Washing and drying machine

Abstract

To provide a washing and drying machine in which heating efficiency of a heat pump unit has been improved.SOLUTION: A washing and drying machine includes: an outer tub arranged in a housing; an inner tub rotatably arranged in the outer tub; a blower for blowing air to the inner tub; a heat pump unit having a heat exchange chamber in which a dehumidification part and a heating part are arranged and a machine chamber in which a compressor is arranged; a first air passage for connecting the blower and the inner tub; and a second air passage for connecting the outer tub with the heat pump unit. A circulation air passage is formed which starts from the heat exchange chamber of the heat pump unit, goes through the blower, the first air passage, the inner tub, the outer tub and the second air passage and returns to the heat exchange chamber. The heat exchange chamber of the heat pump unit includes a first intake port on an upper surface of the upstream side of the heating part, and includes a second intake port on the upstream side of the heating part and on a side surface of the machine chamber side.SELECTED DRAWING: Figure 6

Description

[Technical field]

[0001] The present invention relates to a heat pump type washer / dryer. [Background technology]

[0002] The clothes dryer of Patent Document 1 is known as a clothes dryer that dries wet clothes by blowing hot air generated by a heat pump. For example, the abstract of the document states that the problem is to "provide a clothes dryer that can prevent the compressor from becoming excessively hot and can improve drying efficiency," and as a solution, it states that "the clothes dryer accommodates an evaporator on the upstream side of the circulating air in a circulation air duct and a condenser on the downstream side, and arranges a compressor outside the circulation air duct. Outside the circulation air duct, an enclosure that surrounds the compressor is provided so as to communicate with the circulation air duct at a position between the evaporator and the condenser. The enclosure has a first opening for taking in outside air, and is configured as an intake part that sucks the outside air taken in from the first opening through the enclosure into the circulation air duct from the communicating position."

[0003] Furthermore, paragraph 0024 of the document states, "As shown in FIG. 2, a condenser 31 and an evaporator 32 of a heat pump 30 are disposed within the heat exchanger duct 16. As is well known, the heat pump 30 is configured as a refrigeration cycle in which a compressor 33 that compresses and discharges a refrigerant, a condenser 31 that condenses and liquefies the high-temperature, high-pressure refrigerant discharged from the compressor 33 by dissipating heat, a throttling device 34 that reduces the pressure of the refrigerant liquefied by the condenser 31, an evaporator 32 that evaporates the refrigerant that has passed through the throttling device 34, and an accumulator 35 that stabilizes the flow of the refrigerant into the compressor 33 are connected in a cycle manner by a refrigerant flow path 30a." Paragraph 0031 states, "On the other hand, the surrounding portion 37 is 5, an intake port 39a is provided at a diagonal corner on the right wall 37a side. The intake port 39a is formed by cutting out the bottom wall 37d and the top wall 37e, and corresponds to a first opening that takes in air outside the enclosure 37 (inside the outer box 2), that is, outside air. In the enclosure 37, the intake port 39a and the communication hole 39b are always open. As a result, when the fan motor 21b is in operation, the exhaust damper 29 opens the exhaust port 28a to exhaust a part of the circulating air, and the outside air is taken in through the intake port 39a of the enclosure 37 (see arrow D2 in FIG. 5), passes around the compressor 33, and is sucked into the duct 16 of the circulating air passage 12 through the communication hole 39b.

[0004] As described above, in the clothes dryer of the cited document 1, as shown in Figures 2 and 5 of the same document, room temperature air taken in from outside is supplied upstream of the condenser 31 via communication hole 39b arranged between the condenser 31 and evaporator 32 of the heat pump 30. [Prior art documents] [Patent documents]

[0005] [Patent Document 1] JP 2020-10959 A Summary of the Invention [Problem to be solved by the invention]

[0006] However, as is clear from Figures 2 and 5 of Patent Document 1, the communication hole 39b in the document is a relatively narrow opening provided on only one side of the heat pump 30, so the room-temperature outside air taken in through the communication hole 39b has the following characteristics. That is, first, the room-temperature outside air taken in through the narrow communication hole 39b has a relatively faster wind speed than the same amount of room-temperature outside air taken in through a wide opening. Second, since the communication hole 39b is adjacent to only one side of the condenser 31, the room-temperature outside air that has passed through the condenser 31 has a characteristic of concentrating near one side of the condenser 31.

