JP2021045331A - Clothes dryer - Google Patents

Abstract

To provide a clothes dryer with a heat pump that ensures a widely dispersed airflow through an overall evaporator to increase heat exchange efficiency.SOLUTION: A clothes dryer according to an embodiment of the present invention includes a circulation air path that is provided so as to communicate an air outlet for discharging air from a water tank and an air inlet for blowing air into the water tank on the outside of the water tank, and a heat pump that is configured by including a compressor, and an evaporator and a condenser that are disposed in the circulation air path, and the circulation air path is configured by including an exhaust air duct extending from the air outlet, and an evaporator inlet duct whose base end side is connected to the exhaust air duct and whose tip side is connected to an inlet of the evaporator, and the inside of the evaporator inlet duct is divided into a plurality of divided-duct paths, and air is incident to each part of the evaporator through each corresponding divided-duct path.SELECTED DRAWING: Figure 2

Description

Embodiments of the present invention relate to a clothes dryer.

Conventionally, as a clothes dryer, a drum-type washer-dryer that employs a heat pump has been known (see, for example, Patent Document 1). The heat pump is configured by connecting a compressor, a condenser, a drawing device, and an evaporator in a closed loop in order by a refrigerant pipe, and the evaporator and the condenser are included in the heat pump duct among the ducts constituting the circulation air passage. Are arranged in order. As a result, the moist air discharged from the drum is dehumidified by passing through the evaporator, and subsequently heated by passing through the condenser so that it becomes hot dry air and is supplied to the drum again. It has become.

Japanese Unexamined Patent Publication No. 2016-214460

By the way, the heat pump duct has a rectangular cross section, and an evaporator having a rectangular block shape as a whole is arranged so as to partition the inside of the duct at a right angle to the air flow direction. In this case, in the circulation air passage, an exhaust duct having a relatively small diameter extending from the exhaust port is connected to the heat pump duct so as to expand the air passage at the tip thereof. As a result, the air discharged from the drum exits the exhaust duct, rapidly spreads into the heat pump duct, and passes through the evaporator. However, in the configuration in which the air passage is expanded in this way, the wind does not hit the entire evaporator uniformly, and the flow of the wind concentrates on a part of the evaporator, and the heat exchange efficiency is sufficient. There was a tendency that it could not be done.

In Patent Document 1, the wind direction plate is used to adjust the direction of the air toward the evaporator. In such a wind direction plate, for example, moist air gathers in the lower part of the duct due to the influence of gravity. It was not always an effective device, such as putting it away.
Therefore, there is provided a clothes dryer provided with a heat pump, which can widely disperse and allow air to pass through the entire evaporator and can improve heat exchange efficiency.

The clothes dryer of the embodiment includes a water tank supported in an outer box via an elastic support mechanism, a drum rotatably supported in the water tank and accommodating clothes, and an exhaust port for discharging air from the water tank. A circulation air passage provided so as to communicate between the air and the air supply port for blowing air into the water tank on the outside of the water tank, and a blower device for circulating the air in the water tank through the circulation air passage. The circulation air passage includes a compressor and a heat pump including an evaporator and a condenser arranged in the circulation air passage, and the circulation air passage has an exhaust duct extending from the exhaust port and a base end side of the exhaust duct. The tip side is configured to include an EVA inlet duct which is connected and arranged at the inlet of the evaporator, and the inside of the EVA inlet duct is divided into a plurality of divided air passages, and each of the divided air passages is provided with respect to the evaporator. Air is incident on each part of the evaporator through the air.

The right side view of the vertical section which shows the 1st Embodiment and shows roughly the internal structure of a washer-dryer. Longitudinal rear view showing the internal configuration of the washer / dryer in a state including the heat pump. External perspective view of the washer / dryer seen from the back side Schematic rear view of the heat pump unit part Top view of the inlet side of the heat pump unit Longitudinal front view of the EVA entrance duct Side view showing the exit part of the EVA entrance duct The second embodiment is shown, and is a vertical sectional front view of the EVA entrance duct. The third embodiment is shown, and the side view which shows the exit part of the EVA entrance duct. It shows the 4th Embodiment, and is the side view which shows the outlet part of the EVA entrance duct. The fifth embodiment is shown, and the side view which shows the exit part of the EVA entrance duct. The sixth embodiment is shown, and the side view which shows the exit part of the EVA entrance duct.

