WO2021106317A1 - Blower and washing machine - Google Patents
Blower and washing machine Download PDFInfo
- Publication number
- WO2021106317A1 WO2021106317A1 PCT/JP2020/034439 JP2020034439W WO2021106317A1 WO 2021106317 A1 WO2021106317 A1 WO 2021106317A1 JP 2020034439 W JP2020034439 W JP 2020034439W WO 2021106317 A1 WO2021106317 A1 WO 2021106317A1
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- WIPO (PCT)
- Prior art keywords
- flow path
- diffuser
- blower
- vane
- impeller
- Prior art date
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-
- D—TEXTILES; PAPER
- D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
- D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
- D06F58/00—Domestic laundry dryers
- D06F58/02—Domestic laundry dryers having dryer drums rotating about a horizontal axis
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
Definitions
- the present invention relates to a blower and a washing machine equipped with the blower.
- Patent Document 1 describes a blower having a configuration in which the rotating shaft of the impeller and the central shaft of the diffuser are different from each other.
- the blower described in Patent Document 1 has blades on the central axis of the diffuser in order to suppress a decrease in pressure recovery rate, that is, a decrease in efficiency due to a pressure distribution generated in the circumferential direction in the diffuser due to the influence of a scroll provided downstream of the diffuser. It is characterized by shifting with respect to the rotation axis of the car. As a result, the pressure recovery rate by the diffuser is changed in the circumferential direction and offset by the pressure distribution caused by scrolling, so that the pressure distribution in the circumferential direction is made uniform and high efficiency is realized.
- the present invention solves the above-mentioned conventional problems, and an object of the present invention is to provide a blower capable of achieving both miniaturization and high efficiency, and a washing machine equipped with the blower.
- the present invention is a diffuser composed of an electric motor, a rotating shaft rotatably provided on the electric motor, an impeller provided on the rotating shaft, and vanes provided downstream of the impeller and arranged in the circumferential direction.
- a flow path and a scroll flow path provided downstream of the diffuser flow path on the side opposite to the axial direction of the rotation axis with respect to the diffuser flow path are provided, and the tongue portion of the scroll flow path is used as a reference.
- the vane length changes as the impeller rotates in the direction of rotation.
- the present invention it is possible to provide a blower capable of achieving both miniaturization and high efficiency, and a washing machine equipped with the blower.
- FIG. 1 is a vertical cross-sectional view showing a washing machine equipped with the blower of the present embodiment.
- a vertical washer / dryer will be described as an example, but it can also be applied to a drum-type washer / dryer having a laundry inlet / outlet port formed on the front side.
- the washing machine S includes an outer frame 1 which is a housing, an outer tub 2 for storing washing water, a rotary tub 3, a drive motor 10, a blower 22 and the like.
- the outer tub 2 is built in the outer frame 1 and is vibration-proof supported by the outer frame 1.
- the rotary tub 3 is a washing / dehydrating tub for accommodating laundry such as clothes to be washed and dried, and is provided inside the outer tub 2. Further, the rotary tank 3 is rotatably supported in the outer tank 2.
- a stirring blade 4 for stirring and washing the laundry is rotatably provided at the bottom of the rotary tub 3.
- the stirring blade 4 repeats forward / reverse rotation during washing operation and drying operation. Further, the stirring blade 4 rotates at high speed together with the rotary tub 3 during the dehydration operation to dehydrate the water contained in the laundry in the rotary tub 3.
- the drive motor 10 is provided in the outer frame 1 and drives the stirring blade 4 and the rotary tank 3 in rotation. Further, as the drive motor 10, for example, a DC brushless motor is used. The DC brushless motor is controlled by a vector. In the present embodiment, the stirring blade 4 and the rotary tank 3 are directly rotationally driven by the drive motor 10, but may be driven by using a belt or the like (not shown).
- an outer lid 5 is provided on the upper part of the outer frame 1.
- the outer lid 5 is provided on a top cover 6 provided on the upper part of the outer frame 1 so as to be openable and closable.
- An inner lid 34 is provided on the upper portion of the outer tank 2 so as to be openable and closable. By opening the outer lid 5 and the inner lid 34, laundry can be taken in and out of the rotary tub 3.
- a water supply unit 7 is provided on the back side of the top cover 6.
- the water supply unit 7 has a water supply box (not shown) having a plurality of water channels inside, and supplies tap water or bath water from the water supply hose connection port 8 to the outer tank 2.
- a detergent and finishing agent charging device 35 is provided on the front side of the top cover 6. The detergent and finishing agent are poured between the outer tank 2 and the rotary tank 3 by the charging hose 36.
- the washing machine S is provided with a drying mechanism 9.
- the drying mechanism 9 circulates and dehumidifies the drying air for drying the laundry in the rotary tub 3. Further, the drying mechanism 9 is mostly occupied by the air circulation path for drying.
- the drying air circulation passage includes a bottom circulation passage 20 connected so as to communicate with the bottom of the outer tank 2, and a dehumidifying vertical passage 21 extending upward from the bottom circulation passage 20.
- the suction side of the blower 22 is connected to the upper side of the dehumidifying vertical passage 21.
- the discharge side of the blower 22 is connected so as to communicate with the return connection circulation path 25.
- a drying filter 45 is arranged between the blower 22 and the dehumidifying vertical passage 21 to prevent foreign matter from flowing into the blower 22. The details of the blower 22 will be described later.
- the return connection circulation path 25 has an upper bellows hose 23, and is connected so as to communicate with the upper part of the outer tank 2 via the upper bellows hose 23.
- the bottom circulation path 20 also has a lower bellows hose 26, and is connected to the bottom of the outer tank 2 via the lower bellows hose 26.
- the lower bellows hose 26 is connected to the bottom drop portion 31 of the outer tank 2.
- the bottom drop portion 31 communicates with the washing water drainage channel 42 and the washing water circulation water channel 43 via the lower communication pipe 41.
- a drain valve 44 is provided in the washing water drainage channel 42.
- a foreign matter removing trap 32 is provided in the washing water circulation water channel 43.
- the drain valve 44 is closed during the washing operation and the drying operation. Further, the drain valve 44 is opened at the time of draining the washing water, and the washing water and rinsing water accumulated in the outer tub 2 are discharged from the washing water drainage channel 42 to the outside (outside the machine) of the washing machine S.
- the washing water circulation water channel 43 is connected to the washing water circulation water vertical water channel 46.
- the washing water circulating water vertical channel 46 rises along the outer surface of the outer tub 2 and extends to the upper side of the rotary tub 3 so as to communicate with the washing thread waste removing device 33 provided on the upper side of the rotary tub 3. Be connected.
- washing water and rinsing water collected in the outer tub 2 flows through the washing water circulating water vertical water channel 46 and is poured from the washing thread waste removing device 33 into the rotary tub 3. Since washing and rinsing are performed while this spraying and water injection continues, washing and rinsing are performed with a small amount of water.
- the washing machine S is provided with a water level sensor 47 that detects the water level of washing water and rinsing water accumulated in the outer tub 2.
- An air trap 50 is provided near the bottom of the outer tank 2.
- An air tube 49 is connected so as to communicate with the air trap 50.
- a water level sensor 47 is connected to the upper end of the air tube 49 so as to communicate with the upper end. The water level sensor 47 detects the fluctuation of the water level in the outer tank 2 to detect the water level.
- the centrifugal impeller 300 (see FIG. 2) of the blower 22 rotates, so that the drying air circulates in the rotary tub 3 and dries the laundry in the rotary tub 3.
- the electric heater 24 (see FIG. 3) of the blower 22 reheats the drying air in which the moisture is condensed in the dehumidifying region and flows through the rotary tub 3, so that the moisture in the laundry is further evaporated.
- the laundry is dried by repeating this water removal in the circulation of the drying air.
- FIG. 2 is an external perspective view showing the blower of the first embodiment.
- the blower 22 includes a fan cover 51, a fan casing 52, an electric motor 100, a centrifugal impeller 300, a diffuser 400 (see FIG. 3), and an electric heater 24 (see FIG. 3). .
- the blower 22 is mounted on the washing machine S (see FIG. 1), for example, the fan cover 51 of the blower 22 is installed in the outer frame 1 (see FIG. 1) so as to be substantially downward.
- the fan cover 51 is formed with a suction port 57 and an discharge port 58.
- the suction port 57 is connected to the dehumidifying vertical passage 21 (see FIG. 1) via the drying filter 45 (see FIG. 1).
- the discharge port 58 is connected to the return connection circulation path 25 (see FIG. 1) of the drying air circulation path.
- FIG. 3 is an exploded perspective view of the blower when viewed from the fan cover side.
- the fan cover 51 has an elongated shape in one direction, a suction port 57 is formed on one side in the longitudinal direction, and a discharge port 58 is formed on the other side in the longitudinal direction.
- the suction port 57 is a circular through hole and faces the center of the suction opening 302 of the centrifugal impeller 300.
- the discharge port 58 is a circular through hole and is located on the downstream side of the electric heater 24. Further, the diameter of the discharge port 58 is formed to be larger than the diameter of the suction port 57. Further, the suction port 57 and the discharge port 58 are formed so as to face substantially the same direction.
- the fan cover 51 is formed with an annular protrusion 51a protruding in the axial direction Ax around the suction port 57.
- the axial direction Ax means the direction in which the rotating shaft 101 of the electric motor 100 extends.
- the fan cover 51 has a substantially rectangular protrusion 51b formed at a position where the electric heater 24 is provided.
- screw fixing portions 91 to be screw-fixed to the fan casing 52 are formed at a plurality of places.
- the fan casing 52 has a shape corresponding to the fan cover 51.
- a space for arranging the centrifugal impeller 300, the diffuser 400, and the electric heater 24 is formed between the fan cover 51 and the fan casing 52. ing.
- a scroll flow path 70 is formed on the back surface (lower surface) side on which the diffuser 400 is arranged.
- the scroll flow path 70 is formed so that the flow path width on the tongue end portion 71 side is narrow and the flow path width gradually increases in the clockwise direction from the tongue end portion 71.
- the tip of the tongue 71 is the starting point of the scroll flow path 70.
- the outlet of the scroll flow path 70 is the casing discharge port 59 (see the shaded area).
- the fan casing 52 is formed with an introduction path 72a for introducing air from the scroll flow path 70 into the electric heater 24.
- the electric heater 24 includes a large number of fins, flows out of the scroll flow path 70, and heats the air that has passed through the introduction path 72a.
- the introduction path 72a is configured so that the flow path width widens toward the electric heater 24. More specifically, the introduction path 72a is configured to extend to substantially the same width as the width of the heating portion 24a of the electric heater 24.
- the introduction path 72b (see FIG. 4) of the fan cover 51 is also configured so that the flow path width widens toward the downstream as in the introduction path 72a.
- a concave flow path 77 communicating with the discharge port 58 of the fan cover 51 is formed on the downstream side of the electric heater 24. Further, the flow path 77 is configured to be obliquely upward so as to be inclined toward the discharge port 58.
- the fan casing 52 has a shape that protrudes in the width direction so that the position deviated from the heating portion of the electric heater 24 does not interfere with the air flow.
- a shaft insertion hole 80 into which the rotation shaft 101 of the electric motor 100 is inserted is formed in the center of the scroll flow path 70. Further, on the outer peripheral edge portion of the fan casing 52, a screw insertion portion 92 through which a screw (not shown) is inserted is formed at a position corresponding to the screw fixing portion 91 of the fan cover 51.
- screw holes 93 for fixing the diffuser 400 to the fan casing 52 are formed at a plurality of locations (4 locations in the present embodiment) between the shaft insertion hole 80 and the scroll flow path 70. ing. These screw holes 93 are formed so as to surround the shaft insertion hole 80. Further, the fan casing 52 has a circular recess 93a formed on the peripheral edge of the screw hole 93.
- a fan casing recess 94 (concave groove portion) is formed on the radial outer peripheral side of the screw hole 93.
- the fan casing recess 94 is formed in an annular shape.
- the motor 100 has a rotating shaft 101 coupled to the centrifugal impeller 300 at the center in the radial direction, and is attached to the fan casing 52. Further, the motor 100 has a rotor (rotor) fixed to the rotating shaft 101, a stator (stator) provided around the rotor, and a bearing that rotatably supports the rotating shaft 101. Further, the motor 100 has a substantially columnar case 102 that houses a rotor, a stator, and a bearing. An annular brim 103 is formed on the outer peripheral surface (side surface) of the case 102. In the brim 103, screw insertion holes 104 for screw-fixing the motor 100 to the fan casing 52 are formed at a plurality of locations (four locations in the present embodiment) at intervals in the circumferential direction.
- the diffuser 400 is formed of, for example, a synthetic resin, and has a circular bottom plate 400a facing the surface of the centrifugal impeller 300 in the axial direction Ax.
- the bottom plate 400a has a circular through hole 400b formed in the center in the radial direction.
- the through hole 400b is formed to have a diameter larger than that of the shaft insertion hole 80 of the fan casing 52.
- the bottom plate 400a is formed with a plurality of screw insertion holes 430 around the through holes 400b through which screws (not shown) for fixing the diffuser 400 to the fan casing 52 are inserted.
- the screw insertion hole 430 is formed at a position corresponding to (opposing) the screw hole 93 of the fan casing 52.
- a recessed portion 430a is formed on the peripheral edge of the screw insertion hole 430 so that the head of the screw (not shown) does not protrude from the surface (upper surface of the drawing) of the bottom plate 400a.
- a diffuser outer bottom surface (base) 400c formed one step higher in the axial direction Ax than the bottom plate 400a is formed on the entire outer peripheral edge of the bottom plate 400a.
- Diffuser vanes 401 are formed at equal intervals along the circumferential direction on the upper surface (the surface on the fan cover 51 side) of the outer bottom surface portion 400c of the diffuser in the axial direction.
- FIG. 4 is an exploded perspective view of the blower when viewed from the motor side.
- a bell mouth portion 57a is formed at the suction port 57 of the fan cover 51.
- the fan cover 51 is formed with a recess 51c in which a ring-shaped sealing member (not shown) is housed around the bell mouth portion 57a.
- the fan cover 51 is provided with an annular holding member (not shown) for holding the seal member (not shown) in the recess 51c.
- This holding member (not shown) is placed in an annular recess 51d formed around the recess 51c and formed one step higher (shallow) than the recess 51c.
- the holding member (not shown) is fixed via a fixing portion 51e formed around the recess 51d.
- the fan cover 51 is provided with an elastic member 90 formed in an annular shape. Note that FIG. 4 illustrates a state in which the elastic member 90 is attached to the fan cover 51.
- the elastic member 90 is arranged at a position facing the tip (upper end) of the diffuser vane 401.
- the fan cover 51 is formed with an introduction path 72b extending from the scroll flow path 70 (see FIG. 3) toward the electric heater 24.
- the introduction path 72b is formed along the introduction path 72a (see FIG. 3). Further, the introduction path 72b is configured so that the depth dimension H (flow path height) of the flow path becomes deeper (higher) from the scroll flow path 70 (see FIG. 3) side toward the electric heater 24.
- the scroll flow path 70 of the fan casing 52 is configured to bulge toward the side where the motor 100 is installed (motor installation side). Further, in the scroll flow path 70, the flow path depth (depth of Ax in the axial direction) gradually increases from the flow path on the tongue end 71 (see FIG. 3) side toward the introduction path 72a (see FIG. 3). It is configured to be deep in. Further, the introduction path 72a is configured so that the flow path depth becomes substantially constant toward the electric heater 24. The flow path 77 on the downstream side of the electric heater 24 is configured to be lifted toward the fan cover 51 side.
- the fan casing 52 is formed with screw bosses 78 for fixing the motor 100 to the fan casing 52 at a plurality of locations (four locations in the present embodiment).
- the diffuser 400 has a ridge portion 440 formed on the side (rear side) opposite to the surface on which the diffuser vane 401 is provided.
- the ridge portion 440 fits into the fan casing recess 94 (see FIG. 3) of the fan casing 52.
- the screw insertion hole 430 of the diffuser 400 is formed with a protrusion 430b that is unevenly fitted with the recess 93a (see FIG. 3) of the fan casing 52.
- Each protrusion 430b fits into a recess 93a corresponding to each of the fan casings 52.
- the screw insertion hole 430 of the diffuser 400 and the screw hole 93 of the fan casing 52 are fixed by screws (not shown).
- the rotating shaft 101 (see FIG. 3) of the electric motor 100 is inserted into the shaft insertion hole 80 of the fan casing 52.
