JP2004229954A - Drum type washer/drier - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a drum type washer/drier which raises drying efficiency. <P>SOLUTION: A drying unit 8 installed in a duct 9 which passes between a drum 4 and an outer tub and couples an air outlet 6 and an air inlet 7 formed in the drum 4 is driven, and air from the air outlet 6 is condensed and dehumidified, and the dehumidified air is heated and made to flow into the drum 4 as a hot air, then, laundry in the drum 4 is dried. At this time, the drying unit 8 is structured with a heat pump 16 which comprises a compressor 10 which compresses a cooling medium, an elevated temperature side heat exchanger 26 which is supplied with the compressed cooling medium from the compressor 10 and heats the air with heat of the cooling medium, an expansion valve 27 which expands the cooling medium from the elevated temperature side heat exchanger 26 and a low temperature side heat exchanger 28 which condenses and dehumidifies the air after heat exchange of the cooling medium from the expansion valve 27 and the air from the air outlet 6. <P>COPYRIGHT: (C)2004,JPO&NCIPI

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a drum-type washing / drying machine capable of drying laundry using a heat pump having high energy efficiency.
[0002]
[Prior art]
Today, washing and drying machines that automatically perform washing, dehydration, and drying have begun to be offered to the market, and among them, a drum-type washing and drying machine has been beginning to be offered to the market in consideration of the convenience of loading and unloading of laundry (Patent Document 1). reference).
[0003]
Such a drum type washing and drying machine is disposed in an outer tub for collecting water, a rotary drum provided in the outer tub and into which laundry is put, and a duct formed between the outer tub and the drum. The main structure is a drying mechanism for drying the laundry that has been washed and dewatered.
[0004]
The drying mechanism includes a dehumidifying unit that dehumidifies and dehumidifies the air flowing through the duct, a heating unit that heats the air dehumidified by the dehumidifying unit to generate hot air, and a heating unit that supplies air from the drum to the heating unit. And a blower that circulates back to the drum.
[0005]
Dehumidification of air is performed by contacting the air with water supplied from a water supply port to cool the air, thereby forming dew. For this reason, a plurality of cooling plates whose plate surfaces are set substantially perpendicular to the flow direction of the air are provided so that the water and the air can efficiently touch each other, and the water flows down along the cooling plates. It is formed as follows.
[0006]
The heating unit includes an electric heater, and heats the air dehumidified by the dehumidifying unit to generate hot air.
[0007]
Washing is performed by putting laundry and water into the drum and rotating the drum, and then draining the water and rotating the drum at high speed to perform dehydration.
[0008]
When the dehydration is completed, the drying mechanism is operated while rotating the drum to loosen the laundry, thereby drying the laundry. To dry the laundry, the air in the drum is circulated through a duct by a blower, and at that time, the air passes through the dehumidifying unit and is dehumidified, and the air is heated by the heating unit to become hot air. This is done by returning to the drum.
[0009]
[Patent Document 1]
JP-A-11-114292
[0010]
[Problems to be solved by the invention]
However, in the above-mentioned drum type washer / dryer, water is used to cool and dehumidify the air, and an electric heater is used to heat the air to generate hot air. It was difficult to achieve high drying efficiency.
[0011]
That is, the cooling plate in the cooling unit is provided so that its plate surface is substantially perpendicular to the flow direction of the air so that the water and the air can be in efficient thermal contact. For this reason, the flow resistance of air becomes large and the number of the cooling plates cannot be increased so much that it is difficult to efficiently perform dehumidification.
[0012]
In addition, since water such as city water is used as a heat source for dew condensation in the dehumidifying section, the temperature difference between the water and the air cannot be increased. ), The efficiency of dehumidification could not be improved, and the water at that time was disposable, resulting in poor economic efficiency.
[0013]
Further, in the heating section, air is heated by an electric heater. However, even if the heater temperature is set higher than necessary, it is difficult to efficiently heat the air, which is not preferable from the viewpoint of safety.