[0007] The first characteristic shortens the time it takes for the high-speed room-temperature outside air to pass through the condenser 31 (i.e., the time it takes for the room-temperature outside air to exchange heat with the condenser 31), resulting in a decrease in the heating efficiency of the heat pump 30. The first characteristic also causes the high-speed room-temperature outside air to scatter condensed water adhering to the evaporator 32 upstream of the communication hole 39b, which causes the scattered condensed water to be re-evaporated in the condenser 31, resulting in a decrease in the heating efficiency of the heat pump 30. Furthermore, the second characteristic narrows the area in which the condenser 31 exchanges heat with the room-temperature outside air, resulting in a decrease in the heating efficiency of the heat pump 30.

[0008] Therefore, the present invention aims to provide a washing / drying machine that improves the heating efficiency of a heat pump unit by suppressing the wind speed of the room temperature outside air taken in through the air intake of the heat pump unit and suppressing the bias in the wind speed distribution of the room temperature outside air taken in through the air intake. [Means for solving the problem]

[0009] In order to solve the above problems, the washing and drying machine of the present invention is a washing and drying machine comprising: an outer tub arranged within a housing, an inner tub arranged to be freely rotatable within the outer tub, a blower which sends air into the inner tub, a heat pump unit having a heat exchange chamber in which a dehumidifier and a heating section are arranged and a machine chamber in which a compressor is arranged, a first air duct connecting the blower and the inner tub, and a second air duct connecting the outer tub and the heat pump unit, wherein a circulating air duct is formed which runs from the heat exchange chamber of the heat pump unit via the blower, the first air duct, the inner tub, the outer tub and the second air duct and returns to the heat exchange chamber, and the heat exchange chamber of the heat pump unit has a first air intake on an upper surface upstream of the heating section, and a second air intake on a side surface upstream of the heating section facing the machine chamber. Effect of the Invention

[0010] According to the washer-dryer of the present invention, the wind speed of the room temperature outside air taken in through the air intake of the heat pump unit can be suppressed, and the bias in the wind speed distribution of the room temperature outside air taken in through the air intake can be suppressed, thereby improving the heating efficiency of the heat pump unit. [Brief description of the drawings]

[0011] [Figure 1] 1 is an external perspective view of a washing / drying machine according to a first embodiment. [Diagram 2] 1 is a cross-sectional view of a washing / drying machine according to a first embodiment. [Diagram 3] FIG. 1 is a schematic configuration diagram of a heat pump unit according to a first embodiment. [Figure 4] FIG. 1 is an external perspective view of a heat pump unit according to a first embodiment. [Diagram 5] 5 is a perspective view of the heat pump unit of FIG. 4 with an upper casing removed. [Figure 6] FIG. 2 is a cross-sectional view showing the arrangement of the intake ports of the heat pump unit of the first embodiment. [Figure 7] FIG. 11 is a cross-sectional view showing the arrangement of the intake ports of the heat pump unit of the second embodiment. [Figure 8] FIG. 11 is a cross-sectional view showing the arrangement of the intake ports of the heat pump unit of the third embodiment. [Figure 9A] FIG. 11 is a cross-sectional view showing the arrangement of the intake ports of the heat pump unit of the fourth embodiment. [Figure 9B] FIG. 9B is a front view of the air inlet of FIG. 9A. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0012] Hereinafter, embodiments of the motor drive device of the present invention will be described with reference to the drawings. Note that the configurations of the following embodiments may be combined as appropriate. EXAMPLES

[0013] First, a washing / drying machine 100 according to a first embodiment of the present invention will be described with reference to Figs. 1 to 6.

[0014] 1 is an external perspective view of a washer / dryer 100 of this embodiment. As shown in the figure, the front, back, left, right, top and bottom sides of the washer / dryer 100 are covered with a housing 101 made of metal or resin. A door 102 is provided on the front of the washer / dryer 100, which can be opened and closed to insert or remove clothes C to be washed. An operation unit 103 operated by a user is provided on the upper front side of the housing 101, and by operating this operation unit 103, desired settings can be registered for each process of washing, rinsing, spin-drying and drying.

