JP2014140808A - Dehumidifier - Google Patents

Abstract

PROBLEM TO BE SOLVED: To realize a dehumidifier capable of being simplified even with a high dehumidifying capability and realizing compactness and lower cost.SOLUTION: A first heat exchanger 4, a desiccant block 7, and a second heat exchanger 6 are arranged in series. In a dehumidification operation, a dehumidifier alternately repeats a first operation mode in which the first heat exchanger 4 operates as either a condenser or a radiator and in which the second heat exchanger 6 operates as an evaporator, and a second operation mode in which the first heat exchanger 4 operates as the evaporator and in which the second heat exchanger operates as either the condenser or the radiator. Furthermore, the first heat exchanger 4 is configured so that a plurality of heat transfer tubes 13 are arranged in an intake air, and so as to form a channel configuration in which the refrigerant flows from an upstream heat transfer tube array to a downstream heat transfer tube array in a flow direction of the air if the first heat exchanger 4 operates as the evaporator in the second operation mode.

Description

  The present invention relates to a dehumidifying device.

  Conventionally, there is an example of Patent Document 1 as a dehumidifying device that dehumidifies the inside of a dehumidifying target space by using adsorption / desorption by a desiccant material that performs adsorption and desorption of moisture. Patent Document 1 is a technique for performing dehumidification by combining cooling and heating by a heat exchanger of a refrigeration cycle and adsorption / desorption by a desiccant rotor. Part, the evaporator of the refrigeration cycle, and the air passage through which the adsorbing part of the desiccant rotor passes.

  The air in the air to be dehumidified taken into this air passage is heated with a radiator, the heated air is humidified at the desorption part of the desiccant rotor, and the humidified air is cooled to below the dew point temperature with an evaporator to cool and dehumidify. . Then, the dehumidified air is further dehumidified by the adsorbing portion of the desiccant rotor and then returned to the dehumidifying target space. And it is set as the structure which performs a dehumidification driving | operation continuously by rotating a desiccant rotor.

JP 2006-150305 A (summary, FIG. 1)

  In the above conventional apparatus, by combining the adsorption / desorption action of the desiccant material and the cooling and heating action of the refrigeration cycle, it is possible to realize a larger amount of dehumidification than dehumidification using only the refrigeration cycle or only the desiccant material, It is a high-performance dehumidifier. However, on the other hand, there are the following problems.

  Since a desiccant rotor is used, a rotor drive unit is required. In addition, a seal structure that hermetically separates the boundary between the adsorbing part and the desorbing part is necessary so that no air leakage occurs between the adsorbing part and the desorbing part of the desiccant. There was a problem of becoming. In addition, since the air passage configuration returns the air after passing through the desiccant rotor to the desiccant rotor again, the air passage configuration has many bent portions, the pressure loss at the time of conveying the air increases, and the fan power increases. There was a problem that the power consumption of the apparatus increased.

  In addition, in the dehumidifying apparatus, it is of course important to obtain a high dehumidifying effect, and further improvements are required.

  The present invention has been made to solve the above-described problems, and achieves a dehumidifying apparatus that can be simplified and reduced in size and cost while having a high dehumidifying capacity. The purpose is to do.

  A dehumidifying device according to the present invention includes a refrigerant circuit in which a compressor, a flow path switching device, a first heat exchanger, a decompression device, and a second heat exchanger are sequentially connected by a refrigerant pipe, a first heat exchanger, An air passage in which a desiccant material capable of adsorbing and desorbing and a second heat exchanger are arranged in series in this order, and a blower for flowing air in a dehumidification target space in the order of the first heat exchanger, the desiccant material and the second heat exchanger. A first operation mode in which the first heat exchanger operates as a condenser or a radiator and the second heat exchanger operates as an evaporator to desorb moisture held in the desiccant material; The second operation mode in which the exchanger operates as an evaporator and the second heat exchanger operates as a condenser or a radiator, and the desiccant material adsorbs moisture from the air passing through the air passage, Control device that performs dehumidifying operation that switches alternately by switching the flow path The first heat exchanger includes a plurality of fins arranged in parallel at intervals, and a plurality of fins in a row direction passing through the plurality of fins and perpendicular to the air flow direction and the air flow direction. A plurality of heat transfer tubes arranged in multiple rows and stages, and having a plurality of heat transfer tubes through which the refrigerant passes, and when operating as an evaporator, when operating as an evaporator, from the heat transfer tube rows upstream to the air flow direction The heat transfer tube array has a flow path configuration in which the refrigerant flows.

  ADVANTAGE OF THE INVENTION According to this invention, dehumidification of a high dehumidification amount can be performed by combining the adsorption / desorption effect | action of a desiccant material, and the cooling and heating effect | action by the refrigerating cycle operation | movement of a refrigerant circuit. In addition to this, the first heat exchanger, the desiccant material, and the second heat exchanger are arranged in series, and the first heat exchanger operates as a condenser or a radiator, and the second heat exchange. The first operation mode in which the condenser operates as an evaporator and the moisture held in the desiccant material is desorbed, the first heat exchanger operates as an evaporator, and the second heat exchanger serves as a condenser or a radiator. Since the dehumidifying operation is performed by alternately switching the second operation mode in which the desiccant material absorbs moisture from the air passing through the air passage by switching the flow path of the flow path switching device, the device structure is simplified. Therefore, a more compact and low-cost device can be obtained.

  Moreover, since it was set as the structure which has arrange | positioned the heat exchanger tube of a 1st heat exchanger in multi-row multistage, the area of a fin can be enlarged compared with the heat exchanger arrange | positioned in multistage 1 row. Therefore, the amount of dehumidification can be increased as compared with the heat exchangers arranged in a multistage one row, and a high dehumidifying effect can be obtained.

  Moreover, since it was set as the flow-path structure used as a parallel flow when it operate | moves as an evaporator, compared with the case where it is set as a counterflow, a heat exchange amount can be increased and a dehumidification amount can be increased.

It is a figure which shows the structure of the dehumidification apparatus which concerns on Embodiment 1 of this invention. It is an air wetness diagram which shows the state change of the air at the time of the 1st operation mode in the dehumidification apparatus which concerns on Embodiment 1 of this invention. It is an air wetness diagram which shows the state change of the air at the time of the 2nd operation mode in the dehumidification apparatus which concerns on Embodiment 1 of this invention. It is a figure which shows the structure of the dehumidification apparatus which concerns on Embodiment 2 of this invention. It is a figure which shows the detailed structure of the 1st heat exchanger of FIG. It is an air line diagram of the state change of the passing air of the 1st heat exchanger when the 1st heat exchanger of Drawing 4 operates as an evaporator.

