JP7204906B2 - dehumidifier - Google Patents

Description

The present invention relates to a dehumidifier.

2. Description of the Related Art Conventionally, a dehumidifier including a refrigerating cycle circuit and a heat pipe has been proposed, for example, as described in Japanese Patent Application Laid-Open No. 61-272568 (Patent Document 1). In this refrigeration cycle circuit, the first refrigerant circulates in the order of the compressor, condenser, decompression device, and evaporator. In this heat pipe, the second refrigerant circulates through the precooler and the reheater. The precooler is positioned opposite the evaporator and positioned upwind in airflow relative to the evaporator. The reheater is positioned opposite the condenser and positioned upwind in the airflow relative to the condenser. By pre-cooling the moist air sent to the evaporator by the precooler, the relative humidity of the moist air increases, so that the amount of dehumidification in the evaporator can be increased.

JP-A-61-272568

In the dehumidifier disclosed in the above publication, when the throughput of the precooler increases, the amount of heat released from the reheater to the condenser increases, resulting in a higher condensation temperature. As a result, since the compression ratio of the compressor increases, the EF (Energy Factor) value (L/kWh), which is an index indicating the dehumidification performance of the dehumidifier and indicates the amount of dehumidification L per kWh, decreases.

The present invention has been made in view of the above problems, and an object thereof is to provide a dehumidifier capable of improving the EF value.

A dehumidifier of the present invention includes a housing, and a first refrigerant circuit, a second refrigerant circuit, and a blower housed inside the housing. The first refrigerant circuit includes a compressor, a condenser, a pressure reducing device, an evaporator, and a first refrigerant, and is configured such that the first refrigerant flows in order of the compressor, the condenser, the pressure reducing device, and the evaporator. The second refrigerant circuit includes a precooler, a reheater and a second refrigerant, and is configured such that the second refrigerant circulates through the precooler and the reheater. The condenser includes a first condenser section through which the first refrigerant in a supercooled liquid state flows, and a second condenser section through which the first refrigerant in a superheated gas state flows. The housing includes a first air passage and a second air passage separated from the first air passage. The first air passage is configured such that air drawn into the housing from the outside by the blower passes through the precooler, the evaporator, the reheater, and the first condenser in order. The second air passage is configured to allow air to pass through the second condenser. The housing includes a first region in which the first air passage and the second air passage are arranged, a second region in which the blower is arranged, and an opening connecting the first region and the second region. The blower includes a fan. The diameter of the opening and the diameter of the fan are smaller than the height of the most downwind portion of the condenser.

According to the dehumidifier of the present invention, the dehumidification amount in the evaporator can be increased by the precooler. Moreover, since the second air passage can improve the condensation performance in the condenser, the EF value can be improved.

BRIEF DESCRIPTION OF THE DRAWINGS It is a figure which shows roughly the structure of the dehumidifier which concerns on Embodiment 1 of this invention. FIG. 4 is a diagram schematically showing the configuration of a dehumidifier according to a modification of Embodiment 1 of the present invention; 7 is a graph showing the relationship between the EF value improvement rate and the outside-tube area ratio of the dehumidifier according to Embodiment 2 of the present invention. It is a figure which shows roughly the structure of the dehumidifier based on Embodiment 3 of this invention. It is a figure which shows roughly the structure of the dehumidifier based on Embodiment 4 of this invention. FIG. 5 is a refrigerant circuit diagram of a dehumidifier according to Embodiment 5 of the present invention. FIG. 12 is a refrigerant circuit diagram showing a state in which refrigerant flows through the first condensation section of the dehumidifier according to Embodiment 5 of the present invention, and refrigerant does not flow through the second condensation section and the third condensation section; FIG. 11 is a refrigerant circuit diagram showing a state in which refrigerant flows through a first condensation section, a second condensation section, and a third condensation section of a dehumidifier according to Embodiment 5 of the present invention; It is a figure which shows roughly the structure of the dehumidification apparatus which concerns on Embodiment 6 of this invention. It is a perspective view which shows roughly the dehumidification apparatus which concerns on Embodiment 6 of this invention. FIG. 10 is a diagram showing the positional relationship of a fan, an opening, a condenser, etc. of a dehumidifier according to Embodiment 7 of the present invention;

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the drawings below, the same or corresponding parts are denoted by the same reference numerals, and the description thereof will not be repeated.

Embodiment 1.
Referring to FIG. 1, a dehumidifier 1 according to Embodiment 1 includes a first refrigerant circuit C1 including a compressor 2, a condenser 3, a pressure reducing device 4 and an evaporator 5, an air blower 6, a precooler 7 and a second refrigerant circuit C<b>2 including a reheater 8 and a housing 20 . The first refrigerant circuit C<b>1 , the second refrigerant circuit C<b>2 and the blower 6 are housed inside the housing 20 . The housing 20 faces an external space (indoor space) to be dehumidified by the dehumidifier 1 .

