Patent Application
20090211309
The present invention relates to a drum type washing-drying machine in which a heat pump mechanism is used to dry clothes in a drum.
General drum type washing-drying machines are constructed so that a drum accommodating clothes is controlled to be rotated, thereby being capable of automatically carrying out steps of wash, rinse. dehydration and drying.
Furthermore, hot air is supplied into the drum in the drying step so that the clothes are dried.
Conventional drum type washing-drying machines are provided with an electric heater such as a sheathed heater or honeycomb heater serving as a heat source, whereby air is heated by the electric heater into hot air. Furthermore, the drum type washing-drying machine is provided with a heat exchanger which is adapted to dehumidify hot air which has already depleted the clothes in the drum of water content.
However, since the system of heating air by an electric heater consumes a large amount of heat energy, there is a possibility that the consumption of heat energy may result in a huge burden for general household. A drum type washing-drying machine has therefore been suggested which employs a heat-pump mechanism to heat air. This type of drum type washing-drying machine is described, for example, in Japanese Laid-open Patent Application No. 2004-135715 (JP-2004-135715A).
The above-described heat pump mechanism comprises a construction circulating a refrigerant by a compressor into a condenser, capillary tube (throttle) and evaporator in this sequence. A hot-air circulation path is defined along an outer periphery of a water tub. The condenser and evaporator both constituting the heat pump mechanism are disposed in the circulation path. Hot air is then produced by heat exchange between air circulating through the circulation path and the condenser, whereby the hot air is dehumidified by the heat exchange with the evaporator.
However, when the aforesaid heat pump mechanism is employed, the hot air supplied into the drum unavoidably has a low temperature of about 60° C. or below, which temperature is approximately one half of a temperature in the use of an electric heater or lower. As a result, since the drying performance is lowered, a period of the drying step needs to be increased.
Furthermore, even a heat pump can exert substantially the same drying performance as achieved by an electric heater when a flow rate of recirculated air is rendered larger than in the use of an electric heater. For example, when a compressor has a cooling capacity of about 1500 W, a flow rate of circulating air needs to be set to about 3 m3/min. This value is twice to thrice larger than a flow rate of circulating air in the use of an electric heater.
In order that such a high flow rate as noted above may be ensured, the blowing capacity of a blower fan needs to be increased. by rendering the blower fan large-scaled or by increasing a rotational speed of the blower fan. However, the large-scaled blower fan would increase an installation space of the blower fan, whereupon the size of a whole washing machine would be increased increasing the rotational speed of the blower fan would result in an increase in an amount of noise due to rotation of the blower fan.
Furthermore, the circulation air flow has an air-flow resistance proportional to the square of the air-flow velocity. Accordingly, the flow rate of the circulating air can be increased by increasing an area of the circulating air-flow path thereby lowering a mean flow velocity of circulating air. In this case, however, the circulating air-flow path is rendered larger, which results in an increase in the size of the whole washing machine.
An object of the present invention is therefore to provide a drum type washing-drying machine which can reduce the air-flow resistance of a circulation path through which air is recirculated between a hot-air supply unit provided with a heat pump mechanism and a drum, thereby increasing the flow rate of circulating air.
The present invention provides a drum type washing-drying machine comprising a water tub elastically mounted in a washing machine body, a drum rotatably mounted in the water tub, an air supply opening and an air discharge opening both provided in the water tub, a circulation path having both ends connected to the air supply opening and the air discharge opening respectively, a heat pump mechanism including a condenser and an evaporator both disposed in the circulation path, and a blower fan disposed in the circulation path to circulate air between the circulation path and the water tub, characterized by a plurality of branch paths provided between a part of the circulation path where the condenser is located and the air supply opening and/or another part of the circulation path where the evaporator is located and the air discharge opening.
A part of the circulation path is composed of a plurality of branch paths, whereby a flow path area is increased in the drum type washing-drying machine of the invention. Accordingly, an amount of air circulated is increased without rendering the blower large-scaled or increasing the rotational speed of the blower fan, whereupon the drying performance can be improved.