- the rotary shaft 101 is inserted into the through hole 400b of the diffuser 400, and the tip of the rotary shaft 101 is coupled (fixed) to the centrifugal impeller 300.
- the fan cover 51 and the fan casing 52 are connected to each other by inserting a screw (not shown) into the screw insertion portion 92 and fixing the screw (not shown) to the screw fixing portion 91.
- the blower 22 forms a casing portion 61 (see FIG. 2) in which the centrifugal impeller 300 and the diffuser 400 are arranged, and a heater portion 62 (see FIG. 2) in which the electric heater 24 is arranged.
- the connection space boundary surface between the casing portion 61 and the heater portion 62 is designated as the casing discharge port 59 (see FIG. 3).
- the inner diameter end of the blade 321 is located radially outside the suction opening 302 (see FIG. 3). Further, the centrifugal impeller 300 is configured such that the outer diameter end portion of the blade 321 substantially coincides with the outer peripheral edge portion of the shroud plate 301 and the outer peripheral edge portion of the hub plate 311.
- a closed type centrifugal impeller 300 having a shroud plate 301 will be described as an example, but an open type centrifugal impeller in which the hub plate 311 and the blade 321 are integrally molded with resin may be used. ..
- the resin type facilitates three-dimensionalization and improves efficiency. The three-dimensionalization is to form the blade by further twisting it. As a result, efficiency can be further improved.
- a turbofan having rearward blades will be described as an example, but a sirocco fan having forward blades may be applied.
- the shape of the impeller is not limited to the centrifugal type, and may be a mixed flow type. By adopting the oblique flow type, the outer diameter of the impeller can be miniaturized, and the blower 22 can be miniaturized.
- FIG. 5 is a plan view of a conventional diffuser.
- FIG. 6 is a plan view of a blower equipped with a conventional diffuser.
- FIG. 7 is a schematic view showing a communication passage formed by a conventional diffuser.
- the diffuser 1400 is configured such that a plurality of diffuser vanes 1401 are arranged around the bottom plate 1400a at equal intervals in the entire circumferential direction.
- the diffuser vane 1401 is formed so as to stand up in the axial direction Ax (see FIGS. 3 and 4) with respect to the diffuser outer bottom surface portion 1400c formed around the bottom plate 1400a. Further, the diffuser vane 1401 is located outside the outer peripheral edge portion of the centrifugal impeller 300 (see FIGS. 3 and 4).
- the diffuser vane 1401 is formed in a thin plate shape and extends in the circumferential direction in a plan view. Further, the diffuser vane 1401 is configured such that the trailing edge 1402 (the other end) is located radially outside the front edge 1412 (one end). Further, in the diffuser vane 1401A (1401), the front edge 1412 of the diffuser vane 1401B (1401) adjacent to the diffuser vane 1401B (1401) is located substantially in the center in the circumferential direction and inside the radial direction of the diffuser vane 1401A.
- the trailing edge 1402 of the diffuser vane 1401A (1401) adjacent to the diffuser vane 1401B (1401) is located substantially in the center in the circumferential direction and outside in the radial direction of the diffuser vane 1401B.
- a diffuser flow path 1410 described later is formed between the adjacent diffuser vanes 1401A and 1401B.
- the diffuser flow path 1410 is configured so that the width in the radial direction gradually increases from the front edge 1412 side to the trailing edge 1402 side.
- the cut portion 1404 is provided so that the outer peripheral edge portion of the diffuser outer bottom surface portion 1400c extends from the trailing edge 1402 substantially perpendicular to the pressure surface 1403 of the adjacent diffuser vane 1401B. It is formed.
- the pressure surface 1403 means the entire surface of the diffuser vane 1401 from the front edge 1412 to the trailing edge 1402 facing outward in the radial direction.
- a substantially triangular notch 1405 penetrating in the axial direction Ax is formed on the outer peripheral edge portion of the diffuser outer bottom surface portion 1400c.
- the outer peripheral edge of the diffuser 1400 is formed so as to be serrated along the circumferential direction.
- a substantially triangular continuous passage 1420 formed by the fan casing 52, the diffuser vane 1401, and the notch 1404 is formed. Further, on the outer circumference of the diffuser 1400 in the radial direction, substantially triangular passages 1420 are formed side by side in the circumferential direction. The upstream side of the communication passage 1420 communicates with the diffuser flow path 1410 surrounded by the adjacent diffuser vanes 1401, 1401, the diffuser outer bottom surface portion 1400c, and the fan cover 51 (see FIGS. 3 and 4). When the centrifugal impeller 300 rotates in the W direction, air (fluid) is discharged from the outer circumference of the centrifugal impeller 300.
- the discharged air passes through the diffuser flow path 1410 (see the arrow) and flows into the substantially triangular continuous passage 1420, and the scroll flow path 70 provided on the back side of the diffuser 1400 (in the direction perpendicular to the paper surface in FIG. 6). It flows into the back side).
- the air flowing through the scroll flow path 70 passes through the scroll portion 75 and is discharged to the discharge portion 76. Then, the air that has passed through the discharge portion 76 passes through the casing discharge port 59 and is introduced into the introduction path 72.
- the discharge unit 76 means a scroll flow path 70 from the point B to the casing discharge port 59.
- the outer diameter of the trailing edge 1402 of the diffuser vane 1401 is a constant value, so that the blower has a constant value with the trailing edge 1402.
- the distance S100 from the radial outer wall surface 74 increases in the rotation direction W of the centrifugal impeller 300.
- the flow of air passing through the diffuser flow path 1410 is not constrained by the radial outer wall surface 74, and thus this region (distance). A high pressure recovery rate cannot be obtained in the gap of S100).
- FIG. 8 is a plan view of the diffuser of the first embodiment.
- FIG. 9 is a plan view of a blower equipped with the diffuser of the first embodiment, showing a state in which the fan cover is removed.
- FIG. 10 is a schematic view showing a communication passage formed by the diffuser of the first embodiment.
- the shape of the diffuser 400 shown below is an example, and is not limited to the first embodiment.
- the blower 22 of the first embodiment is provided with a diffuser 400 in place of the diffuser 1400 of the conventional example (see FIG. 5 and FIG. 7).
- the lengths of the diffuser vanes 401 are different in the circumferential direction. More specifically, the position of the front edge 412 of the diffuser vane 401 is the same in the circumferential direction, but the position of the trailing edge 402 is different in the radial direction.
- a plurality of diffuser vanes 401 are arranged at equal intervals in the circumferential direction around the bottom plate 400a as in the conventional example.
- the reference position (position at 0 °) of the region R1 is a line passing through the tip of the tongue end portion 71 and the rotation center O of the centrifugal impeller 300.
- the diffuser vane 401 stands up in the axial direction Ax (see FIGS. 3 and 4) (direction toward the front side perpendicular to the paper surface in FIG. 8) with respect to the diffuser outer bottom surface portion 400c formed around the bottom plate 400a. Is formed. Further, the diffuser vane 401 is located outside the outer peripheral edge portion of the centrifugal impeller 300 (see FIGS. 3 and 4).
- the diffuser vane 401 is formed in a thin plate shape and extends in the circumferential direction in a plan view. Further, in the diffuser vane 401, the trailing edge 402 (the other end or the outer diameter side end) is located radially outside the front edge 412 (one end or the inner diameter side end). Further, in the diffuser vane 401A (401) of the region R1, the front edge 412 of the diffuser vane 401B (401) adjacent to the diffuser vane 401B (401) is located substantially in the center in the circumferential direction and inside the radial direction of the diffuser vane 401A. There is.
- the trailing edge 402 of the diffuser vane 401A (401) adjacent to the diffuser vane 401B (401) is located substantially in the center in the circumferential direction and outside in the radial direction of the diffuser vane 401B.
- a diffuser flow path 410 described later is formed between the adjacent diffuser vanes 401A and 401B.
- the diffuser flow path 410 is configured so that the width in the radial direction gradually increases from the front edge 412 side to the trailing edge 402 side.
- the notch portion 404 is provided so that the outer peripheral edge portion of the diffuser outer bottom surface portion 400c extends from the trailing edge 402 substantially perpendicular to the pressure surface 403 of the adjacent diffuser vane 401B. It is formed.
- the pressure surface 403 means the entire surface of the diffuser vane 401 from the front edge 412 to the trailing edge 402 facing outward in the radial direction.
- a substantially triangular notch portion 405 penetrating in the axial direction Ax is formed on the outer peripheral edge portion of the diffuser outer bottom surface portion 400c.
- the outer peripheral edge of the diffuser 400 in the region R1 is formed so as to be serrated along the circumferential direction.
- the diffuser vanes 401 having the same length in the circumferential direction are arranged at equal intervals in the circumferential direction (rotational direction W) as in the reference numeral R1. ..
- the diffuser 400 in the region R3 (range of 90 °) is configured to become longer as the diffuser vane 401 approaches the rotation direction W.
- the diffuser vane 401D is formed longer in the rotation direction W than the adjacent diffuser vanes 401C.
- the diffuser vanes 401E are formed longer in the rotation direction W than the adjacent diffuser vanes 401D.
- the diffuser vanes 401F are formed longer in the rotation direction W than the adjacent diffuser vanes 401E.
- the diffuser vanes 401G are formed longer in the rotation direction W than the adjacent diffuser vanes 401F.
- the diffuser vane 401H is formed longer in the rotation direction W than the adjacent diffuser vanes 401G.
- some diffusers 400 in the region R4 are configured to become longer as the diffuser vane 401 approaches the rotation direction W.
- the diffuser vane 401J is formed longer in the rotation direction W than the adjacent diffuser vanes 401I.
- the diffuser vanes 401K are formed longer in the rotation direction W than the adjacent diffuser vanes 401J.
- the diffuser vanes 401L are formed longer in the rotation direction W than the adjacent diffuser vanes 401K.
- the diffuser 400 in the other portion in the region R4 (range of 90 °) is configured to become shorter as the diffuser vane 401 approaches the rotation direction W.
- the diffuser vane 401M is formed shorter in the rotation direction W than the adjacent diffuser vanes 401L.
- the diffuser vanes 401N are formed so as to have the same length in the rotation direction W as the adjacent diffuser vanes 401M.
- the diffuser vanes 401M and 401N are formed longer in the rotation direction W than the diffuser vanes 401 in the region indicated by reference numeral R1.
- the diffuser outer bottom surface portion 400c is formed so as to extend to the trailing edge 402 of the diffuser vanes 401J, 401K, 401L. Further, the diffuser 400 extends radially outward from the trailing edge 402 of the diffuser vane 401M in the region R4. As described above, the diffuser 400 has an arc portion 400c1 in which the diffuser outer bottom surface portion 400c is formed in a substantially arc shape over the diffuser vanes 401J, 401K, 401L, 401M, and 401N in the region R4. In other words, the diffuser 400 has a shape (a shape other than the saw blade shape) in which the communication passage 420 is not formed in a part of the region R4.
- the tip (rear edge 402) of the diffuser vane 401N comes into contact with the tongue end portion 71. Further, the arc portion 400c1 (hub wall surface) of the diffuser outer bottom surface portion 400c extends toward the casing discharge port 59 (outlet of the scroll flow path 70).
- the position of the tongue end portion 71 of the scroll flow path 70 is used as a reference, and the length of the diffuser vane 401 in the circumferential direction is longer in the rotation direction W of the centrifugal impeller 300 from there. More specifically, in the first embodiment, when the position P1 connecting the tip of the tongue end portion 71 and the rotation center O of the centrifugal impeller 300 is set as a reference (0 °), 90 in the rotation direction W from the reference position P1. Let P2 be the position rotated by °, P3 be the position rotated 180 ° in the rotation direction W from the reference position P1, and P4 be the position rotated 270 ° in the rotation direction W from the reference position P1.
- the positions P1 to P2 correspond to the above-mentioned region R1.
- the position P2 to the position P3 correspond to the above-mentioned region R2.
- the position P3 to the position P4 corresponds to the above-mentioned region R3.
- the position P4 to the position P1 corresponds to the above-mentioned region R4.
- the diffuser vane 401 having the same length in the rotation direction W is obtained, and the diffuser vane 401 is from 180 ° to 270 °.
- the length of the diffuser vane 401 is gradually increased in the rotation direction W.
- the length of the diffuser vane 401 is gradually increased in a part in the rotation direction W from 270 ° to 360 ° (0 °) (region R4 in FIG. 8). It is configured in.
- the length of the diffuser vane 401 in the rotation direction W in the other portion (the remaining part). Is configured to be shorter.
- the length of the diffuser vane 401 in the circumferential direction is formed to be the same at the position P1 at 0 ° and the position P2 at 90 °. Further, the length of the diffuser vane 401 in the circumferential direction is formed to be the same at the position P2 at 90 ° and the position P3 at 180 °. At the 180 ° position P3 and the 270 ° position P4, the diffuser vane 401 at the 270 ° position P4 is formed longer than the diffuser vane 401 at the 180 ° position P3.
- the diffuser vane 401 is formed long in the rotation direction W so as to fill the distance S100 (see FIG. 7) in the conventional example.
- the blower 22 of the first embodiment is particularly effective when the radial outer wall surface 74 (see FIG. 9) of the fan casing 52 changes in the circumferential direction.
- the radial outer wall surface 74 of the fan casing 52 is circular. Cannot be secured.
- the trailing edge 402 of the diffuser vane 401 may be in contact with or separated from the radial outer wall surface 74 of the scroll flow path 70.
- a gap of about several mm may be provided.
- the gap width S1 (see FIG. 9) between the trailing edge 402 of the diffuser vane 401 and the outer wall surface 74 in the radial direction is preferably a constant value in the circumferential direction.
- the diffuser 400 is provided with a diffuser flow path 410A (see FIG. 9) which does not have a communication passage 420 in the region R4a which can be directly connected to the introduction path 72 in the diffuser flow path 410.
- the air flow through the diffuser flow path 410A is directly guided to the introduction path 72 without being converted from the radial direction to the axial direction Ax.
- the pressure loss due to the conversion of the air flow can be suppressed, and the efficiency of the blower 22 can be improved.
- the blower 22 of the first embodiment includes the electric motor 100, the rotating shaft 101 rotatably provided on the electric motor 100, the centrifugal impeller 300 provided on the rotating shaft 101, and the downstream of the centrifugal impeller 300.
- a diffuser flow path 410 composed of diffuser vanes 401 arranged in the circumferential direction and a scroll provided downstream of the diffuser flow path 410 on the opposite side of the axial direction Ax with respect to the diffuser flow path 410.
- a flow path 70 is provided. With reference to the tongue end portion 71 of the scroll flow path 70, the circumferential length of the diffuser vane 401 changes as the rotation direction W of the centrifugal impeller 300 is directed (see FIG. 9).
- the diffuser vane 401 is formed longer toward the rotation direction W. Further, in a part of the region R4, the diffuser vane 401 is formed longer toward the rotation direction W. According to this, when the radial outer wall surface 74 (see FIG. 9) of the fan casing 52 changes in the circumferential direction (for example, when the scroll flow path 70 expands in the radial direction in the circumferential direction), the diffuser flow. The flow of air passing through the road 410 can be restrained, and a high pressure recovery rate can be obtained. As a result, even when the scroll flow path 70 is arranged on the side opposite to the axial direction Ax with respect to the diffuser vane 401 to reduce the size of the blower 22, the efficiency of the blower 22 can be improved.
- the length of the diffuser vane 401 in the circumferential direction increases toward the rotation direction W of the centrifugal impeller 300 with the tongue end portion 71 as a reference position (see FIG. 9). According to this, in a shape in which the scroll flow path 70 expands in the rotation direction W, the flow of air passing through the diffuser flow path 410 can be restrained, and a high pressure recovery rate can be obtained.
- the cross-sectional area of the communication passage 420 connecting the diffuser flow path 410 and the scroll flow path 70 changes in the rotation direction W of the centrifugal impeller 300 (see FIG. 10). According to this, it is possible to suppress the pressure loss due to the sudden contraction / expansion when passing through the communication passage 420, and it is possible to further improve the efficiency of the blower 22.
- the cross-sectional area of the communication passage 420 connecting the diffuser flow path 410 and the scroll flow path 70 increases in the rotation direction W of the centrifugal impeller 300 (see FIG. 10). According to this, in a shape in which the scroll flow path 70 expands in the rotation direction W, it is possible to suppress a pressure loss due to sudden contraction / expansion when passing through the communication passage 420, and further improve the efficiency of the blower 22. be able to.
