JP2020034268A - Dehumidification device - Google Patents

Abstract

To provide a dehumidification device that stably performs dehumidification in any outside air conditions, is inexpensive, and does not require a fluorocarbon refrigerant cooler as an outer unite.SOLUTION: A dehumidification device according to an embodiment has a desiccant rotor, a pre-cooler, a heat collector, a heat pump device that uses a calorie of heat collected from outside air as a heat source, a sensor that detects the calorie, a valve control mechanism, and a control unit that controls the valve control mechanism so that the detection of result of the sensor becomes a target value.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a dehumidifier.

2. Description of the Related Art Conventionally, a dehumidifying device that uses a desiccant rotor and supplies dehumidified air to an air-conditioning room or the like (demand destination) is known (for example, Patent Document 1).
The desiccant rotor has a disk-shaped rotor surface having an adsorption surface carrying an adsorbent as a means for adsorbing and dehumidifying water vapor in the air. The desiccant rotor is disposed straddling the processing air chamber and the regeneration air chamber, and the processing air chamber and the regeneration air chamber are partitioned by a partition so as to be arranged in parallel. The desiccant rotor rotates around a rotation shaft provided on the partition wall, and adsorbs water vapor contained in the airflow introduced into the processing air chamber at a position located in the processing air chamber. The portion that has adsorbed the water vapor rotates and moves to the regeneration air chamber. The regeneration air heated in the regeneration air chamber is blown to the desiccant rotor, and the adsorbed water vapor is released to the regeneration air.

  However, if an electric heater is used to heat the regenerated air used for regenerating the desiccant rotor, energy efficiency deteriorates. Therefore, the desiccant rotor has not been used in a large-sized dehumidifier.

  On the other hand, a device including a desiccant rotor and a heat pump device is known (Patent Document 2). In this apparatus, heat of adsorption of a desiccant rotor is collected by a heat pump device, and is used for heating regeneration air used for regeneration of the desiccant rotor. The heat pump device includes a refrigerant circulation path through which the refrigerant circulates, and heat pump cycle components such as a compressor, an air heater, an expansion valve, and an air cooler connected in series with the refrigerant circulation path. An air heater constituting a part of the heat pump device is provided at a position on the upstream side of the desiccant rotor in the regeneration air chamber. The regeneration air is heated by an air heater, and its temperature and relative humidity are adjusted to be suitable for taking in water vapor. In the processing air chamber, when the desiccant rotor adsorbs water vapor from the air stream, the adsorbent emits heat of adsorption, so that the processing air is heated and the temperature rises. An air cooler constituting a part of the heat pump device is provided at a position downstream of the desiccant rotor in the processing air chamber. The processing air that has passed through the desiccant rotor is cooled (heat-collected) by an air cooler.

  However, when the temperature is high, such as in summer, the amount of water vapor dissolved in the air becomes excessive (absolute humidity increases), and depending on the conditions, the desiccant rotor may not be able to dehumidify to the demand of the demand destination. Therefore, a dehumidifier provided with a desiccant rotor and a heat pump device is provided with a pre-cooler for cooling and dehumidifying so as to cope with a summer climate. For example, a precooler is provided outside the apparatus to precool air taken into the processing air chamber.

JP 2013-24448 A Japanese Patent No. 4870843

  Preparing the precooler so as to cope with the summer climate involves the cost of operating the precooler, and there is a device that is not used in other seasons, which is wasteful. In general, a chiller device using a chlorofluorocarbon-based refrigerant is used as the precooler. For this reason, a chiller device using a chlorofluorocarbon-based refrigerant has been indispensable in order to operate all year long, even though it is a dehumidifier using an energy saving effect and a natural refrigerant. In addition, when a CFC-based refrigerant cooling device is provided outside the device, there is a problem that it is not possible to achieve the objectives of low cost, energy saving effect, etc. for operation throughout the year.

  In view of the circumstances described above, an object of the present invention is to provide a dehumidifier that stably performs dehumidification under any external air condition, and that is low in cost and does not require an external Freon-based refrigerant cooling device. I do.

  The dehumidifier according to one embodiment of the present invention includes a desiccant rotor, a precooler, a heat collector, a heat pump device that uses a heat amount obtained from outside air as a heat source, a sensor that detects the heat amount, and a valve adjustment mechanism. A control unit that controls the valve adjustment mechanism so that the detection result of the sensor becomes a target value.

A dehumidifying device according to another aspect of the present invention,
A pre-cooler for cooling the air to be dehumidified by heat exchange with a heat source,
A desiccant rotor that adsorbs moisture in the air by being brought into contact with the air cooled by the precooler and dehumidifies the air,
A compressor, a condenser, an expansion valve and an evaporator are provided, and air is heated by the heat generated in the condenser by circulating a refrigerant through these, and the heated air is removed from the moisture adsorbed by the desiccant rotor. A heat pump device for supplying for removal,
A flow path that circulates the heat source body cooled by heat exchange with the refrigerant in the evaporator to the precooler.

The dehumidifying device of the other aspect further includes:
A heat collector that heats the heat source body by exchanging heat between the air and the heat source body from which moisture adsorbed on the desiccant rotor has been removed,
A valve adjustment mechanism for returning a part or all of the heat source body returning from the precooler to the evaporator to the evaporator through the heat collector,
A sensor for measuring the temperature of the heat source body,
A control unit that controls the valve adjustment mechanism based on the detection result of the sensor and adjusts a flow rate of the heat source returning to the evaporator via the heat collector.

  In a more specific aspect, the dehumidifying device is provided in the processing air chamber and the processing air chamber and the regeneration air chamber disposed adjacent to each other, and a process for forming a processing air flow inside the processing air chamber. A fan, a regeneration fan provided in the regeneration air chamber to form a regeneration air flow inside the regeneration air chamber, a desiccant rotor disposed across the processing air chamber and the regeneration air chamber, A pre-cooler provided in the chamber and pre-cooling (cooling and dehumidifying) the processing air upstream of the desiccant rotor; a heat-collector provided in the regeneration air chamber and collecting heat from the regeneration air downstream of the desiccant rotor; A heat pump device that heats regenerated air upstream of the desiccant rotor, comprising an evaporator that exchanges heat between a heat source and a refrigerant for cooling the heat source, and evaporating the heat source. From the evaporator, the first flow path, which flows the heat source body that has passed through the precooler to the evaporator, and the heat source body that flows from the evaporator to the precooler, and the heat source body that has passed through the precooler, A second flow path for flowing a part of the heat source body that has passed through the precooler to the heat collector and flowing the heat source body that has passed the heat collector to the evaporator, A valve adjustment mechanism that allows the body to flow from the evaporator in the order of the precooler and the heat collector, and a third flow path for flowing the heat source body that has passed through the heat collector to the evaporator; and A temperature sensor (sensor) for detecting the temperature (heat amount) of the heat source flowing into the evaporator; and a control unit for controlling the valve adjustment mechanism so that the temperature detected by the temperature sensor (detection result) becomes a target value. Prepare.

