JP2010065616A - Centrifugal type blower and drying apparatus equipped with centrifugal type blower - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a centrifugal type blower that suppresses an increase in blowing noise and prevents lowering of blowing performance when duct resistance becomes large in a blowing circuit of the centrifugal type blower having a scroll type casing, and a washing/drying machine that suppresses an increase in drying noise using the centrifugal type blower. <P>SOLUTION: A distance between an upper plate 8b and a bottom plate 8c configuring the casing 8 is set by bending the bottom plate 8c so that a distance h1 of a portion 8d on the outside of an impeller 5 becomes larger than a distance h2 of a portion 8e on the inside of the impeller 5, to increase the capacity in the casing 8 on a main plate 2 side of the impeller, decelerate an air stream flowing out of the main plate 2 side of the impeller 5, and spread the air stream to a capacity enlarged portion of the bottom plate 8d. Thereby, a directional component of the air stream from the main plate 2 side toward a side plate 3 side of the impeller 5 is made small and is blown out along a spiral wall face 8a from a blowout port 10 of the casing 8. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a centrifugal blower for a blower circuit that circulates between a storage portion of the object to be dried and a heat pump unit in a drying method for drying an object to be dried such as a laundry by using a heat pump, and its centrifugal It is related with the structure of the drying apparatus which comprised the air blower.

  In recent years, a washing / drying machine is known as a representative of this type of drying apparatus. In the washer / dryer market, the drum-type washer / dryer market that performs washing, dehydration and drying in the same rotating tank is rapidly expanding. Compared to the conventional heater type, there is less clothing pain and energy saving. There is an increasing demand for washing dryers equipped with a heat pump type drying function.

  Conventionally, in a blower circuit that circulates between a rotary tank, a heat pump unit, and a heater, not only normal duct resistance but also a certain amount of dust adheres to a filter for removing dust from clothes etc. Centrifugal blowers having scroll-type casings have been used because they do not deteriorate the blowing action.

  However, the duct cross-sectional area of the blower circuit is reduced due to the downsizing of the casing of the washing and drying machine, and the fin pitch is packed to improve the performance of the heat pump, the heat absorber in the heat pump unit, and the radiator. When the duct resistance in the blower circuit increases, it is required to suppress an increase in blowing noise and a decrease in blowing performance in a centrifugal blower having a scroll-type casing.

  There exists a thing described in patent document 1 as a prior art of the centrifugal air blower with a scroll casing.

  9 and 10 show a centrifugal blower having a scroll casing described in Patent Document 1, FIG. 9 is a perspective view, and FIG. 10 is a cross-sectional view taken along the line CC in FIG. is there.

  9 and 10, reference numeral 101 denotes a casing, which is a spirally wound winding plate 102, a flat plate 113 connected to the beginning of the winding, and side plates 103 and 104 that close both ends of the winding plate 102 and the flat plate 113. Consists of. The side plate 103 is provided with a suction port 111, and a bell mouth 112 is formed around the suction port 111. An outlet 114 is formed by both ends of the winding plate 102 and the flat plate 113 and the side plates 103 and 104.

  An impeller 105 is built in the casing 101, and the impeller 105 has a large number of forward wings 106 arranged at equal intervals along the circumferential direction, and a circle that supports the right end of the forward wings 106. It consists of an annular support plate 107 and a disc-shaped hub 108 that supports the left end. A rotating shaft 109 is fixed at the center of the hub 108, and the rotating shaft 109 penetrates through the side plate 104 and protrudes to the outside, and its protruding end is connected to the motor 110.

  Next, the operation of the centrifugal blower described in Patent Document 1 will be described.

  First, when the impeller 105 is driven by the motor 110 via the rotation shaft 109, air is guided from the suction port 111 to the bell mouth 112 and sucked into the casing 101. Then, the air enters the impeller 105 through the central opening of the support plate 107, is energized in the process of passing through the gaps of the many forward wings 106, flows out of the impeller 105, and is guided to the inner surface of the winding plate 102. And blown out from the outlet 114.

  Here, the axial width of the outlet 114 is reduced by providing a rectangular parallelepiped reducing member 130 on the right side of the outlet 114, that is, on the side plate 103 on the suction inlet 111 side.

