JP2011218285A - Dehumidifier - Google Patents

Abstract

PROBLEM TO BE SOLVED: To lower the motive energy of a blower of a dehumidifier by adjusting an aeration temperature to the temperature equivalent to that of indoor air or a prescribed level and also by lessening the pressure loss of the air passing through a moisture adsorption system.SOLUTION: The dehumidifier 100 is constituted such that the downstream air of a moisture adsorption system 10 in a first air flow path 1a and that of a second cooling system 30b in a second air flow path 1b are heat-exchanged with each other to discharge.

Description

  The present invention relates to a dehumidifying device.

Various types of dehumidifying devices have been proposed that include a desiccant rotor (moisture adsorbing means) that is circular and has a vent in parallel with the thickness direction. This desiccant rotor absorbs moisture contained in the air, and has a property of releasing moisture into the air when exposed to dry air. Then, a shaft is provided at the center of the desiccant rotor so that the desiccant rotor can be driven rotatably. The desiccant rotor is disposed so as to straddle a region where the humid air taken into the dehumidifier is vented and a region where a heat source (for example, a heater) is ventilated by the dry air.
In other words, the desiccant rotor can continuously perform absorption of moisture in the air with high humidity and release of moisture absorbed inside the desiccant rotor by rotating the shaft. ing.

As such, “a heat pump having a heat absorber that absorbs heat from the supply air, a heat radiator that dissipates heat to the heat absorption air, a moisture absorption portion that absorbs moisture from the supply air, and a moisture release portion that dehumidifies the supply air” Means for heating the dehumidification control air by heat radiation of the radiator, humidifying the heated dehumidification target air by dehumidification of the moisture release section, and cooling the humidified dehumidification target air by heat absorption of the heat absorber. A dehumidifying device that dehumidifies the cooled air to be dehumidified by moisture absorption by the moisture absorbing section has been proposed (see Patent Document 1).
This dehumidifier is configured to vent and release the taken-in air in the order of heating means, moisture adsorption means (moisture desorption section), cooling means, and moisture adsorption section (moisture adsorption section).

Further, “a vapor compression heat pump in which a compressor that compresses refrigerant, a radiator that radiates heat to the supply air, an expansion mechanism that expands and decompresses the refrigerant, and a heat absorber that absorbs heat from the supply air are connected by piping. A desiccant rotor that is rotated by the driving means and absorbs moisture from the supply air in the moisture absorption region and is heated in the moisture release region to release moisture, and the indoor air is supplied to the radiator, the moisture release region, the heat absorber, In a dehumidifying device that supplies moisture absorption regions in order and performs a dehumidifying operation, the dehumidifying device includes frost prediction means for predicting the frost formation state of the heat absorber, and when the frost prediction means predicts frost formation of the heat absorber, There has been proposed a dehumidifying device that performs a dehumidifying operation while suppressing frost formation of a heat absorber (see Patent Document 2).
In this dehumidifying device, a first cooling means 30a and a second cooling means 30b are arranged in the adsorption area of the moisture adsorption means and the desorption area of the moisture adsorption means, respectively, and two channels of air flowing therethrough are provided. It is the composition which divides into.

In addition, a heat pump in which a compressor that compresses refrigerant, a radiator that radiates heat to the supply air, a decompression mechanism that expands and decompresses the refrigerant, and a heat absorber that absorbs heat from the supply air are connected by piping, and driving means. A desiccant rotor that rotates and absorbs moisture from the supply air in the moisture absorption region and is heated in the regeneration region to release moisture, and indoor air is supplied in the order of the radiator, the regeneration region, the heat absorber, and then the moisture absorption region. A blower is provided, and the desiccant rotor and the heat absorber are arranged side by side so that their ventilation surfaces face each other, and the indoor air that has passed through the regeneration region passes through a first heat absorption region that forms part of the heat absorber. The air blowing direction is reversed later, and the heat absorption device is configured to supply the moisture absorption region through a second heat absorption region other than the first heat absorption region. Hybrid-type dehumidifier. Has been proposed as such "(see Patent Document 3).
In this dehumidifier, air passes through one air flow path in the order of the heating means and the adsorption portion of the moisture adsorption means. In the other air flow path, the desorption part of the moisture adsorption means, the cooling means, and the adsorption part of the moisture adsorption means are arranged in this order.

