Dryer

Abstract

To provide a dryer capable of improving dehumidification performance of circulation air with increased circulation air passing through an evaporator.SOLUTION: The dryer of the present invention includes a heat pump unit 610 having a condenser 612, an evaporator 614, and drain tanks 204C and 204E disposed below the evaporator 614 and the condenser 612. The evaporator 614 and the condenser 612 are disposed in the order of the evaporator 614 and the condenser 612 from the upstream side of a circulation air channel. The heat pump unit 610 includes a baffle 205E that covers at least a part of the lower end face of the evaporator 614.SELECTED DRAWING: Figure 6

Description

Technical Field

[0001] The present invention relates to a dryer including a washing dryer having a drying function by a heat pump device.

Background Art

[0002] Patent Document 1 describes a clothes dryer provided with a drain tank for receiving drain water generated by dehumidification at the bottom of a heat pump duct (paragraph 0018). The drain tank is configured as a shallow-bottom rectangular container with an open top, sized to receive the entire area below the evaporator and condenser, and a tank rib is integrally provided to partition the inside thereof in the front-rear direction. The tank rib is disposed at a position shifted toward the condenser side from the position between the evaporator and the condenser, and is partially open so that drain water can flow through the front and rear in the drain tank (paragraphs 0046 and FIG. 6). A tank cover is provided on the drain tank so as to close its top surface, and a cover rib located between the evaporator and the condenser is provided on the tank cover (paragraph 0047). If wind blows in from the evaporator side and causes drain water to be lifted into the drain tank, the drain water will hit the wall surface of the tank rib and try to bounce up. The tank rib is provided at a position shifted toward the condenser side, and the drain water that hits the wall surface of the tank rib and bounces up hits the lower surface of the tank cover at the lower part of the condenser and flows down. Therefore, the drain water does not flow in the direction of the condenser, that is, toward the circulation air duct side. As a result, in a device equipped with a heat pump, even if the drying air volume is increased, it is possible to obtain an effect of suppressing the drain water in the drain tank from being lifted up (paragraph 0048).

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] In Patent Document 1, the tank cover is provided at a position covering the lower part of the condenser and is not provided below the evaporator. Therefore, a short path is formed that returns to the circulation air passage between the evaporator and the condenser through the lower part of the evaporator, and there is a possibility that the amount of air that circulates without passing through the evaporator and being dehumidified increases.

[0005] An object of the present invention is to provide a dryer that can increase the amount of circulating air passing through the evaporator and improve the dehumidification performance of the circulating air.

Means for Solving the Problems

[0006] In order to solve the above problems, the dryer of the present invention comprises a heat pump device having a condenser, an evaporator, and a drain tank disposed below the evaporator and the condenser, and in the dryer in which the evaporator and the condenser are arranged in this order from the upstream side of the air passage of the circulating air, the heat pump device includes a baffle that covers at least a part of the lower end surface of the evaporator.

Effects of the Invention

[0007] According to the present invention, by covering at least a part of the lower surface of the evaporator with a baffle plate, it is possible to suppress the formation of a short path on the lower surface of the evaporator, increase the amount of circulating air passing through the evaporator, and improve the dehumidification performance of the circulating air.

Brief Description of the Drawings

[0008]

Figure 1

Figure 2

Figure 3

Figure 4

Figure 5

Figure 6

Figure 7

Figure 8

Figure 9

Figure 10

Figure 11

Figure 12

Mode for Carrying Out the Invention

[0009] The washing and drying machine of this embodiment performs washing to drying in one rotating tub. The drum-type washing and drying machine performs a series of steps of washing, rinsing, dehydrating, and drying by the rotation of a drum rotatably installed around an axis arranged horizontally or slightly inclined horizontally.

[0010] As heat sources during the drying operation, a drying method using a heat pump device and a drying method using a heater are used. In order to dry clothes containing moisture, it is necessary to perform a drying cycle in which air with high humidity is removed from the drum, dehumidified and heated, and circulated into the drum.

[0011] A washing and drying machine using a heat pump device includes a refrigeration cycle in which a compressor, a heat exchanger (condenser) for heating circulating air, a decompression means, and a heat exchanger (evaporator) for dehumidifying circulating air are sequentially connected by pipes, a circulation air passage in which the evaporator and the condenser are arranged, and a blower device for circulating drying air.

[0012] In the refrigeration cycle, the refrigerant compressed to a high temperature and high pressure by the compressor is sent to a heat exchanger (condenser) for heating to heat the air, and the air is dehumidified by a heat exchanger (evaporator) for dehumidification. The refrigerant that has become low temperature and low pressure is circulated to the compressor and compressed again, repeating the cycle. The blower device dehumidifies the moist air taken from the clothes in the drum by the evaporator, heats it by the condenser, and blows it into the drum again as low-humidity air to dry the clothes.