The first refrigerant circuit C1 includes a compressor 2, a condenser 3, a pressure reducing device 4, an evaporator 5 and a first refrigerant. The first refrigerant circuit C1 is configured such that the first refrigerant flows through the compressor 2, the condenser 3, the decompression device 4, and the evaporator 5 in this order. Specifically, the first refrigerant circuit C1 is configured by connecting the compressor 2, the condenser 3, the decompression device 4, and the evaporator 5 in this order via pipes. The first refrigerant passes through this pipe and circulates through the first refrigerant circuit C1 through the compressor 2, the condenser 3, the decompression device 4, and the evaporator 5 in this order. Solid arrows in FIG. 1 indicate the flow of the first refrigerant in the first refrigerant circuit C1.

Compressor 2 is configured to compress the first refrigerant. Specifically, the compressor 2 is configured to suck low-pressure refrigerant through a suction port, compress it, and discharge it as a high-pressure refrigerant through a discharge port. The compressor 2 may be configured such that the discharge capacity of the refrigerant is variable. Specifically, the compressor 2 may be an inverter compressor. When the compressor 2 has a variable discharge capacity of the first refrigerant, the circulation amount of the first refrigerant in the dehumidifier 1 can be controlled by adjusting the discharge capacity of the compressor 2. becomes.

The condenser 3 is configured to condense and cool the first refrigerant pressurized by the compressor 2 . The condenser 3 is a heat exchanger that exchanges heat between the first refrigerant and air. The condenser 3 has an inlet and an outlet for the first refrigerant and an inlet and an outlet for air. The first refrigerant inlet of the condenser 3 is connected to the discharge port of the compressor 2 by a pipe.

The condenser 3 includes a first condenser section 3a and a second condenser section 3b. The first condensing portion 3a is configured so that the supercooled first refrigerant flows therethrough. The second condensing portion 3b is configured to allow the refrigerant in a superheated gas state to flow. The first condensing section 3a may have a region through which the supercooled first refrigerant flows, and may have a region through which the supercooled and gas-liquid two-phase first refrigerants flow. The second condensing section 3b may have a region through which the first refrigerant in the superheated gas state flows, and may have a region through which the first refrigerant in the superheated gas state and the gas-liquid two-phase state flows.

In the condenser 3, the first refrigerant flows through the second condensation section 3b and the first condensation section 3a in this order. Each of the first condenser section 3a and the second condenser section 3b has a refrigerant inlet and a refrigerant outlet. A refrigerant inlet of the second condensing section 3b is connected to a discharge port of the compressor 2 via a pipe. A refrigerant inlet of the first condenser 3a is connected to a refrigerant outlet of the second condenser 3b. A refrigerant outlet of the first condensing section 3a is connected to the decompression device 4 via a pipe. The second condensation section 3b is arranged above the first condensation section 3a.

The condenser 3 may be configured as one piece or a plurality of pieces. The condenser 3 is arranged downstream of the evaporator 5, the precooler 7, and the reheater 8 in the direction of air flow. The height of the condenser 3 is higher than the heights of the evaporator 5 , precooler 7 and reheater 8 .

The decompression device 4 is configured to decompress and expand the first refrigerant cooled in the condenser 3 . The decompression device 4 is, for example, an expansion valve. This expansion valve may be an electronically controlled valve. The decompression device 4 is not limited to an expansion valve, and may be a capillary tube. The decompression device 4 is connected to each of the refrigerant outlet of the condenser 3 and the refrigerant inlet of the evaporator 5 via piping.

The evaporator 5 is configured to cause the first refrigerant decompressed and expanded by the decompression device 4 to absorb heat and evaporate the refrigerant. The evaporator 5 is a heat exchanger that exchanges heat between the first refrigerant and air. The evaporator 5 has an inlet and an outlet for the first refrigerant and an inlet and an outlet for air. A first refrigerant outlet of the evaporator 5 is connected to a suction port of the compressor 2 via a pipe. The evaporator 5 is arranged upstream of the condenser 3 in the air flow generated by the blower 6 . That is, the evaporator 5 is arranged on the windward side of the condenser 3 .

The blower 6 is configured to blow air. The blower 6 is configured to take in air from the outside of the housing 20 into the inside and blow the air to the condenser 3 and the evaporator 5 . Specifically, the blower 6 is configured to take air from the outside space (indoor space) into the housing 20 , pass the air through the evaporator 5 and the condenser 3 , and then discharge the air outside the housing 20 .

In this embodiment, the blower 6 has a shaft 6a and a fan 6b. Fan 6b is configured to rotate about axis 6a. As the fan 6b rotates around the shaft 6a, air is drawn into the housing 20 from the room as indicated by arrows A and C in the drawing. As indicated by an arrow B in the drawing, air taken into the interior of the housing 20 is discharged to the external space (indoor space). In this way, the air circulates in the external space (indoor space) via the dehumidifier 1 .

In the present embodiment, the blower 6 is arranged downstream of the condenser 3 in the direction of air flow. In addition, the blower 6 may be arranged between the condenser 3 and the evaporator 5 in the air flow direction. Further, the blower 6 may be arranged upstream of the evaporator 5 in the air flow direction.