The present invention will be described in more detail with reference to the accompanying drawings.
A cylindrical water tub 3 is provided in the body 1. An annular tub cover 3a is attached to an opening of a front of the water tub 3. The water tub 3 is elastically by elastic supports 7 so as to be inclined diagonally forward. A cylindrical drum 4 is mounted in the water tub 3 so as to be rotatable about an inclined shaft which is inclined diagonally forward. The drum 4 has a front opening to which an annular balance ring 4a is attached. Furthermore, the drum 4 has a peripheral wall formed with a number of through holes 4b. A plurality of baffles 4c (only one being shown) are provided on an inner surface of the peripheral wall of the drum 4. The drum 4 serves as a wash tub, dehydration tub and drying tub.
The central openings of the tub cover 3a and balance ring 4a are opposed to the access opening 1a of the body 1. Hollow cylindrical elastic bellows 5 is connected between the access opening 1a and the tub cover 3a so as to communicate in a watertight manner. As a result, water can be prevented from leaking between the water tub 3 and body 1. Furthermore, clothes or the like can be put into and taken out of the drum 4 through the access opening 1a.
Furthermore, an electric motor 6 (hereinafter, “DD motor”) directly driving the drum 4 is provided on a central rear of the water tub 3. The DD motor 6 comprises a DC brushless motor of the outer rotor type, for example. The DD motor 6 has a rotor 6a to which a rotational shaft 6b is directly connected. The rotational shaft 6b extends through a rear plate of the water tub 3, being connected to a central rear of the drum 4. Accordingly, when the DD motor 6 is energized to be driven, the drum 4 is rotated together with the rotor 6a.
A drain outlet 3b is formed in a lowermost rear part of the water tub 3. A drain pipe 9 is connected via a drain valve 8 to the drain outlet 3b. On the other hand, an air supply opening 20 and an air discharge opening 21 are formed on the upper rear and the upper front respectively. Both ends of a circulation path 10 are connected to the air supply opening 20 and the air discharge opening 21 respectively.
The circulation path 10 includes an air supply path 22 connecting a duct 10a (serving as a heat exchange section) located below the water tub 3, an air supply path 22 located in the rear of the water tub 3 for connecting the rear end of the duct 10a and the air supply opening 20 to each other, and an exhaust path 23 located in front of the water tub 3 for connecting the front end of the duct 10a and the air discharge opening 21 to each other.
An air blower fan 11 is provided in the rear interior of the duct 10a. A condenser 14 and an evaporator 15 both constituting a heat pump mechanism 12 are disposed in an upstream part of the air blower fan 11 in the interior of the duct 10a in turn from the rear.
The heat pump mechanism 12 includes a compressor 13 disposed on the front bottom of the body 1 and a capillary tube (throttle) which is not shown as well as the condenser 14 and the evaporator 15. Refrigerant fed out of the compressor 13 as the result of drive of the compressor is circulated through the condenser 14, capillary tube, evaporator 15 and compressor 13 sequentially in this order. Furthermore, the blowing action of the blower fan 11 circulates air through the circulation path 10, water tub 3 and drum 4 in the direction as shown by arrow A in
A lint filter 19 for trapping lint is provided on an upstream art of the evaporator 15 in a front end interior of the duct 10a. Lint produced in a drying step and flowing into the circulation path 10 can be trapped by the filter 19 before reaching the evaporator 15. As a result, the dehydrating function can be prevented from being reduced due to the adherence of lint to finned tubing or the like, and flow of circulation air can be prevented from being blocked by the adherence of lint to finned tubing. The filter 19 is attachable to and detachable from the front or a side of the body 1 although the construction is not shown in detail. As a result, the filter 19 can be detached from the body 1 to be cleaned when clogged.