[0015] 2 is a cross-sectional view of the washer / dryer 100 of this embodiment, and is a diagram mainly for explaining air flow A (broken line arrow) and water flow W (dash line arrow) during the drying process for drying wet clothes C and the like. As shown in this figure, an outer tub 104 is disposed inside the housing 101, and an inner tub 105 (drum) is disposed rotatably inside the outer tub 104. The inner tub 105 is rotated by a drum motor (not shown) provided on the rear side of the inner tub 105.

[0016] Inside the washer / dryer 100, a heat pump unit 1, a blower 2, an air passage 3, a flap 4, and a drainage passage 5 are provided. The heat pump unit 1, the blower 2, and the air passage 3 form a circulation air passage D that blows high-temperature dry air A1 to the inner tub 105 and collects high-temperature humid air A2 from the outer tub 104 as follows. That is, an air passage 3a toward the inner tub 105 is connected to the discharge side of the blower 2. An air passage 3b toward the heat pump unit 1 is connected to the outlet side of the outer tub 104 via an outer tub filter that collects lint generated in the drying process. The blower 2 is connected to the downstream side of the heat pump unit 1. In this way, a circulation air passage D is formed that flows from the heat pump unit 1 through the blower 2, the air passage 3a, the inner tub 105, the outer tub 104, and the air passage 3b, and returns to the heat pump unit 1.

[0017] Inside the heat pump unit 1, there are provided an evaporator 11 and a condenser 12 through which the wind flowing through the circulation air passage D passes. The evaporator 11 is a heat exchanger that dehumidifies the high-temperature, high-humidity air A2 that flows in from the outer tank 104 through the air passage 3b, and is also called a dehumidifying section. The dehumidified water that drips here accumulates at the bottom of the heat pump unit 1 and is discharged to the outside through a pump (not shown) and a drainage passage 5. The condenser 12 is a heat exchanger that heats the air dehumidified by the evaporator 11 to generate high-temperature dry air A1, and is also called a heating section. The evaporator 11 and the condenser 12 are cross-fin tube type heat exchangers in which refrigerant piping is inserted through stacked aluminum fins.

[0018] The blower 2 provided downstream of the heat pump unit 1 imparts a desired momentum to the high-temperature dry air A1, and controls the speed of the air flowing through the circulation air duct D.

[0019] Here, air passage 3c that communicates with the outside branches off from air passage 3b, and a step motor is used to switch between opening and closing of flap 4 to appropriately discharge high-temperature, high-humidity air A3, which is part of high-temperature, high-humidity air A2, to the outside, thereby promoting dehumidification within circulating air passage D. Note that even if high-temperature, high-humidity air A3 is discharged from air passage 3c, normal-temperature outside air A0 (e.g., 20°C) is appropriately taken in from intake port 16, which will be described later, so that an appropriate air pressure can be maintained within circulating air passage D.

[0020] FIG. 3 is a schematic diagram of the heat pump unit 1 of this embodiment. Note that FIG. 3 is a diagram mainly for explaining the flow of the refrigerant and the general arrangement of the intake port 16, and the shape and size of each part in the figure do not correspond to the actual ones. As shown in this figure, the heat pump unit 1 of this embodiment includes, in addition to the above-mentioned evaporator 11, condenser 12, and intake port 16, a compressor 13, an expansion valve 14, and a refrigerant pipe 15 connecting them. The inside of the heat pump unit 1 is partitioned into a heat exchange chamber 17 in which the evaporator 11 and the condenser 12 are arranged and which is also a part of the circulation air passage D, and a machine chamber 18 in which the compressor 13, the expansion valve 14, and the refrigerant pipe 15 are arranged. Each component of the heat pump unit 1 will be described below in order.

[0021] The evaporator 11 is cooled by the low-temperature gas-liquid two-phase refrigerant flowing inside. The high-temperature, high-humidity air A2 has a humidity level close to 100% by removing moisture from the wet clothes C in the inner tub 105. When the high-temperature, high-humidity air A2 comes into contact with the low-temperature evaporator 11, the refrigerant temperature in the evaporator 11 rises due to heat exchange between the two, and condensation occurs on the surface of the evaporator 11. As a result, the high-temperature, high-humidity air A2 from which moisture has been removed by the evaporator 11 becomes low-temperature dry air. Note that the amount of moisture removed by the evaporator 11 from the high-temperature, high-humidity air A2 is large, for example, about 30 to 40 g / min, so the condensed water on the surface of the evaporator 11 drips and accumulates at the bottom of the evaporator 11. The water accumulated at the bottom of the evaporator 11 is discharged to the outside of the washer / dryer 100 through the drainage channel 5 by appropriately driving the pump.