The second refrigerant circuit C2 includes a precooler 7, a reheater 8 and a second refrigerant. The second refrigerant circuit C<b>2 is configured such that the second refrigerant circulates through the precooler 7 and the reheater 8 . Specifically, the second refrigerant circuit C2 is configured by connecting the precooler 7 and the reheater 8 via piping. The second refrigerant circuit C2 may be a natural circulation circuit. Specifically, the second refrigerant circuit C2 may be a heat pipe. A dashed arrow in FIG. 1 indicates the flow of the second refrigerant in the second refrigerant circuit C2.

The pre-cooler 7 is configured to pre-cool the air taken from the outside of the housing 20 into the inside by the blower 6 before flowing into the evaporator. The precooler 7 is configured to cause the second refrigerant to absorb heat from the air and evaporate the second refrigerant. The precooler 7 is a heat exchanger that exchanges heat between the second refrigerant and air. The precooler 7 has an inlet and an outlet for the second refrigerant and an inlet and an outlet for the air. Each of the second refrigerant inlet and outlet of the precooler 7 is connected to each of the second refrigerant outlet and inlet of the reheater 8 via a pipe. The precooler 7 is arranged upstream of the reheater 8 in the air flow generated by the blower 6 . Also, the precooler 7 is arranged upstream of the evaporator 5 in the flow of air generated by the blower 6 . That is, the precooler 7 is arranged on the windward side of the evaporator 5 .

The reheater 8 is configured to reheat the air taken from the outside of the housing 20 into the inside by the blower 6 before flowing into the condenser 3 . The reheater 8 is configured to condense the second refrigerant evaporated in the precooler 7 to heat the air. The reheater 8 is a heat exchanger that exchanges heat between the second refrigerant and air. The reheater 8 has an inlet and an outlet for the second refrigerant and an inlet and an outlet for the air. The reheater 8 is arranged between the first condenser section 3 a and the evaporator 5 in the first air passage 9 . The reheater 8 is arranged upstream of the first condenser section 3 a in the flow of air generated by the blower 6 . That is, the reheater 8 is arranged on the windward side of the first condenser section 3a.

The housing 20 includes a first air passage 9 , a second air passage 10 and a first partition portion 11 . The second air passage 10 is separated from the first air passage 9 . The first partition 11 is configured to partition the first air passage 9 and the second air passage 10 . Each of first air duct 9 and second air duct 10 is defined by housing 20 and first partition 11 . That is, two air passages (air passages) of the first air passage 9 and the second air passage 10 are provided inside the housing 20 . A first condenser section 3 a , an evaporator 5 , a precooler 7 and a reheater 8 are arranged in the first air passage 9 .

Inside the first air passage 9, a first condenser section 3a, an evaporator 5, a precooler 7 and a reheater 8 are arranged. The first air passage 9 is configured such that the air taken into the housing 20 from the outside by the blower 6 passes through the precooler 7, the evaporator 5, the reheater 8, and the first condenser 3a in this order. ing. In the first air passage 9, as indicated by an arrow A in the drawing, air taken into the housing 20 from the outside by the rotation of the fan 6b around the shaft 6a flows through the precooler 7, the evaporator 5, and the precooler 7. It passes through the reheater 8 and the first condensation section 3a in order.

A second condensing section 3 b is arranged inside the second air passage 10 . The second air passage 10 is configured such that the air taken into the interior from the outside of the housing 20 by the blower 6 passes through the second condensing portion 3b. In the second air passage 10, as indicated by an arrow C in the figure, the fan 6b rotates around the shaft 6a, so that the air taken into the housing 20 from the outside passes through the second condensation section 3b. As indicated by arrows A and C in the figure, the air in the first air passage 9 flows parallel to and in the same direction as the air in the second air passage 10 .

Note that the space defining the first air passage 9 does not need to be completely separated from the space defining the second air passage 10 . In the present embodiment, the space that defines the first air passage 9 is the space that defines the second air passage 10 downstream of the first condensing section 3a in the direction of air flow in the first air passage 9. It is connected.

One end (upstream end) located on the upstream side of the first partition 11 in the air circulation direction in the first air passage 9 is arranged upstream of the air outlet of the precooler 7 . The other end (downstream end) located on the downstream side of the first partition 11 in the direction of air flow in the second air passage 10 is located at the same position as the air outlet of the reheater 8 or downstream from this air outlet. placed on the side. The first partition portion 11 is formed in a flat plate shape, for example. The first partition 11 is fixed inside the housing 20 .

The housing 20 is provided with an inlet 14 and an outlet 21 . The suction port 14 is for introducing air into the housing 20 from an external space (indoor space) to be dehumidified. The suction port 14 includes a first suction port 14a and a second suction port 14b. The first suction port 14 a communicates with the first air passage 9 . The second suction port 14 b communicates with the second air passage 10 . The air outlet 21 is for blowing air from the inside of the housing 20 to the external space.

The housing 20 has a back surface 20a and a front surface 20b. A first suction port 14a and a second suction port 14b are provided on the rear surface 20a. The first suction port 14a on the rear surface 20a is configured to draw air into the first air passage 9. As shown in FIG. The second suction port 14b on the rear surface 20a is configured to draw air into the second air passage 10. As shown in FIG.

The first suction port 14 a is arranged upstream of the air inlet of the precooler 7 in the first air passage 9 in the air circulation direction of the first air passage 9 . The second suction port 14 b is arranged upstream of the air inlet of the second condensation section 3 b in the second air passage 10 in the air circulation direction of the second air passage 10 .

