JP4852080B2 - Drum type washer / dryer - Google Patents

Description

  The present invention relates to a drum-type washing / drying machine, and more specifically, a rotating drum is installed in a water tank so that the rotational axis direction is horizontal or inclined downward from the horizontal direction toward the rear, and is used in each step of washing, rinsing, and dewatering. In addition, it relates to a drum-type laundry dryer that performs a drying process of drying laundry by sucking air in a water tank with a blower fan, dehumidifying and heating it through an evaporator and a condenser and then blowing it into the water tank It is.

  Such a drum-type washing / drying machine is already known as an air-conditioning unit mounted for the drying process (see, for example, Patent Document 1). If it demonstrates with reference to FIG. 22, the air conditioning unit a will be incorporated in the washing machine main body b using the dead space m of the rear part of the water tank c, and in the middle of the circulation ventilation path e with the ventilation fan d. Connected. Thereby, the circulation air flow path e sucks and exhausts the air in the water tank c by driving the air blowing fan d, introduces the air into the air conditioning unit a through the suction inlet, and dehumidifies by the evaporator f, and heats by the condenser g. The hot air is dried and used as a hot air, then discharged from the suction outlet, blown to the water tank c, returned to the water tank c, and repeatedly drying the laundry in the rotating drum h, the washing process and the rinsing process A later drying step is performed.

  The blower fan d has a suction port connected to the suction discharge port of the air conditioning unit a, and is configured as an integrated air conditioning blower unit i for compactness and space saving.

  These blower fans are integrated by screwing together half-shells divided into two in the axial direction through seal members between their mating surfaces. The conventional type shown in FIG. 15 has a side portion connected to the end of the spiral portion B as a form in which the blowing portion A has a rectangular cross section and extends from the counter-blowing port A1 side toward the blowing port A1. As a result, the container-shaped deep half-shell C1 and the shallow lid-shaped half-shell C2 are arranged in a simple divided structure or seal structure in which the annular regions on the substantially same plane are combined.

  In addition, the conventional type shown in FIGS. 17 and 18 has a simple and highly sealable structure in which the sealing surfaces between the two half shells are connected in an annular shape, and the blowing portion D is provided with a blowing portion D. The cross section is smoothly connected from the spiral portion E to the cylindrical outlet D1, and the stagnation portion as described above does not occur, which is suitable for further enhancement of performance.

On the other hand, in the spiral casing of such a blower fan, the air flow extending from the starting point of the spiral portion toward the blowout portion gradually decreases and the air flow toward the blowout port and the air flow returning to the spiral portion are branched. It has already been known to provide a tong for rectification to suppress pressure loss and a decrease in blown air volume (see, for example, Patent Document 2).
JP 2008-79859 A JP 2008-67746 A

  However, in the conventional type shown in FIG. 15, the blowout part A has to be connected to the downstream air passage by making the blowout opening A1 cylindrical, and the corner angle as shown in FIG. 21 upstream of the blowout opening A1. Since the portions become the stagnation portions A2 and A3 that stagnate part of the blown air, further improvement in performance is difficult.

  Moreover, in the conventional type shown in FIGS. 17 and 18, the container-shaped deep half-shell E1 and the shallow lid shape are not affected by the three-dimensional shape of the blowing portion D that smoothly extends from the spiral portion E to the blowing port D1. In order to secure a simple divided structure and seal structure that match the half-shell E2 with a ring region on substantially the same plane, the shallow half-shell E2 is made shallower or substantially plate-shaped, and the middle of the blowout part D Along with the reduction of the divided area to the vicinity of the portion, the range extending from the cylindrical outlet D1 to the spiral portion E in the outlet portion D is defined as the undercut portion D2, and the spiral portion E from the outlet D1 side. The amount of undercut is gradually increased toward the connection position. However, high performance with no stagnation means high air volume and high static pressure, but the rigidity of the shallow half shell E2 is difficult and the seal pressure between the deep half shell E1 is reduced. It is difficult to raise and leaks easily.

  In view of this, the present inventor has divided the spiral casing into two substantially at the center in the axial direction and integrated them by screwing together with a seal member, thereby increasing the rigidity of both half shells and increasing the sealing pressure. After satisfying the pressure resistance characteristics, we considered to improve the performance of the drying function by increasing the air volume and static pressure by adopting tongs known in the past.

  However, like the conventional blower fan d shown in FIGS. 18 and 19, the deep container-type half-shell E1 has a depth substantially equal to the fan height of the fan p to be accommodated as shown in FIG. Therefore, the air flow can be adjusted by forming a tong q that reaches the height of the fan within the height of the deep half-shell itself. However, the half shells divided into two at the substantially central position in the axial direction do not reach the fan height within the depth of the half shell, no matter which side of the half shell is provided. If this is dealt with by projecting the tongue from the side of the half shell on which it is provided to the other half shell, it will cause troubles in interference and alignment work when mating with the other half shell. However, if a gap is provided between the other side in order to avoid interference, an air flow flows into this gap, so there is a problem that a sufficient effect for reducing wind noise cannot be obtained.

  The object of the present invention is to adopt a center-divided type spiral casing suitable for high air flow and high static pressure, and to provide one half-shell with a tongue protruding on the other side, and to the other half-shell. Even if there is a gap between the other half-shell and the other half-shell to avoid interference and interference with the work, it can reduce wind noise due to the inflow of air flow and does not reduce pressure loss or blowing air volume. An object of the present invention is to provide a drum type washing and drying machine effective for increasing the air volume and increasing the static pressure.

  In order to achieve the above object, a drum-type washing / drying machine according to the present invention is installed in a water tank so that the rotation axis is horizontal or inclined downward from the horizontal direction with the rotation drum facing rearward. With rotation, after washing, rinsing, and dehydrating processes, and air in the water tank by the blower fan, the air is passed through the heat exchanger for dehumidification and the heat exchanger for heating into the water tank as dry high-temperature air. The drying process for drying the laundry is carried out, and the air flow and the swirl portion extending so as to gradually decrease in height from the start portion of the swirl portion of the swirl casing in the blower fan toward the blowout portion side. In the drum type washer / dryer provided with a tongue for branching and rectifying the returning air flow, the spiral casing of the blower fan is composed of two half-shells that are divided into two at approximately the central position in the axial direction. The tongs are formed so that one of the half shells protrudes to the other side, and the protruding portion has a gap to avoid mutual interference with the other side, and the outer peripheral side of the fan. It is characterized by being provided to project.