[0013] The condensed water dehumidified from the high-humidity air by the evaporator flows down from the evaporator and is stored in a water receiving part (drain tank) arranged below the evaporator, and is discharged outside the machine by a pump.

[0014] In a washing and drying machine using a heat pump device, in order to improve the drying performance or shorten the drying operation time, an operation of increasing the circulating air volume is performed. During such an operation, the amount of condensed water on the surface of the evaporator increases, and the water level in the drain tank rises due to the flowing-down condensed water.

[0015] In addition, the wind speed in front of the heat exchanger increases, and a part of the circulating air flows into the drain tank, causing a phenomenon of lifting the condensed water to the condenser side. The condensed water that has moved to the condenser side vaporizes on the surface of the condenser, humidifying the circulating air, which may reduce the drying performance.

[0016] According to the present embodiment, by bringing a part of the lower surface of the heat exchanger into contact with the baffle, it is possible to prevent the flow of circulating air (short path) passing through the gap between the heat exchanger and the wall surface, suppress the lifting of the condensed water by the circulating air passing through the short path, and obtain an effect of drawing the condensed water on the surface of the heat exchanger into the drain tank, thereby improving the drainage performance.

[0017] By providing a space below the baffle, the flow from the water receiving part in front of the contact part to the heat exchanger can be suppressed, and by preventing the entrainment of condensed water, a decrease in drying performance can be suppressed.

[0018] In addition, since the air volume during the drying operation can be ensured, it is possible to provide a washing and drying machine that achieves both power consumption reduction and improvement in drying performance by improving the dehumidification performance.

[0019] With reference to FIGS. 1 to 3, the structure and operation of a washing and drying machine 100 according to an embodiment of the present invention will be described. FIG. 1 is a perspective view showing the appearance of the washing and drying machine 100. The washing and drying machine 100 is a drum-type washing and drying machine. On the upper part of a base (stand) 1a, side plates 1b mainly made of steel plates and resin molded products and a reinforcing material (not shown) are combined to form a skeleton, and further, a front cover 1c and an upper cover 1d are attached thereto to form a housing 1. A door 1e for loading and unloading laundry is provided on the front cover 1c. On the upper front part of the upper cover 1d, a power switch, buttons for selecting an operation course, and a display 1f are provided. Also, on the upper cover 1d, a lid 1g for a storage part of a detergent box and a softener box is provided.

[0020] Note that the washing and drying machine 100 according to the present invention is not limited to a drum-type washing and drying machine, and may be a washing and drying machine equipped with a heat pump unit or a vertical washing and drying machine.

[0021] With reference to FIG. 2, the configuration related to the outer tub 2 and the rotating drum 3 will be described. FIG. 2 is a central cross-sectional view of the washing and drying machine 100 shown in FIG. 1. Note that FIG. 2 shows the state of the washing and drying machine 100 as viewed from the left side.

[0022] Inside the housing 1, an outer tub 2 and a rotary drum (inner tub) 3 are provided, and the outer tub 2 and the rotary drum 3 are enclosed by the housing 1. The outer tub 2 is supported from below by a plurality of suspensions (not shown) and is suspended at the upper part by a spring (not shown). The rotary drum 3 is disposed inside the outer tub 2, and the door 1e is opened to load the laundry 200. Further, the rotary drum 3 is directly connected to a drum driving motor 4 via a main shaft 3d connected to a metal flange 3c for the rotary drum. A drainage device 5 including a drainage path is provided at the lower part of the outer tub 2.

[0023] Next, the configuration and operation of the heat pump device 610 will be described. FIG. 3 is a rear view showing the internal structure of the washing and drying machine 100 shown in FIG. 1. In FIG. 3, the configuration of the refrigerant circuit and the circulation air path of the heat pump device 610 is shown.

[0024] The heat pump device 610 includes a compressor 611, a heat exchanger for heat dissipation to air (condenser) 612, a pressure reducing device (expansion valve or the like) 613, a heat exchanger for dehumidifying air (evaporator) 614, and a refrigerant pipe 616 connecting these devices. The refrigerant circuit formed by sequentially connecting the devices 611 to 614 is housed in a resin casing 618. The refrigerant flows in the direction of the arrow indicated by R1 in the figure, in the order of the compressor 611, the condenser 612, the pressure reducing device 613, and the evaporator 614, and returns to the compressor.

[0025] The evaporator 614 and the condenser 612 of the present embodiment are configured by a cross fin tube type heat exchanger, but are not limited thereto. The cross fin tube type heat exchanger is attached such that a heat transfer tube penetrates through laminated aluminum fins to perform heat exchange with air.

[0026] The compressor 611 is installed on the base 1a via an anti-vibration rubber or the like. The refrigerant pipe 616 is connected to each of the condenser 612 and the evaporator 614 in a meandering state in order to prevent breakage due to the propagation of the rotational vibration of the compressor 611.

[0027] The compressor 611 is a controllable compressor, and for example, compressors such as piston type, rotary type, scroll type, etc. can be used. The rotation speed of the compressor 611 is variable from low speed to high speed by inverter control.