Hereinafter, some embodiments applied to a drum-type washer-dryer equipped with a heat pump and having both a washing function and a drying function will be described with reference to the drawings. In the plurality of embodiments described below, the common parts will be designated by the same reference numerals, and new illustrations and repetitive explanations will be omitted.

(1) First Embodiment First, with reference to FIGS. 1 to 3, the overall configuration of the washer / dryer 1 as the clothes dryer according to the present embodiment will be described. As shown in FIG. 1 and the like, the outer box 2 constituting the main body of the washer / dryer 1 has a substantially rectangular box shape, and the cylindrical water tank 3 is inclined backward in the outer box 2. It is supported via an elastic support mechanism (not shown). In the water tank 3, a cylindrical rotating drum 4 (hereinafter, simply referred to as “drum 4”) as a drum for accommodating clothes to be laundry is rotatably supported. The drum 4 is configured to rotate about an inclined axis extending in the front-rear direction and inclined slightly backward from the horizontal.

As shown in FIG. 1, a large number of holes 4a for water passage and ventilation are formed in the peripheral wall portion and the rear wall portion of the drum 4, and the inner surface of the peripheral wall portion of the drum 4 is used for washing laundry. A plurality of baffles (not shown) are provided. Although not shown in detail, the front portion of the drum 4 is provided with a circular opening through which clothes are taken in and out, and the front portion of the water tank 3 is formed with an inlet 3a connected to the opening. ing. A door 5 for opening and closing the insertion port 3a is provided on the front surface of the outer box 2. An operation panel 6 is provided on the upper portion of the front surface of the outer box 2. Although not shown in detail, the operation panel 6 is provided with a power switch 7 (see FIG. 3), and is provided with a display unit and an operation unit.

As shown in FIGS. 1 and 2, a drum motor 8 made of, for example, an outer rotor type brushless motor constituting a drive mechanism is arranged at the rear portion of the water tank 3. As shown in FIG. 1, the tip of the rotating shaft of the drum motor 8 penetrates the back surface of the water tank 3 and protrudes into the water tank 3, and is connected and fixed to the rear central portion of the drum 4. With such a configuration, the drum 4 is directly rotationally driven by the drum motor 8. In this case, the drum 4 is continuously rotated in the normal rotation direction, that is, in the clockwise direction when viewed from the front in the dehydration stroke. In the washing stroke, rinsing stroke, drying stroke, etc., the drum 4 is repeatedly rotated forward and backward.

Although not shown in detail, a water supply mechanism for supplying water from tap water as a water supply source to the inside of the water tank 3 or the like is provided in the upper part of the outer box 2. This water supply mechanism includes a water supply valve. On the other hand, as shown in FIG. 1, a drainage pipe line 12 is connected to the lower part of the water tank 3, and a drainage valve 13 is provided in the middle of the drainage pipe line 12. When water is supplied into the water tank 3 by the water supply mechanism with the drain valve 13 closed, the water is stored in the water tank 3. At this time, the water level in the water tank 3 is detected by a water level sensor (not shown). As the drain valve 13 is opened, the water stored in the water tank 3 is discharged to the outside of the machine through the drain pipe line 12.

As shown in FIG. 1, the water tank 3 is provided with an exhaust port 17 for discharging the air in the drum 4 at the upper right side portion of the front portion, and in the drum 4 at the upper left side portion of the back portion. An air supply port 18 for supplying dry air is provided. Then, as shown in FIGS. 1 and 2, inside the outer box 2, a warm air supply mechanism 19 for circulating and supplying dry air, that is, warm air to the inside of the drum 4 to execute the drying operation of clothes is provided. ing.