According to the above dehumidifier, dehumidification can be performed stably under any external air condition, and at low cost, there is no need for an external Freon-based refrigerant cooling device.
For example, control can be performed as in the following (I) to (III).
(I) Since the outside air temperature (inlet temperature of the processing air chamber) is higher in summer than in winter, cooling dehumidification and heat collection are performed by a precooler. In summer, the temperature detected by the temperature sensor can be maintained at the target value only by collecting heat from the precooler, and the amount of heating required for the heat pump device can be secured. In addition, since the desiccant rotor is used to perform dehumidification in addition to cooling and dehumidification by the precooler, processing air with low dehumidification can be supplied stably.
(II) Since the outside air temperature (the inlet temperature of the processing air chamber) is lower in the middle period (spring and autumn) between summer and winter than in summer, cooling and dehumidification in the precooler is less necessary, and therefore the amount of heat taken is also lower. Decrease. In the interim period, a part of the heat source is flowed to the heat collector, and the heat collected by the precooler is used to secure the amount of heat insufficient. As a result, the detection result of the temperature sensor can be maintained at the target value even in the intermediate period, and the necessary heating amount can be secured. Further, the processing air with low dehumidification can be stably supplied only by dehumidification by the desiccant rotor.
(III) In winter, cooling and dehumidification in the pre-cooler is no longer necessary, and it becomes difficult to collect heat. Therefore, heat is secured only by the heat collector. As a result, even in winter, the detection result of the temperature sensor can be maintained at the target value, and a necessary heating amount can be secured. Subsequently, the processing air with low dehumidification can be stably supplied only by dehumidification by the desiccant rotor.

From the above, regardless of the outside air condition (outside air temperature), the required low dehumidification processing air can be secured throughout the year, and the heating amount necessary for the heat pump device is always secured almost quantitatively. Can also be played.
In other words, in the summer (pre-cooler), in the middle (pre-cooler and heat collector), and in the winter (heat collector), an environment capable of cooling and dehumidifying and collecting heat is formed and controlled, so that it comes out of the evaporator. For example, a heat source at, for example, 15 ° C. can always be returned to the evaporator at 20 ° C. at any time. Thereby, the operation of the heat pump device can be kept constant (evaporation temperature is kept constant) at any time, and the operation can be performed without affecting the heating amount as much as possible.

In one aspect of the present invention, the pre-cooler has both a cooling and dehumidifying function and a heat collecting function, and the control unit controls the valve adjustment mechanism when the amount of heat of the pre-cooler is insufficient. Heat may also be collected.
For example, in Patent Document 2, cooling and dehumidification are performed by a pre-cooler provided outside, and heat collection is performed by an air cooler inside the apparatus. On the other hand, according to this configuration, the pre-cooler inside the device has both the cooling and dehumidifying function and the heat collecting function, so that it is possible to reduce the number of parts and the cost.

In one embodiment of the present invention, the apparatus further includes a hot air temperature detection sensor that detects a temperature of hot air flowing from the heat pump device to the desiccant rotor, and the control unit causes the detection temperature of the hot air temperature detection sensor to be a target hot air temperature. Alternatively, the reproduction fan may be controlled.
According to this configuration, the temperature of the hot air flowing from the heat pump device to the desiccant rotor can be adjusted to the target hot air temperature regardless of the outside air condition, so that the required heating amount can be kept within a certain range. Therefore, dehumidification can be performed more stably under any external air condition.

In one embodiment of the present invention, a second precooler provided in the processing air chamber and precooling the processing air upstream of the desiccant rotor and downstream of the precooler may be further provided.
According to this configuration, the relative humidity of the processing air sent to the desiccant rotor can be further increased as compared with the configuration including only one pre-cooler, so that the total dehumidifying effect can be further improved.

In one embodiment of the present invention, the heat pump device may be arranged outside a regeneration air chamber.
According to this configuration, the degree of freedom in the layout of the valve adjustment mechanism (such as piping) can be increased as compared with the configuration in which the heat pump device is disposed inside the regeneration air chamber.

In one aspect of the present invention, the heat pump device may include an evaporator for exchanging heat between a heat source for cooling the precooler and a refrigerant, and the refrigerant may be carbon dioxide.
According to this configuration, since a natural refrigerant is used and a CFC-based refrigerant is not used, it is suitable for global warming countermeasures.

In one embodiment of the present invention, the heat pump device may include an evaporator for exchanging heat between a heat source for cooling the precooler and a refrigerant, and the heat source may be water or brine.
According to this configuration, since water or brine has a higher heat transfer coefficient than air, COP (Coefficient Of Performance) of the dehumidifier can be easily improved.

A dehumidifier according to another aspect of the present invention,
A desiccant rotor that adsorbs moisture in the air by being brought into contact with air to be dehumidified and dehumidifies the air,
A compressor, a condenser, an expansion valve and an evaporator are provided, and air is heated by the heat generated in the condenser by circulating a refrigerant through these, and the heated air is removed from the moisture adsorbed by the desiccant rotor. A heat pump device for supplying for removal,
An aftercooler for cooling air dehumidified by the desiccant rotor by using cold generated in the evaporator.

The dehumidifier of the above aspect further comprises
A heater that further heats the air heated by the heat pump device and supplies the air to remove moisture adsorbed on the desiccant rotor,
A pre-cooler that cools the air to be dehumidified and then contacts the desiccant rotor.

  According to the present invention, it is possible to provide a dehumidifier that stably performs dehumidification under any external air conditions, and that does not require a CFC-based refrigerant cooling device outside at low cost.

The block diagram of the dehumidifier which concerns on embodiment. FIG. 3 is an explanatory diagram of a first flow channel according to the embodiment. Explanatory drawing of the 2nd flow path which concerns on embodiment. FIG. 4 is an explanatory diagram of a third flow channel according to the embodiment. The figure which shows the relationship between the flow volume of the heat source water which passes through each of a precooler and a heat collector, and external temperature. The block diagram of the dehumidifier which concerns on the 1st modification of embodiment. The block diagram of the dehumidifier which concerns on the 2nd modification of embodiment. The block diagram of the dehumidifier which concerns on other embodiment of this invention.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In each of the drawings, the same components are denoted by the same reference numerals. In the embodiment, as an example of the dehumidifier, a dehumidifier using carbon dioxide (CO ₂ ) as a refrigerant and water as a heat source will be described. The dehumidifying device is connected to an air conditioning room (not shown) that is a destination of the demand for the processing air. For example, an air conditioning room is applied to a foundry. For example, a dehumidifier is used for dehumidifying air blown into an oil furnace in a foundry.

[Dehumidifier 1]
As shown in FIG. 1, the dehumidifier 1 includes a processing air chamber 2, a regeneration air chamber 3, a processing fan 4, a regeneration fan 5, a desiccant rotor 6, a precooler 7, a heat collector 10, a heat pump device 8, and a valve adjustment mechanism 11. , A temperature sensor 42 (sensor) and the control unit 13.

  The processing air chamber 2 and the regeneration air chamber 3 are arranged adjacent to each other. The processing air chamber 2 and the regeneration air chamber 3 are partitioned by a partition 14 so as to be arranged in parallel. The processing air chamber 2 and the regeneration air chamber 3 have a rectangular parallelepiped shape extending in parallel with each other.

  A first end of the processing air chamber 2 is provided with an inlet for outside air (hereinafter, also referred to as “processing inlet 15”). At a second end of the processing air chamber 2 (an end opposite to the first end of the processing air chamber 2), a processing air supply port (hereinafter also referred to as “processing outlet 16”) is provided. I have.

  A first end of the regeneration air chamber 3 (an end opposite to the first end of the processing air chamber 2) is provided with a hot air inlet (hereinafter, also referred to as “hot air inlet 17”). At a second end of the regeneration air chamber 3 (an end opposite to the first end of the regeneration air chamber 3), an exhaust port 18 for regeneration air (hereinafter, also referred to as an “exhaust port 18”) is provided. ing.