  In general, in this type of blower, a three-dimensional flow in the casing 101 causes a drift toward the air outlet 114, and a backflow region is generated near the side plate 103 of the air outlet 114. There has been a problem that the main flow is changed, and the flow blown out from the blow-out port 114 becomes unstable due to this, and the unstable flow increases noise and the sound quality also deteriorates.

However, in the above blower, the Coanda effect in which the backflow region is reduced by the reduction member 130 provided at the outlet 114, and as a result, partial backflow is suppressed, and the main flow of the outlet 114 flows along the reduction member 130. As a result, the flow is stabilized, noise can be suppressed and the sound quality can be improved.
JP-A-10-159798

  However, when a centrifugal blower having a scroll-type casing as described above is disposed in a large duct resistance blower circuit such as a heat pump washer / dryer, the air flowing from the suction port 111 is biased to the hub 108. When discharging from a large number of forward wings 106, it is biased toward the hub side 108. As a result, in the width direction of the forward wings 106, the radial component of the discharged airflow is large on the hub 108 side and small on the support plate 107 side. Distribution.

  Therefore, the airflow flowing out from the hub 108 side of the impeller 105 is guided to the inner surface of the winding plate 102, and most of the airflow is guided to the inner surface of the winding plate 102 and blown out from the outlet 114. A part of the flow then flows from the hub 108 side of the winding plate 102 toward the support plate 107 side. On the support plate 107 side, since the circumferential component is strong, the flow is directed toward the flat plate 113 without being blown out from the blowout port 114. Here, since the suction port 111 side has a low pressure in the casing 101 and the blowout port 114 side, a part thereof does not go to the blowout port 114 side, and the support plate 107 is interposed between the impeller 105 and the side plate 103. And the tip of the bell mouth 112 are blown out into the suction port 111 in a jet state.

  As a result, a large speed difference is generated between the air flow velocity from the upstream side of the suction port 111, the shearing stress of the air flow is increased, the inflow air flow is disturbed, and the suction plate 111 reaches the suction port 111 on the side plate 103 side. Circulation flow was generated, and blowing noise increased and blowing performance decreased.

  For this reason, in the conventional centrifugal blower, the airflow flowing out from the hub 108 side of the impeller 105 is wound outside by forming a large distance from the rotating shaft 109 of the impeller 105 of the winding plate 102 of the casing 101. Although the flow from the hub 108 side to the support plate 107 side of the plate 102 is suppressed, such a configuration increases the outer dimension of the casing 101 in the radial direction, so that the washing and drying machine equipped with a drum or a heat pump unit is used. When installed, storage becomes difficult, and the washing and drying machine itself has to be enlarged.

  The present invention solves the above-described conventional problems, and even in the case of a configuration in which a centrifugal blower having a scroll type casing is arranged in a blower circuit having a large duct resistance such as a heat pump type washing and drying machine. , Without increasing the outer dimension of the casing in the radial direction, the air is blown from the casing in the vicinity of the air outlet to the air inlet, and the inflow air current is prevented from being disturbed at the air inlet, and the circulating flow is suppressed. An object of the present invention is to provide a centrifugal blower that suppresses an increase and prevents a decrease in blowing performance, and further provides a washing and drying machine that suppresses an increase in noise during drying operation and a decrease in drying performance.

  In order to solve the above-mentioned conventional problems, the present invention is a centrifugal blower comprising an impeller having a main plate, an annular side plate, and a plurality of blades, and a casing containing the impeller. The upper plate having a bell mouth-like suction port on the annular side plate side of the impeller, and the side wall extending from the tongue portion so as to be a spiral and surrounding the periphery of the impeller in the radial direction And the bottom plate on the main plate side of the impeller, and further the distance between the bottom plate and the upper plate of the casing, the portion outside the outer diameter of the impeller is more than the portion inside the outer diameter of the impeller The bottom plate is bent so as to be larger.

  With this configuration, the volume up to the spiral side wall on the main plate side of the casing can be expanded, and as a result, the airflow flowing out from the main plate side of the impeller can be decelerated and also expanded to the protruding bottom plate side. . Therefore, the direction component of the airflow from the main plate side to the side plate side is reduced, and a flow that is blown out from the outlet of the casing along the spiral side wall is easily formed. As a result, it is possible to suppress the jet flow that blows from the gap between the side plate and the tip of the bell mouth to the suction port through the space between the side plate of the impeller and the upper plate on the suction port side that constitutes the casing. .

