JP2011001838A - Centrifugal blower and drying apparatus equipped with the same - Google Patents

Abstract

In a centrifugal blower having a scroll type casing, there is provided a drying device that suppresses an increase in blowing noise, prevents a decrease in blowing performance, and suppresses an increase in drying noise.
By bending a region x on the outer peripheral side of the outer diameter of the impeller 5 of the upper plate 8b from the tongue 7 to the discharge port 10 in a direction gradually decreasing from the region y inside the impeller 5. The airflow on the side plate 3 side on the tongue 7 side is guided by the side wall 8a and is deflected in the circumferential direction. Moreover, since the distance between the region x of the bottom plate 8c and the upper plate 8b is large, the airflow is smoothly reduced while being decelerated. Converted to pressure. On the other hand, on the outlet 10 side where the distance between the impeller 5 and the peripheral side wall 8a is far, a part of the airflow that is displaced toward the main plate 2 side of the impeller 5 in the region x of the upper plate 8b is along the peripheral side wall 8a. The air flows between the side plate 3 and the upper plate 8b, and is blown out from the outlet 10 while being decelerated along the spiral peripheral side wall 8a on the upper plate 8b side, and is smoothly converted to static pressure.
[Selection] Figure 3

Description

  The present invention relates to a centrifugal blower employed in a blower unit and the like, and a drying apparatus equipped with the centrifugal blower.

  In recent years, the market for drum-type washing and drying machines that perform washing, dehydration and drying in the same rotating tank is rapidly expanding. A type of drying device is employed.

  In addition, such a washing and drying machine has not only a normal duct resistance but also a filter for removing dust and the like from clothes etc. in a blower circuit that circulates between the rotary tub and the heat pump unit and the heater. Therefore, a centrifugal blower having a scroll type casing is mainly employed as a blower device.

  However, the washing and drying machine is required to be further downsized, and due to the downsizing, the duct cross-sectional area of the blower circuit is reduced, or the heat pump unit that is a drying device is forced to be downsized. In centrifugal blowers with scroll-type casings, such as reducing the fin pitch to improve the performance of internal heat sinks and radiators, the increase in blowing noise accompanying the increase in duct resistance in the blowing circuit, or the blowing There is a demand for suppressing a decrease in performance.

  Generally, as a centrifugal blower having a scroll casing, a configuration described in Patent Document 1 is known.

  FIG. 11 is a perspective view of a centrifugal blower having a scroll casing described in Patent Document 1, and FIG. 12 is a cross-sectional view of the blower taken along line DD of FIG.

  11 and 12, the casing 101 includes a spirally wound winding plate 102, a flat plate 113 connected to the beginning of winding, and side plates 103 and 104 that close both ends of the winding plate 102 and the flat plate 113. . 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. The impeller 105 includes a large number of forward wings 106 arranged at equal intervals in the circumferential direction, an annular support plate 107 that supports the right end of the forward wings 106, and a disk-shaped hub that supports the left end. 108. A rotating shaft 109 is fixed at the center of the hub 108, and the rotating shaft 109 protrudes outside through the side plate 104, and its protruding end is connected to the motor 110.

  In the centrifugal blower having the above configuration, 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 1. 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, the blower having the above-described configuration is configured such that a three-dimensional flow in the casing 101 causes a drift toward the outlet 114, and a backflow region is generated near the side plate 103 of the outlet 114.

  Therefore, the centrifugal blower having a general configuration can cause fluctuation in the main flow of the outlet 114 due to the occurrence of the above-described backflow region, and the flow blown out from the outlet 114 becomes unstable. As a result, there is a problem that noise increases and sound quality deteriorates.

  The centrifugal blower having the configuration shown in FIG. 9 and FIG. 10 reduces the above-described reverse flow region by the reduction member 130 to suppress the partial reverse flow, and further, the Coanda effect in which the main flow of the outlet 114 flows along the reduction member 130. This stabilizes the flow, so that noise can be suppressed and the sound quality can be improved.

Japanese Patent Laid-Open No. 10-159798

  However, when the blower having the above-described configuration is arranged in a blower circuit having a large duct resistance, such as a washing / drying machine having a heat pump unit, the air flowing in from the suction port 111 is biased to the hub 108, and the large number of forward wings 106 When discharging, the state is biased toward the hub side 108 side.