[0014]
In order to heat the air efficiently, it is preferable to heat the air uniformly at an appropriate heater temperature. For this purpose, it is necessary to increase the thermal contact area with the air.
[0015]
In order to increase the thermal contact area, for example, in the case of an electric heater made of a nichrome wire, it is necessary to use a lot of the nichrome wire, but since the nichrome wire itself cannot maintain its shape, there are many members for supporting the nichrome wire. As a result, the flow resistance of the air by such a member increases.
[0016]
Of course, even if a member such as a heating plate is used instead of a nichrome wire, a similar problem occurs when it is necessary to support the plates one by one.
[0017]
As described above, it is difficult to improve the drying efficiency due to poor dehumidifying efficiency and heating efficiency.
[0018]
Then, an object of the present invention is to provide a drum type washing and drying machine with improved drying efficiency.
[0019]
[Means for Solving the Problems]
In order to solve the above-mentioned problem, the invention according to claim 1 puts laundry in a drum provided in an outer tub, performs washing by swinging the drum, and dehydrates when washing is completed. Driving a drying unit provided in a duct that connects an air outlet and an air inlet provided on the drum through a space between the drum and the outer tank to dehumidify and condense air from the air outlet, By heating the dehumidified air and flowing it into the drum as warm air, in a drum type washing and drying machine for drying laundry in the drum, a drying unit includes a compressor for compressing a refrigerant and a compressor for compressing a refrigerant. A compressed refrigerant is supplied, and a high-temperature heat exchanger that heats air with the heat of the refrigerant, an expansion valve that expands the refrigerant from the high-temperature heat exchanger, and a refrigerant and an air outlet from the expansion valve With air from And heat exchange, a heat pump and a low-temperature heat exchanger for dehumidifying by condensing the air, characterized in that enhanced drying efficiency.
[0020]
The invention according to claim 2 is characterized in that the refrigerant is a carbon dioxide refrigerant.
[0021]
According to a third aspect of the present invention, the high-temperature side heat exchanger and the low-temperature side heat exchanger have a plurality of fins that exchange heat with air and a refrigerant pipe through which the refrigerant circulates, and the fins are fixed to the refrigerant pipe. A refrigerant plate plate forming a part of the duct.
[0022]
The invention according to claim 4 is characterized in that the high-temperature side heat exchanger is provided at a position where water is not immersed during washing or rinsing.
[0023]
The invention according to claim 5 is characterized in that the low-temperature side heat exchanger is provided at a position where water is not immersed during washing or rinsing.
[0024]
BEST MODE FOR CARRYING OUT THE INVENTION
An embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a side view showing a schematic configuration of a drum type washer / dryer to which the present invention is applied, and FIG. 2 is a schematic diagram showing a circuit of a heat pump constituting a later-described drying unit using the drum dryer. It is.
[0025]
The drum-type washing / drying machine 1 includes an outer box 2 having a door 5 which can be opened and closed on a front plate, an outer cylindrical tank 3 arranged in the outer box 2 for storing water, and a horizontal axis in the outer tank 3. A cylindrical drum 4 disposed rotatably around (the direction perpendicular to the paper surface in FIG. 1 is the direction of the rotation axis), a drain unit (not shown) for draining water in the outer tank 3, and a rotating drum 4 A drive unit (not shown) for driving and a drying unit 8 for drying the washed laundry stored in the drum 4 while draining water in the outer tub 3 are provided.
[0026]
On the side surface of the drum 4, an air outlet 6 serving as a port through which the air in the drum 4 flows into the drying unit 8 and an air inlet 7 serving as a port through which the air from the drying unit 8 enters the drum 4 are provided. ing.
[0027]
As shown in FIGS. 1 and 2, the drying unit 8 mainly includes a duct 9, a heat pump 16, and a blower 17 for circulating air. Note that, in FIG. 2, the dotted arrows indicate the flow direction of the air, and the solid arrows indicate the flow of the refrigerant.