In addition, in the dehumidifier 1 , the decompression device 4 may be arranged in the first air passage 9 .
The housing 20 also includes a second partition 12 . The second partition part 12 is configured to partition the first area 22 and the second area 23 . Each of first region 22 and second region 23 is defined by housing 20 and second partition 12 . In other words, the housing 20 includes a first area 22 and a second area 23 . A first air passage 9 and a second air passage 10 partitioned by a first partition portion 11 are arranged in the first region 22 . That is, in the first region 22, the first condenser section 3a, the evaporator 5, the precooler 7, and the reheater 8 are arranged in the first air passage 9. As shown in FIG. Also, in the first region 22, the second condensation section 3b is arranged in the second air passage 10. As shown in FIG. A blower 6 is arranged in the second area 23 .

The second partition 12 is provided with an opening 12 a that connects the first region 22 and the second region 23 . That is, the housing 20 includes the opening 12a. The second partition part 12 is formed in a flat plate shape, for example. When the opening 12a of the second partition 12 is viewed from the first area 22 along the direction from the first area 22 to the second area 23, the fan 6b is arranged in the opening 12a. That is, the outer diameter of the fan 6b is smaller than the inner diameter of the opening 12a. Also, the height of the second partition 12 is adjusted so that the air flowing from the first area 22 to the second area 23 passes through the upper end of the second condenser 3b. Therefore, since heat exchange is performed up to the upper end of the second condenser section 3b, the heat exchange of the second condenser section 3b is not hindered.

The first refrigerant and the second refrigerant may be the same. Also, the first refrigerant and the second refrigerant may be different. For example, the first refrigerant may be a Freon-based refrigerant, and the second refrigerant may be a hydrocarbon (HC)-based refrigerant. Since the first refrigerant and the second refrigerant are different, it is possible to reduce costs and reduce the global warming potential (GWP) compared to the case where both the first refrigerant and the second refrigerant are Freon-based refrigerants. .

If both the first refrigerant and the second refrigerant are Freon-based refrigerants, Freon-based refrigerants are subject to the Freon gas (F-Gas) regulations in Europe, so they are difficult to obtain and their prices tend to rise. Therefore, the dehumidifier 1 becomes expensive. In addition, when a hydrocarbon (HC)-based flammable refrigerant is used, the risk of flammability increases as the amount of refrigerant charged increases, so the amount of refrigerant is subject to regulation in Europe. An inexpensive hydrocarbon (HC) refrigerant such as R290 may be used as the first refrigerant, and an expensive Freon refrigerant such as R1234f may be used as the second refrigerant. The first and second refrigerants may be combined depending on performance, cost and safety.

The distance between condenser 3 and reheater 8 may be greater than the distance between reheater 8 and evaporator 5 . Specifically, the distance k1 between the first condenser 3a and the reheater 8 may be greater than the distance j1 between the reheater 8 and the evaporator 5 . Also, the distance k1 between the first condenser section 3a and the reheater 8 may be greater than the distance j2 between the evaporator 5 and the precooler 7 .

Next, the operation of the dehumidifier 1 according to the present embodiment during dehumidification operation will be described.
In the first refrigerant circuit C<b>1 , the first refrigerant in the superheated gas state discharged from the compressor 2 flows into the second condensation section 3 b arranged in the second air passage 10 . The first refrigerant in the superheated gas state that has flowed into the second condensation section 3b is cooled by exchanging heat with the air taken into the second air passage 10 from the external space through the second suction port 14b. phase state.

The gas-liquid two-phase first refrigerant flowing out of the second condenser 3 b flows into the first condenser 3 a arranged in the first air passage 9 . The gas-liquid two-phase first refrigerant that has flowed into the first condensation section 3a is taken from the external space into the first air passage 9 through the first suction port 14a, and It heat-exchanges with the air that has passed through 8 in order and becomes supercooled.

The supercooled first refrigerant flowing out of the first condenser section 3a is decompressed by passing through the decompression device 4 and becomes a gas-liquid two-phase state, after which the evaporator disposed in the first air passage 9 Flow into 5. The first refrigerant in the gas-liquid two-phase state that has flowed into the evaporator 5 is heated by heat exchange with the air taken into the first air passage 9 from the external space through the first suction port 14a to become a superheated gas state. becomes. The first refrigerant in the superheated gas state is sucked into the compressor 2, compressed by the compressor 2, and discharged again. Thus, the first refrigerant circulates through the first refrigerant circuit C1.

In the second refrigerant circuit C<b>2 , the second refrigerant in the precooler 7 evaporates by exchanging heat with the air taken into the first air passage 9 . The evaporated second refrigerant flows to the reheater 8 due to the pressure difference. The second refrigerant that has flowed to the reheater 8 is condensed by exchanging heat with the air that has passed through the precooler 7 and the evaporator 5 in that order. The condensed second refrigerant flows to precooler 7 by gravity. Thus, the second refrigerant circulates through the second refrigerant circuit C2.

