JP2008104478A - Washing/drying machine - Google Patents

Washing/drying machine Download PDF

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Publication number
JP2008104478A
JP2008104478A JP2006287275A JP2006287275A JP2008104478A JP 2008104478 A JP2008104478 A JP 2008104478A JP 2006287275 A JP2006287275 A JP 2006287275A JP 2006287275 A JP2006287275 A JP 2006287275A JP 2008104478 A JP2008104478 A JP 2008104478A
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air
drying
washing
heat pump
blowing
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JP2006287275A
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Inventor
Toru Hirose
Takumi Kida
Masahito Kyo
Koichi Yagi
功一 八木
雅人 姜
徹 廣瀬
琢己 木田
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Matsushita Electric Ind Co Ltd
松下電器産業株式会社
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Priority to JP2006287275A priority Critical patent/JP2008104478A/en
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Abstract

[PROBLEMS] To reduce the noise during drying operation by maintaining the drying performance and reducing the noise from the fan.
SOLUTION: A multi-blade turbofan 16 comprising a main plate 13, an annular support plate 14 and a large number of swept-back blades 15 and a bell mouth-like suction port 17 on the support plate 14 side housing the multi-blade turbofan 16 are provided. The air blowing means 12 is constituted by the casing 20 surrounded by the spiral wall surface 19 with the tongue portion 18 as a starting point around the multi-blade turbofan 16, and the outer tub 3, the rotary tub 5, the heat pump device 33, and the air circulation The pressure loss in the circulation path of the drying air including the road is 100 to 150 mmAq, and the air volume during the drying operation is 2.0 to 3.0 m 3 / min.
[Selection] Figure 1

Description

  The present invention relates to a washing and drying machine that performs washing, dehydration and drying in the same rotating tank using a heat pump.
  A conventional drum type washing and drying machine has a configuration as shown in FIG. Hereinafter, the configuration will be described. As shown in the drawing, a cylindrical water tank 3 elastically supported by a plurality of suspensions 2 is provided inside the housing 1 so that vibrations during washing and dehydration are absorbed by the suspension 2. Inside the water tank 3, a cylindrical, horizontal axis type rotating tank 5 that accommodates an object 4 to be washed or dried (hereinafter referred to as clothing) is rotatably arranged, and a rotating shaft 6 a is rotated by a drive motor 6. To rotate.
  A plurality of baffles (not shown) for stirring clothes are provided on the inner wall of the rotating tub 5, and a plurality of small holes 5 a are provided on the peripheral wall of the rotating tub 5. On the front surface of the housing 1, there are provided an opening 1a through which clothes 4 are taken in and out and a door 7 for opening and closing the opening 1a. Similar openings 3 a and 5 b are also provided on the front side of the water tank 3 and the rotating tank 5, and the opening 3 a of the water tank 3 is water-tightly connected to the opening 1 a of the housing 1 by a bellows 8. The bottom of the aquarium 3 has a drain port 9 for discharging washing water, and is connected to a drain hose 11 via a drain valve 10, and its tip is led out of the machine.
  The blower 12 blows and supplies the warm air heated by the heater 13 from the air supply port 14 into the rotary tank 5. The circulation duct 15 performs dehumidification of the damp drying air that has passed through the rotary tank 5 and the water tank 3, and has one end connected to the exhaust port 16 at the bottom of the water tank 3 and the other end connected to the blower 12. . The water supply valve 17 controls water supply from a water supply hose 18 connected to a tap or the like of a water supply.
  In the above configuration, when the washing operation is performed, the door 7 is opened, the clothes 4 and the detergent are put into the rotating tub 5, and the operation is started. First, when the water supply valve 17 opens the water supply port on the washing water side and a predetermined amount of water is supplied into the water tank 3 and the rotary tank 5, the drive motor 6 is activated and the rotary tank 5 is rotationally driven to perform a washing operation. . After a predetermined time, the drive motor 6 is stopped, the drain valve 10 is opened, and dirty water is drained from the rotary tank 5 and the water tank 3 and drained to a drainage place outside the machine via the drain hose 11. Next, water is supplied to the water tank 3 and the rotary tank 5 in the same manner as described above, and a rinsing operation is performed. When the rinsing is completed, the drain valve 10 is opened and drained, and then the rotating tub 5 is rotationally driven by the drive motor 6 at a high speed, whereby the clothes 4 are dehydrated.
  When the washing operation is completed as described above, the drying operation is started. In the drying process, while the rotating tub 5 is driven to rotate at a low speed by the drive motor 6 and the clothes 4 are stirred, the air blown in the direction of the arrow 19 by the blower 12 is heated by the heater 13 to become warm air, and the air supply port 14 into the rotary tank 5. This hot air takes away moisture from the garment 4, then passes through the water tank 3 through the small hole 5 a of the rotating tub 5 and reaches the circulation duct 15 through the exhaust port 16.
  At this time, the water supply valve 17 opens the water supply port on the cooling water side, and cooling water is poured into the circulation duct 15. When the warm air containing moisture from the clothing 4 deprives moisture and passes through the circulation duct 15, the cooling water cools it to cause moisture condensation, and the moist warm air is dehumidified and again as shown by the arrow. Return to the blower 12. This cooling water and dew condensation water is drained out of the machine via the drain valve 10. By circulating hot air through the circulation path of the blower 12, the heater 13, the air supply port 14, the rotary tank 5, the water tank 3, the exhaust port 16, and the circulation duct 15, the clothes 4 in the rotary tank 5 can be dried. it can.
  In the above-described conventional configuration, the heat used for drying the garment 4 is all discarded to the outside by the cooling water of the circulation duct 15 or the heat radiation from the housing 1, and is not reused.