[0028]
The duct 9 is provided in a space between the outer tub 3 and the drum 4, communicates the air outlet 6 and the air inlet 7, and a blower 17 is provided in the duct 9 so that the air in the drum 4 is The air is circulated such that air is taken in from the outlet 6 and blown into the drum 4 from the air inlet 7 through the duct 9.
[0029]
The heat pump 16 includes a compressor 10 for compressing the refrigerant, a high-temperature side heat exchanger 26 for exchanging heat between the refrigerant and air compressed by the compressor 10 to heat the air, and a heat for the high-temperature side heat exchanger 26. An expansion valve 27 for expanding the exchanged refrigerant, a low-temperature side heat exchanger 28, a high-temperature side heat exchanger 26, and a low-temperature side heat exchange for exchanging heat between the refrigerant expanded by the expansion valve 27 and air to cool the air. A high-temperature heat exchanger 26, a low-temperature heat exchanger 28, and a blower 17 are provided in the duct 9.
[0030]
The high-temperature side heat exchanger 26 and the low-temperature side heat exchanger 28 are preferably located so as not to be immersed in water that is stretched during washing or rinsing. The reason will be described later.
[0031]
Such a high-temperature side heat exchanger 26 and a low-temperature side heat exchanger 28 have substantially the same configuration. Therefore, in the following description, these components are collectively referred to as the heat exchanger 29 unless it is particularly necessary to distinguish them.
[0032]
FIG. 3 is a partially cutaway perspective view showing a schematic configuration of the heat exchanger 29. The heat exchanger 29 has a refrigerant pipe plate 36 attached to the concave member 18 integrally formed with the outer tub 3 by screws 19 or the like. On one surface of the refrigerant tube plate 36, a refrigerant tube 37 for circulating the refrigerant is attached in close thermal contact by brazing or the like, and a plurality of fins 38 are mounted on the other surface by brazing or the like. Mounted in thermal contact with
[0033]
In FIG. 3, thick arrows indicate the direction of air flow, thin arrows indicate the flow of refrigerant, and the air flow direction and the refrigerant flow direction are provided in opposite directions (counterflow). The surface 38 is provided so as to follow the flow of air.
[0034]
Thereby, the flow resistance of the air can be reduced, and the air and the refrigerant form a counter flow, so that heat can be efficiently exchanged.
[0035]
As described later, since the fins 38 are formed of metal, the fins 38 can hold their own posture. Therefore, it is easy to increase the number of the fins 38, and from this point, it is possible to increase the heat exchange efficiency.
[0036]
The refrigerant pipe plate 36 is assembled by inserting the refrigerant pipe plate 36 so that the fins 38 fit into the concave portions of the concave member 18 and screwing the concave member 18 and the refrigerant pipe plate 36 with screws 19. Done.
[0037]
As shown in FIG. 2, the duct 9 connects the air outlet 6 and the air inlet 7 to form an air passage, and the space surrounded by the refrigerant tube plate 36 and the concave member 18 is Part 9
[0038]
The concave member 18 integrally formed with the outer tank 3 is formed of the same material (for example, resin) as the outer tank 3, and the refrigerant tube plate 36 and the fins 38 are made of metal such as stainless steel, cupronickel, copper, or aluminum. It is formed with.
[0039]
In recent years, a technique of washing with electrolytic water without using a detergent has been proposed. When such electrolyzed water is used, copper or aluminum or the like is corroded by hypochlorous acid or the like contained therein. Therefore, the refrigerant pipe plate 36 is made of stainless steel or cupronickel having high corrosion resistance. , Fins 38 and screws 19 are preferably formed.
[0040]
Of course, when such electrolyzed water is not used, it is preferable to form the refrigerant tube plate 36 and the fins 38 from copper or aluminum, and the cost can be reduced by using these materials.