  The centrifugal blower having the scroll-type casing of the present invention has a side plate of the impeller and the tip of the bell mouth without increasing the outer dimension in the radial direction of the casing even when duct resistance increases in the blower circuit. It is possible to suppress the jet that blows out from the gap to the suction port.

  As a result, the turbulence of the inflow air flow at the suction port due to blowing from the casing near the blowout port to the suction port is suppressed, and the flow that circulates between the side plate and the bell mouth tip to the impeller is suppressed. can do. Therefore, while suppressing the increase in ventilation noise, the fall of ventilation performance can be prevented.

  In addition, in the case of a drying apparatus equipped with such a centrifugal blower, a quiet drying operation can be expected, and a decrease in drying performance accompanying a decrease in blowing performance can be suppressed, thereby improving reliability.

  The invention according to claim 1 is a centrifugal blower including an impeller having a main plate, an annular side plate, and a plurality of blades, a suction port and a blowout port, and a casing containing the impeller. The casing has an upper plate having a bell mouth-like suction port on the annular side plate side of the impeller, a tongue, and is spiral, and surrounds the periphery of the impeller in the radial direction. It is composed of an extended side wall and a bottom plate located on the main plate side of the impeller, and further the distance between the bottom plate and the upper plate of the casing is a portion outside the outer diameter of the impeller, the outer diameter of the impeller The bottom plate is bent so as to be larger than the inner part.

  By adopting such a configuration, the casing has a configuration in which the volume to the spiral side wall on the main plate side of the impeller is increased, and as a result, in the distribution of the air flow passing through the impeller, the air flow close to the main plate side is decelerated. In the impeller, the direction component of the airflow from the main plate side to the side plate side is reduced, and the air is blown out from the outlet of the casing along the spiral side wall. Therefore, it is possible to suppress the jet flow from the gap between the side plate and the tip of the bell mouth to the suction port through the gap between the side plate of the impeller and the upper plate on the suction port side constituting the casing.

  As a result, a reverse flow at the suction port of the casing that is likely to occur when a ventilating path such as a duct is connected to the blowout port, such as a duct, that is, the flow from the casing near the blowout port to the suction port. Disturbance of the inflow airflow at the suction port accompanying the discharge can be suppressed, and the flow circulating between the side plate and the tip of the bell mouth to the impeller can be suppressed. Therefore, an increase in blowing noise can be suppressed and a decrease in blowing performance can be prevented.

  The invention according to claim 2 is the invention according to claim 1, wherein the bottom plate of the casing is inclined in the direction opposite to the upper plate from the outer periphery of the impeller to the spiral side wall. .

  With this configuration, in the distribution of the airflow that has passed through the impeller, the airflow close to the main plate side is smoothly decelerated along the wall surface on the bottom plate side of the casing, and the bottom plate is inclined and protrudes. However, since it gradually spreads to the bottom plate side, it is possible to suppress turbulence of the airflow when reaching the spiral side wall of the casing, and to suppress an increase in blowing noise due to the turbulence of the airflow in the casing, as well as static pressure by the casing The conversion ability can be improved.

  According to a third aspect of the present invention, in the first or second aspect of the present invention, the tongue portion is provided across the rotational axis direction of the impeller, and the shape of the tip thereof is provided on the rotational axis of the impeller. In a cross section orthogonal to each other, it has a substantially arc shape, and further, the tip of the tongue is extended so that the main plate side is higher than the side plate side of the impeller with the rotation axis of the impeller as a base axis. It is.

  By adopting such a configuration, the airflow from the impeller is blown out earlier from the outlet in the vicinity of the tongue portion at a position substantially opposed to the main plate side than a position substantially opposed to the side plate side. Therefore, the pressure at the outlet side of the tongue at a position substantially opposite to the main plate side of the impeller is lower than that at the outlet side of the tongue at a position substantially opposite to the side plate side. As a result, the airflow in the vicinity of the tongue at the portion substantially opposite to the side plate side of the impeller has a strong circumferential component, and the airflow discharged from the impeller has a strong circumferential component is positioned substantially opposite the main plate side. Gently swirl the tip of the tongue so that it goes to, and blow out from the outlet.