[0022] The medium-temperature, low-pressure refrigerant flowing out of the evaporator 11 flows into the compressor 13 via the refrigerant pipe 15. In the compressor 13, the medium-temperature, low-pressure refrigerant is pressurized to generate a high-temperature, high-pressure gas refrigerant. The high-temperature, high-pressure gas refrigerant flowing out of the compressor 13 flows into the condenser 12 via the refrigerant pipe 15.

[0023] The condenser 12 is heated by the high-temperature, high-pressure gas refrigerant flowing inside. The dry air that has passed through the evaporator 11 has its heat removed by the evaporator 11 and is therefore at a low temperature. Therefore, when the low-temperature dry air comes into contact with the high-temperature condenser 12, the temperature of the gas refrigerant in the condenser 12 drops due to heat exchange between them, and the refrigerant liquefies, and the dry air is heated to generate high-temperature dry air A1.

[0024] The liquefied refrigerant flowing out from the condenser 12 flows into the expansion valve 14 via the refrigerant pipe 15. In the expansion valve 14, the liquefied refrigerant is decompressed to generate a low-temperature two-phase gas-liquid refrigerant. The low-temperature two-phase gas-liquid refrigerant flowing out from the compressor 13 flows into the evaporator 11 via the refrigerant pipe 15. In this manner, the refrigerant cycle of the heat pump 1 is formed.

[0025] Here, as shown in Fig. 3, in the heat pump unit 1 of this embodiment, a plurality of intake ports 16 are provided between the evaporator 11 and the condenser 12. The intake ports 16 are openings for taking in room temperature outside air A0. The specific positions of the intake ports 16 and the significance of providing a plurality of intake ports 16 will be described below. Note that Fig. 3 illustrates an example of a configuration in which a plurality of intake ports 16 are provided between the evaporator 11 and the condenser 12, but the intake ports 16 may be provided at any position upstream of the condenser 12 of the heat pump unit 1 (for example, upstream of the evaporator 11).

[0026] Fig. 4 is an external perspective view of the heat pump unit 1 and the blower 2 combined. As shown in Fig. 4, the heat pump unit 1 of this embodiment is surrounded by a casing 10 that can be separated into upper and lower casings. Hereinafter, the upper casing 10 will be referred to as the upper casing 10a, and the lower casing 10 will be referred to as the lower casing 10b. Note that the illustration of the air intake 16 is omitted in Fig. 4.

[0027] Fig. 5 is a perspective view of the heat pump unit 1 of Fig. 4 with the upper casing 10a removed. As shown in Fig. 5, the inside of the heat pump unit 1 is divided by a wall erected on the bottom surface of the lower casing 10b into a heat exchange chamber 17 in which the high-temperature, high-humidity air A2 is converted into high-temperature dry air A1 using an evaporator 11 and a condenser 12, and a machine chamber 18 in which the compressor 13 and the like are disposed. Note that the air intake 16 is not shown in Fig. 5.

[0028] 6 is a cross-sectional view of the heat pump unit 1 at the cross section X in FIG. 3. As shown in the figure, a mesh-shaped air intake 16a is provided on the top surface of the upper casing 10a at the cross section X. Also, at the cross section X, an air intake 16b consisting of a large number of small holes is provided on the wall separating the heat exchange chamber 17 and the machine chamber 18. Therefore, at the cross section X, the room temperature outside air A0 can be taken in from two directions, the top surface and the side surface of the heat exchange chamber 17. In this way, the heat pump unit 1 of this embodiment that takes in the room temperature outside air A0 from two directions of the heat exchange chamber 17 can provide the following effects.

[0029] First, compared to a configuration in which an intake port for taking in room temperature outside air is provided on only one surface (see Figs. 2 and 5 of Patent Document 1), the heating efficiency of air flow A in condenser 12 can be improved. This is due to the following mechanism.