[0041]
FIG. 4 is a cross-sectional view showing a schematic configuration of the compressor 10. In the present invention, a carbon dioxide refrigerant is used as a refrigerant. However, the present invention is not an essential requirement for the drum-type washing and drying machine 1 using a heat pump, but is a conventional one. It is also possible to use a refrigerant (HFC refrigerant, R-20 refrigerant or the like).
[0042]
However, the carbon dioxide refrigerant has the advantage that it is easier to obtain a higher temperature than the conventionally used HFC refrigerant, and has the advantage that the ozone layer is not destroyed because it does not contain chlorine unlike the R-20 refrigerant. preferable.
[0043]
The compressor 10 is a two-stage rotary compressor having a motor 11 as a driving unit, a compression unit 12 provided below the motor 11, and the like, and these are housed in a closed case 13. .
[0044]
A lubricating oil 14 is stored at the bottom of the closed case 13 so as to lubricate a sliding portion of the compression means 12.
[0045]
The compression means 12 includes a first-stage compression element 20 and a second-stage compression element 30, and each of the compression elements 20, 30 is provided with suction ports 21, 31 and discharge ports 22, 32.
[0046]
Further, a connection pipe 40 is provided in the sealed case 13. One end of the connection pipe 40 communicates with the space inside the closed case 13, and the other end communicates with the suction port 31 of the rear compression element 30. A radiator 41 is provided in the connection pipe 40.
[0047]
The compression mechanism of the first-stage compression element 20 and the second-stage compression element 30 have substantially the same configuration, and rollers 24 and 34 are disposed in cylindrical cylinders 23 and 33 for each of the compression elements 20 and 30. The rollers 24 and 34 are formed in a cylindrical shape, and cranks 25 and 35 are disposed inside the rollers 24 and 34, and a vane (not shown) abuts on the outer surfaces of the rollers 24 and 34 to partition an intake chamber and a compression chamber. ing.
[0048]
The rollers 24 of the first-stage compression element 20 and the rollers 34 of the second-stage compression element 30 are provided with rotation phases shifted by 180 degrees so that vibrations generated by the eccentric rotation of the rollers 24 and 34 are offset. Have been.
[0049]
Since the cranks 25, 35 are provided fixedly (or integrally formed) to the rotating shaft 15 of the motor 11, the rotation of the cranks 25, 35 causes the rollers 24, 34 to eccentrically rotate and follow the eccentric rotation. As a result, the vane is displaced, and the space volume between the suction chamber and the compression chamber fluctuates, thereby sucking and compressing the carbon dioxide refrigerant.
[0050]
As the compression chamber is reduced, the carbon dioxide refrigerant is compressed, and when it reaches a discharge pressure specified by a discharge valve (not shown), the carbon dioxide refrigerant is discharged from the discharge ports 22 and 32.
[0051]
The discharge port 32 of the rear compression element 30 is not in communication with the space in the closed case 13, but the discharge port 22 of the front compression element 20 is in communication with the space in the closed case 13.
[0052]
With such a configuration, first, a required amount of water such as city water is stored in the outer tub 3 and the laundry is put into the drum 4 and the drum 4 is rotated (including a swinging motion) to perform washing.
[0053]
Thereafter, the water in the outer tub 3 is once drained by the drain unit, and then the drum 4 is rotated while supplying water to rinse, dehydrate and dry the laundry.
[0054]
When drying the laundry, the drying unit 8 is driven. Thereby, the heat pump 16 operates and the blower 17 operates. In addition, the drum 4 starts the swinging motion to stir the laundry.
[0055]
When the heat pump 16 operates, the carbon dioxide refrigerant is compressed by the compressor 10 to become a high-temperature and high-pressure carbon dioxide refrigerant. The high-temperature and high-pressure carbon dioxide refrigerant is supplied to the high-temperature side heat exchanger 26 and exchanges heat with air, and heats the air to generate hot air.