Japanese Patent Laying-Open No. 2005-34838 (1 page, FIG. 1) JP 2008-207046 A (1 page, FIG. 1) Japanese Patent Laid-Open No. 2008-80233 (1 page, FIG. 1)

  In the conventional dehumidifying device, the moisture adsorbing means provided in the dehumidifying device dissipates heat during moisture adsorption, so that the temperature of the supply air may be higher than the room temperature. In addition, when the moisture adsorbing means is ventilated, the pressure loss increases, and the power of the air blowing means increases.

  The present invention has been made to solve the above-described problems, and has a first object of adjusting the temperature of the supply air to be equal to or a predetermined temperature as room air. A second object is to reduce the pressure loss of the air passing through the moisture adsorbing means and to reduce the power of the blowing means.

  The dehumidifying device according to the present invention is a dehumidifying device in which a first air flow path and a second air flow path are formed, and is disposed in the first air flow path and the second air flow path, and the first air flow path Moisture adsorption means for adsorbing moisture from the air flowing through the flow channel and desorbing the moisture to the second air flow channel, and air blowing that takes in and exhausts air through the first air flow channel and the second air flow channel Means, a first cooling means provided upstream of the moisture adsorption means in the first air flow path, for cooling the air flowing through the first air flow path, and the moisture adsorption means in the second air flow path. A heating means for heating air flowing in the second air flow path provided upstream; and air flowing in the second air flow path provided downstream of the moisture adsorption means in the second air flow path. A second cooling means for cooling, the water adsorption means of the first air flow path In the air flow, downstream of the air of the second cooling means of the second air passage, is exhausted from by heat exchange.

  According to the dehumidifying apparatus of the present invention, the comfort of the user is improved because the temperature of the air supply is adjusted to the room air equivalent or a predetermined temperature. In addition, since the pressure loss of the air passing through the moisture adsorbing means is reduced, the power of the air blowing means is reduced and energy is saved.

It is a schematic diagram which shows schematic structure of the dehumidification apparatus which concerns on Embodiment 1 of this invention. It is a humid air line figure showing the operation state at the time of a driving | running of the dehumidification apparatus shown in FIG. It is a control block diagram of the dehumidifier shown in FIG. It is a schematic diagram which shows schematic structure of the dehumidification apparatus which concerns on Embodiment 2 of this invention. It is the figure showing the relationship between the moisture moving speed of the water | moisture content hold | maintained at the water | moisture-content adsorption | suction means of the dehumidifier shown in FIG. 4, and the wind speed of the air sent to a water | moisture-content adsorption | suction means. It is a schematic diagram which shows schematic structure of the dehumidification apparatus which concerns on Embodiment 3 of this invention. It is a Mollier diagram regarding the refrigerant circuit of the dehumidifier shown in FIG. FIG. 7 is a control block diagram of the dehumidifying device shown in FIG. 6.

Embodiment 1 FIG.
Embodiment 1 of the present invention will be described below with reference to the drawings.
FIG. 1 is a schematic diagram showing a schematic configuration of a dehumidifier according to Embodiment 1 of the present invention.
The dehumidifying apparatus 100 according to the first embodiment includes a first air channel 1a, a second air channel 1b, a moisture adsorbing unit 10, a heating unit 20, a first cooling unit 30a, a second cooling unit 30b, and a blowing unit. 40, at least.
An arrow AR1 represents the flow of air taken into the first air channel 1a or the second air channel 1b. RA represents the air returned to the room. SA represents air supplied into the room. SA1 represents the air downstream of the first air flow path 1a. SA2 represents the air downstream of the second air flow path 1b.

  The 1st air flow path 1a is a path | route through which the air taken in by the dehumidification apparatus 100 distribute | circulates in the order used as the 1st cooling means 30a and the water | moisture-content adsorption | suction means 10.

  The 2nd air flow path 1b is a path | route through which the air taken in into the dehumidification apparatus 100 distribute | circulates in the order used as the heating means 20, the moisture adsorption means 10, and the 2nd cooling means 30b. That is, the first air flow path 1a and the second air flow path 1b described above may be configured to independently take in RA, but as shown in FIG. You may become the structure branched to the path | route 1a and the 2nd air flow path 1b. Moreover, as shown in FIG. 1, SA1 and SA2 may be merged and exhausted, or may be independently exhausted after heat exchange.

  The blower means 40 forcibly takes air into the first air flow path 1a and the second air flow path 1b. In the first embodiment of the present invention, the air blowing means 40 is arranged on the most downstream side of the first air flow path 1a and the second air flow path 1b, but the predetermined air volume is the first air flow path 1a and the first air flow path 1b. Since it should just be obtained by the 2 air flow path 1b, you may arrange | position in the most upstream etc., and the arrangement position of the ventilation means 40 shall not be limited.