The air taken into the first air passage 9 is cooled by heat exchange with the second refrigerant in the precooler 7 . The air cooled in the precooler 7 is cooled to a temperature below the dew point of the air by heat exchange with the first refrigerant in the evaporator 5 . The air is thereby dehumidified in the evaporator 5 . Since the air sent to the evaporator 5 is cooled in advance by the precooler 7, the relative density of the moist air increases, so that the amount of dehumidification in the evaporator 5 can be increased.

The air cooled in the evaporator 5 is heated by being heat-exchanged with the second refrigerant in the reheater 8 . The air heated in the reheater 8 is further heated by being heat-exchanged with the first refrigerant in the first condenser section 3a. Also, the air taken into the second air passage 10 is heated by being heat-exchanged with the first refrigerant in the second condensation section 3b.

Next, the effects of the dehumidifier 1 according to this embodiment will be described in comparison with a comparative example. Referring to FIG. 2, dehumidifier 1 of the comparative example is mainly different in that first air passage 9 and second air passage 10 of the present embodiment are not provided. Air is taken into the housing 20 from the suction port 14 as indicated by an arrow A in the figure. The air taken into the housing 20 passes through the precooler 7, the evaporator 5, the reheater 8, and the condenser 3 in order, and exits the housing 20 from the air outlet 21 as indicated by the arrow B in the figure. is blown out of the

In the dehumidifier 1 of the comparative example, when the throughput of the precooler 7 increases, the amount of heat released from the reheater 8 to the condenser 3 increases, so the condensation temperature increases. As a result, the compression ratio of the compressor 2 increases, so the EF (Energy Factor) value (L/kWh), which is an index indicating the dehumidification performance of the dehumidifier 1 and indicates the amount of dehumidification L per kWh, decreases.

In contrast, according to the dehumidifier 1 according to the present embodiment, the dehumidification amount in the evaporator 5 can be increased by the precooler 7 . That is, since the moist air sent to the evaporator 5 is cooled in advance by the precooler 7, the relative humidity of the moist air increases, so that the amount of dehumidification in the evaporator 5 can be increased. Moreover, since the second air passage 10 can improve the condensation performance in the condenser 3, the EF value can be improved. That is, the air taken into the housing 20 flows through the second air passage 10 and is heat-exchanged in the second condensation section 3b. Therefore, the amount of air flowing through the condenser 3 can be increased. Moreover, it becomes possible to flow air having a temperature lower than that of the air passing through the reheater 8 and flowing to the first condenser section 3a to the second condenser section 3b. Therefore, it is possible to improve the condensing capacity of the first refrigerant circuit C1. As a result, the EF value can be improved even if the heat dissipation amount of the reheater 8 increases due to the increased throughput of the precooler 7 .

Also, by improving the cooling capacity of the second refrigerant circuit C2, the size of the first refrigerant circuit C1 can be reduced. The second refrigerant circuit C2 does not require power because the circuit operates by self-circulation of the refrigerant. As the throughput of the second refrigerant circuit C2 increases, the power of the first refrigerant circuit C1 can be reduced. That is, the amount of refrigerant circulated in the first refrigerant circuit C1 required to satisfy the cooling performance can be reduced, so the size of the compressor 2 can be reduced. Thereby, the power required to operate the compressor 2 can be reduced.

According to the dehumidifier 1 according to the present embodiment, the first refrigerant and the second refrigerant may be different. Therefore, it is possible to reduce costs by reducing the amount of expensive refrigerant charged. Also, by using a refrigerant with a low GWP (global warming potential), it is possible to reduce the GWP (global warming potential). In addition, safety can be ensured by reducing the amount of flammable refrigerant charged.

According to the dehumidifier 1 according to this embodiment, the distance between the condenser 3 and the reheater 8 is greater than the distance between the reheater 8 and the evaporator 5 . Therefore, heat loss in the reheater 8 due to radiant heat from the condenser 3 can be suppressed.

Embodiment 2.
In the dehumidifier 1 according to Embodiment 2, the sum of the outer tube areas of the precooler 7 and the reheater 8 is twice or less than the outer tube area of the evaporator 5. It differs mainly from device 1. The tube outer area is the area of the outer peripheral surface of the heat transfer tube. If the tube outer area ratio is the sum of the outer tube areas of the precooler and the reheater/the outer tube area of the evaporator x 100, then 4 < the outer tube area ratio (the sum of the outer tube areas of the precooler and the reheater /outside area of evaporator x 100) <100.

Referring to FIG. 3, when the sum of the tube outer areas of precooler 7 and reheater 8 is more than twice the tube outer area of evaporator 5, the EF value improvement rate becomes small. That is, the effect of the second refrigerant circuit C2 composed of the precooler 7 and the reheater 8 is reduced. This is because when the temperature of the second refrigerant in the precooler 7 rises, the temperature difference between the second refrigerant and the air inlet temperature decreases, resulting in a decrease in heat exchange efficiency. Since the circulation path of the second refrigerant is lengthened, the flow path resistance is increased, and the amount of circulation of the refrigerant is reduced, so the amount of heat exchange in the second refrigerant circuit is reduced. Therefore, even if the size of the precooler 7 and the reheater 8 are increased, the corresponding performance improvement cannot be obtained, resulting in poor cost performance. Further, when the number of rows in the air flow direction increases, the power of the blower 6 increases because the ventilation resistance increases. This reduces the EF value.