[0056]
The warm air is blown into the drum 4 and dries the laundry by taking in the moisture of the laundry (by forming high-humidity air).
[0057]
On the other hand, the carbon dioxide refrigerant that has exchanged heat in the high-temperature side heat exchanger 26 expands in the expansion valve 27, is supplied to the low-temperature side heat exchanger 28, and evaporates by exchanging heat with air.
[0058]
At this time, the latent heat of evaporation is provided by air. Therefore, the temperature of the air decreases, and the amount of the saturated steam decreases, and the supersaturated steam contained in the air condenses. The condensed water drops along the fins 38 and is drained.
[0059]
Thereafter, the air is heated by the high-temperature side heat exchanger 26 as described above, and is blown into the drum 4 as hot air.
[0060]
As described above, the refrigerant pipe plate 36 forming a part of the duct 9 is cooled or heated by the action of the carbon dioxide refrigerant to dehumidify and heat the air flowing through the duct 9, so that efficient drying can be performed. Will be possible.
[0061]
It has been described earlier that it is preferable that the high-temperature side heat exchanger 26 and the low-temperature side heat exchanger 28 are not immersed in water at the time of washing or rinsing.
[0062]
This is because when the high-temperature heat exchanger 26 or the low-temperature heat exchanger 28 is immersed in water during washing or rinsing, the water adhered at that time remains in a state in which the fins 38 are bridged, and the drying operation is performed in this state. If this is done, the temperature of the low-temperature side heat exchanger 28 becomes 0 ° C. or lower and freezes, thereby increasing the flow resistance of air.
[0063]
In addition, extra energy is required for freezing the attached water, and extra energy is required for evaporating the attached water in the high-temperature side heat exchanger 26. Such energy is originally unnecessary energy.
[0064]
Further, since the compressor 10 is disposed outside the outer tub 3, there is no inconvenience due to such flooding. However, since the blower 17 is provided in the duct 9, the high-temperature side heat exchanger 26 and the low-temperature side heat exchanger 26 are provided. It is anticipated that a large amount of water adhering to the blower 17 will be sucked (sent to the blower 17 side) at the same time as the start of operation of the blower 17 to wet the blower 17 and cause the blower 17 to break down.
[0065]
Further, the air dehumidified by the low-temperature side heat exchanger 28 is heated by the high-temperature side heat exchanger 26. At this time, if the high-temperature side heat exchanger 26 is configured to be flooded during washing or the like, the air adheres at that time. It is expected that the air dehumidified by the low-temperature side heat exchanger 28 becomes wet again by the moisture.
[0066]
From the above, it is preferable that at least the high-temperature side heat exchanger 26 is provided at a position where no water is flooded, and further it is preferable that not only the high-temperature side heat exchanger 26 but also the low-temperature side heat exchanger 28 is provided at a position where water is not flooded.
[0067]
In the above description, as shown in FIG. 3, the high-temperature side heat exchanger 26 and the low-temperature side heat exchanger 28 are formed by fixing a meandering refrigerant pipe 37 to a refrigerant pipe plate 36 by fusing or the like, and forming the same into a concave shape. The configuration is such that the refrigerant pipe plate 36 is a plate-shaped member.
[0068]
However, the present invention is not limited to this, and may have a configuration as shown in FIG. 5, for example. FIG. 5 is a diagram schematically showing the configuration of the refrigerant tube plate 36 and the refrigerant tube 37, and FIG. 5A is a schematic diagram corresponding to the configuration shown in FIG.
[0069]
FIG. 5B is a schematic diagram showing a case where the refrigerant tube plate 36 is formed in a concave shape (U-shape), and the refrigerant tube 37 is fixed around the concave portion. FIG. It is a schematic diagram in the case where it is formed in a tubular shape (including a divided shape) (including divided formation), and a refrigerant pipe 37 is fixed so as to surround it.