The hot air supply mechanism 19 is located outside the water tank 3 and includes a circulation air passage 20. The inlet of the circulation air passage 20 is connected to the exhaust port 17 of the water tank 3, and the outlet of the circulation air passage 20 is connected to the air supply port 18. The hot air supply mechanism 19 includes a heat pump 15 that dehumidifies and heats the circulating air to generate dry air. At the same time, the blower fan 16 as a blower device that supplies the air discharged from the exhaust port 17 from the air supply port 18 into the water tank 3 and the drum 4 while circulating in the circulation air passage 20 in the direction of arrow A is provided. I have.

Specifically, as shown in FIGS. 1 and 2, the circulation air passage 20 includes an upper exhaust duct 21, a rear exhaust duct 22, an EVA inlet duct 23, a heat pump duct 24, and an air supply duct 25. It has. The exhaust duct is composed of the upper exhaust duct 21 and the rear exhaust duct 22. As shown in FIG. 1, the upper exhaust duct 21 is provided with its base end connected to the exhaust port 17 and extending the upper right side in the outer box 2 rearward, and the rear exhaust duct 21 is provided at the tip thereof. The upper end of 22 is connected. A well-known lint filter 26 for capturing lint from dry air is provided in the middle of the upper exhaust duct 21. As shown in FIG. 3, the lint filter 26 is provided so as to be able to be taken in and out from the upper surface of the main body 2.

Further, as shown in FIG. 3, an exhaust opening for exhausting the internal air from the upper surface of the main body 2 is located in the upper part of the middle part of the upper exhaust duct 21 behind the lint filter 26. A section 9 is provided. Along with this, as shown in FIG. 1, an exhaust damper 10 for opening and closing the exhaust opening 9 is provided. The exhaust damper 10 is opened and closed by a drive mechanism including a motor (not shown) or the like. With this, by opening the exhaust damper 10, a part of the air flowing in the circulation air passage 20 can be discharged to the outside of the outer box 2 from the exhaust opening 9.

As shown in FIG. 2, the rear exhaust duct 22 has a rectangular cross section, extends downward behind the water tank 3, and its tip, that is, the lower end is connected to the base end side of the EVA inlet duct 23. The tip end side of the EVA inlet duct 23 is connected to the right end portion which is the base end portion of the heat pump duct 24. The details of the EVA inlet duct 23 will be described later. The heat pump duct 24 has a rectangular cross section, extends in the rearward portion of the bottom of the outer box 2 in the right-left direction, and the blower fan 16 is provided on the tip end side (right end side in FIG. 2).

The blower fan 16 is configured to include, for example, a centrifugal fan 33 and a fan motor 34 for driving the centrifugal fan 33 in a fan casing 32. The lower end portion, which is the base end portion of the air supply duct 25, is connected to the outlet portion of the fan casing 32. The air supply duct 25 extends upward behind the water tank 3 on the left side in the outer box 2, and the upper end portion, which is the tip end portion thereof, is connected to the air supply port 18. As shown in FIG. 2, in the heat pump duct 24, the evaporator 27 and the condenser 28 constituting the heat pump 15 are arranged in order on the left and right (left and right in FIG. 2).

Further, as partially shown in FIGS. 4 and 5, the heat pump 15 has a compressor 29, a condenser 28, a throttle valve 30 as a depressurizing means, and an evaporator 27, and a refrigerant pipe 31. It is configured by connecting in a closed loop shape. A required amount of refrigerant is sealed inside the heat pump 15 and circulates in the refrigerant pipe 31. At this time, the condenser 28 functions as a heating means for heating the dry air, and the evaporator 27 functions as a dehumidifying means for removing moisture from the dry air. In the present embodiment, the evaporator 27 and the condenser 28 are composed of, for example, a well-known so-called fin tube type heat exchanger in which the refrigerant pipes are arranged in a serpentine shape and heat exchange fins are attached, and as a whole. , It is configured in the shape of a rectangular block that is slightly thin in the direction of air flow.