Therefore, a compressor that compresses the refrigerant, a radiator that dissipates the heat of the compressed refrigerant, a throttle means for reducing the pressure of the high-pressure refrigerant, and the reduced-pressure and low-pressure refrigerant generate heat from the surroundings. It has been proposed to provide a clothes dryer with a heat pump device in which a refrigerant is circulated through a pipe line so that the refrigerant circulates (see, for example, Patent Document 1). According to this configuration, it has been found that the amount of heat released to the outside can be recovered and the clothes can be effectively dried using energy.
JP 7-178289 A
  However, by providing the heat pump device, not only a normal duct resistance but also a resistance by the heat pump device is added in the blower circuit which is a circulation path of the drying air. In addition, in the washing and drying machine, a filter for removing dust and the like from clothes is provided, and in order to reduce the size of the housing, a heat pump device and a blower are installed in a limited space in the housing. When trying to provide, by reducing the duct cross-sectional area of the blower circuit, miniaturizing the heat pump device, and by taking measures such as filling the fin pitch to improve the performance of the heat absorber and heat radiator in the heat pump device, The blowing resistance of the duct in the blowing circuit increases.
  Furthermore, in the case of the washing and drying machine, since the blower circuit is in a closed state in which the blower circuit is almost completely closed and circulated, there is a factor that the duct resistance is increased due to this. Under these conditions, the blower used is required to have a small size, high pressure, and high air volume in order to dry clothes as quickly as possible.
  In general, as a small-sized, high-pressure, high-air-volume blower, a fan having a multi-blade and a blade shape inclined forward with respect to the rotation direction (hereinafter, referred to as a multi-blade forward-inclined fan) is used. However, the multi-blade forward-tilting fan tends to cause separation between the blades. For this reason, when the pressure-air volume characteristic (QH characteristic) is drawn as a graph (the horizontal axis is the air volume and the vertical axis is the pressure), the curve There is a region with a positive slope (the curve is mountain-shaped) or a region that is horizontal to the airflow axis, so that the operating pressure point of the blower is positive or When in the position, the air flow may fluctuate and become unstable (hereinafter referred to as surging phenomenon). Therefore, the multi-blade forward tilt fan tends to increase noise.
  The present invention solves the above-described conventional problems, and aims to maintain the drying performance, reduce the noise from the fan, and reduce the noise during the drying operation.
In order to solve the above-described conventional problems, the washing and drying machine of the present invention includes a multiblade turbofan including a main plate, an annular support plate, and a large number of swept wings, and the multiblade turbofan. A casing having a bell mouth suction port on the support plate side, and surrounding the multi-blade turbofan with a spiral wall surface around the tongue, and the outer tank, the rotary tank, and the heat pump The pressure loss in the circulation path of the drying air including the apparatus and the air circulation path is 100 to 150 mmAq, and the air volume during the drying operation is 2.0 to 3.0 m 3 / min.
  As a result, it is small and satisfies performance conditions such as required pressure and air volume, maintains the drying performance, and can reduce the noise during the drying operation.
  The washing / drying machine of the present invention can maintain the drying performance and reduce noise during the drying operation.
According to a first aspect of the present invention, there is provided an outer tub elastically supported by a casing, a rotating tub rotatably provided in the outer tub, a driving means for rotating the rotating tub, dehumidification and heating of clothes drying air. A heat pump device for supplying air, an air circulation path for supplying and circulating the air heated by the heat pump device, and a blowing means for blowing drying air to the air circulation path, the blowing means Has a multi-blade turbofan composed of a main plate, an annular support plate and a large number of swept wings, and a bell mouth-like suction port on the side of the support plate that accommodates the multi-blade turbofan. The casing is surrounded by a spiral wall surface starting from the tongue, and the pressure loss in the drying air circulation path including the outer tank, the rotating tank, the heat pump device, and the air circulation path is 100 A 150MmAq, by air volume of the drying operation was 2.0~3.0m 3 / min, as compared compact at high pressure, a multiblade anteversion fan with the performance of the high air volume, delamination between wings The surging phenomenon as shown in the above problem can be eliminated, and the noise performance can be improved. Further, the fan has a pressure loss in the circulation path of the drying air including the outer tank, the rotary tank, the heat pump device, and the air circulation path, even under a condition where the pressure loss is as high as 100 to 150 mmAq. Airflow of 2.0 to 3.0 m 3 / min (approximately the same size as a multi-blade forward-tilting fan) to satisfy about 140 minutes, which is an index of time required from washing to drying required by the user (drying at that time The temperature of the working air can be 60 to 75 ° C.). As a result, even when the pressure loss in the circulation path of the drying air is high, it is possible to reduce the noise during the drying operation by maintaining the drying performance and reducing the noise from the fan.
  In the second invention, in particular, the heat pump device according to the first invention is provided at the lower back of the housing, and the air circulation path of the heat pump device is provided so as to open the suction port of the air blowing device. Noise is reduced by muting the noise on the intake side with a heat pump device, and the noise is further reduced by moving the heat pump device and the fan that are the sound source during drying operation away from the ears of the user who uses the washing dryer. Can be difficult to hear.
  The third invention, in particular, by setting the outer diameter of the fan of the first or second invention to 130 to 140 mm, without reducing the size of the outer tub or the heat pump device or increasing the housing, The blowing means can be provided in a limited space, the noise performance of the blowing means can be improved, the drying performance can be maintained, and the noise during the drying operation can be reduced.