[0070]
In the case of the configuration shown in FIG. 5A, there is an advantage that manufacturing and assembling become easy because it is only necessary to attach the refrigerant pipe plate 36 to the concave member 18 formed in the outer tank 3.
[0071]
In the case of the configuration shown in FIG. 5B, the refrigerant tube plate 36 can be attached to the outer tank 3 at an arbitrary position, and thus there is an advantage that the assembly becomes easy.
[0072]
Further, in the case of the configuration shown in FIG. 5C, heat is transferred to the fins 38 by the two opposed refrigerant tube plates 36, and therefore, compared to the case of FIGS. 5A and 5B. There is an advantage that heat transfer can be performed efficiently and drying efficiency is improved.
[0073]
By the way, in the above description, the configuration shown in FIG. 3 is adopted so that the flow direction of the air and the flow direction of the carbon dioxide refrigerant are opposed to each other. However, the present invention is not limited to this. The configuration shown is also possible.
[0074]
6A and FIG. 6B, the flow direction of the air and the flow direction of the carbon dioxide refrigerant have an opposite relationship, and the configuration shown in FIG. 3 corresponds to FIG. 6A. .
[0075]
However, the carbon dioxide refrigerant compressed by the first-stage compression element 20 as shown in FIG. 4 is discharged into the closed case 13, supplied to the second-stage compression element 30, further compressed by the second-stage compression element 30, and In the case of using the compressor 10 configured to discharge the water in the opposite direction, it is preferable to use the counterflow having the configuration illustrated in FIG.
[0076]
Generally, when compressing the carbon dioxide refrigerant, the lubricating oil 14 is taken into the carbon dioxide refrigerant. In the case of one-stage compression (when the compression element is 1), the compressed carbon dioxide refrigerant is discharged into the closed case 13 having a large space volume, and then discharged from the compressor 10.
[0077]
At this time, when the carbon dioxide refrigerant is discharged into the closed case 13, the lubricating oil and the refrigerant are separated sufficiently or within the space volume, and only the lubricating oil remains in the closed case 13. Not ejected.
[0078]
However, in the case of two-stage compression as shown in FIG. 4, there is no problem because the carbon dioxide refrigerant compressed by the first-stage compression element 20 is discharged into the closed case 13, but is compressed by the second-stage compression element 30. Since the carbon dioxide refrigerant is discharged from the compressor 10 as it is, a large amount of the lubricating oil 14 is also discharged from the compressor 10 accordingly.
[0079]
Therefore, in the case of the configuration as shown in FIG. 6B in which the carbon dioxide refrigerant flows upward from the bottom, the lubricating oil 14 is easily stored in the meandering refrigerant pipe 37, but the configuration as shown in FIG. In this case, the carbon dioxide refrigerant flows from top to bottom, so that it is difficult to store the refrigerant in the refrigerant pipe 37.
[0080]
From such a viewpoint, in the case of the compressor 10 having the multi-stage compression element and configured to discharge the carbon dioxide refrigerant compressed in the last stage as it is, FIG. 3, that is, FIG. It is preferred to have a countercurrent flow of the configuration.
[0081]
Next, a second embodiment of the present invention will be described with reference to the drawings. Note that the same components as those in the first embodiment are denoted by the same reference numerals, and description thereof will be omitted as appropriate.
[0082]
In the first embodiment, the intervals between the fins 38 in the high-temperature side heat exchanger 26 and the low-temperature side heat exchanger 28 are the same, and all the fins 38 have the same dimensions.
[0083]
In the low-temperature side heat exchanger 28, the moisture contained in the air is dewed by dew condensation. This dew water adheres to the fins 38, which may grow and bridge between the adjacent fins 38. .
[0084]
Since there is an air flow path between the fins 38, if the dew water bridges and closes the space between the fins 38, the flow path of the air is narrowed, the flow resistance is increased, and the drying efficiency is reduced. .