Furthermore, in response to the inclined drum 4, the duct 10a is constructed so that the front part thereof where the evaporator 15 is disposed is located higher than the rear thereof where the condenser is disposed. The bottom of the duct 10a has a recess 16 and drain outlet 17 both formed for collecting and draining dehydration fluid produced by heat exchange between the evaporator 15 and air. A dehydration fluid drain pipe 18 is connected to the drain outlet 17. The drain pipe 18 has a downstream end joining a downstream end of the wash liquid drain pipe 9, so that water flowing into the drain pipe 18 is adapted to be spontaneously drained outside the machine. In this case, since the air supply opening 20 and air discharge opening 21 are located at the upper part of the water tub 3, wash fluid or the like can be prevented from flowing into the circulation path.
A concrete construction of the circulation path 10 will now be described with reference to
On the other hand, the air discharge opening 21 is comprised of an arc-shaped opening which spreads right and left from the front ton of the water tub 3. The exhaust path 23 includes branch paths 23a and 23b diverging from air discharge opening 21 into right and left portions of the bellows 5 respectively and bellows 23a at lower end thereof at which the exhaust path 23 is connected to duct 10a. The branch paths 23a and 23b join together at the lower end of the exhaust path 23, communicating with the bellows 23a. A space is defined between the periphery of the bellows 5 and the front panel, of the body 1 in the front of the water tub 3. The branch paths 23a and 23b are disposed utilizing the space in the embodiment. Accordingly, the body 1 need not be extended frontward since the branch paths 23a and 23b are disposed in the front of the water tub 3.
The operation of the drum washing-drying machine will next be described. For example, when a standard washing-drying course starts, steps of wash, rinse, dehydration and drying are automatically carried out sequentially. In this case, the DD motor 6 is inverter-controlled so that the drum 4 is rotated at suitable rotational speeds.
Furthermore, the air blower fan 11 and the compressor 13 are driven in the drying step. As a result, air is circulated between the circulation path 10 and the water tub 3 and the drum 4. Furthermore, high-temperature high-pressure refrigerant flows from the compressor 13 into the condenser 14. After heat exchange has been carried out between the refrigerant and the circulation air in the circulation path 10 (duct 10a), the temperature of the refrigerant is decreased such that the refrigerant is liquefied. Thereafter, the refrigerant passes through the capillary tube and is subsequently decompressed, whereupon the refrigerant assumes a low-temperature low-pressure gas-liquid mixed state, flowing into the evaporator 15.
On the other hand, hot air due to the heat exchange with the condenser 14 flows through the exhaust path 23 by the blowing operation of the air blower fan 11, being supplied through the air supply opening 20 into the water tub 3 and the drum 4. After absorbing water content from clothes in the drum 4, the air is discharged from the air discharge opening 21, flowing through the exhaust path 23 into the duct 10a.
Air discharged out of the air discharge opening 21 is branched into the branch paths 23a and 23b. Thus, since the exhaust path 23 is composed of the branch paths 23a and 23b, the flow path area of the exhaust path 23 is substantially doubled. This increases a flow rate of air flowing from the air discharge opening 21 through the exhaust path 23 toward the duct 10a and accordingly a flow rate of whole circulated air.
Furthermore, air flowing through the branch paths 23a and 23b joins together, thereafter flowing into the duct 23a. Lint is eliminated from air when the air passes through the filter 19. Heat exchange is then carried out between the air and the evaporator 15 so that the air is dehumidified. Dehumidification fluid drops to be collected in the recess 16, thereafter being discharged from the outlet 17 through the drain pipe 18 out of the machine. Air dehumidified by the evaporator 15 flows to the condenser 14, where air is again rendered hot by heat exchange thereby to be supplied through the air supply path 22 and the air supply opening 20 into the drum 4. Air is thus circulated so that the clothes or the like in the drum 4 are dried.