- the air flow through the diffuser flow path 410 is directly guided to the introduction path 72 without being turned from the radial direction to the axial direction.
- the pressure loss due to the conversion of the air flow can be suppressed, and the efficiency of the blower 22 can be improved.
- the electric motor 100, the rotating shaft 101 rotatably provided on the electric motor 100, the centrifugal impeller 300 provided on the rotating shaft 101, and the centrifugal impeller 300 provided downstream of the centrifugal impeller 300 are provided in the circumferential direction. It includes a diffuser flow path 410 composed of the arranged diffuser vanes 401, and a scroll flow path 70 provided downstream of the diffuser flow path 410 on the side opposite to the axial direction Ax with respect to the diffuser flow path 410. ..
- the straight line connecting the rotation center O of the centrifugal impeller 300 and the tongue end 71 of the scroll flow path 70 is 0 °, the length L of the diffuser vane 401 (see FIG.
- FIG. 11 is a perspective view of a blower equipped with the diffuser of the second embodiment. Note that FIG. 11 shows a state in which the fan cover 51 is removed, as in FIG. 9. As shown in FIG. 11, the blower of the second embodiment includes a diffuser 400A instead of the diffuser 400 of the first embodiment.
- the diffuser outer bottom surface portion 400c extends further to the introduction path 72 on the outer diameter side of the discharge portion 76.
- the formed diffuser outer extension bottom surface portion 400d is provided.
- the diffuser outer extension bottom surface portion 400d is formed in the vicinity of the wall surface 74a formed so as to extend continuously from the radial outer wall surface 74 from the discharge portion 76 toward the introduction path 72, and from the tongue end portion 71. It is formed close to the wall surface 74b extending toward the introduction path 72 so as to face the wall surface 74a.
- the diffuser outer extension bottom surface portion 400d plays a role of a kind of guide vane, and the pressure can be recovered more efficiently even in the introduction path 72.
- the rate of change in the cross-sectional area of the flow path from the casing discharge port 59 to the outlet of the introduction path 72 tends to increase.
- the flow in the introduction path 72 is separated from the wall surface, and the pressure loss becomes large.
- the flow control by extending the diffuser outer extension bottom surface portion 400d to the introduction path 72 is effective for improving efficiency.
- the diffuser outer extension bottom surface portion 400d is provided with a diffuser vane extension portion 406 that extends a part of the diffuser vane 401 to the introduction path 72 on the outer diameter side of the discharge portion 76.
- the diffuser vane extension portion 406 is formed up to the edge portion (end portion) of the diffuser outer extension bottom surface portion 400d on the introduction path 72 side.
- the diffuser outer extension bottom surface portion 400d is provided with a guide vane 407 formed continuously from the inside of the scroll flow path 70 to the introduction path 72 via the discharge portion 76 on the scroll flow path 70 side on the back surface.
- the addition of such a guide vane 407 is also effective in obtaining a high rectifying effect.
- the blower 22 is provided in the washing machine S (see FIG. 1).
- the mounting power is good and the input power to the blower 22 during the drying operation can be reduced, so that the washing machine S with reduced power consumption can be provided.
- the size can be reduced in the radial direction, when the blowers 22 of the first and second embodiments are mounted on a washing machine having the same housing, a sound absorbing material or the like can be installed in an empty space in the radial direction, and the washing machine. It becomes possible to reduce the noise.
- the present invention is not limited to the above-described embodiment, and includes various modifications.
- the case where the length of the diffuser vane 401 in the circumferential direction increases in the rotation direction W has been described as an example, but the length of the diffuser 401 in the circumferential direction tends to be in the rotation direction W. It may have a structure that becomes smaller.
- the diffuser vane 401 at the 90 ° position P2 may have a longer circumferential length than the diffuser vane 401 at the 0 ° position P1. Further, the diffuser vane 401 at the 180 ° position P3 may have a longer circumferential length than the diffuser vane 401 at the 90 ° position P2.
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Abstract
The present invention comprises: an electric motor; a rotating shaft rotatably provided to the electric motor; a centrifugal impeller (300) provided to the rotating shaft; a diffuser flow path (410) that is provided downstream of the centrifugal impeller (300) and that is constituted by a vane arranged in a circumferential direction; and a scroll flow path (70) that is provided downstream of the diffuser flow path (410) and on the side opposite the axial direction with respect to the diffuser flow path (410). With reference to a tongue end (71) of the scroll flow path (70), the length of a diffuser vane (401) changes toward the direction of rotation (W) of the centrifugal impeller (300).
Description
本発明は、送風機およびこれを備えた洗濯機に関する。
The present invention relates to a blower and a washing machine equipped with the blower.
送風機は、電動機によって羽根車を回転させて、空気の流れを作り出す。送風機の吸込口から流入した空気は、羽根車で昇圧および増速され、静止流路で減速されることによって、流入した空気のもつ運動エネルギーが圧力エネルギーに変換され圧力が上昇する。高効率な送風機を得るには、良好な圧力回復を行う静止流路が重要である。静止流路を持つ送風機として、特許文献1に記載されているものがある。この特許文献1には、羽根車の回転軸とディフューザの中心軸とが異なるようにした構成の送風機が記載されている。
The blower rotates the impeller with an electric motor to create an air flow. The air flowing in from the suction port of the blower is boosted and accelerated by the impeller, and decelerated in the stationary flow path, so that the kinetic energy of the inflowing air is converted into pressure energy and the pressure rises. In order to obtain a highly efficient blower, a static flow path that performs good pressure recovery is important. As a blower having a stationary flow path, there is one described in Patent Document 1. Patent Document 1 describes a blower having a configuration in which the rotating shaft of the impeller and the central shaft of the diffuser are different from each other.
特許文献1に記載の送風機は、ディフューザ下流に設けられたスクロールの影響でディフューザ内において周方向に生じた圧力分布による圧力回復率の低下すなわち効率の低下を抑えるために、ディフューザの中心軸を羽根車の回転軸に対してずらすことを特徴としている。これにより、ディフューザによる圧力回復率を周方向に変化させ、スクロールに起因する圧力分布と相殺させることにより、周方向圧力分布の均一化を図り、高効率化を実現している。
The blower described in Patent Document 1 has blades on the central axis of the diffuser in order to suppress a decrease in pressure recovery rate, that is, a decrease in efficiency due to a pressure distribution generated in the circumferential direction in the diffuser due to the influence of a scroll provided downstream of the diffuser. It is characterized by shifting with respect to the rotation axis of the car. As a result, the pressure recovery rate by the diffuser is changed in the circumferential direction and offset by the pressure distribution caused by scrolling, so that the pressure distribution in the circumferential direction is made uniform and high efficiency is realized.
しかしながら、特許文献1に記載された送風機では、ディフューザによる最大の圧力回復率は周方向に均一なディフューザベーンの長さによってほぼ決定される。この場合、送風機を小型化すると、ディフューザベーンの長さも周方向に均等に短くなり、圧力回復率が低下する。このため、小型化と高効率化の両立が困難であった。
However, in the blower described in Patent Document 1, the maximum pressure recovery rate by the diffuser is almost determined by the length of the diffuser vane which is uniform in the circumferential direction. In this case, if the blower is miniaturized, the length of the diffuser vane is also shortened evenly in the circumferential direction, and the pressure recovery rate is lowered. Therefore, it has been difficult to achieve both miniaturization and high efficiency.
本発明は、前記した従来の課題を解決するものであり、小型化と高効率化の両立が可能な送風機およびこれを備えた洗濯機を提供することを目的とする。
The present invention solves the above-mentioned conventional problems, and an object of the present invention is to provide a blower capable of achieving both miniaturization and high efficiency, and a washing machine equipped with the blower.
本発明は、電動機と、前記電動機に回転自在に設けられる回転軸と、前記回転軸に設けられる羽根車と、前記羽根車の下流に設けられ、周方向に配置されたベーンによって構成されるディフューザ流路と、前記ディフューザ流路の下流に、当該ディフューザ流路に対して前記回転軸の軸方向とは逆側に設けられるスクロール流路と、を備え、前記スクロール流路の舌部を基準として、前記ベーンの長さが前記羽根車の回転方向に向かうにつれて変化することを特徴とする。
The present invention is a diffuser composed of an electric motor, a rotating shaft rotatably provided on the electric motor, an impeller provided on the rotating shaft, and vanes provided downstream of the impeller and arranged in the circumferential direction. A flow path and a scroll flow path provided downstream of the diffuser flow path on the side opposite to the axial direction of the rotation axis with respect to the diffuser flow path are provided, and the tongue portion of the scroll flow path is used as a reference. , The vane length changes as the impeller rotates in the direction of rotation.
本発明によれば、小型化と高効率化の両立が可能な送風機およびこれを備えた洗濯機を提供できる。
According to the present invention, it is possible to provide a blower capable of achieving both miniaturization and high efficiency, and a washing machine equipped with the blower.
以下、本発明を実施するための形態について、図面を参照して詳細に説明する。
図1は、本実施形態の送風機が搭載される洗濯機を示す縦断面図である。なお、以下では、縦型洗濯乾燥機を例に挙げて説明するが、前面側に洗濯物の出し入れ口が形成されたドラム式洗濯乾燥機に適用することもできる。 Hereinafter, embodiments for carrying out the present invention will be described in detail with reference to the drawings.
FIG. 1 is a vertical cross-sectional view showing a washing machine equipped with the blower of the present embodiment. In the following, a vertical washer / dryer will be described as an example, but it can also be applied to a drum-type washer / dryer having a laundry inlet / outlet port formed on the front side.
図1は、本実施形態の送風機が搭載される洗濯機を示す縦断面図である。なお、以下では、縦型洗濯乾燥機を例に挙げて説明するが、前面側に洗濯物の出し入れ口が形成されたドラム式洗濯乾燥機に適用することもできる。 Hereinafter, embodiments for carrying out the present invention will be described in detail with reference to the drawings.
FIG. 1 is a vertical cross-sectional view showing a washing machine equipped with the blower of the present embodiment. In the following, a vertical washer / dryer will be described as an example, but it can also be applied to a drum-type washer / dryer having a laundry inlet / outlet port formed on the front side.
図1に示すように、洗濯機Sは、筐体である外枠1、洗濯水を貯留する外槽2、回転槽3、駆動モータ10、送風機22などを備える。外槽2は、外枠1内に内蔵されるとともに外枠1に防振支持されている。回転槽3は、洗浄、乾燥される衣類などの洗濯物を収容する洗濯兼脱水槽であり、外槽2の内部に設けられている。また、回転槽3は、外槽2内に回転自在に支持される。
As shown in FIG. 1, the washing machine S includes an outer frame 1 which is a housing, an outer tub 2 for storing washing water, a rotary tub 3, a drive motor 10, a blower 22 and the like. The outer tub 2 is built in the outer frame 1 and is vibration-proof supported by the outer frame 1. The rotary tub 3 is a washing / dehydrating tub for accommodating laundry such as clothes to be washed and dried, and is provided inside the outer tub 2. Further, the rotary tank 3 is rotatably supported in the outer tank 2.
回転槽3の底部には、洗濯物を撹拌して洗う攪拌翼4が回動自在に設けられている。この攪拌翼4は、洗濯運転時および乾燥運転時に、正転/逆転を繰り返す動作が行われる。また、攪拌翼4は、脱水運転時に、回転槽3と一緒に高速回転し、回転槽3内の洗濯物に含まれる水分を脱水するようになっている。
At the bottom of the rotary tub 3, a stirring blade 4 for stirring and washing the laundry is rotatably provided. The stirring blade 4 repeats forward / reverse rotation during washing operation and drying operation. Further, the stirring blade 4 rotates at high speed together with the rotary tub 3 during the dehydration operation to dehydrate the water contained in the laundry in the rotary tub 3.
駆動モータ10は、外枠1内に設けられ、攪拌翼4および回転槽3の回転駆動を行う。また、駆動モータ10は、例えばDCブラシレスモータが使用される。DCブラシレスモータは、ベクトル制御によって行われる。なお、本実施形態では、駆動モータ10により、攪拌翼4および回転槽3を直接回転駆動しているが、ベルトなど(図示せず)を用いて駆動してもよい。
The drive motor 10 is provided in the outer frame 1 and drives the stirring blade 4 and the rotary tank 3 in rotation. Further, as the drive motor 10, for example, a DC brushless motor is used. The DC brushless motor is controlled by a vector. In the present embodiment, the stirring blade 4 and the rotary tank 3 are directly rotationally driven by the drive motor 10, but may be driven by using a belt or the like (not shown).
また、外枠1の上部には、外蓋5が設けられている。この外蓋5は、外枠1の上部に設けられたトップカバー6に開閉自在に設けられている。外槽2の上部には、内蓋34が開閉自在に設けられている。外蓋5および内蓋34を開くことで、回転槽3に対して洗濯物の出し入れを行うことができる。
Further, an outer lid 5 is provided on the upper part of the outer frame 1. The outer lid 5 is provided on a top cover 6 provided on the upper part of the outer frame 1 so as to be openable and closable. An inner lid 34 is provided on the upper portion of the outer tank 2 so as to be openable and closable. By opening the outer lid 5 and the inner lid 34, laundry can be taken in and out of the rotary tub 3.
また、外枠1内には、トップカバー6の背面側に、給水ユニット7が設けられている。この給水ユニット7は、内部に複数の水路を有する給水ボックス(図示せず)を有し、給水ホース接続口8からの水道水や風呂水を外槽2に供給する。また、トップカバー6の前側には、洗剤、仕上剤の投入装置35が設けられている。洗剤、仕上剤は、投入ホース36により、外槽2と回転槽3の間に注がれる。
Further, in the outer frame 1, a water supply unit 7 is provided on the back side of the top cover 6. The water supply unit 7 has a water supply box (not shown) having a plurality of water channels inside, and supplies tap water or bath water from the water supply hose connection port 8 to the outer tank 2. Further, on the front side of the top cover 6, a detergent and finishing agent charging device 35 is provided. The detergent and finishing agent are poured between the outer tank 2 and the rotary tank 3 by the charging hose 36.
また、洗濯機Sは、乾燥機構9を備えている。この乾燥機構9は、回転槽3内の洗濯物を乾燥する乾燥用空気の循環送風や除湿を行う。また、乾燥機構9は、大部分が乾燥用空気循環路で占められる。乾燥用空気循環路は、外槽2の底部に連通するように接続される底部循環路20、底部循環路20から上向きに延びる除湿用縦通路21を備える。
Further, the washing machine S is provided with a drying mechanism 9. The drying mechanism 9 circulates and dehumidifies the drying air for drying the laundry in the rotary tub 3. Further, the drying mechanism 9 is mostly occupied by the air circulation path for drying. The drying air circulation passage includes a bottom circulation passage 20 connected so as to communicate with the bottom of the outer tank 2, and a dehumidifying vertical passage 21 extending upward from the bottom circulation passage 20.
送風機22の吸込側は、除湿用縦通路21の上側に接続される。送風機22の排出側は、戻り接続循環路25と連通するように接続されている。また、送風機22と除湿用縦通路21の間には乾燥フィルタ45が配置され、送風機22に異物が流入しないようになっている。なお、送風機22の詳細については後述する。
The suction side of the blower 22 is connected to the upper side of the dehumidifying vertical passage 21. The discharge side of the blower 22 is connected so as to communicate with the return connection circulation path 25. Further, a drying filter 45 is arranged between the blower 22 and the dehumidifying vertical passage 21 to prevent foreign matter from flowing into the blower 22. The details of the blower 22 will be described later.
戻り接続循環路25は、上部蛇腹ホース23を有し、この上部蛇腹ホース23を介して外槽2の上部に連通するように接続される。底部循環路20も下部蛇腹ホース26を有し、この下部蛇腹ホース26を介して外槽2の底部に連通するように接続される。
The return connection circulation path 25 has an upper bellows hose 23, and is connected so as to communicate with the upper part of the outer tank 2 via the upper bellows hose 23. The bottom circulation path 20 also has a lower bellows hose 26, and is connected to the bottom of the outer tank 2 via the lower bellows hose 26.