In such a configuration, the bottomed cylindrical rotary drum is accommodated so that the rotation axis direction is inclined downward from the horizontal or horizontal direction to the rear side, and after washing, rinsing, dehydration, etc. in the installed water tank In the blower fan that draws air in the aquarium and sucks the air in the aquarium and passes it through the heat exchanger for dehumidification and the heating heat exchanger to dry it back into the aquarium as a high-temperature air, it is divided into two at the center in the axial direction Since the half shells of the spiral casing are in a three-dimensional shape and sufficient rigidity is ensured, they can be integrated with a high sealing pressure and the pressure resistance is increased. In addition, the tongue provided on one half-shell to the other half-shell and satisfying the same fan height as the conventional one is more fan-shaped than the one extending to the blow-out side on the extension line along the conventional spiral part. The amount of air that is guided by the tongue and directed toward the outlet by increasing the degree of sealing against the air flow blown to the outlet entering between the fan and the tongue by the amount provided closer to the outer peripheral side of the And the reduction of wind noise due to the gap with the other half shell of the tongue can be reduced.

  In the above, further, the tongue is molded in a form in which the outer surface is recessed on the side of the half shell that houses the rotating substrate side of the fan, and from the spiral start point of the spiral part and the blow part toward the blow part. It is characterized by being streamlined so as to extend while gradually decreasing the width and height, and provided so as to be substantially the same height as the fan at the end of the spiral start point.

  In such a configuration, in addition to the above, further, frictional resistance with the air flow, turbulence of the air flow, and wind noise can be further reduced by the streamline of the tongue.

  In the above, further, an auxiliary tongue that is less than its depth and that does not interfere with the tongue is provided on the side having the suction port of each half-shell with a depression on the outer surface. Can do.

  In such a configuration, in addition to the above, the auxiliary tongue is contained in the half shell provided with it, and does not interfere with the tongue or the half shell provided with it, and the blowout cooperated with the tongue. A function of guiding air can be exhibited, and the blowing can be made smoother. In addition, higher performance can be achieved by increasing the amount of air blown to the blowout port 15d1 without any problem of wind noise.

  According to the drum type washing and drying machine of the present invention, the spiral casing of the blower fan used for drying the laundry is divided into two at the substantially center in the axial direction, so that each half shell is divided into two parts. Since it has a three-dimensional shape with sufficient rigidity, both the sealing pressure and pressure resistance are improved, it can cope with further higher air volume and higher static pressure. In addition, a tongue that protrudes from one half-shell to the other half-shell and satisfies the fan height correspondence similar to the conventional one is blown out by the amount provided closer to the outer peripheral side of the fan than the conventional one. Increases the degree of sealing against the inflow of airflow blown to the part between the fan and the tongs, increases the amount of air that is guided by the tongs toward the outlet, and is effective for increasing the airflow, It is also effective for high static pressure because it reduces the loss of wind noise due to the gap between the tongue and the other half-shell and reduces the pressure loss. In addition to the above, the tong streamline can further reduce the frictional resistance with the air flow, the turbulence of the air flow, and the wind noise, and is effective for further increasing the air volume and static pressure in addition to the quietness.

  In addition to the above, the auxiliary tongs fit within the half-shell provided with it, and do not interfere with the tongs and half-shell provided with it. Thus, the balloon can be made smoother, and the performance can be improved by increasing the volume of the blown-out air without causing a problem of wind noise.

  The drum-type washing machine according to the embodiment of the present invention will be described below with reference to the drawings for understanding of the present invention. The following description is a specific example of the present invention and does not limit the content of the claims.

As shown in FIGS. 1 and 2, the drum-type washing / drying machine 1 according to the embodiment of the present invention is a water tank in which the rotary drum 2 is inclined downward from the horizontal direction with the rotation axis direction horizontal or rearward. In addition to the washing, rinsing and dehydration processes, the evaporator 31 as a heat exchanger for dehumidification and the heat for heating are deduced by sucking the air in the water tank 3 through the circulation fan 5 by the blower fan 15. After the dehumidification and heating through the condenser 32 as an exchanger, the drying process of drying the laundry by repeatedly blowing air into the water tank 3 is performed. For this drying process, an air conditioner unit 39 containing an evaporator 31, a condenser 32, and a compressor 37 that circulates a refrigerant in them, and an air blower fan 15 are mounted as an air conditioner blower unit 81. Connected on the way.

  Corresponding to the horizontal arrangement of the rotating drum 2 or the inclination shown in the drawing, a clothing doorway leading to the opening end of the rotating drum 2 is formed on the front side of the water tank 3, and the upward inclination formed on the front side of the washing / drying machine main body 44 Laundry can be taken in and out of the rotary drum 2 by opening a door that opens and closes an opening provided on the surface. Since the door is provided on the upward inclined surface, the work for putting in and out the laundry can be performed without bending the waist.

  The rotating drum 2 has a large number of through-holes communicating with the water tank 3 on its peripheral surface, and is provided with stirring protrusions (not shown) at a plurality of circumferential positions on the inner peripheral surface. The rotating drum 2 is rotationally driven in the forward and reverse directions by a motor 7 attached to the rear side of the water tank 3. In addition, a water injection pipe and a drain pipe are connected to the water tank 3, and water is poured into and drained into the water tank 3 by controlling the water injection valve and the drain valve. When the door is opened, laundry and detergent are put into the rotating drum 2 and the operation is performed on the operation panel provided at the upper front of the drum-type washing / drying machine 1, for example, by the control board provided on the inside thereof. When the operation is started through the water tank 3, a predetermined amount of water is injected from the water injection pipe, and the rotating drum 2 is driven to rotate by the motor 7 to start the washing process. By the rotation of the rotating drum 2, the laundry accommodated in the rotating drum 2 is lifted in the rotating direction by the stirring protrusion provided on the inner peripheral wall of the rotating drum 2, and the stirring operation of dropping from the lifted appropriate height position Is repeated, so that the laundry has the effect of tapping and washing. After the required washing time, the dirty washing liquid is discharged from the drain pipe, and the washing liquid contained in the laundry is dehydrated by a dehydrating operation that rotates the rotating drum 2 at a high speed. The rinsing process is carried out by pouring water. Also in this rinsing step, the laundry stored in the rotary drum 2 is rinsed by repeating the stirring operation in which the laundry is lifted by the stirring protrusion by the rotation of the rotary drum 2 and dropped.