  In particular, the fourth aspect of the invention relates to the rotational speed of the blower means by separating the operational rotational speed of the blower means of any one of the first to third inventions from the operational rotational speed of the compressor by at least 10 Hz or more. In addition, it is possible to eliminate noise caused by beating caused by the closeness of the operation speed of the compressor, and it is possible to reduce noise during the drying operation.
  In the fifth aspect of the invention, in particular, the operating rotational speed of the compressor according to any one of the first to fourth inventions is set to 20 to 90 Hz, and the operating rotational speed of the blower unit is set to 100 Hz or more, so that the drying operation is performed. Without being affected by the rotational speed of the compressor, which fluctuates depending on the air volume and the surrounding environment, it is possible to eliminate the noise caused by the beating caused by the proximity of the rotational speed of the blower and the operational rotational speed of the compressor, and the drying performance The noise during the drying operation can be reduced.
  Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the present invention is not limited to the embodiments.
(Embodiment 1)
FIG. 1 is a sectional view of a washing / drying machine according to a first embodiment of the present invention, and FIG. 2 is a rear view thereof. FIG. 3 is a view showing a multiblade turbofan, and FIG. 4 is a view showing a blowing means.
  As shown in FIGS. 1 and 2, a cylindrical outer tub 3 elastically supported by a plurality of suspensions 2 is provided inside the housing 1, and vibration during washing and dehydration is absorbed by the suspension 2. . Inside the outer tub 3, a cylindrical rotating tub 5 that accommodates the clothing 4 is rotatably provided and is driven to rotate by a drive motor 6. The rotating tub 5 becomes a laundry room in the washing process, and becomes a drying room in the drying process. Here, the outer tub 3 and the rotating tub 5 are provided in the casing 1 so as to be inclined so that the back surface is lowered from the front surface, and the rotation axis direction of the rotating tub 5 is inclined 20 to 30 degrees from the horizontal direction. (In the outer tub 3, the opening 3a may be installed horizontally with respect to the ground). On the front surface of the housing 1, there are provided an opening 1a for taking in and out the garment 4 and a door 7 for opening and closing the opening 1a.
  Similar openings 3 a and 5 b are also provided on the front side of the outer tub 3 and the rotating tub 5, and the opening 3 a of the outer tub 3 is water-tightly connected to the opening 1 a of the housing 1 by a bellows 8. The bottom of the outer tub 3 has a drain port 9 for discharging washing water and is connected to a drain valve 10. Moreover, the overflow tank 50 is provided in the outer tank 3, and when water is supplied to a predetermined water level or higher, the overflowed water flows to the drainage hose 11 via the overflow hose 51 and is discharged outside the apparatus. .
  As shown in FIGS. 3 and 4, the air blowing means 12 includes a multiblade turbofan 16 (the number of blades is omitted in the figure) comprising a main plate 13, an annular support plate 14, and a large number of retracted blades 15, and the multiblade turbofan. The casing 20 has a bell mouth-like suction port 17 on the side of the support plate 14 that accommodates 16 and is surrounded by a casing 20 surrounded by a spiral wall surface 19 with a tongue 18 as a starting point. .
  Further, as shown in FIG. 1, the empty space 60 in the housing 1 at the lower back of the outer tub 3 includes a heat absorber 30, a radiator 31, and a compressor 32 that are used as a heat source for heating the drying air. A heat pump device 33 is provided. The heat absorber 30 and the heat radiator 31 are fin-and-tube heat exchangers that perform heat exchange between the refrigerant of the heat pump device and the drying air.
  About the installation place of the ventilation means 12, it installs by attaching to the side surface of the heat pump apparatus 33 provided in the back lower part in the housing | casing 1, as shown in FIG. This is configured such that the air inlet 17 of the air blowing means 12 is opened in the heat pump device 33 and the air flowing through the heat absorber 30 and the heat radiator 31 reaches the air inlet 17 of the air blowing means 12. ing.
  The air blowing means 12 communicates with an air supply duct 21 (air circulation path) provided on the outer surface of the outer tub 3, and blows drying air that has entered from the air supply duct inlet 22 of the air supply duct 21 in the direction of arrow i. The air is supplied from the air supply port 23 into the rotary tank 5. Further, an exhaust duct 25 (air circulation path) communicating with an exhaust port 24 provided above the outer tub 3 is provided on the outer surface of the outer tub 3, and passes through the rotary tub 5 and the outer tub 3 to be an exhaust port 24. The air coming out of the air flows in the direction of arrow B and is led out from the exhaust duct inlet 26 to the exhaust duct outlet 27.
  The air blowing means 12 and the air supply duct inlet 22 communicate with each other via an air supply hose 41 made of a bellows-like stretchable flexible material. In this way, the vibration of the outer tub 3 is prevented from being transmitted to the heat pump device 33.
  A lint filter 43 made of a synthetic fiber net or the like is detachably provided as a filter means for removing foreign substances in the air in the middle of the air circulation path. As described above, the heat pump device 33 is provided in the lower portion of the back surface in the housing 1 and further provided on the side surface so that the suction port 17 of the air blowing means 12 is opened, thereby effectively utilizing the empty space 60 in the housing 1. In addition, a washing and drying machine can be configured in a compact manner.
  Further, regarding the noise reduction during the drying operation, the noise due to the intake air generated at the suction port 17 side of the air blowing means 12 is silenced by the heat pump device 33 acting as a silencer, and further becomes a sound source during the drying operation. By moving the heat pump device 33 and the air blowing means 12 as far as possible from the position of the user's ear, noise can be made difficult to hear and the noise performance during the drying operation of the washing dryer can be improved. Further, the noise on the discharge port side of the blowing means 12 is also silenced by the outer tub 3 acting as a silencer.