In this heat pump 15, as shown by the arrow B in the flow of the refrigerant in FIG. 2, the gaseous refrigerant discharged from the compressor 29 by driving the compressor 29 flows into the condenser 28, and the condenser 28 It is condensed by heat exchange in the above to make a liquid refrigerant. The liquid refrigerant flowing out of the condenser 28 is expanded by the throttle valve 30 to form a mist, and the mist-like refrigerant flows into the evaporator 27. Then, in the evaporator 27, the refrigerant is vaporized by heat exchange with the outside air, and the gaseous refrigerant is returned to the compressor 29. Further, a circulation is performed in which the refrigerant is compressed by the compressor 29 and discharged at a high temperature and a high pressure.

By driving the blower fan 16 together with the drive of the heat pump 15, the air in the water tank 3, that is, the drum 4, is moved from the exhaust port 17 to the upper part as shown by the arrow A in FIGS. 1 and 2. It passes through the exhaust duct 21, the rear exhaust duct 22, and the EVA inlet duct 23 in this order to reach the heat pump duct 24. At this time, when the air passes through the upper exhaust duct 21, the lint, that is, lint contained in the air is captured by the lint filter 26 and the like.

Then, the air that has passed through the EVA inlet duct 23 flows through the heat pump duct 24, passes through the evaporator 27 and the condenser 28 in order, then flows into the air supply duct 25, passes through the air supply port 18 and the hole 4a, and is a drum. A cycle of being supplied within 4 is performed. This air circulation removes moisture from the clothes in the water tank 3, that is, the drum 4, and the air containing a large amount of steam is cooled through the evaporator 27 portion in the heat pump duct 24, so that the steam is condensed or It is sublimated and dehumidified, and the dehumidified air is heated by passing through the condenser 28 portion to become dry warm air, which is supplied into the drum 4 again and is used for drying clothes.

Further, as shown in FIG. 2, a plurality of temperature sensors including, for example, a thermistor for detecting the temperature of the refrigerant are provided in the main part of the heat pump 15. That is, a discharge temperature sensor 35 is provided near the discharge port of the compressor 29. A condenser temperature sensor 36 is provided in the condenser 28 portion. An evaporator temperature sensor 37 is provided in the evaporator 27 portion. An inlet temperature sensor 38 is provided near the inlet of the compressor 29.

Further, as shown in FIG. 1, the circulation air passage 20 is also provided with a plurality of temperature sensors for dry air, for example, made of a thermistor, for detecting the temperature of the dry air. Specifically, an air supply port temperature sensor 39 is provided in the vicinity of the air supply port 18, and an exhaust temperature sensor 40 is provided in the rear exhaust duct 22 portion. Then, as shown in FIG. 1, in the outer box 2, for example, a control device 41 mainly composed of a microcomputer and controlling the entire washer / dryer 1 is provided. The control device 41 controls the water supply valve, the drain valve 13, the drum motor 8, the fan motor 34 of the blower fan 16, the compressor 29 of the heat pump 15, the throttle valve 30, and the like.

With the above configuration, the control device 41 controls each mechanism of the washing / drying machine 1 based on the input signal from each sensor and the control program stored in advance according to the operation course set by the user in the operation unit. It controls and automatically executes a washing operation consisting of a washing process, a rinsing process, and a dehydration process, and a drying operation. At this time, the control device 41 drives and controls the compressor 29 of the heat pump 15, the blower fan 16, and the like based on the detected temperatures of the temperature sensors 35 to 40, and rotates the drum 4 to dry the product. Perform driving.