[0030] That is, as shown in FIG. 2 and FIG. 5 of Patent Document 1, if there is only one air intake port and the opening area is relatively small, when the same volume of room temperature outside air is taken in through the air intake port, the wind speed of the room temperature outside air passing through the air intake port becomes relatively fast, and the bias of the wind speed distribution becomes relatively large. As a result, if the wind speed of the air flow A passing through the condenser 12 becomes fast and the wind speed distribution of the air flow A becomes uneven, the time during which the air flow A can exchange heat with the condenser 12 becomes short, and the area in which efficient heat exchange can be realized becomes narrow. In contrast, if multiple air intake ports 16 (16a, 16b) are provided as in this embodiment, the speed of the room temperature outside air A0 flowing into the condenser 12 can be suppressed, the time during which the air flow A can exchange heat with the condenser 12 can be extended, and the range in which the room temperature outside air A0 flows into the condenser 12 can be expanded, so that the efficiency of heat exchange between the room temperature outside air A0 and the condenser 12 can be improved.

[0031] Secondly, compared to a configuration in which the air intake port for taking in room temperature outside air is provided on only one surface (see Figs. 2 and 5 of Patent Document 1), it is possible to suppress the scattering of condensed water on the surface of the evaporator 11 and suppress the decrease in heating efficiency caused by the re-evaporation of the scattered condensed water. This is due to the following mechanism.

[0032] That is, as shown in FIG. 2 and FIG. 5 of Patent Document 1, if there is only one air intake and the opening area is relatively small, the wind speed of the room temperature outside air passing through the air intake becomes relatively fast, and the condensed water attached to the evaporator upstream of the condenser is easily drawn in. The condensed water drawn in by the high-speed room temperature outside air is re-evaporated by contacting the high temperature condenser, but the condenser loses energy at that time, and the efficiency of the condenser heating the air flow is reduced. In contrast, if multiple air intakes 16 (16a, 16b) are provided as in this embodiment, the speed of the room temperature outside air A0 flowing in from the air intake 16 is suppressed, so the amount of condensed water drawn in by the room temperature outside air A0 from the evaporator 11 can be reduced, and the amount of energy that the scattered condensed water takes from the condenser 12 can be suppressed.

[0033] According to the washer-dryer of this embodiment described above, the wind speed of the room temperature outside air taken in through the heat pump's air intake is suppressed, and the bias in the wind speed distribution of the room temperature outside air taken in through the air intake is suppressed, thereby improving the heating efficiency of the heat pump. EXAMPLES

[0034] Next, a washer / dryer 100 according to a second embodiment of the present invention will be described with reference to Fig. 7. Note that a duplicated description of points common to the first embodiment will be omitted.

[0035] 6, in cross section X of heat pump unit 1 of Example 1, air intake 16a is provided on the top surface, and air intake 16b is provided on the side surface on the side of machine room 18. In contrast, in this example, an air intake is also provided on the surface opposite air intake 16b, so that bias in the wind speed and wind speed distribution of room-temperature outside air A0 taken in through air intake 16 can be further suppressed.

[0036] Specifically, as shown in Fig. 7, a mesh-like intake port 16c is provided on the side of the lower casing 10b, and an intake port 16d consisting of many small holes is provided inside the mesh-shaped intake port 16c, so that the room temperature outside air A0 can also be taken in through the route via the intake ports 16c and 6d of this double structure. Note that, because condensed water dripping from the evaporator 11 accumulates at the bottom of the lower casing 10b, in order to prevent this water from flowing out, in the present invention, no intake port 16 is provided at the bottom of the lower casing 10b.

[0037] According to the washer-dryer of this embodiment described above, the wind speed of the room temperature outside air taken in through the heat pump's air intake is further suppressed, and the bias in the wind speed distribution of the room temperature outside air taken in through the air intake is further suppressed, thereby further improving the heating efficiency of the heat pump. EXAMPLES

[0038] Next, a washer / dryer 100 according to a third embodiment of the present invention will be described with reference to Fig. 8. Note that a duplicated description of points common to the first embodiment will be omitted.