下部蛇腹ホース26は、外槽2の底落込部31に接続される。この底落込部31は、下部連通管41を介して洗濯水排水路42と洗濯水循環水路43に連通する。洗濯水排水路42には排水弁44が設けられている。洗濯水循環水路43には異物除去トラップ32が設けられている。
The lower bellows hose 26 is connected to the bottom drop portion 31 of the outer tank 2. The bottom drop portion 31 communicates with the washing water drainage channel 42 and the washing water circulation water channel 43 via the lower communication pipe 41. A drain valve 44 is provided in the washing water drainage channel 42. A foreign matter removing trap 32 is provided in the washing water circulation water channel 43.
排水弁44は、洗濯運転時や乾燥運転時には閉じられている。また、排水弁44は、洗濯水を排水する排水時に開いて、外槽2に溜まっている洗濯水やすすぎ水を、洗濯水排水路42から洗濯機Sの外部(機外)に排出する。
The drain valve 44 is closed during the washing operation and the drying operation. Further, the drain valve 44 is opened at the time of draining the washing water, and the washing water and rinsing water accumulated in the outer tub 2 are discharged from the washing water drainage channel 42 to the outside (outside the machine) of the washing machine S.
洗濯水循環水路43は、洗濯水循環水縦水路46に接続される。この洗濯水循環水縦水路46は、外槽2の外側面に沿って上昇して回転槽3の上側まで延び、回転槽3の上側に設けられている洗濯糸屑除去装置33に連通するように接続される。
The washing water circulation water channel 43 is connected to the washing water circulation water vertical water channel 46. The washing water circulating water vertical channel 46 rises along the outer surface of the outer tub 2 and extends to the upper side of the rotary tub 3 so as to communicate with the washing thread waste removing device 33 provided on the upper side of the rotary tub 3. Be connected.
外槽2に溜まる洗濯水やすすぎ水は、洗濯水循環水縦水路46を流れて洗濯糸屑除去装置33から回転槽3に散布するように注がれる。この散布注水が続くなかで洗濯やすすぎが行われるので、少ない水量で洗濯、すすぎが行われる。
The washing water and rinsing water collected in the outer tub 2 flows through the washing water circulating water vertical water channel 46 and is poured from the washing thread waste removing device 33 into the rotary tub 3. Since washing and rinsing are performed while this spraying and water injection continues, washing and rinsing are performed with a small amount of water.
また、洗濯機Sは、外槽2に溜まる洗濯水やすすぎ水の水位を検知する水位センサ47を備えている。外槽2の底部近傍にはエアートラップ50が設けられている。このエアートラップ50に連通するようにエアーチューブ49が接続されている。このエアーチューブ49の上端には水位センサ47が連通するように接続される。外槽2内の水位変動を水位センサ47が感知して水位検知が行われる。
Further, the washing machine S is provided with a water level sensor 47 that detects the water level of washing water and rinsing water accumulated in the outer tub 2. An air trap 50 is provided near the bottom of the outer tank 2. An air tube 49 is connected so as to communicate with the air trap 50. A water level sensor 47 is connected to the upper end of the air tube 49 so as to communicate with the upper end. The water level sensor 47 detects the fluctuation of the water level in the outer tank 2 to detect the water level.
また、洗濯機Sでは、送風機22の遠心羽根車300(図2参照)が回転することによって乾燥用空気が回転槽3内を流通し、回転槽3内の洗濯物を乾燥させる。また、送風機22の電気ヒータ24(図3参照)によって、除湿領域で水分が凝縮された乾燥用空気が再加熱されて回転槽3を流れるので、洗濯物の水分をさらに蒸発させる。この水分除去が乾燥用空気の循環で繰り返されることにより洗濯物が乾燥される。
Further, in the washing machine S, the centrifugal impeller 300 (see FIG. 2) of the blower 22 rotates, so that the drying air circulates in the rotary tub 3 and dries the laundry in the rotary tub 3. Further, the electric heater 24 (see FIG. 3) of the blower 22 reheats the drying air in which the moisture is condensed in the dehumidifying region and flows through the rotary tub 3, so that the moisture in the laundry is further evaporated. The laundry is dried by repeating this water removal in the circulation of the drying air.
図2は、第1実施形態の送風機を示す外観斜視図である。
図2に示すように、送風機22は、ファンカバー51、ファンケーシング52、電動機100、遠心羽根車300、ディフューザ400(図3参照)、電気ヒータ24(図3参照)を備えて構成されている。なお、送風機22を洗濯機S(図1参照)に搭載する場合には、例えば、送風機22のファンカバー51が略下向きとなるようにして外枠1(図1参照)内に設置される。 FIG. 2 is an external perspective view showing the blower of the first embodiment.
As shown in FIG. 2, theblower 22 includes a fan cover 51, a fan casing 52, an electric motor 100, a centrifugal impeller 300, a diffuser 400 (see FIG. 3), and an electric heater 24 (see FIG. 3). .. When the blower 22 is mounted on the washing machine S (see FIG. 1), for example, the fan cover 51 of the blower 22 is installed in the outer frame 1 (see FIG. 1) so as to be substantially downward.
図2に示すように、送風機22は、ファンカバー51、ファンケーシング52、電動機100、遠心羽根車300、ディフューザ400(図3参照)、電気ヒータ24(図3参照)を備えて構成されている。なお、送風機22を洗濯機S(図1参照)に搭載する場合には、例えば、送風機22のファンカバー51が略下向きとなるようにして外枠1(図1参照)内に設置される。 FIG. 2 is an external perspective view showing the blower of the first embodiment.
As shown in FIG. 2, the
ファンカバー51には、吸込口57と排出口58が形成されている。吸込口57は、乾燥フィルタ45(図1参照)を介して除湿用縦通路21(図1参照)に接続される。排出口58は、乾燥用空気循環路の戻り接続循環路25(図1参照)に接続される。
The fan cover 51 is formed with a suction port 57 and an discharge port 58. The suction port 57 is connected to the dehumidifying vertical passage 21 (see FIG. 1) via the drying filter 45 (see FIG. 1). The discharge port 58 is connected to the return connection circulation path 25 (see FIG. 1) of the drying air circulation path.
図3は、ファンカバー側から見たときの送風機の分解斜視図である。
図3に示すように、ファンカバー51は、一方向に細長い形状を有し、長手方向の一方に吸込口57が形成され、長手方向の他方に排出口58が形成されている。吸込口57は、円形状の貫通孔であり、遠心羽根車300の吸込開口302の中央と対向する。排出口58は、円形状の貫通孔であり、電気ヒータ24の下流側に位置している。また、排出口58の直径は、吸込口57の直径よりも大きく形成されている。また、吸込口57と排出口58は、略同じ方向を向いて形成されている。 FIG. 3 is an exploded perspective view of the blower when viewed from the fan cover side.
As shown in FIG. 3, thefan cover 51 has an elongated shape in one direction, a suction port 57 is formed on one side in the longitudinal direction, and a discharge port 58 is formed on the other side in the longitudinal direction. The suction port 57 is a circular through hole and faces the center of the suction opening 302 of the centrifugal impeller 300. The discharge port 58 is a circular through hole and is located on the downstream side of the electric heater 24. Further, the diameter of the discharge port 58 is formed to be larger than the diameter of the suction port 57. Further, the suction port 57 and the discharge port 58 are formed so as to face substantially the same direction.
図3に示すように、ファンカバー51は、一方向に細長い形状を有し、長手方向の一方に吸込口57が形成され、長手方向の他方に排出口58が形成されている。吸込口57は、円形状の貫通孔であり、遠心羽根車300の吸込開口302の中央と対向する。排出口58は、円形状の貫通孔であり、電気ヒータ24の下流側に位置している。また、排出口58の直径は、吸込口57の直径よりも大きく形成されている。また、吸込口57と排出口58は、略同じ方向を向いて形成されている。 FIG. 3 is an exploded perspective view of the blower when viewed from the fan cover side.
As shown in FIG. 3, the
また、ファンカバー51は、吸込口57の周囲に、円環状の突出部51aが軸方向Axに突出して形成されている。なお、軸方向Axとは、電動機100の回転軸101が延びる方向を意味する。また、ファンカバー51は、電気ヒータ24が設けられる位置に略矩形状の突出部51bが形成されている。
Further, the fan cover 51 is formed with an annular protrusion 51a protruding in the axial direction Ax around the suction port 57. The axial direction Ax means the direction in which the rotating shaft 101 of the electric motor 100 extends. Further, the fan cover 51 has a substantially rectangular protrusion 51b formed at a position where the electric heater 24 is provided.
また、ファンカバー51の周縁部には、ファンケーシング52とねじ固定されるねじ固定部91が複数箇所に形成されている。
Further, on the peripheral edge of the fan cover 51, screw fixing portions 91 to be screw-fixed to the fan casing 52 are formed at a plurality of places.
ファンケーシング52は、ファンカバー51に対応する形状を有している。ファンケーシング52とファンカバー51とを組み合わせたときに、ファンカバー51とファンケーシング52との間に、遠心羽根車300、ディフューザ400および電気ヒータ24が配置される空間が形成されるように構成されている。
The fan casing 52 has a shape corresponding to the fan cover 51. When the fan casing 52 and the fan cover 51 are combined, a space for arranging the centrifugal impeller 300, the diffuser 400, and the electric heater 24 is formed between the fan cover 51 and the fan casing 52. ing.
また、ファンケーシング52は、ディフューザ400が配置される背面(下面)側にスクロール流路70が形成されている。このスクロール流路70は、舌端部71側の流路幅が狭く形成され、舌端部71から時計回り方向に向けて流路幅が徐々に広くなるように構成されている。なお、舌端部71は、スクロール流路70の開始点である。また、スクロール流路70の出口は、ケーシング吐出口59である(斜線部参照)。
Further, in the fan casing 52, a scroll flow path 70 is formed on the back surface (lower surface) side on which the diffuser 400 is arranged. The scroll flow path 70 is formed so that the flow path width on the tongue end portion 71 side is narrow and the flow path width gradually increases in the clockwise direction from the tongue end portion 71. The tip of the tongue 71 is the starting point of the scroll flow path 70. The outlet of the scroll flow path 70 is the casing discharge port 59 (see the shaded area).
また、ファンケーシング52は、スクロール流路70から電気ヒータ24に空気を導入する導入路72aが形成されている。電気ヒータ24は、多数のフィンを備え、スクロール流路70から流出し、導入路72aを通過した空気を加熱する。導入路72aは、電気ヒータ24に向けて流路幅が広がるように構成されている。詳述すると、導入路72aは、電気ヒータ24の加熱部分24aの幅と略同一の幅に広がるように構成されている。また、ファンカバー51の導入路72b(図4参照)についても、導入路72aと同様に下流に向けて流路幅が広がるように構成されている。ファンケーシング52とファンカバー51とを組み合わせることで、電気ヒータ24の矩形状の加熱部分24aに沿った形状の導入路72(図2参照)が形成される。
Further, the fan casing 52 is formed with an introduction path 72a for introducing air from the scroll flow path 70 into the electric heater 24. The electric heater 24 includes a large number of fins, flows out of the scroll flow path 70, and heats the air that has passed through the introduction path 72a. The introduction path 72a is configured so that the flow path width widens toward the electric heater 24. More specifically, the introduction path 72a is configured to extend to substantially the same width as the width of the heating portion 24a of the electric heater 24. Further, the introduction path 72b (see FIG. 4) of the fan cover 51 is also configured so that the flow path width widens toward the downstream as in the introduction path 72a. By combining the fan casing 52 and the fan cover 51, an introduction path 72 (see FIG. 2) having a shape along the rectangular heating portion 24a of the electric heater 24 is formed.
また、ファンケーシング52は、電気ヒータ24の下流側に、ファンカバー51の排出口58に連通する凹形状の流路77が形成されている。また、流路77は、排出口58に向けて傾斜するように、斜め上向きとなるように構成されている。
Further, in the fan casing 52, a concave flow path 77 communicating with the discharge port 58 of the fan cover 51 is formed on the downstream side of the electric heater 24. Further, the flow path 77 is configured to be obliquely upward so as to be inclined toward the discharge port 58.
また、ファンケーシング52は、電気ヒータ24の加熱部分から外れた位置が空気の流れの邪魔にならないように、幅方向に突出する形状を有している。
Further, the fan casing 52 has a shape that protrudes in the width direction so that the position deviated from the heating portion of the electric heater 24 does not interfere with the air flow.
また、ファンケーシング52には、スクロール流路70の中心に、電動機100の回転軸101が挿入される軸挿入孔80が形成されている。また、ファンケーシング52の外周縁部には、ファンカバー51のねじ固定部91に対応する位置に、ねじ(不図示)が挿通されるねじ挿通部92が形成されている。
Further, in the fan casing 52, a shaft insertion hole 80 into which the rotation shaft 101 of the electric motor 100 is inserted is formed in the center of the scroll flow path 70. Further, on the outer peripheral edge portion of the fan casing 52, a screw insertion portion 92 through which a screw (not shown) is inserted is formed at a position corresponding to the screw fixing portion 91 of the fan cover 51.
また、ファンケーシング52には、軸挿入孔80とスクロール流路70との間に、ディフューザ400をファンケーシング52に固定するためのねじ穴93が複数箇所(本実施形態では4箇所)に形成されている。これらのねじ穴93は、軸挿入孔80を囲むように形成されている。また、ファンケーシング52は、ねじ穴93の周縁に、円形の凹部93aが形成されている。
Further, in the fan casing 52, screw holes 93 for fixing the diffuser 400 to the fan casing 52 are formed at a plurality of locations (4 locations in the present embodiment) between the shaft insertion hole 80 and the scroll flow path 70. ing. These screw holes 93 are formed so as to surround the shaft insertion hole 80. Further, the fan casing 52 has a circular recess 93a formed on the peripheral edge of the screw hole 93.
また、ファンケーシング52には、ねじ穴93の径方向外周側に、ファンケーシング凹部94(凹状の溝部)が形成されている。このファンケーシング凹部94は、環状に形成されている。
Further, in the fan casing 52, a fan casing recess 94 (concave groove portion) is formed on the radial outer peripheral side of the screw hole 93. The fan casing recess 94 is formed in an annular shape.
電動機100は、径方向の中心に遠心羽根車300と結合される回転軸101を有し、ファンケーシング52に取り付けられる。また、電動機100は、回転軸101に固定されるロータ(回転子)、ロータの周囲に設けられるステータ(固定子)、回転軸101を回転自在に支持する軸受を有している。また、電動機100は、ロータ、ステータおよび軸受を収容する略円柱状のケース102を有している。このケース102の外周面(側面)には、円環状のつば部103が形成されている。つば部103には、電動機100をファンケーシング52にねじ固定するためのねじ挿通孔104が周方向に間隔を置いて複数箇所(本実施形態では4箇所)に形成されている。
The motor 100 has a rotating shaft 101 coupled to the centrifugal impeller 300 at the center in the radial direction, and is attached to the fan casing 52. Further, the motor 100 has a rotor (rotor) fixed to the rotating shaft 101, a stator (stator) provided around the rotor, and a bearing that rotatably supports the rotating shaft 101. Further, the motor 100 has a substantially columnar case 102 that houses a rotor, a stator, and a bearing. An annular brim 103 is formed on the outer peripheral surface (side surface) of the case 102. In the brim 103, screw insertion holes 104 for screw-fixing the motor 100 to the fan casing 52 are formed at a plurality of locations (four locations in the present embodiment) at intervals in the circumferential direction.
ディフューザ400は、例えば合成樹脂によって形成され、遠心羽根車300の軸方向Axの面と対向する円形の底板400aを有している。この底板400aは、径方向の中心に円形の貫通孔400bが形成されている。この貫通孔400bは、ファンケーシング52の軸挿入孔80よりも大径に形成されている。また、底板400aは、貫通孔400bの周囲に、該ディフューザ400をファンケーシング52に固定するためのねじ(不図示)が挿通されるねじ挿通孔430が複数箇所に形成されている。このねじ挿通孔430は、ファンケーシング52のねじ穴93と対応(対向)する位置に形成されている。
The diffuser 400 is formed of, for example, a synthetic resin, and has a circular bottom plate 400a facing the surface of the centrifugal impeller 300 in the axial direction Ax. The bottom plate 400a has a circular through hole 400b formed in the center in the radial direction. The through hole 400b is formed to have a diameter larger than that of the shaft insertion hole 80 of the fan casing 52. Further, the bottom plate 400a is formed with a plurality of screw insertion holes 430 around the through holes 400b through which screws (not shown) for fixing the diffuser 400 to the fan casing 52 are inserted. The screw insertion hole 430 is formed at a position corresponding to (opposing) the screw hole 93 of the fan casing 52.