The EVA inlet duct 23 in the present embodiment will be described with reference to FIGS. 5 to 7. The EVA inlet duct 23 has a quadrangular cross section, and as shown in FIGS. 4 to 6, the lower end portion which is the tip end portion of the rear exhaust duct 22 and the base end portion of the heat pump duct 24. It is provided so as to extend diagonally so as to connect with the right end. As shown in FIG. 6, the rear exhaust duct 22 is connected to the horizontal upper surface portion which is the base end portion, and the left end portion in the figure which is the tip end portion is a substantially vertical surface and is connected to the inlet portion of the heat pump duct 24. It is connected. At this time, since the cross-sectional area of the rear exhaust duct 22 is relatively small and the cross-sectional area of the heat pump duct 24 is relatively large, the EVA inlet duct 23 is provided so that the air passage expands from the base end portion to the tip end portion. Has been done.

As shown in FIGS. 4 and 5, the evaporator 27 is arranged at the right end of the heat pump duct 24 so that the tip of the evaporator inlet duct 23 directly faces the inlet of the evaporator 27. Have been placed. Then, as shown in FIG. 6, the inside of the EVA inlet duct 23 is divided into a plurality of divided air passages 23a to 23c, and the evaporator 27 is passed through the divided air passages 23a to 23c to the evaporator 27. It is configured so that air is incident on each part. In the present embodiment, as shown in FIG. 7, two partition walls 42 and 43 are provided in the EVA inlet duct 23 so as to extend substantially parallel to the air passage, and the tip side of the EVA inlet duct 23 is provided. Three divided air passages 23a to 23c are provided side by side in the vertical direction.

At this time, as shown in FIG. 6, the two partition walls 42 and 43 are provided so that the positions of the base end portions are deviated in the wind flow direction. In this case, the upper partition wall 42 is located at a position where its base end is closer to the upper surface opening which is the base end of the EVA inlet duct 23, and the lower partition wall 43 has its base end closer to it. It is located on the lower side. As a result, the inlet opening areas a, b, and c of the divided air passages 23a, 23b, and 23c are made uneven. Specifically, the inlet opening area a of the upper split air passage 23a is the largest, the inlet opening area b of the middle split air passage 23b is slightly smaller than that, and the inlet opening area c of the lower split air passage 23c is further increased. It is configured small. On the other hand, as shown in FIG. 7, the outlet opening areas d of the divided air passages 23a to 23c at the tip of the EVA inlet duct 23 are equal.

According to the washer / dryer 1 having the above configuration, the following actions and effects can be obtained. That is, in the washer / dryer 1, for example, when the washing operation for washing the clothes in the drum 4 is completed, the drying operation is continuously started. In this drying operation, the drum 4 is rotated at a low speed in both forward and reverse directions by driving the drum motor 8, the compressor 29 is driven, and the heat pump 15 is operated. At the same time, the blower fan 16 is driven. As a result, as shown by the arrow A in FIGS. 1 and 2, the air in the drum 4 is returned to the drum 4 from the exhaust port 17 through the circulation air passage 20 and the air supply port 18. Will be done.

At this time, the moist air discharged from the drum 4 passes through the upper exhaust duct 21, the rear exhaust duct 22, and the EVA inlet duct 23 in this order to reach the heat pump duct 24, and is dehumidified by passing through the evaporator 27. The dehumidified air is continuously heated by passing through the condenser 28 to become high-temperature dry air, which is supplied into the drum 4 from the air supply port 18 through the air supply duct 25. Here, in order to improve the heat exchange efficiency, the evaporator 27 and the condenser 28 have been enlarged, and the air passage rapidly expands in the evaporator inlet duct 23 to reach the evaporator 27. Therefore, the wind does not hit the entire evaporator 27 uniformly, and the flow of the wind concentrates on a part of the evaporator 27, so that the heat exchange capacity of the evaporator 27 may not be fully exhibited.

However, in the present embodiment, the inside of the EVA inlet duct 23 is divided into a plurality of divided air passages 23a to 23c, and air is passed through each of the divided air passages 23a to 23c to the evaporator 27 for each portion of the evaporator 27. Is configured to be incident. As a result, the air containing moisture is incident on the entire evaporator 27 almost evenly in each portion. Therefore, according to the present embodiment, in the one provided with the heat pump 15, the air flow can be widely dispersed and passed through the entire evaporator 27 without being biased, and the heat exchange efficiency can be improved. You can get the excellent effect of being able to.

