JP2017020715A - Waste heat utilizing type dehumidifying system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a waste heat utilizing type dehumidifying system which can reuse exhaust air lowered in temperature and humidity by a second heat exchange mechanism, and can save energy.SOLUTION: When a measurement temperature of exhaust air measured by a first temperature sensor 33 is equal to or lower than a set temperature, a waste heat utilizing type dehumidifying system 10A performs first circulation operation for maintaining a flow rate of exhaust air exhausted from a regeneration side downstream duct 26 at a prescribed flow rate and increasing a flow rate of exhaust air flowing through an exhaust air circulation duct 29, or second circulation operation for maximizing the flow rate of the exhaust air flowing through the exhaust air circulation duct 29 while cutting off exhausting of the exhaust air from the regeneration side downstream duct 26. When the measurement temperature of the exhaust air measured by the first temperature sensor 33 exceeds the set temperature, the waste heat utilizing type dehumidifying system 10A performs third circulation operation for maintaining the flow rate of the exhaust air exhausted from the regeneration side downstream duct 26 at the prescribed flow rate and decreasing the flow rate of the exhaust air flowing through the exhaust air circulation duct 29.SELECTED DRAWING: Figure 1

Description

  The present invention relates to an exhaust heat utilization type dehumidification system that supplies dehumidified air using a dehumidifying mechanism to a dehumidified air-conditioned space while supplying heated air to the dehumidifying mechanism to regenerate the dehumidifying function of the dehumidifying agent.

  Dehumidification processing zone for generating dehumidified air, dehumidification function regeneration zone for regenerating the dehumidification function, dehumidification mechanism having a dehumidifier and disposed in the dehumidification processing zone and dehumidification function regeneration zone, and dehumidification function upstream of the dehumidification mechanism A first heat exchange mechanism that heats air supplied to the dehumidification mechanism using a heat pump and a second heat exchange mechanism that is disposed downstream of the dehumidification mechanism located in the dehumidification function regeneration zone; A dehumidification mechanism located in the dehumidification processing zone while supplying heated air heated to a predetermined temperature by the first heat exchange mechanism to the dehumidification mechanism located in the dehumidification function regeneration zone and regenerating the dehumidification function of the dehumidifier There is disclosed a dehumidification system that supplies dehumidified air made by using a dehumidifying air-conditioning space (see Patent Document 1).

  In this dehumidification system, the second heat exchange mechanism collects exhaust heat of the exhaust air that has flowed through the dehumidification mechanism of the dehumidification function regeneration zone using a predetermined refrigerant, and the exhaust heat recovered by the second heat exchange mechanism is recovered. The refrigerant is supplied from the second heat exchange mechanism to the first heat exchange mechanism, and the exhaust heat is used to heat the air in the first heat exchange mechanism. In the second heat exchanging mechanism, the exhaust heat of the exhaust air is recovered, so that the temperature of the exhaust air decreases, and at the same time, the exhaust air is dehumidified and the humidity of the exhaust air decreases. Exhaust air whose temperature and humidity are reduced is exhausted outdoors.

Japanese Patent Application No. 2014-0192217

  In the dehumidification system disclosed in Patent Document 1, energy saving of the heater is achieved by heating by the first heat exchange mechanism used together with the heater. However, the exhaust air from which the exhaust heat is recovered in the second heat exchange mechanism is exhausted to the outside as it is, and the exhaust air having a low temperature and humidity is not reused, and the outside air is supplied to the first heat exchange mechanism. The outside air is heated by the first heat exchange mechanism to create heated air, or an outside air conditioner that adjusts the temperature and humidity of the outside air is installed upstream of the first heat exchange mechanism, and the outside air conditioner The outside air adjusted to temperature and humidity is supplied to the first heat exchange mechanism, and the outside air adjusted to temperature and humidity is heated by the first heat exchange mechanism to create heated air, reducing the load on the outside air conditioner It is not possible to save energy of the system. This dehumidification system must constantly supply outside air to the first heat exchange mechanism, and realizes a circulation type dehumidification system that operates with heated air and exhaust air circulating through a closed route without using outside air. I can't.

  An object of the present invention is to recycle exhaust air whose temperature and absolute humidity have been reduced by the second heat exchange mechanism, and to reduce energy consumption by reducing the load on the outdoor air conditioner. To provide a system. Another object of the present invention is to provide a recirculation type exhaust heat utilization type dehumidification system operated by air circulating through a closed route.

  The premise of the present invention for solving the above problems is that the dehumidification processing zone for generating dehumidified air, the dehumidification function regeneration zone for regenerating the dehumidification function, and the dehumidification treatment zone and dehumidification function regeneration zone having a dehumidifying agent are disposed. A dehumidifying mechanism, a processing-side upstream duct located upstream of the dehumidifying zone and connected to the dehumidifying zone, and a processing-side downstream duct located downstream from the dehumidifying zone and connected to the dehumidifying zone A regeneration-side upstream duct located upstream of the dehumidification function regeneration zone and connected to the dehumidification function regeneration zone; and a regeneration-side downstream duct located downstream of the dehumidification function regeneration zone and connected to the dehumidification function regeneration zone; A first heat exchange mechanism that is disposed upstream of the dehumidifying mechanism located in the dehumidifying function regeneration zone and that heats the air supplied to the dehumidifying mechanism using a heat pump; and a dehumidifying function regeneration zone It is arranged on the downstream side of the dehumidifying mechanism that performs heat exchange with the first heat exchanging mechanism while recovering the exhaust heat of the exhaust air at a predetermined temperature that flows through the dehumidifying mechanism in the dehumidifying function regeneration zone using a predetermined refrigerant. A second heat exchange mechanism, the exhaust heat recovered by the second heat exchange mechanism is used for heating the air in the first heat exchange mechanism, and the heated air heated to a predetermined temperature by the first heat exchange mechanism Dehumidification function Uses exhaust heat to supply dehumidification air created by the dehumidification mechanism located in the dehumidification processing zone to the dehumidification air-conditioning space while supplying air to the dehumidification mechanism located in the dehumidification function regeneration zone and regenerating the dehumidification function of the dehumidifying agent Dehumidification system.

  The first feature of the exhaust heat utilization type dehumidification system of the present invention based on the above premise is that the exhaust heat utilization type dehumidification system has a regeneration side upstream duct extending upstream of the first heat exchange mechanism and a downstream side of the second heat exchange mechanism. An exhaust air recirculation duct for connecting exhaust air that has passed through the dehumidification mechanism of the regeneration zone to circulate from the regeneration downstream duct to the regeneration upstream duct, and downstream of the exhaust air recirculation duct A first damper that adjusts the flow rate of exhaust air exhausted from the regeneration downstream duct that is installed in the regeneration downstream duct, and the flow rate of exhaust air that is installed in the exhaust air circulation duct and flows through the exhaust air circulation duct. A second damper to be adjusted, and a first temperature sensor installed in a regeneration-side downstream duct extending between the second heat exchange mechanism and the exhaust air circulation duct to measure the temperature of the exhaust air. When the measured temperature of the exhaust air measured by the first temperature sensor is equal to or lower than the set temperature, the mold dehumidification system keeps the opening of the first damper at a predetermined opening and exhausts air from the regeneration downstream duct The first circulation operation in which the flow rate of the second damper is increased and the flow rate of the exhaust air flowing through the exhaust air circulation duct is increased by increasing the opening amount of the second damper, and the opening amount of the first damper is fully increased. A second circulation operation in which the exhaust air from the regeneration-side downstream duct is closed to shut off the exhaust air, and the opening of the second damper is fully opened to maximize the flow rate of the exhaust air flowing through the exhaust air circulation duct. When the measured temperature of the exhaust air measured by the first temperature sensor exceeds the set temperature, the exhaust gas is exhausted from the regeneration downstream duct while maintaining the opening degree of the first damper at a predetermined opening degree. If the air flow rate is kept at a predetermined flow rate Moni is to to reduce the degree of opening of the second damper to implement a third circulation operation to reduce the flow rate of the exhaust air flowing through the exhaust air recirculation duct.

  As an example of the exhaust heat utilization type dehumidification system of the present invention having the first feature, the exhaust heat utilization type dehumidification system is configured such that the exhaust air flow in the exhaust air recirculation duct with the second damper fully closed. Including exhaust gas standby operation that starts the system while maximizing the flow rate of exhaust air exhausted from the regeneration downstream duct with the opening of the first damper fully open. When the measured temperature of the exhaust air measured by the first temperature sensor becomes equal to or lower than the set temperature after the measured temperature of the exhaust air measured by the first temperature sensor after the standby operation is performed, the first and second Exhaust gas measured by the first temperature sensor after the measured temperature of the exhaust air measured by the first temperature sensor after performing any of the circulation operation and performing the exhaust gas circulation standby operation is stabilized. If the measured temperature of the gas exceeds the set temperature, carrying out the third circulation operation.

  As another example of the exhaust heat utilization type dehumidification system of the present invention having the first feature, the exhaust heat utilization type dehumidification system recirculates the refrigerant to the first heat exchange mechanism and the second heat exchange mechanism. A pipe, a refrigerant bypass pipe connected to the refrigerant circulation pipe and allowing the refrigerant to circulate to the first heat exchange mechanism without passing the refrigerant to the second heat exchange mechanism, and a flow rate of the refrigerant to be circulated to the second heat exchange mechanism And a valve mechanism for adjusting the flow rate of the refrigerant to be passed through the refrigerant bypass pipe, and a refrigerant circulation pipe extending between the refrigerant outlet and the refrigerant bypass pipe in the second heat exchange mechanism, And a second temperature sensor that measures the temperature of the refrigerant flowing out from the refrigerant outlet, and in the exhaust heat utilization type dehumidification system, the second temperature sensor measured during any of the first to third circulation operations. If the measured temperature of the refrigerant exceeds the set temperature, While maintaining the opening of the compressor at a predetermined opening, the flow rate of the refrigerant flowing into the second heat exchange mechanism is increased while the flow rate of the refrigerant flowing into the refrigerant bypass pipe is decreased by adjusting the valve mechanism, When the measured temperature of the refrigerant measured by the second temperature sensor is lower than the set temperature during any one of the first to third circulation operations, the valve opening of each damper is maintained at a predetermined opening degree. The mechanism is adjusted to increase the flow rate of the refrigerant flowing into the refrigerant bypass pipe and reduce the flow rate of the refrigerant flowing into the second heat exchange mechanism.

  As another example of the exhaust heat utilization type dehumidification system of the present invention having the first feature, in the exhaust heat utilization type dehumidification system, the measured temperature of the refrigerant measured by the second temperature sensor during the exhaust gas recirculation standby operation is performed. When the temperature exceeds the set temperature, adjust the valve mechanism to reduce the flow rate of the refrigerant flowing into the refrigerant bypass pipe, increase the flow rate of the refrigerant flowing into the second heat exchange mechanism, and perform the exhaust gas recirculation standby operation When the measured temperature of the refrigerant measured by the second temperature sensor becomes lower than the set temperature, the flow rate of the refrigerant flowing into the refrigerant bypass pipe is increased by adjusting the valve mechanism and flows into the second heat exchange mechanism. The measured temperature of the exhaust air measured by the first temperature sensor after the measured temperature of the exhaust air measured by the first temperature sensor after the flow rate of the refrigerant to be reduced and the exhaust gas recirculation standby operation is performed is stabilized. When the temperature is lower than the set temperature, the first circulation operation or the second circulation operation is performed while the refrigerant flow rate in the valve mechanism is kept constant, and the exhaust gas circulation standby operation is performed, and then the exhaust gas measured by the first temperature sensor When the measured temperature of the exhaust air measured by the first temperature sensor exceeds the set temperature after the measured temperature of the air has stabilized, the third circulation operation is performed while keeping the flow rate of the refrigerant in the valve mechanism constant.

  The second feature of the exhaust heat utilization type dehumidification system of the present invention based on the above premise is that the exhaust heat utilization type dehumidification system has a regeneration-side upstream duct extending upstream of the first heat exchange mechanism and a downstream side of the second heat exchange mechanism. An exhaust air recirculation duct that connects the regeneration side downstream duct extending to the regeneration side and circulates the exhaust air that has passed through the dehumidification mechanism of the dehumidification function regeneration zone from the regeneration side downstream duct to the regeneration side upstream duct, and a dehumidification located in the dehumidification treatment zone The purge air at a predetermined temperature, which is connected to the mechanism and the regeneration upstream duct extending upstream of the first heat exchange mechanism and flows through the purge region of the dehumidification mechanism in the dehumidification processing zone, is introduced from the dehumidification mechanism into the regeneration upstream duct. A purge air introduction duct, an air exhaust duct connected to a regeneration side downstream duct extending between the dehumidification function regeneration zone and the second heat exchange mechanism, and a downstream side of the exhaust air recirculation duct A first damper that adjusts the flow rate of exhaust air that is installed in the raw-side downstream duct and exhausts from the regeneration-side downstream duct and a flow rate of exhaust air that is installed in the exhaust-air circulation duct and flows through the exhaust-air circulation duct. Installed in the second damper, the third damper that is installed in the air exhaust duct and adjusts the flow rate of the air exhausted from the air exhaust duct, and in the regeneration downstream duct that extends between the second heat exchange mechanism and the exhaust air recirculation duct And a first temperature sensor for measuring the temperature of the exhaust air. When the measured temperature of the exhaust air measured by the first temperature sensor is equal to or lower than the set temperature, The opening degree of the second damper is increased while the opening degree of the second damper is fully closed and the opening degree of the third damper is maintained at a predetermined opening degree while the flow rate of the air exhausted from the air exhaust duct is maintained at a predetermined flow rate. Exhaust When the first circulation operation to increase the flow rate of the exhaust air flowing through the circulating duct is performed and the measured temperature of the exhaust air measured by the first temperature sensor exceeds the set temperature, the opening of the first damper is fully closed In addition, while maintaining the opening of the third damper at a predetermined opening and maintaining the flow rate of air exhausted from the air exhaust duct at a predetermined flow rate, the opening of the second damper is reduced and the exhaust air recirculation duct The second circulation operation is performed to reduce the flow rate of the exhaust air flowing therethrough.

  As an example of the exhaust heat utilization type dehumidification system of the present invention having the second feature, the exhaust heat utilization type dehumidification system is configured such that the exhaust air flow in the exhaust air recirculation duct with the second damper fully closed. The exhaust gas circulation standby operation for starting the system while maximizing the flow rate of the exhaust air exhausted from the regeneration downstream duct by fully closing the opening of the third damper and fully opening the opening of the first damper In addition, in the dehumidification system, the measured temperature of the exhaust air measured by the first temperature sensor becomes equal to or lower than the set temperature after the measured temperature of the exhaust air measured by the first temperature sensor after the exhaust gas recirculation standby operation is performed. If the measured temperature of the exhaust air measured by the first temperature sensor after the first circulation operation is performed and the exhaust gas circulation standby operation is performed, the exhaust gas measured by the first temperature sensor is stabilized. If the measured temperature of the gas exceeds the set temperature, performing the second circulation operation.

  As another example of the exhaust heat utilization type dehumidification system of the present invention having the second feature, the exhaust heat utilization type dehumidification system causes the refrigerant to circulate between the first heat exchange mechanism and the second heat exchange mechanism. A pipe, a refrigerant bypass pipe connected to the refrigerant circulation pipe and allowing the refrigerant to circulate to the first heat exchange mechanism without passing the refrigerant to the second heat exchange mechanism, and a flow rate of the refrigerant to be circulated to the second heat exchange mechanism And a valve mechanism for adjusting the flow rate of the refrigerant to be passed through the refrigerant bypass pipe, and a refrigerant circulation pipe extending between the refrigerant outlet and the refrigerant bypass pipe in the second heat exchange mechanism, A second temperature sensor for measuring the temperature of the refrigerant flowing out from the refrigerant outlet, and in the exhaust heat utilization type dehumidification system, during the execution of either the first circulation operation or the second circulation operation, the second temperature sensor The measured temperature of the refrigerant measured by exceeds the set temperature. In this case, while maintaining the opening degree of each damper at a predetermined opening degree, the flow rate of the refrigerant flowing into the second heat exchange mechanism is increased while the valve mechanism is adjusted to reduce the flow rate of the refrigerant flowing into the refrigerant bypass pipe. When the measured temperature of the refrigerant measured by the second temperature sensor becomes lower than the set temperature during the execution of either the first circulation operation or the second circulation operation, the opening degree of each damper is set to a predetermined opening degree. The flow rate of the refrigerant flowing into the second heat exchange mechanism is decreased while the flow rate of the refrigerant flowing into the refrigerant bypass pipe is increased by adjusting the valve mechanism.

  As another example of the exhaust heat utilization type dehumidification system of the present invention having the second feature, in the exhaust heat utilization type dehumidification system, the measured temperature of the refrigerant measured by the second temperature sensor during the exhaust gas recirculation standby operation. When the temperature exceeds the set temperature, adjust the valve mechanism to reduce the flow rate of the refrigerant flowing into the refrigerant bypass pipe, increase the flow rate of the refrigerant flowing into the second heat exchange mechanism, and perform the exhaust gas recirculation standby operation When the measured temperature of the refrigerant measured by the second temperature sensor becomes lower than the set temperature, the flow rate of the refrigerant flowing into the refrigerant bypass pipe is increased by adjusting the valve mechanism and flows into the second heat exchange mechanism. The measured temperature of the exhaust air measured by the first temperature sensor after the measured temperature of the exhaust air measured by the first temperature sensor after the flow rate of the refrigerant to flow is reduced and the exhaust gas recirculation standby operation is performed is stabilized. When the temperature falls below the set temperature, the first circulation operation is performed while the refrigerant flow rate in the valve mechanism is kept constant, and the exhaust air measurement temperature measured by the first temperature sensor after the exhaust gas recirculation standby operation is performed. After the stabilization, when the measured temperature of the exhaust air measured by the first temperature sensor exceeds the set temperature, the second circulation operation is performed while the refrigerant flow rate in the valve mechanism is kept constant.