  The processing fan 4 is provided in the processing air chamber 2. The processing fan 4 forms a processing air flow inside the processing air chamber 2. The outside air is introduced into the processing air chamber 2 from the processing inlet 15 by the operation of the processing fan 4. The introduced air forms an airflow toward the processing outlet 16.

The regeneration fan 5 is provided in the regeneration air chamber 3. The regeneration fan 5 forms a regeneration air flow inside the regeneration air chamber 3. By the operation of the regeneration fan 5, hot air (outside air) is introduced into the regeneration air chamber 3 from the hot air inlet 17. The introduced air forms an airflow toward the exhaust port 18.
The processing air flow formed in the processing air chamber 2 and the regeneration air flow formed in the regeneration air chamber 3 are configured to flow in opposite directions.

  The desiccant rotor 6 has, as a means for adsorbing and dehumidifying water vapor in the air, an adsorbing surface 6a carrying an adsorbent on the surface of a disk-shaped rotor. For example, as the adsorbent, an inorganic adsorbent such as silica gel and zeolite or a polymer adsorbent is used. The desiccant rotor 6 is disposed across the processing air chamber 2 and the regeneration air chamber 3. The rotating shaft 6 b of the desiccant rotor 6 is arranged on the partition 14. The desiccant rotor 6 rotates around a rotation shaft 6b.

  For example, the desiccant rotor 6 is rotated by a drive motor (not shown) at a low speed of several tens of rotations per hour. By the rotation of the desiccant rotor 6, the suction surface 6a alternately enters the processing air chamber 2 and the regeneration air chamber 3. The desiccant rotor 6 continuously alternately repeats adsorption and regeneration.

  The precooler 7 is provided in the processing air chamber 2. The precooler 7 is disposed near the first end of the processing air chamber 2 (near the processing inlet 15). The precooler 7 precools the processing air upstream of the desiccant rotor 6. A filter 19 for removing dust and the like in the outside air is provided between the processing inlet 15 and the precooler 7.

  The heat collector 10 is provided in the regeneration air chamber 3. The heat collector 10 is arranged near the second end of the regeneration air chamber 3 (downstream in the flow direction of the regeneration air). The heat collector 10 collects heat from the regeneration air downstream of the desiccant rotor 6.

  The heat pump device 8 uses the amount of heat collected from outside air as a heat source. The heat pump device 8 includes an evaporator 24 for exchanging heat between water as a heat source for cooling the precooler 7 and carbon dioxide as a refrigerant. The heat pump device 8 heats the regeneration air upstream of the desiccant rotor 6. For example, the heat pump device 8 generates hot air by a drive fan (not shown).

  The heat pump device 8 includes a refrigerant circulation line 20 through which carbon dioxide is circulated as a refrigerant, and a compressor 21, a condenser 22, an expansion valve 23, and an evaporator 24 connected in series to the refrigerant circulation line 20.

  The refrigerant circulation line 20 has an annular shape (closed circuit). In the flow direction of the refrigerant in the refrigerant circulation line 20, the compressor 21, the condenser 22, the expansion valve 23, and the evaporator 24 are arranged in this order.

  The heat pump device 8 is arranged outside the regeneration air chamber 3. The heat pump device 8 has a rectangular parallelepiped shape overlapping the regeneration air chamber 3 when viewed from the direction in which the regeneration air chamber 3 extends.

  A connection gate 25 that connects the heat pump device 8 and the first end of the regeneration air chamber 3 is provided between the heat pump device 8 and the first end of the regeneration air chamber 3 (the portion where the hot air inlet 17 is formed). ing. In the connection gate 25, a flow path for guiding the hot air from the heat pump device 8 to the regeneration air chamber 3 is formed.

  At an upstream end (an end opposite to the connection gate 25) of the heat pump device 8, an inlet gate 27 having an outside air inlet 26 (hereinafter, also referred to as a "regeneration inlet 26") is provided. The entrance gate 27 is provided with a filter 28 for removing dust and the like in the outside air.

  The high-pressure and high-temperature refrigerant compressed in the compressor 21 is discharged from the compressor 21. The refrigerant discharged from the compressor 21 is condensed in the condenser 22 and heats the regeneration air flowing from the regeneration inlet 26 to the desiccant rotor 6. In the embodiment, the heat pump device 8 can raise the temperature of the regenerated air to a high temperature of 80 ° C. or higher by using carbon dioxide which becomes a supercritical state and becomes high temperature in a high pressure region as a refrigerant.

  The refrigerant flowing out of the condenser 22 expands at the expansion valve 23 to have a low pressure and a low temperature. Water (hereinafter, also referred to as “heat source water”) is supplied to the evaporator 24 as a heat source that gives evaporation heat to the refrigerant. The refrigerant flowing out of the expansion valve 23 exchanges heat with the heat source water in the evaporator 24 to obtain latent heat of evaporation and evaporates. The refrigerant evaporated by the evaporator 24 flows into the compressor 21 again and is compressed in the compressor 21.

The valve adjustment mechanism 11 can switch between a first flow path L1 (see FIG. 2), a second flow path L2 (see FIG. 3), and a third flow path L3 (see FIG. 4). .
As shown in FIG. 2, the first flow path L1 is a flow path in which water (heat source water) as a heat source flows from the evaporator 24 to the precooler 7, and the heat source water passing through the precooler 7 flows to the evaporator 24. is there. The first flow path L <b> 1 forms a circulation path of the heat source water between the evaporator 24 and the precooler 7.
As shown in FIG. 3, the second flow path L <b> 2 allows the heat source water to flow from the evaporator 24 to the precooler 7, the heat source water that has passed through the precooler 7 to the evaporator 24, and the heat source water that has passed through the precooler 7. It is a flow path in which a part flows to the heat collector 10 and the heat source water that has passed through the heat collector 10 flows to the evaporator 24. The second flow path L <b> 2 forms a circulation path of the heat source water between the evaporator 24 and the precooler 7 and between the evaporator 24 and the heat collector 10.
As shown in FIG. 4, the third flow path L3 is a flow path in which the heat source water flows from the evaporator 24 to the precooler 7 and the heat collector 10 in this order, and the heat source water passing through the heat collector 10 flows to the evaporator 24. It is. In other words, the third flow path L3 allows the heat source water to flow from the evaporator 24 to the pre-cooler 7, the heat source water that has passed through the pre-cooler 7 to flow to the heat collector 10, and the heat source water that has passed through the heat collector 10 to flow. This is a flow path that flows to the evaporator 24. The third flow path L <b> 3 forms a circulation path of the heat source water between the evaporator 24 and the heat collector 10.

As illustrated in FIG. 1, the valve adjustment mechanism 11 includes a first pipe 31, a second pipe 32, a third pipe 33, a fourth pipe 34, and a valve mechanism 35.
Each end of the first pipe 31 is connected to the evaporator 24 and the precooler 7, respectively. The first pipe 31 allows the heat source water to flow from the evaporator 24 to the precooler 7. The first pipe 31 forms a forward path for flowing the heat source water from the evaporator 24 to the precooler 7. The first pipe 31 is provided with a pump 41 for flowing heat source water.
Each end of the second pipe 32 is connected to the precooler 7 and the evaporator 24, respectively. The second pipe 32 allows the heat source water to flow from the precooler 7 into the evaporator 24. The second pipe 32 forms a return path for flowing the heat source water from the precooler 7 to the evaporator 24. The second pipe 32 is provided with a temperature sensor 42 that detects the temperature of the heat source water flowing to the evaporator 24. The temperature sensor 42 is an example of a sensor that detects the amount of heat taken from outside air (the amount of heat used by the heat pump device 8 as a heat source).