When the sum of the outer tube areas of the precooler 7 and the reheater 8/the outer tube area of the evaporator x 100 ≤ 4, the second refrigerant circuit C2 is formed only of heat transfer tubes without fins, whereby the outer heat transfer Since the area becomes too small, the heat exchange amount of the precooler 7 is significantly reduced. Also, by filling the second refrigerant circuit C2 with refrigerant, it is possible to increase the amount of heat exchange. The temperature difference is also small. The fins of the heat exchanger have a function of anti-corrosion and are designed to corrode in order from the fins to the heat transfer tubes. If there are no fins, the heat transfer tubes will immediately corrode, so the second refrigerant in the second refrigerant circuit C2 will easily leak into the room. Therefore, the reliability is lowered.

According to the dehumidifier 1 according to the present embodiment, the sum of the outer tube areas of the precooler 7 and the reheater 8 is less than twice the outer tube area of the evaporator 5, so the EF value improvement rate is Because it is large, cost performance can be improved.

In addition, by setting 4<outside area ratio (sum of outside area of precooler and reheater/outside area of evaporator×100)<100, transfer of precooler 7 and reheater 8 It becomes possible to improve the EF value corresponding to the expansion of the thermal area.

Embodiment 3.
Referring to FIG. 4, dehumidifier 1 according to Embodiment 3 is mainly different from dehumidifier 1 according to Embodiment 1 in that condenser 3 includes a third condensation section 3c.

In the dehumidifier 1 according to Embodiment 3, the condenser 3 includes a first condensation section 3a, a second condensation section 3b, and a third condensation section 3c. The third condenser 3c is arranged between the first condenser 3a and the second condenser 3b in the first refrigerant circuit C1. The third condensing portion 3c is configured such that a gas-liquid two-phase refrigerant flows. The third condensation section 3 c is arranged in the first air passage 9 . The air taken in from the outside of the housing 20 by the blower 6 passes through the first air passage 9 through the precooler 7, the evaporator 5, the reheater 8, the first condenser 3a, and the third condenser 3c in this order. pass. The first air passage 9 is configured such that the air passes through the first condensation section 3a and then passes through the third condensation section 3c.

The distance k1 between the first condenser section 3a and the reheater 8 may be greater than the distance j1 between the reheater 8 and the evaporator 5 . Also, the distance k1 between the first condenser section 3a and the reheater 8 may be greater than the distance j2 between the evaporator 5 and the precooler 7 . Furthermore, the distance k2 between the third condenser 3c and the first condenser 3a may be greater than the distance k1 between the first condenser 3a and the reheater 8.

The first condenser section 3a and the third condenser section 3c are arranged downstream of the first condenser section 3a, the evaporator 5, the precooler 7, and the reheater 8 in the air flow direction. The total height of the first condenser section 3a and the third condenser section 3c is higher than the height of the first condenser section 3a, the evaporator 5, the precooler 7, and the reheater 8.

According to the dehumidifier 1 of the present embodiment, the first air passage 9 is configured such that the air passes through the first condensation section 3a and then passes through the third condensation section 3c. The first condensation section 3a through which supercooled refrigerant flows has the lowest refrigerant temperature among the first condensation section 3a, the second condensation section 3b, and the third condensation section 3c. Therefore, the temperature difference between the air temperature of the reheater 8 and the first refrigerant in the first condenser section 3a during heat dissipation becomes closer, and the amount of heat received in the first condenser section 3a becomes smaller. As a result, deterioration in condensation performance due to heat dissipation from the reheater 8 can be suppressed. In addition, since the temperature of the refrigerant in the third condensation section 3c is higher than the temperature of the refrigerant in the first condensation section 3a, heat can be exchanged with the air whose temperature has increased due to the heat exchange in the first condensation section 3a. As a result, the condensation performance can be ensured by the third condensing portion 3c, so that the deterioration of the condensation performance in the first refrigerant circuit C1 can be suppressed.

Also, the volume of air passing through the second condensing section 3b may be increased by increasing the volume of air flowing through the second air passage 10 . For example, the air volume may be increased by providing a suction port of the housing 20 between the first condensation section 3a and the second condensation section 3b.

In addition, since the diameter of the heat transfer tube of the first condenser section 3a, in which the liquid region of the refrigerant increases, is made smaller than that of other heat exchangers, the amount of refrigerant is reduced, the airflow resistance is reduced, and the heat transfer performance is improved. may be realized. These make it possible to further improve the EF value over the first embodiment.

Embodiment 4.
Referring to FIG. 5, dehumidifier 1 according to Embodiment 4 is mainly different from dehumidifier 1 according to Embodiment 1 in that damper DP is further provided.

The dehumidifier 1 according to Embodiment 4 further includes a damper DP. A damper DP is arranged in the second air passage 10 . The damper DP is configured to be able to adjust the amount of air passing through the second air passage 10 . For example, damper DP is configured to be rotatable by a motor (not shown). In this case, the amount of air passing through the second air passage 10 can be increased or decreased by increasing or decreasing the passage area of the second air passage 10 by rotating the damper DP.