  As an example of the exhaust heat utilization type dehumidification system of the present invention having the first and second features, the second heat exchange mechanism is a coil unit, and the coil unit collects exhaust air while collecting exhaust heat of the exhaust air. Dehumidify.

  As another example of the exhaust heat utilization type dehumidification system of the present invention having the first and second features, the exhaust heat utilization type dehumidification system is installed between the first heat exchange mechanism and the dehumidification mechanism. A heater for heating the heated air heated to a predetermined temperature by the heat exchange mechanism is included.

  As another example of the exhaust heat utilization type dehumidification system of the present invention having the first and second features, the exhaust heat utilization type dehumidification system supplies the dehumidification mechanism of the dehumidification treatment zone and the dehumidification mechanism of the dehumidification function regeneration zone. An outside air conditioner that adjusts the temperature of the outside air while dehumidifying the outside air is included.

  As another example of the exhaust heat utilization type dehumidification system of the present invention having the first and second features, the dehumidifying mechanism is a desiccant rotor, and the refrigerant is water or brine.

  According to the exhaust heat utilization type dehumidification system of the present invention having the first feature, the regeneration side upstream duct extending upstream of the first heat exchange mechanism and the regeneration side downstream duct extending downstream of the second heat exchange mechanism are provided. The exhaust air circulation duct is connected by an exhaust air circulation duct, and the low-temperature and low-humidity exhaust air that has been dehumidified while being reduced in temperature by the second heat exchange mechanism flows into the regeneration-side upstream duct that extends to the upstream side of the first heat exchange mechanism, Since the exhaust air flows into the first heat exchange mechanism, the exhaust air is heated again by the first heat exchange mechanism to form heated air, and the dehumidifying function of the dehumidifier is regenerated by the heated air. Exhaust air whose temperature and humidity are reduced by the mechanism can be reused, and energy saving of the system can be achieved. The dehumidifying system utilizing exhaust heat can fully regenerate the dehumidifying function of the dehumidifying agent by supplying the dehumidifying mechanism with heated air that has heated the low-humidity exhaust air. Air can be supplied to the dehumidified air-conditioned space. When the measured temperature of the exhaust air measured by the first temperature sensor is equal to or lower than the set temperature, the flow rate of the exhaust air exhausted from the regeneration-side downstream duct while the opening degree of the first damper is maintained at the predetermined opening degree The exhaust heat dehumidification system that performs the first circulation operation that maintains the flow rate and increases the flow rate of the exhaust air flowing through the exhaust air recirculation duct by increasing the opening of the second damper is the measured temperature of the exhaust air. Is lower than the set temperature, the temperature and humidity of the exhaust air are kept low, the temperature and humidity of the exhaust air are good, and a large amount of exhaust air with good temperature and humidity is converted into the first heat. Since the heated air having a low humidity can be made by circulating through the exchange mechanism, the load on the first heat exchange mechanism can be reduced, and the energy saving of the system can be achieved. When the measured temperature of the exhaust air measured by the first temperature sensor falls below the set temperature, the opening of the first damper is fully closed to shut off the exhaust air exhaust from the regeneration-side downstream duct, and the second damper The exhaust heat measurement type dehumidification system that performs the second circulation operation that maximizes the flow rate of the exhaust air that flows through the exhaust air circulation duct with the opening degree fully opened has the measured temperature of the exhaust air below the set temperature. Thus, the temperature and humidity of the exhaust air are kept low, the temperature and humidity of the exhaust air are good, and all the exhaust air of good temperature and humidity flows into the first heat exchange mechanism and the humidity is low. Since heated air can be created, the load on the first heat exchange mechanism can be reduced, and not only can the system save energy, but also the first heat exchange mechanism, the dehumidifying mechanism, and the second heat exchange mechanism. And exhaust air circulating through And it is possible to realize a dehumidification system circulation running by heated air. When the measured temperature of the exhaust air measured by the first temperature sensor exceeds the set temperature, the flow rate of the exhaust air exhausted from the regeneration-side downstream duct while maintaining the opening degree of the first damper at a predetermined opening degree is set to a predetermined flow rate. The exhaust gas dehumidification system that performs the third circulation operation in which the opening amount of the second damper is reduced and the flow rate of the exhaust air flowing through the exhaust air circulation duct is decreased. When the set temperature is exceeded, the temperature and humidity of the exhaust air are high. In this case, the outside air adjusted to the predetermined temperature and humidity is supplied to the first heat exchange mechanism, so that the temperature of the exhaust air is increased. The temperature of the exhaust air can be stabilized in the vicinity of the set temperature while reducing the load on the heat pump of the first heat exchange mechanism to save energy in the system, while stabilizing the temperature of the exhaust air near the set temperature. It can rapidly shift to any of the operation of the first and second circulation operation speed.

  While the opening of the second damper is fully closed, the flow of exhaust air in the exhaust air circulation duct is blocked, and the opening of the first damper is fully opened to maximize the flow rate of exhaust air exhausted from the regeneration downstream duct. Including the exhaust gas recirculation standby operation for starting the system, the measured temperature of the exhaust air measured by the first temperature sensor after the measured temperature of the exhaust air measured by the first temperature sensor after the exhaust gas recirculation standby operation is performed is When the temperature falls below the set temperature, one of the first and second circulation operations is performed, and when the measured temperature of the exhaust air measured by the first temperature sensor exceeds the set temperature, the third circulation operation is performed. The heat-based dehumidification system shuts off the flow of exhaust air in the exhaust air circulation duct during start-up operation of the exhaust gas circulation standby operation system, fully opens the first damper and lowers the regeneration side. The flow rate of the exhaust air exhausted from the duct is maximized, and the outside air adjusted to a predetermined temperature and a predetermined humidity flows into the first heat exchange mechanism to create heated air, so that the temperature of the exhaust air is brought close to the set temperature. It can be stabilized, and can smoothly shift to the first and second circulation operations and the third circulation operation after the exhaust gas recirculation standby operation. After the exhaust air circulation standby operation is performed and the measured temperature of the exhaust air measured by the first temperature sensor is stabilized, the measured temperature of the exhaust air measured by the first temperature sensor becomes lower than the set temperature, and the first circulation operation is performed. When performing, a large amount of exhaust air having a good temperature and humidity can be caused to flow into the first heat exchange mechanism to make heated air with low humidity, so the load on the first heat exchange mechanism can be reduced, Energy saving of the system can be achieved. After the exhaust gas recirculation standby operation is performed, the measured temperature of the exhaust air measured by the first temperature sensor is stabilized, and then the measured temperature of the exhaust air measured by the first temperature sensor becomes lower than the set temperature, and the second circulation operation is performed. When performing, a large amount of exhaust air having a good temperature and humidity can be caused to flow into the first heat exchange mechanism to make heated air with low humidity, so the load on the first heat exchange mechanism can be reduced, Not only can the energy saving of the system be achieved, but also a circulation type dehumidification system that operates by air circulating through the first heat exchange mechanism, the dehumidification mechanism, and the second heat exchange mechanism can be realized. After the exhaust gas recirculation standby operation is performed and the measured temperature of the exhaust air measured by the first temperature sensor is stabilized, the measured temperature of the exhaust air measured by the first temperature sensor exceeds the set temperature, and the third circulation operation is performed. When performing, the outside air adjusted to a predetermined temperature and humidity is supplied to the first heat exchange mechanism, whereby the temperature of the exhaust air can be returned to the set temperature or lower, and the load of the heat pump of the first heat exchange mechanism The temperature of the exhaust air can be stabilized near the set temperature while reducing the energy consumption of the system and can be quickly shifted from the third circulation operation to one of the first and second circulation operation speeds. Can do.

  A refrigerant circulation pipe, a refrigerant bypass pipe, a valve mechanism, and a second temperature sensor are included, and the measured temperature of the refrigerant measured by the second temperature sensor becomes equal to or higher than the set temperature during any one of the first to third circulation operations. In this case, while maintaining the opening degree of each damper at a predetermined opening degree, the flow rate of the refrigerant flowing into the second heat exchange mechanism is reduced while adjusting the valve mechanism to reduce the flow rate of the refrigerant flowing into the refrigerant bypass pipe. When the measured temperature of the refrigerant measured by the second temperature sensor is lower than the set temperature, the valve mechanism is adjusted to flow into the refrigerant bypass pipe while maintaining the opening degree of each damper at a predetermined opening degree. In the exhaust heat dehumidification system that increases the flow rate of the refrigerant and decreases the flow rate of the refrigerant flowing into the second heat exchange mechanism, the measured temperature of the refrigerant is set during any of the first to third circulation operations. When the temperature rises above the temperature, it flows to the second heat exchange mechanism. By increasing the flow rate of the refrigerant to be used, the temperature adjustment function and the dehumidification function in the second heat exchange mechanism can be utilized to the maximum, and the temperature and humidity of the exhaust air are reliably reduced by the second heat exchange mechanism. The exhaust air whose temperature and humidity are reduced by the second heat exchange mechanism can be efficiently reused. The exhaust heat utilization type dehumidification system reduces the flow rate of the refrigerant flowing into the second heat exchange mechanism when the measured temperature of the refrigerant becomes lower than the set temperature during any of the first to third circulation operations. The heating capacity of the first heat exchange mechanism using the heat pump is reduced, and for example, when the regeneration temperature of the dehumidifying function of the dehumidifying agent is low, the temperature of the heated air can be lowered and consumed in the first heat exchange mechanism The dehumidifying function of the dehumidifying agent can be recovered while suppressing energy. When adjusting the valve mechanism and adjusting the flow rate of the refrigerant, the exhaust heat utilization type dehumidification system maintains the opening degree of each damper at a predetermined opening degree, so that the opening degree of each damper is changed during the adjustment of the valve mechanism. Compared with the case of making it possible, the adjustment control of the valve mechanism and the adjustment control of each damper can be coordinated.

  If the measured temperature of the refrigerant measured by the second temperature sensor is equal to or higher than the set temperature during the exhaust gas recirculation standby operation, the valve mechanism is adjusted to reduce the flow rate of the refrigerant flowing into the refrigerant bypass pipe, and 2 When the flow rate of the refrigerant flowing into the heat exchange mechanism is increased and the measured temperature of the refrigerant measured by the second temperature sensor becomes lower than the set temperature, the flow rate of the refrigerant flowing into the refrigerant bypass pipe is adjusted by adjusting the valve mechanism. In addition to increasing the flow rate of the refrigerant flowing into the second heat exchange mechanism, after the exhaust gas circulation standby operation is performed and the measured temperature of the exhaust air measured by the first temperature sensor is stabilized, the first temperature sensor When the measured temperature of the exhaust air is equal to or lower than the set temperature, the first circulation operation or the second circulation operation is performed while the refrigerant flow rate in the valve mechanism is kept constant, and the first temperature sensor measures. When the measured temperature of the air and air exceeds the set temperature, the exhaust heat utilization type dehumidification system that performs the third circulation operation while keeping the flow rate of the refrigerant in the valve mechanism constant measures the refrigerant during the exhaust gas recirculation standby operation. When the temperature is equal to or higher than the set temperature, the temperature adjustment function and the dehumidification function in the second heat exchange mechanism can be maximized by increasing the flow rate of the refrigerant flowing into the second heat exchange mechanism. The temperature and humidity of the exhaust air can be reliably reduced by the second heat exchange mechanism, and the temperature of the exhaust air can be quickly stabilized in the vicinity of the set temperature, and the first and second circulations after the exhaust recirculation standby operation It is possible to smoothly shift to the operation and the third circulation operation. The exhaust heat utilization type dehumidification system uses a heat pump by reducing the flow rate of the refrigerant flowing into the second heat exchange mechanism when the measured temperature of the refrigerant becomes lower than the set temperature during the exhaust gas recirculation standby operation. The heating capacity of the first heat exchange mechanism is reduced, for example, when the regeneration temperature of the dehumidifying function of the dehumidifying agent is low, the temperature of the heated air can be lowered, and the dehumidification is performed while suppressing the energy consumed in the first heat exchange mechanism. The dehumidifying function of the agent can be restored. The exhaust heat utilization type dehumidification system has a valve mechanism for performing any of the first to third circulation operations after the measured temperature of the exhaust air measured by the first temperature sensor after the exhaust gas circulation standby operation is performed. Since the flow rate of the refrigerant in the second heat exchange mechanism is kept constant by adjusting the flow rate of the valve mechanism, the control control of the valve mechanism is compared with the case where the flow rate of the refrigerant in the valve mechanism is changed during the first to third circulation operations. And adjustment control of each damper can be coordinated.

  According to the exhaust heat utilization type dehumidification system of the present invention having the second feature, the regeneration side upstream duct extending upstream of the first heat exchange mechanism and the regeneration side downstream duct extending downstream of the second heat exchange mechanism are provided. The exhaust air circulation duct is connected by an exhaust air circulation duct, and the low-temperature and low-humidity exhaust air that has been dehumidified while being reduced in temperature by the second heat exchange mechanism flows into the regeneration-side upstream duct that extends to the upstream side of the first heat exchange mechanism, Since the exhaust air flows into the first heat exchange mechanism, the exhaust air is heated again by the first heat exchange mechanism to form heated air, and the dehumidifying function of the dehumidifier is regenerated by the heated air. Exhaust air whose temperature and humidity are reduced by the mechanism can be reused, the load on the first heat exchange mechanism can be reduced, and energy saving of the system can be achieved. The dehumidifying system utilizing exhaust heat can fully regenerate the dehumidifying function of the dehumidifying agent by supplying the dehumidifying mechanism with heated air that has heated the low-humidity exhaust air. Air can be supplied to the dehumidified air-conditioned space. When the measured temperature of the exhaust air measured by the first temperature sensor becomes equal to or lower than the set temperature, the opening of the first damper is fully closed and the opening of the third damper is held at a predetermined opening to exhaust the air. Use of exhaust heat to perform the first circulation operation in which the flow rate of the air exhausted from the duct is maintained at a predetermined flow rate, and the flow rate of the exhaust air flowing through the exhaust air circulation duct is increased by increasing the opening of the second damper. The mold dehumidification system maintains the low temperature and humidity of the exhaust air because the measured temperature of the exhaust air is below the set temperature, the exhaust air temperature and humidity are good, and the purge air content is reduced. Since all the exhaust air having good temperature and humidity except the above can be circulated to the first heat exchange mechanism to create low-humidity heated air, the load on the first heat exchange mechanism can be reduced, To save energy Not only can, it is possible to realize a circulating dehumidification system running by the exhaust air and heated air circulates between the first heat exchange mechanism and dehumidifying mechanism and a second heat exchange mechanism. When the measured temperature of the exhaust air measured by the first temperature sensor exceeds the set temperature, the opening degree of the first damper is fully closed and the opening degree of the third damper is maintained at a predetermined opening degree, and the air exhaust duct Exhaust heat utilization type that performs the second circulation operation in which the flow rate of the air exhausted from the exhaust air is maintained at a predetermined flow rate, and the flow rate of the exhaust air flowing through the exhaust air circulation duct is reduced by reducing the opening of the second damper In the dehumidification system, when the measured temperature of the exhaust air exceeds the set temperature, the temperature and humidity of the exhaust air are high. In this case, the outside air adjusted to the predetermined temperature and humidity is sent to the first heat exchange mechanism. By supplying air, the temperature of the exhaust air can be returned to the set temperature or lower, reducing the load on the heat pump of the first heat exchange mechanism and saving the system energy, while keeping the temperature of the exhaust air close to the set temperature. Stabilizing It is possible, it is possible to quickly shift from the second circulation operation in the first circulation operation speed.

  The opening of the second damper is fully closed to block the flow of exhaust air in the exhaust air circulation duct, the opening of the third damper is fully closed, the opening of the first damper is fully opened, and the regeneration side is downstream. Including exhaust gas recirculation standby operation for activating the system while maximizing the flow rate of exhaust air exhausted from the duct, and after the exhaust air standby operation has been performed, When the measured temperature of the exhaust air measured by the first temperature sensor falls below the set temperature, the first circulation operation is performed, and when the measured temperature of the exhaust air measured by the first temperature sensor exceeds the set temperature, the second The exhaust heat utilization type dehumidification system that performs the circulation operation is configured such that the exhaust air circulation in the exhaust air circulation duct and the air circulation in the air exhaust duct are blocked during the exhaust circulation standby operation. The exhaust air is exhausted from the regeneration-side downstream duct with the opening of the damper fully opened, and the outside air adjusted to a predetermined temperature and a predetermined humidity flows into the first heat exchange mechanism to create heated air. Thus, the temperature of the exhaust air can be stabilized in the vicinity of the set temperature, and the first circulation operation and the second circulation operation can be smoothly shifted after the exhaust gas recirculation standby operation. After the exhaust air circulation standby operation is performed and the measured temperature of the exhaust air measured by the first temperature sensor is stabilized, the measured temperature of the exhaust air measured by the first temperature sensor becomes lower than the set temperature, and the first circulation operation is performed. When performing, since all the exhaust air having a good temperature and humidity excluding the purge air can be flowed into the first heat exchange mechanism to produce heated air with low humidity, the load on the first heat exchange mechanism is reduced. Not only can the energy saving of the system be reduced, but also a circulation type dehumidification system operated by heated air and exhaust air circulating through the first heat exchange mechanism, the dehumidification mechanism and the second heat exchange mechanism. Can be realized. After the exhaust gas recirculation standby operation is performed and the measured temperature of the exhaust air measured by the first temperature sensor is stabilized, the measured temperature of the exhaust air measured by the first temperature sensor exceeds the set temperature, and the second circulation operation is performed. When performing, the outside air adjusted to a predetermined temperature and humidity is supplied to the first heat exchange mechanism, whereby the temperature of the exhaust air can be returned to the set temperature or lower, and the load of the heat pump of the first heat exchange mechanism The temperature of the exhaust air can be stabilized in the vicinity of the set temperature while reducing the energy consumption of the system, and the second circulation operation can be promptly shifted to the first circulation operation speed.