  The air blowing means 40 may be anything that can control the air volume, and in that case, for example, the air volume can be set according to the air condition. The air volume control can be performed by controlling the rotational speed using a DC motor as a motor for rotating the fan. Further, in the AC motor, the air volume can be controlled by changing the number of revolutions by changing the power supply frequency by inverter control.

  Further, the flow rate of air passing through the moisture adsorbing means 10 is also changed by controlling the air volume of the blowing means 40. The moisture transfer speed between the air and the adsorbent during adsorption and desorption of the moisture adsorption means 10 increases as the air flow rate increases. Can be increased.

  The moisture adsorbing means 10 is provided in the middle of the first air channel 1a so as to adsorb moisture contained in the air taken into the first air channel 1a, and is also introduced into the second air channel 1b. What is necessary is just to be provided in the middle of the 2nd air flow path 1b so that a water | moisture content may be remove | desorbed to air. In the first embodiment, the moisture adsorbing means 10 is described as being provided in the first air channel 1a and the second air channel 1b as a single body. However, the present invention is not limited to this, and a plurality of moisture adsorbing units are provided. Means 10 may be provided.

  As the moisture adsorbing means 10 in the first embodiment, for example, a desiccant rotor in which an adsorbent is formed in a rotor shape may be applied. The desiccant rotor is a rotor having a honeycomb structure or a corrugated structure having air permeability in the rotation axis direction, and has a motor rotation mechanism. Also, the rotational speed of the rotor can be controlled by changing the rotational speed using a DC motor as the motor used for the rotating mechanism, or by changing the rotational speed by changing the power supply frequency by inverter control in the AC motor. It is. Therefore, the rotational speed of the rotor can be controlled according to the air condition and the air volume of the dehumidifying device 100.

  An adsorbent is supported on the surface of the rotor in contact with the air in the first air flow path 1a and the second air flow path 1b of the moisture adsorbing means 10 so that moisture can be adsorbed and desorbed continuously. (Moisture is adsorbed by the first air flow path 1a, and water is desorbed by the second air flow path 1b). As the adsorbent of the moisture adsorbing means, for example, a zeolite, mesoporous silica, a polymer sorbent or the like that is applied, surface-treated or impregnated on a porous rotor substrate may be used.

  The first cooling means 30a is provided upstream of the moisture adsorption means 10 in the first air flow path 1a. The 1st cooling means 30a has a function which cools the air which flows into the 1st air flow path 1a. The first cooling means 30a is provided with a first temperature sensor.

The heating means 20 is provided upstream of the moisture adsorption means 10 in the second air flow path 1b. The heating means 20 has a function of heating the air flowing into the second air flow path 1b. The heating means 20 is provided with a second temperature sensor.
The second cooling means 30b is provided downstream of the moisture adsorption means 10 in the second air flow path 1b. The 2nd cooling means 30b has a role which cools the air which flows in into the 2nd air flow path 1b, and condenses the water | moisture content of the air in air. The second cooling means 30b is provided with a third temperature sensor.

  The dehumidifying device 100 is provided with a first temperature / humidity sensor 2a and a seventh temperature / humidity sensor 2g. The first air flow path 1a is provided with a second temperature / humidity sensor 2b, a third temperature / humidity sensor 2c, and a second wind speed sensor 4b. The 2nd temperature / humidity sensor 2b is provided in the position between the 1st cooling means 30a and the water | moisture-content adsorption | suction means 10 which are mentioned later. The 3rd temperature / humidity sensor 2c is provided in the downstream of the moisture adsorption means 10 mentioned later of the 1st air flow path 1a. However, since the third temperature / humidity sensor 2c is intended to measure the temperature and humidity of the air that has passed through the moisture adsorbing means 10, it should not be provided extremely downstream of the moisture adsorbing means 10. The second wind speed sensor 4b is provided on the most downstream side of the first air flow path 1a. Since the second wind speed sensor 4b is intended to measure the wind speed of the air discharged from the second air flow path 1b, it is better not to be provided extremely upstream of the second air flow path 1b.