  Therefore, in the vicinity of the tongue portion, the jet flow that blows out from the gap between the support plate and the tip of the bell mouth from the inside of the casing through the side plate of the impeller and the side plate on the suction port side of the casing is suppressed. Can do. As a result, it is possible to blow out from the casing in the vicinity of the tongue portion to the suction port, disturb the inflow airflow at the suction port, suppress the circulating flow, and further suppress the blowing noise.

  According to a fourth aspect of the present invention, there is provided a storage unit that is disposed in a housing and stores a material to be dried such as clothing, a heat pump device that is disposed inside the housing, and air that is heat-exchanged by the heat pump device. Drying provided with a wind circuit having an air supply duct and an exhaust duct that conveys the air exchanged by the air blowing means into the storage unit and circulates the air exchanged from the storage unit to the heat pump device. The heat pump device includes: a compressor; a radiator through which the refrigerant compressed by the compressor flows; a throttle unit that depressurizes a high-pressure refrigerant that has flowed through the radiator; and the reduced pressure The heat absorber through which the refrigerant flows has a refrigerant circulation circuit connected so that the refrigerant circulates, further houses the heat absorber and the radiator, and the heat absorber side is in front. A heat exchange chamber is provided that communicates with the exhaust duct side, the radiator side communicates with the air supply duct side, and the blower means is the centrifugal blower according to any one of claims 1 to 3, It is a drying device in which a bell mouth-like suction port of a blower is connected to the radiator side of the heat exchange chamber and a blower outlet of the centrifugal blower is connected to the air supply duct.

  With such a configuration, the drying device is a drum type heat pump device that performs washing, dehydration and drying in the same rotating tub, and a blowing circuit having a relatively large ventilation resistance as in the case of a washing dryer equipped with blowing means. Even if it has a configuration, the suction port of the centrifugal blower is directly connected to the radiator air passage of the heat pump device, thereby increasing the dry noise without increasing the outer dimension in the radial direction of the casing of the centrifugal blower. Further, it is possible to suppress a decrease in drying performance, and to be integrated into the housing in a compact manner together with the heat pump device.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. The present invention is not limited to the embodiments.

(Embodiment 1)
FIG. 1 is a front view of a state where an upper plate and a side plate of an impeller constituting a casing of a centrifugal blower in Embodiment 1 of the present invention are removed. FIG. 2 is a side view seen from the outlet side of the centrifugal blower according to Embodiment 1 of the present invention. 3 is a cross-sectional view of the centrifugal blower according to Embodiment 1 of the present invention, taken along line AA in FIG.

  As shown in FIGS. 1 to 3, a centrifugal blower (hereinafter referred to as a blower) 1 includes a casing 8 having a suction port 6 and an outlet 10, and an impeller 5 provided in the casing 8. ing. The impeller 5 includes a disc-shaped main plate 2, an annular side plate 3 arranged at a predetermined interval from the main plate 2, and a number of forward wings arranged in a circular shape along the outer periphery of the main plate 2 and the side plate 3. The configuration is made up of blades 4. Further, the casing 8 is spiral and has a predetermined interval with the upper plate 8b provided with the bell mouth-like suction port 6 on the side plate 3 side of the impeller 5 and the tongue 7 as a base point. A wall surface 8a extending so as to surround the periphery, and a bottom plate 8c positioned on the main plate 2 side of the impeller 5 so as to face the upper plate 8b. Due to the configuration of the casing 8, the air outlet 10 is formed between the terminal end 9 of the spiral wall surface 8 a and the tongue 7.

  The tongue 7 is provided as one of the purposes for stabilizing the direction of the airflow blown from the blowout port 10, and is positioned over the rotation axis direction (width direction) of the impeller 5 on the blowout port 10 side. The tip 7x is formed in a substantially arc shape in a cross section orthogonal to the rotation shaft 5a of the impeller 5. Further, the tip 7x of the tongue 7 is substantially opposed to the main plate 2 rather than the side (hereinafter referred to as the side plate side) 7b that is substantially opposed to the side plate 3 of the impeller 5 with the rotation axis of the impeller 5 as a base axis. The side 7a (hereinafter referred to as the main plate side) 7a is in a high position and has a shape extending in the counter-rotating direction of the impeller 5.

  The bottom plate 8c constituting the casing 8 is bent so that the portion 8d outside the outer diameter of the impeller 5 is substantially parallel to the axis of the impeller 5, and the top plate 8a and the bottom plate in the outer portion 8d are bent. The distance h1 of 8c is formed so as to be larger than the distance h2 of the upper plate 8a and the bottom plate 8c in the portion 8e inside the outer diameter of the impeller 5.