  A refrigerant circulation pipe, a refrigerant bypass pipe, a valve mechanism, and a second temperature sensor are included, and the measured temperature of the refrigerant measured by the second temperature sensor during the first circulation operation or the second circulation operation is the set temperature. In this case, while maintaining the opening of each damper at a predetermined opening, the valve mechanism is adjusted to reduce the flow rate of the refrigerant flowing into the refrigerant bypass pipe, and the refrigerant flowing into the second heat exchange mechanism When the measured temperature of the refrigerant measured by the second temperature sensor is lower than the set temperature, the refrigerant bypass pipe is adjusted by adjusting the valve mechanism while maintaining the opening degree of each damper at a predetermined opening degree. The exhaust heat utilization type dehumidification system that increases the flow rate of the refrigerant flowing into the heat exchanger and decreases the flow rate of the refrigerant flowing into the second heat exchange mechanism measures the refrigerant while performing either the first or second circulation operation. If the temperature exceeds the set temperature, the second By increasing the flow rate of the refrigerant flowing into the exchange mechanism, the temperature adjustment function and the dehumidification function in the second heat exchange mechanism can be utilized to the maximum, and the temperature and humidity of the exhaust air can be reduced by the second heat exchange mechanism. The exhaust air can be reliably reduced, and the exhaust air whose temperature and humidity are reduced by the second heat exchange mechanism can be efficiently reused. The exhaust heat utilization type dehumidification system reduces the flow rate of the refrigerant flowing into the second heat exchange mechanism when the measured temperature of the refrigerant becomes lower than the set temperature during any one of the first and second circulation operations. The heating capacity of the first heat exchange mechanism using the heat pump is reduced, and for example, when the regeneration temperature of the dehumidifying function of the dehumidifying agent is low, the temperature of the heated air can be lowered and consumed in the first heat exchange mechanism The dehumidifying function of the dehumidifying agent can be recovered while suppressing energy. When adjusting the valve mechanism and adjusting the flow rate of the refrigerant, the exhaust heat utilization type dehumidification system maintains the opening degree of each damper at a predetermined opening degree, so that the opening degree of each damper is changed during the adjustment of the valve mechanism. Compared with the case of making it possible, the adjustment control of the valve mechanism and the adjustment control of each damper can be coordinated.

  If the measured temperature of the refrigerant measured by the second temperature sensor is equal to or higher than the set temperature during the exhaust gas recirculation standby operation, the valve mechanism is adjusted to reduce the flow rate of the refrigerant flowing into the refrigerant bypass pipe, and 2 When the flow rate of the refrigerant flowing into the heat exchange mechanism is increased and the measured temperature of the refrigerant measured by the second temperature sensor becomes lower than the set temperature, the flow rate of the refrigerant flowing into the refrigerant bypass pipe is adjusted by adjusting the valve mechanism. In addition to increasing the flow rate of the refrigerant flowing into the second heat exchange mechanism, after the exhaust gas circulation standby operation is performed and the measured temperature of the exhaust air measured by the first temperature sensor is stabilized, the first temperature sensor When the measured temperature of the exhaust air is equal to or lower than the set temperature, the first circulation operation is performed while the flow rate of the refrigerant in the valve mechanism is kept constant, and the measured temperature of the exhaust air measured by the first temperature sensor. In the exhaust heat utilization type dehumidification system in which the second circulation operation is performed while the refrigerant flow rate in the valve mechanism is kept constant, the measured temperature of the refrigerant is set to the set temperature during the exhaust gas recirculation standby operation. In this case, since the temperature adjustment function and the dehumidification function of the second heat exchange mechanism can be utilized to the maximum by increasing the flow rate of the refrigerant flowing into the second heat exchange mechanism, the second heat exchange The mechanism can surely reduce the temperature and humidity of the exhaust air, and can quickly stabilize the temperature of the exhaust air near the set temperature. After the exhaust recirculation standby operation, the first circulation operation and the second circulation operation can be performed. A smooth transition is possible. The exhaust heat utilization type dehumidification system uses a heat pump by reducing the flow rate of the refrigerant flowing into the second heat exchange mechanism when the measured temperature of the refrigerant becomes lower than the set temperature during the exhaust gas recirculation standby operation. The heating capacity of the first heat exchange mechanism is reduced, for example, when the regeneration temperature of the dehumidifying function of the dehumidifying agent is low, the temperature of the heated air can be lowered, and the dehumidification is performed while suppressing the energy consumed in the first heat exchange mechanism. The dehumidifying function of the agent can be restored. The exhaust heat utilization type dehumidification system performs either the first circulation operation or the second circulation operation after the measured temperature of the exhaust air measured by the first temperature sensor is stabilized after the exhaust gas circulation standby operation is performed. Since the flow rate of the refrigerant in the second heat exchange mechanism is kept constant by adjusting the flow rate by the valve mechanism, the valve mechanism is compared with the case where the flow rate of the refrigerant in the valve mechanism is changed during the first and second circulation operations. The adjustment control of each damper and the adjustment control of each damper can be coordinated.

  The exhaust heat utilization type dehumidification system in which the second heat exchange mechanism is a coil unit and the coil unit dehumidifies exhaust air while collecting exhaust heat of the exhaust air reliably reduces the temperature and humidity of the exhaust air by the coil unit. Therefore, the exhaust air of low temperature and low humidity is caused to flow into the regeneration-side upstream duct extending upstream of the first heat exchange mechanism, and the exhaust air is caused to flow into the first heat exchange mechanism. Heating by the first heat exchange mechanism can be performed to produce low-humidity heated air, and the dehumidifying function of the dehumidifying agent can be reliably regenerated by the heated air. The exhaust heat utilization type dehumidification system can recirculate the exhaust air whose temperature and humidity are reduced by the coil unit while flowing through the dehumidification mechanism of the dehumidification function regeneration zone, and reducing the load of the first heat exchange mechanism Can save energy of the system.

  An exhaust heat utilization type dehumidification system including a heater that is installed between the first heat exchange mechanism and the dehumidification mechanism and that heats heated air heated to a predetermined temperature by the first heat exchange mechanism uses the heater to achieve the predetermined temperature. Since the heated air heated further is heated, the air supplied to the dehumidifying mechanism can be sufficiently heated even when the amount of heat supplied to the evaporator of the heat pump is small, such as in winter when the temperature of the outside air is low. The dehumidifying function of the dehumidifying agent can be reliably regenerated using the heated air.

  The first temperature sensor measures the dehumidification system using the exhaust heat that includes the outside air conditioner that dehumidifies the outside air supplied to the dehumidifying mechanism of the dehumidifying treatment zone and the dehumidifying mechanism of the dehumidifying function regeneration zone while adjusting the temperature of the outside air. When the measured temperature of the exhaust air becomes lower than the set temperature, the flow rate of the exhaust air flowing through the exhaust air circulation duct is increased, and the first heat exchange of the outside air adjusted to a predetermined temperature and humidity by the outside air conditioner Reduces the load on the air conditioner by reducing the supply of air to the mechanism or by stopping the supply of air to the first heat exchange mechanism that has been adjusted to a predetermined temperature and humidity by the outdoor air conditioner The energy consumption of the system can be reduced by reducing the energy consumed in the outdoor air conditioner. When the measured temperature of the exhaust air measured by the first temperature sensor exceeds a set temperature, the exhaust heat utilization type dehumidification system uses the outside air conditioner to convert the outside air adjusted to a predetermined temperature and humidity to the first heat. By making the heated air flow into the exchange mechanism, the temperature of the exhaust air can be stabilized in the vicinity of the set temperature, and a smooth transition can be made to each circulation operation after the exhaust gas recirculation standby operation.

  The dehumidification mechanism is a desiccant rotor, and the exhaust heat utilization type dehumidification system in which the refrigerant is water or brine can reliably produce dehumidified air from which moisture contained in the air is removed using the desiccant rotor. Can be supplied to the dehumidified air-conditioned space. In the exhaust heat utilization type dehumidification system, heat is reliably exchanged between the first heat exchange mechanism and the second heat exchange mechanism by using a refrigerant of water or brine, and is recovered by the second heat exchange mechanism. The exhaust heat from the exhaust air can be reliably used for heating the air in the first heat exchange mechanism.

The block diagram of the exhaust-heat utilization type dehumidification system shown as an example. The figure which shows an example of supply of the dehumidification air with respect to dehumidification air-conditioning space, and return air. The figure which shows another example of the supply and exhaust_gas | exhaustion of dehumidification air with respect to dehumidification air-conditioning space. The figure explaining the exhaust gas recirculation standby operation of a waste heat utilization type dehumidification system. The figure explaining the 1st circulation operation or the 3rd circulation operation of an exhaust-heat utilization type dehumidification system. The figure explaining the 2nd circulation driving | operation of a waste heat utilization type dehumidification system. The block diagram of the exhaust-heat utilization type dehumidification system shown as another example. The figure explaining the exhaust gas recirculation standby operation of the exhaust heat utilization type dehumidification system of FIG. The figure explaining 1st circulation operation or 3rd circulation operation of the exhaust-heat utilization type dehumidification system of FIG. The figure explaining the 2nd circulation operation of the exhaust-heat utilization type dehumidification system of FIG. The block diagram of the exhaust-heat utilization type dehumidification system shown as another example. The figure explaining the exhaust gas recirculation standby operation of the exhaust heat utilization type dehumidification system of FIG. The figure explaining 1st circulation operation or 2nd circulation operation of the exhaust-heat utilization type dehumidification system of FIG. The block diagram of the exhaust-heat utilization type dehumidification system shown as another example. The figure explaining the exhaust gas recirculation standby operation of the exhaust heat utilization type dehumidification system of FIG. The figure explaining 1st circulation operation or 2nd circulation operation of the exhaust-heat utilization type dehumidification system of FIG.

  The details of the exhaust heat utilization type dehumidification system according to the present invention will be described with reference to the accompanying drawings such as FIG. 1 which is a configuration diagram of the exhaust heat utilization type dehumidification system 10A as an example. 2 is a diagram illustrating an example of supply and return of dehumidified air to the dehumidified air-conditioned space 35, and FIG. 3 is a diagram illustrating another example of supply and exhaust of dehumidified air to the dehumidified air-conditioned space 35. It is. 1, illustration of the dehumidification air-conditioning space 35 is abbreviate | omitted, and illustration of the component apparatus of the desiccant air conditioner 11 is abbreviate | omitted in FIG.

  Waste heat utilization type dehumidification system 10A (including exhaust heat utilization type dehumidification systems 10B to 10D described later) creates dehumidified air (including low dew point air) with low humidity, and uses the dehumidified air as a lithium battery manufacturing factory or pharmaceutical factory. The air is supplied to a dehumidified air-conditioned space 35 (see FIGS. 2 and 3) that requires dehumidified air such as a clean room, an environmental test room, a food processing factory, a semiconductor manufacturing factory, and a machine product warehouse. The exhaust heat utilization type dehumidification system 10A includes a desiccant air conditioner 11, a first heat exchange mechanism 12, a heater 13, a second heat exchange mechanism 14, an outside air conditioner 15, and a controller 16.

  The desiccant air conditioner 11 includes a desiccant rotor 17 (dehumidification mechanism), a dehumidification processing zone 18 that creates dehumidified air using the desiccant rotor 17, and a dehumidification function regeneration zone 19 that regenerates the dehumidification function of the desiccant rotor 17 (dehumidifier). And have. The desiccant rotor 17 is disposed in the dehumidifying treatment zone 18 and the dehumidifying function regeneration zone 19. The desiccant rotor 17 contains a dehumidifying agent (not shown) such as a silica gel agent or a zeolite agent inside a cylindrical housing, and rotates in one direction inside the desiccant air conditioner 11 to regenerate the dehumidifying treatment zone 18 and the dehumidifying function. The zone 19 is moved repeatedly.

  In the desiccant rotor 17, a portion located in the dehumidifying treatment zone 18 becomes a dehumidifying region 20, and a portion located in the dehumidifying function regeneration zone 19 becomes a moisture releasing region 21. In the dehumidifying area 20 of the desiccant rotor 17 located in the dehumidifying treatment zone 18, moisture contained in the air is adsorbed (absorbed) by the dehumidifying agent to generate dehumidified air. In the dehumidifying area 21 of the desiccant rotor 17 located in the dehumidifying function regeneration zone 19, the dehumidifying agent that has adsorbed the moisture is heated to flow the heated air to heat the dehumidifying agent, and the dehumidifying agent is released to release the moisture. Play the function.

  On the upstream side of the dehumidification processing zone 18 of the desiccant air conditioner 11, a processing side upstream duct 22 is installed. The processing-side upstream duct 22 is connected to an air intake port of the dehumidification processing zone 18 and is connected to the dehumidification processing zone 18 and an outside air intake port (not shown) of the building. The processing-side upstream duct 22 is connected to a dehumidifying space circulating duct 23 connected to the dehumidifying air-conditioned space 35 of the building. A processing-side downstream duct 24 is installed on the downstream side of the dehumidification processing zone 18 of the desiccant air conditioner 11. The processing-side downstream duct 24 is connected to the air supply port of the dehumidification treatment zone 18 and is connected to the dehumidification treatment zone 18 and the dehumidification air-conditioning space 35 of the building.

  A regeneration-side upstream duct 25 is installed upstream of the dehumidifying function regeneration zone 19 of the desiccant air conditioner 11. The regeneration-side upstream duct 25 is connected to the air intake of the dehumidification function regeneration zone 19 and is connected to the dehumidification function regeneration zone 19 and the outside air intake of the building. A regeneration-side downstream duct 26 is installed on the downstream side of the dehumidifying function regeneration zone 19 of the desiccant air conditioner 11. The regeneration-side downstream duct 26 is connected to the air exhaust port of the dehumidification function regeneration zone 19 and is connected to the dehumidification function regeneration zone 19 and a building exhaust port (not shown).

  An air supply blower 27 is installed between the air intake (the processing-side upstream duct 22) and the desiccant rotor 17 in the dehumidification processing zone 18 of the desiccant air conditioner 11. An exhaust fan 28 is installed between the desiccant rotor 17 and the air exhaust port (regeneration side downstream duct 26) in the dehumidifying function regeneration zone 19 of the desiccant air conditioner 11. An exhaust air recirculation duct 29 is installed in the regeneration side upstream duct 25 and the regeneration side downstream duct 26.

  The exhaust air recirculation duct 29 is connected to a regeneration upstream duct 25 extending upstream of the first heat exchange mechanism 12 and to a regeneration downstream duct 26 extending downstream of the second heat exchange mechanism 14. Yes. The exhaust air recirculation duct 29 circulates the exhaust air flowing through the desiccant rotor 17 in the dehumidifying function regeneration zone 19 from the regeneration downstream duct 26 to the regeneration upstream duct 25.

  In the desiccant air conditioner 11, when the air supply blower 27 is activated, air flows from the processing-side upstream duct 22 through the air intake port into the dehumidification processing zone 18, and the air contacts the dehumidifying agent of the desiccant rotor 17 and moisture. After the dehumidified air is absorbed, the dehumidified air flows into the processing-side downstream duct 24 from the air supply port. When the exhaust blower 28 is activated, air flows from the regeneration upstream duct 25 through the air intake into the dehumidifying function regeneration zone 19, and the heated air heated by the first heat exchange mechanism 12 and the heater 13 is desiccant. After contacting the dehumidifier of the rotor 17 and drying the dehumidifier, the exhaust air (heated air) flows into the regeneration downstream duct 26 from the air exhaust port.

  A first damper 30 (first motor damper) is installed in the regeneration-side downstream duct 26 that extends downstream from the exhaust air circulation duct 29. The first damper 30 adjusts the flow rate of exhaust air exhausted from the regeneration-side downstream duct 26. The first damper 30 has a control unit (not shown) connected to the controller 16 via a control signal line 31. A second damper 32 (second motor damper) is installed in the exhaust air circulation duct 29 extending in the vicinity of the regeneration-side downstream duct 26. The second damper 32 adjusts the flow rate of the exhaust air flowing through the exhaust air circulation duct 29. The second damper 32 has a control unit (not shown) connected to the controller 16 via the control signal line 31.

  A first temperature sensor 33 is installed in the regeneration-side downstream duct 26 extending between the second heat exchange mechanism 14 and the exhaust air circulation duct 29. The first temperature sensor 33 is connected to the controller 16 via the control signal line 31. The first temperature sensor 33 measures the temperature of the exhaust air flowing through the regeneration-side downstream duct 26 and transmits the measured temperature (measurement temperature) of the exhaust air to the controller 16. A temperature sensor 34 is installed in the dehumidifying function regeneration zone 18 located on the upstream side of the desiccant rotor 17. The temperature sensor 34 is connected to the controller 16 via the control signal line 31. The temperature sensor 34 measures the temperature of the heated air flowing through the dehumidifying function regeneration zone 19 and sets the measured temperature (measured temperature) of the heated air to the controller 16.