  Next, the pressure loss in the air path of the drying air in the washing and drying machine as described above will be described. In the case of the washing and drying machine using the heat pump device 33 as described above, in order to provide the heat pump device 33 and the air blowing means 12 in a limited space in the housing 1, the duct cross-sectional area of the air blowing circuit is reduced, or the heat pump By reducing the size of the device 33 and improving the performance of the heat absorber 30 and the heat radiator 31 in the heat pump device 33, the duct resistance in the blower circuit tends to increase due to measures such as closing the fin pitch.
  Moreover, pressure loss increases also when said lint filter 43 becomes resistance of an air path. Furthermore, in the case of a washing / drying machine, since the blower circuit is in a closed state in which the blower circuit is almost completely closed and circulated, for example, when pressure fluctuation occurs somewhere in the blower circuit, Therefore, there is a factor that the pressure loss increases due to this.
  Actually, in the case where the washing and drying machine is configured as shown in FIGS. 1 and 2 in the present invention, the configuration of the air path such as the length of the air path of the air circulation path, the cross-sectional area, the bent part, the enlarged part, the reduced part, etc. The pressure loss is calculated in consideration of the factors as follows (the size (outside dimension) of the washer / dryer casing at this time is about 650 mm wide, about 700 mm deep, and 1000 to 1100 mm high. (This is the standard size of a laundry dryer for clothing with a capacity of 8 to 9 kg currently on the market).
  As shown in FIGS. 5 and 6, the air circulation path of the washing and drying machine shown in FIGS. 1 and 2 was divided into portions A to F, and the pressure loss in each portion was calculated. The components of the air passages found in the portions A to F are: A: bellows shape of the air supply hose, B: straight portion and bent portion of the air supply duct, C: rotating tank, D: exhaust hose The bellows shape, the straight part of the exhaust duct, the bent part, E: exhaust duct, F: heat pump device, the pressure loss in each component was calculated with reference to the following.
(Straight part of the air passage)
Pressure loss = λ × L × ρ × v 2/2 / d
Where λ is the coefficient of friction, L is the duct length, ρ is the air density, v is the flow velocity, d is the diameter in the case of a circular cross section, otherwise d = 4 m, and m = (duct cross sectional area) / ( The length of the duct circumference in the duct section). The coefficient of friction λ is a function of the Reynolds number and the duct wall roughness.
(Wind bellows)
Pressure loss = λ × L × ρ × v 2/2 / d
(Enlarged part of the air path)
Pressure loss = (1- (A1 / A2) ) 2 × ρ × V1 2/2
Here, A1 is the upstream area, A2 is the downstream area, and V1 is the upstream flow velocity.
(Reduction part of wind path)
Pressure loss = η × ρ × V2 2/ 2
Here, η is a loss coefficient and is calculated from the following equation.
η = 0.43116−0.172 × (A2 / A1) −0.6285 × (A2 / A1) 2 + 0.371 × (A2 / A1) 3
V2 is a downstream flow velocity.
(Bending part of the airway)
Pressure loss = σ × ρ × v 2/ 2
σ = 0.0052 × 0.000871 × (β) + 0.0001472 × (β) 2
β is a turning angle.
For the pressure loss of the heat pump device 33 and the outer tub 3 (rotary tub 5), numerical values obtained by experiments were used.
  As mentioned above, the pressure loss of each part of A to F was calculated from these equations, and as a result of totaling each, the pressure loss in the circulation path was about 100 mmAq. With respect to the value obtained by this calculation, in the washer / dryer actually configured as in the present embodiment, the pressure loss in the entire air circulation path was measured and found to be about 150 mmAq. This is because the calculation did not consider the pressure loss due to the sudden expansion part of the fine air passage, the sudden reduction part of the air passage, the diffuser part, etc., and the pressure loss of the filter part was not considered. .
  From these facts, in the configuration shown in the present embodiment and considering the outer dimensions as shown above, even in an actual washer / dryer, a sudden expansion / reduction portion of the duct, etc. It is considered that the pressure loss of the air circulation path can be made to be almost equal to the calculation result by eliminating as much as possible or reviewing the structure of the lint filter 43 part. Therefore, when the washing / drying machine is configured as in the present embodiment, the pressure loss in the air passage is considered to be about 100 to 150 mmAq.
In addition, washing machine dryers using heat pump devices are characterized by being able to dry clothing at a low temperature and in a short time compared to those using a heater as a heat source for heating the drying air. When the air temperature is about 60 ° C. to 75 ° C. and the drying time is about 90 minutes, the required air volume is about 2.0 to 3.0 m 3 / min from FIG. 7 showing the drying time and the air temperature. Yes.
  Here, the reason why the drying time is 90 minutes will be described. In a conventional washing and drying machine, the time required for washing clothes and completing the drying operation is approximately 190 minutes. However, since it takes too long for the user to wash and dry the clothes in the morning, it is necessary to wash the clothes at night in order to use the washing dryer to complete the clothes from washing to drying. More opportunities to do. However, washing at night is very problematic from the viewpoint of noise, and there is a demand from the user to complete washing until drying in the morning before going out.
  It is said that it takes about 140 minutes for the user to wake up and to finish washing before going out, and it is said that they need to be completed in about 140 minutes. When considering the process of drying, the conventional washing and drying machine requires about 50 minutes to dehydrate, and therefore, drying needs to be completed in about 90 minutes.
  Next, the reason why the temperature of the drying air is set to 60 ° C. to 75 ° C. will be described. It is said that the lower the temperature of the drying air, the less likely it will be wrinkled on the clothing, but if it is too low, it will take longer to dry under the same air flow conditions, and shorten the drying time. Even if you try to increase the air volume for this reason, the noise will increase by the increased air volume. Moreover, it is very difficult to make it 60 degrees C or less also from the point of the dehumidification capability of a heat pump apparatus.