  The second air flow path 1b is provided with a fourth temperature / humidity sensor 2d, a fifth temperature / humidity sensor 2e, a sixth temperature / humidity sensor 2f, and a first wind speed sensor 4a. The fourth temperature / humidity sensor 2 d is provided between the heating means 20 and the moisture adsorption means 10. The fifth temperature / humidity sensor 2e is provided between the moisture adsorbing means 10 and the second cooling means 30b. The sixth temperature / humidity sensor 2f is provided downstream of the second cooling means 30b. Since the purpose of the sixth temperature / humidity sensor 2f is to measure the temperature and humidity of the air that has passed through the second cooling means 30b, the sixth temperature / humidity sensor 2f should not be provided extremely downstream of the second cooling means 30b.

  The first temperature / humidity sensor 2a is provided at a position where the temperature and humidity can be measured before the air taken into the dehumidifier 100 flows into the first air flow path 1a and the second air flow path 1b. ing. The seventh temperature / humidity sensor 2g is a temperature after heat exchange between the air downstream of the moisture adsorbing means 10 in the first air passage 1a and the air downstream of the second cooling means 30b in the second air passage 1b. It is provided at a position where it can be measured.

The temperature / humidity after passing through the first cooling means 30a can be calculated from the measurement result of the first temperature / humidity sensor 2a and the measurement result of the first temperature sensor 3a.
The temperature and humidity after passing through the heating means 20 can be calculated from the measurement result of the first temperature / humidity sensor 2a and the measurement result of the second temperature sensor 3b.
The temperature and humidity of the air supplied to the room indicated by SA in FIG. 1 are detected values from the third temperature / humidity sensor 2c, the sixth temperature / humidity sensor 2f, the first wind speed sensor 4a, and the second wind speed sensor 4b. It is possible to calculate by In the first embodiment, the first temperature / humidity sensor 2a, the second temperature / humidity sensor 2b, and the seventh temperature / humidity sensor 2g are described as being provided in the dehumidifier 100, but are not necessarily required. .

  In addition, each temperature and humidity sensor described above only needs to know one of the measurement area temperature and relative humidity, absolute humidity, dew point, or wet bulb temperature, and it can be measured by two sensors such as a dry bulb thermometer and a wet bulb thermometer. Good. That is, the number of temperature and humidity sensors provided in the dehumidifying device 100 is not particularly limited.

From FIG. 1, the temperature and humidity change of the air which distribute | circulates the 1st air flow path 1a is demonstrated.
The RA is taken into the dehumidifying device 100 by the blowing means 40 and flows into the first air flow path 1a, passes through the first cooling means 30a, and then is dehumidified by moisture adsorbed by the moisture adsorbing means 10. It becomes SA2 (adsorption dehumidified air). Thereafter, the heat is exchanged with SA1, which will be described later, and the heat is released from the dehumidifier. Various means can be considered for the heat exchange described above. For example, a method of mixing SA1 and SA2 and releasing it as SA can be considered.

Next, changes in temperature and humidity of the air flowing through the second air flow path 1b will be described.
RA is taken into the dehumidifying device 100 by the blowing means 40, flows into the second air flow path 1b, passes through the heating means 20, and then receives moisture desorbed from the moisture adsorbing means 10, and receives the second cooling means 30b. The air is dehumidified by being cooled to a dew point temperature or less by (cooled dehumidified air).

  The adsorbed dehumidified air downstream of the first air channel 1 a is dehumidified air that has been heated by the adsorption heat received from the moisture adsorbing means 10. Further, the cooled dehumidified air downstream of the second air flow path 1b is dehumidified air cooled by passing through the second cooling means 30b. In other words, by exchanging both the dehumidified air described above, it is possible to release air having the same temperature as the temperature of the taken-in air into the room.

  Moreover, although the ratio of the area of the 1st air flow path 1a and the 2nd air flow path 1b which faces the water | moisture-content adsorption | suction means 10 is set to 1: 1, you may change into arbitrary ratios.

Then, the 1st cooling means 30a located in the upstream of the moisture adsorption means 10 of the 1st air flow path 1a and the heating means 20 located in the upstream of the moisture adsorption means 10 of the 2nd air flow path 1b are demonstrated.
The heating means 20 and the first cooling means 30a installed upstream of the moisture adsorbing means 10 adjust the relative humidity of the air that flows to the moisture adsorbing means 10 and dehumidify the moisture adsorbing means 10 in order to increase the water exchange capacity. The apparatus 100 is provided. The rate of moisture adsorption and desorption of the moisture adsorbing means 10 is determined from the relative humidity difference and the air flow velocity when passing through the moisture adsorbing means 10 as shown in the following equation.