[0028] Also, when the refrigerant returns to the compressor in the liquid phase, it may reduce the reliability due to poor lubrication on the sliding surface of the compressor. To prevent this, it is advisable to provide an accumulator on the suction side of the refrigerant.

[0029] The high-temperature and high-pressure gas refrigerant discharged from the compressor 611 flows into the condenser 612, condenses and liquefies by releasing heat to the circulating air. The liquefied refrigerant is depressurized by an expansion valve (pressure reducing device) 613 adjusted to a predetermined opening degree, becomes a low-temperature and low-pressure gas-liquid two-phase state, and flows into the evaporator 614. Then it evaporates and vaporizes by absorbing heat from the circulating air. The vaporized refrigerant is sucked into the compressor 611 and is compressed again by the compressor 611 to become a high-temperature and high-pressure gas refrigerant. In this way, the refrigeration cycle in the heat pump device 610 is formed.

[0030] As the refrigerant enclosed in the refrigerant circuit, for example, HFC single refrigerant, HFC mixed refrigerant, HFO-1234yf, HFO-1234ze, natural refrigerant (for example, CO2 refrigerant), etc. can be used.

[0031] In this embodiment, the heat pump device 610 is installed on the base 1a behind the housing 1 of the washing and drying machine 100 and at the lower part of the outer tank 2. The circulating air is discharged from the rotary drum (inner tank) 3 through the discharge port 15 (see FIG. 2), and after passing through a filter (not shown), it flows from the upper part to the lower part of the outer tank 2 via the return flow path 662 and flows into the heat pump device 610. The arrangement of the heat pump device 610 is not limited to the configuration of this embodiment.

[0032] In the heat pump device 610, the dehumidified and heated circulating air flows from the lower part to the upper part of the outer tank 2 via the air supply passage 661 of the circulating air by the blower device 630 connected to the circulating air passage downstream of the heat exchanger, and is blown into the rotary drum 3 from a blowout port (not shown) provided at the upper front part of the outer tank 2.

[0033] The evaporator 614 dehumidifies the high-humidity air evaporated from the clothes 200 in the rotary drum 3, and the condenser 612 dissipates the heat amount absorbed by the evaporator 614 and the heat amount of the compressor 611 to the circulating air. Generally, in the fin-tube type heat exchanger, the heat transfer area is increased by raising slits on the surface of the laminated aluminum fins, processing folds, reducing the fin pitch, etc., and the heat transfer performance is improved by the leading-edge effect on the air flow. Further, the surface of the aluminum fins is subjected to surface treatment such as hydrophilic treatment so that the moisture condensed on the fin surface can easily flow down.

[0034] During the drying operation, since the evaporator 614 is controlled to be below the dew point temperature of the circulating air, moisture in the circulating air condenses and adheres to the surface of the fins constituting the evaporator 614.

[0035] If this condensed dehumidified water does not flow down to the lower part of the evaporator 614 and is held between the slits of the fins or between the fins, that is, if the water drainage property is poor, it becomes a ventilation resistance to the circulating air and increases the power of the blower device. Further, the water film becomes a heat resistance, causing a performance degradation due to the inability to obtain a predetermined heat exchange amount. Furthermore, since the pressure loss in the air passage increases, the air volume decreases and the drying time becomes longer, increasing the power consumption.

[0036] Here, the ventilation resistance is obtained by providing pressure gauges before and after the heat exchanger (evaporator 614 and condenser 612) and measuring the pressure difference of the air passing through the heat exchanger (evaporator 614, condenser 612).

[0037] In the washing and drying machine 100 using the heat pump device 610, in order to enhance the drying performance or shorten the drying operation time, an operation is performed to increase the circulating air volume. During such an operation, the amount of dew condensation on the surface of the evaporator 614 increases, and the water level in the drain tank rises due to the flowing-down dew condensation water.

[0038] Furthermore, the wind speed in front of the heat exchanger increases, and a part of the circulating air flows into the drain tank below the evaporator 614, resulting in a phenomenon of lifting the dew condensation water toward the condenser 612 side. The dew condensation water that has moved to the condenser 612 side vaporizes on the surface of the condenser 612, which may humidify the circulating air and cause concern about reducing the drying performance. To prevent the lifting of the dew condensation water in the drain tank below the evaporator 614, a baffle (baffle plate) is provided below the evaporator 614.

[0039] With reference to FIGS. 4 and 5, the structure of the heat pump device 610 will be described. FIG. 4 is a perspective view showing the appearance of the heat pump device 610 according to an embodiment of the present invention. FIG. 5 is a perspective view with the upper casing 618b of the heat pump unit 610 removed. The X direction, Y direction, and Z direction are defined as shown in FIG. 5. The X direction is the length direction of the heat exchangers 612 and 614. The Y direction is the depth direction of the heat exchangers 612 and 614. The Z direction is the height direction of the heat exchangers 612 and 614.