  Further, a driving motor 11 is directly connected to the rotating shaft 5a of the impeller 5 via a vibration isolating rubber 5b.

  The operation of the centrifugal blower 1 configured as described above will be described below.

  First, when the impeller 5 is driven by the motor 11 via the rotating shaft 5a, air is guided from the bell mouth-shaped suction port 6 and sucked into the casing 8 as shown by an arrow X in FIG. Then, in the process of passing through the annular side plate 3 and entering the inside of the impeller 5 and passing between a large number of blades 4, dynamic pressure and static pressure are applied and flow out of the impeller 5. Then, as indicated by an arrow Y in FIG. 1, the space between the inside of the spiral wall surface 8a and the impeller 5 is guided to efficiently convert the dynamic pressure into a static pressure, and the air is blown out from the blowout port 10 to perform a blowing action.

  Here, in the distance between the bottom plate 8c and the upper plate 8a constituting the casing 8, the distance h1 of the portion 8d outside the outer diameter of the impeller 5 in the bottom plate 8c is the distance of the portion 8e within the outer diameter of the impeller 5. By projecting and forming the bottom plate 8c in a direction larger than h2, the volume up to the wall surface 8a on the main plate 2 side of the impeller 5 is expanded in the casing 8 and, as a result, flows out from the main plate 2 side of the impeller 5 Since the airflow is decelerated and also spreads toward the protruding outer portion 8d as indicated by arrow Z, the direction component of the airflow from the main plate 2 side to the side plate 3 side of the impeller 5 is reduced, and the spiral wall surface 8a. Along the air flow from the air outlet 10 of the casing 8 (arrow in FIG. 2).

  Therefore, from the inside of the casing 8 through the gap between the side plate 3 of the impeller 5 and the upper plate 8b on the suction port 6 side, the gap between the side plate 3 and the tip 6a of the bell mouth-shaped suction port 6 is changed to the suction port 6. The jet stream (arrow x in FIG. 3) that blows out can be suppressed.

  As a result, the turbulent flow at the suction port 6 that is likely to occur when the duct resistance is increased in the blower circuit without increasing the radial dimension of the casing 8 or suppressing the increase in length thereof, that is, Disturbance of the inflow airflow at the suction port 6 caused by blowing a part of the airflow in the casing 8 from the vicinity of the blowout port 10 to the suction port 6 can be suppressed, and the side plate 3 and the bell mouth-like suction are further suppressed. The circulation flow which flows between the front-end | tip 6a of the opening | mouth 6 and flows into the impeller 5 again can be suppressed. Therefore, an increase in blowing noise can be suppressed and a decrease in blowing performance can be prevented.

  Further, the tip 7x of the tongue portion 7 in the width direction of the blade 4 from the side plate side 7b substantially facing the side plate 3 toward the main plate side 7a substantially facing the main plate 2 in the counter-rotating direction of the impeller 5; In addition, since the main plate side 7a has a shape extending so as to be higher than the side plate side 7b, the airflow in the vicinity of the tongue 7 is compared with the side plate side 7b in a range substantially opposed to the width direction of the blade 4. The main plate side 7a is blown out from the blowout port 10 first. Therefore, in the blowout port 10, the pressure on the main plate side 7a is lower than that on the side plate side 7b. As a result, the air current having a strong circumferential component discharged from the impeller 5 in the vicinity of the tongue 7 on the side plate side 7 b is directed toward the main plate 7 a, smoothly flows around the tip 7 x of the tongue 7, and blows from the outlet 10. put out.

  Therefore, as described above, the extending shape of the tongue portion 7 is the counter-rotating direction of the impeller 5 from the side plate side 7b substantially facing the side plate 3 toward the main plate side 7a substantially facing the main plate 2, and the main plate side 7a is Also by forming the shape so as to be higher than the side plate side 7 b, the side plate 3 of the impeller 5 and the upper plate 8 b on the suction port 6 side of the casing 8 from the inside of the casing 8 in the vicinity of the tongue 7. Through the gap, it is possible to suppress the jet flow (arrow x) that blows out to the suction port 6 from the gap between the side plate 3 and the tip 6a of the bell mouth-shaped suction port 6.