Each end of the third pipe 33 is connected to the second pipe 32 and the heat collector 10, respectively. The third pipe 33 allows at least a part of the heat source water that has passed through the precooler 7 to flow into the heat collector 10.
Each end of the fourth pipe 34 is connected to the heat collector 10 and a position downstream of the connection position of the third pipe 33 in the second pipe 32. The fourth pipe 34 allows the heat source water that has passed through the heat collector 10 to flow into the evaporator 24.

  The valve mechanism 35 can switch between the first flow path L1 (see FIG. 2), the second flow path L2 (see FIG. 3), and the third flow path L3 (see FIG. 4). The valve mechanism 35 is provided at a connection between the second pipe 32 and the third pipe 33. For example, the valve mechanism 35 is a three-way valve. By adjusting the opening of the valve of the valve mechanism 35, the flow rate of the heat source flowing through the third pipe 33 can be adjusted. By adjusting the flow rate of the heat source water flowing through the third pipe 33, the flow rate of the heat source water flowing into the heat collector 10 can be adjusted.

  The control unit 13 performs overall control of each component of the dehumidifier 1. The control unit 13 controls the valve adjustment mechanism 11 so that the temperature detected by the temperature sensor 42 becomes a target value. The control unit 13 controls the valve adjustment mechanism 11 to selectively switch the first flow path L1, the second flow path L2, and the third flow path L3. The control unit 13 controls the valve adjustment mechanism 11 to adjust the flow rate of the heat source water passing through the heat collector 10.

  For example, the control unit 13 controls the valve adjustment mechanism 11 (valve mechanism 35) such that the temperature detected by the temperature sensor 42 (the temperature of the heat source water flowing to the evaporator 24) is maintained at 20 ° C. The control unit 13 controls the valve adjustment mechanism 11, and when the flow path is switched to any one of the flow paths L1 to L3, the heat source water is discharged so that the detection result of the temperature sensor 42 becomes a target value. The flow rate through the calorie precooler 10 is adjusted.

  FIG. 5 is a diagram showing the relationship between the flow rate of the heat source water passing through each of the precooler 7 and the heat collector 10 and the outside air temperature. The horizontal axis in FIG. 5 indicates the outside air temperature (° C.), and the vertical axis indicates the flow rate. In FIG. 5, reference numeral C1 indicates a flow rate of the heat source water passing through the precooler 7 and reference numeral C2 indicates a flow rate of the heat source water passing through the heat collector 10.

As shown in FIG. 5, the flow rate C1 of the heat source water passing through the precooler 7 is constant. On the other hand, the flow rate C2 of the heat source water passing through the heat collector 10 decreases as the outside air temperature increases.
In the example of FIG. 5, the flow rate C2 of the heat source water passing through the heat collector 10 is substantially the same as the flow rate C1 of the heat source water passing through the precooler 7 when the outside air temperature is 0 ° C. (C2 ≒ C1). When the temperature is 10 ° C., the flow rate is approximately half of the flow rate C1 of the heat source water passing through the precooler 7 (C2） C1 / 2), and is substantially zero when the outside air temperature is 35 ° C. (C2 ≒ 0).

[Operation of each component of dehumidifier 1]
The outside air is introduced into the processing air chamber 2 from the processing inlet 15 by the operation of the processing fan 4. The introduced air forms an airflow toward the processing outlet 16. Foreign matter is removed from the introduced processing air by the filter 19 and flows into the precooler 7.

  The pre-cooler 7 lowers the temperature of the inflowing processing air, performs cooling dehumidification, and then causes the desiccant rotor 6 to adsorb the processing air. For example, the processing air flowing into the precooler 7 has a temperature of 30C to 40C. The processing air flowing into the precooler 7 exchanges heat with the heat source water in the precooler 7 to be cooled and dehumidified.

  The desiccant rotor 6 adsorbs water vapor contained in the processing air introduced into the processing air chamber 2 at a portion located in the processing air chamber 2. In the processing air chamber 2, when the desiccant rotor 6 adsorbs water vapor from the air flow, the adsorbent emits heat of adsorption, so that the processing air is heated and the temperature rises. The processing air whose temperature has risen and the relative humidity has decreased is supplied to the air conditioning room, which is the demand destination.

By the operation of the heat pump device 8, outside air is introduced into the heat pump device 8 from the regeneration inlet 26.
Foreign matter from the outside air from the regeneration inlet 26 is removed by the filter 28. The heat pump device 8 uses carbon dioxide as a refrigerant circulating in the refrigerant circulation line 20 to raise the temperature to a high temperature of 80 ° C. or higher using outside air as regenerated air. The heat pump device 8 raises the temperature of the regeneration air flow formed in the regeneration air chamber 3. In the refrigerant circulation line 20, the refrigerant flowing out of the expansion valve 23 exchanges heat with the heat source water in the evaporator 24.

  The adsorption surface 6 a that adsorbs the water vapor contained in the processing air in the processing air chamber 2 moves to the regeneration air chamber 3 by the rotation of the desiccant rotor 6. The regenerated airflow whose temperature has been raised by the heat pump device 8 and the relative humidity has been reduced contacts the adsorption surface 6a and desorbs the water vapor adsorbed on the adsorption surface 6a. The regenerated air having taken in steam from the desiccant rotor 6 flows into the heat collector 10.

  In the heat collector 10, if necessary, heat is collected from the inflowing regeneration air. Thereafter, the regeneration air is discharged from the exhaust port 18 to the outside of the regeneration air chamber 3. For example, the regeneration air flowing into the heat collector 10 has a temperature of 40C to 60C. The regenerated air flowing into the heat collector 10 exchanges heat with the heat source water in the heat collector 10 to heat the heat source water.

[Control of Valve Mechanism 35]
The control unit 13 controls the valve mechanism 35 so that the temperature detected by the temperature sensor 42 becomes a target value. For example, the control unit 13 controls the valve mechanism 35 so that the temperature detected by the temperature sensor 42 (the temperature of the heat source water flowing to the evaporator 24) is maintained at 20 ° C.

  For example, the control unit 13 controls the valve mechanism 35 to switch to the first flow path L1 in summer (see FIG. 2). The outside air temperature (the inlet temperature of the processing air chamber) is higher in summer than in winter. In summer, by flowing heat source water only through the first flow path L1, the temperature detected by the temperature sensor 42 is maintained at a target value (for example, 20 ° C.) only by collecting heat from the precooler 7. For example, in summer, the temperature of the heat source water (for example, 15 ° C.) flowing from the evaporator 24 is set to 20 ° C. when returning to the evaporator 24 only by the precooler 7. The control unit 13 controls the valve mechanism 35, and when the flow path is switched to the first flow path L1, the heat source water reduces the heat release amount of the pre-cooler 10 so that the temperature detected by the temperature sensor 42 is maintained at 20 ° C. (See FIG. 5).