Further, in the present embodiment, as shown in FIGS. 6 and 7, the tip of the EVA inlet duct 23 is arranged in the vertical direction and divided into a plurality of divided air passages 23a to 23c. As a result, with respect to each part in the vertical direction of the evaporator 27, air containing moisture can be incident on each part substantially evenly, and the air can be widely dispersed in the vertical direction of the evaporator 27 to allow air to pass through. .. At this time, as shown in FIG. 7 and the like, the outlet opening areas d of the divided air passages 23a to 23c at the tip of the evaporator inlet duct 23 are made uniform, so that the evaporator 27 is evenly arranged in the vertical direction. Can let the wind through.

In particular, in the present embodiment, as shown in FIG. 6 and the like, the positions of the base end portions of the partition walls 42 and 43 for dividing the split air passages 23a to 23c in the EVA inlet duct 23 are displaced in the wind flow direction. It was configured to be provided in the same form. As a result, it is possible to reduce the area of the wall surface of the portions of the partition walls 42 and 43 that are exposed to the wind at one time, and reduce the pressure loss thereof. Further, in the present embodiment, the inlet opening areas a to c of the divided air passages 23a to 23c on the base end side of the EVA inlet duct 23 are made uneven so that the upper part is larger, and each divided air passage at the tip portion is made uneven. The outlet opening areas d of 23a to 23c were made uniform. As a result, for example, even if there is a situation in which moist air tends to collect in the lower part of the evaporator inlet duct 23 due to the influence of gravity, it is possible to increase the air volume flowing in the upper part of the evaporator 27, and the equalization is further improved. It will be effective.
In addition, in the present embodiment, the lengths of the partition walls 42 and 43 are extended in the direction of arrow A to the inlet of the heat pump duct 24. This is because if the partition walls 42 and 43 are short, the rectified air flow tends to collect again at the lower part between the time the partition walls 42 and 43 exit and the time the partition walls 42 and 43 reach the heat pump duct 24 inlet. Equalization can be surely achieved by the configuration.

(2) Second to Sixth Embodiments FIG. 8 shows a second embodiment, and the difference from the first embodiment is in the configuration of the EVA inlet duct 51. That is, the EVA inlet duct 51 is provided with three divided air passages 51a to 51c arranged in the vertical direction inside by the two partition walls 42 and 43, as in the first embodiment. A damper 52 is provided at the base end of the EVA inlet duct 51 to adjust the air volume flowing into each of the divided air passages 51a to 51c according to the total air volume. The damper 52 can be operated between a first position shown by a solid line in the figure and a second position shown by an imaginary line in the figure by a drive mechanism including a motor or the like (not shown).

In this case, for example, when the total air volume flowing through the circulating air passage 20 is relatively small, the damper 52 is located at the first position, so that the air volume entering the divided air passage 51a becomes normal. On the other hand, when the total air volume flowing through the circulating air passage 20 is large, the damper 52 is displaced to the second position, and the air volume entering the split air passage 51a becomes larger. According to such a second embodiment, in addition to being able to obtain the same actions and effects as those of the first embodiment, the air volume hitting each part of the evaporator 27 is adjusted by providing the damper 52. It becomes possible to do it, and it becomes more effective.

FIG. 9 shows a third embodiment, and the configuration of the EVA inlet duct 61 is different from that of the first embodiment. That is, three partition walls 62 are provided in the EVA inlet duct 61, and four divided air passages 61a to 61d are provided side by side in the vertical direction on the tip side. At this time, the outlet opening area of each of the divided air passages 61a to 61d at the tip of the EVA inlet duct 61 is configured to be the largest in the upper stage and gradually become smaller as it goes down. That is, the outlet opening area of each of the divided air passages 61a to 61d is configured so that the one located above is larger than the one located below. Although not shown, the inlet opening areas of the divided air passages 61a to 61d on the base end side of the EVA inlet duct 61 are, for example, equal.