  As an example of supply / exhaust of dehumidified air to / from the dehumidified air conditioning space 35, as shown in FIG. 2, the dehumidified air produced by the desiccant air conditioner 11 is supplied from the processing side downstream duct 24 to the dehumidified air conditioned space 35, and dehumidified air conditioning is performed. The circulating air exhausted from the space 35 is returned to the processing-side upstream duct 22 through the dehumidifying space circulating duct 23. The dehumidification processing zone 18 of the desiccant air conditioner 11 is supplied with the ambient air exhausted from the dehumidification conditioned space 35 and the outside air taken in from the processing side upstream duct 22. As another example of supply / exhaust of dehumidified air to / from the dehumidified air-conditioned space 35, as shown in FIG. 3, the air exhausted from the dehumidified air-conditioned space 35 is not returned to the processing-side upstream duct 22, but outside (outside air). Released. The dehumidifying zone 18 of the desiccant air conditioner 11 is supplied with a predetermined flow rate of outside air taken from the processing-side upstream duct 22. The systems 10A to 10D will be described by taking the supply and exhaust of the dehumidified air in FIG. 2 as an example.

  The first heat exchange mechanism 12 is disposed on the upstream side of the desiccant rotor 17 (dehumidification function regeneration zone 18), and is disposed in the regeneration-side upstream duct 22. The first heat exchange mechanism 12 is formed of a heat pump unit 37 having an inverter control type compressor 36 (compressor) and a heat exchanger 38. The heat pump unit 37 constitutes a refrigeration cycle using CO2 as a refrigerant. The heat pump unit 37 includes a condenser 39 installed in the regeneration-side upstream duct 22, an evaporator 40 installed in the heat exchanger 38, and an expansion valve 47.

  The compressor 36, the condenser 39, the evaporator 40, and the expansion valve 47 of the heat pump unit 37 are connected by an outgoing pipe 41 and a return pipe 42. The compressor 36 of the heat pump unit 37 is installed in the outgoing pipe 41. The heat pump unit 37 has a control unit (not shown) connected to the controller 16 via the control signal line 31. The condenser 39 may be installed in the dehumidifying function regeneration zone 18 (inside the desiccant air conditioner 11) on the upstream side of the desiccant rotor 17.

  The heat exchanger 38 is provided with a heat exchange coil 43 that exchanges heat with the first heat exchange mechanism 12 (the evaporator 40 of the heat pump unit 37). A refrigerant circulation pipe 44 is connected to the heat exchange coil 43. The refrigerant circulation pipe 44 causes the refrigerant to circulate through the heat exchange coil 43 and the second heat exchange mechanism 14 of the heat exchanger 38 (refrigerant circulates through the first heat exchange mechanism 12 and the second heat exchange mechanism 14). A refrigerant circulation pipe 44 extending between the heat exchange coil 43 and the second heat exchange mechanism 14 is provided with a circulation pump 45 for circulating the refrigerant. Water or brine is used as the refrigerant flowing through the second heat exchange mechanism 14, the heat exchange coil 43, and the refrigerant circulation pipe 44, but a refrigerant different from water or brine can also be used.

  The heater 13 is installed in the regeneration-side upstream duct 22 that extends between the first heat exchange mechanism 12 and the desiccant air conditioner 17. The heater 13 further heats the heated air heated to a predetermined temperature by the condenser 39 (first heat exchange mechanism 12) of the heat pump unit 37. When the air in the condenser 39 is insufficiently heated, the heater 13 supplements the heating function, and the air supplied to the desiccant rotor 17 in the dehumidifying function regeneration zone 19 is set to a predetermined temperature (about 120 to about 130 ° C.). Let the temperature rise. The control unit (not shown) of the heater 13 is connected to the controller 16 via the control signal line 31.

  The second heat exchange mechanism 14 is disposed on the downstream side of the desiccant rotor 17 (dehumidification function regeneration zone 19), and is disposed in the regeneration-side downstream duct 26. The second heat exchange mechanism 14 is a coil unit 46 including a heat exchange coil, and the coil unit 46 is installed inside the regeneration-side downstream duct 26. A refrigerant circulation pipe 44 extending from the heat exchange coil 43 of the heat exchanger 38 is connected to the coil unit 46.

  The coil unit 46 may be installed in the dehumidifying function regeneration zone 19 (inside the desiccant air conditioner 11) on the downstream side of the desiccant rotor 17. In the second heat exchange mechanism 14, exhaust air that flows through the regeneration-side downstream duct 26 using the refrigerant (water or brine) that flows into the coil unit 46 (the moisture release region 21 of the desiccant rotor 17 in the dehumidifying function regeneration zone 19). Exhaust air that has passed through it is exchanged with heat to recover the exhaust air heat (exhaust heat).

  The outside air conditioner 15 adjusts the outside air to a predetermined temperature and a predetermined humidity to create conditioned air, supplies the conditioned air to the regeneration-side upstream duct 25, and supplies the conditioned air to the processing-side upstream duct 22. To do. 1 shows a state in which the outdoor air conditioner 15 is installed in a regeneration-side upstream duct 25 extending upstream of the exhaust air recirculation duct 29 and a processing-side upstream duct 22 extending upstream of the air-conditioned space recirculation duct 23. However, the outdoor air conditioner 15 installed in the regeneration-side upstream duct 25 and the processing-side upstream duct 22 is the same, and the regeneration-side upstream duct 25 and the processing-side upstream duct 22 are handled by one outside-air conditioner 15. And conditioned air.

  The controller 16 is a logical computer that includes a central processing unit, a storage device, and a storage area (such as a hard disk) and is operated by a physical OS (operating system). The storage area of the controller 16 stores the set temperature (about 120 to about 130 ° C.) of the heated air supplied to the moisture release area 21 of the desiccant rotor 17, and the second heat exchange mechanism 14 (coil unit 46). A set temperature (for example, 12 ° C.) of exhaust air flowing through the regeneration-side downstream duct 26 extending downstream is stored. Each set temperature can be arbitrarily set. The controller 16 compares the measured temperature of the heated air transmitted from the temperature sensor 34 with the set temperature of the heated air, adjusts the increase / decrease in the rotation speed of the compressor 36 of the heat pump unit 37 based on the comparison result, and While stopping, the increase / decrease in the amount of heat (output) of the heater 13 is adjusted.

  When the controller 16 sends a rotation speed increase signal for increasing the rotation speed of the compressor 36 to the control section of the heat pump unit 37, the control section of the heat pump unit 37 increases the rotation speed of the compressor 36 and the work amount of the heat pump unit 37 increases. To do. Conversely, when the controller 16 sends a rotation speed decrease signal for decreasing the rotation speed of the compressor 36 to the control section of the heat pump unit 37, the control section of the heat pump unit 37 decreases the rotation speed of the compressor 36 and the work of the heat pump unit 37 is performed. The amount decreases.

  When the controller 16 sends an ON signal (activation signal) to the control unit of the heater 13, the control unit operates the heater 13. When the controller 16 sends an OFF signal (stop signal) to the control unit of the heater 13, the control unit stops the heater 13 in operation. When the controller 16 sends a heat amount increase signal to the control unit of the heater 13, the control unit increases the heat amount of the heater 13 in operation, and when the controller 16 sends a heat amount decrease signal to the control unit of the heater 13, the control unit operates. The amount of heat of the heater 13 inside is reduced.

  The air passing through the dehumidifying function regeneration zone 19 is heated to a predetermined temperature (about 120 to about 130 ° C.) by the condenser 39 (which may include the heater 13) of the heat pump unit 37 to be heated air, and the heat exchange coil 43 is By exchanging heat with the evaporator 39 of the heat pump unit 37, the refrigerant flowing into the heat exchange coil 43 from the refrigerant circulation tube 44 is cooled to a predetermined temperature (about 7 ° C.). The cooled refrigerant flows into the refrigerant circulation pipe 44 from the heat exchange coil 43, flows into the second heat exchange mechanism 14 (coil unit 46) through the refrigerant circulation pipe 44, and rises to a predetermined temperature (about 12 ° C.). Be warmed.

  FIG. 4 is a diagram for explaining the exhaust gas recirculation standby operation (system preliminary operation) of the exhaust heat utilization type dehumidification system 10A, and FIG. 5 illustrates the first circulation operation or the third circulation operation of the exhaust heat utilization type dehumidification system 10A. It is a figure explaining. FIG. 6 is a diagram illustrating a second circulation operation of the exhaust heat utilization type dehumidification system 10A. 4-6, illustration of the dehumidification air-conditioning space 35 is abbreviate | omitted. 4 to 6, the flow of heated air and exhaust air in the ducts 25, 26, 29 and the desiccant air conditioner 11 is indicated by an arrow A1, and the outside air, dehumidified air, and ring in the ducts 22, 23, 24 and the desiccant air conditioner 11 are shown. The flow of air is indicated by arrow A2.

  When the system start switch of the controller 16 is turned ON, the dehumidifying system 10A is started. When the dehumidifying system 10A is activated, the desiccant air conditioner 11, the first heat exchange mechanism 12 (heat pump unit 37), the heater 13, the second heat exchange mechanism 14 (coil unit 46), the outside air conditioner 15, the first and second dampers. 30 and 32, the temperature sensors 33 and 34, and the circulation pump 45 are activated.

  When the desiccant air conditioner 11 is activated, the air supply fan 27 and the exhaust fan 28 are activated, and the desiccant rotor 17 starts to rotate in one direction. When the heat pump unit 37 and the circulation pump 45 are operated, the refrigerant circulates through the refrigerant circulation pipe 44, and the refrigerant circulates through the forward pipe 41 and the return pipe 42. The temperature sensor 34 starts measuring the temperature of the heated air flowing through the dehumidification function regeneration zone 19 and transmits the measured temperature of the heated air to the controller 16. The first temperature sensor 33 starts measuring the temperature of the exhaust air flowing through the regeneration-side downstream duct 26 and transmits the measured temperature of the measured exhaust air to the controller 16.

  In the exhaust heat utilization type dehumidification system 10A, the exhaust gas recirculation standby operation is performed at the time of activation. In the exhaust gas recirculation standby operation, the controller 16 transmits an opening fully open signal to the control unit of the first damper 30 and transmits an opening fully closed signal to the control unit of the second damper 32. The control unit of the first damper 30 that has received the opening fully open signal turns the swirl vanes of the first damper 30 to open (fully open) the air flow path of the damper 30 and exhausts air from the regeneration downstream duct 26. Maximize the flow rate. The control unit of the second damper 32 that has received the opening fully closed signal turns the swirl vanes of the second damper 32 to close (fully close) the air flow path of the damper 32, and exhausts the exhaust air to the exhaust air recirculation duct 29. Shut off air inflow.

  In the exhaust gas recirculation standby operation, as indicated by an arrow A1 in FIG. 4, the outside air flows into the outside air conditioner 15, and the outside air conditioner 15 adjusts the temperature and humidity of the outside air to a predetermined temperature and humidity. Conditioned air is made. The conditioned air flows into the condenser 39 of the first heat exchange mechanism 12 through the regeneration-side upstream duct 25 and flows into the dehumidification processing zone 18 of the desiccant air conditioner 11 through the processing-side upstream duct 22. In the first heat exchange mechanism 12, the refrigerant (CO 2) is circulated through the forward pipe 41 and the return pipe 42 (the compressor 36, the condenser 39, the evaporator 40, and the expansion valve 47) by the compressor 36 of the heat pump unit 37. As a result, the air-conditioned air is heated to produce heated air at a predetermined temperature.

  When the measured temperature of the heated air measured by the temperature sensor 34 is transmitted to the controller 16, the controller 16 stores the measured temperature of the heated air (heated air supplied to the moisture release area 21 of the desiccant rotor 17) and the storage area. The stored set temperature (about 120 ° C. to about 130 ° C.) is compared. The controller 16 performs feedback control or feedforward control on the compressor 36 and the heater 13 of the heat pump unit 37 so that the measured temperature of the heated air falls within the set temperature range. The controller 16 increases or decreases the amount of work of the heat pump unit 37, starts and stops the heater 13, or increases or decreases the amount of heat (output) of the heater 13 so that the measured temperature of the heated air becomes the set temperature. Adjust the temperature of the heated air.

  In the heat exchanger 38 of the first heat exchange mechanism 12, heat exchange is performed between the evaporator 40 of the heat pump unit 37 and the heat exchange coil 43, and the refrigerant (about 12) flowing into the heat exchange coil 43 from the refrigerant circulation pipe 44. Water or brine at 0 ° C.) is cooled to a predetermined temperature (about 7 ° C.), and the refrigerant flows out again into the refrigerant circulation pipe 44 and is sent to the second heat exchange mechanism 14 (coil unit 46) through the refrigerant circulation pipe 44. It is done. The heated air heated by the first heat exchange mechanism 12 (the condenser 39 of the heat pump unit 37) flows through the dehumidifying area 21 of the desiccant rotor 17 located in the regeneration zone 19 through the dehumidifying function regeneration zone 19. When the heated air flows through the moisture release area 21, the dehumidifier present in the moisture release area 21 of the desiccant rotor 17 is heated by the heated air, and the moisture adsorbed by the dehumidifier is released, whereby the desiccant rotor 17 is released. The dehumidifying function of (dehumidifying agent) is regenerated (recovery of adsorption performance by drying).

  Exhaust air (heated air) (approximately 80 ° C.) flowing through the moisture release area 21 of the desiccant rotor 17 flows into the regeneration downstream duct 26 from the dehumidification function regeneration zone 19 and passes through the regeneration downstream duct 26 outdoors ( To the outside air). When the exhaust air flows through the regeneration side downstream duct 26, heat exchange is performed between the refrigerant flowing through the second heat exchange mechanism 12 (coil unit 46) and the exhaust air flowing through the regeneration side downstream duct 26. The exhaust heat of the exhaust air is recovered by the second heat exchange mechanism 12. The recovered exchange heat is carried to the heat exchange coil 43 of the heat exchanger 38 by the refrigerant. The exhaust air is dehumidified while its temperature is lowered by the coil unit 46, and becomes low temperature and low humidity exhaust air.

  The conditioned air from which moisture has been removed by the outside air conditioner 15 and cooled to a predetermined temperature is dehumidified by the desiccant air conditioner 11 from the outside air conditioner 15 through the processing-side upstream duct 22 as indicated by an arrow A2 in FIG. It flows into the processing zone 18. The conditioned air that has flowed into the dehumidification treatment zone 18 flows through the dehumidification zone 20 of the desiccant rotor 17 located in the dehumidification treatment zone 18. As the conditioned air flows through the dehumidifying zone 20, the moisture of the air is removed by the dehumidifying agent, and dehumidified air (including low dew point air) is created.

  The dehumidified air flows into the processing downstream duct 24 from the dehumidifying treatment zone 18 extending downstream of the desiccant rotor 17 and is supplied to the dehumidifying conditioned space 35 through the processing downstream duct 24. The dehumidified air supplied to the dehumidified air-conditioned space 35 becomes ambient air containing the humidity of the dehumidified air-conditioned space 35. The circulating air flows from the dehumidified air-conditioned space 35 into the space circulating duct 23, flows through the space circulating duct 23 into the processing side upstream duct 22, is mixed with the conditioned air, and passes again through the dehumidified area 20 of the desiccant rotor 17. Flow into dehumidified air.

  The exhaust heat utilization type dehumidification system 10 </ b> A (including the exhaust heat utilization type dehumidification systems 10 </ b> B to 10 </ b> D) reduces the opening of the first damper 30 while blocking the exhaust air flow in the exhaust air circulation duct 29 during the start-up operation. The condenser of the first heat exchange mechanism 12 converts the conditioned air (outside air) adjusted to a predetermined temperature and a predetermined humidity by the outdoor air conditioner 15 by maximizing the flow rate of the exhaust air exhausted from the regeneration-side downstream duct 26 by full opening. The temperature of the exhaust air can be stabilized in the vicinity of the set temperature by flowing into 39 and heated air, and smoothly transition to the first and second circulation operations and the third circulation operation after the exhaust gas recirculation standby operation. Can do.

  The exhaust heat utilization type dehumidification system 10 </ b> A (including the exhaust heat utilization type dehumidification systems 10 </ b> B to 10 </ b> D) generates exhaust heat (exchange heat) of exhaust air flowing through the moisture release area 21 of the desiccant rotor 17 in the dehumidification function regeneration zone 19. The second heat exchange mechanism 14 (coil unit 46) collects using the refrigerant, and the exhaust heat collected by the second heat exchange mechanism 14 is transferred from the second heat exchange mechanism 14 to the heat exchanger 38 using the refrigerant. When the heat exchange is performed between the evaporator 40 of the first heat exchange mechanism 12 and the heat exchange coil 43 that are supplied and use the heat pump unit 37, the exhaust heat of the exhaust air is the air in the first heat exchange mechanism 12. Therefore, the exhaust heat of the exhaust air used for the regeneration of the dehumidifying function of the desiccant of the desiccant rotor 17 is not wasted, but the exhaust heat recovered from the exhaust air is used to heat the exhaust gas. It can be reused for heating the air in Puyunitto 37.

  The exhaust heat utilization type dehumidification system 10A (including the exhaust heat utilization type dehumidification systems 10B to 10D) uses the exhaust heat of the exhaust air for heating the air in the first heat exchange mechanism 12, so that the temperature of the outside air is low in winter. Even if it exists, since the heat pump unit 37 can be stably operated, the air supplied to the desiccant rotor 17 can be sufficiently heated, and the dehumidifying function of the dehumidifying agent of the desiccant rotor 17 using the heated air Can be reliably reproduced.