Embodiment 1 FIG.
FIG. 1 is a diagram showing a configuration of a dehumidifying device according to Embodiment 1 of the present invention. In FIG. 1 and each figure to be described later, the same reference numerals denote the same or equivalent parts, which are common throughout the entire specification. Moreover, the form of the component which appears in the whole specification is an illustration to the last, and is not limited to these description.

  The dehumidifying device 1 includes a compressor 2, a four-way valve 3 that is a flow path switching device, a first heat exchanger 4, an expansion valve 5 that is a decompression device, and a second heat exchanger 6 in a housing 10. These are connected in an annular shape by a refrigerant pipe to constitute a refrigerant circuit A. The inside of the housing 10 is divided into an air passage chamber 20 and a machine chamber 30. The compressor 2 and the four-way valve 3 are arranged in the machine chamber 30, and the others are arranged in the air passage chamber 20. In addition, a through hole (not shown) is formed in the wall surface 11 partitioning the machine room 30 and the air passage chamber 20, and a refrigerant pipe is passed through the through hole (not shown) to connect each element. Is connected. Moreover, it is good to comprise so that a clearance gap part may be kept airtight so that an airflow may not arise between the machine room 30 and the air channel room 20 through the clearance gap between a through-hole and connection piping.

  The four-way valve 3 can switch the flow path so that the refrigerant flows in the solid line direction or the dotted line direction in FIG. 1, and when switched to the solid line flow path in FIG. 1, the refrigerant discharged from the compressor 2 flows. The four-way valve 3, the first heat exchanger 4, the expansion valve 5, the second heat exchanger 6, and the four-way valve 3 flow in that order to return to the compressor 2. In this configuration, the first heat exchanger 4 operates as a condenser (heat radiator), and the second heat exchanger 6 operates as an evaporator.

On the other hand, when the flow path of the four-way valve 3 is switched to the dotted flow path in FIG. 1, the refrigerant discharged from the compressor 2 is transferred to the four-way valve 3, the second heat exchanger 6, the expansion valve 5, and the first heat. A refrigeration cycle that flows in the order of the exchanger 4 and the four-way valve 3 and returns to the compressor 2 is configured. In this configuration, the second heat exchanger 6 operates as a condenser (heat radiator), and the first heat exchanger 4 operates as an evaporator. For example, R410A is used as the refrigerant of the dehumidifier 1. Note that the refrigerant is not limited to R410A, and other HFC refrigerants may be used, or natural refrigerants such as HC refrigerants, CO ₂ refrigerants, and NH ₃ refrigerants may be used. In the case of using a CO ₂ refrigerant and the operation is performed at a high pressure equal to or higher than the critical pressure, the condenser operates as a radiator.

  The 1st heat exchanger 4 and the 2nd heat exchanger 6 are plate fin tube heat exchangers, a plurality of fins 12 arranged in parallel at intervals, and a plurality of fins 12 are penetrated, and in the air flow direction. It has a plurality of heat transfer tubes 13 that are arranged in multiple rows and multiple rows in a row direction and a row direction orthogonal to the air flow direction, and through which the refrigerant passes. The first heat exchanger 4 and the second heat exchanger 6 exchange heat between the refrigerant flowing in the heat transfer tube 13 and the air flowing around the fins.

  The first heat exchanger 4 and the second heat exchanger 6 are so-called parallel flows in which the refrigerant flows from the upstream heat transfer tube row to the downstream heat transfer tube row with respect to the air flow direction when operating as an evaporator. The flow path configuration is as follows. The reason for this will be described below.

  In the evaporator, in an ideal state, the refrigerant undergoes an isothermal phase change, but actually, the pressure of the refrigerant decreases due to the pressure loss caused by passing through the heat transfer tube, and the refrigerant temperature decreases. That is, the refrigerant temperature on the refrigerant outlet side is lower than that on the refrigerant inlet side of the evaporator. On the other hand, since the air flowing through the evaporator is cooled by passing through the evaporator, the temperature of the air on the air downstream side is lower than that on the air upstream side of the evaporator. In the evaporator, from the viewpoint of improving the performance as a heat exchanger, the temperature difference between the air temperature and the refrigerant temperature is required to be uniform from the refrigerant inlet to the outlet of the evaporator.

  Thus, if the temperature difference between the air temperature and the refrigerant temperature is uniform from the refrigerant inlet to the outlet of the evaporator, the average temperature difference increases, and the flow becomes a counterflow when operating as an evaporator. Compared to the case of a path configuration (a configuration in which the refrigerant flows from the downstream heat transfer tube row to the upstream heat transfer tube row with respect to the air flow direction), more heat exchange can be performed. That is, when the heat exchanger operates as an evaporator, the amount of heat exchange is increased by using a parallel flow, and the performance as a heat exchanger is improved. Moreover, since the amount of heat exchange increases, the amount of dehumidification can be increased with respect to the dehumidification amount as compared with the case where the parallel flow is the counter flow.

  Returning to FIG. 1, the expansion valve 5 is a valve whose opening degree can be controlled, and expands the refrigerant passing thereunder under reduced pressure.

  The air channel chamber 20 has a suction port 20a for introducing air to be dehumidified therein, and an air outlet 20b for discharging the dehumidified air to the outside. In the direction of the white arrow in FIG. Air conveyed by the blower 8 flows. The air passage chamber 20 is configured in a rectangular shape, and the first heat exchanger 4, the desiccant block 7 that is a desiccant material, the second heat exchanger 6, and the blower 8 are arranged in series in the air passage chamber 20. An air path B is formed. Therefore, the air sucked into the air passage B from the suction port 20a is straight in the air passage B in the order of the first heat exchanger 4, the desiccant block 7, which is a desiccant material, the second heat exchanger 6, and the blower 8. After flowing in the shape, the air is exhausted to the outside of the dehumidifier 1 from the air outlet 20b.

  The desiccant block 7 is a desiccant material molded into a solid and rectangular shape, and is made of a material that absorbs and desorbs moisture. For example, zeolite, silica gel, a polymeric adsorbent, and the like are applied.

  Further, in the air channel chamber 20, a drain pan 40 is disposed below each of the first heat exchanger 4 and the second heat exchanger 6, and drain water generated during operation is dripped from each heat exchanger. ing. The drain water received by the drain pan 40 flows into the drain tank 42 at the lowermost part of the dehumidifier 1 through the water channel 41 indicated by the broken line extending from the drain pan 40 in FIG.

  The air passage chamber 20 further includes a temperature / humidity sensor 50 for measuring the temperature / humidity of the intake air of the dehumidifying device 1 (temperature / humidity around the dehumidifying device 1), and the temperature / humidity of the inflowing air flowing into the second heat exchanger 6. The temperature / humidity sensor 51 to detect is provided.