  As can be seen from the above formula, the greater the relative humidity difference between the air in the first air channel 1a and the second air channel 1b, the greater the amount of moisture exchange in the moisture adsorbing means 10. It should be noted that the relative humidity of air has the property that if the absolute humidity is the same, the relative humidity becomes lower when the air temperature is raised and becomes higher if the air temperature is lowered. Therefore, before the air in the first air flow path 1a passes through the moisture adsorption means 10, the temperature of the air is lowered in advance to increase the relative humidity. On the other hand, before the air in the second air flow path 1b passes through the moisture adsorption means 10, the air temperature is raised in advance to reduce the relative humidity. This increases the relative humidity difference. Therefore, as described above, the water exchange capacity (adsorption capacity and desorption capacity) is increased. That is, the dehumidifying capacity of the moisture adsorbing means 10 is increased.

  Next, the 2nd cooling means 30b installed in the downstream of the moisture adsorption means 10 of the 2nd air flow path 1b is demonstrated. The second cooling means 30b installed downstream of the moisture adsorption means 10 is provided for the purpose of cooling the air that has passed through the moisture adsorption means 10 to a dew point temperature or less and removing the moisture as condensed water. That is, it is not dehumidified by adsorbing moisture in the air that is vented to the moisture adsorbing means 10 as in the first air flow path 1a, but the air is cooled and contained in the air by the second cooling means 30b. Moisture is removed.

  The heating means 20 used in the first embodiment may use a heater, for example, and the output may be controlled by a thyristor unit. Moreover, the 1st cooling means 30a and the 2nd cooling means 30b use a brine cooler, for example, and set the temperature of supply air SA to the target temperature which set as shown in FIG. 1 by controlling refrigerant | coolant temperature. Is possible.

FIG. 2 is a moist air diagram showing the operating state of the dehumidifying device 100 shown in FIG. 1 during operation.
The dehumidifying operation of the first embodiment will be described with reference to FIG.
FIG. 2A is a wet air diagram showing the movement of the operating state in the first air passage 1a, and FIG. 2B is a wet air diagram showing the movement of the operating state in the second air passage 1b. Moreover, the states 1 to 7 indicating the state of air respectively correspond to the numbers (1) to (7) in FIG.

  As shown in FIG. 2A, the indoor air RA (state 1) introduced into the first air flow path 1a is sent to the first cooling means 30a. Here, the air flowing into the first air flow path 1a is first cooled by exchanging heat with the first cooling means 30a (state 2). At this time, since the cooled air has a relative humidity as high as about 80 to 100% RH, the moisture adsorbing means 10 can easily adsorb moisture. The cooled introduced air flows into the adsorption side region of the moisture adsorbing means 10 and becomes adsorption dehumidified air (state 3) in which moisture is adsorbed (dehumidified) by the adsorbent. The adsorbed dehumidified air and the cooled dehumidified air (state 6) of the second air flow path 1b described later exchange heat to become an air supply SA (state 7), which is supplied indoors.

  As shown in FIG. 2 (b), the room air RA (state 1) introduced into the second air flow path 1 b is sent to the heating means 20. Here, the air is heated by exchanging heat with the heating means 20 (state 4). At this time, since the heated air has a relative humidity as low as about 5 to 25% RH, the moisture adsorbing means 10 can easily desorb moisture. The heated air passes through the moisture adsorption means 10 and moisture is desorbed (humidified). The humidified air (state 5) is sent to the second cooling means 30b. The humidified air (state 5) is cooled by exchanging heat with the second cooling means 30b. At this time, the air is cooled below the dew point, so that the moisture in the air is condensed into water. That is, the air in (state 5) is dehumidified to become cooled dehumidified air (state 6). The cooled dehumidified air and the adsorbed dehumidified air (state 6) in the first air flow path 1a are heat-exchanged to become an air supply SA (state 7), which is supplied indoors.

  FIG. 3 is a control block diagram of the dehumidifying apparatus 100 shown in FIG. A measurement control system configuration using the above-described temperature and humidity sensors 2a to 2g, temperature sensors 3a to 3c, and wind speed sensors 4a to 4b is shown. These sensors are connected to a control board 5 that controls the dehumidifier 100. The control board 5 acquires information on the temperature, humidity, and wind speed measured by each sensor, the temperature of the heating means 20, the first cooling means 30a and the second cooling means 30b, the air volume of the blower means 40, and moisture. It is possible to control the rotation speed of the suction means 10.