According to the embodiment, the exhaust path 23 connecting the air discharge opening 21 and the duct 10a of the hot air circulation path 10 together is composed of two branch paths 23a and 23b. Accordingly, the flow path area of the exhaust path 23 can be increased to a large degree. As a result, even when the blower fan 11 having the same P-Q (static pressure-flow rate) characteristic as in the conventional construction is used, the flow rate of circulated air is reduced such that the flow path resistance is reduced, the flow rate of circulated air can be increased. Accordingly, even when the hot air supply is composed of the heat pump mechanism 12, a sufficient drying performance can be achieved and accordingly, the drying time need not be increased. Furthermore, since an amount of circulated air can be increased without increase in the size or rotational speed of the blower fan. Furthermore, only one filter 19 is required in the circulation path 10 since the filter 19 is disposed in the single path after joint of the branch paths 23a and 23b.
The DD motor 6 protrudes rearward relative to the rear face of the water tub 3. Accordingly, a space is defined between the rear face of the body 1 and a part of the rear face other than the DD motor 6. The space is utilized for the branch paths 22a and 22b in the embodiment. Thus, the branched air supply path 22 can suppress a rearward increase in the size of the body 1. The exhaust path 23 is comprised of a single path disposed in the right or left part of the bellows 5 in the front of the water tub 3 although the disposition is not shown.
According to the embodiment, the flow path area of the air supply path 22 can be increased since the air supply path 22 is comprised of the branch paths 22a and 22b. Accordingly, the flow rate of air circulating in the circulation path 10 can be increased without increase in the size of the blower fan 11 or increase in the rotational speed of the blower fan 11 as in the first embodiment. As a result, a sufficient drying performance can be achieved without increase in the drying time even when the hot air supply unit is composed of the heat pump mechanism 12.
Each of the branch paths 24a and 24b has a section configured into a flat rectangular shape and is constructed so as not to protrude so far axially with respect to the water tub 3 when disposed on the surface of the cylindrical body 3c. Furthermore, each branch path is made of elastic rubber, for example. Consequently, the branch paths 24a and 24b can be prevented from breakage or deformation even when the branch paths 24a and 24b are brought into contact with the body 1 upon oscillation or vibration of the water tub 3 during rotation of the drum 4.
The above-described construction operates in the same manner as in the first embodiment and achieves the same effects as in the first embodiment. Furthermore, air in the water tub 3 and drum 4 can effectively be taken into the branch paths 25a and 25b as the result of provision of two air outlets 21 spaced away from each other. Moreover, since the two air outlets 21 are spaced away from each other, an addition of the lengths of the branch paths 25a and 25b can be rendered shorter than an addition of the lengths of the branch paths 23a and 23b in the first embodiment. A flow path resistance is proportional to the flow path length. Accordingly, the flow path resistance can further be reduced when the lengths of the branch paths 25a and 25b are shortened.
The above-described construction operates in the same manner as in the second embodiment and achieves the same effects as in the second embodiment since the flow path area of the air supply path 26 can be increased. Furthermore, dry air can quickly be taken into a wider range of interior of the drum 4 in the water tub 3 as the result of provision of two air discharge openings 21 spaced away from each other. Consequently, the drying performance can be improved. Furthermore, the flow length of the air supply path can be shortened such that the flow path resistance can be reduced, in the same manner as in the fourth embodiment.
The branch paths 28a and 28b constituting the exhaust path 28 are disposed on the portions of the rear of the water tub 3 located on the right and left of the DD motor 6 respectively. The branch paths 28a and 28b join together at one ends or lower ends into a single path, which is connected via the bellows 28c to the rear end of the duct 10a.
The branch paths 28a and 28b have the other ends connected to the left and right air discharge openings 21 respectively. The branch paths 28a and 28b extend substantially vertically upwards from the respective air discharge openings 21 and are bent near the body 3c of the water tub 3 into a U shape in such a direction that both outlets come close to each other. The air discharge openings 21 thereafter extend downward. Furthermore, the branch paths 28a and 28b join together at lower ends into a single path, which is connected to the bellows 28c.
Portions of the branch paths 28a and 28b extending upright from the air discharge openings 21 serve as water-cooled heat exchangers 31 respectively. Water-supply pipes 29 have one ends connected to upper portions of the heat exchangers 31 respectively. The water-supply pipes 29 have the other ends connected to a water-supply valve 30. As the result of the above-described construction, cooling water from the water-supply valve 30 is supplied via the water-supply pipes 29 into the heat exchangers 31 respectively.