  The blower fan 15 is a centrifugal fan in which a centrifugal fan 15a is accommodated in a spiral casing 15b. As shown in FIGS. 4 to 6, the air conditioning unit 39 and the blower fan 15 are connected to the spiral casing 15 b to the suction / discharge port 392 formed in the end wall 38 a on one end side in the longitudinal direction facing the left and right of the air conditioning case 38. The mouth 15c1 is fitted and connected to each other.

  As a result, the suction force of the blower fan 15 extends into the air conditioning case 38 and from the suction inlet 391 on the other end side of the air conditioning case 38 to the water tank 3 through the suction path 16 of the circulation air blowing path 5. The air is sucked into the air conditioning case 38 and dehumidified and heated through the evaporator 31 and the condenser 32, and the dried high-temperature air after dehumidification and heating is opened inside the suction outlet 392, the connection port 15c1, and the connection port 15c1. Then, the air is sucked into the spiral casing 15b through the suction port 15c, and blown into the water tub 3 from the blowing portion 15d of the spiral casing 15b through the air passage 33 of the circulation air passage 5 to dry the laundry in the rotary drum 2.

  Here, the blower fan 15 connects the connection port 15c1 to the suction / discharge port 392 of the air conditioning unit 39, and configures the air conditioning blower unit 81 as a single unit to achieve compactness and space saving. It arrange | positions using the space S between the rear part walls 44a of the washing machine main body 44. FIG.

However, in the present embodiment, in order to realize a high air volume and high static pressure of the blower fan 15 without increasing the size of the washing machine main body 44, the blower fan 15 has the suction port 15c and the rotation center. 2 to 5, 8, and 9, 15 e is eccentric to the water tank 3 side from the center 15 f of the connection port 15 c 1 with the air conditioning case 38 provided around the suction port 15 c of the spiral casing 15 b. Provided. As a result, the bottomed cylindrical rotary drum 2 is housed and installed such that the rotational axis direction is horizontal or inclined downward from the horizontal direction to the rear side as shown in FIG. The air conditioning case 38 and the blower fan 15 are connected to each other in the space S between the rear wall 44a and the air conditioning / blower unit 81. The air conditioning case 38 is connected to the end wall 38a on one end side in the left-right direction of the air conditioning case 38. The suction port 15c and the rotation center 15e of the blower fan 15 are eccentric to the water tank 3 side with respect to the connection port 15c1 of the spiral casing 15b. As shown in FIG. 2, the space S between the tank 3 and the water tank 3 is approached as much as possible without being affected by the connection with the air-conditioning case 38, such as the approach limit of the tank 38 to the tank 3 side. Anti water tank 3 side, i.e. laundry room S between the rear wall 44a of the main body 44 is likely take a large expansion angle of the spiral casing 15b by utilizing from increasing.

  As a result, the air conditioning / blower unit 81 is arranged between the rear part of the water tub 3 installed so as to be inclined downward from the horizontal or horizontal direction to the rear side together with the accommodated rotating drum 2 and the rear wall 44a of the washing machine body 44. However, the suction port 15c and the rotation center 15e of the blower fan 15 are eccentric to the water tank 3 side with respect to the connection port 15c1 of the spiral casing 15b connected to the end wall 38a of the air conditioning case 38. The restraint from the connection relationship with the air conditioning case 38 is suppressed as compared with the case where there is not, the blower fan 15 is brought to the water tank 3 side to the full space S between the water tank 3 and the rear side of the anti-water tank 3 side, that is, the washing machine body 44. As the space S with the wall 44a increases, the enlargement angle of the spiral casing 15 increases from the water tank 3 side to the rear wall 44a side, specifically to the end of the blowing portion 15d. Raising the blowing performance Te, additional large air volume without affecting the surrounding such enlargement of the washing machine main body 44 may correspond to the high static pressure.

  In particular, the aquarium 3 of the present embodiment is installed so as to be inclined downward from the horizontal direction toward the rear part together with the rotary drum 2, and the rear part is viewed from the side with the rear wall 44 a of the washing machine body 44. A substantially right-angled triangular space S whose rear side is substantially vertical is formed on the bottom 44b of the washing machine main body 44, and the air conditioning / blower unit 81 is located below the triangular space S and is located at the bottom 44b of the washing machine main body 44. It is installed on the top. As a result, the triangular space S is naturally formed on the bottom 44b between the rear portion of the water tank 3 and the rotating drum 2 and the rear wall 44a of the washing machine main body 44. Therefore, the width of the lower half is utilized. Thus, the air-conditioning / air-blowing unit 81 can be installed, and the air-conditioning case 38 and the air-blowing fan 15 can be installed in a size that uses a particularly wide bottom. As a result, air conditioning is performed by utilizing the width of the lower half of the triangular space S formed naturally on the bottom 44b between the rear wall 44a of the washing machine main body 44 and the rear of the water tub 3 inclined together with the rotary drum 2. The blower unit 81 can be installed on the stable bottom portion 44b, and in particular, the spiral casing 15b is brought closer to the lower part of the water tank 3 farthest from the rear wall 44a of the washing machine main body 44 by the eccentricity as shown in FIG. Since the enlargement angle from the rear part of the water tank 3 to the rear wall 44a side can be sufficiently increased, it can further contribute to the improvement of the blowing performance.

  More specifically, the air conditioning unit 39 accommodates the compressor 37, the evaporator 31 and the condenser 32 even if the air volume unit 39 has a shape corresponding to the triangular space S and the volume of the triangular space S can be effectively utilized. Since the main body portion to be formed is substantially a rectangular parallelepiped as described above, a dead space S1 is inevitably left between the rear portion of the water tank 3 inclined in the triangular space S as shown in FIG. On the other hand, the blower fan 15 has a spiral shape and has a roundness unlike the air-conditioning case 38 that is square when viewed from the side, but its position is restricted by the connection relationship with the air-conditioning unit 38. As a result, conventionally, as shown in FIG. 22, a dead space m similar to that of the air conditioning case a is left between the rear part of the water tank c, and the enlargement angle is increased with the rear wall of the washing machine body b. It was difficult to achieve high air volume and high static pressure.