[0085]
Of course, if the fin 38 spacing is sufficiently large, the occurrence of bridges can be completely prevented. However, if the fin 38 is set to such a large size, the number of fins 38 that exchange heat with air is reduced, and the heat exchange efficiency is reduced. .
[0086]
Therefore, there is an optimum interval between the fins 38 for suppressing the generation of the bridge and for suppressing the decrease in the heat exchange efficiency. The interval between the fins 38 is determined by the material and surface condition of the fin 38, the coating property, the air flow rate, and the like. Therefore, it is difficult to specify all of them.
[0087]
The inventor of the present application has proposed that when air is blown by a blower used in a conventional configuration using fins 38 of rolled aluminum, if the distance between the fins 38 is set to about 2 mm or more, the occurrence of bridges is suppressed, and the heat is reduced. It has been found that it is possible to suppress a decrease in exchange efficiency.
[0088]
In the present invention, the distance between the fins 38 is not limited to a predetermined value or more. For example, as shown in FIG. 7, the dimensions of the fins 38 (the dimensions in the direction of air flow) may be different. .
[0089]
The configuration shown in FIG. 7 includes a side on which air flows in (hereinafter, referred to as a downstream area), a side on which dehumidified air flows out (hereinafter, referred to as an upstream area), and a region between a downstream region and an upstream region (hereinafter, a midstream region). Of the fins 38 are arranged such that the interval between the fins 38 becomes narrower toward the upstream region.
[0090]
As a result, the air immediately after flowing from the drum 4 containing a large amount of moisture is roughly dehumidified in the downstream region, the dehumidification of the moisture that can be removed in the middle flow region is almost completed, and the moisture that can be removed in the upstream region is removed. The dehumidification for minutes is completed, and the occurrence of bridges due to dew water can be suppressed without increasing the air resistance.
[0091]
The dew water flows down the fins 38. In the downstream area, there is dew water flowing down in addition to the dew water condensed in the area. In consideration of these, it is preferable to determine the size of the fin 38 in each region.
[0092]
Next, a third embodiment of the present invention will be described with reference to the drawings. Note that the same components as those in the first and second embodiments are denoted by the same reference numerals, and description thereof is omitted as appropriate.
[0093]
In each of the embodiments described above, the fins 38 are formed of flat plates having no irregularities for the main purpose of minimizing the air flow resistance.
[0094]
However, the flat fins 38 having no irregularities can reduce the flow resistance of air, but are not preferable from the viewpoint of heat exchange efficiency.
[0095]
This is because air flows along the fins 38 arranged in parallel, so that heat exchange proceeds in the air in contact with the fins 38, but heat exchange does not proceed so much in the air located substantially in the middle of the fins 38. It is. Such a state in which air flows in a phase is referred to as a phase flow.
[0096]
Therefore, in the present embodiment, as shown in FIG. 8, a plurality of turbulent flow guiding portions 42 are provided in a direction perpendicular to the direction of air flow to disturb the air flowing between the fins 38, whereby the air is substantially The heat exchange is made uniform.
[0097]
If a pipe or rod made of the same metal as the fins 38 and the refrigerant tube plate 36 is used as the turbulence guide 42, the advantage is that heat conduction between the fins 38 is promoted while disturbing the flow of air. is there.
[0098]
When a pipe is used as the turbulence guide 42, a carbon dioxide refrigerant may be circulated through the pipe.
[0099]
Note that, as shown in FIG. 9, the fins 38 themselves may be provided with irregularities, cutouts, bends, or the like to disturb the air flow.
[0100]
FIG. 9A illustrates a case where the unevenness 43 is provided in a scaly shape as the shape of the unevenness, FIG. 9B illustrates a case where the notch 44 is provided, and FIG. 45 is provided as an example. FIG. 9D shows a state where the fin 38 of FIG. 9C is viewed from the side.