[0040] As shown in FIG. 4, the heat pump device (heat pump unit) 610 includes a resin casing 618, and inside the casing 618, a compressor 611, a condenser (heater) 612, an expansion valve (pressure reducing mechanism) 613, an evaporator (dehumidifier) 614, and an accumulator 615 are provided. The casing 618 is separable into a lower casing 618a and an upper casing 618b, and both are fixed by resin claws or screws. In this embodiment, the blower device 630 is integrated with the casing 618 of the heat pump device 610, and the blower device 630 can also be regarded as a part of the heat pump unit 610.

[0041] As shown in FIG. 5, the heat exchangers (heat exchange sections) 614 and 612 are installed so as to be sandwiched between the upper casing 618b and the lower casing 618a, and are disposed in the circulation air passage 664 for drying air. End plates 619a and 619b are provided at both ends of the heat exchangers 614 and 612 in the X direction so as to inhibit the air flowing on the sides of the heat exchangers 614 and 612. The circulation air passage 664 is a circulation air passage in the heat pump unit. The circulation air passage 664 is divided into an upstream air passage 664a disposed upstream of the heat exchangers 614 and 612, a downstream air passage 664b disposed downstream of the heat exchangers 614 and 612, and an inter-heat-exchanger air passage 664c disposed between the evaporator 614 and the condenser 612.

[0042] The drying air flows through the circulation air passage 664 in the heat pump unit from the upstream air passage 664a to the downstream air passage 664b as shown by the white arrows in FIG. 5. The drying air in the downstream air passage 664b is sucked into the blower 630 and discharged from the discharge port 630a of the blower 630.

[0043] As described above, a cross fin tube type heat exchanger in which a circular heat transfer tube penetrates through aluminum fins laminated at a predetermined pitch and is attached by flaring is used for the condenser 612 and the evaporator 614.

[0044] A drain tank is provided below the evaporator 614 for discharging the condensed water that has flowed down. By periodically operating a condensate pump (not shown) or operating the condensate pump by detecting the water level, the condensed water is drained outside the washing dryer 100.

[0045] With reference to FIGS. 6 to 8, the circulation air passage 664 of the heat pump device 610 according to an embodiment of the present invention will be described. FIG. 6 is a schematic diagram showing a cross section of the heat pump device 610 according to an embodiment of the present invention. FIG. 7 is a cross-sectional view schematically showing a first modification of the heat pump device 610 shown in FIG. 6. FIG. 8 is a cross-sectional view schematically showing a second modification of the heat pump device 610 shown in FIG. 6.

[0046] As shown in FIG. 6, the circulation air passage 664 of the heat pump device 610 is configured, from the upstream side, in the order of the upstream side air passage 664a, the inter-heat exchanger air passage 664c, and the downstream side air passage 664b, and is connected to the blower device 630.

[0047] The lower casing 618a forms a space 204 serving as a drain tank at the lower part of the heat exchangers (evaporator 612 and condenser 614). The drain tank 204 has a water receiving part 204C formed below the condenser 614 and a water receiving part 204E formed below the evaporator 612. A rib 206A is provided on the upstream side of the water receiving part 204E, and a rib 206E is arranged between the water receiving part 204E and the water receiving part 204C so as to partition the two 204E and 204C. The bottom surface (the bottom surfaces of the water receiving part 204E and the water receiving part 204C) 204F of the drain tank 204 has a structure inclined so as to have a downward gradient from the downstream side to the upstream side of the circulation air passage 664. That is, the bottom surface of the water receiving part 204C is located above the bottom surface of the water receiving part 204E. For this reason, the condensed water has a structure in which it easily gathers from the water receiving part 204C side toward the water receiving part 204E side.

[0048] During the drying operation, most of the circulated air flowing into the upstream side air passage 664a flows to the evaporator 614. At this time, the evaporator 614 is controlled to be below the dew point temperature of the circulated air, and dehumidifies moisture from the highly humid air evaporated from the clothing WA (see FIG. 2) in the rotary drum 3. Moisture in the circulated air condenses on the surface of the fins constituting the evaporator 614 and flows down toward the lower end of the evaporator 614, and flows down into the water receiving part 204E below the evaporator 614. The condensed water flowing into the water receiving part 204E is drained outside the washing and drying machine 100 by a condensed water pump (not shown).

[0049] Part of the circulated air flowing into the upstream air passage 664a flows into the water receiving portion 204E through the gap S1 between the rib 206A and the upstream end face (front face) 614a of the evaporator 614, causing a phenomenon (water splashing) of lifting the condensed water toward the condenser 612. To deal with this water splashing, to some extent, it can be addressed by raising the rib 206A on the upstream side of the evaporator 614 and the rib 206E on the downstream side to suppress the air flow in the gaps S1 and S2. However, on the upstream end faces (front faces) 614a and 612a of the evaporator 614 and the condenser 612, the area (upstream area) in contact with the circulated air will be reduced. The gap S2 is a gap formed between the downstream end face (rear face) 614b of the evaporator 612 and the rib 206E in the Y direction.