  However, in the present embodiment, the suction port 15c and the rotation center 15e of the blower fan 15 are eccentric to the water tank 3 side with respect to the connection port 15c1 of the spiral casing 15b connected to the end wall 38a of the air conditioning case 38. 2 and FIG. 3, the spiral casing 15b can be designed to protrude from the air-conditioning case 38 to the rear side of the water tank 3, so that the air-conditioning case 38 and the air-conditioning case 38 Taking advantage of the rounded shape from a different side view, it is as close as possible to the rear of the aquarium 3. Accordingly, the swirl casing 15b has a size utilizing the full lower half of the triangular space S between the rear portion of the water tub 3 and the rear wall 44a of the washing machine body 44. In other words, the swirl casing 15b The volume is increased in the front-rear direction by the amount close to the rear, and an increase in the angle of expansion from the rear side of the water tub 3 toward the rear wall 44a of the washing machine main body 44 is realized without increasing the size of the washing machine main body 44. Contributes to higher air flow and higher static pressure.

  In addition, as shown in FIGS. 1 and 2, the air conditioning case 38 is provided with a suction inlet 391 for introducing circulating air by suction from the blower fan 15 so as to rise upward toward the rear of the other left and right ends, Corresponding to the fact that the suction / discharge port 392 for connecting the connection port 15c1 of the spiral casing 15b is provided near the front part of the end wall 38a on the other end side as shown in FIGS. The casing 15b is provided so that the expansion angle increases from the water tub 3 side to the rear wall 44a side of the washing machine main body 44 so that the blowing portion 15d rises upward along the rear wall 44a. In this way, the suction inlet 391 of the air conditioning case 38 is provided near the rear on the left and right other ends of the air conditioning case 38, so that the suction connected from the suction inlet 391 to around the trunk of the water tank 3 and the like. A space S2 that is naturally formed between the narrow upper half portion of the triangular space S and the rear wall 44a of the washing machine main body 44 that is lowered while curving from the center of the water tank 3 to the side. In addition, the suction / discharge port 392 for connecting the connection port 15c1 of the spiral casing 15b is provided near the front of the end wall 38a on one end side of the air conditioning case 38, that is, close to the water tank 3. Therefore, even if the eccentricity with respect to the connection port 15c1 is suppressed, the blower fan 15 is easily provided close to the water tank 3, which is advantageous for increasing the enlargement angle, and is connected from the blowing part 15d to the 3 rear part of the water tank. The air passage 33 is provided raised by utilizing the narrow upper half of the triangular space S. Further, the flow of suction air sucked into the air conditioning case 38 from the suction inlet 391 and sucked into the suction port 15c of the blower fan 15 from the suction outlet 392 is changed from the rear end on the one end side to the front on the other end side of the air conditioning case 38. 8 and FIG. 9 with respect to the longitudinal direction of the air-conditioning case 38 facing toward the section, the evaporator 31 installed in the air-conditioning case 38 so as to be inclined obliquely from the rear side to the front side as indicated by arrows It becomes somewhat easier to approach the direction of the fins 395a of the condenser 32.

  As a result, the suction inlet 391 is positioned near the rear on the left and right other ends of the air-conditioning case 38, and the suction passage 16 extending from the suction inlet 391 is raised without being enlarged due to a special space. In addition to being able to be routed to the connection position such as around, the blower fan 15 can be easily provided near the water tank 3 even if the eccentricity with respect to the connection port 15c1 is suppressed, which is further advantageous for increasing the expansion angle to the blowing portion 15d and improving the blowing performance. And the ventilation path 33 connected to the rear part of the water tank 3 from the blowing part 15d is also started and provided without the enlargement by a special space. Further, the flow of the suction air that is sucked and introduced into the air conditioning case 38 from the suction inlet 391 and sucked from the suction discharge port 392 is changed from the rear end of the air conditioning case 38 to the front end of the other end of the air conditioning case 38. As the direction oblique to the direction, the passage resistance to the evaporator 31 and the condenser 32 is reduced somewhat easily to be somewhat closer to the direction of the fins 395a of the evaporator 31 and the condenser 32 installed in the air conditioning case 38, and Heat exchanging efficiency can be improved by preventing the drift of ventilation.

Further, the evaporator 31 and the condenser 32 are parallel to each other, and the ventilation path partitioned from the storage area 394 of the compressor 37 shown in FIGS. 8 and 9 from the suction inlet 391 to the suction outlet 392 of the air conditioning case 38. In the middle of 393, the air conditioning case 38 faces in the longitudinal direction as shown in FIG. 9, or the suction introduction port 391 side is closer to the front side than the suction discharge port 392 side as shown in FIG. It is provided to face. Thus, even when the evaporator 31 and the condenser 32 are parallel to each other and are oriented in the longitudinal direction of the air conditioning case 38, if the suction air passes obliquely through the air conditioning case 38 as described above, suction is performed. The air flow is made somewhat closer to the direction of the fins 395a of the evaporator 31 and the condenser 32. Further, if the evaporator 31 and the condenser 32 are provided so that the suction inlet 391 side is inclined obliquely closer to the front than the suction outlet 392 with respect to the longitudinal direction of the air conditioning case, the flow of the suction air flows. Even in the case where the air conditioning case 38 is oriented in the longitudinal direction, the flow of the suction air is made somewhat closer to the direction of the fins 395a of the evaporator 31 and the condenser 32 as in the above case, and the air inside the air conditioning case 38 is sucked into the air. In particular, when the gas passes diagonally, the flow of the suction air makes the angle of the evaporator 31 and the condenser 32 with respect to the fins closer to further improve the heat exchange efficiency and the drying performance.

  In the blower fan 15 using the centrifugal fan 15a and the spiral casing 15b as described above, spiral casings having various characteristics have been proposed and put into practical use. Most of them are divided into two types.

  The conventional type shown in FIG. 15 has a side portion connected to the end of the spiral portion B as a form in which the blowing portion A has a rectangular cross section and extends from the counter-blowing port A1 side toward the blowing port A1. As a result, the container-shaped deep half-shell C1 and the shallow lid-shaped half-shell C2 are arranged in a simple divided structure or seal structure in which the annular regions on substantially the same plane are combined. It is necessary to make A1 cylindrical and connect it to the downstream air passage, and the corners as shown in FIG. Therefore, further improvement in performance is difficult.