  Therefore, in the width direction of the forward wing 106, the radial component of the discharged airflow is large on the hub 108 side and small on the support plate 107 side. 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 blown out from the outlet 114 while being guided to the inner surface of the winding plate 102. Flows from the hub 108 side of the winding plate 102 toward the support plate 107 side. Further, since the flow on the support plate 107 side has a strong circumferential component, a flow toward the flat plate 113 occurs without being blown out from the blowout port 114, and accordingly, in the casing 101 and on the blowout port 114 side. The suction port 111 side becomes a low pressure. As a result, a part of the airflow does not go to the blowout port 114 side, but is blown out in a jet state from the gap between the support plate 107 and the tip of the bell mouth 112 through the space between the impeller 105 and the side plate 103.

  Accordingly, a large speed difference is generated between the air flow velocity from the upstream side of the suction port 111, the shear stress of the air flow is increased, the inflow air flow is disturbed, and the circulation reaching the suction port 111 on the side plate 103 side of the blowout port 114. A flow was generated, and blowing noise increased and blowing performance was reduced.

  As a countermeasure, in the casing 101, by ensuring a large distance from the rotating shaft 109 formed between the inner surface of the winding plate 102 and the outer periphery of the impeller 105, the airflow flowing out from the hub 108 side of the impeller 105 to the outside is prevented. It is possible to suppress the flow of the wound plate 102 from the hub 108 side toward the support plate 107 side.

  However, such a configuration has a problem that the outer dimension of the casing in the radial direction is large, and when it is used in a washing / drying machine equipped with a drum or a heat pump unit, it is difficult to store the washing / drying machine itself. is there.

  The present invention solves the above-described conventional problems, and blows out from the casing near the blowout port to the suction port, suppresses the turbulence of the inflow airflow at the suction port and suppresses the circulating flow. The purpose of this is to suppress the increase in air flow and to suppress the decrease in air blowing performance.

  Another object of the present invention is to provide a drying apparatus such as a washing dryer that suppresses an increase in drying noise and suppresses a decrease in drying performance.

  In order to solve the above-described conventional problems, a centrifugal blower of the present invention includes an impeller and a casing containing the impeller, and the distance between the bottom plate and the upper plate constituting the casing is determined by the impeller. The region outside the outer diameter is set to be smaller than the region inside the outer diameter of the impeller.

  With this configuration, without increasing the radial dimension of the casing, the generation of the airflow flowing between the side plate and the upper plate of the impeller is suppressed, and the airflow blown out from the outlet of the casing along the spiral side wall on the upper plate side. Can be secured.

  Therefore, it is possible to obtain a centrifugal blower that suppresses an increase in blowing noise and suppresses a decrease in blowing performance.

  Moreover, since the said centrifugal blower can obtain the above-mentioned effect without enlarging the casing, it can be mounted on the drying device, and the size of the drying device can be suppressed.

  The centrifugal blower of the present invention suppresses the turbulence of the airflow at the suction port in the casing, and is particularly suitable for incorporation into a blower circuit having a large blower resistance, and suppresses deterioration in noise characteristics and blower performance. can do.

  Further, a drying apparatus equipped with such a centrifugal blower can be expected to achieve a quiet drying operation and an improvement in drying efficiency, and can improve reliability as a drying apparatus.

It is the front view which removed the upper plate and the side plate of an impeller which comprise the casing of the centrifugal air blower in Embodiment 1 of this invention. The side view seen from the blower outlet side of the centrifugal blower in the first embodiment 3 is a cross-sectional view of the centrifugal blower according to the first embodiment, taken along line AA in FIG. The front view which shows the internal structure of the centrifugal blower in Embodiment 2 of this invention in a see-through state Sectional drawing by the BB line of FIG. 4 of the centrifugal blower in Embodiment 2 Sectional drawing by CC line of FIG. 4 of the centrifugal air blower in Embodiment 2 The figure which shows the expansion | deployment degree of the involute shape from the tongue part 7 in the casing seen from the suction inlet side to the blower outlet 10 The rear view of the washing-drying machine in Embodiment 3 of this invention The figure seen from the upper side of the heat pump unit of the washing / drying machine in Embodiment 3 The system conceptual diagram which shows the structure of the refrigerant circuit of the washing dryer in Embodiment 3 and the flow of the air for drying A perspective view of a centrifugal blower having a conventional scroll casing Sectional drawing by the DD line of FIG. 9 in the same centrifugal blower

  The invention according to claim 1 includes a main plate, an annular side plate, an impeller composed of a plurality of blades provided between the main plate and the side plate, and a casing including the impeller and having a discharge port. In the centrifugal blower, the casing is located on the side plate side of the impeller and has a bell mouth-like suction port, a bottom plate located on the main plate side of the impeller, the upper plate and the bottom plate And a peripheral side wall extending in a spiral shape so as to surround the periphery of the impeller in the radial direction with a tongue portion provided in the vicinity of the discharge port as a base point, and a bottom plate of the casing The upper plate is bent to the bottom plate side so that a portion outside the outer diameter of the impeller is smaller than a portion inside the outer diameter of the impeller at a distance of the upper plate.