[0050] To suppress such water splashing, in the embodiment shown in FIG. 6, a baffle (baffle plate) 205E is provided on the rib 206E so as to cover at least a part of the lower end face of the evaporator 614. Also, on the condenser 612 side, a baffle 205C is provided so as to cover at least a part of the lower end face of the condenser 612. The baffle 205E is disposed at the opening of the water receiving portion 204E at a position covering at least the lower end portion of the downstream end face 614b of the evaporator 614. At this time, the baffle 205E is provided in a range overlapping at least a part of the gap S2 and the lower end face of the evaporator 614 in the Y direction. The baffle (baffle plate) 205C is disposed at the opening of the water receiving portion 204E at a position covering at least the lower end portion of the downstream end face (rear face) 612b of the condenser 612.

[0051] By providing the baffle 205E on the downstream side of the evaporator 614, it is possible to suppress water splashing from the evaporator 614 to the condenser 612 without raising the rib 206E.

[0052] Also, the baffle 205C on the downstream side of the condenser 612 is provided to suppress water splashing to the blower device 630. Since there is a space between the baffle 205C and the bottom surface of the water receiver 204C, it is possible to secure the volume at the lower part of the heat exchanger and reduce the rising speed of the liquid level.

[0053] In the first modification example shown in FIG. 7, the form of the baffle 205E is changed with respect to the embodiment of FIG. 6. The baffle (baffle plate) 205E is provided on the rib 206E so as to cover at least a part of the lower end surface of the evaporator 614 and the heat exchanger intermediate air passage 664c between the evaporator 614 and the condenser 612. Other configurations are the same as those of the embodiment of FIG. 6.

[0054] The baffle 205E is disposed at the opening of the water receiving portion 204E at a position covering at least the lower end portion of the downstream end surface (rear surface) 614b of the evaporator 614. At this time, the baffle 205E is provided in a range overlapping at least a part of the lower end surface of the gap S2 and the evaporator 614 in the Y direction. The baffle 205E is also disposed at the opening of the water receiving portion 204C at a position covering at least the lower end portion of the upstream end surface (front surface) 612a of the condenser 612. At this time, the baffle 205E is provided in a range overlapping at least a part of the lower end surface of the gap S3 and the evaporator 614 in the Y direction. The gap S3 is a gap formed between the upstream end surface 612a of the condenser 612 and the rib 206E in the Y direction.

[0055] The baffle 205E is expected to suppress the entrainment of condensed water and to suppress the formation of a short path of the circulating air from the evaporator 614 to the condenser 612. Further, the rib 206E can be made lower, and it becomes possible to secure an area in contact with the circulating air on the front surface 612a of the condenser 612. In this example, the upper end of the rib 206E is at a position lower than the lower end surface of the evaporator 614.

[0056] In the second modification example shown in FIG. 8, a baffle (baffle plate) 205F is added with respect to the embodiment of FIG. 6. The baffle 205F is provided on the rib 206A so as to cover at least a part of the lower end surface of the evaporator 614. In this example, the height of the rib 206E is made lower than that of the configuration of FIG. 6, and the upper end of the rib 206E is at a position lower than the lower end surface of the evaporator 614. The height of the rib 206E in this example can be applied to the embodiment of FIG. 6 and the first modification example of FIG. 7. Other configurations are the same as those of the embodiment of FIG. 6.

[0057] The baffle 205F is disposed at the opening of the water receiving portion 204E at a position covering at least the lower end portion of the upstream end face 614a of the evaporator 614 with little gap. At this time, the baffle 205F is provided in a range that overlaps at least a part of the gap S1 and the lower end face of the evaporator 614 in the Y direction.

[0058] The baffle 205F upstream of the evaporator 614 suppresses the inflow of the circulating air to the lower part of the evaporator 614 and suppresses the entrainment of the condensed water. Further, the baffle 205F enables securing of the area that contacts the circulating air on the front face 614a of the evaporator 614.

[0059] In FIGS. 6 to 8, the rib 206E and the baffle 205E, and the rib 206A and the baffle 205F are shown separately, but a structure in which the rib and the baffle are integrated may also be used. Further, the baffles 205C, 205E, 205F may have a structure integrated with the end plates 619a, 619b.

[0060] Referring to FIG. 9, the baffle 205 according to an embodiment of the present invention will be described. FIG. 9 is a schematic diagram showing the structure of the baffle 205 according to an embodiment of the present invention. FIG. 9 schematically shows the configuration of the evaporator 614 and the baffle 205 as viewed from the Y direction (the depth direction of the heat exchanger) of FIG. 4.