  As a result, the disturbance of the inflow airflow at the suction port 6 can be suppressed, and further the blowing noise can be suppressed.

  In the first embodiment of the present invention, many blades 4 of the impeller 5 are forward wings in the rotational direction, but the same effect can be expected with radial wings and backward wings.

(Embodiment 2)
FIG. 4 is a front cross-sectional view showing a state where an upper plate and a side plate of an impeller constituting a casing of a centrifugal blower in Embodiment 2 of the present invention are removed. FIG. 5 is a cross-sectional view of the centrifugal blower according to Embodiment 2 of the present invention, taken along line BB in FIG. The same constituent elements as those of the first embodiment are denoted by the same reference numerals, description thereof is omitted, and differences from the first embodiment will be mainly described.

  The difference from the first embodiment is that, as shown in FIG. 4 and FIG. 5, the configuration in which the volume of the outer peripheral portion of the casing 8 is increased is the portion 8g outside the outer diameter of the impeller 5 in the bottom plate 8f. Further, it is a point that is bent at a predetermined angle in a direction opposite to the upper plate 8b over the spiral side wall 8a to form an inclined surface.

  Therefore, the airflow flowing out from the main plate 2 side of the impeller 5 is smoothly decelerated along the wall surface on the portion 8g side outside the outer diameter of the impeller 5 of the bottom plate 8f of the casing 8 as shown by an arrow Z in FIG. And, when it extends along the outer portion 8g of the protruding bottom plate 8f, it reaches the spiral side wall 8a without increasing the radial dimension of the casing 8 or suppressing the increase in length. Can be suppressed. Therefore, as in the first embodiment, it is possible to suppress an increase in blowing noise due to airflow turbulence in the casing 8 and to improve the static pressure conversion capability of the casing 8.

  In particular, the spread along the bottom plate 8f in the process in which the airflow flowing out from the impeller 5 reaches the spiral side wall a is spread along the surface of the outer portion 8g of the bottom plate 8f inclined at a predetermined angle. , Rapid spread can be suppressed and more silence can be expected.

(Embodiment 3)
FIG. 6 is a rear view showing the internal structure of the washing / drying machine according to Embodiment 3 of the present invention. FIG. 7: is the front view seen from the upper side of the heat pump apparatus mounted in the washing / drying machine. FIG. 8 is a system conceptual diagram showing the configuration of the refrigerant circuit and the flow of drying air in the washing and drying machine.

  A centrifugal blower having the configuration described in the first embodiment or the second embodiment is connected to the heat pump device mounted on the washing and drying machine in the third embodiment. Accordingly, the centrifugal blower is denoted by the same reference numeral, and detailed description thereof is omitted.

  6 to 8, a cylindrical water tank 53 (corresponding to the storage portion of the present invention) 53 elastically supported by a plurality of suspensions 52 is provided inside a casing 51 constituting the main body of the washing / drying machine 50. Is provided.

  Inside the water tank 53, a cylindrical and horizontal axis type rotating tank (not shown) that accommodates clothes 54 and the like is rotatably provided, and is driven to rotate by a drive motor 55.

  A heat pump unit 57 connected to the water tank 53 via the exhaust duct 56 is provided at the lower back of the housing 51.

  The heat pump unit 57 includes a heat absorber air passage 58 and a radiator air passage 59, and a unit in which a heat exchange chamber 60 that communicates the heat absorber air passage 58 and the radiator air passage 59 and a compressor chamber 61 are formed. Case 62, heat absorber 63 and radiator 64 provided in heat exchange chamber 60, capillary tube (corresponding to the throttle means of the present invention) 65 connecting radiator 64 and heat absorber 63, compressor chamber 61 The heat pump cycle (refrigerant circuit) is configured by connecting the compressor 66, the radiator 64, the capillary tube 65, and the heat absorber 63.

  In the unit case 62 of the heat pump unit 57, the heat absorber 63 and the radiator 64 are arranged in the heat exchanger chamber 60 so that the respective opening surfaces face each other, and the compressor 66 is arranged in the substantially left direction of the casing 51. Arranged side by side with the heat exchange chamber 61, the inlet 58a of the heat sink air passage 58 is disposed above the compressor chamber 61, and the discharge port 59a of the radiator air passage 59 is disposed on the side where the compressor chamber 61 is disposed. It is the structure arrange | positioned in the substantially right side of the heat exchanger chamber 60 opposite to. Therefore, the heat absorber 63 is disposed on the windward side of the radiator 64.