According to such a third embodiment, it is possible to increase the amount of air flowing to the upper part of the evaporator 27, and the same actions and effects as those of the first embodiment can be obtained. Then, the outlet opening area of each of the divided air passages 61a to 61d at the tip of the EVA inlet duct 61 is configured so that the one located above is larger than the one located below. Here, since the inlet / outlet of the refrigerant of the evaporator 27 is generally located at the upper part, more air can be passed upward in the vertical direction of the evaporator 27. Therefore, heat exchange can be efficiently performed in the portion of the evaporator 27 having a high heat exchange capacity.

FIG. 10 shows a fourth embodiment, and what is different from the first embodiment is the configuration of the outlet portion which is the tip end portion of the EVA inlet duct 71. That is, the inside of the EVA inlet duct 71 is divided into a plurality of parts, but in the fourth embodiment, for example, by two partition walls 72, the tip of the EVA inlet duct 71 is laterally divided. A plurality of side-by-side ducts In this case, the ducts are divided into three divided air passages 71a to 71c. The outlet opening areas of the divided air passages 71a to 71c are, for example, equal.

According to this configuration, with respect to each portion in the lateral direction of the evaporator 27, air containing moisture can be incident on each portion almost evenly, and the air is widely dispersed in the lateral direction of the evaporator 27 to allow air to pass therethrough. be able to. In other words, it is possible to prevent the left and right ends of the evaporator 27 from being less likely to be exposed to the wind. Therefore, according to the fourth embodiment, in the one provided with the heat pump 15, the air flow can be widely dispersed and passed through the entire evaporator 27 without being biased, and heat can be passed. It is possible to obtain an excellent effect that the exchange efficiency can be increased.

FIG. 11 shows a fifth embodiment, and shows the configuration of an outlet portion which is a tip end portion of the EVA inlet duct 81. In the present embodiment, the inside of the EVA inlet duct 81 is divided into a plurality of parts. For example, the tip portion is vertically 4 due to the three horizontal partition walls 82 and the two vertical partition walls 83. It is divided into a total of 12 divided air passages 81a in 3 rows and 3 rows. In this case, the horizontal partition wall 82 is provided so that the opening area becomes larger as the divided air passage 81a located above, and the vertical partition wall 83 is provided so as to divide the divided air passage 81a evenly in the lateral direction. ing.

According to the fifth embodiment, similarly to the first embodiment and the like, the heat pump 15 is provided, and the wind flow is not biased and is widely dispersed over the entire evaporator 27. It is possible to obtain an excellent effect that the air can be passed through and the heat exchange efficiency can be improved. Then, in the present embodiment, the split air passage 81a is provided so as to partition the EVA inlet duct 81 in both the vertical and horizontal directions. As a result, with respect to each portion divided into a large number in the vertical and horizontal directions of the evaporator 27, it is possible to inject moist air over the entire portion, and the air is widely dispersed in each portion of the evaporator 27 to pass air. be able to.

FIG. 12 shows the sixth embodiment and shows the configuration of the tip end portion of the EVA inlet duct 91. The difference between the EVA inlet duct 91 of the sixth embodiment and the EVA inlet duct 81 of the fifth embodiment is that, for example, one horizontal partition wall 92 and one vertical partition wall 93 make it vertically and horizontally. It has a configuration in which four divided air passages 91a are provided. Also in this sixth embodiment, as in the fifth embodiment, it is possible to inject moist air into each of the parts divided into a large number in the vertical and horizontal directions of the evaporator 27. It can be widely dispersed in each part of the evaporator 27 to allow air to pass through, and since the number of partitions is smaller than that of the fifth embodiment, the formation of the air passage 91 is easy and the resistance of the air passage is also reduced. be able to.