A single air supply opening is provided in the upper front of the water tub 3 although not shown. An air supply path is disposed in the front of the water tub 3. The air supply path has a lower end connected via the bellows to the front end of the duct. The condenser and evaporator are disposed in the front and rear interiors of the duct so as to correspond to the air supply opening and air discharge openings 21 respectively.
Air discharged from the air discharge openings 21 in the drying step flows upward in the heat exchanger 31 as shown by arrows A. In this case, the water-supply valve 30 is opened so that cooling water is sprinkled from the water-supply pipes 29 into the heat exchangers 31 respectively. As a result, the air flowing upward in the heat exchangers 31 is brought into contact with the cooling water such that water content in the air is cooled thereby to be condensed, dropping downward. Water having dropped (dehydration water) flows through the air discharge openings 21 into the water tub 3 thereby to be discharged from the drain outlet 3b (see
Humidified air flows along t-he branch paths 28a and 28b and then join together, thereafter flowing through the bellows 28c into the duct 10a. Air having flowed into the duct 10a is dehumidified by heat exchange with the evaporator. The evaporator is supplementarily operated since the heat exchangers 31 are located above the evaporator. More specifically, an amount of dehumidification water produced by the evaporator is smaller than in the foregoing embodiments.
Air having passed through the evaporator 15 thereafter flows into the condenser 14, where the air is heated into dried air which is supplied into the drum 4. Clothes and the like in the drum 4 are dried by the above-described air circulation.
According to the embodiment, a part of the exhaust path 28 serves as the heat exchanger 31, the dehumidifying performance can be improved and accordingly, the drying performance can be improved.
Since the air discharge openings 21 are provided in the lower rear of the water tub 3 in the embodiment, wash liquid is easy to enter the heat exchangers 31 in the wash or rinse step. However, the heat exchangers 31 extend upward from the air discharge openings 21, and the upper ends of the heat exchangers 31 are located higher than the cylindrical portion 3c of the water tub 3. Accordingly, the wash liquid having entered the heat exchangers 31 through the air discharge openings 21 are prevented from flowing over the heat exchangers 31 to reach the duct 10a respectively.
Furthermore, there is a possibility that cooling water may be flung up by exhaust air flow thereby to enter the branch paths 28a and 28b at the duct 10a side. However, the flow rate of exhaust air is reduced by an increase in the flow path area due to provision of the branch paths 28a and 28b. Accordingly, it becomes difficult for the exhaust air to fling up the cooling air.
The present invention should not be limited by the embodiments described above with reference to the accompanying drawings but the embodiments may be modified as follows. The dehydration drain pipe 18 may be provided with a drain valve in order that reverse flow of water from the drain pipe 18 into the circulation path 10 may be coped with.
When the heat exchangers 31 are provided as in the seventh embodiment, the sizes of the condenser 14 and evaporator 15 may be reduced. It is considered that a sufficient drying performance can be achieved even in such construction. According to the construction, the size of the heat pump mechanism and furthermore, the size of the entire washing-drying machine can be reduced. Furthermore, when the heat exchangers 31 are provided, the dehumidifying performance can be improved accordingly. Hence, an auxiliary heater may be provided for improvement of heating performance separately from the heat pump mechanism 12. As the result of the construction, the drying efficiency can be improved to a large degree. Additionally, the heat exchanger 31 may be provided on only one of the branch paths.
The cross-sectional shape and length of each branch path may be suitably adjustable. The motor driving the drum may be provided with a gear transmission mechanism, for example. Furthermore, the rotational shaft of the drum may be coupled by a belt to the rotational shaft of the motor.
As described above, the drum washing-drying machine of the present invention can achieve energy saving, size reduction and noise reduction and is accordingly useful as a household washing-drying machine.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2005-045612 | Feb 2005 | JP | national |
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/JP2006/301224 | 1/26/2006 | WO | 00 | 2/11/2009 |