  By adopting such a configuration, the air flow that is discharged toward the main plate side of the impeller along the peripheral side wall of the casing at the portion of the upper plate outside the outer diameter of the impeller and bent toward the bottom plate side. The main blade side of the impeller is caused to flow from the main plate side to the side plate side, and a part of the airflow is prevented from flowing between the side plate and the upper plate of the impeller, and the casing is formed along the spiral side wall on the upper plate side. It blows out from the outlet.

  Therefore, in the casing, it is possible to suppress the jet flow that blows out from the gap between the side plate and the tip of the bell mouth through the gap between the side plate of the impeller and the upper plate on the suction port side that constitutes the casing. it can. As a result, even when duct resistance increases in the blower circuit, the airflow blown out from the casing to the suction port and the turbulence of the inflow airflow at the suction port due to this are suppressed, and the gap between the side plate and the bell mouth tip is suppressed. The flow which circulates through to the impeller can be suppressed. Therefore, while suppressing the increase in ventilation noise, the fall of ventilation performance can be prevented.

  According to a second aspect of the present invention, in the first aspect of the present invention, the distance between the bent portion of the bottom plate and the upper plate of the casing is from the tongue of the spiral peripheral side wall to the discharge port of the casing. It is designed to gradually become smaller.

  With this configuration, the airflow discharged from the impeller from the main plate side to the side plate side is originally guided by the side wall and deflected in the circumferential direction on the tongue side where the distance between the impeller and the peripheral side wall of the casing is short. As the distance between the flow and the bottom plate and the top plate increases, the pressure is smoothly converted to static pressure while being decelerated.

  On the other hand, on the air outlet side where the distance between the impeller and the peripheral side wall of the casing is far, the airflow is a portion of the upper plate bent to the bottom plate side, and the airflow discharged toward the main plate side of the impeller is offset. The casing flows along the side wall of the impeller from the main plate side to the side plate side, and further suppresses the flow of a part of the airflow between the side plate and the upper plate of the impeller, along the spiral side wall on the upper plate side. It blows out from the outlet.

  At this time, since the distance between the impeller and the side wall of the casing is sufficiently ensured, the deceleration of the airflow is not hindered and the static pressure conversion effect is sufficiently exhibited. Therefore, while suppressing the increase in ventilation noise, the fall of the static pressure conversion capability by a casing can be suppressed as much as possible.

According to a third aspect of the invention, in the first or second aspect of the invention, a portion of the upper plate of the casing outside the outer diameter of the impeller is inclined toward the bottom plate toward the peripheral side wall. In the configuration in which the inclined portion has a spiral shape with the tongue as a starting point, like the peripheral side wall of the casing, the enlarged angle of the spiral of the inclined portion of the upper plate is changed from the upper plate side to the peripheral side wall side. The size is gradually increased.

  By adopting such a configuration, on the side closer to the outer diameter of the impeller in the inclined portion of the upper plate, the radial component is extremely small from the vicinity of the side plate of the impeller, and the discharge airflow is substantially strong in the circumferential component. Even if the enlargement angle of the spiral is small, it can be smoothly decelerated and exhibit high static pressure conversion ability.

  On the other hand, in the inclined portion of the upper plate, on the side close to the side wall of the casing, the radial component of the air flow discharged from the impeller increases compared to the vicinity of the side plate. It is difficult to obtain a static pressure conversion effect. However, by increasing the swirl expansion angle from the side closer to the outer diameter of the impeller, the above-described air flow can be decelerated, and sufficient static pressure conversion capability is exhibited. Therefore, the static pressure conversion capability by the casing can be improved.

  Invention of Claim 4 is substantially circular arc shape in the cross section in which the front-end | tip is orthogonal to the rotating shaft of the said impeller in the invention as described in any one of Claim 1 to 3, And it is made into the shape extended in the anti-rotation direction of the said impeller toward the position which substantially opposes the main board side of the said impeller from the position substantially opposed to the support plate side of the said blade width direction.