  As described above, the dehumidifying device 100 according to Embodiment 1 is cooled by the air (SA1) in which moisture is adsorbed by the moisture adsorbing means 10 of the first air flow path 1a and the cooling means 30b of the second air flow path 1b. As a result, the dehumidified air (SA2) is heat-exchanged and released. SA1 is dehumidified air having a high temperature because it receives heat of adsorption when moisture is adsorbed by the moisture adsorbing means 10. On the other hand, SA2 is dehumidified air having a low temperature because it is cooled and dehumidified. As described above, by changing the ratio of heat exchange between SA1 and SA2, the temperature of the released air can be suppressed to, for example, the room temperature. Further, since the humidity of SA1 and SA2 is different, it goes without saying that the humidity can be controlled, for example, if SA1 and SA2 are mixed and exhausted.

  Further, in the first embodiment, the air passage pressure loss is reduced by dividing the air passage into two, and the number of times the water adsorbing means 10 having a larger pressure loss passes through the first air passage 1a and the second air. Since both of the flow paths 1b are once, it is possible to reduce the power to be blown with the same air volume, which can be said to be energy saving.

  Further, by individually controlling the cooling capacities of the first cooling means 30a and the second cooling means 30b, the place where condensation occurs can be limited to only the second cooling means 30b that performs cooling and dehumidification. It is possible to reduce the drain piping for water) discharge, and it is possible to make it compact.

Embodiment 2. FIG.
In the second embodiment, differences and features from the first embodiment will be described, and the same parts as those in the first embodiment will be omitted.
FIG. 4 is a schematic diagram showing a schematic configuration of the dehumidifying apparatus 100 according to Embodiment 2 of the present invention. In the second embodiment, instead of the air blowing means 40 of the first embodiment, the first air blowing means 40a and the second air flow path 1b of the first air flow path 1a are provided downstream of the adsorption portion of the water adsorption means 10. The 2nd ventilation means 40b is arrange | positioned downstream of the 2 cooling means 30b, and it can control now the air volume of the 1st air flow path 1a and the 2nd air flow path 1b.
An arrow AR1 represents the flow of air taken into the first air channel 1a or the second air channel 1b. RA represents the air returned to the room. SA represents air supplied into the room. SA1 represents the air downstream of the first air flow path 1a. SA2 represents the air downstream of the second air flow path 1b.

  FIG. 5 is a diagram showing the relationship between the moisture moving speed of the moisture held in the moisture adsorbing means 10 of the dehumidifying apparatus 100 shown in FIG. 4 and the wind speed of the air fed into the moisture adsorbing means 10. The vertical axis represents the moisture movement speed, and the horizontal axis represents the wind speed. The change in the absolute value of the moisture transfer rate is shown separately for the adsorption reaction and the desorption reaction.

  As shown in FIG. 5, the adsorption reaction and the desorption reaction often have different absolute values of the moisture movement speed even if the wind speed is the same. Therefore, in the case where the air volumes of the first air channel 1a and the second air channel 1b are equal, the moisture transfer rate is limited by either adsorption or desorption where the moisture transfer rate is low. Therefore, the air flow rates of the first air blowing means 40a and the second air blowing means 40b are individually changed, and the wind speed passing through the moisture adsorption means 10 is individually changed by adsorption and desorption. As a result, if the amount of moisture adsorbed in the air (adsorption reaction rate) in the first air channel 1a and the amount of moisture desorption (desorption reaction rate) in the second air channel 1b are made closer to each other, the efficiency is further increased. It is possible to increase the dehumidifying ability well.

Embodiment 3 FIG.
In the third embodiment, differences and features from the first and second embodiments will be described, and the same parts as those in the first and second embodiments will be omitted.
The configuration of the dehumidifying device 100 according to the third embodiment will be described with reference to FIGS.
FIG. 6 is a schematic diagram showing a schematic configuration of the dehumidifying apparatus 100 according to Embodiment 3 of the present invention.

  As shown in FIG. 6, the dehumidifying device 100 according to the third exemplary embodiment includes a refrigerant circuit 80 (a compressor 60, a first expansion valve 70a, a second expansion valve 70b, a condenser 50, and a first evaporator). 31a, the second evaporator 31b), the moisture adsorbing means 10, and the air blowing means 40. The condenser 50, the first expansion valve 70a, the first evaporator 31a, the second expansion valve 70b, the second evaporator 31b, and the suction side of the compressor 60 (the left side of the compressor 60 in FIG. 6) are arranged in this order in the refrigerant pipe. Are connected to form a refrigerant circuit 80. An arrow AR1 represents the flow of air taken into the first air channel 1a or the second air channel 1b. An arrow AR2 represents the flow direction of the refrigerant flowing through the refrigerant circuit 80. RA represents the air returned to the room. SA represents air supplied into the room. SA1 represents the air downstream of the first air flow path 1a. SA2 represents the air downstream of the second air flow path 1b.