また、ディフューザ400は、ねじ挿通孔430の周縁に、図示しないねじの頭部が、底板400aの表面(図示上面)から突出しないようにするための窪み部430aが形成されている。これにより、遠心羽根車300が回転したときに、底板400aと遠心羽根車300との距離を縮めつつ、遠心羽根車300がねじ(不図示)に接触しないようになっている。
Further, in the diffuser 400, a recessed portion 430a is formed on the peripheral edge of the screw insertion hole 430 so that the head of the screw (not shown) does not protrude from the surface (upper surface of the drawing) of the bottom plate 400a. As a result, when the centrifugal impeller 300 rotates, the distance between the bottom plate 400a and the centrifugal impeller 300 is shortened, and the centrifugal impeller 300 does not come into contact with the screw (not shown).
底板400aの外周縁部の全体には、該底板400aよりも軸方向Axに一段高く形成されたディフューザ外側底面部(基部)400cが形成されている。このディフューザ外側底面部400cの軸方向Axの上面(ファンカバー51側の面)には、ディフューザベーン401(ベーン)が周方向に沿って等間隔に形成されている。
A diffuser outer bottom surface (base) 400c formed one step higher in the axial direction Ax than the bottom plate 400a is formed on the entire outer peripheral edge of the bottom plate 400a. Diffuser vanes 401 (vanes) are formed at equal intervals along the circumferential direction on the upper surface (the surface on the fan cover 51 side) of the outer bottom surface portion 400c of the diffuser in the axial direction.
図4は、電動機側から見たときの送風機の分解斜視図である。
図4に示すように、ファンカバー51の吸込口57には、ベルマウス部57aが形成されている。また、ファンカバー51は、ベルマウス部57aの周囲にリング状のシール部材(不図示)が収容される凹部51cが形成されている。また、ファンカバー51には、シール部材(不図示)を凹部51cに保持させる環状の抑え部材(不図示)が設けられている。この抑え部材(不図示)は、凹部51cの周囲に形成され、凹部51cよりも一段高く(浅く)形成された環状の凹部51dに載置される。また、抑え部材(不図示)は、凹部51dの周囲に形成された固定部51eを介して固定される。 FIG. 4 is an exploded perspective view of the blower when viewed from the motor side.
As shown in FIG. 4, abell mouth portion 57a is formed at the suction port 57 of the fan cover 51. Further, the fan cover 51 is formed with a recess 51c in which a ring-shaped sealing member (not shown) is housed around the bell mouth portion 57a. Further, the fan cover 51 is provided with an annular holding member (not shown) for holding the seal member (not shown) in the recess 51c. This holding member (not shown) is placed in an annular recess 51d formed around the recess 51c and formed one step higher (shallow) than the recess 51c. Further, the holding member (not shown) is fixed via a fixing portion 51e formed around the recess 51d.
図4に示すように、ファンカバー51の吸込口57には、ベルマウス部57aが形成されている。また、ファンカバー51は、ベルマウス部57aの周囲にリング状のシール部材(不図示)が収容される凹部51cが形成されている。また、ファンカバー51には、シール部材(不図示)を凹部51cに保持させる環状の抑え部材(不図示)が設けられている。この抑え部材(不図示)は、凹部51cの周囲に形成され、凹部51cよりも一段高く(浅く)形成された環状の凹部51dに載置される。また、抑え部材(不図示)は、凹部51dの周囲に形成された固定部51eを介して固定される。 FIG. 4 is an exploded perspective view of the blower when viewed from the motor side.
As shown in FIG. 4, a
また、ファンカバー51には、円環状に形成された弾性部材90が設けられている。なお、図4では、弾性部材90がファンカバー51に取り付けられた状態を図示している。この弾性部材90は、ディフューザベーン401の先端(上端)と対向する位置に配置されている。
Further, the fan cover 51 is provided with an elastic member 90 formed in an annular shape. Note that FIG. 4 illustrates a state in which the elastic member 90 is attached to the fan cover 51. The elastic member 90 is arranged at a position facing the tip (upper end) of the diffuser vane 401.
また、ファンカバー51は、スクロール流路70(図3参照)から電気ヒータ24に向けて延びる導入路72bが形成されている。この導入路72bは、導入路72a(図3参照)に沿って形成されている。また、導入路72bは、スクロール流路70(図3参照)側から電気ヒータ24に向けて流路の深さ寸法H(流路高さ)が深く(高く)なるように構成されている。
Further, the fan cover 51 is formed with an introduction path 72b extending from the scroll flow path 70 (see FIG. 3) toward the electric heater 24. The introduction path 72b is formed along the introduction path 72a (see FIG. 3). Further, the introduction path 72b is configured so that the depth dimension H (flow path height) of the flow path becomes deeper (higher) from the scroll flow path 70 (see FIG. 3) side toward the electric heater 24.
ファンケーシング52のスクロール流路70は、電動機100が設置される側(電動機設置側)に膨らむようにして構成されている。また、スクロール流路70は、舌端部71(図3参照)側の流路から、導入路72a(図3参照)側に向けて、流路深さ(軸方向Axの深さ)が徐々に深くなるように構成されている。また、導入路72aは、電気ヒータ24に向けて流路深さが略一定となるように構成されている。電気ヒータ24の下流側の流路77は、ファンカバー51側に持ち上がるようにして構成されている。
The scroll flow path 70 of the fan casing 52 is configured to bulge toward the side where the motor 100 is installed (motor installation side). Further, in the scroll flow path 70, the flow path depth (depth of Ax in the axial direction) gradually increases from the flow path on the tongue end 71 (see FIG. 3) side toward the introduction path 72a (see FIG. 3). It is configured to be deep in. Further, the introduction path 72a is configured so that the flow path depth becomes substantially constant toward the electric heater 24. The flow path 77 on the downstream side of the electric heater 24 is configured to be lifted toward the fan cover 51 side.
また、ファンケーシング52には、電動機100を該ファンケーシング52に固定するためのねじボス78が複数箇所(本実施形態では4箇所)に形成されている。
Further, the fan casing 52 is formed with screw bosses 78 for fixing the motor 100 to the fan casing 52 at a plurality of locations (four locations in the present embodiment).
ディフューザ400は、ディフューザベーン401が設けられる面とは反対側(背面側)に凸条部440が形成されている。この凸条部440は、ファンケーシング52のファンケーシング凹部94(図3参照)と嵌合する。
The diffuser 400 has a ridge portion 440 formed on the side (rear side) opposite to the surface on which the diffuser vane 401 is provided. The ridge portion 440 fits into the fan casing recess 94 (see FIG. 3) of the fan casing 52.
また、ディフューザ400のねじ挿通孔430には、ファンケーシング52の凹部93a(図3参照)と凹凸嵌合する突起部430bが形成されている。それぞれの突起部430bは、ファンケーシング52のそれぞれに対応する凹部93aと嵌合する。
Further, the screw insertion hole 430 of the diffuser 400 is formed with a protrusion 430b that is unevenly fitted with the recess 93a (see FIG. 3) of the fan casing 52. Each protrusion 430b fits into a recess 93a corresponding to each of the fan casings 52.
また、ディフューザ400が有するねじ挿通孔430とファンケーシング52のねじ穴93とが、ねじ(図示せず)によって固定される。電動機100の回転軸101(図3参照)は、ファンケーシング52の軸挿入孔80に挿通される。そして、回転軸101は、ディフューザ400の貫通孔400bに挿通され、遠心羽根車300に回転軸101の先端が結合(固定)される。
Further, the screw insertion hole 430 of the diffuser 400 and the screw hole 93 of the fan casing 52 are fixed by screws (not shown). The rotating shaft 101 (see FIG. 3) of the electric motor 100 is inserted into the shaft insertion hole 80 of the fan casing 52. Then, the rotary shaft 101 is inserted into the through hole 400b of the diffuser 400, and the tip of the rotary shaft 101 is coupled (fixed) to the centrifugal impeller 300.
ファンカバー51とファンケーシング52は、ねじ(図示せず)がねじ挿通部92に挿通され、ねじ固定部91に固定されることで互いに結合される。これにより、送風機22は、遠心羽根車300とディフューザ400を配置するケーシング部61(図2参照)と、電気ヒータ24を配置するヒータ部62(図2参照)と、を形成する。なお、ケーシング部61とヒータ部62との接続空間境界面をケーシング吐出口59(図3参照)とする。
The fan cover 51 and the fan casing 52 are connected to each other by inserting a screw (not shown) into the screw insertion portion 92 and fixing the screw (not shown) to the screw fixing portion 91. As a result, the blower 22 forms a casing portion 61 (see FIG. 2) in which the centrifugal impeller 300 and the diffuser 400 are arranged, and a heater portion 62 (see FIG. 2) in which the electric heater 24 is arranged. The connection space boundary surface between the casing portion 61 and the heater portion 62 is designated as the casing discharge port 59 (see FIG. 3).
また、遠心羽根車300は、羽根321の内径端部が、吸込開口302(図3参照)よりも径方向外側に位置している。また、遠心羽根車300は、羽根321の外径端部が、シュラウド板301の外周縁部とハブ板311の外周縁部と略一致するように構成されている。
Further, in the centrifugal impeller 300, the inner diameter end of the blade 321 is located radially outside the suction opening 302 (see FIG. 3). Further, the centrifugal impeller 300 is configured such that the outer diameter end portion of the blade 321 substantially coincides with the outer peripheral edge portion of the shroud plate 301 and the outer peripheral edge portion of the hub plate 311.
なお、第1実施形態では、シュラウド板301を有するクローズドタイプの遠心羽根車300を例に挙げて説明するが、樹脂によりハブ板311と羽根321を一体成型したオープンタイプの遠心羽根車としてもよい。これにより、部品点数を低減でき、低コスト化が図られる。また、樹脂型とすることで、三次元化も容易となり、高効率化も図られる。なお、三次元化とは、羽根にさらにひねりを加えて形成することである。これにより、さらに効率化が図れる。
In the first embodiment, a closed type centrifugal impeller 300 having a shroud plate 301 will be described as an example, but an open type centrifugal impeller in which the hub plate 311 and the blade 321 are integrally molded with resin may be used. .. As a result, the number of parts can be reduced and the cost can be reduced. In addition, the resin type facilitates three-dimensionalization and improves efficiency. The three-dimensionalization is to form the blade by further twisting it. As a result, efficiency can be further improved.
また、第1実施形態では、後向き羽根を持つターボファンを例に挙げて説明するが、前向き羽根を持つシロッコファンを適用しもよい。また、羽根車の形状は遠心型に限定されるものではなく、斜流型でもよい。斜流型とすることで、羽根車の外径を小型化でき、送風機22の小型化が可能となる。
Further, in the first embodiment, a turbofan having rearward blades will be described as an example, but a sirocco fan having forward blades may be applied. Further, the shape of the impeller is not limited to the centrifugal type, and may be a mixed flow type. By adopting the oblique flow type, the outer diameter of the impeller can be miniaturized, and the blower 22 can be miniaturized.
次に、従来例としてのディフューザを備えた送風機について説明する。図5は、従来のディフューザの平面図である。図6は、従来のディフューザを搭載した送風機の平面図である。図7は、従来のディフューザによって形成される連通路を示す模式図である。
図5に示すように、ディフューザ1400は、底板1400aの周囲に、複数のディフューザベーン1401が周方向全体に等間隔で配置されるようにして構成されている。このディフューザベーン1401は、底板1400aの周囲に形成されたディフューザ外側底面部1400cに対して軸方向Ax(図3、図4参照)の向きに立ち上がるようにして形成されている。また、ディフューザベーン1401は、遠心羽根車300(図3、図4参照)の外周縁部よりも外側に位置している。 Next, a blower equipped with a diffuser as a conventional example will be described. FIG. 5 is a plan view of a conventional diffuser. FIG. 6 is a plan view of a blower equipped with a conventional diffuser. FIG. 7 is a schematic view showing a communication passage formed by a conventional diffuser.
As shown in FIG. 5, thediffuser 1400 is configured such that a plurality of diffuser vanes 1401 are arranged around the bottom plate 1400a at equal intervals in the entire circumferential direction. The diffuser vane 1401 is formed so as to stand up in the axial direction Ax (see FIGS. 3 and 4) with respect to the diffuser outer bottom surface portion 1400c formed around the bottom plate 1400a. Further, the diffuser vane 1401 is located outside the outer peripheral edge portion of the centrifugal impeller 300 (see FIGS. 3 and 4).
図5に示すように、ディフューザ1400は、底板1400aの周囲に、複数のディフューザベーン1401が周方向全体に等間隔で配置されるようにして構成されている。このディフューザベーン1401は、底板1400aの周囲に形成されたディフューザ外側底面部1400cに対して軸方向Ax(図3、図4参照)の向きに立ち上がるようにして形成されている。また、ディフューザベーン1401は、遠心羽根車300(図3、図4参照)の外周縁部よりも外側に位置している。 Next, a blower equipped with a diffuser as a conventional example will be described. FIG. 5 is a plan view of a conventional diffuser. FIG. 6 is a plan view of a blower equipped with a conventional diffuser. FIG. 7 is a schematic view showing a communication passage formed by a conventional diffuser.
As shown in FIG. 5, the
ディフューザベーン1401は、薄板状に形成され、平面視において周方向に延びて形成されている。また、ディフューザベーン1401は、その前縁1412(一端)よりも後縁1402(他端)が径方向外側に位置するように構成されている。また、ディフューザベーン1401A(1401)は、周方向の略中央、かつ、ディフューザベーン1401Aの径方向の内側に、周方向に隣り合うディフューザベーン1401B(1401)の前縁1412が位置している。換言すると、ディフューザベーン1401B(1401)は、周方向の略中央、かつ、ディフューザベーン1401Bの径方向の外側に、周方向に隣り合うディフューザベーン1401A(1401)の後縁1402が位置している。また、隣り合うディフューザベーン1401A、1401B間には後記するディフューザ流路1410が形成されている。このディフューザ流路1410は、前縁1412側から後縁1402側に向けて径方向の幅が徐々に広くなるように構成されている。
The diffuser vane 1401 is formed in a thin plate shape and extends in the circumferential direction in a plan view. Further, the diffuser vane 1401 is configured such that the trailing edge 1402 (the other end) is located radially outside the front edge 1412 (one end). Further, in the diffuser vane 1401A (1401), the front edge 1412 of the diffuser vane 1401B (1401) adjacent to the diffuser vane 1401B (1401) is located substantially in the center in the circumferential direction and inside the radial direction of the diffuser vane 1401A. In other words, in the diffuser vane 1401B (1401), the trailing edge 1402 of the diffuser vane 1401A (1401) adjacent to the diffuser vane 1401B (1401) is located substantially in the center in the circumferential direction and outside in the radial direction of the diffuser vane 1401B. Further, a diffuser flow path 1410 described later is formed between the adjacent diffuser vanes 1401A and 1401B. The diffuser flow path 1410 is configured so that the width in the radial direction gradually increases from the front edge 1412 side to the trailing edge 1402 side.
また、ディフューザベーン1401A(1401)は、ディフューザ外側底面部1400cの外周縁部が、後縁1402から、隣接するディフューザベーン1401Bの圧力面1403に対して略垂直に延びるようにして切込部1404が形成されている。なお、圧力面1403とは、ディフューザベーン1401の径方向外側に向いている前縁1412から後縁1402までの全体の面を意味している。このような切込部1404が形成されることで、ディフューザ外側底面部1400cの外周縁部に、軸方向Ax(図3、図4参照)に貫通する略三角形状の切欠部1405が形成されている。換言すると、ディフューザ1400の外周縁部は、周方向に沿って鋸歯状になるように形成されている。
Further, in the diffuser vane 1401A (1401), the cut portion 1404 is provided so that the outer peripheral edge portion of the diffuser outer bottom surface portion 1400c extends from the trailing edge 1402 substantially perpendicular to the pressure surface 1403 of the adjacent diffuser vane 1401B. It is formed. The pressure surface 1403 means the entire surface of the diffuser vane 1401 from the front edge 1412 to the trailing edge 1402 facing outward in the radial direction. By forming such a notch portion 1404, a substantially triangular notch 1405 penetrating in the axial direction Ax (see FIGS. 3 and 4) is formed on the outer peripheral edge portion of the diffuser outer bottom surface portion 1400c. There is. In other words, the outer peripheral edge of the diffuser 1400 is formed so as to be serrated along the circumferential direction.