  For example, the control unit 13 controls the valve mechanism 35 to switch to the second flow path L2 in an intermediate period (spring and autumn) between summer and winter (see FIG. 3). The outside air temperature (the inlet temperature of the processing air chamber) is lower in the intermediate period than in the summer. Therefore, in the interim period, the frequency of cooling dehumidification in the precooler 7 is reduced, and accordingly, the amount of heat taken is also reduced. In the intermediate period, a part of the heat source water is caused to flow to the heat collecting device 10, so that the heat collecting device 10 secures the amount of heat that is insufficient due to the heat collection from the precooler 7. That is, in the interim period, the amount of heat is secured in each of the precooler 7 and the heat collector 10, and the detection temperature of the temperature sensor 42 is maintained at the target value (for example, 20 ° C.). For example, in the interim period, the temperature (for example, 15 ° C.) of the heat source water flowing from the evaporator 24 in both the precooler 7 and the heat collector 10 is set to 20 ° C. when returning to the evaporator 24. The control unit 13 controls the valve mechanism 35, and when the flow path is switched to the second flow path L2, the heat source water reduces the heat release amount of the pre-cooler 10 so that the temperature detected by the temperature sensor 42 is maintained at 20 ° C. (See FIG. 5).

  For example, the control unit 13 controls the valve mechanism 35 to switch to the third flow path L3 in winter (see FIG. 4). In winter, cooling and dehumidification in the pre-cooler 7 is no longer necessary, and heat collection becomes difficult. In winter, the heat source water is heated by the regenerated air flow, which has been heated by the heat pump device 8 and has a reduced relative humidity, flowing into the heat collector 10. In winter, the heat source 10 secures the heat quantity by flowing all the heat source water to the heat collector 10. That is, in winter, the temperature detected by the temperature sensor 42 is maintained at the target value (for example, 20 ° C.) in the heat collector 10. For example, in winter, the temperature of the heat source water (for example, 15 ° C.) flowing from the evaporator 24 in the heat collector 10 is set to 20 ° C. when returning to the evaporator 24. The control unit 13 controls the valve mechanism 35, and when the flow path is switched to the third flow path L3, the heat source water reduces the heat release amount of the pre-cooler 10 so that the temperature detected by the temperature sensor 42 is maintained at 20 ° C. (See FIG. 5).

As described above, the dehumidifier 1 according to the embodiment includes the desiccant rotor 6, the pre-cooler 7, the heat collector 10, the heat pump device 8 that uses the amount of heat collected from the outside air as a heat source, and the heat amount. The control unit 13 includes a sensor 42 for detecting, the valve adjustment mechanism 11, and the control unit 13 for controlling the valve adjustment mechanism 11 so that a detection result of the sensor 42 becomes a target value.
Specifically, the dehumidifier 1 is provided in the processing air chamber 2 and the regeneration air chamber 3 and the processing air chamber 2 disposed adjacent to each other, and forms a processing air flow inside the processing air chamber 2. A fan 4, a regeneration fan 5 provided in the regeneration air chamber 3 to form a regeneration air flow inside the regeneration air chamber 3, a desiccant rotor 6 disposed across the processing air chamber 2 and the regeneration air chamber 3, A pre-cooler 7 provided in the processing air chamber 2 for pre-cooling (cooling and dehumidifying) the processing air upstream of the desiccant rotor 6; and a heat collector provided in the regeneration air chamber 3 and collecting heat from the regeneration air downstream of the desiccant rotor 6. 10, a heat pump device 8 having an evaporator 24 for exchanging heat between a heat source and a refrigerant for cooling the precooler 7 and heating the regeneration air upstream of the desiccant rotor 6, and a precooler for transferring the heat source from the evaporator 24. And a first flow path L1 through which the heat source that has passed through the precooler 7 flows into the evaporator 24, and a heat source that flows from the evaporator 24 into the precooler 7, and the heat source that has passed through the precooler 7 flows into the evaporator 24. A part of the heat source that has passed through the pre-cooler 7 flows into the heat collector 10 and the heat source that has passed through the heat collector 10 flows through the evaporator 24; 7. A valve adjusting mechanism 11 that can switch between a third flow path L3 that flows through the heat collector 10 in the order of the heat collector 10 and the heat source body that has passed through the heat collector 10 to the evaporator 24, and a heat source body that flows through the evaporator 24. And a control unit 13 that controls the valve adjustment mechanism 11 so that the temperature detected by the temperature sensor 42 becomes a target value.

According to this configuration, it is possible to provide the dehumidifier 1 that stably performs dehumidification under any external air conditions, and that does not require an external Freon-based refrigerant cooling device at low cost.
In this device, for example, control is performed as in the following (I) to (III).
(I) Since the outside air temperature (the temperature of the processing inlet 15) is higher in summer than in winter, cooling and dehumidification and heat collection are performed by the precooler 7. In the summer, the temperature detected by the temperature sensor 42 can be maintained at the target value only by collecting heat from the precooler 7, and the amount of heating required for the heat pump device 8 can be secured. In addition, since the desiccant rotor 6 performs dehumidification in addition to cooling and dehumidification by the precooler 7, processing air with low dehumidification can be stably supplied.
(II) Since the outside air temperature (the temperature at the processing inlet 15) is lower in the intermediate period (spring and autumn) between summer and winter than in summer, the frequency of cooling and dehumidification in the precooler 7 is reduced, and thus the amount of heat collected is also reduced. Decrease. In the interim period, a part of the heat source is flowed to the heat collector 10, and the heat collected by the pre-cooler 7 secures the amount of heat insufficient. As a result, even in the intermediate period, the detection result of the temperature sensor 42 can be maintained at the target value, and the necessary heating amount can be obtained. Further, the processing air with low dehumidification can be stably supplied only by the dehumidification by the desiccant rotor 6.
(III) In winter, cooling and dehumidification in the pre-cooler 7 is no longer necessary, and it becomes difficult to collect heat. As a result, the detection result of the temperature sensor 42 can be maintained at the target value even in winter, and the necessary heating amount can be obtained. Subsequently, the processing air with low dehumidification can be stably supplied only by the dehumidification by the desiccant rotor 6.

From the above, regardless of the outside air condition (outside air temperature), the required low dehumidification processing air can be secured throughout the year, and the heating amount required for the heat pump device 8 is always secured almost quantitatively. Regeneration of the rotor 6 is also possible.
In other words, in the summer period (pre-cooler 7), the middle period (pre-cooler 7 and the heat collector 10), and in the winter (heat collector 10), an environment capable of performing cooling and dehumidification and heat collection is configured and controlled, so that evaporation is performed. For example, the heat source of, for example, 15 ° C. coming out of the vessel 24 can always be returned to the evaporator 24 at 20 ° C. at any time. Thereby, the operation of the heat pump device 8 can be kept constant (evaporation temperature is kept constant) at any time, and the operation can be performed without affecting the heating amount as much as possible.

In the above embodiment, the precooler 7 has both a cooling / dehumidifying function and a heat collecting function, and the control unit 13 controls the valve adjusting mechanism 11 and collects heat from the heat collector 10 when the amount of heat collected by the precooler 7 is insufficient. Heating has the following effects.
For example, in Patent Document 2, cooling and dehumidification are performed by a pre-cooler provided outside, and heat collection is performed by an air cooler inside the apparatus. On the other hand, according to this configuration, since the pre-cooler 7 in the apparatus has both the cooling and dehumidifying function and the heat collecting function, it is possible to reduce the number of parts and the cost.