  The conventional type shown in FIGS. 17 and 18 has a configuration in which the cross section is smoothly connected from the spiral portion E to the cylindrical blowout port D1 in the blowout portion D, and the stagnation portion as described above does not occur. Suitable for conversion. However, the container-shaped deep half-shell E1 and the shallow lid-shaped half-shell E2 are substantially connected to each other without being affected by the three-dimensional shape of the blowing portion D that is smoothly connected and expanded from the spiral portion E to the blowing port D1. In order to secure a simple divided structure and seal structure that fit in an annular area on the same plane, the shallow half-shell E2 is made shallower or substantially plate-shaped, and the divided area is reduced to the middle part of the blowing part D. In addition, the range extending from the cylindrical outlet D1 to the spiral part E in the outlet part D in the outlet part D is defined as the undercut part D2, and the amount of undercut from the outlet part D1 side to the connecting part side of the spiral part E Is gradually increased. However, high performance with no stagnation means high air volume and high static pressure, but the rigidity of the shallow half shell E2 is difficult and the seal pressure between the deep half shell E1 is reduced. It is difficult to raise and leaks easily. Further, since the undercut amount of the undercut portion D2 is large, the moldability is poor and the mold structure is complicated and expensive, and there is a limit to increasing the air volume and increasing the static pressure.

Corresponding to these, the spiral casing 15b of the present embodiment is divided into two parts at approximately the center position in the width direction and in the left-right direction as shown in FIGS. 1, 3 to 5, and 7 to 9. The half-shells 15b1 and 15b2 are integrated with each other through the annular seal member 102 and screwed around the mating portion with screws 200 at a plurality of locations. In particular, a cylindrical blowout port 15d1 of the blowout portion 15d is integrally formed with one of the half shells 15b1 and 15b2, and the mating surface 12 of the half shells 15b1 and 15b2 has a spiral portion 15e as shown in FIGS. From the outline form part 12a to the vicinity of the blowout opening 15d1 of the blowout part 15d, the contour form part 12a forms the same plane or a plane close to the outline of the air passage formed by the spiral part 15e and the blowout part 15d. A pair of overhanging portions 12b extending from the blowout portion 15d outwardly on both sides are formed between 15d1 and 15d1. A space is provided as a cylindrical shape portion 12c that forms a cylindrical surface along the cylindrical outer surface of the outlet 15d1. Here, the projecting form portion 12b has a function of continuously connecting the contour form portion 12a and the tubular form portion 12c of the mating surface 12 with the mating surface area in the same mating direction as those. Specifically, the annular seal member 102 sandwiched between the mating surfaces 12 detours outward from the position P where the annular form member 12a rises from the contour form part 12a side to the tubular form part 12c side. The detour path that connects the projecting form part 12a to the tubular form part 12c is secured within the mating surface range that does not change in the mating direction without the influence of narrowing the formed ventilation path. Therefore, the form of detouring is not particularly questioned, and it is essential that the position P deviates outward. Here, both the half-shells 15b1 and 15b2 have a three-dimensional shape that swells substantially in a container shape, and the rigidity in the alignment direction in the area of the alignment surface 12 is increased, so that a sufficient sealing pressure can be secured, Can be avoided. Moreover, since such a mating structure and seal structure are realized without requiring flattening by undercut, the undercut is exclusively provided in the washing machine body 44 with the air conditioning unit 39 of the blower fan 15, When the blower unit 81 is installed in the washing machine body 44 and the natural enlargement angle of the spiral casing 15b is taken, it is sufficient to avoid interference with the surroundings. The minimum gap L of the portion 15d is larger than the width of the spiral portion, and can be made larger than the minimum gap M (smaller than the width of the spiral portion) due to the undercut portion D2 in the conventional case shown in FIG. Higher air volume and higher static pressure can be achieved by increasing the magnifying angle, greatly improving performance, and improving moldability, making the mold structure simple and inexpensive. .

  In addition, as described above, due to the recent increase in air volume and static pressure, it is essential to increase the size of the spiral casing 15b and the size of the air conditioning unit 39 is also required. For this purpose, it is also important to make the flow of suction air from the air conditioning case 38 of the air conditioning unit 39 into the spiral casing 15b smooth. This is because if the flow of the suction air introduced into the suction port 15c of the spiral casing 15b is biased or disturbed, the air volume loss and the static pressure loss are caused and the performance is lowered. Therefore, between the air-conditioning case 38 and the suction port 15c of the spiral casing 15b, a run-up section N as shown in FIG. 4 that guides the suction air to the suction port 15c so as not to be biased or disturbed is necessary. .

  Such a run-up section N includes an evaporator 31 and a condenser 32 that are arranged in the air-conditioning case 38 substantially in the longitudinal direction as shown in FIG. 9 or inclined with respect to the longitudinal direction as shown in FIG. After passing from the rear side to the front side, the flow of suction air bent almost at right angles toward the suction / discharge port 392 provided on the one end side wall 38a of the air conditioning case 38 is rectified and equalized. Therefore, a sufficient length is required.

  However, conventionally, as shown in FIG. 14, the air-conditioning unit a has a suction port n fitted with a connection port d2 formed on the outer peripheral surface of the suction port d1 of the blower fan d via the seal member o, and the blower fan d. And a bell mouth d3 as a guide wall serving as a running section N is formed at the suction port d1. For this reason, the connection structure part which fitted the suction discharge port n located in the upstream of the suction port d1 and the connection port d2 cannot be used for the run-up section N, and extending the run-up section N is restricted.

Corresponding to this, the blower fan 15 of the present embodiment, as shown in FIG. 4, is connected to the air suction case 38 side of the connection port 15 c 1 that connects the suction port 15 c to the suction / discharge port 392 of the air conditioning case 38 around the outside. It extends so as to be folded inward from the end, and is formed so as to fit a certain amount on the inner periphery of the fan 15a to ensure a sealing property between them. Thus, the suction port 15c itself forms a bell mouth 15c2 that contributes to an increase in the run-up section N that rectifies the flow of the suction air and contributes to equalization. In addition, the suction / discharge port 392 is connected to the connection port 15c1 via the seal member 104, and the connection port 15c1 of the suction port 15c extends from the end of the air-conditioning case 38 to the inside of the connection port 392a. The rectifying flange 392b covers the fitting portion of the connection ports 392a and 15c1 through the seal member 104 from the air-conditioning case 38 side. The flow of suction air from the suction / discharge port 392 toward the suction port 15c is prevented from being disturbed by the fitting portion, and is caused to flow into the suction port 15c. As a result, the run-up section N that guides the flow of suction air sucked from the suction / discharge port 392 through the suction port 15c to the blower fan 15 to rectify and equalize the air flow of the rectifying flange 392b as shown in FIG. From the inner surface on the case 38 side to the inner end of the suction port 15c on the spiral casing 15b side, the connection distance between the air conditioning case 38 and the spiral casing 15b is doubled compared to the conventional one without any further increase, contributing to further higher performance. . In addition, a seal peripheral wall 105 extending from the inner peripheral side of the fan 15a to the outer periphery of the suction port 15c is provided using the space inside the folded portion of the suction port 15c from the connection port 15c1 as indicated by a virtual line in FIG. it can. Thereby, the sealing performance between the suction port 15c and the fan 15a can be further enhanced, which contributes to higher performance. On the other hand, in the connection between the suction / discharge port 392 and the connection port 15c1, the necessary sealing performance can be ensured by satisfying the circumferential fitting or contact relationship between the connection port 392a or the rectifying flange 392b. . Thus, the seal member 104 is not essential.