  Further, in the dehumidifying device 1, a control device 60 for controlling the entire dehumidifying device 1 is provided on the machine room 30 side. The control device 60 is constituted by a microcomputer and includes a CPU, a RAM, a ROM, and the like, and a control program is stored in the ROM. The control device 60 calculates the dew point temperatures of the intake air (inflow air of the first heat exchanger 4) and the inflow air of the second heat exchanger 6 based on the detection signals of the temperature and humidity sensors 50 and 51. Then, the control device 60 controls the dehumidifying operation described later (switching of the four-way valve 3 according to the detection signals of the temperature / humidity sensors 50 and 51) based on the calculation result, the rotational speed control of the blower 8, and the rotational speed of the compressor 2. Various controls such as control and opening degree control of the expansion valve 5 are performed.

  Next, the dehumidifying operation operation of the dehumidifying device 1 will be described. In the dehumidifying device 1, two operation modes are realized by switching the flow path of the four-way valve 3. Hereinafter, it demonstrates in order.

(First operation mode: operation of the refrigeration cycle)
First, the operation in the first operation mode that is a case where the flow path of the four-way valve 3 is switched to the solid line in FIG. 1 will be described. The solid line arrows in FIG. 1 indicate the refrigerant flow in the first operation mode, and the operation of the refrigeration cycle in the first operation mode is as follows. After the low pressure gas is sucked into the compressor 2, it is compressed and discharged from the compressor 2 as a high temperature and high pressure gas. The refrigerant discharged from the compressor 2 flows into the first heat exchanger 4 through the four-way valve 3. The refrigerant flowing into the first heat exchanger 4 dissipates heat to the air flowing through the air passage B, and while the air is heated, the refrigerant itself is cooled and condensed to become a high-pressure liquid refrigerant from the first heat exchanger 4. leak. The liquid refrigerant flowing out from the first heat exchanger 4 is decompressed by the expansion valve 5 and becomes a low-pressure two-phase refrigerant. Thereafter, the refrigerant flows into the second heat exchanger 6, absorbs heat from the air flowing through the air passage B, and while the air is cooled, the refrigerant itself is heated and evaporated to become low-pressure gas. Thereafter, the refrigerant is sucked into the compressor 2 through the four-way valve 3.

(First operation mode: Air operation)
Next, the operation of air in the first operation mode will be described with reference to FIG. FIG. 2 is an air wetting diagram showing the air state change in the first operation mode in the dehumidifier according to Embodiment 1 of the present invention, where the vertical axis represents the absolute humidity of the air and the horizontal axis represents the dry bulb temperature of the air. It is. Moreover, the curve of FIG. 2 shows saturated air, and the relative humidity in saturated air is 100%.

  The air around the dehumidifier 1 (FIG. 2, point A) flows into the dehumidifier 1 and is heated by the first heat exchanger 4 to increase the temperature and decrease the relative humidity (point B in FIG. 2). ). Thereafter, air flows into the desiccant block 7, but since the relative humidity of the air is low, the moisture held in the desiccant block 7 is desorbed (released), and the amount of moisture contained in the air increases. On the other hand, desorption heat accompanying desorption is deprived from the air flowing into the desiccant block 7, the temperature of the air is lowered, and the temperature becomes low and high humidity (point C in FIG. 2).

  Thereafter, the air flows into the second heat exchanger 6 and is cooled. The refrigerant circuit A is operated such that the refrigerant temperature in the second heat exchanger 6 is lower than the dew point temperature of the air, and the air is cooled and dehumidified by the second heat exchanger 6, and the low temperature Thus, the absolute humidity is low (D point in FIG. 2).

  Here, in the second heat exchanger 6, moisture in the air flowing into the second heat exchanger 6 is dehumidified by condensation on the surfaces of the fins 12. Therefore, the larger the area of the fin 12, the greater the dehumidification amount. In the first embodiment, since the heat transfer tubes 13 of the second heat exchanger 6 are arranged in multiple rows and multiple stages, the area of the fins 12 can be increased compared to the heat exchangers arranged in multiple rows and one row. it can. Therefore, the amount of dehumidification can be increased as compared with the heat exchangers arranged in a multistage one row, and a high dehumidifying effect can be obtained. Then, the air that has been cooled and dehumidified by the second heat exchanger 6 flows into the blower 8 and is exhausted from the air outlet 20b to the outside of the dehumidifier 1.

(Second operation mode: operation of the refrigeration cycle)
Next, the operation in the second operation mode in which the flow path of the four-way valve 3 is switched to the dotted line in FIG. 1 will be described. The dotted arrows in FIG. 1 indicate the flow of the refrigerant in the second operation mode, and the operation of the refrigeration cycle in the second operation mode is as follows. After the low pressure gas is sucked into the compressor 2, it is compressed and discharged from the compressor 2 as a high temperature and high pressure gas. The refrigerant discharged from the compressor 2 flows into the second heat exchanger 6 through the four-way valve 3. The refrigerant flowing into the second heat exchanger 6 radiates heat to the air flowing through the air passage B, and while the air is heated, the refrigerant itself is cooled and condensed to become a high-pressure liquid refrigerant. Spill from. The liquid refrigerant flowing out of the second heat exchanger 6 is decompressed by the expansion valve 5 and becomes a low-pressure two-phase refrigerant. Thereafter, the refrigerant flows into the first heat exchanger 4, absorbs heat from the air flowing through the air passage B, and while the air is cooled, the refrigerant itself is heated and evaporated to become a low-pressure gas. Thereafter, the refrigerant is sucked into the compressor 2 through the four-way valve 3.

(Second operation mode: air operation)
Next, the operation of air in the second operation mode will be described with reference to FIG. FIG. 3 is an air wetting diagram showing a change in the air state in the second operation mode in the dehumidifying apparatus according to Embodiment 1 of the present invention, where the vertical axis is the absolute humidity of the air and the horizontal axis is the dry bulb temperature of the air. It is. Moreover, the curve of FIG. 3 shows saturated air, and the relative humidity in saturated air is 100%.

  The air around the dehumidifying device 1 (point A in FIG. 3) flows into the dehumidifying device 1 and is then cooled by the first heat exchanger 4. Note that the refrigerant circuit A is operated such that the refrigerant temperature in the first heat exchanger 4 is lower than the dew point temperature of the air, and the air is cooled and dehumidified by the first heat exchanger 4 so that the temperature is low. In a high relative humidity state (FIG. 3, point E).

  Here, in the first heat exchanger 4, moisture in the air flowing into the first heat exchanger 4 is dehumidified by condensation on the surfaces of the fins 12. Therefore, the larger the area of the fin 12, the greater the dehumidification amount. In the first embodiment, since the heat transfer tubes 13 of the first heat exchanger 4 are arranged in multiple rows and multiple stages, the area of the fins 12 can be increased compared to the heat exchanger arranged in multiple rows and one row. it can. Therefore, the amount of dehumidification can be increased as compared with the heat exchangers arranged in a multistage one row, and a high dehumidifying effect can be obtained.