In the above embodiment, the valve adjusting mechanism 11 has a first pipe 31 having each end connected to the evaporator 24 and the precooler 7, respectively, and allowing a heat source to flow into the precooler 7 from the evaporator 24; Are connected to the precooler 7 and the evaporator 24, respectively, and the second pipe 32 that allows the heat source to flow from the precooler 7 to the evaporator 24, and each end is connected to the second pipe 32 and the heat collector 10, respectively. The connection between the third pipe 33 that allows at least a part of the heat source body that has passed through the precooler 7 to flow into the heat collector 10, each end having the heat collector 10, and the third pipe 33 in the second pipe 32. A fourth pipe 34 connected to a position downstream of the position and allowing the heat source passing through the heat collector 10 to flow into the evaporator 24; a first flow path L1 and a second flow path L2; Valve mechanism 3 capable of switching with third flow path L3 When, by providing the the following effects.
According to this configuration, dehumidification can be performed stably in a configuration in which the evaporator 24, the precooler 7, and the heat collector 10 are connected in series by piping and the valve mechanism 35 is provided.

  In the above embodiment, since the heat pump device 8 is disposed outside the regeneration air chamber 3, the valve adjustment mechanism 11 (such as piping) is compared with a configuration in which the heat pump device 8 is disposed inside the regeneration air chamber 3. ) Can increase the degree of freedom in layout.

  In the above embodiment, since the refrigerant is carbon dioxide, a natural refrigerant is used, and a CFC-based refrigerant is not used, which is suitable for global warming countermeasures.

  In the above embodiment, since the heat source body is water, water has a higher heat transfer coefficient than air, so that the COP (Coefficient Of Performance) of the dehumidifier 1 is easily improved.

[Modification]
In the above embodiment, the example in which only the valve mechanism 35 is provided in the second pipe 32 has been described, but the present invention is not limited to this. For example, a valve other than the valve mechanism 35 may be provided in the second pipe 32.

For example, as shown in FIG. 6, the valve adjustment mechanism 111 may further include a valve 45 provided between the connection position of the third pipe 33 and the connection position of the fourth pipe 34 in the second pipe 32. Good. The control unit 13 controls opening and closing of the valve 45.
According to this configuration, by controlling the opening and closing of the valve 45, the pressure loss between the connection position of the third pipe 33 and the connection position of the fourth pipe 34 in the second pipe 32 can be adjusted. Accordingly, it is possible to suppress a difference in pressure loss between summer and winter (the first flow path L1 and the third flow path L3).

For example, the dehumidifier 101 may further include a hot air temperature detection sensor 46 that detects the temperature of hot air flowing from the heat pump device 8 to the desiccant rotor 6. The control unit 13 may control the regeneration fan 5 such that the temperature detected by the hot air temperature detection sensor 46 becomes the target hot air temperature.
According to this configuration, the temperature of the hot air flowing from the heat pump device 8 toward the desiccant rotor 6 can be adjusted to the target hot air temperature regardless of the outside air condition, so that the heating amount of the heat pump device 8 can be kept within a certain range. Therefore, dehumidification can be performed more stably under any external air condition.
For example, the control unit 13 makes the rotation of the reproduction fan 5 slower as the outside air temperature is lower and the temperature of the hot air is lower so that the detection temperature of the hot air temperature detection sensor 46 becomes the target hot air temperature. For example, the control unit 13 makes the rotation of the reproduction fan 5 faster as the outside air temperature is higher and the temperature of the hot air is higher so that the detection temperature of the hot air temperature detection sensor 46 becomes the target hot air temperature.

  In the above embodiment, an example in which only one precooler 7 is provided in the processing air chamber 2 has been described, but the present invention is not limited to this. For example, a plurality of precoolers may be provided in the processing air chamber 2.

For example, as shown in FIG. 7, the dehumidifier 201 may further include a second precooler 150 provided in the processing air chamber 2 and precooling the processing air upstream of the desiccant rotor 6 and downstream of the precooler 7.
According to this configuration, since the absolute humidity of the processing air sent to the desiccant rotor 6 can be further reduced as compared with the configuration having only one precooler 7, the dehumidifying effect as a whole can be further improved. Can be.

  7, reference numeral 159 denotes a refrigerator, reference numeral 160 denotes a refrigerant circulation line connected to the second precooler 150 and the refrigerator 159, and reference numeral 161 denotes an outward path of the refrigerant circulation line 160 in which refrigerant flows from the refrigerator 159 to the second precooler 150. 162 denotes a return path of the refrigerant circulation line 160 in which the refrigerant flows from the second precooler 150 to the refrigerator 159, and 163 denotes a pump.

  In the above embodiment, an example in which the dehumidifier includes the heat collector 10 and the valve adjustment mechanism 11 has been described, but the present invention is not limited to this. For example, depending on conditions, the dehumidifier may not include the heat collector 10 and the valve adjustment mechanism 11. For example, in summer, the temperature detected by the temperature sensor 42 is maintained at the target value by collecting heat only from the pre-cooler 7, and dehumidification can be performed stably.

  In the above-described embodiment, an example has been described in which the evaporator 24, the precooler 7, and the heat collecting device 10 are connected in series by piping, but the present invention is not limited to this. For example, the evaporator 24 and the precooler 7 and the radiator 24 and the heat collector 10 may be connected in parallel by piping.

Next, another embodiment of the present invention will be described with reference to FIG. The same components as those of the previous embodiment are denoted by the same reference numerals, and the above description is referred to.
The dehumidifier 301 of this embodiment includes a desiccant dehumidifier 303 having a processing air chamber 2 and a regeneration air chamber 3, a precooler 308 for cooling and supplying outside air to an inlet P1 of the processing air chamber 2, A heat pump device 8 for supplying high-temperature air to an inlet P5 of the air conditioner, and an aftercooler 312 for further cooling the air after cooling and dehumidification derived from the processing air chamber 2.

  The feature of this embodiment is that the cold generated by the heat pump device 8 is supplied to the aftercooler 312, and the air cooled and dehumidified by passing through the desiccant rotor 6 is further cooled by the aftercooler 312.

  The processing air chamber 2 and the regeneration air chamber 3 of the desiccant dehumidifier 303 are separated by a partition 14. The disc-shaped desiccant rotor 6 penetrates vertically through a rectangular opening formed in the partition 14. Have been. One semicircle of the desiccant rotor 6 protrudes into the processing air chamber 2, and the other semicircle protrudes into the regeneration air chamber 3. The desiccant rotor 6 is rotatable around a rotation shaft 6b penetrating the center thereof, and the rotation shaft 6b is arranged in parallel with the partition 14. The desiccant rotor 6 is rotated at a low speed by a motor (not shown).

  In the regeneration air chamber 3, an electric heater 302 is disposed on the upstream side of the desiccant rotor 6, heats air supplied from the upstream side, and supplies high-temperature air to a semicircular portion of the desiccant rotor 6, The desiccant rotor 6 removes moisture adsorbed in the processing air chamber 2. In the regeneration air chamber 3, a regeneration fan 304 is disposed downstream of the desiccant rotor 6, and exhausts hot high-temperature air passing through the desiccant rotor 6 from an outlet P <b> 7 of the regeneration air chamber 3.