When the amount of dehumidified water in the evaporator 5 is large and the air volume on the first air passage 9 side decreases, the damper DP is closed. That is, the second air passage 10 is closed by rotating the damper DP so as to block the flow path of the second air passage 10 . At this time, the damper DP is arranged so as to extend in the vertical direction in FIG. As a result, the air volume on the first air passage 9 side increases.

The damper DP is opened when the dehumidification load in the room is small and therefore the cooling capacity may be small. That is, the second air passage 10 is opened by rotating the damper DP so that the flow path of the second air passage 10 communicates. At this time, the damper DP is arranged so as to extend in the horizontal direction in FIG. This increases the amount of air flowing through the second air passage 10, thereby improving the condensation performance. Therefore, the input to the dehumidifier 1 can be reduced.

In the dehumidifier 1 according to the present embodiment, the damper DP adjusts the air volume of the air flowing through the first air passage 9 and the second air passage 10 according to the load from the room of the dehumidifier 1, thereby further increasing the efficiency. good driving can be realized. Therefore, a high EF value can be maintained even when load fluctuations occur.

Embodiment 5.
Referring to FIG. 6, dehumidifier 1 according to Embodiment 5 further includes a flow control valve 13 and evaporator 5 includes first evaporator 5a and second evaporator 5b. It is mainly different from the dehumidifier 1 according to the third embodiment.

The dehumidifier 1 according to Embodiment 5 further includes a flow control valve 13 . The flow control valve 13 is arranged in the first refrigerant circuit C1. In this embodiment, a plurality of flow control valves 13 are arranged. The flow control valve 13 is arranged upstream or downstream of the condenser 3 and the evaporator 5 in the first refrigerant circuit C1. The flow control valve 13 is configured to be openable and closable. The flow control valve 13 is, for example, an electromagnetic valve.

The evaporator 5 includes a first evaporator 5a and a second evaporator 5b. The first evaporator 5 a and the second evaporator 5 b are connected via a flow rate control valve 13 . The flow control valve 13 is configured to allow the first refrigerant to flow through at least one of the first evaporator 5a and the second evaporator 5b.

Referring to FIG. 7, when the load is small, the flow regulating valve 13 is opened and closed so that the first refrigerant flows in the order of the compressor 2, the first condensing section 3a, the decompression device 4, and the first evaporating section 5a. . In FIG. 7, the flow control valves 13 shown in white are open and the flow control valves 13 shown in black are closed.

Referring to FIG. 8, when the load is large, compressor 2, second condenser 3b, third condenser 3c, first condenser 3a, decompression device 4, evaporator 5 (first evaporator 5a and The flow control valve 13 is opened and closed so that the first refrigerant flows in order of the second evaporator 5b). In FIG. 8, the flow control valves 13 shown in white are open and the flow control valves 13 shown in black are closed.

According to the dehumidifier 1 according to the present embodiment, opening and closing the flow control valve 13 enables switching of the path of the first refrigerant circuit C1 according to the load and operating state of each heat exchanger. In addition, since the condensing pressure and the evaporating pressure can be adjusted in two stages depending on the degree of throttling of the flow control valve 13, highly efficient operation becomes possible by adjusting the pressure of each heat exchanger.

Embodiment 6.
9 and 10, dehumidifier 1 according to Embodiment 6 is different from dehumidifier 1 according to Embodiment 3 in that intake port 15 is provided in side surface 20c of housing 20. different.

In the dehumidifier 1 according to Embodiment 6, the side surface 20c of the housing 20 is provided with the intake port 15 . The intake port 15 is configured to draw air into the first air passage 9 and the second air passage 10 . The intake port 15 is arranged between the first condenser section 3a and the second condenser section 3b and the third condenser section 3c. The air intake port 15 is configured to draw air between the first condensation section 3a and the second and third condensation sections 3b and 3c.

According to the dehumidifier 1 according to the present embodiment, the housing 20 is provided with the intake port 15 in addition to the first intake port 14a and the second intake port 14b. It is possible to increase the amount of air passing through the portion 3c. Thereby, the condensation ability can be improved.

Embodiment 7.
Referring to FIG. 11, in dehumidifier 1 according to the seventh embodiment, the diameter of opening 12a and the diameter of fan 6b are smaller than the height of condenser 3 located on the most downwind side.

When the diameter of the opening 12a of the housing 20 and the diameter of the fan 6b of the blower 6 are larger than the height of the most downstream part of the condenser 3 in the air suction direction, the diameter of the fan 6b determines the width of the dehumidifier 1, Since the height is determined, the dehumidifier 1 is enlarged.