  After the predetermined time has elapsed after the exhaust gas recirculation standby operation is performed and the measured temperature of the exhaust air measured by the first temperature sensor 33 is stabilized, the controller 16 is in any one of the first circulation operation to the third circulation operation. To do. The controller 16 compares the measured temperature of the exhaust air measured by the first temperature sensor 33 with the set temperature of the exhaust air stored in the storage area, and when the measured temperature of the exhaust air becomes equal to or lower than the set temperature (measured temperature). ≦ Set temperature), either the first circulation operation or the second circulation operation is performed. When the measured temperature of the exhaust air exceeds the set temperature (measured temperature> set temperature), the controller 16 performs the third circulation operation. In the first to third circulation operations, similarly to the exhaust gas recirculation standby operation, the dehumidified air that has flowed through the dehumidified region of the desiccant rotor 17 is supplied to the dehumidified air-conditioned space 35 through the processing-side downstream duct 24.

  In the dehumidifying system 10A, when the measured temperature of the exhaust air becomes equal to or lower than the set temperature, a predetermined flow rate of outside air (air-conditioned air) is supplied from the regeneration-side upstream duct 25, and the amount of the outside air flow is regenerated. When discharging from the downstream duct 26 to the outside (outside air), the first circulation operation is performed. In the first circulation operation, the controller 16 transmits an opening degree holding signal to the control unit of the first damper 30 and transmits an opening degree expansion signal to the control unit of the second damper 32. The control unit of the first damper 30 that has received the opening degree holding signal stops the turning of the swirling blades of the first damper 30 and holds the current opening degree. Exhaust air that has passed through the air flow path of the first damper 30 (the amount of the flow of outside air) is discharged to the outside through the regeneration-side downstream duct 26. The control unit of the second damper 32 that has received the opening degree expansion signal turns the swirl blades of the second damper 32 to increase the opening degree and increase the flow rate of the exhaust air flowing through the exhaust air recirculation duct 29.

  A large amount of low-temperature and low-humidity exhaust air flowing into the exhaust air recirculation duct 29 flows into the regeneration upstream duct 25 through the exhaust air recirculation duct 29 as shown by an arrow A1 in FIG. 15 is mixed with a small amount of conditioned air (outside air) adjusted to a predetermined temperature and humidity, and is heated again by the condenser 39 of the first heat exchange mechanism 12 to become heated air. The dehumidifying function of the desiccant rotor 17 is regenerated.

  In the exhaust heat utilization type dehumidification system 10A, when the measured temperature of the exhaust air measured by the first temperature sensor 33 is lower than the set temperature and the first circulation operation is performed, a large amount of exhaust gas in which the temperature and humidity are kept low. Since air can be circulated to the condenser 39 of the first heat exchange mechanism 12 to produce heated air with low humidity, a large amount of outside air adjusted to low temperature and low humidity by the outside air conditioner 15 is subjected to the first heat exchange. It is not necessary to supply air to the mechanism 12, the load on the outside air conditioner 15 can be reduced, and the energy consumed in the outside air conditioner 15 can be reduced to save energy in the system 10A.

  In the dehumidification system 10A, the second circulation operation is performed when the measured temperature of the exhaust air becomes equal to or lower than the set temperature, and when the outside air conditioner 15 is stopped and the supply of the outside air is shut off (stopped). . In the second circulation operation, the controller 16 transmits an opening fully closed signal to the control unit of the first damper 30 and transmits an opening fully open signal to the control unit of the second damper 32. The control unit of the first damper 30 that has received the opening fully closed signal turns the swirl blades of the first damper 30 to fully close the opening to block the air flow path of the first damper 30. The control part of the 2nd damper 32 which received the opening fully open signal turns the turning blade of the 2nd damper 32, and makes the opening fully open.

  All of the exhaust air flows into the exhaust air circulation duct 29 as indicated by an arrow A1 in FIG. All the low-temperature and low-humidity exhaust air flowing into the exhaust air recirculation duct 29 flows into the regeneration upstream duct 25 through the exhaust air recirculation duct 29 and is heated again by the condenser 39 of the first heat exchange mechanism 12. Then, it becomes heated air and flows through the moisture release area 21 of the desiccant rotor 17 to regenerate the dehumidifying function of the desiccant of the desiccant rotor 17.

  In the exhaust heat utilization type dehumidification system 10A, when the measured temperature of the exhaust air measured by the first temperature sensor 33 is equal to or lower than the set temperature and the second circulation operation is performed, all the exhausts in which the low temperature and humidity are maintained. Since air can be circulated to the condenser 39 of the first heat exchange mechanism 12 to produce heated air with low humidity, the outside air adjusted to a low temperature and low humidity by the outside air conditioner 15 is used as the first heat exchange mechanism 12. It is not necessary to supply air to the external air conditioner, the load on the outdoor air conditioner 15 can be reduced, the energy saving of the system 10A can be achieved, and the condenser 39 and the desiccant air conditioner 11 of the first heat exchange mechanism 12 can be achieved. A circulating dehumidification system 10A that operates by exhaust air and heated air that circulates between the (dehumidification mechanism) and the second heat exchange mechanism 14 (coil unit 46) can be realized.

  In the dehumidification system 10A, when the measured temperature of the exhaust air exceeds the set temperature, the third circulation operation is performed. In the third circulation operation, the controller 16 transmits an opening degree holding signal to the control unit of the first damper 30 and transmits an opening degree reduction signal to the control unit of the second damper 32. The control unit of the first damper 30 that has received the opening degree holding signal stops the turning of the swirling blades of the first damper 30 and holds the current opening degree. Exhaust air that has passed through the air flow path of the first damper 30 (the amount of the flow of outside air) is discharged to the outside through the regeneration-side downstream duct 26. The control unit of the second damper 32 that has received the opening degree reduction signal turns the swirl blades of the second damper 32 to reduce the opening degree and reduce the flow rate of the exhaust air flowing through the exhaust air recirculation duct 29.

  A small amount of low-temperature and low-humidity exhaust air that has flowed into the exhaust air recirculation duct 29 flows into the regeneration-side upstream duct 25 through the exhaust air recirculation duct 29 as shown by an arrow A1 in FIG. 15 is mixed with a large amount of conditioned air adjusted to a predetermined temperature and humidity by 15 and heated again by the condenser 39 of the first heat exchange mechanism 12 to become heated air, and flows through the moisture release area 21 of the desiccant rotor 17. The dehumidifying function of the desiccant of the desiccant rotor 17 is regenerated.

  When the measured temperature of the exhaust air exceeds the set temperature and the third circulation operation is performed, the exhaust heat utilization type dehumidification system 10A circulates a small amount of exhaust air having a high temperature and humidity and adjusts it to a predetermined temperature and humidity. By supplying the conditioned air (outside air) to the first heat exchange mechanism 12, the temperature of the exhaust air can be returned to the set temperature or less, and the load on the heat pump unit 37 of the first heat exchange mechanism 12 is reduced. Thus, the temperature of the exhaust air can be stabilized in the vicinity of the set temperature while saving energy of the system 10A, and can be quickly shifted from the third circulation operation to one of the first and second circulation operation speeds. .

  The exhaust heat utilization type dehumidification system 10 </ b> A (including the exhaust heat utilization type dehumidification systems 10 </ b> B to 10 </ b> D) extends to the regeneration side upstream duct 25 extending to the upstream side of the first heat exchange mechanism 12 and to the downstream side of the second heat exchange mechanism 14. The regeneration-side downstream duct 26 is connected by an exhaust air recirculation duct 29, and the low-temperature and low-humidity exhaust air that has been dehumidified while the temperature is decreased by the second heat exchange mechanism 14 (coil unit 46) is the first heat exchange mechanism. The exhaust air is caused to flow into the regeneration side upstream duct 25 extending to the upstream side of 12, and the exhaust air is caused to flow into the condenser 39 of the first heat exchange mechanism 12, and the exhaust air is heated again by the first heat exchange mechanism 12 and heated. Since the air is made and the dehumidifying function of the dehumidifying agent is regenerated by the heated air, the exhaust air whose temperature and humidity are reduced by the coil unit 46 can be reused. It is possible to save energy of the system 10A.

  The exhaust heat utilization type dehumidification system 10A (including the exhaust heat utilization type dehumidification systems 10B to 10D) supplies the desiccant air conditioner 11 (dehumidification mechanism) with the heated air obtained by heating the low-humidity exhaust air so that the desiccant rotor 17 is supplied. The dehumidifying function of the dehumidifying agent can be sufficiently regenerated, and the dehumidified air produced by the desiccant air conditioner 11 can be supplied to the dehumidified air-conditioned space 35.

  FIG. 7 is a configuration diagram of an exhaust heat utilization type dehumidification system 10B shown as another example, and FIG. 8 is a diagram illustrating an exhaust recirculation standby operation of the exhaust heat utilization type dehumidification system 10B. FIG. 9 is a diagram illustrating the first circulation operation or the third circulation operation of the exhaust heat utilization type dehumidification system 10B, and FIG. 10 is a diagram illustrating the second circulation operation of the exhaust heat utilization type dehumidification system 10B. . 7-10, illustration of the dehumidification air-conditioning space 35 is abbreviate | omitted. 8 to 10, the flow of heated air and exhaust air in the ducts 25, 26, 29 and the desiccant air conditioner 11 is indicated by an arrow A 1, and the outside air, dehumidified air, and ring in the ducts 22, 23, 24 and the desiccant air conditioner 11 are shown. The flow of air is indicated by arrow A2.

  This exhaust heat utilization type dehumidification system 10B is different from that in FIG. 1 in that a refrigerant bypass pipe 48, a three-way valve 49 (valve mechanism), and a second temperature sensor 50 are installed in the refrigerant circulation pipe 44. 1 is the same as that of the dehumidifying system 10A in FIG. 1, and therefore, the same reference numerals as those in FIG. 1 are attached and the description of the dehumidifying system 10A in FIG. .

  The waste heat utilization type dehumidification system 10B is the same as the system 10A of FIG. 1, and the desiccant air conditioner 11, the first heat exchange mechanism 12, the heater 13, the second heat exchange mechanism 14, the outside air conditioner 15, the controller 16, and the processing side. Upstream duct 22, dehumidification space circulation duct 23, processing side downstream duct 24, regeneration side upstream duct 25, regeneration side downstream duct 26, exhaust air circulation duct 29, first and second dampers 30 and 32, and temperature sensors 33 and 34 The heat exchanger 38 and the circulation pump 45 are provided. The storage area of the controller 16 stores a set temperature of heated air (about 120 to about 130 ° C.), a set temperature of exhaust air (for example, 12 ° C.), and a set temperature of refrigerant (for example, 12 ° C.). Each set temperature can be arbitrarily set.

  The refrigerant bypass pipe 48 is connected to a refrigerant circulation pipe 44 extending in the vicinity of the second heat exchange mechanism 14 (coil unit 46). The refrigerant bypass pipe 48 causes the refrigerant to flow therethrough, and causes the refrigerant to circulate through the heat exchange coil 43 (first heat exchange mechanism) of the heat exchanger 38 without causing the refrigerant to flow through the coil unit 46. The three-way valve 49 is installed in a refrigerant circulation pipe 44 and a refrigerant bypass pipe 48 that extend in the vicinity of the coil unit 46. The three-way valve 49 adjusts the flow rate of the refrigerant passed through the coil unit 46 and the flow rate of the refrigerant passed through the refrigerant bypass pipe 48. The control unit (not shown) of the three-way valve 49 is connected to the controller 16 via the control signal line 31.

  The second temperature sensor 50 is installed in the refrigerant circulation pipe 44 extending between the refrigerant outlet and the refrigerant bypass pipe 48 in the second heat exchange mechanism 14 (coil unit 46). The second temperature sensor 50 is connected to the controller 16 via the control signal line 31. The second temperature sensor 50 measures the temperature of the refrigerant flowing out from the refrigerant outlet of the heat exchange coil 46 of the second heat exchange mechanism 14, and transmits the measured refrigerant temperature (measured temperature) to the controller 16.

  When the system start switch of the controller 16 is turned on, the dehumidification system 10B is started. When the dehumidifying system 10B is activated, the desiccant air conditioner 11, the first heat exchange mechanism 12 (heat pump unit 37), the heater 13, the second heat exchange mechanism 14 (coil unit 46), the outside air conditioner 15, the first and second dampers. 30, 32, temperature sensors 33, 34, 50, circulation pump 45, and three-way valve 49 are activated. The supply blower 27 and the exhaust blower 28 are activated, and the desiccant rotor 17 starts to rotate in one direction. The refrigerant circulates through the refrigerant circulation pipe 44, and the refrigerant circulates through the forward pipe 41 and the return pipe 42. The temperature sensor 34 starts measuring the temperature of the heated air flowing through the dehumidifying function regeneration zone 19, the first temperature sensor 33 starts measuring the temperature of the exhaust air flowing through the regeneration-side downstream duct 26, and the second temperature. The sensor 50 starts measuring the temperature of the refrigerant flowing out from the refrigerant outlet of the coil unit 46.

  In the dehumidification system 10B, the exhaust gas recirculation standby operation (system preliminary operation) is performed at the time of activation. The exhaust gas recirculation standby operation is the same as that of the dehumidification system 10A of FIG. 1, and the effect of the exhaust gas recirculation standby operation is the same as that of the dehumidification system 10A of FIG. The flow of the outside air, the conditioned air, the heated air, and the exhaust air in each of the ducts 25 and 26 during the exhaust gas recirculation standby operation is the same as that of FIG. Further, the flow of the outside air, the conditioned air, the dehumidified air, and the circulating air in each of the ducts 22 to 24 during the exhaust gas recirculation standby operation is the same as that of FIG. 4 as indicated by an arrow A2 in FIG. The controller 16 performs feedback control or feedforward control on the compressor 36 and the heater 13 of the heat pump unit 37 so that the measured temperature of the heated air measured by the temperature sensor 34 falls within the set temperature range.

  In the heat exchanger 38 of the first heat exchange mechanism 12, heat exchange is performed between the evaporator 40 of the heat pump unit 37 and the heat exchange coil 43, and the refrigerant (about 12) flowing into the heat exchange coil 43 from the refrigerant circulation pipe 44. Water or brine at 0 ° C.) is cooled to a predetermined temperature (about 7 ° C.), and the refrigerant flows out again into the refrigerant circulation pipe 44 and is sent to the second heat exchange mechanism 14 (coil unit 46) through the refrigerant circulation pipe 44. It is done. The exhaust heat of the exhaust air is recovered by the coil unit 46, and the recovered exchange heat is conveyed to the heat exchange coil 43 of the heat exchanger 38 by the refrigerant. As in the system 10 </ b> A in FIG. 1, the exhaust heat recovered from the exhaust air is used for heating the air in the heat pump unit 37.

  The controller 16 compares the measured temperature of the refrigerant measured by the second temperature sensor 50 with the set temperature of the refrigerant stored in the storage area during the exhaust gas recirculation standby operation, and the refrigerant measured by the second temperature sensor 50 When the measured temperature is equal to or higher than the set temperature, a reduction signal of the valve opening on the refrigerant bypass pipe 48 side is transmitted to the control unit of the three-way valve 49, and an expansion signal of the valve opening on the refrigerant circulation pipe 44 side is transmitted. Send. The control unit of the three-way valve 49 that has received the reduction signal and the expansion signal of the valve opening reduces the valve opening on the refrigerant bypass pipe 48 side to reduce the flow rate of the refrigerant flowing into the refrigerant bypass pipe 48, The valve opening degree on the side of the reflux pipe 44 is increased to increase the flow rate of the refrigerant flowing into the second heat exchange mechanism 14 (coil unit 46).

  The exhaust heat utilization type dehumidification system 10B increases the flow rate of the refrigerant flowing into the second heat exchange mechanism 14 (coil unit 46) when the measured temperature of the refrigerant becomes equal to or higher than the set temperature during the exhaust gas recirculation standby operation. Thus, the temperature adjusting function and the dehumidifying function in the heat exchange coil 46 can be utilized to the maximum, so that the temperature and humidity of the exhaust air can be reliably reduced by the coil unit 46 and the temperature of the exhaust air can be reduced. The temperature can be quickly stabilized in the vicinity of the set temperature, and after the exhaust gas recirculation standby operation, the first and second circulation operations and the third circulation operation can be smoothly shifted to.

  When the measured temperature of the refrigerant measured by the second temperature sensor 50 is lower than the set temperature during the exhaust gas recirculation standby operation, the controller 16 opens the valve on the refrigerant bypass pipe 48 side to the control unit of the three-way valve 49. Is transmitted, and a reduction signal of the valve opening on the refrigerant circulation pipe 44 side is transmitted. The controller of the three-way valve 49 that has received the expansion signal and the reduction signal of the valve opening increases the valve opening on the refrigerant bypass pipe 48 side to increase the flow rate of the refrigerant flowing into the refrigerant bypass pipe 48. The valve opening on the side of the reflux pipe 44 is reduced to reduce the flow rate of the refrigerant flowing into the second heat exchange mechanism 14 (coil unit 46).

  The exhaust heat utilization type dehumidification system 10B reduces the flow rate of the refrigerant flowing into the second heat exchange mechanism 14 (coil unit 46) when the measured temperature of the refrigerant becomes lower than the set temperature during the exhaust gas recirculation standby operation. Thus, the heating capacity of the first heat exchange mechanism 12 using the heat pump unit 37 is lowered, for example, when the regeneration temperature of the dehumidifying function of the desiccant of the desiccant rotor 17 is low, the temperature of the heated air can be lowered, The dehumidifying function of the dehumidifying agent can be recovered while suppressing the energy consumed in the first heat exchange mechanism 12.