  The heat pump device 8 arranged upstream of the inlet P5 of the regeneration air chamber 3 has a compressor 21, a condenser 22, an expansion valve 23, and an evaporator 24 therein, and circulates a refrigerant filled with carbon dioxide as a refrigerant. These are connected sequentially in line 20. When the carbon dioxide pressurized by the compressor 21 circulates through the refrigerant circulation line 20, the carbon dioxide is pressurized in the condenser 22 to generate heat, while being decompressed in the evaporator 24 to generate cold heat.

  Air is supplied to the condenser 22 from the inlet P2 of the heat pump device 8 via a filter 28. The air exchanges heat with carbon dioxide generated in the condenser 22 and is heated. It is introduced into the electric heater 302 through the inlet P5.

  The evaporator 24 is connected to an aftercooler 312 via a first pipe 322 and a second pipe 324. The circulation flow path is filled with water as a heat source, and the evaporator 24 is Water is circulated in the order of the two pipes 324, the aftercooler 312, and the first pipe 322. The water deprives the evaporator 24 of the cold heat, cools the air flowing in the aftercooler 312, returns to the evaporator 24 via the pump 320, and is cooled again.

  The air cooled by the aftercooler 312 is introduced into the switching damper 314. The switching damper 314 includes a pair of dampers 316 and 318, and by opening the first damper 316, cooling air is supplied to a refrigerator or the like to be cooled. On the other hand, by opening the second damper 318, the air is exhausted to the outside. If the air supplied from the aftercooler 312 is not sufficiently dehumidified in the early stage of the operation, the damper 316 is closed and the damper 318 is opened, and the air is exhausted to the outside without supplying the air into the refrigerator. Prevent condensation. When the air from the after cooler 312 has been sufficiently dehumidified, the damper 318 is closed and the damper 316 is opened to supply the air into the refrigerator.

  The precooler 308 is connected to another cooling facility 326 through a coolant circulation path 328, and a coolant such as water is circulated between the precooler 308 and the cooling facility 326. The precooler 308 cools air taken in from the outside via the filter 310 by heat exchange with a refrigerant, and supplies precooled air to the processing air chamber 2 from the inlet P1.

  The operation of the dehumidifier 301 will be described. The following conditions are examples for explaining the effects of the present invention, and the present invention is not limited to the following conditions. It is assumed that the outside air temperature is 35 ° C. and the relative humidity is 60.0% RH. After the outside air is removed through a filter 310, the outside air is cooled by a pre-cooler 308, and is set to a temperature of 5 ° C., a relative humidity of 95.0% RH, and a low temperature and high humidity state. When the low-temperature and high-humidity air passes through the desiccant rotor 6 through the processing fan 306, most of the moisture is absorbed by the adsorbent carried on the adsorption surface 6a of the desiccant rotor 6. Since the adsorbent generates heat when absorbing water, the temperature of the air passing through the desiccant rotor 6 becomes 26.7 ° C., and the relative humidity drops to 1.1% RH. The dew point at this time reaches -30 ° C DP.

  The dehumidified air is then introduced into the aftercooler 312 and cooled by the water cooled by the evaporator 24 to a temperature of 10 ° C. and a relative humidity of 3.1% RH. Supplied.

On the other hand, the portion of the desiccant rotor 6 to which moisture has been adsorbed moves to the regeneration air chamber 3 as the desiccant rotor 6 rotates. Regeneration in the regeneration air chamber 3 is performed as follows.
Outside air having an outside air temperature of 35 ° C. and a relative humidity of 60.0% RH is removed through a filter 28 and supplied to the heat pump device 8. In the heat pump device 8, the air passes through the condenser 22 and is heated to about 120 ° C. The heated air is further heated through the electric heater 302 and reaches about 140 ° C. before being supplied to the desiccant rotor 6. Moisture is removed as hot air passes through the desiccant rotor 6, and the air containing moisture is discharged from the outlet P7 by the regeneration fan 304 to the outside.

  In the heat pump device 8, the compressor 21 circulates carbon dioxide, and the carbon dioxide pressurized in the condenser 22 generates heat, heats the air passing through the condenser 22, and releases heat. The pressure is reduced by the evaporator 24 through the expansion valve 23, and cool water is generated to supply cold water to the aftercooler 312. By performing the above operations continuously, the dehumidifier 301 can continuously supply the cool air dehumidified to the low dew point (−25 ° C. DB or less) to the refrigerator.

  According to the dehumidifying device 301 having the above-described configuration, the use of the heat pump device 8 can save, for example, about 30% of electric power as compared with the case where the entire device is heated by the electric heater. Is supplied to the aftercooler 312 and can be used to further cool the dehumidified air, and is highly energy efficient.

  Further, regardless of the outside air temperature, for example, even when the outside air temperature is as low as about 0 ° C., since the desiccant rotor 6 generates heat due to the adsorption of moisture to the adsorbent, the temperature of the air that has passed through the desiccant rotor 6 Temperature of the air to be supplied to the Therefore, since a cooling load is always generated in the aftercooler 312 irrespective of the outside air temperature, the aftercooler 312 can always be operated. Therefore, it is possible to effectively consume the cold generated in association with the high temperature generated by the heat pump device 8, and it is possible to increase the overall energy efficiency of the dehumidifier 301.

  In the above embodiment, an example in which water is used as the heat source has been described, but the present invention is not limited to this. For example, brine may be used as the heat source.

  In the above embodiment, the example in which the air-conditioning room, which is the demand destination of the processing air, is applied to a foundry or a refrigerator has been described. However, the present invention is not limited to this. For example, the air-conditioning room may be applied to any application such as an automobile painting factory, a loading space of a bulk ship, a food manufacturing site for confectionery and the like.

  Further, the technical scope of the present invention is not limited to the above-described embodiment, and various changes can be made without departing from the spirit of the present invention.

  Hereinafter, the present invention will be described more specifically with reference to Examples, but the present invention is not limited to the following Examples.

The inventor has confirmed that by setting each element of the dehumidifier of the embodiment to predetermined conditions, it is possible to obtain processing air having a low relative humidity at the outlet (processing outlet) of the desiccant rotor.
In each example, carbon dioxide was used as the refrigerant, and water (heat source water) was used as the heat source. The heat source water was circulated only in the first flow path (hereinafter, referred to as “heat source body circulation line”).

(Example 1)
As the dehumidifying device of Example 1, the dehumidifying device 1 of the embodiment (see FIG. 1) was used.
The conditions of the processing inlet (position P1 in the figure) were as follows: the temperature of the outside air was 35.0 ° C., the relative humidity was 60.0%, the absolute humidity was 21.45 g / kg (DA), and the air flow was 5300 m ³ / h.
The conditions of the regeneration inlet (position P2 in the figure) were as follows: the temperature of the outside air was 32.0 ° C., the relative humidity was 71.0%, the absolute humidity was 21.45 g / kg (DA), and the air flow was 5100 m ³ / h.
The flow rate of the heat source water circulating in the heat source body circulation line was 200 L / min.
The external static pressure was 500 Pa.