Next, the reason for being 75 degrees C or less is demonstrated. Although depending on the type of refrigerant, the alternative chlorofluorocarbon refrigerant used in the present embodiment has a critical point of about 80 ° C., and if used at a temperature higher than that, the efficiency becomes poor. For that reason, it is 75 ° C. In addition, CO 2 is currently used as a refrigerant, but there is a problem that the cost is increased.
Next, the multiblade turbofan 16 used in the present invention will be described. Generally, when selecting the type of fan, it is selected from the specific speed Rs shown in the following equation (1).
Rs = N × Q 1/2 / (Pt / γ) 3/4 (1)
Here, N represents the rotational speed [RPM] of the fan, Q represents the air flow [m 3 / min], Pt represents the total pressure [mmAq] of the fan, and γ represents the specific weight of air [kg / m 3 ]. In this formula (1), values of pressure loss (120 mmAq), air volume (2.0 to 3.0 m 3 / min), and rotation speed (= 5000 RPM), which are approximate conditions during the drying operation of the washing machine of the present invention Is substituted (for example, a pressure loss of 120 mmAq and an air volume of 2.0 m 3 / min are substituted),
Rs = 5000 × 2.0 1/2 /(120/1.2) 3/4 ≈230
In view of the specific speed value and the small size, the selected fan is a multi-blade forward tilt fan. However, as described above, the multi-blade forward tilt fan tends to increase noise due to a surging phenomenon related to separation between blades.
  Therefore, in the present invention, a turbo fan having multiple blades and reverse blades is used as a fan to be used. Compared with a multi-blade forward tilt fan of the same size, the turbo fan has a feature that the flow of wind between the blades is easy to follow along the blades and is smooth, so that separation between the blades is difficult to occur and surging phenomenon is unlikely to occur. . Also, efficiency is good. However, on the other hand, pressure and air volume are not easily generated. Therefore, compared with a multi-blade forward tilt fan of the same size, the performance of pressure and air volume was improved by increasing the number of blades and increasing the number of blades.
  Here, FIG. 8 shows a diagram showing the tendency of the QH characteristics (pressure-air flow characteristics) of the multi-blade forward tilt fan, the turbo fan, and the multi-blade turbo fan of the same dimensions. The multi-blade forward tilt fan is indicated by a solid line, the turbo fan is indicated by a broken line, and the multi-blade turbo fan is indicated by a dotted line. From FIG. 8, the multi-blade forward tilt fan has a region where the curve is horizontal in a part of the region. This is thought to be due to a surging phenomenon in which the pressure and air volume fluctuate. However, the cause of this surging phenomenon is that the multi-blade forward tilt fan tends to cause separation between the blades, and a vortex is generated at this separation point. As a result, pressure fluctuations occur and the air flow fluctuates. As a result, noise increases. Therefore, in order not to cause separation between the blades, if a turbo fan in which the flow of wind between the blades is easy to follow along the blades is used, the separation between the blades is eliminated and the surging phenomenon hardly occurs.
  However, as shown in FIG. 8, a turbo fan of the same size and the same number of blades cannot obtain the required performance at the operating point as compared with the multi-blade forward tilt fan. Therefore, by further increasing the number of blades of this turbo fan (increasing the number of blades compared to a multi-blade forward tilt fan of the same size), the required performance at the operating point can be obtained. Actually, the fan 16 having an outer diameter of 140 mm and the number of blades of 50 blades is changed to 80 to 100 blades (the optimum number of blades depends on the fan inner diameter, the inclination angle of the blades 15 and the height of the blades 15). By doing so, the required performance is obtained as shown in FIG. When the number of blades was increased more than this, the noise performance was worsened. This is considered to be due to the fact that the wind speed between the blades is increased due to the narrow width between the blades. FIG. 9 shows a frequency analysis diagram showing the noise performance of the multi-blade forward tilt fan and the multi-blade turbo fan that have obtained the required performance at this operating point.
  Further, it can be confirmed from FIG. 9 that the noise value is particularly small in the multi-blade turbofan 16 having a noise value near 400 to 4000 Hz. It can be confirmed that the noise performance of the multiblade turbofan 16 of the present invention is improved because the noise of the frequency in this band is relatively easy to hear. Here, the operating point of the fan when measuring the noise characteristics of the fan alone is matched with the operating point when the fan is used in the washing / drying machine. At 400 to 4000 Hz where the noise is reduced, it is considered that the noise is reduced mainly by eliminating the noise caused by the separation between the blades of the fan and the accompanying surging phenomenon.
  Further, the number of blades of the multi-blade turbo fan 16 can be 60 to 100 blades by appropriately changing the fan inner diameter, blade inclination angle, and blade height other than the dimensions under the above-described outer shape. A multiblade turbofan having substantially the same performance as described above can be configured. When the number of blades is 60 or less, the required air volume and pressure performance cannot be obtained. When the number of blades is 100 or more, the width between the blades becomes too narrow, and the wind speed between the blades increases, resulting in noise performance. Becomes worse.
Further, the multiblade turbofan 16 of the present invention has an air flow condition for ending drying within the drying time shown above, even if the pressure loss in the air blowing circuit is 100 to 150 mmAq, from the QH characteristics of FIG. 2.0-3.0m < 3 > / min is satisfy | filled. Further, as shown in FIG. 3, the multi-blade turbofan 16 of the present invention has an annular support plate that is inclined from the inner side of the fan toward the outer side so that the height of the fan becomes smaller. Support plate that is generated when the flow of incoming wind is bent suddenly, so that the wind does not flow to the support plate side, and the support plate side becomes low pressure, and the flow from the main plate side flows back to the support plate side. The peeling at the side can be eliminated, and the noise performance can be further improved.