  The blower fan 15 is provided with a tongue 106 extending so that the height gradually decreases from the starting point of the spiral part 15e as shown in FIGS. 6 and 7, which is a typical spiral pump, to the blowing part 15d, and heads toward the blowing port 15d1. The air flow and the air flow returning to the spiral portion 15e are branched and rectified.

  For example, in the conventional blower fan d shown in FIGS. 18 and 19, the deep container-type half-shell E1 has a depth substantially equal to the fan height of the fan p to be accommodated as shown in FIG. The air flow can be adjusted by forming a tongue q that reaches the full height of the fan within the height of the deep half-shell itself.

  However, the spiral casing 15b of the present embodiment is configured by combining the half shells 15b1 and 15b2 that are divided into two at the left and right direction, that is, at the substantially central position in the axial direction, so the left and right half shells 15b1 and 15b2 are combined. In either case, the tongue 106 does not reach the fan height in the half-shells 15b1 and 15b2. If the tongue 106 provided on one of the half-shells 15b1 and 15b is made to protrude to the other side as shown in FIG. 6, it takes time and effort to interfere with the other side. In order to avoid interference, if a gap is provided between the other side in order to avoid interference, an air flow flows into this gap, so that there is a problem that a sufficient effect for reducing wind noise cannot be obtained.

  Corresponding to this, the spiral casing 15b of the present embodiment is provided with a tongue 106 on one of the half shells 15b1 and 15b2, and protrudes on the other side, and the protruding part interferes with the other side. Along with the formation to have a gap S3 to avoid, it is provided so as to protrude from the spiral portion 15e side, that is, from the inner peripheral surface of the spiral portion 15e to the outer peripheral side of the fan 15a. Therefore, it is provided closer to the fan 15a side than the one extending to the blowing portion side on the extension line along the conventional spiral portion. As a result, the degree of sealing against the air flow blown to the blowing portion 15d entering between the fan 15a and the tongue 106 can be improved, so that the air volume guided to the tongue 106 and directed to the blowing port is increased. And the weakening of the wind noise reduction by the gap S3 can be reduced.

More specifically, the tongue 106 is molded in such a manner that the outer surface is recessed on the left half shell 15b1 side that accommodates the rotating board 15a1 side of the fan 15a, and the spiral start points of the spiral part 15e and the blowing part 15d. It is provided in a streamlined manner so as to extend while gradually decreasing the width and height from the portion 15g toward the blowing portion 15d, and is substantially the same height as the fan 15a at the end of the spiral starting point 15 side. I try to be close to the height. Such a streamlined tongue 106 can further reduce frictional resistance with the airflow, airflow turbulence, and wind noise, and further increase the performance. Corresponding to the height of the tongue 106 close to the fan height, the same as the tongue 106 on the side of the suction discharge port 392, and therefore on the right half shell 15b2 having the suction port 15c. An auxiliary tongue 106a that is less than the depth of the half-shell 15b2 and has a height that does not interfere with the tongue 106 is provided with a depression on the outer surface. The auxiliary tongs 106a project toward the other left half shell 15b1 and do not interfere with each other, so that there is no problem of gaps as in the case of the tongs 106, and there is no problem of wind noise. Higher performance can be achieved by increasing the amount of airflow.

  In particular, regarding the behavior of the air flow blown from the spiral portion 15e to the blowout portion 15d by the rotation of the fan 15a in the spiral casing 15b, as shown in the figure, the lower portion 106b1, the middle portion 106b2, and the higher portion 106b3 The air flow 107a guided to the lower portion 106b1 of the tongue 106 is represented by the air flow 107b guided to the middle portion 106b2 as representatively described by the three air flows 107a, 107b, 107c guided to the outlet 15d. In front of the airflow 107b, the airflow 107b guided to the middle 106b2 of the tongue 106 is guided ahead of the airflow 107c guided to the high portion 106b3. It goes to the receiving outlet 15d1. As a result, the suction that is high on the airflow rotating substrate 15a side and weak in the binding force is lowered toward the side. As a result, the air flows in the order of 107a, 107b, and 107c toward the outlet 15d1. That is to say. For this reason, the air flow 107a side is more negative than the air flow 107c side, and a pressure relationship of Va> Vb> Vc is generated. Such a pressure relationship generates a secondary flow 107d that draws the air flow from the high-pressure air flow 107c side to the low-pressure air flow 107a side. Since the air flow 107d acts to draw the air flow 107e to be drawn between the tongue 106 and the fan 15a toward the air flow 107a and direct it toward the outlet, the fan 15a In addition to improving the sealing performance between the two, the blowout air volume can be increased, so higher performance can be expected.

  Further, as described above, the circulating air flow path 5 is driven by the blower fan 15 to suck and exhaust the air in the water tank 3, dehumidified by the evaporator 31, and heated by the condenser 32 to dry. After that, the air is sent to the water tank 3 side and returned to the water tank 3 to dry the laundry in the rotary drum 2, but in order to improve the drying performance, not only the performance of the air blowing fan is improved, but also it is utilized. In this case, it is necessary to bring dry high-temperature air returned to the water tank 3 into contact with laundry such as clothes in the rotating drum 2 evenly. For this purpose, it is effective for the air passage 33 of the circulation air passage 5 to blow the circulating air to the central portion in the rotary drum 2.

  Therefore, the air passage 33 is connected to a position closest to the motor 7 closest to the central portion of the rotating drum 2 at the rear portion of the water tank 3 as in the example shown in FIGS. Further, the connection portion of the air passage 33 to the rear portion of the water tank is an air guide 33 a that smoothly guides the circulating air to be blown to the connection port 108 with the water tank 3 and directs it toward the center of the rotating drum 2.