  The heating means 20 in the first and second embodiments corresponds to the condenser in the third embodiment. The first cooling means 30a and the second cooling means 30b in the first and second embodiments correspond to the first evaporator 31a and the second evaporator 31b, respectively. That is, the 1st cooling means 30a, the 2nd cooling means 30b, and the heating means 20 are comprised with the heat exchanger.

  The condenser 50 is connected to the first evaporator 31a via the first expansion valve 70a. Furthermore, the first evaporator 31a is connected to the second evaporator 31b via the second expansion valve 70b. By controlling the opening / closing states of the first expansion valve 70a and the second expansion valve 70b, the first evaporator 31a and the second evaporator 31b can control the refrigerant evaporation temperatures as different temperatures. That is, the temperatures of the first evaporator 31a and the second evaporator 31b can be adjusted separately.

  The refrigerant used in the refrigerant circuit 80 is not limited and is used for natural refrigerants such as carbon dioxide, hydrocarbon or helium, refrigerants not containing chlorine such as HFC410A or HFC407C, or existing products. R22 or R134a or other chlorofluorocarbon refrigerant. For example, in the apparatus used in the refrigerant circuit 80, various types such as a reciprocating, a rotary, a scroll, or a screw can be applied to the compressor 60.

Next, the refrigerant circuit 80 will be described.
FIG. 7 is a Mollier diagram regarding the refrigerant circuit 80 of the dehumidifying apparatus 100 shown in FIG. 6. The vertical axis in FIG. 7 represents the refrigerant pressure. The vertical axis represents enthalpy. The refrigerant flow during operation in the refrigerant circuit 80 is first compressed by the compressor 60 and flows into the condenser 50 as a high-temperature and high-pressure gas. In the condenser 50, the refrigerant changes its phase from a high-temperature high-pressure gas to a liquid by exchanging heat with air. That is, the air taken into the dehumidifier 100 is heated by the condenser 50. Thereafter, the refrigerant is depressurized through the first expansion valve 70a, becomes a two-phase state in which low-temperature and low-pressure liquid and gas are mixed, and flows into the first evaporator 31a. In the first evaporator 31a, a part of the refrigerant changes phase from liquid to gas, and the air passing through the first evaporator 31a is cooled by exchanging heat with the refrigerant. Further, the refrigerant that has passed through the first evaporator 31a is further decompressed through the second expansion valve 70b in a two-phase state, and the air that passes through the second evaporator 31b is cooled by exchanging heat with the refrigerant. Thereafter, the refrigerant again flows into the compressor 60 and becomes a high-temperature and high-pressure gas again.

  As described above, in the third embodiment, by applying the heat pump to the air heating and cooling method, the dehumidification can be efficiently performed, and the frequency at which the refrigerant of the compressor 60 is sent to the refrigerant circuit 80. Alternatively, it is possible to change the evaporation temperature of the refrigerant by changing the opening states of the first expansion valve 70a and the second expansion valve 70b. From the above, it is possible to control the supply air SA temperature.

  Further, the second evaporator 31b disposed in the second air flow path 1b is disposed after passing through the expansion valve 70b in the flow of the refrigerant circuit 80, rather than the first evaporator 31a disposed in the first air flow path 1a. ing. Therefore, since the refrigerant passing through the second evaporator 31b passes through the expansion valve 70b, the pressure is lower than that of the refrigerant passing through the first evaporator 31a. Therefore, the refrigerant evaporation temperature of the second evaporator 31b is lower than the refrigerant evaporation temperature of the first evaporator 31a. For this reason, by disposing the second expansion valve 70b, the temperature in the second evaporator 31b of the second air flow path 1b is lowered, so that moisture in the air is further condensed. That is, it is possible to increase the dehumidification amount of the air in the second air flow path 1b. In addition, by controlling the evaporation temperature of the first evaporator 31a to be equal to or higher than the dew point temperature of the air passing through the first evaporator 31a, the location where water in the air condenses is limited to the second evaporator 31b. It is possible to reduce the drain piping of the first evaporator 31a and to make it compact.

  In Embodiment 3 of the present invention, one blowing means 40 is arranged on the most downstream side, but it may be arranged on the most upstream side as long as the target air volume of the two air flow paths can be obtained. As in the second embodiment, it may be arranged in each of the first air channel 1a and the second air channel 1b, and the arrangement position and the number of the air blowing means 40 are not limited.