  By adopting such a configuration, at the position facing the blade in the width direction in the vicinity of the tongue portion, the airflow at the position substantially opposite to the main plate side is blown out earlier from the outlet than the position substantially opposite 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. By this, the air current with strong circumferential component discharged from the impeller in the vicinity of the tongue portion at a position substantially opposite to the side plate side of the impeller is directed to a position substantially opposite to the main plate side, smoothly wraps around the tip of the tongue portion, It blows out from the outlet.

  Therefore, it is possible to suppress the jet flow that blows out from the gap between the support plate and the tip of the bell mouth to the suction port through the space between the side plate of the impeller and the side plate on the suction port side of the casing. Therefore, it can blow out from the casing near 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 fifth aspect of the present invention, there is provided a storage unit that is disposed in a housing and stores a matter to be dried such as clothing, a heat pump device that is disposed in a rear lower portion of the storage unit in the housing, and the heat pump device. And a supply duct for supplying the heat exchanged air from the heat pump device into the storage unit and circulating from the storage unit to the heat pump device. And a wind circuit having an exhaust duct, and the heat pump device includes a compressor, a radiator that radiates heat of the refrigerant compressed by the compressor, a throttle means that depressurizes high-pressure refrigerant, and the depressurization The heat pump device further comprises a refrigerant circulation circuit in which a heat absorber that removes heat from the surroundings is connected so that the refrigerant circulates. A heat exchange chamber disposed so that the heat absorber and the radiator are substantially facing each other, a heat sink air passage for guiding air from the inside of the storage portion to the heat exchange chamber, and air in the heat exchange chamber on the storage portion side A heat exchanger air passage leading to the heat exchanger chamber, and further, the compressor is arranged side by side with the heat exchange chamber so as to be substantially in the left-right direction of the housing, and an inlet of the heat absorber air passage is provided in the compressor. It is set as the structure which has arrange | positioned substantially upwards, and has arrange | positioned the discharge port of the said heat radiator air path in the opposite side to the side by which the said compressor is arrange | positioned, The centrifugal blower described above is a drying apparatus in which a bell mouth-shaped suction port of the centrifugal blower is directly connected to a discharge port of a heat radiating air passage.

With this configuration, an increase in drying noise and a decrease in drying performance can be suppressed even when duct resistance in the blower circuit increases. In addition, it can be directly connected to the radiator air passage of the heat pump device without increasing the outer dimension in the radial direction of the casing of the centrifugal blower, and is compactly stored in the space below the storage unit integrally with the heat pump device. be able to.

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

(Embodiment 1)
FIG. 1 is a front view in which 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 of the centrifugal blower as viewed from the outlet side in the first embodiment. 3 is a cross-sectional view of the centrifugal blower according to the first embodiment, taken along line AA of FIG.

  1 to 3, the centrifugal blower 1 includes a casing 8 provided with a suction port 6 and a blowout port 10, an impeller 5 disposed in the casing 8, and a motor 11 that rotates the impeller 5. It has a configuration.

  The impeller 5 includes a circular main plate 2, an annular side plate 3, and a number of blades 4 of forward wings disposed between the main plate 2 and the side plate 3.

  Further, the casing 8 is located on the side plate 3 side of the impeller 5, an upper plate 8 b provided with a bell mouth-like suction port 6 in the center portion, a bottom plate 8 c located on the main plate 2 side of the impeller 5, A peripheral side wall 8a that extends in a spiral shape so as to surround the impeller 5 with a tongue 7 provided in the vicinity of the mouth 10 as a base point. Here, the blowout port 10 is formed between the terminal end 9 of the peripheral side wall 8a and the tongue portion 7.

  As shown in FIG. 3, the casing 8 has a region viewed from the plane of the upper plate 8 b (the axial direction of the impeller 5), the outer periphery of the impeller 5 as a base point, and an outer side of the outer region x, When the inner side is defined as the impeller inner region y, the axial distance dimension L of the impeller 5 in the impeller outer region x is formed so as to gradually decrease from the tongue 7 to the end 9. In other words, the axial interval dimension L1 in the vicinity of the tongue 7 in the outer region x of the impeller (described in the middle part for convenience of description) is the same as the inner region y of the impeller, but the development of the peripheral side wall 8a. As the angle (rotation angle) advances, the interval dimension L also gradually decreases, and the interval dimension L2 near the end 9 (blowout port 10) is the smallest.