  Such a conventional air blowing guide changes the direction to flow around the motor at the rear of the water tank by introducing the air from the air passage r by bending it at a substantially right angle as shown by broken line arrows in FIGS. After that, the exhaust drum provided near the motor at the downstream end portion is connected to the rear portion of the water tank via the blower port s obliquely directed to the center side of the bottom of the rotary drum. A louver (not shown) that changes the air blowing direction facing away from the rotation center O to the direction indicated by the solid line arrow is provided inside the air outlet s.

  However, with such a conventional air blowing guide, it is difficult to further improve the air blowing performance due to high ventilation resistance. Specifically, the sudden change of direction of the air flow by the louver in the conventional air guide causes pressure loss and wind drop, and the direction of the air flow in the narrow air passage of the air guide guides It also makes it difficult to raise the blowing resistance.

  Corresponding to this, the air blowing guide 33a of the present embodiment is guided to the air blowing port 108 by bending substantially at a right angle from the introduction portion 33a1 for introducing the air flow from the air blowing path 33 as shown in FIGS. The guide portion 33a2 to be expanded is expanded toward the rear wall 33a4 toward the downstream end, and the air outlet 108a is formed at the front wall 33a5 of the downstream end thickening portion 33a3 formed by this by the exhaust port 33a6 that is offset toward the motor 7 side. It is connected to. As a result, the air flow flowing into the guide portion 33a2 from the introduction portion 33a1 is bent in the passage from the introduction portion 33a1, or bubbles or the like flowing backward from the exhaust port 33a6 are introduced into the introduction portion 33a1 or the air passage 33 connected thereto. Since the flow direction is changed at a substantially right angle due to the throttling effect of the weir part 109 that prevents the upstream side from entering, the centrifugal force when this flow direction changes affects the air flow that has entered the guide part 33a2. The guide portion 33a2 extends toward the downstream end along the side wall on the counter-motor 7 side, but expands toward the rear wall 33a4 by increasing the thickness toward the downstream end of the guide portion 33a2 toward the downstream end. The air flow that flows while the air flow is shifted toward the rear side is once guided to the rear of the exhaust port 33a6 and then guided to the end peripheral wall 33a7 of the guide portion 33a2. The air flows into the air inlet 33a6 from the rear as shown in FIG. 10 and FIG. 11, flows in the forward direction into the air blowing port 108, and the air blown into the water tank 3 rotates as indicated by a conventional phantom arrow. The fact that the air has been blown away from the center O of the drum 2 can be blown toward the center O of the rotating drum 2 as shown by the solid arrow. Therefore, according to the guide portion 33a2 of the present embodiment, blowing toward the center portion of the rotating drum 2 is realized based on a gradual change in the direction of airflow without pressure loss or airflow reduction. Compared with this, it is possible to further improve the blowing performance.

  Further, the guide portion 33a2 generates a main flow with a high flow velocity along the side wall on the side of the non-motor 7 that gently curves the air flow from the introduction portion 33a1 to the outside, and creates a flow that draws in others, Since the front wall 33a5 has a slope portion 33a8 that is inclined toward the rear wall 33a4 toward the downstream side and guides the air flow passing therethrough toward the rear wall side of the guide portion 33a2, the exhaust port 33a6 The air volume and the air speed guided to the end peripheral wall 33a7 of the guide portion 33a2 are increased after going around further rearward, and the blowing function is further enhanced. In addition, the end side wall of the guide portion 33a2 rises from the front wall 33a5 at a substantially right angle and is connected to the rear wall 33a4 so as to be loosely curved or inclined so that the air flow reaching the end along the rear wall 33a4 is exhausted to the exhaust port. The side wall of the motor 7 is inclined toward the center O side of the rotating drum 2 and reaches the exhaust port 33a6 while exhibiting a guide function to bend gently toward the 33a6 side, so that air blown from the upstream side of the exhaust port 33a6. Since it can guide to the center O side of the rotating drum 2 and reach the exhaust port 33a6 and can flow through the air blowing port 108 as a more stable flow toward the center O side of the rotating drum 2, it can be blown easily. Blowing performance and drying performance can be improved. In particular, the front wall 33a5 of the guide portion 33a2 has a shelf portion 109a that rises inward from the weir 109 and the exhaust port 33a6 so as to form a substantially mountain shape between the weir 109 and the exhaust port 33a6, as shown in FIGS. In addition, the air flow from the introduction portion 33a1 is collected on the side wall on the counter-motor 7 side to increase the main flux, and at the same time, the guide portion is inclined by the slope portion 33a8 while being squeezed by the slope portion 33a8 to increase the flow velocity. Since the rear wall 33a2 is vigorously moved toward the rear wall side, it is easy to increase the air flow toward the exhaust port 33a6 from the rear by a smooth direction change upon receiving guidance from the rear wall 33a4 and the end wall 33a7 of the guide part 33a2. It is convenient for improving the drying performance, and the rear wall 33a4 downstream of the connection port 33a9 with the air passage 33 in the introduction portion 33a1. By the slope approaching toward the downstream side with respect to the front wall 33a5 by the undercut portion 33a10 and the reverse slope portion 33a11 inclined toward the side away from the rear wall 33a4 toward the downstream side provided upstream from the weir portion 109 in the front wall 33a5, After the air flow from the introduction part 33a1 is hung from the upstream side passing through the weir part 109 to the downstream side to make a strong flow once along the front part wall 33a5, the downstream slope part 33a8 has an effect on the rear wall 33a4 side. In other words, the air flow direction is smoothly changed, so that the direction of the air flow is smoothly changed in both the speed and the air volume guided from the rear wall 33a4 and the downstream end side wall 33a7 to the exhaust port 33a6 from behind. There is an advantage that can be further enhanced.

  Further, the air blowing port 108 has an extended edge 108a1 extending toward the bottom side of the rotary drum 2 on the downstream side of the guide portion 33a2 of the opening edge 108a, and the air flow coming out from the rear of the exhaust port 33a6 is rotated. Since it is reasonably prevented that the air is directed away from the center O of the drum 2 or spreads out from the air blowing port 108, the air flow toward the center O of the rotating drum 2 of the circulating air returned to the water tank 3 can be further stabilized. The air blowing performance and the drying performance can be improved accordingly.