  In addition, on the right side of the heat pump unit 57, air blowing means is arranged. The blower means is the centrifugal blower 1 having the configuration described in the first or second embodiment, and the casing 8 has a spiral wall surface 8a, an upper plate 8b, and a bottom plate 8c formed by resin molding of a mold. The structure is formed integrally. The bell mouth-shaped suction port 6 of the centrifugal blower 1 is directly connected to the discharge port 59 a of the radiator air path 59. Further, the blowout port 10 of the centrifugal blower 1 is connected to an air supply duct 67 opened inside the water tank 53. In connection of this blower outlet 10 and the air supply duct 67, the shape of the blower outlet 10 is processed and formed so that a connection with the air supply duct 67 is possible, and is not restricted to the rectangle shown in FIG.

  The operation of the washing / drying machine 50 configured as described above will be described.

  In the washing (washing) process, a predetermined amount of water is supplied into the water tank 53 from a water supply or the like (not shown), and the driving motor 55 is driven to rotate the clothes 54 and the rotating tank containing the washing water. Perform laundry for a predetermined time.

  Next, in the dehydration step, a drain valve (not shown) is opened to drain the water in the water tank 53 to the outside of the washing / drying machine 50, and then the rotary tank containing the clothes 54 and the like is moved in one direction by the drive motor 55. It rotates at high speed and dehydrates by its centrifugal force.

  And when the above-mentioned dehydration process is completed, it will move to a drying process.

  In this drying process, when the compressor 66 of the heat pump unit 57 is operated, the refrigerant is compressed, and this pressure causes the refrigerant to circulate through the radiator 64, the capillary tube 65, and the heat absorber 63 sequentially. As a result, heat is released in the radiator 64, and heat is absorbed in the heat absorber 63 by the refrigerant whose pressure is reduced by the capillary tube 65 to a low pressure.

  In parallel with this, the centrifugal blower 1 is operated, and warm air heated by the heat radiation of the radiator 64 is blown into the water tank 53 and the rotating tank through the air supply duct 67. The rotating tub is rotationally driven by the drive motor 55, and the clothes 54 and the like are in a state of being stirred up and down.

  Therefore, the warm air supplied into the rotating tub takes moisture when passing through a gap such as clothing 54, and the heat absorber 63 passes through the heat absorber air passage 58 from the exhaust duct 56 connected to the water tub 53 in a wet state. When passing through the heat absorber 63, sensible heat and latent heat are deprived and dehumidified, and separated into dry air and condensed water. The dry air is heated when it passes through the radiator 64 again, and the circulation operation described above is performed for a predetermined time to dry the clothes 54 and the like.

  The drying process is completed when the above operation is performed for a predetermined time.

  Here, as shown in FIG. 6, the heat pump unit 57 has a compressor 66 arranged side by side with the heat exchange chamber 61 in the left direction of the housing 51 when viewed from the back side of the housing 51, and the heat absorber air passage. 58 is positioned substantially above the compressor 15, and the centrifugal blower 1 is further connected to the compressor 66 when viewed from the back side of the casing 51, which is the discharge port 59 a side of the radiator air passage 59. Are arranged in the opposite direction. With this configuration, the components of the refrigerant circuit and the air path components in the heat pump unit 57 and the connection structure of the exhaust duct 56 and the air supply duct 67 are as follows. As a result, it can be stored in the empty space at the rear lower part of the casing 51.

  And the duct resistance in the ventilation circuit of the washing dryer 50 including the exhaust duct 56, the air supply duct 67, etc. becomes large by using the centrifugal blower 1 of Embodiment 1 or Embodiment 2 of the present invention. However, without increasing the outer dimension of the casing 8 of the centrifugal blower 1 in the radial direction, an increase in drying noise and a decrease in drying performance can be suppressed, and in combination with this, the suction port 6 is connected to the radiator of the heat pump unit 57. By adopting a configuration in which the discharge port 59a provided in the air passage 59 is directly connected, the heat pump unit 57 can be compactly arranged and stored in a space formed in the lower rear portion of the water tank 53 of the housing 51.