  Specifically, the peripheral side wall 8 a has a shape having a region in which the width dimension is gradually reduced so that the side on the upper plate 8 b side approaches the side on the bottom plate 8 c side, and the upper plate 8 b is a peripheral edge of the suction port 6. Is substantially parallel to the bottom plate 8c, and the casing 8 can be formed by bending with an inclination so as to contact the side of the peripheral side wall 8a as it extends to the outer periphery.

  Furthermore, the tongue 7 has a tip (top) 7x that has a substantially arc shape in a cross section (FIG. 1) orthogonal to the rotation shaft 5a of the impeller 5 and substantially faces the side plate 3 in the width direction of the blade 4. The shape extends from the position 7b to the position 7a substantially opposite to the main plate 2 side in the counter-rotating direction of the impeller 5.

  A driving motor 11 is directly connected to the rotating shaft 5 a of the impeller 5. Furthermore, the motor 11 is attached to the bottom plate 8c of the casing 8 through vibration isolating means 11a such as vibration isolating rubber.

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

  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 indicated by an arrow a. Then, in the process of passing through the annular side plate 3 and entering the inside of the impeller 5 and passing between the numerous blades 4, dynamic pressure and static pressure are applied, and an air current is generated as indicated by an arrow b. It is discharged outside. The discharged air current is guided between the inside of the spiral peripheral side wall 8a and the impeller 5 to efficiently convert the dynamic pressure into a static pressure, and then blows out from the outlet 10 as indicated by an arrow c. Is made.

  Here, the casing 8 is formed so that the axial distance L of the impeller 5 is gradually reduced from the tongue 7 to the outlet 10 in the outer region x of the impeller as described above. On the tongue 7 side where the radial distance R1 between the impeller 5 and the peripheral side wall 8a of the casing 8 is short, and the air outlet 10 side where the distance R2 between the impeller 5 and the peripheral side wall 8a of the casing 8 is separated, different airflows. Occurs.

  That is, on the tongue 7 side, the airflow discharged from the impeller 5 from the main plate 2 side to the side plate 3 side flows while being guided in the peripheral side wall 8a and deflected in the circumferential direction. In addition, since the distance L1 between the impeller outer region x in the bottom plate 8c and the top plate 8b is large, the pressure is smoothly converted to static pressure while being decelerated.

  On the other hand, on the side of the outlet 10 where the distance R2 between the impeller 5 and the peripheral side wall 8a of the casing 8 is separated, the impeller 5 in the outer region x of the impeller 5 becomes smaller as the interval dimension L2 of the outer region x of the impeller becomes smaller. The airflow that has passed through is discharged while being displaced toward the main plate 2 side of the impeller 5, but the deviation is regulated by the bottom plate 8 c of the casing 8, and the airflow from the main plate 2 side to the side plate 3 side of the impeller 5 is controlled. A flow direction component is generated. Further, the partial air flow b1 suppresses the air flow flowing between the side plate 3 of the impeller 5 and the upper plate 8b of the casing 8, and as a result, the air flow along the upper plate 8b side in the spiral peripheral side wall 8a is suppressed. It is blown out from the outlet 10 of the casing 8 as it occurs. Moreover, since the airflow blown out from the blowout port 10 has a sufficient distance R2 between the peripheral side wall 8a of the casing 8 and the impeller 5, the deceleration of the airflow is not hindered and the static pressure conversion effect is sufficient. To be demonstrated.

  As a result, even when the centrifugal blower 1 having the above-described configuration is incorporated in the blower circuit and the duct resistance constituting the blower circuit is increased, the vicinity of the outlet 10 is not increased without increasing the radial dimension of the casing 8. The airflow that blows out from the casing 8 to the suction port 6 can be suppressed, and accordingly, the disturbance of the inflow airflow at the suction port 6 is suppressed, and the side plate 3 and the tip 6a of the bell mouth-shaped suction port 6 The flow which circulates through to the impeller 5 can be suppressed.

  Therefore, an increase in blowing noise can be suppressed, and a decrease in blowing performance can be suppressed.

  Further, the tongue 7 has a shape in which both ends thereof extend in a counter-rotating direction of the impeller 5 from a position 7b substantially facing the side plate 3 side of the impeller 5 toward a position 7a substantially facing the main plate 2 side. As a result, in the vicinity of the tongue portion 7, the airflow that flows faster at the position 7 a substantially opposite to the main plate 2 side than the position 7 b substantially opposite to the side plate 3 side is blown out from the outlet 10. For this reason, the pressure at the outlet 7 side of the position 7a substantially opposite to the main plate 2 side of the impeller 5 is lower than that at the position 7b substantially opposite to the side plate 3 side.