図6に示すように、ディフューザ1400をファンケーシング52に取り付けたときに、ファンケーシング52と、ディフューザベーン1401と、切込部1404とで形成された略三角形状の連通路1420が形成される。また、ディフューザ1400の径方向の外周には、略三角形状の連通路1420が周方向に並んで形成されている。この連通路1420の上流側は、隣り合うディフューザベーン1401,1401と、ディフューザ外側底面部1400cと、ファンカバー51(図3、図4参照)とで囲まれるディフューザ流路1410と連通する。遠心羽根車300がW方向に回転することで、遠心羽根車300の外周から空気(流体)が吐出される。
As shown in FIG. 6, when the diffuser 1400 is attached to the fan casing 52, a substantially triangular continuous passage 1420 formed by the fan casing 52, the diffuser vane 1401, and the notch 1404 is formed. Further, on the outer circumference of the diffuser 1400 in the radial direction, substantially triangular passages 1420 are formed side by side in the circumferential direction. The upstream side of the communication passage 1420 communicates with the diffuser flow path 1410 surrounded by the adjacent diffuser vanes 1401, 1401, the diffuser outer bottom surface portion 1400c, and the fan cover 51 (see FIGS. 3 and 4). When the centrifugal impeller 300 rotates in the W direction, air (fluid) is discharged from the outer circumference of the centrifugal impeller 300.
また、吐出された空気は、ディフューザ流路1410(矢印参照)を通り、略三角形状の連通路1420に流れ込み、ディフューザ1400の背面側に設けられたスクロール流路70(図6の紙面垂直方向の奥側)に流れ込む。
Further, the discharged air passes through the diffuser flow path 1410 (see the arrow) and flows into the substantially triangular continuous passage 1420, and the scroll flow path 70 provided on the back side of the diffuser 1400 (in the direction perpendicular to the paper surface in FIG. 6). It flows into the back side).
スクロール流路70に流れた空気は、スクロール部75を通り、吐出部76に吐出される。そして、吐出部76を通過した空気は、ケーシング吐出口59を通り、導入路72に導入される。なお、吐出部76は、点Bからケーシング吐出口59までのスクロール流路70を意味している。
The air flowing through the scroll flow path 70 passes through the scroll portion 75 and is discharged to the discharge portion 76. Then, the air that has passed through the discharge portion 76 passes through the casing discharge port 59 and is introduced into the introduction path 72. The discharge unit 76 means a scroll flow path 70 from the point B to the casing discharge port 59.
図7に示すように、従来のディフューザ1400を備えた送風機では、連通路1420の断面積が一定にも拘わらず、ディフューザベーン1401の後縁1402の外径が一定値のため、後縁1402と径方向外側壁面74との距離S100が、遠心羽根車300の回転方向Wに向けて大きくなる。これにより、ディフューザベーン1401の後縁1402とファンケーシング52の径方向外側壁面74との間では、ディフューザ流路1410を通過した空気の流れが径方向外側壁面74によって拘束されないので、この領域(距離S100の隙間)では高い圧力回復率を得ることができない。
As shown in FIG. 7, in the blower provided with the conventional diffuser 1400, although the cross-sectional area of the communication passage 1420 is constant, the outer diameter of the trailing edge 1402 of the diffuser vane 1401 is a constant value, so that the blower has a constant value with the trailing edge 1402. The distance S100 from the radial outer wall surface 74 increases in the rotation direction W of the centrifugal impeller 300. As a result, between the trailing edge 1402 of the diffuser vane 1401 and the radial outer wall surface 74 of the fan casing 52, the flow of air passing through the diffuser flow path 1410 is not constrained by the radial outer wall surface 74, and thus this region (distance). A high pressure recovery rate cannot be obtained in the gap of S100).
このような送風機を実装する際の制約の中において、より効率よく圧力回復を得るためには、できる限りディフューザベーン1401の長さを長くし、ディフューザ1400内における圧力回復率を高くすることが、送風機の設計上、極めて重要となる。また、このような場合には、ディフューザ流路1410の出口からスクロール流路70へと導くための連通路1420の流路断面積も、周方向に(回転方向Wに向けて)変化させる必要がある。これは、連通路1420を通過する際の急収縮・拡大に伴う圧力損失を抑えるためである。
Within the constraints of mounting such a blower, in order to obtain pressure recovery more efficiently, it is necessary to increase the length of the diffuser vane 1401 as much as possible and increase the pressure recovery rate in the diffuser 1400. It is extremely important in the design of the blower. Further, in such a case, it is necessary to change the flow path cross-sectional area of the communication passage 1420 for guiding from the outlet of the diffuser flow path 1410 to the scroll flow path 70 in the circumferential direction (toward the rotation direction W). is there. This is to suppress the pressure loss due to sudden contraction / expansion when passing through the communication passage 1420.
次に、第1実施形態の送風機22の構造について図8ないし図10を参照して説明する。図8は、第1実施形態のディフューザの平面図である。図9は、ファンカバーを取り外した状態を示す、第1実施形態のディフューザを搭載した送風機の平面図である。図10は、第1実施形態のディフューザによって形成される連通路を示す模式図である。なお、以下に示すディフューザ400の形状は一例であって、第1実施形態に限定されるものではない。
Next, the structure of the blower 22 of the first embodiment will be described with reference to FIGS. 8 to 10. FIG. 8 is a plan view of the diffuser of the first embodiment. FIG. 9 is a plan view of a blower equipped with the diffuser of the first embodiment, showing a state in which the fan cover is removed. FIG. 10 is a schematic view showing a communication passage formed by the diffuser of the first embodiment. The shape of the diffuser 400 shown below is an example, and is not limited to the first embodiment.
図8に示すように、第1実施形態の送風機22(図3、図4参照)は、従来例(図5ないじ図7参照)のディフューザ1400に替えて、ディフューザ400を備えたものである。このディフューザ400は、ディフューザベーン401の長さが周方向において異なっている。より具体的には、ディフューザベーン401の前縁412の位置は周方向に同一であるが、後縁402の位置が径方向に異なっている。
As shown in FIG. 8, the blower 22 of the first embodiment (see FIGS. 3 and 4) is provided with a diffuser 400 in place of the diffuser 1400 of the conventional example (see FIG. 5 and FIG. 7). .. In this diffuser 400, the lengths of the diffuser vanes 401 are different in the circumferential direction. More specifically, the position of the front edge 412 of the diffuser vane 401 is the same in the circumferential direction, but the position of the trailing edge 402 is different in the radial direction.
また、ディフューザ400は、符号R1で示す領域(90°の範囲)において、従来例と同様に、底板400aの周囲に、複数のディフューザベーン401が周方向に等間隔で配置されている。なお、領域R1の基準位置(0°の位置)は、舌端部71の先端と遠心羽根車300の回転中心Oを通るラインである。このディフューザベーン401は、底板400aの周囲に形成されたディフューザ外側底面部400cに対して軸方向Ax(図3、図4参照)の向き(図8の紙面垂直手前側の向き)に立ち上がるようにして形成されている。また、ディフューザベーン401は、遠心羽根車300(図3、図4参照)の外周縁部よりも外側に位置している。
Further, in the diffuser 400, in the region indicated by the reference numeral R1 (range of 90 °), a plurality of diffuser vanes 401 are arranged at equal intervals in the circumferential direction around the bottom plate 400a as in the conventional example. The reference position (position at 0 °) of the region R1 is a line passing through the tip of the tongue end portion 71 and the rotation center O of the centrifugal impeller 300. The diffuser vane 401 stands up in the axial direction Ax (see FIGS. 3 and 4) (direction toward the front side perpendicular to the paper surface in FIG. 8) with respect to the diffuser outer bottom surface portion 400c formed around the bottom plate 400a. Is formed. Further, the diffuser vane 401 is located outside the outer peripheral edge portion of the centrifugal impeller 300 (see FIGS. 3 and 4).
ディフューザベーン401は、薄板状に形成され、平面視において周方向に延びて形成されている。また、ディフューザベーン401は、その前縁412(一端または内径側の端部)よりも後縁402(他端または外径側の端部)が径方向外側に位置している。また、領域R1のディフューザベーン401A(401)は、周方向の略中央、かつ、ディフューザベーン401Aの径方向の内側に、周方向に隣り合うディフューザベーン401B(401)の前縁412が位置している。換言すると、ディフューザベーン401B(401)は、周方向の略中央、かつ、ディフューザベーン401Bの径方向の外側に、周方向に隣り合うディフューザベーン401A(401)の後縁402が位置している。また、隣り合うディフューザベーン401A,401B間には後記するディフューザ流路410が形成されている。このディフューザ流路410は、前縁412側から後縁402側に向けて径方向の幅が徐々に広くなるように構成されている。
The diffuser vane 401 is formed in a thin plate shape and extends in the circumferential direction in a plan view. Further, in the diffuser vane 401, the trailing edge 402 (the other end or the outer diameter side end) is located radially outside the front edge 412 (one end or the inner diameter side end). Further, in the diffuser vane 401A (401) of the region R1, the front edge 412 of the diffuser vane 401B (401) adjacent to the diffuser vane 401B (401) is located substantially in the center in the circumferential direction and inside the radial direction of the diffuser vane 401A. There is. In other words, in the diffuser vane 401B (401), the trailing edge 402 of the diffuser vane 401A (401) adjacent to the diffuser vane 401B (401) is located substantially in the center in the circumferential direction and outside in the radial direction of the diffuser vane 401B. Further, a diffuser flow path 410 described later is formed between the adjacent diffuser vanes 401A and 401B. The diffuser flow path 410 is configured so that the width in the radial direction gradually increases from the front edge 412 side to the trailing edge 402 side.
また、ディフューザベーン401A(401)は、ディフューザ外側底面部400cの外周縁部が、後縁402から、隣接するディフューザベーン401Bの圧力面403に対して略垂直に延びるようにして切込部404が形成されている。なお、圧力面403とは、ディフューザベーン401の径方向外側に向いている前縁412から後縁402までの全体の面を意味している。このような切込部404が形成されることで、ディフューザ外側底面部400cの外周縁部に、軸方向Axに貫通する略三角形状の切欠部405が形成されている。換言すると、領域R1におけるディフューザ400の外周縁部は、周方向に沿って鋸歯状になるように形成されている。
Further, in the diffuser vane 401A (401), the notch portion 404 is provided so that the outer peripheral edge portion of the diffuser outer bottom surface portion 400c extends from the trailing edge 402 substantially perpendicular to the pressure surface 403 of the adjacent diffuser vane 401B. It is formed. The pressure surface 403 means the entire surface of the diffuser vane 401 from the front edge 412 to the trailing edge 402 facing outward in the radial direction. By forming such a notch portion 404, a substantially triangular notch portion 405 penetrating in the axial direction Ax is formed on the outer peripheral edge portion of the diffuser outer bottom surface portion 400c. In other words, the outer peripheral edge of the diffuser 400 in the region R1 is formed so as to be serrated along the circumferential direction.
また、領域R2(90°の範囲)におけるディフューザ400は、符号R1と同様に、周方向の長さが同じ長さのディフューザベーン401が周方向(回転方向W)に等間隔で配置されている。
Further, in the diffuser 400 in the region R2 (range of 90 °), the diffuser vanes 401 having the same length in the circumferential direction are arranged at equal intervals in the circumferential direction (rotational direction W) as in the reference numeral R1. ..
また、領域R3(90°の範囲)におけるディフューザ400は、ディフューザベーン401が回転方向Wに向かうにつれて長くなるように構成されている。具体的には、ディフューザベーン401Dは、隣り合うディフューザベーン401Cよりも回転方向Wに長く形成されている。ディフューザベーン401Eは、隣り合うディフューザベーン401Dよりも回転方向Wに長く形成されている。ディフューザベーン401Fは、隣り合うディフューザベーン401Eよりも回転方向Wに長く形成されている。ディフューザベーン401Gは、隣り合うディフューザベーン401Fよりも回転方向Wに長く形成されている。ディフューザベーン401Hは、隣り合うディフューザベーン401Gよりも回転方向Wに長く形成されている。
Further, the diffuser 400 in the region R3 (range of 90 °) is configured to become longer as the diffuser vane 401 approaches the rotation direction W. Specifically, the diffuser vane 401D is formed longer in the rotation direction W than the adjacent diffuser vanes 401C. The diffuser vanes 401E are formed longer in the rotation direction W than the adjacent diffuser vanes 401D. The diffuser vanes 401F are formed longer in the rotation direction W than the adjacent diffuser vanes 401E. The diffuser vanes 401G are formed longer in the rotation direction W than the adjacent diffuser vanes 401F. The diffuser vane 401H is formed longer in the rotation direction W than the adjacent diffuser vanes 401G.
また、領域R4(90°の範囲)における一部のディフューザ400は、ディフューザベーン401が回転方向Wに向かうにつれて長くなるように構成されている。具体的には、ディフューザベーン401Jは、隣り合うディフューザベーン401Iよりも回転方向Wに長く形成されている。ディフューザベーン401Kは、隣り合うディフューザベーン401Jよりも回転方向Wに長く形成されている。ディフューザベーン401Lは、隣り合うディフューザベーン401Kよりも回転方向Wに長く形成されている。
Further, some diffusers 400 in the region R4 (range of 90 °) are configured to become longer as the diffuser vane 401 approaches the rotation direction W. Specifically, the diffuser vane 401J is formed longer in the rotation direction W than the adjacent diffuser vanes 401I. The diffuser vanes 401K are formed longer in the rotation direction W than the adjacent diffuser vanes 401J. The diffuser vanes 401L are formed longer in the rotation direction W than the adjacent diffuser vanes 401K.
また、領域R4(90°の範囲)における他部のディフューザ400は、ディフューザベーン401が回転方向Wに向かうにつれて短くなるように構成されている。具体的には、ディフューザベーン401Mは、隣り合うディフューザベーン401Lよりも回転方向Wに短く形成されている。ディフューザベーン401Nは、隣り合うディフューザベーン401Mと回転方向Wに同じ長さになるように形成されている。なお、ディフューザベーン401M,401Nは、符号R1で示す領域のディフューザベーン401よりも回転方向Wに向けて長く形成されている。
Further, the diffuser 400 in the other portion in the region R4 (range of 90 °) is configured to become shorter as the diffuser vane 401 approaches the rotation direction W. Specifically, the diffuser vane 401M is formed shorter in the rotation direction W than the adjacent diffuser vanes 401L. The diffuser vanes 401N are formed so as to have the same length in the rotation direction W as the adjacent diffuser vanes 401M. The diffuser vanes 401M and 401N are formed longer in the rotation direction W than the diffuser vanes 401 in the region indicated by reference numeral R1.
また、ディフューザ400は、領域R4において、ディフューザ外側底面部400cが、ディフューザベーン401J,401K,401Lの後縁402まで延びて形成されている。また、ディフューザ400は、領域R4において、ディフューザベーン401Mの後縁402よりも径方向外側まで延びている。このように、ディフューザ400は、領域R4において、ディフューザ外側底面部400cが、ディフューザベーン401J,401K,401L,401M,401Nにかけて略円弧状に形成された円弧部400c1を有している。換言すると、ディフューザ400は、領域R4の一部において、前記した連通路420が形成されない形状(前記した鋸刃状ではない形状)を有している。
Further, in the diffuser 400, in the region R4, the diffuser outer bottom surface portion 400c is formed so as to extend to the trailing edge 402 of the diffuser vanes 401J, 401K, 401L. Further, the diffuser 400 extends radially outward from the trailing edge 402 of the diffuser vane 401M in the region R4. As described above, the diffuser 400 has an arc portion 400c1 in which the diffuser outer bottom surface portion 400c is formed in a substantially arc shape over the diffuser vanes 401J, 401K, 401L, 401M, and 401N in the region R4. In other words, the diffuser 400 has a shape (a shape other than the saw blade shape) in which the communication passage 420 is not formed in a part of the region R4.
図9に示すように、ディフューザ400をファンケーシング52に搭載すると、ディフューザベーン401Nの先端(後縁402)が舌端部71に当接する。また、ディフューザ外側底面部400cの円弧部400c1(ハブ壁面)は、ケーシング吐出口59(スクロール流路70の出口)に向けて延びている。
As shown in FIG. 9, when the diffuser 400 is mounted on the fan casing 52, the tip (rear edge 402) of the diffuser vane 401N comes into contact with the tongue end portion 71. Further, the arc portion 400c1 (hub wall surface) of the diffuser outer bottom surface portion 400c extends toward the casing discharge port 59 (outlet of the scroll flow path 70).