  The air cooled and dehumidified by the first heat exchanger 4 flows into the desiccant block 7, but since the relative humidity of the air is high, moisture in the air is adsorbed to the desiccant block 7, and the amount of moisture contained in the air is reduced. Reduced and further dehumidified. On the other hand, the air flowing into the desiccant block 7 is heated by the heat of adsorption generated along with the adsorption, and the temperature of the air rises to a high temperature and low humidity state (point F in FIG. 3). Then, air flows into the 2nd heat exchanger 6, is heated, and becomes high temperature (FIG. 3, G point). Thereafter, the air flows into the blower 8 and is exhausted from the air outlet 20b to the outside of the dehumidifier 1.

  Thus, in the second operation mode, dehumidification by adsorption of the desiccant block 7 is performed in addition to dehumidification by cooling with the refrigerant in the first heat exchanger 4. Therefore, as apparent from a comparison between FIG. 2 and FIG. 3, the second operation mode can secure a larger amount of dehumidification than the first operation mode, and the main dehumidification with the present dehumidifier 1 is the second dehumidification amount. It will be carried out in the operation mode.

  In the dehumidifying apparatus 1 of the first embodiment, the first and second operation modes are alternately repeated. Since the amount of moisture contained in the desiccant block 7 has an upper limit, when the second operation mode is continuously operated for a certain time or longer, moisture is not adsorbed on the desiccant block 7 and the dehumidification amount is reduced. Therefore, when the amount of moisture retained in the desiccant block 7 is close to the upper limit, the operation mode is switched to the first operation mode and the operation of releasing moisture from the desiccant block 7 is performed. The first operation mode is carried out for a while, and the operation mode is switched again to the second operation mode when the amount of moisture retained in the desiccant block 7 is appropriately reduced. Thus, by alternately performing the first and second operation modes, the adsorption / desorption action of the desiccant block 7 is sequentially performed, and the effect of increasing the dehumidification amount due to the adsorption / desorption action of the desiccant is maintained.

  Each operation time in the first operation mode and the second operation mode may be a predetermined time, but each operation time in each operation mode is appropriate for the air condition and the operation state of the dehumidifier 1. There is a value. Therefore, the operation time of each operation mode may be determined based on, for example, the air condition detected by the temperature / humidity sensors 50 and 51 and the operation state of the dehumidifier 1 so that the operation can be performed with the appropriate value. The method for determining the operation time in each operation mode is not particularly limited in the present invention, and any method can be adopted.

  As described above, in the first embodiment, when the high-performance dehumidifier 1 that combines the desiccant adsorption / desorption action and the heating / cooling action of the refrigeration cycle is configured, the air path B is configured linearly. Yes. Since the conventional device uses a desiccant rotor, it is necessary to ventilate the adsorbing part and the desorbing part of the desiccant rotor. The pressure loss when doing so was large. On the other hand, in this Embodiment 1, since the air path B was comprised linearly, the pressure loss at the time of conveying air can be made small. Therefore, the power consumption of the blower 8 that conveys air can be reduced correspondingly, and a more efficient device can be obtained.

  In addition, in the configuration using the conventional desiccant rotor, a motor for rotating the desiccant rotor, a fixing structure thereof, and the like are required, and the apparatus configuration is complicated. On the other hand, since the first embodiment is a stationary type, a motor for rotating the desiccant material is not required, and the air path configuration is simple. Therefore, it is possible to reduce the size, simplify the device configuration, and achieve a low-cost device.

  Moreover, in this Embodiment 1, the air path B is comprised in the rectangle. For this reason, when each of the 1st heat exchanger 4, the 2nd heat exchanger 6, and the desiccant block 7 mounted in the air path B is made into the rectangular external structure according to the shape of the air path B, a rectangular air path B can be mounted at a higher density.

  That is, since the conventional apparatus uses a desiccant rotor, a circular rotor is disposed in the rectangular air passage B. Therefore, dead spaces are formed at the four corners in the rotor arrangement portion, and the air passage cannot be made compact. On the other hand, in the first embodiment, by using the rectangular desiccant block 7, it can be arranged without dead space, so that high-density mounting is possible. As a result, the air passage B can be made compact (the air passage chamber 20 is compact).

  Further, in the first embodiment, the first heat exchanger 4 and the second heat exchanger 6 have a configuration in which the heat transfer tubes 13 are arranged in multiple rows and multiple stages, so that compared to the heat exchangers arranged in multiple rows and one row. The area of the fin 12 can be increased. Therefore, a high dehumidifying effect can be obtained.

  In addition, since the first heat exchanger 4 and the second heat exchanger 6 have a flow path configuration that becomes a parallel flow when operating as an evaporator, it is possible to increase the amount of heat exchange compared to the case of the counter flow. And the amount of dehumidification can be increased.

  In the first embodiment, both the first heat exchanger 4 on the upstream side and the second heat exchanger 6 on the downstream side with respect to the air flow direction have a multi-row multi-stage structure. Are not necessarily limited to a multi-row multi-stage structure, and at least one of the multi-row multi-stage structures may be used.

Embodiment 2. FIG.
The second embodiment is intended to further improve the dehumidifying effect.

FIG. 4 is a diagram showing the configuration of the dehumidifying device according to Embodiment 2 of the present invention.
The dehumidifying apparatus 1A of the second embodiment is different from the first embodiment in the configuration of the first heat exchanger 4 and the second heat exchanger 6, and the other configurations are the same as those in the first embodiment. Note that the modification applied to the same components in the second embodiment as those in the first embodiment is similarly applied to the second embodiment.

Here, prior to the description of FIG. 4, the reason for reaching the configuration of FIG. 4 will be described.
In the first heat exchanger 4 operating as an evaporator, moisture in the air condenses on the surfaces of the fins 12, and the condensed water drops from the fins 12 and is recovered as drain water, but does not drop from the fins 12. There is also dew condensation water that stays on the surface of the fin 12. The condensed water staying on the surface of the fin 12 is heated by the high-temperature refrigerant in the heat transfer tube 13 when the first heat exchanger 4 is switched from the evaporator to the condenser by switching the four-way valve 3, Evaporate.

  When the condensed water evaporates, a part of the water cooled and liquefied from the air by the first heat exchanger (evaporator) 4 cannot be taken out as drain water, and the dehumidification amount decreases. And the evaporated dew condensation water will be supplied indoors and will raise indoor humidity. Moreover, re-evaporating the moisture taken out from the air for the purpose of dehumidification again unintentionally results in wasted energy.

  Therefore, in the second embodiment, the amount of condensed water in the heat exchanger (the first heat exchanger 4 and the second heat exchanger 6) when operating as an evaporator is reduced, and the heat exchanger cools and liquefies. More heat is collected as drain water to increase the dehumidification amount.