As a result, an air current having a strong circumferential component discharged from the impeller 5 in the vicinity of the tongue portion 7 at the position 7b substantially facing the side plate 3 side of the impeller 5 is directed toward the position 7a substantially facing the main plate 2 side. The tip 7x of the portion 7 is smoothly wound and blown out from the blowout port 10.

  Therefore, from the inside of the casing 8 in the vicinity of the tongue 7 through the space between the side plate 3 of the impeller 5 and the upper plate 8b of the casing 8, the suction port is formed from the gap between the side plate 3 and the tip 6a of the bell mouth-shaped suction port 6. 6 can be suppressed.

  Therefore, it is possible to suppress the flow that blows out from the casing 8 near the tongue portion 7 to the suction port 6, disturbs the inflow airflow at the suction port 6, and circulates, and further suppresses blowing noise.

  In the first embodiment, a large number of blades 4 constituting the impeller 5 are forward wings inclined in the rotational direction, but the same effect can be expected with radial wings and backward wings.

(Embodiment 2)
FIG. 4 is a front view showing the internal configuration of the centrifugal blower in Embodiment 2 of the present invention in a see-through state. 5 is a cross-sectional view of the centrifugal blower according to the second embodiment, taken along line BB in FIG. 6 is a cross-sectional view taken along line CC of FIG. 4 of the centrifugal blower according to the second embodiment. FIG. 7 is a view showing the degree of development of the involute shape from the tongue 7 to the outlet 10 in the casing as seen from the suction port side. The same constituent elements as those in the first embodiment are denoted by the same reference numerals, and differences from the first embodiment will be mainly described.

  As shown in FIGS. 4 to 6, in the centrifugal blower 1 according to the second embodiment, the impeller outside region x of the upper plate 8 b that constitutes the casing 8 moves the casing 8 from the periphery of the bell mouth-shaped suction port 6. It forms so that it may incline in the direction of the baseplate 8c over the surrounding side wall 8a to comprise.

  Therefore, the axial distance L2 in the peripheral side wall 8a is smaller than the axial distance L1 in the vicinity of the suction port 6.

  Furthermore, since the inclined impeller outer region x in the casing 8 has a spiral shape with the tongue 7 as a starting point, like the peripheral side wall 8a of the casing 8, the swirl expansion angle α in the impeller outer region x of the upper plate 8b. 7, the enlarged angle αA on the side of the peripheral side wall 8a is formed larger than the enlarged angle αB on the side close to the suction port 6.

  In other words, as shown in FIG. 7, in the upper plate 8b, as the development angle (rotation angle) θ advances, the extension of the distance RxA closer to the peripheral side wall 8a is larger than the extension of the distance RxB closer to the suction port 6. Also, the distance Rx from the center of the impeller 5 is larger as the deployment angle (rotation angle) θ advances and closer to the peripheral side wall 8a.

  With the above configuration, in the outer region x of the impeller 8b of the upper plate 8b, as shown in FIGS. 5 and 6, the airflow near the outer diameter of the impeller 5 is from the vicinity of the side plate 3 of the impeller 5 as indicated by the arrow b2. Therefore, even if the swirl enlargement angle αB is reduced, it is smoothly decelerated and exhibits high static pressure conversion capability.

  On the other hand, in the outside region x of the impeller 8b of the upper plate 8b, the airflow near the peripheral side wall 8a has a radial component of the discharge airflow from the impeller 5 as compared to the vicinity of the side plate 3 of the impeller 5 as indicated by an arrow b3. Therefore, if the swirl enlargement angle α is small, it is not decelerated and it becomes difficult to obtain a static pressure conversion effect.

However, as shown in the second embodiment, the swirl expansion angle αA on the side close to the peripheral side wall 8a is made larger than the swirl expansion angle αB on the side close to the outer diameter of the impeller 5, whereby the arrow b
As shown by 4, the radial component of the airflow discharged from the impeller 5 can be decelerated, and sufficient static pressure conversion capability is exhibited. Therefore, the static pressure conversion capability by the casing 8 can be improved, and ventilation performance can be improved.