  1 and 2, the air guide 33a has a connection port 33a9 connected to the upper end of the air passage 33 that rises from the blowout port of the blower fan 15 to the side of the motor 7 at the rear of the water tank 3, for example. 7, the front and rear half-shells 33a21 and 33a22 are formed in a hollow shape through the seal member 110 and connected to the rear portion of the water tank 3 through the air blowing port 108, as in the conventional case. However, the front half-shell 33a21 is relatively shallow and the rear half-shell 33a22 is deeper than that of the front to satisfy the three-dimensional form. In particular, the extension of the guide portion 33a2 toward the rear side from the weir portion 109 toward the downstream side is realized by the inclination toward the side away from the front wall toward the downstream side of the undercut portion 33a10, but the undercut portion 33a10. The width is smaller than that of the guide portion 33a2 toward the downstream end, and is gently connected to the side wall portion. Thereby, the air flow reaching the end portion along the side wall of the guide portion 33a2 on the side opposite to the motor 7 is easily guided by the exhaust port 33a6 and the air blowing port 108, and pressure loss and air volume reduction can be further prevented.

  Further, a bubble sensor 111 that detects bubbles that may enter from the exhaust port 33a6 side is provided near the lower part of the rear wall 33a4 in the vicinity of the downstream side of the weir 109 where bubbles are likely to collect. As a result, during the operation in which bubbles are generated, such as in the washing process or the aquarium washing process, a large amount of bubbles are generated due to excessive detergent and the volume increases, and the bubbles may enter the guide portion 33a2 through the exhaust port 108. Is detected by the bubble sensor 111 before the weir 109 flows back to the upstream side, and measures such as operation stop are taken, and the bubble is installed downstream of the weir 109, particularly in the spiral casing 15b of the blower fan 15. It is possible to prevent a problem such as a short circuit from entering the PCT heater, and it is not necessary to provide two places like the sensor t shown in FIG.

  Here, the evaporator 31 and the condenser 32 form a unit as a heat exchanging unit 395 in which the fins 395c have a minute thermal separation gap and are integrated with each other, and are condensed by the thermal separation gap. The heat transfer from the evaporator 32 side to the evaporator 31 side can be suppressed to such an extent that the growth of frost and ice in the evaporator 31 can be suppressed, and the frost can be melted together with the refrigerant temperature rise to ensure high drying efficiency even at low outside temperatures. I am doing so. This eliminates the isolation space previously provided between the evaporator 31 and the condenser 32 and reduces the installation space, while suppressing bypass passage caused by play in the isolation space toward the suction / discharge port 392 side. The effective area can be kept large, heat exchange efficiency and drying efficiency can be increased, and drying noise can be reduced.

  According to the present invention, the spiral casing of the blower fan used in the drying process in the drum type washing and drying machine is divided into two parts in a high rigidity as a highly rigid part divided substantially at the center in the axial direction. The tongs provided on one half-shell are protruded toward the other half-shell to cope with the fan height, improving the guide function for the blown air and increasing the air flow and static pressure. It will be effective and suitable for further enhancement of the drying function.

It is a rear view which shows the internal structure of the drum type washing-drying machine which mounts the air conditioning and fan unit which concerns on embodiment of this invention. It is a side view of the principal part of the internal structure of the washing / drying machine. It is a perspective view of an air conditioning and a fan unit. It is a cross-sectional view which shows the connection structure of an air conditioning unit and a ventilation fan. It is a perspective view of a ventilation fan. It is a perspective view of one half-shell of a ventilation fan. It is the top view seen from the blower outlet side of the ventilation fan. It is a cross-sectional view showing one example of an air conditioning / fan unit. It is a cross-sectional view showing another example of an air conditioning / fan unit. It is a rear view which shows the ventilation guide which is a part connected to the water tank of a ventilation path. It is a top view of the ventilation guide. It is a perspective view which shows the rear part half shell of the ventilation guide. It is a perspective view which shows the front part side half shell of the ventilation guide. It is a cross-sectional view which shows the connection part of the air conditioning unit of the conventional air conditioning and fan unit, and a ventilation fan. It is a perspective view which shows the conventional ventilation fan. It is a cross-sectional view of the blowing part of the same blower fan. It is a perspective view which shows another conventional ventilation fan. It is the top view which looked at the same ventilation fan from the blower outlet side. It is a perspective view which shows the tongue part of the same ventilation fan. It is a rear view of the ventilation guide connected with the water tank of the conventional ventilation path. It is a side view of the ventilation guide. It is a side view which shows the internal structure of the drum type washing-drying machine of the other example which mounts the conventional air conditioning and fan unit.

Explanation of symbols

12 Matching surface 15 Blower fan 15a Fan 15b Swirl casing 15b1, 15b2 Half shell 15c Suction port 15c1 Connection port 15d Blowout port 15d1 Blowout port 15e Vortex unit 31 Evaporator 32 Condenser 37 Compressor 102 Seal unit 106 Tongue 106a Auxiliary tongue 200 Screw S3 clearance

Claims (3)

Install the rotating drum in the aquarium so that the rotating shaft is oriented horizontally or inclined downward from the horizontal direction with the rotating drum facing the rear side, and with the rotation of the rotating drum, each step of washing, rinsing, dehydration, and blower fan After aspirating the air in the aquarium, the drying process of drying the laundry by blowing it into the aquarium as high-temperature air that has been passed through a heat exchanger for dehumidification and a heat exchanger for heating, Drum-type laundry drying provided with a tongue that branches and rectifies the air flow toward the blow-out port and the air flow that goes back to the blow-off port, extending from the starting point of the swirl portion of the swirl casing toward the blow-off portion side. In the machine
The spiral casing of the blower fan is integrated by combining the half shells divided into two at substantially the center position in the axial direction, and the tongue protrudes from the spiral start point side to one of the half shells, In addition, the drum-type washing and drying machine is characterized in that the protruding portion is formed so as to have a gap for avoiding mutual interference with the other side, and is provided to protrude to the outer peripheral side of the fan.   The tongue is molded in a form in which the outer surface is recessed on the side of the half-shell that houses the rotating substrate side of the fan, and the width and height from the spiral start point of the spiral part and the blowing part toward the blowing part side. The drum type washing and drying machine according to claim 1, wherein the drum type washing and drying machine is provided so as to be streamlined so as to extend gradually and to have a height substantially equal to that of the fan at the end of the spiral start point.   The drum-type drum according to claim 2, wherein auxiliary tongs are provided on the side of each half-shell that has a suction opening, the auxiliary tongs being less than the depth and suppressed to a height that does not interfere with the tongs. Washing and drying machine.

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