  Hereinafter, specific configurations of the first heat exchanger 4 and the second heat exchanger 6 will be described. Since the first heat exchanger 4 and the second heat exchanger 6 have the same structure, the first heat exchanger 4 will be described as a representative here.

FIG. 5 is a diagram showing a detailed configuration of the first heat exchanger of FIG. In FIG. 5, white arrows indicate the direction of air flow.
The first heat exchanger 4 includes a plurality of fins 12 arranged in parallel at intervals, and a plurality of fins 12 in multiple rows and multiple rows in a row direction that is an air flow direction and a step direction orthogonal to the air flow direction. It has a plurality of heat transfer tubes 13 which are arranged through and through which the refrigerant passes. The first heat exchanger 4 includes an upstream heat exchanger 14 provided with an air upstream heat transfer tube row and a downstream heat exchanger 15 provided with an air downstream heat transfer tube row among the plurality of heat transfer tubes 13. Have. And the fin 12 between the upstream heat exchanger 14 and the downstream heat exchanger 15 is cut | disconnected in the step direction, and the fin 12 was interposed between the upstream heat exchanger 14 and the downstream heat exchanger 15. The heat transfer is cut off.

  In addition, a capillary tube 16 that is a pressure difference generating device is connected to a refrigerant pipe that connects the upstream heat exchanger 14 and the downstream heat exchanger 15. A check valve 17 is provided in parallel with the capillary tube 16, and the check valve 17 closes the flow path when the refrigerant flows from the upstream heat exchanger 14 to the downstream heat exchanger 15, and the downstream heat exchanger 15. When the refrigerant flows from the upstream to the upstream heat exchanger 14, it is arranged so as to operate to open the flow path.

  The first heat exchanger 4 and the second heat exchanger 6 configured as described above are configured to exchange the upstream heat so that they flow from the upstream heat exchanger 14 to the downstream heat exchanger 15 when operating as an evaporator. The refrigerant inlet of the cooler 14 is connected to a refrigerant pipe connected to the expansion valve 5, and the refrigerant outlet of the downstream heat exchanger 15 is connected to a refrigerant pipe connected to the four-way valve 3. 4 shows an example in which the capillary tube 16 and the check valve 17 are arranged above the drain pan 40. However, the arrangement position of the capillary tube 16 and the check valve 17 is not limited to this position. Or it may be lateral.

  The flow of the refrigerant when the first heat exchanger 4 and the second heat exchanger 6 configured as described above operate as an evaporator will be described. Since the flow of the refrigerant when the first heat exchanger 4 and the second heat exchanger 6 operate as an evaporator is the same, here, an example of the second operation mode in which the first heat exchanger 4 operates as an evaporator. This will be described as a representative.

  In the second operation mode in which the first heat exchanger 4 operates as an evaporator, the low-pressure two-phase refrigerant flowing out of the expansion valve 5 flows into the first heat exchanger 4 as shown by the dotted arrows in FIG. It flows into the upstream heat exchanger 14. The refrigerant flowing into the upstream heat exchanger 14 absorbs heat from the air flowing through the air passage B, and the refrigerant itself evaporates while cooling the air. The refrigerant in the upstream heat exchanger 14 evaporates to some extent in the process of passing through the heat transfer tube 13 of the upstream heat exchanger 14 and flows out of the upstream heat exchanger 14 with a high degree of dryness. The refrigerant that has flowed out of the upstream heat exchanger 14 flows into the capillary tube 16 and is depressurized by the flow resistance of the capillary tube 16 so that the pressure is lowered and the evaporation temperature is lowered. In addition, since the check valve 17 is installed in the refrigerant pipe provided in parallel with the capillary tube 16, no refrigerant flows.

  The refrigerant depressurized by the capillary tube 16 then flows into the downstream heat exchanger 15 and subsequently absorbs heat from the air flowing through the air passage B, and the refrigerant itself evaporates while cooling the air. Then, the refrigerant evaporated into the low-pressure gas flows out from the downstream heat exchanger 15 and flows into the four-way valve 3.

  When the first heat exchanger 4 and the second heat exchanger 6 operate as evaporators, the target evaporation temperatures (refrigerant evaporation temperatures) of the upstream heat exchanger 14 and the downstream heat exchanger 15 are as follows: Set to temperature. The target evaporation temperature of the upstream heat exchanger 14 is set to the dew point temperature of the inflowing air, and the target evaporation temperature of the downstream heat exchanger 15 is, for example, from the dew point temperature of the inflowing air to ensure dehumidification of the inflowing air. The temperature is set to 10 ° C lower.

  Adjustment for setting the respective evaporation temperatures of the upstream heat exchanger 14 and the downstream heat exchanger 15 to the target evaporation temperature is performed by adjusting the flow resistance of the capillary tube 16 and adjusting the opening of the expansion valve 5. . The dew point temperature of the incoming air when the first heat exchanger 4 operates as an evaporator is calculated by the control device 60 based on the temperature and humidity detected by the temperature and humidity sensor 50, and the second heat exchanger 6 evaporates. The dew point temperature of the inflowing air when operating as a vessel is calculated by the control device 60 based on the temperature and humidity detected by the temperature and humidity sensor 51.

  In this way, the refrigerant is operated such that the evaporation temperature of the refrigerant flowing in the upstream heat exchanger 14 becomes the dew point temperature of the inflowing air, and the evaporation temperature of the refrigerant flowing in the downstream heat exchanger 15 is 10 ° C. lower than the dew point temperature of the inflowing air. Next, FIG. 6 demonstrates the air state change by driving | running so that it may become temperature. Here, the case where the first heat exchanger 4 operates as an evaporator will be described as a representative, but the same applies when the second heat exchanger 6 operates as an evaporator.

  FIG. 6 is an air diagram of a change in the state of air passing through the first heat exchanger when the first heat exchanger of FIG. 4 operates as an evaporator. In FIG. 6, a solid line arrow indicates a change in the air state in the second embodiment. As a comparative example, the dotted line arrows in FIG. 6 indicate that the absolute humidity of the air after passing through the first heat exchanger 4 is the same (the absolute humidity at the points C1 and C2 in FIG. 6 is the same) and the first heat The target evaporation temperatures of the upstream heat exchanger 14 and the downstream heat exchanger 15 are both set so that both the upstream heat exchanger 14 and the downstream heat exchanger 15 of the exchanger 4 are appropriately dehumidified. Both show changes in the air state when the temperature is lower than the dew point temperature of the inflowing air. In addition, although the target evaporation temperature in a comparative example is lower than the dew point temperature of inflow air, it is set higher than the target evaporation temperature of the downstream heat exchanger 15 in this Embodiment 2. FIG. Moreover, the curve in FIG. 6 has shown the saturated air line.