(3) Other Embodiments In the above embodiment, the EVA inlet duct has a shape that extends substantially linearly in the diagonal direction, but the overall shape of the EVA inlet duct is not limited to the shape that extends linearly. , It may extend while bending, or it may extend while bending. In addition, it goes without saying that various changes can be made in the number of divisions and the division form of the division air passage. Further, although not particularly described in the above embodiment, the EVA inlet duct and the partition wall can be made of, for example, a plastic molded product, but they can also be made of a metal such as an aluminum plate. is there. According to this, the wall can be made thinner. In the above embodiment, a so-called fin tube type evaporator and condenser are adopted, but a so-called multi-flow type heat exchanger may be adopted.

In addition, it can be applied to a clothes dryer dedicated to drying without a washing function. The overall configuration of the heat pump For example, the configuration of the circulation air passage may be such that the heat pump is arranged in the upper part of the outer box. The above embodiments are presented as examples and are not intended to limit the scope of the invention. These novel embodiments can be implemented in various other embodiments, and various omissions, replacements, and changes can be made without departing from the gist of the invention. The present embodiment and its modifications are included in the scope and gist of the invention, and are included in the scope of the invention described in the claims and the equivalent scope thereof.

In the drawing, 1 is a washer / dryer (clothes dryer), 2 is an outer box, 4 is a drum, 15 is a heat pump, 16 is a blower fan (blower), 17 is an exhaust port, 18 is an air supply port, and 20 is a circulation. The air passage, 21 is the upper exhaust duct, 22 is the rear exhaust duct, 23, 51, 61, 71, 81, 91 are the EVA inlet ducts, 23a, 23b, 23c, 51a, 51b, 51c, 61a, 61b, 61c, 61d. , 71a, 71b, 71c, 81a, 91a are split air passages, 24 is a heat pump duct, 25 is an air supply duct, 27 is an evaporator, 28 is a condenser, 29 is a compressor, 42, 43, 62, 72, 82. , 83, 92, 93 indicate a partition wall, and 52 indicates a damper.

Claims (9)

A water tank supported in the outer box via an elastic support mechanism,
A drum that is rotatably supported and houses clothes in the aquarium,
A circulation air passage provided so as to communicate between an exhaust port for discharging air from the water tank and an air supply port for blowing air into the water tank on the outside of the water tank.
A blower that circulates the air in the water tank through the circulation air passage, and
A compressor and a heat pump including an evaporator and a condenser arranged in the circulation air passage are provided.
The circulation air passage includes an exhaust duct extending from the exhaust port and an EVA inlet duct whose base end side is connected to the exhaust duct and whose tip end side is arranged at the inlet of the evaporator.
The evaporator inlet duct is a clothes dryer whose inside is divided into a plurality of divided air passages, and air is incident on the evaporator for each portion of the evaporator through each of the divided air passages. The clothes dryer according to claim 1, wherein the EVA inlet duct is divided into a plurality of divided air passages side by side in the vertical direction at the tip thereof. The clothes dryer according to claim 2, wherein the outlet opening area of each of the divided air passages at the tip of the EVA inlet duct is equal. The clothes dryer according to claim 2, wherein the outlet opening area of each of the divided air passages at the tip of the EVA inlet duct is larger than that located above. The clothes dryer according to claim 1, wherein the EVA inlet duct is divided into a plurality of divided air passages side by side at the tip thereof. A plurality of partition walls for dividing the split air passage are provided in the EVA inlet duct, and the partition walls are provided in a form in which the position of the base end portion is deviated in the wind flow direction. The clothes dryer according to any one of items 1 to 5. The garment according to claim 6, wherein the outlet opening area of each of the divided air passages at the tip of the EVA inlet duct is equal, and the inlet opening area of each of the divided air passages on the proximal end side is uneven. Dryer. The garment according to claim 6, wherein the outlet opening area of each of the divided air passages at the tip of the EVA inlet duct is uneven, and the inlet opening area of each of the divided air passages on the base end side is equal. Dryer. The invention according to any one of claims 1 to 8, wherein a damper for adjusting the air volume flowing into each of the divided air passages is provided at the base end portion of the EVA inlet duct according to the total air volume. Clothes dryer.

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