The diameter of the opening 12a and the diameter of the fan 6b are larger than the height of each of the evaporator 5, the precooler 7 and the reheater 8. If the diameter of opening 12a and the diameter of fan 6b become smaller than the height of evaporator 5, precooler 7 and reheater 8, the distance between opening 12a and the most downstream part of condenser 3 must be increased. , the heat exchange performance deteriorates because little air flows above the most downstream condenser 3 portion. In addition, the evaporator 5, the precooler 7, and the reheater 8 tend to have a wind speed distribution in the height direction, so that their heat exchange performance is also lowered. In order to equalize the wind speed distribution in the height direction, the distance between the opening 12a and the most downstream part of the condenser 3, the dimension between the condenser 3 and the reheater 8, the reheater 8 and the evaporation It is necessary to increase the size of the vessel 5. Therefore, since the thickness of the dehumidifier 1 in the depth direction increases, the dehumidifier 1 becomes large. Also, the reduction in the diameter of the fan 6b reduces the air volume. Reducing the diameter of the opening 12a increases ventilation resistance. Therefore, the input of the blower 6 deteriorates.

According to the dehumidifier 1 according to the present embodiment, the diameter of the opening 12a and the diameter of the fan 6b are smaller than the height of the portion of the condenser 3 arranged on the most downwind side. Therefore, it is possible to prevent the dehumidifier 1 from increasing in size.

According to dehumidifier 1 according to the present embodiment, the diameter of opening 12 a and the diameter of fan 6 b are greater than the heights of evaporator 5 , precooler 7 , and reheater 8 . Therefore, the wind velocity distribution in the height direction of the condenser 3, evaporator 5, precooler 7, and reheater 8 can be suppressed. Therefore, the heat exchange efficiency of the heat exchanger can be enhanced. As a result, it is possible to use the air blower 6 of a reasonable size that allows the heat exchanger to be used effectively, so that the dehumidifier 1 of an appropriate size can be provided.

Each of the above embodiments can be combined as appropriate.
It should be considered that the embodiments disclosed this time are illustrative in all respects and not restrictive. The scope of the present invention is indicated by the scope of the claims rather than the above description, and is intended to include all changes within the scope and meaning equivalent to the scope of the claims.

1 dehumidifier, 2 compressor, 3 condenser, 3a first condenser, 3b second condenser, 3c third condenser, 4 decompression device, 5 evaporator, 5a first evaporator, 5b second evaporator, 6 blower, 6a shaft, 6b fan, 7 precooler, 8 reheater, 9 first air passage, 10 second air passage, 11 first partition, 12 second partition, 12a opening, 13 flow rate adjustment valve, 14 suction port, 14a first suction port, 14b second suction port, 15 suction port, 20 housing, 20a back surface, 20b front surface, 20c side surface, 21 blowout port, 22 first region, 23 second region, C1 First Refrigerant Circuit, C2 Second Refrigerant Circuit, DP Damper.

Claims (9)

a housing;
A first refrigerant circuit, a second refrigerant circuit and a blower housed inside the housing,
The first refrigerant circuit includes a compressor, a condenser, a pressure reducing device, an evaporator, and a first refrigerant, and the first refrigerant flows in the order of the compressor, the condenser, the pressure reducing device, and the evaporator. is configured to
the second refrigerant circuit includes a precooler, a reheater and a second refrigerant, and is configured such that the second refrigerant circulates through the precooler and the reheater;
The condenser includes a first condenser section through which the first refrigerant in a supercooled liquid state flows, and a second condenser section through which the first refrigerant in a superheated gas state flows,
The housing includes a first air passage and a second air passage separated from the first air passage,
The first air passage is configured such that the air taken into the interior from the exterior of the housing by the blower passes through the precooler, the evaporator, the reheater, and the first condenser in this order. has been
the second air passage is configured such that the air passes through the second condensation section ;
The housing includes a first region in which the first air passage and the second air passage are arranged, a second region in which the blower is arranged, and an opening connecting the first region and the second region. and
the blower includes a fan;
The dehumidifier , wherein the diameter of the opening and the diameter of the fan are smaller than the height of the most downwind portion of the condenser . 2. The dehumidifier according to claim 1, wherein the sum of the outer tube areas of said precooler and said reheater is less than or equal to twice the outer tube area of said evaporator. the condenser includes a third condenser section disposed between the first condenser section and the second condenser section in the first refrigerant circuit;
The dehumidifier according to claim 1 or 2, wherein said first air passage is configured such that said air passes through said first condensation section and then passes through said third condensation section. Further comprising a damper arranged in the second air passage,
The dehumidifier according to any one of claims 1 to 3, wherein said damper is configured to be able to adjust the amount of said air passing through said second air passage. Further equipped with a flow control valve,
The evaporator includes a first evaporator and a second evaporator,
The dehumidifier according to any one of claims 1 to 4, wherein the flow rate adjustment valve is configured to allow the first refrigerant to flow through at least one of the first evaporator and the second evaporator. . The dehumidifier according to any one of claims 1 to 5, wherein said first refrigerant is different from said second refrigerant. The dehumidifier according to any one of claims 1 to 6, wherein the distance between the condenser and the reheater is greater than the distance between the reheater and the evaporator. The housing includes a rear surface provided with a first inlet and a second inlet, and a side surface provided with an inlet,
The first suction port is configured to suck the air into the first air passage,
The second suction port is configured to suck the air into the second air passage,
The dehumidifier according to any one of claims 1 to 7, wherein said intake port is configured to draw said air into said first air passage and said second air passage. 9. The dehumidifier of claim 8 , wherein the aperture of the opening and the diameter of the fan are greater than the height of each of the evaporator, precooler and reheater.

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