  As shown in FIG. 6, in the case of the present second embodiment, the air (point A) at the inlet of the first heat exchanger 4 flows into the upstream heat exchanger 14 and is cooled to decrease the temperature. In the side heat exchanger 14, since the evaporating temperature is operated at the dew point temperature of the inflowing air, dew condensation on the fin surface does not occur and dehumidification is not performed. For this reason, the air after passing through the upstream heat exchanger 14 only has a lower temperature than the air at the inlet of the first heat exchanger 4, and the absolute humidity does not change (point B1). Then, the air after passing through the upstream heat exchanger 14 flows into the downstream heat exchanger 15. In the downstream heat exchanger 15, the evaporating temperature is operated at a temperature 10 ° C. lower than the dew point temperature of the inflowing air, so the air flowing into the downstream side heat exchanger 15 is cooled and dehumidified, and the absolute humidity decreases as the temperature decreases. (C1 point).

  On the other hand, in the case of the comparative example, the air (point A) at the inlet of the first heat exchanger 4 flows into the upstream heat exchanger 14 and is cooled and dehumidified, so that the temperature decreases and the absolute humidity decreases (point B2). . Then, the air after passing through the upstream heat exchanger 14 flows into the downstream heat exchanger 15 and is further cooled and dehumidified, so that the temperature decreases and the absolute humidity decreases (point C2). As described above, in the case of the comparative example, dehumidification is retained not only in the downstream heat exchanger 15 but also in the upstream heat exchanger 14, so that dew condensation water stays in all rows of the first heat exchanger 4.

  As described above, in the second embodiment, by operating the evaporating temperature of the upstream heat exchanger 14 located on the upstream side of the air at the dew point temperature of the inflowing air, the generation of condensed water in the upstream heat exchanger 14 is suppressed. it can. That is, in FIG. 6, generation | occurrence | production of the dehumidification amount corresponded to the absolute humidity difference Xa can be suppressed compared with a comparative example. Therefore, when the four-way valve 3 is switched, in the comparative example, among the moisture corresponding to the dehumidifying amount corresponding to the absolute humidity difference Xa, the moisture staying without dripping from the first heat exchanger 4 is heated. As a result, the amount of dehumidification is reduced and the humidity of the air is increased. In contrast, in Embodiment 2, since the surface of the upstream heat exchanger 14 is in a dry state, re-evaporation from at least the upstream heat exchanger 14 side can be suppressed, and a dehumidifying device with a high dehumidifying amount can be suppressed. 1A.

  In addition, the target evaporation temperature of the downstream heat exchanger 15 is set to a temperature lower than the dew point temperature of the inflow air of the first heat exchanger 4 so that dehumidification is appropriately performed, and is equal to or higher than a temperature at which a necessary dehumidification amount is obtained. I just need it. Further, the target evaporation temperature of the upstream heat exchanger 14 is not limited to the dew point temperature of the inflowing air, and may be a predetermined range for reducing the dehumidification amount including the dew point temperature. That is, the target evaporation temperature of the upstream heat exchanger 14 may be a temperature that can suppress the generation of condensed water in the upstream heat exchanger 14, and may be a temperature lower by about 1 to 2 ° C. than the dew point temperature. The temperature may be the same as the dew point temperature or 3 to 5 ° C. higher than the dew point temperature.

  When the target evaporation temperature of the upstream heat exchanger 14 is set to a temperature lower by about 1 to 2 ° C. than the dew point temperature, the refrigerant temperature is lower than the dew point temperature, but the surface temperature of the fins 12 of the upstream heat exchanger 14 is Since the dew point temperature is exceeded due to the influence of room temperature, the generation of condensed water can be suppressed. On the other hand, when the target evaporation temperature of the upstream heat exchanger 14 is equal to or higher than the dew point temperature, the generation of condensed water in the upstream heat exchanger 14 can be similarly suppressed.

  Next, the flow of the refrigerant when each of the first heat exchanger 4 and the second heat exchanger 6 operates as a condenser will be described with an example of a second operation mode in which the first heat exchanger 4 operates as a condenser. To do. Here, the case where the first heat exchanger 4 operates as a condenser will be described as a representative, but the operation of the second heat exchanger 6 when the second heat exchanger 6 operates as a condenser is the same. is there.

  In the second operation mode in which the first heat exchanger 4 operates as a condenser, the high-temperature and high-pressure refrigerant discharged from the compressor 2 and flowing out from the four-way valve 3 flows into the first heat exchanger 4, and first, the downstream heat It flows into the exchanger 15. The refrigerant that has flowed into the downstream heat exchanger 15 dissipates heat to the air flowing through the air passage B, and the refrigerant itself condenses and flows out of the downstream heat exchanger 15 while heating the air.

  Most of the refrigerant flowing out of the downstream heat exchanger 15 passes through the check valve 17 and flows into the upstream heat exchanger 14. Since the flow path on the capillary tube 16 side has a high flow resistance, the refrigerant hardly flows. Therefore, the pressure reduction due to the refrigerant flowing toward the capillary tube 16 is negligible.

  Then, the refrigerant flowing into the upstream heat exchanger 14 dissipates heat to the air flowing through the air passage B, and while the air is heated, the refrigerant itself condenses and flows out from the upstream heat exchanger 14 and flows into the expansion valve 5. To do.

  As described above, according to the second embodiment, the same effects as those of the first embodiment can be obtained, and the following effects can be obtained. That is, when the first heat exchanger 4 and the second heat exchanger 6 are operated as an evaporator, the target evaporation temperature of the upstream heat exchanger 14 is set within a predetermined range for reducing the dehumidification amount including the dew point temperature. Thus, the amount of dew that stays in the upstream heat exchanger 14 can be reduced. Therefore, the amount of dehumidification of 1A of dehumidification apparatuses can be increased by the reduction | decrease of the staying dew condensation water.

  In the second embodiment, the capillary tube 16 is used as a pressure difference generating device that generates a pressure difference by reducing the refrigerant pressure between the upstream heat exchanger 14 and the downstream heat exchanger 15. The pressure difference generating device is not limited to the capillary tube 16. That is, other means may be used as the pressure difference generating device. For example, a valve with a fixed opening may be provided instead of the capillary tube 16 and the pressure may be reduced by the flow resistance when passing through the valve.

  Moreover, when the 1st heat exchanger 4 and the 2nd heat exchanger 6 operate | move as an evaporator, when passing through the heat exchanger tube 13 and piping before and behind that, pipe friction loss arises and a refrigerant | coolant pressure falls. Accordingly, when the necessary pressure loss is obtained by the heat transfer tube 13 and the pipes before and after the heat transfer pipe 13 and the same operation as that of the second embodiment can be realized, these pipes become the pressure difference generating device. In this way, when the heat transfer tube 13 and the pipes before and after the heat transfer pipe 13 are pressure difference generating devices, it is not necessary to provide a separate component from the pipe such as the capillary tube 16 or the expansion valve. In other words, it can be said that the evaporation temperature of the upstream heat exchanger 14 can be increased to the dew point temperature by providing the pressure difference generating device.