  The control means 48 controls the washing, dehydration and drying processes by driving the drive motor 6, the drain valve 10, the blower means 12, the compressor 32, and the like.
  Next, the operation of the above configuration will be described. In the washing process, water is supplied until the water level reaches a predetermined water level in the outer tub 3 with the drain valve 10 closed, and the garment 4 and the rotating tub 5 containing the washing water are rotated by the drive motor 6 to wash the garment 4. I do. In the rinsing process after washing, water is supplied into the outer tub 3 as in the washing process, and the garment 4 is rinsed by rotating the rotating tub 5. In the dehydration step, the drain valve 10 is opened to drain water to the outside of the machine, and then the rotating tub 5 containing the clothing 4 is rotated at high speed by the drive motor 6 to dehydrate.
  In the drying process, when the compressor 32 of the heat pump device 33 is operated, the refrigerant is compressed, and this pressure circulates through the radiator 31, the throttle means (not shown), and the heat absorber 30. In the radiator 31, heat is released by the compression of the refrigerant, and in the heat absorber 30, the heat is absorbed by the refrigerant that has been decompressed by the throttle means to become a low pressure. At this time, the air blowing means 12 is activated, and warm air heated by the heat radiation of the radiator 31 is blown from the air supply port 23 into the outer tub 3 and the rotary tub 5 through the air supply duct 21. The rotating tub 5 is rotationally driven by a drive motor 6 and the clothes 4 are stirred up and down.
  The warm air blown into the rotating tub 5 deprives moisture when passing through the gap between the clothes 4, passes through the exhaust duct 24 through the exhaust port 26 of the outer tub 3 and passes through the lint filter 43 in a wet state. Accordingly, foreign matters such as lint are removed, and the heat exchange air passage 28 (air circulation passage) is reached. When the wet warm air passes through the heat absorber 30, sensible heat and latent heat are taken away and dehumidified, and separated into dry air and dehumidified water. The dry air is heated again by the radiator 31 and becomes hot air, passes through the compressor container, and circulates to the blowing means 12.
  By using the heat pump device 33 in this manner, the heat absorbed by the heat absorber 30 can be recovered by the refrigerant and radiated again by the heat radiator 31 to give the garment 4 more heat than the energy input to the compressor 32. As a result, drying time can be shortened and energy can be saved.
  Further, by using the multi-blade turbofan 16 shown above as the air blowing means 12, separation between the blades of a fan that is likely to occur in a multi-blade forward tilt fan that is generally used in a small size, high pressure, and high air volume. By eliminating the surging phenomenon, the noise from the blowing means 12 can be reduced. Further, even under a pressure loss of 100 to 150 mmAq in the air passage, performances such as pressure and air volume satisfy the necessary capabilities.
As described above, in the present embodiment, by using the multiblade turbofan 16 as the blower unit 12 of the washing and drying machine having the heat pump device 33, the blower unit 12 is accommodated in the housing 1 in a compact manner, and the drying operation is performed. Even under the condition that the pressure loss in the blower circuit through which drying air sometimes passes is 100 to 150 mmAq, it is possible to produce an air volume of 2.0 to 3.0 m 3 / min to satisfy a drying time of about 90 minutes, In addition, the noise performance can be improved as compared with the case where the multi-blade forward tilt fan is used. As a result, the noise can be reduced while maintaining the drying performance.
(Embodiment 2)
In the second embodiment of the present invention, by limiting the outer diameter of the multiblade turbofan 16 to 130 mm to 140 mm, without increasing the outer dimensions of the washing and drying machine shown in the first embodiment, The blowing means 12 can be accommodated in a compact manner, and the noise performance of the blowing means 12 can be improved.
  The reason why the outer diameter of the multiblade turbofan 16 is 130 to 140 mm will be described. Here, FIG. 10 is a left side view of the washing / drying machine showing the installed state of the blowing means 12. As shown in the first embodiment, the external dimensions of the washing / drying machine depend on the washing capacity of the clothes, but if the clothes capacity is 8 to 9 kg from the user's desire for a large washing capacity, the width is approximately It is 650 mm, depth is about 700 mm, and height is about 1000 to 1100 mm.
  Further, as shown in the first embodiment, when the heat pump device 33 is installed at the lower back of the housing 1 and the air blowing means 12 is to be installed on the side surface, the size of the air blowing means 12 is most limited. This is the H part in FIG. Considering that the dimensions of the washing / drying machine are as described above, and that the minimum required size of the rotating tub 5 (outer tub 3) for housing the garment 4 is roughly determined, the blowing means 12 (casing 20) The length of the H part is about 200 mm.
  In FIG. 10, a little space is provided between the blowing means 12 and the outer tub 3, but this is because the rotating tub 5 vibrates during dehydration, so that the rotating tub 5, the blowing means 12 and the heat pump device 33 are moved. This is to prevent collisions. In order to increase the installation space of the air blowing means 12 beyond this, it is necessary to increase the size of the casing 1 in the depth direction. This is because the size of the waterproof pan provided for installing the washing machine at home is determined. Therefore, it is almost impossible to increase the size in the depth direction.
From the above, the length H of the H portion of the blowing means 12 is limited to about 200 mm at the maximum. Here, the length of the H portion of the blowing means 12 is calculated by dividing H into r1 and r2 as shown in FIG. 11 (H = r1 + r2). FIG. 11 is a view showing the air blowing means 12. r1 and r2 are calculated from the following equations.
r = D / 2 + tan (αc) × π × D × θ / 360
Here, r1 is calculated by substituting θ = 360 °, and r2 is calculated by substituting θ = 180 °. Regarding other coefficients, D is the outer diameter of the fan 16, and αc is the enlarged angle of the casing 20. θ takes an angle as shown in FIG.
