airflow passes through the primary evaporator
Implementation Method 3
the third airflow generated by transferring heat from the flow of refrigerant to the third airflow as the second airflow passes through the secondary condenser
Implementation Method 4
the dehumidified airflow generated by transferring heat from the refrigerant to the fourth airflow as the fourth airflow contacts the primary condenser
Data Source
Figure 1
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AI summary
A dehumidification system (10; 200; 300; 600; 800; 1500; 1600) includes a compressor (10; 200; 300; 600; 800; 1500; 1600), a primary evaporator (310; 610; 910; 1010; 1508; 1604), a primary condenser (330; 630; 1510; 1606), a secondary evaporator (340; 640; 1040; 1140; 1512; 1608), a secondary condenser (320; 620; 1020; 1120; 1514; 1610), a modulating valve (1602), and an alternate condenser (1620). The secondary evaporator (340; 640; 1040; 1140; 1512; 1608) receives an inlet airflow (101; 601; 901; 1526; 1628) and outputs a first airflow (345; 645; 1532; 1634) to the primary evaporator. The primary evaporator receives the first airflow (345; 645; 1532; 1634) and outputs a second airflow (315; 615; 1530; 1632) to the secondary condenser (320; 620; 1020; 1120; 1514; 1610). The secondary condenser (320; 620; 1020; 1120; 1514; 1610) receives the second airflow (315; 615; 1530; 1632) and outputs a third airflow to the primary condenser (330; 630; 1510; 1606). The primary condenser (330; 630; 1510; 1606) receives the third airflow and outputs a dehumidified airflow. The compressor (10; 200; 300; 600; 800; 1500; 1600) receives a flow of refrigerant (1626) from the primary evaporator (310; 610; 910; 1010; 1508; 1604) and provides the flow of refrigerant (1626) to the modulating valve (1602). The modulating valve (1602) directs the flow of refrigerant (1626) to the primary condenser (330; 630; 1510; 1606) and to the alternate condenser (1620). The alternate condenser (1620) receives a portion of the flow of refrigerant (1626) for heat rejection, where the primary condenser (330; 630; 1510; 1606) receives the remaining portion of the flow of refrigerant (1626).