  In the second embodiment, the fin 12 is cut between the upstream heat exchanger 14 and the downstream heat exchanger 15, but the present invention includes a configuration in which the fin 12 is not cut. However, since the refrigerant evaporation temperature of the downstream heat exchanger 15 when the upstream heat exchanger 14 and the downstream heat exchanger 15 operate as an evaporator is lower than the refrigerant evaporation temperature of the upstream heat exchanger 14, When the fins 12 are integrated without being cut, the cold heat on the downstream heat exchanger 15 side is transmitted to the fins 12 of the upstream heat exchanger 14 due to heat conduction of the fins 12. In this case, the fins 12 of the upstream heat exchanger 14 are cooled to a dew point temperature or lower, the air is also cooled in the upstream heat exchanger 14 and dehumidification is performed, and the dew condensation water is also removed in the upstream heat exchanger 14. Stagnation may occur.

  For this reason, it is preferable that the fins 12 be cut between the upstream heat exchanger 14 and the downstream heat exchanger 15. In this case, the heat conduction of the cold heat from the downstream heat exchanger 15 to the upstream heat exchanger 14 is interrupted, and the temperature of the fins 12 of the upstream heat exchanger 14 becomes equal to or higher than the dew point temperature, and the upstream heat exchanger 14 Generation of condensed water can be suppressed, and as a result, the amount of dehumidification can be increased.

  In the second embodiment, the upstream heat exchanger 14 has one row and the downstream heat exchanger 15 has two rows. However, the number of the upstream heat exchanger 14 and the downstream heat exchanger 15 is different. However, the present invention is not limited to this, and may be appropriately changed according to the necessity such as heat transfer performance.

  Further, in addition to the configuration of the first embodiment or the second embodiment, a measure for further reducing the amount of condensed water staying in the first heat exchanger 4 and the second heat exchanger 6 may be used. For example, the fin 12 may be subjected to a surface treatment to make it hydrophilic. When the hydrophilic treatment is performed, the film thickness of the water staying on the surface of the fin 12 becomes thin, and the amount of dew condensation water staying in the heat exchanger can be reduced correspondingly. For this reason, the dehumidification amount of dehumidification apparatus 1 and 1A can be increased for the reduction | decrease amount of dew condensation water. Further, the water repellent treatment may be used for the fins 12. In this case, the dew condensation water tends to be a sphere on the surface of the fin 12, and is easily dropped from the fin 12, and the amount of dew condensation water staying in the heat exchanger can be reduced.

  Further, as the shape of the fin 12, a shape in which the condensed water hardly stays may be used. When the fin 12 is a slit fin and has a notch portion, the surface tension when a water droplet adheres to the notch portion increases, and the amount of dew condensation water increases and the amount of dew condensation water staying in the heat exchanger tends to increase. Therefore, even with the same slit fin, by reducing the number of notched portions, for example, a fin having a small number of notched portions or a short notched portion, the amount of condensed water can be reduced. it can.

  Further, the fin 12 has a fin shape without a notch portion, for example, a flat plate fin, a ring fin having an uneven portion on the ring around the heat transfer tube 13, and a fin 12 having a wave shape. A fin or the like may be used. In any case, by setting the refrigerant evaporation temperature of the upstream heat exchanger 14 to a temperature at which the generation of condensed water can be suppressed, the amount of condensed water remaining in the heat exchanger can be reduced, and the reduced amount of accumulated condensed water can be reduced. The amount of dehumidification of the dehumidifiers 1 and 1A can be increased.

  In the second embodiment, both the first heat exchanger 4 on the upstream side and the second heat exchanger 6 on the downstream side with respect to the air flow direction have the structure shown in FIG. The first heat exchanger 4 and the second heat exchanger 6 are not necessarily limited to the structure shown in FIG. 5, and at least one of them may be used. In the case of one side, the second heat exchanger 6 on the downstream side is preferably configured as shown in FIG. In the first operation mode in which re-evaporation of accumulated dew condensation water in the first heat exchanger 4 occurs, cooling dehumidification is performed in the second heat exchanger 6 downstream, so that a certain percentage of the re-evaporated water can be dehumidified again, Performance degradation due to re-evaporation can be suppressed. However, in the second operation mode in which re-evaporation of the accumulated condensed water in the second heat exchanger 6 occurs, the re-evaporated water is discharged out of the dehumidifier 1, and the re-evaporated component directly decreases in performance. Therefore, when the structure of the heat exchanger of FIG. 5 in the second embodiment is applied to either one, it is more dehumidifying that the second heat exchanger 6 is the structure of FIG. The effect of increasing the amount is large, and a preferable form is obtained.

  DESCRIPTION OF SYMBOLS 1 Dehumidifier, 1A Dehumidifier, 2 Compressor, 3 Four way valve, 4 1st heat exchanger, 5 Expansion valve, 6 2nd heat exchanger, 7 Desiccant block, 8 Blower, 10 Housing | casing, 11 Wall surface, 12 Fin , 13 Heat transfer tube, 14 Upstream heat exchanger, 15 Downstream heat exchanger, 16 Capillary tube, 17 Check valve, 20 Air channel chamber, 20a Air inlet, 20b Air outlet, 30 Machine chamber, 40 Drain pan, 41 Water channel , 42 Drain tank, 50 temperature / humidity sensor, 51 temperature / humidity sensor, 60 control device, A refrigerant circuit, B air path.

Claims (9)