[0061] The heat exchanger (evaporator 614) performs heat exchange with the drying air (circulating air), and a cross fin tube type heat exchanger in which a circular heat transfer tube penetrates through aluminum fins laminated at a predetermined pitch and is attached by expanding the tube is used. End plates 619b and 619a are attached to both ends in the length direction (X direction) of the heat exchanger (evaporator) 614. As shown in FIG. 5, the heat exchangers 614 and 612 are installed so as to be sandwiched between the upper casing 618b and the lower casing 618a so as to impede the air flowing laterally, and are disposed in the circulation air passage 664 for the drying air.

[0062] The above aluminum fins increase the heat transfer area by processes such as slitting or raising, or by increasing the number of fins, aiming to improve performance. However, in the evaporator 614, in order to dehumidify the highly humid circulating air, the condensed water on the fin surface may be retained between the fins, in the slits, or between the louvers, which may impede the flow of the circulating air. Furthermore, under the operating conditions where the circulating air volume is increased to improve the drying performance, there is a concern that the condensed water may move to the condenser 612 side before flowing down to the water receiver 204E at the lower part of the evaporator 614, resulting in a decrease in the drying performance. To suppress the above phenomena, in this embodiment, a baffle 205 having a water guiding structure is arranged to quickly discharge the condensed water.

[0063] Note that the configuration related to the baffle 205 to be described hereinafter can be applied to the above-described baffles 205C, 205E, and 205F. Hereinafter, the evaporator 614 will be described. The condenser 612 is also configured in the same manner as the evaporator 614 as a heat exchanger.

[0064] In the form shown in Fig. 9(a), the baffle 205 is inclined so as to have a downward gradient from one end to the other end in the length direction (X direction). Therefore, the distance between the baffle 205 and the lower end surface of the evaporator 614 is small at one end in the length direction (X direction) and large at the other end. That is, the baffle 205 is configured such that the distance between the baffle 205 and the lower end surface of the evaporator 614 increases from one end to the other end in the length direction (X direction).

[0065] Specifically, in the vicinity of the end plate 619b, the gap between the lower end surface of the evaporator 614 and the baffle 205 is narrow, while in the vicinity of the end plate 619a, the gap between the lower end surface of the evaporator 614 and the baffle 205 is widened. In the region where the gap between the lower end surface of the evaporator 614 and the baffle 205 is narrow, the condensed water easily moves from the lower end of the evaporator 614 to the baffle 205. The condensed water is held between the baffle 205 and the evaporator 614 by surface tension, but when it exceeds a certain amount, it flows down the inclined surface of the baffle 205 due to gravity. The condensed water that has flowed down the inclined surface of the baffle 205 is discharged from the discharge port 207 provided at the other end of the baffle 205 in the longitudinal direction to the water receiving portion 204E of the drain tank 204. Thus, in this example, the inclination of the baffle 205 promotes the discharge of the condensed water from the evaporator 614.

[0066] In the form shown in FIG. 9(b), a plurality of openings 208 are provided in the baffle 205. By providing the openings 208 in the baffle 205, it becomes possible to draw the condensed water flowing down the lower end surface of the evaporator 614 into the openings 208 and move it to the water receiving portion 204E. Examples of the baffle 205 having the openings 208 include a mesh-like plate member, a perforated plate, etc., but are not limited thereto.

[0067] In the form shown in FIG. 9(c), the baffle 205 has a corrugated plate structure. By alternately having regions where the gap between the lower end surface of the evaporator 614 and the baffle 205 is narrow and wide, an effect of promoting the discharge of the condensed water is obtained.

[0068] In the form shown in FIG. 9(d), a water guiding structure (water guiding member) 209 separate from the baffle 205 is provided between the baffle 205 and the lower end surface of the evaporator 614 and the baffle 205. The water guiding structure 209 alternately forms regions where the gap with the lower end surface of the evaporator 614 is narrow and wide. The condensed water moves from the lower end surface of the evaporator 614 to the baffle 205 through the water guiding structure 9 and flows down to the water receiving portion 204E. By having the structure as described above, it becomes possible to promote the discharge of the condensed water held between the fins of the evaporator 614.

[0069] The baffles 205 in FIGS. 9(a), 9(c), and 9(d) are arranged in a state that makes it easy for the condensed water to flow down by gravity with respect to the lower end surface of the evaporator 614.

[0070] As described above, the baffle 205 in FIGS. 9(a) to 9(d) may have a structure integrated with the ribs 206E and 206A. Alternatively, the baffle 205 may have a structure integrated with at least one of the end plates 619a and 619b. Thereby, the production of the baffle 205 becomes easy, and the assembly man-hours can also be reduced.

[0071] Referring to FIG. 10, the configuration of the rib 206 according to an embodiment of the present invention will be described. FIG. 10 is a schematic diagram showing the structure in the vicinity of the water receiving portions 204C and 204E according to an embodiment of the present invention. The white arrows in the figure indicate the flow direction of the circulating air. End plates 619a (see FIG. 5) and 619b are provided at both ends in the longitudinal direction of the evaporator 614 and the condenser 612, and by arranging the upper casing 618b (see FIG. 4), leakage of drying air from the circulating air passage is suppressed.