  After the predetermined time has elapsed after the exhaust gas recirculation standby operation is performed and the measured temperature of the exhaust air measured by the first temperature sensor 33 is stabilized, the controller 16 is in any one of the first circulation operation to the third circulation operation. To do. The controller 16 compares the measured temperature of the exhaust air measured by the first temperature sensor 33 with the set temperature of the exhaust air stored in the storage area, and when the measured temperature of the exhaust air becomes equal to or lower than the set temperature (measured temperature). ≦ Set temperature), either the first circulation operation or the second circulation operation is performed. When the measured temperature of the exhaust air exceeds the set temperature (measured temperature> set temperature), the controller 16 performs the third circulation operation.

  In the first to third circulation operations, similarly to the exhaust gas recirculation standby operation, the dehumidified air that has flowed through the dehumidified region of the desiccant rotor 17 is supplied to the dehumidified air-conditioned space 35 through the processing-side downstream duct 24. During the execution of the first to third circulation operations, the opening degree of the three-way valve 49 is held at the current opening degree, and the flow rate of the refrigerant in the three-way valve 49 is kept constant. Therefore, the flow rate of the refrigerant flowing into the refrigerant bypass pipe 48 and the flow rate of the refrigerant flowing into the second heat exchange mechanism 14 (coil unit 46) are kept constant. Since the dehumidification system 10B keeps the flow rate of the refrigerant in the three-way valve 49 constant when performing any of the first to third circulation operations, the refrigerant flow in the three-way valve 49 is performed during the execution of the first to third circulation operations. Compared with the case where the flow rate is changed, the adjustment control of the three-way valve 49 (valve mechanism) and the adjustment control of the dampers 30 and 32 can be coordinated.

  The first to third circulation operations are the same as those of the dehumidification system 10A of FIG. 1, and the effects of the first to third circulation operations are the same as those of the dehumidification system 10A of FIG. The flow of the outside air, the conditioned air, the heated air, and the exhaust air in each of the ducts 25 and 26 during the first circulation operation or the third circulation operation is the same as that of FIG. 5 as indicated by an arrow A1 in FIG. Further, the flow of the outside air, the conditioned air, the dehumidified air, and the ambient air in each of the ducts 22 to 24 during the first circulation operation or the third circulation operation is the same as that of FIG. It is. The flow of the outside air, the conditioned air, the heated air, and the exhaust air in each of the ducts 25 and 26 during the second circulation operation is the same as that of FIG. 6, as indicated by an arrow A1 in FIG. Further, the flow of outside air, conditioned air, dehumidified air, and circulating air in the respective ducts 22 to 24 during the second circulation operation is the same as that of FIG. 6 as indicated by an arrow A2 in FIG.

  When the measured temperature of the refrigerant measured by the second temperature sensor 50 becomes equal to or higher than the set temperature during the execution of any one of the first to third circulation operations, the controller 16 controls the first and second dampers 30 and 32. An opening degree holding signal is transmitted to the control unit, a reduction signal of the valve opening degree on the refrigerant bypass pipe 48 side is transmitted to the control part of the three-way valve 49, and an enlarged signal of the valve opening degree on the refrigerant circulation pipe 44 side is transmitted. Send. The control unit of the first and second dampers 30 and 32 that has received the opening degree holding signal stops the turning of the swirling blades of the first and second dampers 30 and 32, and the current opening degree (the first damper 30 is fully closed). ). The control unit of the three-way valve 49 that has received the reduction signal and the expansion signal of the valve opening reduces the valve opening on the refrigerant bypass pipe 48 side to reduce the flow rate of the refrigerant flowing into the refrigerant bypass pipe 48, The valve opening degree on the side of the reflux pipe 44 is increased to increase the flow rate of the refrigerant flowing into the second heat exchange mechanism 14 (coil unit 46).

  The exhaust heat utilization type dehumidification system 10B flows into the second heat exchange mechanism 14 (coil unit 46) when the measured temperature of the refrigerant becomes equal to or higher than the set temperature during any one of the first to third circulation operations. By increasing the flow rate of the refrigerant, the temperature adjustment function and the dehumidification function in the coil unit 46 can be utilized to the maximum, and the temperature and humidity of the exhaust air can be reliably reduced by the coil unit 46. The exhaust air whose temperature and humidity are reduced by the unit 46 can be efficiently reused.

  When the measured temperature of the refrigerant measured by the second temperature sensor 50 becomes lower than the set temperature during the execution of any one of the first to third circulation operations, the controller 16 controls the first and second dampers 30 and 32. An opening degree holding signal is transmitted to the control unit, a valve opening degree enlargement signal on the refrigerant bypass pipe 48 side is sent to the control part of the three-way valve 49, and a valve opening degree reduction signal on the refrigerant circulation pipe 44 side is sent. Send. The control part of the 1st and 2nd dampers 30 and 32 which received the opening degree holding signal stops turning of the turning blades of the first and second dampers 30 and 32 and holds the current opening degree. The controller of the three-way valve 49 that has received the expansion signal and the reduction signal of the valve opening increases the valve opening on the refrigerant bypass pipe 48 side to increase the flow rate of the refrigerant flowing into the refrigerant bypass pipe 48. The valve opening on the side of the reflux pipe 44 is reduced to reduce the flow rate of the refrigerant flowing into the second heat exchange mechanism 14 (coil unit 46).

  The exhaust heat utilization type dehumidification system 10B flows into the second heat exchange mechanism 14 (coil unit 46) when the measured temperature of the refrigerant becomes lower than the set temperature during any one of the first to third circulation operations. Since the flow rate of the refrigerant is reduced, the heating capacity of the first heat exchange mechanism 12 using the heat pump unit 37 is lowered. For example, the temperature of the heated air is lowered when the regeneration temperature of the dehumidifying function of the desiccant rotor 17 is low. The dehumidifying function of the dehumidifying agent can be recovered while suppressing the energy consumed in the first heat exchange mechanism 12. When adjusting the three-way valve 49 to adjust the flow rate of the refrigerant flowing into the coil unit 46 and the refrigerant bypass pipe 44, the exhaust heat utilization type dehumidification system 10B maintains the opening degree of each of the dampers 30 and 32 at a predetermined opening degree. Therefore, hunting of the system 10B can be prevented as compared with the case where the opening degree of each damper 30, 32 is changed during the adjustment of the three-way valve 49.

  It should be noted that any one of the first circulation operation to the third circulation operation is performed after a predetermined time has elapsed after the refrigerant flow rate is adjusted by the three-way valve 49 and the measured temperature of the refrigerant measured by the second temperature sensor 50 is stabilized. Implement (restart). In this case, the opening degree of the three-way valve 49 is maintained at the current opening degree, and the flow rate of the refrigerant in the three-way valve 49 is kept constant.

  FIG. 11 is a configuration diagram of an exhaust heat utilization type dehumidification system 10C shown as another example, and FIG. 12 is a diagram illustrating an exhaust gas recirculation standby operation of the exhaust heat utilization type dehumidification system 10C. FIG. 13 is a diagram for explaining the first circulation operation or the second circulation operation of the exhaust heat utilization type dehumidification system 10C. In FIG. 11 to FIG. 13, illustration of the dehumidifying conditioned space 35 is omitted. In FIGS. 11 to 13, the flow of heated air and exhaust air in the ducts 25, 26, 29 and the desiccant air conditioner 11 is indicated by an arrow A <b> 1. The flow of the air is indicated by an arrow A2, and the flow of the purge air in the purge air introduction duct 51 is indicated by an arrow A3.

  The dehumidifying system 10C differs from that shown in FIG. 1 in that a purge air introduction duct 51 is installed in the regeneration-side upstream duct 25, an air exhaust duct 52 is installed in the regeneration-side downstream duct 26, and an air exhaust duct 52 is installed. Since the third damper 53 is installed and the other configurations are the same as those of the dehumidifying system 10A in FIG. 1, the same reference numerals as those in FIG. 1 are attached, and the dehumidifying system 10A in FIG. The detailed description about other structures is omitted by using.

  The dehumidification system 10C is similar to the system 10A of FIG. 1, and includes a desiccant air conditioner 11, a first heat exchange mechanism 12, a heater 13, a second heat exchange mechanism 14, an outside air conditioner 15, a controller 16, a processing-side upstream duct 22, Dehumidification space recirculation duct 23, treatment side downstream duct 24, regeneration side upstream duct 25, regeneration side downstream duct 26, exhaust air recirculation duct 29, first and second dampers 30, 32, temperature sensors 33, 34, heat exchanger 38 , A circulation pump 45 is provided. The storage area of the controller 16 stores the set temperature of heated air (about 120 to about 130 ° C.) and the set temperature of exhaust air (for example, 12 ° C.). Each set temperature can be arbitrarily set.

  The purge air introduction duct 51 includes a purge region of the desiccant rotor 17 (dehumidification mechanism) located in the dehumidification treatment zone 18 and an upstream side of the first heat exchange mechanism 12 (condenser 39) (the condenser 39 of the first heat exchange mechanism 12). And the regeneration-side upstream duct 25 extending between the exhaust air circulation duct 29). The purge air introduction duct 51 circulates purge air at a predetermined temperature (about 80 to 90 ° C.) flowing through the purge region of the desiccant rotor 17 in the dehumidification treatment zone from the desiccant rotor 17 to the regeneration-side upstream duct 25.

  The air exhaust duct 52 is connected to the regeneration-side downstream duct 26 extending between the dehumidification function regeneration zone 19 and the second heat exchange mechanism 14 (coil unit 46). The air exhaust duct 52 discharges mixed air of purge air and outside air that has flowed into the regeneration-side upstream duct 25 to the outside (outside air). The third damper 53 (third motor damper) is installed in the air exhaust duct 52 and adjusts the flow rate of mixed air (mixed air of purge air and outside air) exhausted from the exhaust duct 52. The third damper 53 has a control unit (not shown) connected to the controller 16 via the control signal line 31.

  When the system start switch of the controller 16 is turned ON, the dehumidification system 10C is started. When the dehumidifying system 10C is activated, the desiccant air conditioner 11, the first heat exchange mechanism 12 (heat pump unit 37), the heater 13, the second heat exchange mechanism 14 (coil unit 46), the outside air conditioner 15, and the first to third dampers. 30, 32, 53, temperature sensors 33, 34, and circulation pump 45 are activated. The supply blower 27 and the exhaust blower 28 are activated, and the desiccant rotor 17 starts to rotate in one direction. The refrigerant circulates through the refrigerant circulation pipe 44, and the refrigerant circulates through the forward pipe 41 and the return pipe 42. The temperature sensor 34 starts measuring the temperature of the heated air flowing through the dehumidifying function regeneration zone 19, and the first temperature sensor 33 starts measuring the temperature of the exhaust air flowing through the regeneration-side downstream duct 26.

  In the dehumidifying system 10 </ b> C, the exhaust gas circulation standby operation (system preliminary operation) is performed at the time of activation. In the exhaust gas recirculation standby operation, the controller 16 transmits an opening fully open signal to the control unit of the first damper 30 and transmits an opening fully closed signal to the control unit of the second damper 32 and the control unit of the third damper 53. . The control unit of the first damper 30 turns the swirl vanes of the first damper 30 to open (fully open) the air flow path of the damper 30 to maximize the flow rate of the exhaust air exhausted from the regeneration-side downstream duct 26. The control unit of the second damper 32 turns the swirl vanes of the second damper 32 to close (fully close) the air flow path of the damper 32, thereby blocking the inflow of exhaust air to the exhaust air recirculation duct 29. The control unit of the third damper 53 turns the swirl vane of the third damper 53 to close (fully close) the air flow path of the damper 53, thereby blocking the inflow of exhaust air to the air exhaust duct 52.

  The flow of outside air, conditioned air, heated air, and exhaust air in the ducts 25 and 26 during the exhaust recirculation standby operation is the same as that of FIG. 4 as indicated by an arrow A1 in FIG. Further, the flow of the outside air, the conditioned air, the dehumidified air, and the circulating air in each of the ducts 22 to 24 during the exhaust gas recirculation standby operation is the same as that of FIG. 4 as indicated by an arrow A2 in FIG. The purge air exhausted from the purge region of the desiccant rotor 17 passes through the purge air introduction duct 51 from the dehumidification treatment zone and the condenser 39 of the first heat exchange mechanism 12 and the exhaust air recirculation as shown by an arrow A3 in FIG. It flows into the regeneration-side upstream duct 25 extending between the duct 29 and mixed with outside air (conditioned air). The controller 16 performs feedback control or feedforward control on the compressor 36 and the heater 13 of the heat pump unit 37 so that the measured temperature of the heated air measured by the temperature sensor 34 falls within the set temperature range.

  In the heat exchanger 38 of the first heat exchange mechanism 12, heat exchange is performed between the evaporator 40 of the heat pump unit 37 and the heat exchange coil 43, and the refrigerant (about 12) flowing into the heat exchange coil 43 from the refrigerant circulation pipe 44. Water or brine at 0 ° C.) is cooled to a predetermined temperature (about 7 ° C.), and the refrigerant flows out again into the refrigerant circulation pipe 44 and is sent to the second heat exchange mechanism 14 (coil unit 46) through the refrigerant circulation pipe 44. It is done. The exhaust heat of the exhaust air is recovered by the second heat exchange mechanism 14, and the recovered exchange heat is conveyed to the heat exchange coil 43 of the heat exchanger 38 by the refrigerant. As in the system 10 </ b> A in FIG. 1, the exhaust heat recovered from the exhaust air is used for heating the air in the heat pump unit 37.

  The controller 16 performs either the first circulation operation or the second circulation operation after a predetermined time has elapsed after the exhaust gas recirculation standby operation is performed and the measured temperature of the exhaust air measured by the first temperature sensor 33 is stabilized. carry out. The controller 16 compares the measured temperature of the exhaust air measured by the first temperature sensor 33 with the set temperature of the exhaust air stored in the storage area, and when the measured temperature of the exhaust air becomes equal to or lower than the set temperature (measured temperature). ≦ Set temperature), the first circulation operation is performed. When the measured temperature of the exhaust air exceeds the set temperature (measured temperature> set temperature), the controller 16 performs the second circulation operation. In the first and second circulation operations, as in the exhaust gas recirculation standby operation, the dehumidified air that has flowed through the dehumidified area of the desiccant rotor 17 is supplied to the dehumidified air-conditioned space 35 through the processing-side downstream duct 24.

  In the first circulation operation, the controller 16 transmits an opening degree fully-closed signal to the control unit of the first damper 30, transmits an opening degree holding signal to the control unit of the third damper 53, and controls the control unit of the second damper 32. Sends an opening enlargement signal. The control part of the 1st damper 30 which received the opening fully closed signal turns the swirl | wing blade of the 1st damper 30, closes the air flow path of the damper 30 (fully closed), and outdoor (from the reproduction | regeneration side downstream duct 26 ( Shut off the exhaust air to the outside air.

  The control unit of the third damper 53 that has received the opening degree holding signal stops the turning of the swirling blades of the third damper 53, maintains the current opening degree, and exhausts air (purge air and exhaust air) that is exhausted from the purge air exhaust duct. The flow rate of the mixed air with the outside air) is maintained at a predetermined (current) flow rate. Exhaust air that has passed through the air flow path of the third damper 53 (a portion of the flow rate of the mixed air of purge air and outside air) is released to the outdoors through the air exhaust duct 52. The control unit of the second damper 32 that has received the opening degree expansion signal turns the swirl blades of the second damper 32 to increase the opening degree and increase the flow rate of the exhaust air flowing through the exhaust air recirculation duct 29.

  A large amount of low-temperature and low-humidity exhaust air flowing into the exhaust air recirculation duct 29 flows into the regeneration upstream duct 25 through the exhaust air recirculation duct 29 as shown by an arrow A1 in FIG. 15 is mixed with a small amount of conditioned air (outside air) adjusted to a predetermined temperature and humidity, and is heated again by the condenser 39 of the first heat exchange mechanism 12 to become heated air, and the moisture release area 21 of the desiccant rotor 17 is changed. The dehumidifying function of the desiccant rotor 17 is regenerated. As indicated by an arrow A 3 in FIG. 13, the purge air passes through the purge air introduction duct 51 from the dehumidification treatment zone and extends between the condenser 39 of the first heat exchange mechanism 12 and the exhaust air circulation duct 29. It flows into the duct 25.

  In the exhaust heat utilization type dehumidification system 10C, when the measured temperature of the exhaust air measured by the first temperature sensor 33 is lower than the set temperature and the first circulation operation is performed, the temperature and humidity excluding the purge air are low. Since all the exhaust air can be circulated to the condenser 39 of the first heat exchange mechanism 12 to produce heated air with low humidity, the outside air adjusted to a low temperature and low humidity by the outside air conditioner 15 is converted into the first heat. There is no need to supply air to the exchange mechanism 12, the load on the outdoor air conditioner 15 can be reduced, and not only can the system 10C save energy, but also the condenser 39 and the desiccant of the first heat exchange mechanism 12 Realizing a circulating dehumidification system 10C operated by exhaust air and heated air circulating through the air conditioner 11 (dehumidification mechanism) and the second heat exchange mechanism 14 (coil unit 46). Kill.

  In the second circulation operation, the controller 16 transmits an opening degree fully closed signal to the control unit of the first damper 30, transmits an opening degree holding signal to the control unit of the third damper 53, and controls the control unit of the second damper 32. Sends an opening reduction signal. The control part of the 1st damper 30 which received the opening fully closed signal turns the swirl | wing blade of the 1st damper 30, closes the air flow path of the damper 30 (fully closed), and outdoor (from the reproduction | regeneration side downstream duct 26 ( Shut off the exhaust air to the outside air.