  As described above, the centrifugal blower according to the present invention suppresses increase in blowing noise and blower performance even when the duct resistance of the blower circuit increases as the centrifugal blower is housed or disposed in the middle. Can be prevented, so that both air blowing performance and high heat exchanging capacity as a heat pump unit can be achieved, and noise can be reduced. Air conditioning equipment such as air conditioners, refrigeration and refrigeration equipment such as home refrigerators and vending machines, heat pump equipment such as water heaters, and electronic equipment with thermoelectric components as well as AV equipment and waste heat recovery equipment Is also applicable.

The front view of the state which removed the upper plate which comprises the casing of the centrifugal air blower in Embodiment 1 of this invention, and the side plate of an impeller The side view seen from the blower outlet side of the centrifugal blower in Embodiment 1 of invention Sectional drawing by the AA line of FIG. 1 of the centrifugal blower in Embodiment 1 of this invention Front sectional drawing of the state which removed the upper board which comprises the casing of the centrifugal blower in Embodiment 2 of this invention, and the side plate of an impeller Sectional drawing by the BB line of FIG. 4 of the centrifugal blower in Embodiment 2 of this invention The rear view which shows the internal structure of the washing-drying machine in Embodiment 3 of this invention Front view of the heat pump installed in the washer / dryer as seen from above System conceptual diagram showing the configuration of the refrigerant circuit and the flow of drying air in the washing and drying machine A perspective view of a centrifugal blower having a conventional casing Sectional view by CC line of FIG.

Explanation of symbols

1 Centrifugal blower (air blowing means)
2 main plate 3 side plate 4 blade 5 impeller 5a rotating shaft 6 suction port 7 tongue 7a main plate side 7b side plate side 7x tip 8 casing 8a spiral wall surface 8b upper plate 8c bottom plate 8d outer portion 8e inner portion 8f bottom plate 8f Part 10 Outlet 50 Washing / drying machine 51 Case 53 Water tank (storage part)
54 Clothes 56 Exhaust Duct 57 Heat Pump Unit 58 Heat Absorber Air Path 58a Inlet 59 Heat Dissipator Air Path 59a Discharge Port 60 Heat Exchange Chamber 63 Heat Absorber 64 Radiator 65 Capillary Tube (Throttle Means)
66 Compressor 67 Air supply duct

Claims (4)

  A centrifugal blower comprising a main plate, an annular side plate, an impeller having a plurality of blades, a casing having a suction port and an outlet, and enclosing the impeller, wherein the casing is the impeller An upper plate having a bell mouth-like suction port on the annular side plate side, a side wall extending from the tongue portion so as to be spiral, and surrounding the periphery of the impeller in the radial direction, and the impeller And the distance between the bottom plate and the upper plate of the casing is such that the portion outside the outer diameter of the impeller is larger than the portion inside the outer diameter of the impeller. A centrifugal blower in which the bottom plate is bent.   The centrifugal blower according to claim 1, wherein a bottom plate of the casing is inclined in a direction opposite to the upper plate from an outer periphery of the impeller to the spiral side wall.   The tongue is provided in the direction of the rotation axis of the impeller, and the shape of the tip thereof is substantially arcuate in a cross section perpendicular to the rotation axis of the impeller. The centrifugal blower according to claim 1 or 2, wherein the centrifugal fan is extended so that the main plate side is higher than the side plate side of the impeller with a rotation axis of the vehicle as a base axis.   A storage unit that is disposed in the housing and stores an object to be dried such as clothes, a heat pump device disposed in the housing, a blower that conveys air heat-exchanged by the heat pump device, and the blower A drying apparatus having a wind circuit having an air supply duct and an exhaust duct for supplying the heat-exchanged air into the storage section and circulating the air from the storage section to the heat pump apparatus. A compressor, a radiator through which the refrigerant compressed by the compressor flows, a throttle means for reducing the pressure of the high-pressure refrigerant flowing through the radiator, and a heat absorber through which the reduced refrigerant flows. A refrigerant circulation circuit connected so as to circulate, further containing the heat absorber and the radiator, and the heat absorber side communicating with the exhaust duct side, The heat-dissipating chamber which the heat radiator side connected to the said air supply duct side is provided, and the said air blower is set as the centrifugal blower as described in any one of Claim 1 to 3, The bellmouth-shaped of the said centrifugal blower A drying apparatus, wherein a suction port is connected to a radiator side of the heat exchange chamber, and a blowout port of the centrifugal blower is connected to the air supply duct side.