[0039] As shown in Fig. 6, the air intake 16b in the first embodiment has many uniformly sized small holes, but in the present embodiment, the size of the small holes in the air intake 16b is made smaller toward the top and larger toward the bottom. The reason for making the small holes different sizes is as follows.

[0040] That is, as is self-evident from Fig. 6 of the first embodiment, if the size of the small holes of the intake port 16b is uniform in the cross section X of the heat pump unit 1, the amount of the room temperature outside air A0 taken in the upper part of the heat exchange chamber 17 will be greater than the amount of the room temperature outside air A0 taken in the lower part, due to the presence of the room temperature outside air A0 taken in from the intake port 16a on the upper surface. This leads to an increase in bias in the wind speed distribution of the room temperature outside air A0 taken in from the intake port of the heat pump, so in this embodiment shown in Fig. 8, the size of the small holes of the intake port 16b is made smaller at the top and larger at the bottom, so that the amount of the room temperature outside air A0 taken in the upper part of the heat exchange chamber 17 approaches the amount of the room temperature outside air A0 taken in the lower part, thereby reducing the bias in the distribution of the room temperature outside air A0 taken in from the intake port of the heat pump. EXAMPLES

[0041] Next, a washer / dryer 100 according to a fourth embodiment of the present invention will be described with reference to Figures 9A and 9B. Note that a duplicated description of points common to the third embodiment will be omitted.

[0042] As shown in Fig. 8, in Example 3, the size of the small holes of the air intake port 16b is smaller toward the top and larger toward the bottom. In contrast, in this example, as shown in Fig. 9A, the air intake port 16b is configured with one large hole, and as shown in Fig. 9B, the width of the air intake port 16b is narrowed at the top and widened at the bottom, so that the same effect as the air intake port 16b configured with many small holes in Example 3 can be obtained with the air intake port 16b configured with one large hole. [Explanation of symbols]

[0043] 100 Washer / dryer 101 Case 102 Doors 103 Operation section 104 Outer tank 105 Inner tank 1 Heat pump unit 10 Casing 10a Upper casing 10b Lower casing 11 Evaporator 12 Condenser 13 Compressor 14 Expansion valve 15 Refrigerant piping 16 Air Intake 17 Heat exchange room 18 Machine room 2. Blower 3 Wind path 4 Flap

Claims

1. An outer tank disposed within the housing; an inner tank rotatably disposed within the outer tank; A blower that blows air into the inner tank; a heat pump unit having a heat exchange chamber in which a dehumidifying section and a heating section are arranged and a machine chamber in which a compressor is arranged; A first air duct connecting the blower and the inner tank; A second air duct connecting the outer tub and the heat pump unit; A washing and drying machine comprising: A circulation air passage is formed from the heat exchange chamber of the heat pump unit, through the blower, the first air passage, the inner tank, the outer tank, and the second air passage, and returning to the heat exchange chamber, The heat exchange chamber of the heat pump unit is A first intake port is provided on an upper surface of the upstream side of the heating section, The washer / dryer further comprises a second air intake port on a side surface upstream of the heating section.

2. The washing and drying machine according to claim 1, The washing / drying machine is characterized in that the second air intake is disposed on a side surface on the machine chamber side.

3. The washing and drying machine according to claim 2, The first air inlet and the second air inlet are disposed downstream of the dehumidifying section.

4. The washing / drying machine according to any one of claims 1 to 3, The first air intake is a mesh air intake, The washing / drying machine according to claim 1, wherein the second air inlet is an air inlet consisting of a large number of small holes.

5. The washing and drying machine according to claim 4, The large number of small holes are smaller at the top and larger at the bottom.

6. The washing / drying machine according to any one of claims 1 to 3, The first air intake is a mesh air intake, The second air inlet is a single hole having a narrow upper portion and a wide lower portion.

7. The washing and drying machine according to claim 1, The washer / dryer is characterized in that the second air intake is disposed on a side surface opposite to the side surface on the machine chamber side.

8. The washing / drying machine according to any one of claims 1 to 3, The heat exchange chamber of the heat pump unit is a third air intake port on a side surface upstream of the heating section and facing the side surface on the machine chamber side,

9. The washing and drying machine according to claim 8, The third air intake is a dual-structure air intake consisting of a mesh-shaped air intake arranged on the outside and an air intake consisting of a large number of small holes arranged on the inside.

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