  As can be seen from this equation, the dimensions of the casing 20 can be calculated from the outer diameter D of the fan 16 and the enlarged angle αc. Here, when r1 and r2 are calculated assuming that the dimension H of the casing 20 is 200 mm or less and is the closest value, the outer diameter D of the fan 16 is 140 mm and the expansion angle αc is 5 °, r1≈108 and r2 respectively. = 89, and from these, H = r1 + r2 = 197 (<200). In order to increase the outer diameter D of the fan 16 further, the enlargement angle αc may be further reduced. However, the performance of the air blowing means 12 is deteriorated. From the above, in order to make the dimension of the H part of the casing 20 200 mm or less, the outer diameter D of the fan 16 can be configured to be 140 mm at the maximum.
  Next, the reason why the lower limit of the outer diameter of the fan 16 is set to 130 mm will be described. In the case where the outer diameter of the fan 16 is set to 130 mm or less and the rotational speed of the fan 16 is increased in order to obtain the same performance as the outer diameter of 140 mm, the noise value of the fan 16 alone increases by 2 dB or more. When the fan diameter was reduced between 130 mm and 140 mm in outer diameter, the increase in noise value was within 2 dB even when the rotational speed was increased to obtain the required performance. The cause of the increase in the noise value when the outer diameter of the fan 16 is reduced may be due to the increase in the rotational speed of the fan 16, but the air path area between the blades is reduced by reducing the outer diameter. Therefore, the wind speed between the blades is increased, and therefore, it is considered that the noise value is increased due to the sound component that increases with the sixth power of the wind speed.
  From this, it is considered that when the outer diameter is 130 mm or less, the influence of the increase in the wind speed between the blades becomes stronger, and the noise value is significantly increased. If the amount of increase in the noise value is 2 dB or more, it seems that it is felt quite loud when actually heard. For the above reasons, the outer diameter of the fan 16 is set to 130 to 140 mm.
  As a result of the above, the air blowing means 12 is compactly installed without increasing the size of the housing 1 or by reducing the size of the heat pump device without reducing its capacity or increasing pressure loss. As a result, the noise performance can be improved while maintaining the drying performance.
(Embodiment 3)
In the third embodiment of the present invention, in the washer / dryer shown in the first or second embodiment, the operating rotational speed of the blowing means 12 during the drying operation is separated from the operating rotational speed of the compressor 32 by at least 10 Hz or more. As a result, noise caused by beating caused when the operating rotational speed of the blowing means 12 and the operating rotational speed of the compressor 32 are close to each other can be eliminated, and noise during the drying operation can be reduced.
  The beat phenomenon will be described. It is assumed that two objects are periodically moving at frequencies (frequency) fa and fb (unit: Hz) and amplitudes Xa and Xb. When the two frequencies fa and fb are close to each other and the difference is much smaller than fa and fb, a beat phenomenon occurs. The beat occurs at the frequency | fa−fb | Hz, the maximum amplitude | Xa + Xb |, and the minimum amplitude | Xa−Xb |. This becomes a roar and generates noise. Therefore, in order to prevent such noise from occurring, it is necessary to prevent the frequencies of the two objects from coming close to each other.
  In the washing and drying machine using the heat pump device 33 as shown in the present invention, the compressor 32 in the heat pump device 33 and the air blowing means 12 are simultaneously operated during the drying operation. And when the operation | movement rotation speed of the compressor 32 and the ventilation means 12 adjoins, the above beats arise and it becomes a noise. Here, in order to prevent the beat from occurring, it is necessary to prevent the compressor 32 and the air blowing unit 12 from coming close to each other. Actually, in order to prevent the beat from occurring, it is necessary to separate the operating rotational speeds of the compressor 32 and the air blowing means by 10 Hz or more. If it falls below that, a beat will occur.
  When the heat pump device 33 is used in a blower circuit in which air is circulated during the drying operation of the washing dryer as in the present invention, first, the compressor 32 is used until the temperature of the drying air reaches a target value (about 70 ° C.). Moves at a high rotational speed (90 Hz). Thereafter, after the air temperature reaches the target value, the rotational speed is changed depending on conditions such as the air volume of the drying air and the ambient temperature. During the drying operation, clogging occurs due to lint of clothing in the air circulation path, pressure loss increases and the air volume decreases, and as a result, heat exchange cannot be performed and the temperature of the drying air rises. Too much.
  In order to suppress this, control is performed to reduce the rotational speed of the compressor 32. Actually, during the drying operation, the rotational speed of the compressor 32 varies between about 20 and 90 Hz. Therefore, in order to separate the operating rotational speed of the air blowing means 12 and the compressor 32 by 10 Hz or more, it is necessary to set the rotational speed of the air blowing means 12 to 10 Hz or less or 100 Hz or more. In the small fan 16 as shown, since the necessary air volume cannot be produced, the rotational speed of the air blowing means 12 must be 100 Hz or more.
  From the above, by setting the operation speed of the air blowing means 12 to 100 Hz or more, the air blowing means 12 can achieve the necessary capacity, and the rotation of the compressor 32 and the air blowing means 12 during the drying operation. The noise performance can be improved by not generating the beat phenomenon caused by the close proximity of the numbers.
  As described above, the washing and drying machine according to the present invention can improve the noise performance without deteriorating the drying performance when drying clothes, and is useful for uses such as a washing and drying machine equipped with a heat pump device. .