また、第1実施形態では、スクロール流路70の舌端部71の位置を基準とし、そこから遠心羽根車300の回転方向Wにディフューザベーン401の周方向の長さが長くなっている。詳述すると、第1実施形態では、舌端部71の先端と遠心羽根車300の回転中心Oとを結ぶ位置P1を基準(0°)とした場合、基準の位置P1から回転方向Wに90°回転した位置をP2、基準の位置P1から回転方向Wに180°回転した位置をP3、基準の位置P1から回転方向Wに270°回転した位置をP4とする。なお、位置P1から位置P2までは、前記した領域R1に相当する。位置P2から位置P3までは、前記した領域R2に相当する。位置P3から位置P4までは、前記した領域R3に相当する。位置P4から位置P1までは、前記した領域R4に相当する。
Further, in the first embodiment, the position of the tongue end portion 71 of the scroll flow path 70 is used as a reference, and the length of the diffuser vane 401 in the circumferential direction is longer in the rotation direction W of the centrifugal impeller 300 from there. More specifically, in the first embodiment, when the position P1 connecting the tip of the tongue end portion 71 and the rotation center O of the centrifugal impeller 300 is set as a reference (0 °), 90 in the rotation direction W from the reference position P1. Let P2 be the position rotated by °, P3 be the position rotated 180 ° in the rotation direction W from the reference position P1, and P4 be the position rotated 270 ° in the rotation direction W from the reference position P1. The positions P1 to P2 correspond to the above-mentioned region R1. The position P2 to the position P3 correspond to the above-mentioned region R2. The position P3 to the position P4 corresponds to the above-mentioned region R3. The position P4 to the position P1 corresponds to the above-mentioned region R4.
このように第1実施形態では、0°から180°までの間(図8の領域R1,R2)では、回転方向Wに向けて同じ長さのディフューザベーン401となり、180°から270°までの間(図8の領域R3)では、回転方向Wに向けてディフューザベーン401の長さが徐々に長くなるように構成されている。また、第1実施形態では、270°から360°(0°)までの間(図8の領域R4)では、一部において回転方向Wに向けてディフューザベーン401の長さが徐々に長くなるように構成されている。また、第1実施形態では、270°から360°(0°)までの間(図8の領域R4)では、他部(残りの一部)において回転方向Wに向けてディフューザベーン401の長さが短くなるように構成されている。
As described above, in the first embodiment, between 0 ° and 180 ° (regions R1 and R2 in FIG. 8), the diffuser vane 401 having the same length in the rotation direction W is obtained, and the diffuser vane 401 is from 180 ° to 270 °. In the space (region R3 in FIG. 8), the length of the diffuser vane 401 is gradually increased in the rotation direction W. Further, in the first embodiment, the length of the diffuser vane 401 is gradually increased in a part in the rotation direction W from 270 ° to 360 ° (0 °) (region R4 in FIG. 8). It is configured in. Further, in the first embodiment, in the range from 270 ° to 360 ° (0 °) (region R4 in FIG. 8), the length of the diffuser vane 401 in the rotation direction W in the other portion (the remaining part). Is configured to be shorter.
また、第1実施形態では、0°の位置P1と90°の位置P2とでは、ディフューザベーン401の周方向の長さが同じに形成されている。また、90°の位置P2と180°の位置P3とでは、ディフューザベーン401の周方向の長さが同じに形成されている。180°の位置P3と、270°の位置P4とでは、270°の位置P4のディフューザベーン401が、180°の位置P3のディフューザベーン401よりも長く形成されている。
Further, in the first embodiment, the length of the diffuser vane 401 in the circumferential direction is formed to be the same at the position P1 at 0 ° and the position P2 at 90 °. Further, the length of the diffuser vane 401 in the circumferential direction is formed to be the same at the position P2 at 90 ° and the position P3 at 180 °. At the 180 ° position P3 and the 270 ° position P4, the diffuser vane 401 at the 270 ° position P4 is formed longer than the diffuser vane 401 at the 180 ° position P3.
また、第1実施形態では、ディフューザベーン401が、従来例での距離S100(図7参照)を埋めるように、回転方向Wに向けて長く形成されている。このように、第1実施形態の送風機22(図3、図4参照)は、特に、ファンケーシング52の径方向外側壁面74(図9参照)が周方向に変化する場合において特に有効である。なお、洗濯機S(図1参照)のように、送風機22(図3、図4参照)の製品内への実装スペースが限定される場合、ファンケーシング52の径方向外側壁面74は、円型を確保できるわけではない。
Further, in the first embodiment, the diffuser vane 401 is formed long in the rotation direction W so as to fill the distance S100 (see FIG. 7) in the conventional example. As described above, the blower 22 of the first embodiment (see FIGS. 3 and 4) is particularly effective when the radial outer wall surface 74 (see FIG. 9) of the fan casing 52 changes in the circumferential direction. When the mounting space of the blower 22 (see FIGS. 3 and 4) in the product is limited as in the washing machine S (see FIG. 1), the radial outer wall surface 74 of the fan casing 52 is circular. Cannot be secured.
そこで、第1実施形態では、図10に示すように、ディフューザベーン401の長さが長いディフューザ流路410であればあるほど、連通路420の流路断面積を大きくする必要がある。すなわち、周方向(回転方向W)に向けて長くなるディフューザベーン401に対応するように、連通路420の流路断面積も、周方向(回転方向W)に大きくなる。
Therefore, in the first embodiment, as shown in FIG. 10, the longer the diffuser flow path 410 of the diffuser vane 401, the larger the flow path cross-sectional area of the communication passage 420 needs to be. That is, the flow path cross-sectional area of the communication passage 420 also increases in the circumferential direction (rotational direction W) so as to correspond to the diffuser vane 401 that becomes longer in the circumferential direction (rotational direction W).
この場合、ディフューザベーン401の後縁402は、スクロール流路70の径方向外側壁面74と接してもいいし、離しても構わない。接する方が、よりディフューザベーン401を長くできるため、高効率化になる。ただし、製品組み立ての観点等により、接することが困難な場合も多いため、数mm程度の隙間を設ける構成にしてもよい。このような隙間を設ける場合、ディフューザベーン401の後縁402と径方向外側壁面74との隙間幅S1(図9参照)は、周方向に一定値とすることが好ましい。
In this case, the trailing edge 402 of the diffuser vane 401 may be in contact with or separated from the radial outer wall surface 74 of the scroll flow path 70. The more in contact, the longer the diffuser vane 401 can be made, resulting in higher efficiency. However, since it is often difficult to make contact from the viewpoint of product assembly, a gap of about several mm may be provided. When such a gap is provided, the gap width S1 (see FIG. 9) between the trailing edge 402 of the diffuser vane 401 and the outer wall surface 74 in the radial direction is preferably a constant value in the circumferential direction.
また、ディフューザ流路410から連通路420、スクロール流路70を経て導入路72(図9参照)へと流入する際、ディフューザ流路410から連通路420を経ずに直接導入路72へと流入できる箇所(図9の領域R4a参照)では、直接に導入路72へと流れを流入させた方が、圧力回復率は高くなり、効率は高くなる。換言すると、ディフューザ400は、ディフューザ流路410のうち、導入路72と直接接続可能な領域R4aにおいて連通路420を有さないディフューザ流路410A(図9参照)が設けられている。これにより、ディフューザ流路410Aを経た空気の流れが、径方向から軸方向Axに転向されることなく、直接導入路72へと導かれることになる。その結果、空気の流れの転向に伴う圧力損失を抑制することができ、送風機22の高効率化を実現できる。
Further, when flowing from the diffuser flow path 410 through the communication passage 420 and the scroll flow path 70 into the introduction path 72 (see FIG. 9), the flow flows directly from the diffuser flow path 410 into the introduction path 72 without passing through the communication passage 420. Where possible (see region R4a in FIG. 9), the pressure recovery rate is higher and the efficiency is higher when the flow is directly flowed into the introduction path 72. In other words, the diffuser 400 is provided with a diffuser flow path 410A (see FIG. 9) which does not have a communication passage 420 in the region R4a which can be directly connected to the introduction path 72 in the diffuser flow path 410. As a result, the air flow through the diffuser flow path 410A is directly guided to the introduction path 72 without being converted from the radial direction to the axial direction Ax. As a result, the pressure loss due to the conversion of the air flow can be suppressed, and the efficiency of the blower 22 can be improved.
以上説明したように、第1実施形態の送風機22は、電動機100と、電動機100に回転自在に設けられる回転軸101と、回転軸101に設けられる遠心羽根車300と、遠心羽根車300の下流に設けられ、周方向に配置されたディフューザベーン401によって構成されるディフューザ流路410と、ディフューザ流路410の下流に、該ディフューザ流路410に対して軸方向Axとは逆側に設けられるスクロール流路70と、を備える。スクロール流路70の舌端部71を基準として、ディフューザベーン401の周方向の長さが遠心羽根車300の回転方向Wに向かうにつれて変化する(図9参照)。すなわち、領域R3では、ディフューザベーン401が回転方向Wに向かうにつれて長く形成されている。また、領域R4の一部では、ディフューザベーン401が回転方向Wに向かうにつれて長く形成されている。これによれば、ファンケーシング52の径方向外側壁面74(図9参照)が周方向に変化する場合(例えば、スクロール流路70が周方向に向けて径方向に拡大する場合)において、ディフューザ流路410を通過した空気の流れを拘束することができ、高い圧力回復率を得ることができる。その結果、スクロール流路70をディフューザベーン401に対して軸方向Axとは逆側に配置して送風機22を小型化した場合であっても、送風機22の高効率化を図ることができる。
As described above, the blower 22 of the first embodiment includes the electric motor 100, the rotating shaft 101 rotatably provided on the electric motor 100, the centrifugal impeller 300 provided on the rotating shaft 101, and the downstream of the centrifugal impeller 300. A diffuser flow path 410 composed of diffuser vanes 401 arranged in the circumferential direction and a scroll provided downstream of the diffuser flow path 410 on the opposite side of the axial direction Ax with respect to the diffuser flow path 410. A flow path 70 is provided. With reference to the tongue end portion 71 of the scroll flow path 70, the circumferential length of the diffuser vane 401 changes as the rotation direction W of the centrifugal impeller 300 is directed (see FIG. 9). That is, in the region R3, the diffuser vane 401 is formed longer toward the rotation direction W. Further, in a part of the region R4, the diffuser vane 401 is formed longer toward the rotation direction W. According to this, when the radial outer wall surface 74 (see FIG. 9) of the fan casing 52 changes in the circumferential direction (for example, when the scroll flow path 70 expands in the radial direction in the circumferential direction), the diffuser flow. The flow of air passing through the road 410 can be restrained, and a high pressure recovery rate can be obtained. As a result, even when the scroll flow path 70 is arranged on the side opposite to the axial direction Ax with respect to the diffuser vane 401 to reduce the size of the blower 22, the efficiency of the blower 22 can be improved.
また、第1実施形態は、舌端部71を基準位置として、ディフューザベーン401の周方向の長さが遠心羽根車300の回転方向Wに向けて大きくなる(図9参照)。これによれば、スクロール流路70が回転方向Wに拡大する形状において、ディフューザ流路410を通過した空気の流れを拘束でき、高い圧力回復率を得ることができる。
Further, in the first embodiment, the length of the diffuser vane 401 in the circumferential direction increases toward the rotation direction W of the centrifugal impeller 300 with the tongue end portion 71 as a reference position (see FIG. 9). According to this, in a shape in which the scroll flow path 70 expands in the rotation direction W, the flow of air passing through the diffuser flow path 410 can be restrained, and a high pressure recovery rate can be obtained.
また、第1実施形態は、ディフューザ流路410とスクロール流路70とを接続する連通路420の断面積が遠心羽根車300の回転方向Wに向けて変化する(図10参照)。これによれば、連通路420を通過する際の急収縮・拡大に伴う圧力損失を抑えることができ、送風機22のさらなる高効率化を図ることができる。
Further, in the first embodiment, the cross-sectional area of the communication passage 420 connecting the diffuser flow path 410 and the scroll flow path 70 changes in the rotation direction W of the centrifugal impeller 300 (see FIG. 10). According to this, it is possible to suppress the pressure loss due to the sudden contraction / expansion when passing through the communication passage 420, and it is possible to further improve the efficiency of the blower 22.
また、第1実施形態は、ディフューザ流路410とスクロール流路70とを接続する連通路420の断面積が遠心羽根車300の回転方向Wに向けて大きくなる(図10参照)。これによれば、スクロール流路70が回転方向Wに拡大する形状において、連通路420を通過する際の急収縮・拡大に伴う圧力損失を抑えることができ、送風機22のさらなる高効率化を図ることができる。
Further, in the first embodiment, the cross-sectional area of the communication passage 420 connecting the diffuser flow path 410 and the scroll flow path 70 increases in the rotation direction W of the centrifugal impeller 300 (see FIG. 10). According to this, in a shape in which the scroll flow path 70 expands in the rotation direction W, it is possible to suppress a pressure loss due to sudden contraction / expansion when passing through the communication passage 420, and further improve the efficiency of the blower 22. be able to.
また、第1実施形態は、スクロール流路70の出口には、ディフューザ流路410とスクロール流路70とを接続する連通路420を有さないディフューザ流路410Aが存在する(図9参照)。これによれば、ディフューザ流路410を経た空気の流れが、径方向から軸方向に転向されることなく、直接導入路72へと導かれることになる。その結果、空気の流れの転向に伴う圧力損失を抑制することができ、送風機22の高効率化を実現できる。
Further, in the first embodiment, at the outlet of the scroll flow path 70, there is a diffuser flow path 410A that does not have a communication passage 420 connecting the diffuser flow path 410 and the scroll flow path 70 (see FIG. 9). According to this, the air flow through the diffuser flow path 410 is directly guided to the introduction path 72 without being turned from the radial direction to the axial direction. As a result, the pressure loss due to the conversion of the air flow can be suppressed, and the efficiency of the blower 22 can be improved.
また、第1実施形態は、電動機100と、電動機100に回転自在に設けられる回転軸101と、回転軸101に設けられる遠心羽根車300と、遠心羽根車300の下流に設けられ、周方向に配置されたディフューザベーン401によって構成されるディフューザ流路410と、ディフューザ流路410の下流に、当該ディフューザ流路410に対して軸方向Axとは逆側に設けられスクロール流路70と、を備える。遠心羽根車300の回転中心Oとスクロール流路70の舌端部71とを結ぶ直線を0°とした場合、ディフューザベーン401の長さL(図8参照)が遠心羽根車300の回転方向Wを正として、270°の位置P4が、90°の位置P2、180°の位置P3とは異なっている(90°の位置、180°の位置、270°の位置の少なくとも1箇所の位置において異なる)。これによれば、ファンケーシング52の径方向外側壁面74(図9参照)が周方向に変化する場合(例えばスクロール流路70が周方向に向けて径方向に拡大する場合)において、ディフューザ流路410を通過した空気の流れを拘束でき、高い圧力回復率を得ることができる。その結果、スクロール流路70をディフューザベーン401に対して軸方向Axとは反対側に配置して送風機22を小型化した場合であっても、送風機22の高効率化を図ることができる。
Further, in the first embodiment, the electric motor 100, the rotating shaft 101 rotatably provided on the electric motor 100, the centrifugal impeller 300 provided on the rotating shaft 101, and the centrifugal impeller 300 provided downstream of the centrifugal impeller 300 are provided in the circumferential direction. It includes a diffuser flow path 410 composed of the arranged diffuser vanes 401, and a scroll flow path 70 provided downstream of the diffuser flow path 410 on the side opposite to the axial direction Ax with respect to the diffuser flow path 410. .. When the straight line connecting the rotation center O of the centrifugal impeller 300 and the tongue end 71 of the scroll flow path 70 is 0 °, the length L of the diffuser vane 401 (see FIG. 8) is the rotation direction W of the centrifugal impeller 300. Is positive, the position P4 at 270 ° is different from the position P2 at 90 ° and the position P3 at 180 ° (at least one position at 90 °, 180 °, 270 °). ). According to this, when the radial outer wall surface 74 (see FIG. 9) of the fan casing 52 changes in the circumferential direction (for example, when the scroll flow path 70 expands in the radial direction in the circumferential direction), the diffuser flow path The flow of air that has passed through the 410 can be constrained, and a high pressure recovery rate can be obtained. As a result, even when the scroll flow path 70 is arranged on the side opposite to the axial direction Ax with respect to the diffuser vane 401 to reduce the size of the blower 22, the efficiency of the blower 22 can be improved.