  In Embodiment 3 of the present invention, the second expansion valve 70b is arranged to change the refrigerant evaporation temperature of the first evaporator 31a and the second evaporator 31b, but controls the temperature of the condenser 50. Thus, the refrigerant evaporation temperatures of the first evaporator 31a and the second evaporator 31b may be controlled. That is, the number of expansion valves in the refrigerant circuit 80 is not limited.

  In the third embodiment, instead of the temperature sensor used in the first and second embodiments, a fourth temperature sensor 3d for detecting the refrigerant pipe temperature of the condenser 50, and the refrigerant pipe temperature of the first evaporator 31a. A fifth temperature sensor 3e for detecting the refrigerant temperature, a sixth temperature sensor 3f for detecting the refrigerant pipe temperature of the second evaporator 31b, and a seventh temperature sensor 3g for detecting the discharge temperature on the discharge side of the compressor 60.

  FIG. 8 is a control block diagram of the dehumidifying apparatus 100 shown in FIG. The control block by these temperature / humidity sensors, temperature sensors, and wind speed sensors is shown. These sensors are connected to a control board 5 that controls the dehumidifier 100. The control board acquires information on these temperature, humidity, and wind speed, the frequency at which the refrigerant of the compressor 60 is sent to the refrigerant circuit 80, the open / close state of the first expansion valve 70a and the second expansion valve 70b, and the air volume of the blowing means 40. It is possible to control the rotation speed of the moisture adsorbing means 10.

  1a 1st air flow path, 1b 2nd air flow path, 2a 1st temperature and humidity sensor, 2b 2nd temperature and humidity sensor, 2c 3rd temperature and humidity sensor, 2d 4th temperature and humidity sensor, 2e 5th temperature and humidity sensor, 2f 6th temperature / humidity sensor, 2g 7th temperature / humidity sensor, 3a, 1st temperature sensor, 3b 2nd temperature sensor, 3c 3rd temperature sensor, 3d 4th temperature sensor, 3e 5th temperature sensor, 3f 6th temperature sensor, 3g 7th temperature sensor, 4a 1st wind speed sensor, 4b 2nd wind speed sensor, 5 control board, 10 moisture adsorption means, 20 heating means, 30a 1st cooling means, 30b 2nd cooling means, 31a 1st evaporator, 31b 2nd evaporator, 40 ventilation means, 40a 1st ventilation means, 40b 2nd ventilation means, 50 condenser, 60 compressor, 70a 1st expansion valve, 70b Second expansion valve, 80 refrigerant circuit, 100 dehumidifier.

Claims (7)

In the dehumidifying device in which the first air flow path and the second air flow path are formed,
Moisture adsorbing means disposed in the first air channel and the second air channel, adsorbing moisture from the air flowing through the first air channel, and desorbing moisture to the second air channel;
Air blowing means for taking in and exhausting air through the first air flow path and the second air flow path;
A first cooling means provided upstream of the moisture adsorbing means in the first air flow path for cooling the air flowing through the first air flow path;
A heating means that is provided upstream of the moisture adsorption means in the second air flow path and heats the air flowing through the second air flow path;
A second cooling means provided downstream of the moisture adsorbing means of the second air flow path for cooling the air flowing through the second air flow path,
A dehumidifying device, wherein heat is exchanged between the air downstream of the moisture adsorbing means in the first air flow path and the air downstream of the second cooling means in the second air flow path, and then exhausted. . The air downstream from the moisture adsorbing means in the first air passage and the air downstream from the second cooling means in the second air passage are mixed and then exhausted. The dehumidifying device described. The dehumidifying device according to claim 1 or 2, wherein the first air flow path and the second air flow path are each provided with the blowing means. The dehumidifying device according to any one of claims 1 to 3, wherein cooling functions of the first cooling unit and the second cooling unit are individually controlled. The heating means, the first cooling means, and the second cooling means are constituted by a heat exchanger,
The compressor, the heating means, the first expansion valve, the first cooling means, and the second cooling means are connected in an annular shape by a refrigerant pipe. The dehumidifying device described. The dehumidifying device according to claim 5, wherein a second expansion valve is provided between the first cooling means and the second cooling means. The moisture adsorbing means is
The dehumidifier according to any one of claims 1 to 6, wherein a hygroscopic material is supported and rotatably disposed so as to straddle the first air flow path and the second air flow path. apparatus.

Images