(Embodiment 3)
FIG. 8 is a rear view of the washing / drying machine according to Embodiment 3 of the present invention. FIG. 9 is a view as seen from the upper side of the heat pump unit of the washing and drying machine according to the third embodiment. FIG. 10 is a system conceptual diagram showing the configuration of the refrigerant circuit of the washing / drying machine and the flow of drying air in the third embodiment. The centrifugal blower used in the heat pump unit of the third embodiment is assumed to have the configuration of the first embodiment, and the same constituent elements as those of the first embodiment will be described with the same reference numerals.

  8 to 10, a cylindrical water tank 53 that is elastically supported by a plurality of suspensions 52 is provided inside a casing 51 that constitutes a main body of the washing and drying machine 50.

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

  A heat pump unit 57 (corresponding to the heat pump device of the present invention) 57 connected to the water tank 53 via the exhaust duct 56 and the suction duct 67 is provided at the lower back of the housing 51.

  The heat pump unit 57 includes a heat exchanger air passage 58 and a radiator air passage 59 (FIG. 9), and a heat exchange chamber 60 and a compressor chamber 61 that communicate with the heat absorber air passage 58 and the radiator air passage 59 therein. A unit case 62 formed with a heat sink 63 and a radiator 64 provided in the heat exchange chamber 60, a capillary tube (corresponding to the throttle means of the present invention) 65 connecting the radiator 64 and the heat absorber 63, A compressor 66 disposed in the compressor chamber 61 is provided. The compressor 66, the radiator 64, the heat absorber 63, and the capillary tube 65 constitute a heat pump cycle as is well known.

  In the unit case 62 of the heat pump unit 57, the heat absorber 63 and the radiator 64 are arranged in the heat exchange chamber 60 so that the respective opening faces substantially face each other, and the compressor 66 is heat exchanged in the substantially left direction of the casing 51. It is arranged side by side with the chamber 61. In addition, 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 in the heat exchange chamber 60 opposite to the side where the compressor chamber 61 is disposed. It is arranged on the substantially right side.

  Further, the centrifugal blower 1 is arranged on the right side of the heat pump unit 57, and 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 passage 59. A suction duct 67 is connected between the outlet 10 of the centrifugal blower 1 and the water tank 53.

  The operation of the washing / drying machine 50 in the above configuration will be described.

  In the washing (washing) step, water is supplied into the water tank 53, and the drive motor 55 is driven to rotate the clothes tank and the rotating tank containing the washing water 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 and drying machine, and then the drive motor 55 causes the rotating tank containing the clothes 54 to move in one direction at high speed. It rotates 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, the compressor 66 of the heat pump unit 57 is operated. Therefore, the refrigerant is compressed, and the refrigerant circulates sequentially through the radiator 64, the capillary tube 65, and the heat absorber 63 by this pressure. As a result, heat is released by the radiator 64, and the heat absorber 63 absorbs heat by the refrigerant that is decompressed by the capillary tube 65 and has a low pressure.

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

  Therefore, the warm air supplied into the rotating tub takes moisture when passing through the gaps of the clothes 54 and from the exhaust duct 56 connected to the water tub 53 in a wet state to the heat absorber 63 through the heat absorber air passage 58. When passing through the heat absorber 63, sensible heat and latent heat are taken away and dehumidified, and separated into dry air and condensed water.

  Here, as shown in FIG. 8, in the heat pump unit 57, the compressor 66 is arranged side by side with the heat exchange chamber 60 in the left direction when viewed from the back side of the casing 51, and the flow of the heat absorber air passage 58 is also determined. The inlet 58a is positioned substantially above the compressor 66, and further, the centrifugal blower 1 is disposed on the discharge port 59a side of the radiator air passage 59 (a position opposite to the compressor 66 when viewed from the back of the housing 51). By disposing the components, the components of the refrigerant circuit and the air channel components, and the connection structure of the exhaust duct 56 and the suction duct 67 can be gathered together in the smallest direction. The heat pump unit 57 can be reasonably arranged in the empty space at the lower rear.

  Further, by using the centrifugal blower 1 according to the first embodiment of the present invention, even if the duct resistance in the blower circuit of the washing dryer 50 including the exhaust duct 56 and the suction duct 67 is increased, the drying noise is increased. And a decrease in drying performance can be suppressed. Furthermore, the space in the lower rear part of the water tank 53 of the casing 51 can be directly connected to the discharge port 59a of the radiator air passage 59 of the heat pump unit 57 without increasing the outer dimension of the casing 8 of the centrifugal blower 1 in the radial direction. In addition, the heat pump unit 57 can be housed compactly.