The air downstream of the precooler and upstream of the processing fan (position P3 in the drawing) had a temperature of 18.2 ° C., a relative humidity of 95.0%, and an absolute humidity of 12.44 g / kg (DA).
The air downstream of the processing fan and upstream of the desiccant rotor (position P4 in the figure) had a temperature of 19.2 ° C. and an absolute humidity of 12.44 g / kg (DA).
The air downstream of the heat pump device and upstream of the desiccant rotor (position P5 in the figure) had a temperature of 85.0 ° C.
The air downstream of the desiccant rotor and upstream of the regeneration fan (position P6 in the drawing) had a temperature of 57.0 ° C., a relative humidity of 25.6%, and an absolute humidity of 28.5 g / kg (DA).
The air at the exhaust port (position P7 in the drawing) had a temperature of 27.9 ° C., a relative humidity of 95.0%, and an absolute humidity of 22.67 g / kg (DA).
The temperature of the heat source water flowing in the outward path of the heat source body circulation line (the temperature of the heat source water inlet at the position P8 in the drawing) was 15.0 ° C.
The temperature of the heat source water flowing in the return path of the heat source body circulation line (the temperature of the heat source water outlet at the position P9 in the figure) was 20.0 ° C.

The air at the processing outlet (position P10 in the drawing) had a temperature of 45.9 ° C, a relative humidity of 9.3%, an absolute humidity of 5.76 g / kg (DA), and a dew point temperature of 6.0 ° C. The dehumidification amount was 27.0 kg / h.
Thereby, it turned out that the processing air with a low absolute humidity above normal temperature can be obtained.

(Example 2)
As the dehumidifier of Example 2, the dehumidifier 201 (see FIG. 7) according to the modification of the embodiment was used.
In Example 2, the conditions of the processing inlet, the conditions of the regeneration inlet, the flow rate of the heat source water circulating through the heat source body circulation line, and the external static pressure were the same as those in Example 1.

The air downstream of the precooler and upstream of the second precooler (position P11 in the figure) had a temperature of 18.2 ° C., a relative humidity of 95.0%, and an absolute humidity of 12.44 g / kg (DA).
The air downstream of the second precooler and upstream of the processing fan (position P12 in the figure) had a temperature of 15.0 ° C., a relative humidity of 95.0%, and an absolute humidity of 10.11 g / kg (DA).
The air downstream of the processing fan and upstream of the desiccant rotor (position P4 in the figure) had a temperature of 17.0 ° C. and an absolute humidity of 10.11 g / kg (DA).
The air downstream of the desiccant rotor and upstream of the regeneration fan (position P6 in the drawing) had a temperature of 57.0 ° C., a relative humidity of 25.6%, and an absolute humidity of 28.5 g / kg (DA).
The temperature of the refrigerant flowing in the outward path of the refrigerant circulation line (refrigerant inlet temperature at the position P13 in the drawing) was 7.0 ° C.
The temperature of the refrigerant flowing through the return path of the refrigerant circulation line (the temperature of the refrigerant outlet at the position P14 in the drawing) was 12.0 ° C.
In Example 2, the measurement results at the other positions (air downstream of the heat pump device and upstream of the desiccant rotor, air at the exhaust port, temperature of the heat source water flowing in the outward path of the heat source circulation line, and the heat source circulation line (The temperature of the heat source water flowing through the return path) was the same measurement result as in Example 1.

  In Example 2, the air at the processing outlet (position P10 in the drawing) had a temperature of 41.1 ° C., a relative humidity of 8.9%, and an absolute humidity of 4.32 g / kg (DA). Thereby, it turned out that the processing air whose absolute humidity is lower than that of Example 1 can be obtained.

1, 101, 201: dehumidifier, 2: processing air chamber, 3: regeneration air chamber, 4: processing fan, 5: regeneration fan, 6: desiccant rotor, 7: precooler, 8: heat pump device, 9: heat source body circulation Line: 10: Heat collector, 11, 111: Valve adjustment mechanism, 13: Control unit, 24: Evaporator, 31: First pipe, 32: Second pipe, 33: Third pipe, 34: Fourth pipe, 35 valve mechanism, 42 temperature sensor (sensor), 45 valve, 46 hot air temperature detection sensor, 150 second precooler, L1 first flow path, L2 second flow path, L3 third , Dehumidifier, 302, electric heater, 303, desiccant dehumidifier, 304, regeneration fan, 306, processing fan, 308, precooler, 310, filter, 312, aftercooler, 314, switching damper, 316 ... group , 318 ... damper, 320 ... pump, 322 ... first pipe (passage), 324 ... second pipe (passage), 326 ... cooling equipment.

Claims (11)

A desiccant rotor,
With a precooler,
A heat collector,
A heat pump device that uses the amount of heat collected from outside air as a heat source,
A sensor for detecting the amount of heat,
A valve adjustment mechanism,
A control unit that controls the valve adjustment mechanism so that a detection result of the sensor becomes a target value. The pre-cooler has both a cooling and dehumidifying function and a heat collecting function,
2. The dehumidifier according to claim 1, wherein the controller controls the valve adjustment mechanism to collect heat from the heat collector when the amount of heat collected by the precooler is insufficient. 3. The apparatus further includes a hot air temperature detection sensor that detects a temperature of hot air flowing from the heat pump device toward the desiccant rotor,
The dehumidifier according to claim 1, wherein the control unit controls the regeneration fan such that a temperature detected by the hot air temperature detection sensor becomes a target hot air temperature.   The dehumidifier according to any one of claims 1 to 3, further comprising a second precooler provided in the processing air chamber and precooling the processing air upstream of the desiccant rotor and downstream of the precooler.   The dehumidifier according to any one of claims 1 to 4, wherein the heat pump device is arranged outside a regeneration air chamber. The heat pump device includes an evaporator that exchanges heat between a heat source and a refrigerant for cooling the precooler,
The dehumidifier according to any one of claims 1 to 5, wherein the refrigerant is carbon dioxide. The heat pump device includes an evaporator that exchanges heat between a heat source and a refrigerant for cooling the precooler,
The dehumidifier according to any one of claims 1 to 6, wherein the heat source is water or brine. A pre-cooler for cooling the air to be dehumidified by heat exchange with a heat source,
A desiccant rotor that adsorbs moisture in the air by being brought into contact with the air cooled by the precooler and dehumidifies the air,
A compressor, a condenser, an expansion valve and an evaporator are provided, and air is heated by the heat generated in the condenser by circulating a refrigerant through these, and the heated air is removed from the moisture adsorbed by the desiccant rotor. A heat pump device for supplying for removal,
A flow path for circulating the heat source body cooled by heat exchange with the refrigerant in the evaporator to the precooler. A heat collector that heats the heat source body by exchanging heat between the air and the heat source body from which moisture adsorbed on the desiccant rotor has been removed,
A valve adjustment mechanism for returning a part or all of the heat source body returning from the precooler to the evaporator to the evaporator through the heat collector,
A sensor for measuring the temperature of the heat source body,
A control unit that controls the valve adjustment mechanism so that the detection result of the sensor becomes a target value and adjusts a flow rate of the heat source body that returns to the evaporator via the heat collector. The dehumidifier according to claim 8, wherein A desiccant rotor that adsorbs moisture in the air by being brought into contact with air to be dehumidified and dehumidifies the air,
A compressor, a condenser, an expansion valve and an evaporator are provided, and air is heated by the heat generated in the condenser by circulating a refrigerant through these, and the heated air is removed from the moisture adsorbed by the desiccant rotor. A heat pump device for supplying for removal,
A dehumidifier, comprising: an aftercooler that cools air dehumidified by the desiccant rotor using cold heat generated in the evaporator. A heater that further heats the air heated by the heat pump device and supplies the air to remove moisture adsorbed on the desiccant rotor,
The dehumidifier according to claim 10, further comprising: a precooler that cools air to be dehumidified and then contacts the desiccant rotor.

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