  The control unit of the third damper 53 that has received the opening degree holding signal stops the turning of the swirling blades of the third damper 53, maintains the current opening degree, and exhausts air (purge air and exhaust air) that is exhausted from the purge air exhaust duct. The flow rate of the mixed air with the outside air is maintained at a predetermined flow rate. Exhaust air that has passed through the air flow path of the third damper 53 (the amount of the purge air flow) is discharged to the outside through the air exhaust duct 52. The control unit of the second damper 32 that has received the opening degree reduction signal turns the swirl blades of the second damper 32 to reduce the opening degree and simultaneously reduce the flow rate of the exhaust air flowing through the exhaust air circulation duct 29. The flow rate of the exhaust air flowing through the air exhaust duct 52 is increased.

  A small amount of low-temperature and low-humidity exhaust air that has flowed into the exhaust air recirculation duct 29 flows into the regeneration upstream duct 25 through the exhaust air recirculation duct 29 as shown by arrow A1 in FIG. 15 is mixed with a large amount of conditioned air adjusted to a predetermined temperature and humidity by 15 and heated again by the condenser 39 of the first heat exchange mechanism 12 to become heated air, and flows through the moisture release area 21 of the desiccant rotor 17. The dehumidifying function of the desiccant of the desiccant rotor 17 is regenerated.

  When the measured temperature of the exhaust air exceeds the set temperature and the second circulation operation is performed, the exhaust heat utilization type dehumidification system 10C circulates a small amount of exhaust air having a high temperature and humidity and adjusts it to a predetermined temperature and humidity. By supplying the conditioned air (outside air) to the first heat exchange mechanism 12, the temperature of the exhaust air can be returned to the set temperature or less, and the load on the heat pump unit 37 of the first heat exchange mechanism 12 is reduced. As a result, the temperature of the exhaust air can be stabilized in the vicinity of the set temperature while saving energy of the system 10C, and the second circulation operation can be quickly shifted to the first circulation operation speed.

  FIG. 14 is a configuration diagram of an exhaust heat utilization type dehumidification system 10D shown as another example, and FIG. 15 is a diagram illustrating an exhaust recirculation standby operation of the exhaust heat utilization type dehumidification system 10D. FIG. 16 is a diagram for explaining the first circulation operation or the second circulation operation of the exhaust heat utilization dehumidification system 10D. 14-16, illustration of the dehumidification air-conditioning space 35 is abbreviate | omitted. 14-16, the flow of the heating air and exhaust air in the ducts 25, 26, 29 and the desiccant air conditioner 11 is indicated by an arrow A1, and the outside air, dehumidified air and the ring in the ducts 22, 23, 24 and the desiccant air conditioner 11 are shown. The flow of the air is indicated by an arrow A2, and the flow of the purge air in the purge air introduction duct 51 is indicated by an arrow A3.

  The dehumidifying system 10D differs from that in FIG. 1 in that a refrigerant bypass pipe 48, a three-way valve 49 (valve mechanism), and a second temperature sensor 50 are installed in the refrigerant circulation pipe 44, and the regeneration upstream duct 25 is purged. An air introduction duct 51 is installed, an air exhaust duct 52 is installed in the regeneration-side downstream duct 26, and a third damper 53 is installed in the air exhaust duct 52. The other configuration is shown in FIG. Since it is the same as those of the dehumidifying system 10A, the same reference numerals as those in FIG. 1 are attached, and the description of the other configurations is omitted by using the description of the dehumidifying system 10A in FIG.

  The dehumidifying system 10D is similar to the system 10A of FIG. 1, the desiccant air conditioner 11, the first heat exchange mechanism 12, the heater 13, the second heat exchange mechanism 14, the outside air conditioner 15, the controller 16, the processing side upstream duct 22, Dehumidification space recirculation duct 23, treatment side downstream duct 24, regeneration side upstream duct 25, regeneration side downstream duct 26, exhaust air recirculation duct 29, first and second dampers 30, 32, temperature sensors 33, 34, heat exchanger 38 , A circulation pump 45 is provided. The storage area of the controller 16 stores a set temperature of heated air (about 120 to about 130 ° C.), a set temperature of exhaust air (for example, 12 ° C.), and a set temperature of refrigerant (for example, 12 ° C.). Each set temperature can be arbitrarily set.

  Since the refrigerant bypass pipe 48, the three-way valve 49, and the second temperature sensor 50 are the same as those of the system 10B of FIG. 7, the same reference numerals as those of the system 10B of FIG. 7 are given, and the description of FIG. Thus, description of the refrigerant bypass pipe 48, the three-way valve 49, and the second temperature sensor 50 is omitted. Since the purge air introduction duct 51, the air exhaust duct 52, and the third damper 53 are the same as those of the system 10C of FIG. 11, the same reference numerals as those of the system 10C of FIG. 11 are given, and the description of FIG. Thus, the description of the purge air introduction duct 51, the air exhaust duct 52, and the third damper 53 is omitted.

  When the system start switch of the controller 16 is turned ON, the dehumidification system 10D is started. When the dehumidifying system 10D is activated, the desiccant air conditioner 11, the first heat exchange mechanism 12 (heat pump unit 37), the heater 13, the second heat exchange mechanism 14 (coil unit 46), the outside air conditioner 15, and the first to third dampers. 30, 32, 53, temperature sensors 33, 34, 50, circulation pump 45, and three-way valve 49 are activated. The supply blower 27 and the exhaust blower 28 are activated, and the desiccant rotor 17 starts to rotate in one direction. The refrigerant circulates through the refrigerant circulation pipe 44, and the refrigerant circulates through the forward pipe 41 and the return pipe 42. The temperature sensor 34 starts measuring the temperature of the heated air flowing through the dehumidifying function regeneration zone 19, the first temperature sensor 33 starts measuring the temperature of the exhaust air flowing through the regeneration-side downstream duct 26, and the second temperature. The sensor 50 starts measuring the temperature of the refrigerant flowing out from the refrigerant outlet of the coil unit 46.

  In the dehumidification system 10D, an exhaust gas recirculation standby operation (system preliminary operation) is performed at the time of activation. The exhaust recirculation standby operation is the same as that of the dehumidification system 10C in FIG. 11, and the effect of the exhaust recirculation standby operation is the same as that of the dehumidification system 10C in FIG. The flow of outside air, conditioned air, heated air, and exhaust air in the ducts 25 and 26 during the exhaust recirculation standby operation is the same as that of FIG. 12, as indicated by an arrow A1 in FIG. Further, the flow of the outside air, the conditioned air, the dehumidified air, and the circulating air in each of the ducts 22 to 24 during the exhaust gas recirculation standby operation is the same as that of FIG. 12, as indicated by an arrow A2 in FIG.

  The purge air exhausted from the purge region of the desiccant rotor 17 passes through the purge air introduction duct 51 from the dehumidification treatment zone and the condenser 39 of the first heat exchange mechanism 12 and the exhaust air recirculation as shown by an arrow A3 in FIG. It flows into the regeneration-side upstream duct 25 extending between the duct 29 and mixed with outside air (conditioned air). The controller 16 performs feedback control or feedforward control on the compressor 36 and the heater 13 of the heat pump unit 37 so that the measured temperature of the heated air measured by the temperature sensor 34 falls within the set temperature range.

  In the heat exchanger 38 of the first heat exchange mechanism 12, heat exchange is performed between the evaporator 40 of the heat pump unit 37 and the heat exchange coil 43, and the refrigerant (about 12) flowing into the heat exchange coil 43 from the refrigerant circulation pipe 44. Water or brine at 0 ° C.) is cooled to a predetermined temperature (about 7 ° C.), and the refrigerant flows out again into the refrigerant circulation pipe 44 and is sent to the second heat exchange mechanism 14 (coil unit 46) through the refrigerant circulation pipe 44. It is done. The exhaust heat of the exhaust air is recovered by the second heat exchange mechanism 12, and the recovered exchange heat is conveyed to the heat exchange coil 43 of the heat exchanger 38 by the refrigerant. As in the system 10 </ b> A in FIG. 1, the exhaust heat recovered from the exhaust air is used for heating the air in the heat pump unit 37.

  The controller 16 compares the measured temperature of the refrigerant measured by the second temperature sensor 50 with the set temperature of the refrigerant stored in the storage area during the exhaust gas recirculation standby operation, and the refrigerant measured by the second temperature sensor 50 When the measured temperature is equal to or higher than the set temperature, a reduction signal of the valve opening on the refrigerant bypass pipe 48 side is transmitted to the control unit of the three-way valve 49, and an expansion signal of the valve opening on the refrigerant circulation pipe 44 side is transmitted. Send. The control unit of the three-way valve 49 that has received the reduction signal and the expansion signal of the valve opening reduces the valve opening on the refrigerant bypass pipe 48 side to reduce the flow rate of the refrigerant flowing into the refrigerant bypass pipe 48, The valve opening degree on the side of the reflux pipe 44 is increased to increase the flow rate of the refrigerant flowing into the second heat exchange mechanism 14 (coil unit 46).

  The exhaust heat utilization type dehumidification system 10D increases the flow rate of the refrigerant flowing into the second heat exchange mechanism 14 (coil unit 46) when the measured temperature of the refrigerant becomes equal to or higher than the set temperature during the exhaust gas recirculation standby operation. Thus, the temperature adjusting function and the dehumidifying function in the heat exchange coil 46 can be utilized to the maximum, so that the temperature and humidity of the exhaust air can be reliably reduced by the coil unit 46 and the temperature of the exhaust air can be reduced. The temperature can be quickly stabilized in the vicinity of the set temperature, and the system can smoothly shift to the first circulation operation and the second circulation operation after the system startup operation.

  When the measured temperature of the refrigerant measured by the second temperature sensor 50 is lower than the set temperature during the exhaust gas recirculation standby operation, the controller 16 opens the valve on the refrigerant bypass pipe 48 side to the control unit of the three-way valve 49. Is transmitted, and a reduction signal of the valve opening on the refrigerant circulation pipe 44 side is transmitted. The controller of the three-way valve 49 that has received the expansion signal and the reduction signal of the valve opening increases the valve opening on the refrigerant bypass pipe 48 side to increase the flow rate of the refrigerant flowing into the refrigerant bypass pipe 48. The valve opening on the side of the reflux pipe 44 is reduced to reduce the flow rate of the refrigerant flowing into the second heat exchange mechanism 14 (coil unit 46).

  The exhaust heat utilization type dehumidification system 10D reduces the flow rate of the refrigerant flowing into the second heat exchange mechanism 14 (coil unit 46) when the measured temperature of the refrigerant becomes lower than the set temperature during the exhaust gas recirculation standby operation. Thus, the heating capacity of the first heat exchange mechanism 12 using the heat pump unit 37 is lowered, for example, when the regeneration temperature of the dehumidifying function of the desiccant of the desiccant rotor 17 is low, the temperature of the heated air can be lowered, The dehumidifying function of the dehumidifying agent can be recovered while suppressing the energy consumed in the first heat exchange mechanism 12.

  The controller 16 performs either the first circulation operation or the second circulation operation after a predetermined time has elapsed after the exhaust gas recirculation standby operation is performed and the measured temperature of the exhaust air measured by the first temperature sensor 33 is stabilized. carry out. The controller 16 compares the measured temperature of the exhaust air measured by the first temperature sensor 33 with the set temperature of the exhaust air stored in the storage area, and when the measured temperature of the exhaust air becomes equal to or lower than the set temperature (measured temperature). ≦ Set temperature), the first circulation operation is performed. When the measured temperature of the exhaust air exceeds the set temperature (measured temperature> set temperature), the controller 16 performs the second circulation operation.

  The first and second circulation operations are the same as those of the dehumidification system 10C of FIG. 11, and the effects of the first and second circulation operations are the same as those of the dehumidification system 10C of FIG. The flow of outside air, conditioned air, heated air, and exhaust air in the ducts 25 and 26 during the first and second circulation operations is the same as that of FIG. 13 as indicated by an arrow A1 in FIG. Further, the flow of the outside air, the conditioned air, the dehumidified air, and the ambient air in each of the ducts 22 to 24 during the first and second circulation operations is the same as that of FIG. 13, as indicated by an arrow A2 in FIG.

  During the execution of the first circulation operation or the second circulation operation, the valve opening degree of the three-way valve 49 is held at the current opening degree, and the refrigerant flow rate in the three-way valve 49 is kept constant. Therefore, the flow rate of the refrigerant flowing into the refrigerant bypass pipe 48 and the flow rate of the refrigerant flowing into the second heat exchange mechanism 14 (coil unit 46) are kept constant. Since the dehumidification system 10D keeps the flow rate of the refrigerant in the three-way valve 49 constant when performing either the first or second circulation operation, the refrigerant depletion in the three-way valve 49 is performed during the execution of the first and second circulation operations. Compared with the case where the flow rate is changed, the adjustment control of the three-way valve 49 (valve mechanism) and the adjustment control of the dampers 30, 32, 53 can be coordinated.

  When the measured temperature of the refrigerant measured by the second temperature sensor 50 becomes equal to or higher than the set temperature during the execution of either the first or second circulation operation, the controller 16 performs the first to third dampers 30, 32, 53 is transmitted to the control unit 53, a reduction signal of the valve opening on the refrigerant bypass pipe 48 side is transmitted to the control unit of the three-way valve 49, and the valve opening on the refrigerant circulation pipe 44 side is increased. Send a signal. The control part of the 1st-3rd damper 30,32,53 which received the opening degree holding signal stops turning of the turning blade of the 1st-3rd damper 30,32,53, and is the present opening degree (1st The damper 30 is fully closed). The control unit of the three-way valve 49 that has received the reduction signal and the expansion signal of the valve opening reduces the valve opening on the refrigerant bypass pipe 48 side to reduce the flow rate of the refrigerant flowing into the refrigerant bypass pipe 48, The valve opening degree on the side of the reflux pipe 44 is increased to increase the flow rate of the refrigerant flowing into the second heat exchange mechanism 14 (coil unit 46).

  The exhaust heat utilization type dehumidification system 10D flows into the second heat exchange mechanism 14 (coil unit 46) when the measured temperature of the refrigerant becomes equal to or higher than the set temperature during the first or second circulation operation. By increasing the flow rate of the refrigerant, the temperature adjustment function and the dehumidification function in the coil unit 46 can be utilized to the maximum, and the temperature and humidity of the exhaust air can be reliably reduced by the coil unit 46. The exhaust air whose temperature and humidity are reduced by the unit 46 can be efficiently reused.

  When the measured temperature of the refrigerant measured by the second temperature sensor 50 is lower than the set temperature during the execution of either the first or second circulation operation, the controller 16 performs the first to third dampers 30, 32, 53, the opening degree holding signal is transmitted to the control unit 53, the enlarged signal of the valve opening degree on the refrigerant bypass pipe 48 side is transmitted to the control part of the three-way valve 49, and the valve opening degree on the refrigerant circulation pipe 44 side is reduced. Send a signal. The control part of the 1st-3rd damper 30,32,53 which received the opening degree holding signal stops turning of the turning blade of the 1st-3rd damper 30,32,53, and is the present opening degree (1st The damper 30 is fully closed). The controller of the three-way valve 49 that has received the expansion signal and the reduction signal of the valve opening increases the valve opening on the refrigerant bypass pipe 48 side to increase the flow rate of the refrigerant flowing into the refrigerant bypass pipe 48. The valve opening on the side of the reflux pipe 44 is reduced to reduce the flow rate of the refrigerant flowing into the second heat exchange mechanism 14 (coil unit 46).

  The exhaust heat utilization type dehumidification system 10D flows into the second heat exchange mechanism 14 (coil unit 46) when the measured temperature of the refrigerant becomes lower than the set temperature during one of the first and second circulation operations. Since the flow rate of the refrigerant is reduced, the heating capacity of the first heat exchange mechanism 12 using the heat pump unit 37 is lowered. For example, the temperature of the heated air is lowered when the regeneration temperature of the dehumidifying function of the desiccant rotor 17 is low. The dehumidifying function of the dehumidifying agent can be restored without damaging the dehumidifying agent. Since the dehumidification system 10D adjusts the three-way valve 49 to adjust the flow rate of the refrigerant flowing into the coil unit 46 and the refrigerant bypass pipe 44, the opening degree of each of the dampers 30, 32, 53 is maintained at a predetermined opening degree. Compared with the case where the opening degree of each damper 30, 32, 53 is changed during the adjustment of the three-way valve 49, the adjustment control of the three-way valve 49 (valve mechanism) and the adjustment control of each damper 30, 32, 53 are coordinated. Can be made.

  In addition, after a predetermined time has passed since the flow rate of the refrigerant is adjusted by the three-way valve 49 and the measured temperature of the refrigerant measured by the second temperature sensor 50 is stabilized, one of the first circulation operation and the second circulation operation is performed. Implement (restart) one of them. In this case, the opening degree of the three-way valve 49 is maintained at the current opening degree, and the flow rate of the refrigerant in the three-way valve 49 is kept constant.