  As described above, the centrifugal blower according to the present invention suppresses an increase in the blowing noise and reduces the blowing performance even when the duct resistance of the blower circuit in which the centrifugal blower is housed or disposed in the middle increases. Therefore, it is possible to achieve both the air blowing performance and the high heat exchange capability as the heat pump unit. Furthermore, since noise reduction is possible, not only washing and drying machines, but also air conditioning equipment such as household and commercial air conditioners, refrigeration and refrigeration equipment such as refrigerators and vending machines, and heat pump equipment such as water heaters Furthermore, it can be widely applied not only to electronic devices having thermoelectric components, but also to AV devices, waste heat recovery devices and the like.

DESCRIPTION OF SYMBOLS 1 Centrifugal blower 2 Main plate 3 Side plate 4 Blade 5 Impeller 6 Suction port 7 Tongue 7x Tip 8 Casing 8a Peripheral side wall 8b Top plate 8c Bottom plate x Impeller outside area 50 Washing dryer 51 Housing 53 Water tank 54 Clothing 56 Exhaust duct 57 Heat pump unit (heat pump device)
58 Heat absorber air passage 58a Inlet 59 Heat radiator air passage 59a Discharge port 60 Heat exchange chamber 63 Heat absorber 64 Heat radiator 65 Capillary tube (throttle means)
66 Compressor 67 Suction duct

Claims (5)

In a centrifugal blower comprising a main plate, an annular side plate, an impeller comprising a plurality of blades provided between the main plate and the side plate, and a casing including the impeller and having a discharge port, the casing is A top plate located on the side plate side of the impeller and having a bell mouth-like suction port, a bottom plate located on the main plate side of the impeller, and located between the top plate and the bottom plate, and the discharge The impeller includes a peripheral side wall extending in a spiral shape so as to surround the periphery of the impeller in the radial direction with a tongue portion provided in the vicinity of the outlet, and further, at the distance between the bottom plate and the upper plate of the casing, the impeller A centrifugal blower in which the upper plate is bent toward the bottom plate so that the portion outside the outer diameter is smaller than the portion inside the outer diameter of the impeller. The centrifugal blower according to claim 1, wherein a distance between a bent portion of the bottom plate and the upper plate of the casing is gradually decreased from a tongue portion of the spiral peripheral side wall to a discharge port of the casing. A portion outside the outer diameter of the impeller on the upper plate of the casing is inclined in the direction of the bottom plate toward the peripheral side wall, and the inclined portion is based on a tongue as in the case of the peripheral side wall of the casing. The centrifugal blower according to claim 1 or 2, wherein a spiral enlargement angle of the inclined portion of the upper plate is gradually increased from the upper plate side to the peripheral side wall side. . The tongue portion has a substantially arc shape in a cross section whose tip is orthogonal to the rotation axis of the impeller, and is substantially opposed to the main plate side of the impeller from a position substantially opposed to the support plate side in the width direction of the blade. The centrifugal blower according to any one of claims 1 to 3, wherein the centrifugal fan has a shape extending in a counter-rotating direction of the impeller toward a position to be moved. A storage unit that is disposed in the housing and stores an object to be dried such as clothing, a heat pump device that is disposed in the lower rear portion of the storage unit in the housing, and air that is heat-exchanged by the heat pump device. A wind circuit including a blowing unit and a supply duct and an exhaust duct for supplying the heat exchanged air by the blowing unit from the heat pump device into the storage unit and circulating the air from the storage unit to the heat pump unit; The heat pump device includes a compressor and a radiator that dissipates heat of the refrigerant compressed by the compressor, a throttle unit that depressurizes the pressure of the high-pressure refrigerant, and the decompressed refrigerant takes heat from the surroundings. A heat sink is provided with a refrigerant circulation circuit connected so that the refrigerant circulates, and the heat pump device further includes the heat absorber and the radiator. A heat exchange chamber disposed so as to face each other, a heat sink air passage that guides air from inside the storage portion to the heat exchange chamber, and a radiator air passage that guides air in the heat exchange chamber to the storage portion side. Further, the compressor is arranged side by side with the heat exchange chamber so as to be substantially in the left-right direction of the casing, and the inlet of the heat absorber air passage is disposed substantially above the compressor, and the heat dissipation The discharge port of the air duct is disposed on the side opposite to the side on which the compressor is disposed, and the blowing means is the centrifugal blower according to any one of claims 1 to 4, wherein the centrifugal Device that directly connects the bell mouth-shaped suction port of the air blower to the discharge port of the heat radiating air passage.