また、第1実施形態は、ディフューザベーン401の長さL(図8参照)は、0°の位置P1=90°の位置P2=180°の位置P3<270°の位置P4の関係を満たす。これによれば、スクロール流路70が回転方向Wに向けて拡大する形状において、ディフューザ流路410を通過した空気の流れを拘束でき、高い圧力回復率を得ることができる。
Further, in the first embodiment, the length L of the diffuser vane 401 (see FIG. 8) satisfies the relationship of 0 ° position P1 = 90 ° position P2 = 180 ° position P3 <270 ° position P4. According to this, in a shape in which the scroll flow path 70 expands in the rotation direction W, the flow of air passing through the diffuser flow path 410 can be restrained, and a high pressure recovery rate can be obtained.
(第2実施形態)
図11は、第2実施形態のディフューザを搭載した送風機の斜視図である。なお、図11では、図9と同様に、ファンカバー51を取り外した状態を示している。
図11に示すように、第2実施形態の送風機は、第1実施形態のディフューザ400に替えてディフューザ400Aを備えている。 (Second Embodiment)
FIG. 11 is a perspective view of a blower equipped with the diffuser of the second embodiment. Note that FIG. 11 shows a state in which thefan cover 51 is removed, as in FIG. 9.
As shown in FIG. 11, the blower of the second embodiment includes adiffuser 400A instead of the diffuser 400 of the first embodiment.
図11は、第2実施形態のディフューザを搭載した送風機の斜視図である。なお、図11では、図9と同様に、ファンカバー51を取り外した状態を示している。
図11に示すように、第2実施形態の送風機は、第1実施形態のディフューザ400に替えてディフューザ400Aを備えている。 (Second Embodiment)
FIG. 11 is a perspective view of a blower equipped with the diffuser of the second embodiment. Note that FIG. 11 shows a state in which the
As shown in FIG. 11, the blower of the second embodiment includes a
ディフューザ400Aは、ディフューザ外側底面部400cがスクロール流路70の径方向外側壁面74と近接する構成に加えて、ディフューザ外側底面部400cが吐出部76のさらに外径側の導入路72まで延長して形成されたディフューザ外側延長底面部400dを備えている。このディフューザ外側延長底面部400dは、吐出部76から導入路72に向けて、径方向外側壁面74と連続して延びて形成される壁面74aに近接して形成されるとともに、舌端部71から導入路72に向けて壁面74aに対向して延びる壁面74bに近接して形成されている。
In the diffuser 400A, in addition to the configuration in which the diffuser outer bottom surface portion 400c is close to the radial outer wall surface 74 of the scroll flow path 70, the diffuser outer bottom surface portion 400c extends further to the introduction path 72 on the outer diameter side of the discharge portion 76. The formed diffuser outer extension bottom surface portion 400d is provided. The diffuser outer extension bottom surface portion 400d is formed in the vicinity of the wall surface 74a formed so as to extend continuously from the radial outer wall surface 74 from the discharge portion 76 toward the introduction path 72, and from the tongue end portion 71. It is formed close to the wall surface 74b extending toward the introduction path 72 so as to face the wall surface 74a.
これにより、導入路72内では、ディフューザ外側延長底面部400dが、ある種のガイドベーンの役割を果たし、導入路72内においても、より効率的に圧力回復が可能となる。特に、洗濯機Sのように送風機22の実装スペースが限られる場合、ケーシング吐出口59から導入路72の出口にかけての流路断面積の変化率が大きくなる傾向にある。それにより、導入路72内での流れが壁面からはく離し、圧力損失が大きくなる。この圧力損失を防ぐためにも、ディフューザ外側延長底面部400dを導入路72まで延長することによる流れの制御は、高効率化に効果的である。
As a result, in the introduction path 72, the diffuser outer extension bottom surface portion 400d plays a role of a kind of guide vane, and the pressure can be recovered more efficiently even in the introduction path 72. In particular, when the mounting space of the blower 22 is limited as in the washing machine S, the rate of change in the cross-sectional area of the flow path from the casing discharge port 59 to the outlet of the introduction path 72 tends to increase. As a result, the flow in the introduction path 72 is separated from the wall surface, and the pressure loss becomes large. In order to prevent this pressure loss, the flow control by extending the diffuser outer extension bottom surface portion 400d to the introduction path 72 is effective for improving efficiency.
また、ディフューザ外側延長底面部400dは、ディフューザベーン401の一部を吐出部76のさらに外径側の導入路72まで延長するディフューザベーン延長部406を備えている。このディフューザベーン延長部406は、ディフューザ外側延長底面部400dの導入路72側の縁部(端部)まで形成されている。このようなディフューザベーン延長部406を追加して設けることによって、より高い整流効果が得られる。
Further, the diffuser outer extension bottom surface portion 400d is provided with a diffuser vane extension portion 406 that extends a part of the diffuser vane 401 to the introduction path 72 on the outer diameter side of the discharge portion 76. The diffuser vane extension portion 406 is formed up to the edge portion (end portion) of the diffuser outer extension bottom surface portion 400d on the introduction path 72 side. By additionally providing such a diffuser vane extension portion 406, a higher rectifying effect can be obtained.
また、ディフューザ外側延長底面部400dは、裏面のスクロール流路70側にスクロール流路70内から吐出部76を経て導入路72へと連続して形成されるガイドベーン407を備えている。このようなガイドベーン407を追加して設けることによっても、高い整流効果を得る点において有効である。
Further, the diffuser outer extension bottom surface portion 400d is provided with a guide vane 407 formed continuously from the inside of the scroll flow path 70 to the introduction path 72 via the discharge portion 76 on the scroll flow path 70 side on the back surface. The addition of such a guide vane 407 is also effective in obtaining a high rectifying effect.
第1実施形態および第2実施形態では、送風機22が洗濯機Sに備えられている(図1参照)。これにより、搭載性が良く、乾燥運転時の送風機22への入力電力を低減できるため、消費電力量を抑えた洗濯機Sを提供することができる。また、径方向に小さくできるため、同じ筐体の洗濯機に第1および第2実施形態の送風機22を搭載した場合、径方向の空いた空間に吸音材等を設置することができ、洗濯機の低騒音化を図ることが可能になる。
In the first embodiment and the second embodiment, the blower 22 is provided in the washing machine S (see FIG. 1). As a result, the mounting power is good and the input power to the blower 22 during the drying operation can be reduced, so that the washing machine S with reduced power consumption can be provided. Further, since the size can be reduced in the radial direction, when the blowers 22 of the first and second embodiments are mounted on a washing machine having the same housing, a sound absorbing material or the like can be installed in an empty space in the radial direction, and the washing machine. It becomes possible to reduce the noise.
なお、本発明は上記した実施形態に限定されるものではなく、様々な変形例が含まれる。例えば、前記した実施形態では、ディフューザベーン401の周方向の長さが回転方向Wに向けて大きくなる場合を例に挙げて説明したが、ディフューザ401の周方向の長さが回転方向Wに向けて小さくなる構成を備えていてもよい。
The present invention is not limited to the above-described embodiment, and includes various modifications. For example, in the above-described embodiment, the case where the length of the diffuser vane 401 in the circumferential direction increases in the rotation direction W has been described as an example, but the length of the diffuser 401 in the circumferential direction tends to be in the rotation direction W. It may have a structure that becomes smaller.
また、第2実施形態では、1本のディフューザベーン延長部406を設けた場合を例に挙げて説明したが、複数のディフューザベーン延長部を設ける構成であってもよい。
Further, in the second embodiment, the case where one diffuser vane extension portion 406 is provided has been described as an example, but a configuration in which a plurality of diffuser vane extension portions are provided may be provided.
また、第2実施形態では、1本のガイドベーン407を設けた場合を例に挙げて説明したが、複数のガイドベーンを設ける構成であってもよい。
Further, in the second embodiment, the case where one guide vane 407 is provided has been described as an example, but a configuration in which a plurality of guide vanes are provided may be used.
また、90°の位置P2のディフューザベーン401が、0°の位置P1のディフューザベーン401よりも周方向の長さを長くした構成であってもよい。また、180°の位置P3のディフューザベーン401が、90°の位置P2のディフューザベーン401よりも周方向の長さを長くした構成であってもよい。
Further, the diffuser vane 401 at the 90 ° position P2 may have a longer circumferential length than the diffuser vane 401 at the 0 ° position P1. Further, the diffuser vane 401 at the 180 ° position P3 may have a longer circumferential length than the diffuser vane 401 at the 90 ° position P2.
1 外枠
2 外槽
3 回転槽
22 送風機
51 ファンカバー
52 ファンケーシング
57 吸込口
59 ケーシング吐出口(スクロール流路の出口部)
61 ケーシング部
70 スクロール流路
71 舌端部(舌部)
72,72a,72b 導入路
74 径方向外側壁面
75 スクロール部
76 吐出部
90 弾性部材
100 電動機
101 回転軸
300 遠心羽根車(羽根車)
400,400A ディフューザ
400c ディフューザ外側底面部
400d ディフューザ外側延長底面部
401,401A ディフューザベーン(ベーン)
402 後縁
406 ディフューザベーン延長部(ベーン延長部)
407 ガイドベーン
410 ディフューザ流路
412 前縁
420 連通路
Ax 軸方向
P1 0°の位置
P2 90°の位置
P3 180°の位置
P4 270°の位置
S 洗濯機
W 回転方向 1Outer frame 2 Outer tank 3 Rotating tank 22 Blower 51 Fan cover 52 Fan casing 57 Suction port 59 Casing discharge port (outlet part of scroll flow path)
61Casing part 70 Scroll flow path 71 Tongue end part (tongue part)
72, 72a, 72bIntroductory path 74 Radial outer wall surface 75 Scroll part 76 Discharge part 90 Elastic member 100 Electric motor 101 Rotating shaft 300 Centrifugal impeller (impeller)
400,400ADiffuser 400c Diffuser outer bottom surface 400d Diffuser outer extension bottom surface 401,401A Diffuser vane (vane)
402Trailing edge 406 Diffuser vane extension (vane extension)
407Guide vane 410 Diffuser flow path 412 Front edge 420 Continuous passage Ax Axial direction P10 ° position P2 90 ° position P3 180 ° position P4 270 ° position S Washing machine W Rotation direction
2 外槽
3 回転槽
22 送風機
51 ファンカバー
52 ファンケーシング
57 吸込口
59 ケーシング吐出口(スクロール流路の出口部)
61 ケーシング部
70 スクロール流路
71 舌端部(舌部)
72,72a,72b 導入路
74 径方向外側壁面
75 スクロール部
76 吐出部
90 弾性部材
100 電動機
101 回転軸
300 遠心羽根車(羽根車)
400,400A ディフューザ
400c ディフューザ外側底面部
400d ディフューザ外側延長底面部
401,401A ディフューザベーン(ベーン)
402 後縁
406 ディフューザベーン延長部(ベーン延長部)
407 ガイドベーン
410 ディフューザ流路
412 前縁
420 連通路
Ax 軸方向
P1 0°の位置
P2 90°の位置
P3 180°の位置
P4 270°の位置
S 洗濯機
W 回転方向 1
61
72, 72a, 72b
400,400A
402
407
Claims (11)
- 電動機と、
前記電動機に回転自在に設けられる回転軸と、
前記回転軸に設けられる羽根車と、
前記羽根車の下流に設けられ、周方向に配置されたベーンによって構成されるディフューザ流路と、
前記ディフューザ流路の下流に、当該ディフューザ流路に対して前記回転軸の軸方向とは逆側に設けられるスクロール流路と、を備え、
前記スクロール流路の舌部を基準として、前記ベーンの長さが前記羽根車の回転方向に向かうにつれて変化することを特徴とする送風機。 With an electric motor
A rotating shaft rotatably provided on the motor and
An impeller provided on the rotating shaft and
A diffuser flow path provided downstream of the impeller and composed of vanes arranged in the circumferential direction,
Downstream of the diffuser flow path, a scroll flow path provided on the side opposite to the axial direction of the rotation axis with respect to the diffuser flow path is provided.
A blower characterized in that the length of the vane changes as the impeller rotates in the direction of rotation with respect to the tongue portion of the scroll flow path. - 請求項1に記載の送風機において、
前記舌部を基準位置として、前記ベーンの周方向の長さが前記羽根車の回転方向に向けて大きくなることを特徴とする送風機。 In the blower according to claim 1,
A blower characterized in that the circumferential length of the vane increases in the rotational direction of the impeller with the tongue portion as a reference position. - 電動機と、
前記電動機に回転自在に設けられる回転軸と、
前記回転軸に設けられる羽根車と、
前記羽根車の下流に設けられ、周方向に配置されたベーンによって構成されるディフューザ流路と、
前記ディフューザ流路の下流に、当該ディフューザ流路に対して前記回転軸の軸方向とは逆側に設けられるスクロール流路と、を備え、
前記羽根車の回転中心と前記スクロール流路の舌部とを結ぶ直線を0°とした場合、前記ベーンの長さが前記羽根車の回転方向を正として、90°の位置、180°の位置、270°の位置の少なくとも1箇所の位置において異なることを特徴とする送風機。 With an electric motor
A rotating shaft rotatably provided on the motor and
An impeller provided on the rotating shaft and
A diffuser flow path provided downstream of the impeller and composed of vanes arranged in the circumferential direction,
Downstream of the diffuser flow path, a scroll flow path provided on the side opposite to the axial direction of the rotation axis with respect to the diffuser flow path is provided.
When the straight line connecting the center of rotation of the impeller and the tongue of the scroll flow path is 0 °, the length of the vane is 90 ° and 180 ° with the rotation direction of the impeller as positive. A blower characterized in that it differs at at least one position at a position of 270 °. - 請求項3に記載の送風機において、
前記ベーンの長さは、0°の位置≦90°の位置≦180°の位置<270°の位置の関係を満たすことを特徴とする送風機。 In the blower according to claim 3,
The blower is characterized in that the length of the vane satisfies the relationship of 0 ° position ≤ 90 ° position ≤ 180 ° position <270 ° position. - 請求項1または請求項3に記載の送風機において、
前記ディフューザ流路と前記スクロール流路とを接続する連通路の断面積が前記羽根車の回転方向に向けて変化することを特徴とする送風機。 In the blower according to claim 1 or 3.
A blower characterized in that the cross-sectional area of a communication passage connecting the diffuser flow path and the scroll flow path changes in the rotational direction of the impeller. - 請求項5に記載の送風機において、
前記ディフューザ流路と前記スクロール流路とを接続する連通路の断面積が前記羽根車の回転方向に向けて大きくなることを特徴とする送風機。 In the blower according to claim 5,
A blower characterized in that the cross-sectional area of the communication passage connecting the diffuser flow path and the scroll flow path increases in the rotational direction of the impeller. - 請求項1または請求項3に記載の送風機において、
前記スクロール流路の出口には、前記ディフューザ流路と前記スクロール流路とを接続する連通路を有さないディフューザ流路が少なくとも一つ存在することを特徴とする送風機。 In the blower according to claim 1 or 3.
A blower characterized in that at least one diffuser flow path having no communication path connecting the diffuser flow path and the scroll flow path exists at the outlet of the scroll flow path. - 請求項1または請求項3に記載の送風機において、
前記ディフューザ流路を形成するハブ壁面が、前記スクロール流路の出口部より外側まで延長して形成されていることを特徴とする送風機。 In the blower according to claim 1 or 3.
A blower characterized in that a hub wall surface forming the diffuser flow path is formed so as to extend to the outside from an outlet portion of the scroll flow path. - 請求項8に記載の送風機において、
前記ハブ壁面には、前記ベーンを延長したベーン延長部が形成されていることを特徴とする送風機。 In the blower according to claim 8,
A blower characterized in that a vane extension portion extending the vane is formed on the hub wall surface. - 請求項8に記載の送風機において、
前記ハブ壁面には、前記ベーンとは逆側の面に前記スクロール流路から前記出口部の外側に向けてガイドベーンが形成されていることを特徴とする送風機。 In the blower according to claim 8,
A blower characterized in that a guide vane is formed on the wall surface of the hub from the scroll flow path toward the outside of the outlet portion on a surface opposite to the vane. - 請求項1または請求項3に記載の送風機を備えたことを特徴とする洗濯機。 A washing machine provided with the blower according to claim 1 or 3.
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