[0072] The rib 206E is arranged so as to partition the spaces 204C and 204E below the heat exchangers 614 and 612, and a baffle 205E is arranged so as to cover a part of the downstream side of the lower end surface of the evaporator 614. Further, a reflux hole (opening) 210 is provided near the lower end portion of the rib 206E (near the bottom surface 204F).

[0073] The condensed water generated in the evaporator 614 is stored in the water receiving portion 204E and discharged outside the machine by a drainage pump (not shown). By providing an opening in the rib 206E, it becomes possible to move the condensed water that has moved to the water receiving portion 204C below the condenser 612 to the water receiving portion 204E.

[0074] Here, the rib 206E may have a structure integrated with the lower casing 618a, or a structure integrated with at least one of the end plates 619a and 619b.

[0075] Referring to FIG. 11, the configuration of the drain tanks 204C and 204E according to an embodiment of the present invention will be described. FIG. 11 is a schematic diagram showing the structure in the vicinity of the water receiving portions 204C and 204E according to an embodiment of the present invention. It schematically shows the cross section XI-XI of FIG. 4. The white arrows in the figure indicate the flow direction of the circulating air.

[0076] The rib 206E is arranged so as to partition the spaces 204C and 204E below the heat exchangers 614 and 612, and a baffle 205E is arranged so as to cover a part on the downstream side of the lower end surface of the evaporator 614. Further, a reflux hole (opening) 210 is provided near the lower end portion of the rib 206E (near the bottom surface 204F).

[0077] The bottoms 204F of the water receiving portions 204C and 204E are inclined so as to be lower toward the upstream side of the circulating air, and a step 618d is formed near the rib 206E. By inclining the bottom of the water receiving portion 204C, the condensed water staying in the water receiving portion 204C can be easily returned to the water receiving portion 204E. The condensed water flowing down the bottom of the water receiving portion 204C is stored in the space between the step 618d and the rib 206E, and the condensed water can be moved to the water receiving portion 204E while keeping the space between the water receiving portion 204C and the water receiving portion 204E sealed.

[0078] Here, the rib 206E may have a structure integrated with the lower casing 618a, or may be attached to or integrated with the end plates 619b or 619a. Thereby, the production of the rib 206E and the baffle 205E becomes easy, and the number of assembly steps can also be reduced.

[0079] Referring to FIG. 12, the arrangement of the heat exchangers 614 and 612 according to an embodiment of the present invention will be described. FIG. 12 is a schematic diagram showing a cross section (the same cross section as FIG. 11) in the vicinity of the heat exchangers 614 and 612 according to an embodiment of the present invention. The white arrows in the figure indicate the flow direction of the circulating air.

[0080] As in this example, the evaporator 614 may have an inclined configuration such that, in the flow direction (Y direction) of the circulating air, the upper part of the evaporator 614 approaches the condenser 612 and the lower part of the evaporator 614 moves away from the condenser 612.

[0081] By tilting the evaporator 614, the water droplets that have gathered at the ends of the slits formed on the fin surface of the evaporator 614 or at the lower ends of the heat transfer tubes can easily flow down, and the effect of suppressing water splashing onto the condenser 612 can be improved. Further, by increasing the distance between the lower part of the evaporator 614 and the lower part of the condenser 612 in the circulation air passage 664c, it is possible to suppress the direct movement of the condensed water from the evaporator 614 to the condenser 612.

[0082] In the embodiments and modified examples according to the present invention described above, it is preferable to reduce the distance in the Z direction between the lower end surface of the evaporator 614 and the baffle 205E or the baffle 205F (see FIG. 8). Thereby, it is possible to reduce the circulating air that short - circuits the evaporator by flowing through the gap in the Z direction between the lower end surface of the evaporator 614 and the baffle 205E or the baffle 205F. In particular, by bringing the lower end surface of the evaporator 614 into contact with the baffle 205E or the baffle 205F, the effect of reducing the circulating air that short - circuits the evaporator is enhanced.

[0083] Also, it is preferable to reduce the distance in the Z direction between the lower end surface of the condenser 612 and the baffle 205C or the baffle 205E (see FIG. 7). Thereby, it is possible to reduce the circulating air that short - circuits the condenser by flowing through the gap in the Z direction between the lower end surface of the condenser 612 and the baffle 205C or the baffle 205E. In particular, by bringing the lower end surface of the condenser 612 into contact with the baffle 205E or the baffle 205C, the effect of reducing the circulating air that short - circuits the condenser is enhanced.