Sectional drawing of the washing-drying machine in Embodiment 1 of this invention Rear view of the washer / dryer (A) Plan view of the multi-blade turbofan of the washer / dryer (b) Side view (A) Plan view of air blowing means of the washing and drying machine (b) Side view Sectional drawing which shows division | segmentation of the air circulation path of the said washing dryer Rear view showing division of air circulation path of the washing and drying machine Relationship diagram between drying time and air condition of the washer / dryer PQ diagram of the multi-blade turbofan of the washer / dryer Noise frequency analysis diagram of the multi-blade turbofan of the washer / dryer The figure which shows the installation state of the ventilation means in Embodiment 2 of this invention. Enlarged view of the air blowing means of the washer / dryer Cross-sectional view of a conventional washing and drying machine
Explanation of symbols
DESCRIPTION OF SYMBOLS 1 Housing | casing 3 Outer tank 5 Rotating tank 6 Drive motor 12 Blower means 13 Main plate 14 Support plate 15 Backward blade 16 Multiblade turbofan 17 Suction port 20 Casing 33 Heat pump device

Claims (5)

  1. An outer tub elastically supported by a housing, a rotating tub rotatably provided in the outer tub, a driving means for rotating the rotating tub, a heat pump device for dehumidifying and heating clothes drying air, An air circulation path for supplying and circulating the air heated by the heat pump device, and a blowing means for blowing drying air to the air circulation path; A multi-blade turbofan comprising a support plate and a large number of swept wings, and a bell mouth-like suction port on the side of the support plate that accommodates the multi-blade turbofan, with the tongue around the multiblade turbofan As a casing surrounded by a spiral wall surface, and a pressure loss in a circulation path of drying air including the outer tank, the rotary tank, the heat pump device, and the air circulation path is 100 to 150 mmA. , And the air volume at the time of drying operation was 2.0~3.0m 3 / min washing and drying machine.
  2. The washing / drying machine according to claim 1, wherein a heat pump device is provided in a lower part of the back surface of the housing, and a suction port of the blowing means is provided in an air circulation path of the heat pump device.
  3. The washing / drying machine according to claim 1 or 2, wherein the fan has an outer diameter of 130 to 140 mm.
  4. The washing / drying machine according to any one of claims 1 to 3, wherein the operating rotational speed of the blowing means is separated from the operating rotational speed of the compressor by at least 10 Hz.
  5. The washing / drying machine according to any one of claims 1 to 4, wherein an operation rotation speed of the compressor is set to 20 to 90 Hz, and an operation rotation speed of the blowing unit is set to 100 Hz or more.
JP2006287275A 2006-10-23 2006-10-23 Washing/drying machine Pending JP2008104478A (en)

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JP2010063697A (en) * 2008-09-11 2010-03-25 Panasonic Corp Drum-type washing/drying machine
JP2010063699A (en) * 2008-09-11 2010-03-25 Panasonic Corp Drum washing and drying machine
JP2010063700A (en) * 2008-09-11 2010-03-25 Panasonic Corp Drum-type washing/drying machine
JP2010119573A (en) * 2008-11-19 2010-06-03 Toshiba Consumer Electronics Holdings Corp Washing and drying machine
JP2012085836A (en) * 2010-10-20 2012-05-10 Panasonic Corp Washing and drying machine
JP2012143580A (en) * 2012-03-14 2012-08-02 Hitachi Appliances Inc Drying machine
JP2013046651A (en) * 2011-08-29 2013-03-07 Hitachi Appliances Inc Drum type washing machine
WO2013111589A1 (en) * 2012-01-27 2013-08-01 パナソニック株式会社 Drum-type washing and drying machine
WO2014024355A1 (en) * 2012-08-06 2014-02-13 パナソニック株式会社 Dryer device
CN104593992A (en) * 2013-10-30 2015-05-06 海尔集团公司 Wave-wheel type heat pump washing and drying integrated machine and drying method

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Publication number Priority date Publication date Assignee Title
JP2010063699A (en) * 2008-09-11 2010-03-25 Panasonic Corp Drum washing and drying machine
JP2010063700A (en) * 2008-09-11 2010-03-25 Panasonic Corp Drum-type washing/drying machine
JP2010063697A (en) * 2008-09-11 2010-03-25 Panasonic Corp Drum-type washing/drying machine
JP2010119573A (en) * 2008-11-19 2010-06-03 Toshiba Consumer Electronics Holdings Corp Washing and drying machine
JP2012085836A (en) * 2010-10-20 2012-05-10 Panasonic Corp Washing and drying machine
JP2013046651A (en) * 2011-08-29 2013-03-07 Hitachi Appliances Inc Drum type washing machine
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CN104080966A (en) * 2012-01-27 2014-10-01 松下电器产业株式会社 Drum-type washing and drying machine
WO2013111589A1 (en) * 2012-01-27 2013-08-01 パナソニック株式会社 Drum-type washing and drying machine
JP2012143580A (en) * 2012-03-14 2012-08-02 Hitachi Appliances Inc Drying machine
JP2014030665A (en) * 2012-08-06 2014-02-20 Panasonic Corp Drying apparatus
WO2014024355A1 (en) * 2012-08-06 2014-02-13 パナソニック株式会社 Dryer device
CN104334787A (en) * 2012-08-06 2015-02-04 松下知识产权经营株式会社 Dryer device
CN104593992A (en) * 2013-10-30 2015-05-06 海尔集团公司 Wave-wheel type heat pump washing and drying integrated machine and drying method
WO2015062148A1 (en) * 2013-10-30 2015-05-07 海尔集团公司 Pulsator-type heat pump combined washer-dryer and drying method

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