[0101]
In this manner, by providing the fins 38 with the irregularities 43, the notches 44, the bent portions 45, and the like, the flow of air is disturbed and heat can be exchanged uniformly.
[0102]
【The invention's effect】
As described above, according to the present invention, a compressor that compresses a refrigerant in a drying unit, and a high-temperature side heat exchanger that is supplied with the compressed refrigerant from the compressor and heats air with the heat of the refrigerant And an expansion valve for expanding the refrigerant from the high-temperature side heat exchanger, and a low-temperature side heat exchanger for exchanging heat between the refrigerant from the expansion valve and the air from the air outlet to condense and dehumidify the air. , The drying efficiency can be improved.
[Brief description of the drawings]
FIG. 1 is a side view showing a schematic configuration of a drum type washing and drying machine applied to the description of a first embodiment of the present invention.
FIG. 2 is a configuration diagram of a heat pump circuit.
FIG. 3 is a partially broken perspective view showing a configuration of a high-temperature side heat exchanger and a low-temperature side heat exchanger.
FIG. 4 is a sectional view of the compressor.
FIG. 5 is a partially cutaway perspective view showing a configuration of a high-temperature side heat exchanger and a low-temperature side heat exchanger instead of FIG. 3;
FIG. 6 is a diagram showing the relationship between the flow of air and the flow of refrigerant.
FIG. 7 is a diagram showing a configuration of a low-temperature side heat exchanger applied to the description of the second embodiment.
FIG. 8 is a diagram showing a configuration of a high-temperature side heat exchanger and a low-temperature side heat exchanger applied to the description of the third embodiment.
FIG. 9 is a diagram showing a configuration of a fin used in the high-temperature side heat exchanger and the low-temperature side heat exchanger instead of FIG. 8;
[Explanation of symbols]
1 drum washing and drying machine
3 outer tank
4 drums
6 Air outlet
7 Air inlet
8 Drying unit
9 Duct
10 Compressor
16 Heat pump
17 Blower
18 concave member
26 High-temperature side heat exchanger
27 expansion valve
28 Low-temperature heat exchanger
29 heat exchanger
36 Refrigerant tube plate
37 refrigerant pipe
38 Fins
42 Turbulence induction unit

Claims (5)

The laundry is put in a drum provided in the outer tub, the laundry is washed by rocking the drum, and dehydration is performed when the washing is completed, and then the drum passes through the space between the drum and the outer tub. The drying unit provided in the duct connecting the provided air outlet and the air inlet is driven to dehumidify the air from the air outlet by dew condensation, and heat the dehumidified air to generate hot air. In a drum-type washing and drying machine that dries laundry in the drum by flowing into the drum,
The drying unit, a compressor that compresses a refrigerant,
A high-temperature side heat exchanger that is supplied with a compressed refrigerant from the compressor and heats air with heat of the refrigerant,
An expansion valve for expanding the refrigerant from the high-temperature side heat exchanger,
A heat pump including a low-temperature side heat exchanger for exchanging heat between the refrigerant from the expansion valve and the air from the air outlet to condense and dehumidify moisture in the air. Washing and drying machine. The drum type washing and drying machine according to claim 1, wherein the refrigerant is a carbon dioxide refrigerant. The high-temperature side heat exchanger and the low-temperature side heat exchanger, a plurality of fins that exchange heat with the air,
The refrigerant pipe through which the refrigerant circulates is fixed, and a refrigerant pipe plate to which the fin is fixed is provided, and the refrigerant pipe plate forms a part of the duct. Drum type washer / dryer. The drum type washing and drying machine according to any one of claims 1 to 3, wherein the high-temperature side heat exchanger is provided at a position where water is not immersed during washing or rinsing. The drum type washing and drying machine according to any one of claims 1 to 4, wherein the low-temperature side heat exchanger is provided at a position where water is not immersed during washing or rinsing.

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