10A Waste heat utilization type dehumidification system 10B Waste heat utilization type dehumidification system (configuration with a three-way valve)
10C exhaust heat dehumidification system (configuration with air exhaust duct)
10D Waste heat utilization type dehumidification system (configuration with three-way valve and air exhaust duct)
DESCRIPTION OF SYMBOLS 11 Desiccant air conditioner 12 1st heat exchange mechanism 13 Heater 14 2nd heat exchange mechanism 15 Outside air conditioner 16 Controller 17 Desiccant rotor (dehumidification mechanism)
DESCRIPTION OF SYMBOLS 18 Dehumidification treatment zone 19 Dehumidification function reproduction | regeneration zone 20 Dehumidification zone 21 Moisture release zone 22 Processing side upstream duct 23 Dehumidification space recirculation duct 24 Processing side downstream duct 25 Reproduction side upstream duct 26 Regeneration side downstream duct 27 Air supply blower 28 Exhaust blower 29 exhaust air recirculation duct 30 first damper 31 control signal line 32 second damper 33 first temperature sensor 34 temperature sensor 35 dehumidified air-conditioned space 36 compressor (compressor)
37 Heat pump unit (heat pump)
38 Heat Exchanger 39 Condenser 40 Evaporator 41 Outgoing Pipe 42 Return Pipe 43 Heat Exchange Coil (for Heat Pump Unit)
44 Refrigerant recirculation pipe 45 Circulation pump 46 Heat exchange coil (for exhaust)
47 Expansion valve 48 Refrigerant bypass pipe 49 Valve mechanism (three-way valve)
50 Second temperature sensor 51 Purge air introduction duct 52 Air exhaust duct 53 Third damper

Claims (12)

A dehumidification treatment zone for producing dehumidified air, a dehumidification function regeneration zone for regenerating the dehumidification function, a dehumidification mechanism having a dehumidifier and disposed in the dehumidification treatment zone and the dehumidification function regeneration zone, and upstream of the dehumidification treatment zone A treatment-side upstream duct connected to the dehumidification treatment zone located on the side, a treatment-side downstream duct located downstream of the dehumidification treatment zone and connected to the dehumidification treatment zone, and the dehumidification function regeneration zone A regeneration-side upstream duct located upstream and connected to the dehumidification function regeneration zone; a regeneration-side downstream duct located downstream from the dehumidification function regeneration zone and connected to the dehumidification function regeneration zone; A first heat exchange mechanism that is disposed upstream of the dehumidifying mechanism located in the function regeneration zone and that heats the air supplied to the dehumidification mechanism using a heat pump; and the dehumidification function regeneration zone The first heat exchanging mechanism is disposed on the downstream side of the dehumidifying mechanism located in the first heat exchanging mechanism while recovering exhaust heat of exhaust air having a predetermined temperature flowing through the dehumidifying mechanism in the dehumidifying function regeneration zone using a predetermined refrigerant. A second heat exchange mechanism that performs heat exchange, and uses the exhaust heat recovered by the second heat exchange mechanism to heat the air in the first heat exchange mechanism, and at a predetermined temperature by the first heat exchange mechanism. Dehumidified air produced by the dehumidification mechanism located in the dehumidification processing zone while supplying heated air heated to the dehumidification mechanism located in the dehumidification function regeneration zone to regenerate the dehumidification function of the dehumidifying agent In the dehumidification system using exhaust heat that supplies air to the dehumidified air conditioning space,
The exhaust heat utilization type dehumidification system connects the regeneration side upstream duct extending upstream of the first heat exchange mechanism and the regeneration side downstream duct extending downstream of the second heat exchange mechanism, and the dehumidifying function. An exhaust air recirculation duct that circulates the exhaust air that has passed through the dehumidifying mechanism in the regeneration zone from the regeneration downstream duct to the regeneration upstream duct, and the regeneration downstream duct that extends downstream of the exhaust air recirculation duct. A first damper that adjusts the flow rate of exhaust air exhausted from the regeneration-side downstream duct, and a second damper that is installed in the exhaust air circulation duct and adjusts the flow rate of exhaust air flowing through the exhaust air circulation duct. A first temperature sensor that is installed in the regeneration-side downstream duct extending between the second heat exchange mechanism and the exhaust air circulation duct and measures the temperature of the exhaust air,
The exhaust heat utilization type dehumidification system maintains the opening degree of the first damper at a predetermined opening degree when the measured temperature of the exhaust air measured by the first temperature sensor falls below a preset temperature. A first circulation operation in which a flow rate of exhaust air exhausted from the downstream duct is maintained at a predetermined flow rate, and an opening amount of the second damper is increased to increase a flow rate of exhaust air flowing through the exhaust air circulation duct; The exhaust air flowing through the exhaust air recirculation duct with the opening of the first damper fully closed to shut off the exhaust of exhaust air from the regeneration downstream duct and the opening of the second damper fully opened When the measured temperature of the exhaust air measured by the first temperature sensor exceeds a preset temperature, the opening degree of the first damper is set to a predetermined value. Holding the opening at the bottom of the regeneration side The third circulation operation is performed in which the flow rate of the exhaust air exhausted from the duct is maintained at a predetermined flow rate, and the flow rate of the exhaust air flowing through the exhaust air circulation duct is reduced by reducing the opening of the second damper. An exhaust heat utilization type dehumidification system characterized by   The exhaust heat utilization type dehumidification system fully closes the opening degree of the second damper to cut off the flow of exhaust air in the exhaust air circulation duct and opens the opening degree of the first damper to the regeneration side. An exhaust gas recirculation standby operation that starts the system while maximizing the flow rate of exhaust air exhausted from the downstream duct. In the exhaust heat utilization type dehumidification system, the exhaust gas recirculation standby operation is performed, and then the first temperature sensor is When the measured temperature of the exhaust air measured by the first temperature sensor becomes equal to or lower than a set temperature after the measured temperature of the measured exhaust air is stabilized, one of the first and second circulation operations is performed. The measured temperature of the exhaust air measured by the first temperature sensor after the measured temperature of the exhaust air measured by the first temperature sensor after the exhaust recirculation standby operation is performed is stabilized. If it exceeds the set temperature, heat-using dehumidification system of claim 1, implementing the third circulation operation.   The exhaust heat utilization type dehumidification system is connected to the refrigerant circulation pipe for circulating the refrigerant through the first heat exchange mechanism and the second heat exchange mechanism, and connected to the refrigerant circulation pipe to exchange the refrigerant with the second heat exchange. A refrigerant bypass pipe that circulates the refrigerant to the first heat exchange mechanism without flowing through the mechanism, a flow rate of the refrigerant that flows through the second heat exchange mechanism, and a refrigerant bypass pipe that flows through the refrigerant bypass pipe A valve mechanism for adjusting the flow rate; and installed in the refrigerant circulation pipe extending between the refrigerant outlet and the refrigerant bypass pipe in the second heat exchange mechanism, and flows out from the refrigerant outlet of the second heat exchange mechanism A second temperature sensor for measuring the temperature of the refrigerant, and in the dehumidification system using exhaust heat, measuring the refrigerant measured by the second temperature sensor during any one of the first to third circulation operations. When the temperature exceeds the set temperature While maintaining the opening degree of each damper at a predetermined opening degree, the flow rate of the refrigerant flowing into the second heat exchange mechanism is reduced while adjusting the valve mechanism to reduce the flow rate of the refrigerant flowing into the refrigerant bypass pipe. When the measured temperature of the refrigerant measured by the second temperature sensor becomes lower than a set temperature during the execution of any one of the first to third circulation operations, the opening degree of each damper is set to a predetermined opening degree. The flow rate of the refrigerant flowing into the second heat exchange mechanism is decreased while the flow rate of the refrigerant flowing into the refrigerant bypass pipe is increased by adjusting the valve mechanism while maintaining The waste heat utilization type dehumidification system of description.   In the exhaust heat utilization type dehumidification system, when the measured temperature of the refrigerant measured by the second temperature sensor becomes equal to or higher than a set temperature during the exhaust gas circulation standby operation, the refrigerant bypass is adjusted by adjusting the valve mechanism. The flow rate of the refrigerant flowing into the pipe is decreased, the flow rate of the refrigerant flowing into the second heat exchange mechanism is increased, and the measured temperature of the refrigerant measured by the second temperature sensor during the exhaust gas recirculation standby operation. When the temperature becomes lower than the set temperature, the flow rate of the refrigerant flowing into the second heat exchange mechanism is decreased while adjusting the valve mechanism to increase the flow rate of the refrigerant flowing into the refrigerant bypass pipe, and the exhaust gas recirculation The measured temperature of the exhaust air measured by the first temperature sensor is equal to or lower than the set temperature after the measured temperature of the exhaust air measured by the first temperature sensor is stabilized after the standby operation is performed. In this case, the first circulation operation or the second circulation operation is performed while the flow rate of the refrigerant in the valve mechanism is kept constant, and the first temperature sensor measures after performing the exhaust gas recirculation standby operation. When the measured temperature of the exhaust air measured by the first temperature sensor exceeds the set temperature after the measured temperature of the exhaust air has stabilized, the third circulation operation is performed while keeping the flow rate of the refrigerant in the valve mechanism constant. The exhaust heat utilization type dehumidification system of Claim 3 to implement. A dehumidification treatment zone for producing dehumidified air, a dehumidification function regeneration zone for regenerating the dehumidification function, a dehumidification mechanism having a dehumidifier and disposed in the dehumidification treatment zone and the dehumidification function regeneration zone, and upstream of the dehumidification treatment zone A treatment-side upstream duct connected to the dehumidification treatment zone located on the side, a treatment-side downstream duct located downstream of the dehumidification treatment zone and connected to the dehumidification treatment zone, and the dehumidification function regeneration zone A regeneration-side upstream duct located upstream and connected to the dehumidification function regeneration zone; a regeneration-side downstream duct located downstream from the dehumidification function regeneration zone and connected to the dehumidification function regeneration zone; A first heat exchange mechanism that is disposed upstream of the dehumidifying mechanism located in the function regeneration zone and that heats the air supplied to the dehumidification mechanism using a heat pump; and the dehumidification function regeneration zone The first heat exchanging mechanism is disposed on the downstream side of the dehumidifying mechanism located in the first heat exchanging mechanism while recovering exhaust heat of exhaust air having a predetermined temperature flowing through the dehumidifying mechanism in the dehumidifying function regeneration zone using a predetermined refrigerant. A second heat exchange mechanism that performs heat exchange, and uses the exhaust heat recovered by the second heat exchange mechanism to heat the air in the first heat exchange mechanism, and at a predetermined temperature by the first heat exchange mechanism. Dehumidified air produced by the dehumidification mechanism located in the dehumidification processing zone while supplying heated air heated to the dehumidification mechanism located in the dehumidification function regeneration zone to regenerate the dehumidification function of the dehumidifying agent In the dehumidification system using exhaust heat that supplies air to the dehumidified air conditioning space,
The exhaust heat utilization type dehumidification system connects the regeneration side upstream duct extending upstream of the first heat exchange mechanism and the regeneration side downstream duct extending downstream of the second heat exchange mechanism, and the dehumidifying function. An exhaust air recirculation duct that circulates exhaust air flowing through the regeneration zone dehumidification mechanism from the regeneration downstream duct to the regeneration upstream duct; the dehumidification mechanism located in the dehumidification treatment zone; and the first heat exchange mechanism. A purge air introduction duct which is connected to the regeneration upstream duct extending upstream and introduces purge air of a predetermined temperature flowing through the purge region of the dehumidification mechanism of the dehumidification treatment zone from the dehumidification mechanism to the regeneration upstream duct. An air exhaust duct connected to the regeneration-side downstream duct extending between the dehumidifying function regeneration zone and the second heat exchange mechanism, and a bottom of the exhaust air circulation duct A first damper that is installed in the regeneration-side downstream duct extending to the side and adjusts a flow rate of exhaust air exhausted from the regeneration-side downstream duct, and is installed in the exhaust air circulation duct and flows through the exhaust air circulation duct A second damper that adjusts the flow rate of the exhaust air, a third damper that is installed in the air exhaust duct and adjusts the flow rate of the air exhausted from the air exhaust duct, the second heat exchange mechanism, and the exhaust air recirculation duct A first temperature sensor installed in the regeneration-side downstream duct extending between and for measuring the temperature of exhaust air,
In the exhaust heat utilization type dehumidification system, when the measured temperature of the exhaust air measured by the first temperature sensor falls below a set temperature, the opening degree of the first damper is fully closed and the third damper is opened. Exhaust gas that flows through the exhaust air recirculation duct by increasing the opening degree of the second damper while maintaining the flow rate of air exhausted from the air exhaust duct with a predetermined opening degree and a predetermined flow rate. When the first circulation operation for increasing the air flow rate is performed and the measured temperature of the exhaust air measured by the first temperature sensor exceeds the set temperature, the opening degree of the first damper is fully closed and the first 3. Maintain the opening of the 3 damper at a predetermined opening and maintain the flow rate of air exhausted from the air exhaust duct at a predetermined flow rate, while reducing the opening of the second damper to Reduce the flow rate of exhaust air Dehumidification system waste heat utilization type which comprises carrying out the second circulation operation that.   The exhaust heat utilization-type dehumidification system fully closes the opening of the second damper to block the flow of exhaust air in the exhaust air circulation duct, and fully closes the opening of the third damper. Including an exhaust recirculation standby operation for starting the system while fully opening the first damper and maximizing the flow rate of exhaust air exhausted from the regeneration downstream duct. In the exhaust heat utilizing dehumidification system, When the measured temperature of the exhaust air measured by the first temperature sensor becomes equal to or lower than a preset temperature after the measured temperature of the exhaust air measured by the first temperature sensor after the standby operation is performed, the first temperature sensor Exhaust gas measured by the first temperature sensor after the measured temperature of the exhaust air measured by the first temperature sensor after the circulation operation is performed and the exhaust gas circulation standby operation is performed is stabilized. If the measured temperature of the gas exceeds the set temperature, heat-using dehumidification system according to claim 5 for implementing the second circulation operation.   The exhaust heat utilization type dehumidification system is connected to the refrigerant circulation pipe for circulating the refrigerant through the first heat exchange mechanism and the second heat exchange mechanism, and connected to the refrigerant circulation pipe to exchange the refrigerant with the second heat exchange. A refrigerant bypass pipe that circulates the refrigerant to the first heat exchange mechanism without flowing through the mechanism, a flow rate of the refrigerant that flows through the second heat exchange mechanism, and a refrigerant bypass pipe that flows through the refrigerant bypass pipe A valve mechanism for adjusting the flow rate; and installed in the refrigerant circulation pipe extending between the refrigerant outlet and the refrigerant bypass pipe in the second heat exchange mechanism, and flows out from the refrigerant outlet of the second heat exchange mechanism A second temperature sensor that measures the temperature of the refrigerant, and in the dehumidification system using exhaust heat, the second temperature sensor measures during either the first circulation operation or the second circulation operation. The measured temperature of the selected refrigerant is lower than the set temperature. In this case, while maintaining the opening degree of each damper at a predetermined opening degree, the flow rate of the refrigerant flowing into the refrigerant bypass pipe is reduced by adjusting the valve mechanism, and flows into the second heat exchange mechanism. When the measured temperature of the refrigerant measured by the second temperature sensor is lower than a set temperature during the execution of either the first circulation operation or the second circulation operation, While maintaining the opening of the damper at a predetermined opening, the flow rate of the refrigerant flowing into the second heat exchange mechanism is decreased while adjusting the valve mechanism to increase the flow rate of the refrigerant flowing into the refrigerant bypass pipe. The exhaust heat utilization type dehumidification system according to claim 5 or 6.   In the exhaust heat utilization type dehumidification system, when the measured temperature of the refrigerant measured by the second temperature sensor becomes equal to or higher than a set temperature during the exhaust gas circulation standby operation, the refrigerant bypass is adjusted by adjusting the valve mechanism. The flow rate of the refrigerant flowing into the pipe is decreased, the flow rate of the refrigerant flowing into the second heat exchange mechanism is increased, and the measured temperature of the refrigerant measured by the second temperature sensor during the exhaust gas recirculation standby operation. When the temperature becomes lower than the set temperature, the flow rate of the refrigerant flowing into the second heat exchange mechanism is decreased while adjusting the valve mechanism to increase the flow rate of the refrigerant flowing into the refrigerant bypass pipe, and the exhaust gas recirculation The measured temperature of the exhaust air measured by the first temperature sensor is equal to or lower than the set temperature after the measured temperature of the exhaust air measured by the first temperature sensor is stabilized after the standby operation is performed. In this case, the first circulation operation is performed while the refrigerant flow rate in the valve mechanism is kept constant, and the measured temperature of the exhaust air measured by the first temperature sensor after the exhaust recirculation standby operation is performed. 8. The second circulation operation is performed according to claim 7, wherein when the measured temperature of the exhaust air measured by the first temperature sensor exceeds a set temperature after stabilization, the second circulation operation is performed while maintaining a constant flow rate of the refrigerant in the valve mechanism. The waste heat utilization type dehumidification system of description.   The exhaust heat utilization type according to any one of claims 1 to 8, wherein the second heat exchange mechanism is a coil unit, and the coil unit dehumidifies the exhaust air while collecting exhaust heat of the exhaust air. Dehumidification system.   The exhaust heat utilization type dehumidification system is installed between the first heat exchange mechanism and the dehumidification mechanism, and includes a heater that heats heated air heated to a predetermined temperature by the first heat exchange mechanism. The waste heat utilization type dehumidification system in any one of Claim thru | or 9.   The exhaust heat utilization type dehumidification system includes an outside air conditioner that dehumidifies outside air supplied to the dehumidifying mechanism of the dehumidifying treatment zone and the dehumidifying mechanism of the dehumidifying function regeneration zone while adjusting the temperature of the outside air. The waste heat utilization type dehumidification system in any one of Claim thru | or 10. The exhaust heat utilization type dehumidification system according to any one of claims 1 to 11, wherein the dehumidifying mechanism is a desiccant rotor, and the refrigerant is water or brine.

Images