A refrigerant circuit in which a compressor, a flow path switching device, a first heat exchanger, a decompression device, and a second heat exchanger are sequentially connected by a refrigerant pipe;
An air path in which the first heat exchanger, a desiccant material capable of absorbing and desorbing moisture, and the second heat exchanger are arranged in this order in series;
A blower for flowing air in the dehumidification target space in the order of the first heat exchanger, the desiccant material, and the second heat exchanger;
A first operation mode in which the first heat exchanger operates as a condenser or a radiator, the second heat exchanger operates as an evaporator, and desorbs moisture held in the desiccant material; A second operation mode in which one heat exchanger operates as an evaporator and the second heat exchanger operates as a condenser or a radiator, and the desiccant material adsorbs moisture from the air passing through the air passage; A controller for performing a dehumidifying operation to switch alternately by switching the flow path of the flow path switching device,
The first heat exchanger includes a plurality of fins arranged in parallel at intervals, and a plurality of rows extending in the row direction passing through the plurality of fins and perpendicular to the air flow direction. It is arranged in multiple stages and has a plurality of heat transfer tubes through which refrigerant passes, and when operating as an evaporator, when operating as an evaporator, the heat transfer tube array on the downstream side from the heat transfer tube array on the upstream side with respect to the air flow direction. A dehumidifier having a flow path configuration in which a refrigerant flows in a heat tube row. The first heat exchanger has an upstream heat exchanger having an upstream air heat transfer tube array and a downstream heat exchanger having an air downstream heat transfer tube array among the plurality of heat transfer tubes. ,
Between the upstream heat exchanger and the downstream heat exchanger, the refrigerant after passing through the upstream heat exchanger is decompressed and flows into the downstream heat exchanger, and the upstream heat exchanger A pressure difference generating device that lowers the refrigerant evaporation temperature of the downstream heat exchanger from the refrigerant evaporation temperature of
In the second operation mode, the first heat exchanger is configured such that the refrigerant evaporation temperature of the upstream heat exchanger is within a predetermined range for reducing the dehumidification amount including the dew point temperature of the inflow air of the first heat exchanger. 2. The operation according to claim 1, wherein the refrigerant evaporating temperature of the downstream heat exchanger is not less than the dew point temperature and not less than a temperature at which a necessary dehumidification amount is obtained. Dehumidifier. The plurality of fins of the first heat exchanger are cut in a step direction between the upstream heat exchanger side and the downstream heat exchanger side. Dehumidifier. A refrigerant circuit in which a compressor, a flow path switching device, a first heat exchanger, a decompression device, and a second heat exchanger are sequentially connected by a refrigerant pipe;
An air path in which the first heat exchanger, a desiccant material capable of absorbing and desorbing moisture, and the second heat exchanger are arranged in this order in series;
A blower for flowing air in the dehumidification target space in the order of the first heat exchanger, the desiccant material, and the second heat exchanger;
A first operation mode in which the first heat exchanger operates as a condenser or a radiator, the second heat exchanger operates as an evaporator, and desorbs moisture held in the desiccant material; A second operation mode in which one heat exchanger operates as an evaporator and the second heat exchanger operates as a condenser or a radiator, and the desiccant material adsorbs moisture from the air passing through the air passage; A controller for performing a dehumidifying operation to switch alternately by switching the flow path of the flow path switching device,
The second heat exchanger includes a plurality of fins arranged in parallel at intervals, and a plurality of rows in a row direction passing through the plurality of fins and perpendicular to the air flow direction and the air flow direction. It is arranged in multiple stages and has a plurality of heat transfer tubes through which refrigerant passes, and when operating as an evaporator, when operating as an evaporator, the heat transfer tube array on the downstream side from the heat transfer tube array on the upstream side with respect to the air flow direction. A dehumidifier having a flow path configuration in which a refrigerant flows in a heat tube row. The second heat exchanger includes an upstream heat exchanger including an air upstream heat transfer tube array and a downstream heat exchanger including an air downstream heat transfer tube array among the plurality of heat transfer tubes. ,
Between the upstream heat exchanger and the downstream heat exchanger, the refrigerant after passing through the upstream heat exchanger is decompressed and flows into the downstream heat exchanger, and the upstream heat exchanger A pressure difference generating device that lowers the refrigerant evaporation temperature of the downstream heat exchanger from the refrigerant evaporation temperature of
In the first operation mode, the second heat exchanger has a refrigerant evaporation temperature of the upstream heat exchanger within a predetermined range for dehumidification amount reduction including a dew point temperature of the inflow air of the second heat exchanger. 5. The dehumidification according to claim 4, wherein the dehumidifying operation is performed at a temperature, and the refrigerant evaporating temperature of the downstream heat exchanger is operated at a temperature equal to or lower than the dew point temperature to obtain a necessary dehumidifying amount. apparatus. The plurality of fins of the second heat exchanger are cut in a step direction between the upstream heat exchanger side and the downstream heat exchanger side. Dehumidifier. A refrigerant circuit in which a compressor, a flow path switching device, a first heat exchanger, a decompression device, and a second heat exchanger are sequentially connected by a refrigerant pipe;
An air path in which the first heat exchanger, a desiccant material capable of absorbing and desorbing moisture, and the second heat exchanger are arranged in this order in series;
A blower for flowing air in the dehumidification target space in the order of the first heat exchanger, the desiccant material, and the second heat exchanger;
A first operation mode in which the first heat exchanger operates as a condenser or a radiator, the second heat exchanger operates as an evaporator, and desorbs moisture held in the desiccant material; A second operation mode in which one heat exchanger operates as an evaporator and the second heat exchanger operates as a condenser or a radiator, and the desiccant material adsorbs moisture from the air passing through the air passage; A controller for performing a dehumidifying operation to switch alternately by switching the flow path of the flow path switching device,
Each of the first heat exchanger and the second heat exchanger includes a plurality of fins arranged in parallel at intervals, a row direction passing through the plurality of fins, which is an air flow direction, and an air flow And a plurality of heat transfer tubes that are arranged in a multi-row and multi-stage in a stage direction orthogonal to the direction and through which the refrigerant passes, and when operating as an evaporator, upstream of the air flow direction A dehumidifier having a flow path configuration in which a refrigerant flows from the heat transfer tube row to the downstream heat transfer tube row. Each of the first heat exchanger and the second heat exchanger includes an upstream heat exchanger provided with an air upstream heat transfer tube row and an air downstream heat transfer tube row among the plurality of heat transfer tubes. A downstream heat exchanger,
Between the upstream heat exchanger and the downstream heat exchanger, the refrigerant after passing through the upstream heat exchanger is decompressed and flows into the downstream heat exchanger, and the upstream heat exchanger A pressure difference generating device that lowers the refrigerant evaporation temperature of the downstream heat exchanger from the refrigerant evaporation temperature of
In the first operation mode, the second heat exchanger has a predetermined dehumidifying amount reduction range in which the refrigerant evaporation temperature of the upstream heat exchanger includes the dew point temperature of the inflow air of the second heat exchanger. And the refrigerant evaporating temperature of the downstream heat exchanger is operated at a temperature equal to or higher than a temperature at which the dehumidifying amount is obtained at or below the dew point temperature,
In the second operation mode, the first heat exchanger has a predetermined dehumidifying amount reduction method in which the refrigerant evaporation temperature of the upstream heat exchanger includes the dew point temperature of the inflow air of the first heat exchanger. It is operated at a temperature within a range, and the refrigerant evaporating temperature of the downstream heat exchanger is operated at a temperature not higher than the dew point temperature and not less than a temperature at which a necessary dehumidification amount is obtained. Item 8. The dehumidifying device according to Item 7. The plurality of fins of each of the first heat exchanger and the second heat exchanger are cut in a step direction between the upstream heat exchanger side and the downstream heat exchanger side. The dehumidifying device according to claim 8.

Images