[0084] The embodiments and modified examples according to the present invention described above have the following features. (1) The dryer 100 includes a heat pump device 610 having a condenser 612, an evaporator 614, and drain tanks 204C and 204E disposed below the evaporator 614 and the condenser 612. In the dryer 100, the evaporator 614 and the condenser 612 are arranged in the order of the evaporator 614 and the condenser 612 from the upstream side of the air duct of the circulating air. The heat pump device 610 includes a baffle 205E that covers at least a part of the lower end surface of the evaporator 614.

[0085] (2) The heat pump device 610 includes a baffle 205C that covers at least a part of the lower end surface of the condenser 612.

[0086] (3) The baffle 205E is disposed at a position that covers at least the lower end portion of the downstream end surface 614b of the evaporator 614.

[0087] (4) A dryer characterized in that a water guiding structure 209 is disposed between the lower end surface of the evaporator 614 and the baffle 205E.

[0088] (5) The baffle 205E is inclined so as to have a downward gradient from one end portion to the other end portion in the longitudinal direction of the evaporator 614, and a drain outlet 207 for condensed water is provided at the other end portion of the baffle 205E.

[0089] (6) The baffles 205 and 205E have a plurality of openings 208.

[0090] (7) The baffles 205 and 205E have a corrugated plate structure.

[0091] (8) The baffles 205 and 205E alternately form regions with a narrow gap and a wide gap with the lower end surface of the evaporator 614.

[0092] (9) The baffles 205 and 205E are attached to end plates 619a and 619b disposed at both end portions of the evaporator 614 and the condenser 612 in the longitudinal direction of the evaporator 614.

[0093] (10) The evaporator 614 is disposed obliquely such that the upper part of the evaporator 614 approaches the condenser 612 and the lower part of the evaporator 614 moves away from the condenser 612 in the flow direction (Y direction) of the circulating air.

[0094] In the above embodiment, the drum - type washing and drying machine is described as an example of the application device. However, the present invention is also applicable to a vertical washing and drying machine using a heat pump device as a drying method. Further, the present invention is also applicable to a dryer having only a drying function. In this specification, the dryer includes a washing and drying machine.

[0095] Also, in the configuration of the washing and drying machine 100 shown in FIG. 3, the blower device 630 is integrated with the heat pump device 610, but it is not limited thereto. For example, the blower device 630 may be disposed between the air supply duct 661 and the drying air outlet (not shown).

[0096] Also, in the above embodiment, the heat pump device 610 is disposed below the outer tub 2, but it is not limited thereto. For example, the heat pump device 610 may be disposed above the outer tub 2.

[0097] Note that the present invention is not limited to the above - described embodiments, and various modifications are included. For example, the above - described embodiments are described in detail for easy understanding of the present invention and are not necessarily limited to those having all configurations. Also, a part of the configuration of one embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of one embodiment. Further, for a part of the configuration of each embodiment, addition, deletion, or replacement with other configurations is possible.

Explanation of Reference Numerals

[0098] 100... Washing and drying machine (dryer), 204C, 204E... Drain tank, 205, 205C, 205E... Baffle, 207... Dew water discharge port, 208... A plurality of openings provided in the baffles 205, 205E, 209... Water guide structure, 610... Heat pump device, 612... Condenser, 614... Evaporator, 614b... Downstream end face of the evaporator 614, 619a, 619b... End plates.

Claims

1. A dryer comprising a heat pump device having a condenser, an evaporator, and a drain tank disposed below the evaporator and the condenser, wherein the evaporator and the condenser are arranged in the order of the evaporator and the condenser from the upstream side of the air duct of the circulating air. The dryer is characterized in that the heat pump device includes a baffle that covers at least a part of the lower end surface of the evaporator.

2. In the dryer according to Claim 1, The dryer is characterized in that the heat pump device includes a baffle that covers at least a part of the lower end surface of the condenser.

3. In the dryer according to Claim 1, The dryer is characterized in that the baffle is disposed at a position that covers at least the lower end portion of the downstream end surface of the evaporator.

4. In the dryer according to Claim 1, The dryer is characterized in that a water guiding structure is disposed between the lower end surface of the evaporator and the baffle.

5. In the dryer according to Claim 1, The dryer is characterized in that the baffle is inclined so as to have a downward gradient from one end to the other end in the longitudinal direction of the evaporator, and a drain outlet for condensed water is provided at the other end of the baffle.

6. In the dryer according to Claim 1, The dryer is characterized in that the baffle has a plurality of openings.

7. In the dryer according to Claim 1, The dryer is characterized in that the baffle has a corrugated plate structure.

8. In the dryer according to Claim 1, The dryer is characterized in that the baffle alternately forms regions with a narrow gap and a wide gap with the lower end surface of the evaporator.

9. In the dryer according to Claim 1, The dryer is characterized in that the baffle is attached to end plates disposed at both ends of the evaporator and the condenser in the longitudinal direction of the evaporator.

10. In the dryer according to Claim 1, The dryer is characterized in that the evaporator is inclined such that the upper part of the evaporator approaches the condenser and the lower part of the evaporator moves away from the condenser in the direction of the flow of the circulating air.

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