CN114729648A - Blower and washing machine - Google Patents
Blower and washing machine Download PDFInfo
- Publication number
- CN114729648A CN114729648A CN202080078780.5A CN202080078780A CN114729648A CN 114729648 A CN114729648 A CN 114729648A CN 202080078780 A CN202080078780 A CN 202080078780A CN 114729648 A CN114729648 A CN 114729648A
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- China
- Prior art keywords
- diffuser
- flow path
- blower
- impeller
- scroll
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Links
- 238000005406 washing Methods 0.000 title claims description 45
- 238000004891 communication Methods 0.000 claims description 27
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 36
- 230000002093 peripheral effect Effects 0.000 description 14
- 238000011084 recovery Methods 0.000 description 14
- 238000001035 drying Methods 0.000 description 13
- 238000003780 insertion Methods 0.000 description 13
- 230000037431 insertion Effects 0.000 description 13
- 238000007791 dehumidification Methods 0.000 description 6
- 238000003756 stirring Methods 0.000 description 6
- 239000012530 fluid Substances 0.000 description 4
- 230000008602 contraction Effects 0.000 description 3
- 238000010981 drying operation Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000010438 heat treatment Methods 0.000 description 3
- 238000009434 installation Methods 0.000 description 3
- 230000007246 mechanism Effects 0.000 description 3
- 239000008237 rinsing water Substances 0.000 description 3
- 239000003795 chemical substances by application Substances 0.000 description 2
- 239000003599 detergent Substances 0.000 description 2
- 230000000149 penetrating effect Effects 0.000 description 2
- 229920005989 resin Polymers 0.000 description 2
- 239000011347 resin Substances 0.000 description 2
- 239000011358 absorbing material Substances 0.000 description 1
- 238000007664 blowing Methods 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000018044 dehydration Effects 0.000 description 1
- 238000006297 dehydration reaction Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000000452 restraining effect Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 238000009751 slip forming Methods 0.000 description 1
- 229920003002 synthetic resin Polymers 0.000 description 1
- 239000000057 synthetic resin Substances 0.000 description 1
- 239000008399 tap water Substances 0.000 description 1
- 235000020679 tap water Nutrition 0.000 description 1
- 210000005182 tip of the tongue Anatomy 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Images
Classifications
-
- 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
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Textile Engineering (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Detail Structures Of Washing Machines And Dryers (AREA)
Abstract
The disclosed device is provided with: an electric motor; a rotating shaft rotatably provided to the motor; a centrifugal impeller provided on the rotating shaft; a diffuser flow path (410) which is provided downstream of the centrifugal impeller (300) and is formed by blades arranged in the circumferential direction; and a swirl flow path (70) which is provided downstream of the diffuser flow path (410) on the side opposite to the axial direction with respect to the diffuser flow path (410). The length of the diffuser blade (401) changes in the direction (W) of rotation of the centrifugal impeller (300) with reference to the tongue end (71) of the swirl flow path (70).
Description
Technical Field
The present invention relates to a blower and a washing machine provided with the same.
Background
The blower rotates an impeller by a motor to form a flow of air. 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, and the kinetic energy of the air flowing in is converted into pressure energy to increase the pressure. In order to obtain a highly efficient blower, a stationary flow path that performs good pressure recovery is important. As an air blower having a stationary flow path, there is an air blower described in patent document 1. Patent document 1 describes a blower having a structure in which the rotation axis of the impeller and the center axis of the diffuser are different from each other.
Documents of the prior art
Patent document
Patent document 1: japanese patent laid-open publication No. 2014-202102
Disclosure of Invention
Problems to be solved by the invention
The blower described in patent document 1 is characterized in that the center axis of the diffuser is shifted from the rotation axis of the impeller in order to suppress a decrease in the pressure recovery rate, that is, a decrease in efficiency, due to the pressure distribution generated in the diffuser in the circumferential direction by the influence of the scroll provided downstream of the diffuser. Thus, the pressure recovery rate of the diffuser is changed in the circumferential direction and the pressure distribution caused by the scroll is offset, whereby the circumferential pressure distribution is made uniform and the efficiency is improved.
However, in the blower described in patent document 1, the maximum pressure recovery rate of the diffuser is substantially determined by the length of the diffuser blades that are uniform in the circumferential direction. In this case, when the blower is downsized, the length of the diffuser blades is also equally shortened in the circumferential direction, and the pressure recovery rate is lowered. Therefore, it is difficult to achieve miniaturization and high efficiency.
The present invention has been made to solve the above conventional problems, and an object thereof is to provide a blower that can achieve both miniaturization and high efficiency, and a washing machine including the blower.
Means for solving the problems
The present invention is characterized by comprising: an electric motor; a rotating shaft rotatably provided to the motor; an impeller provided on the rotating shaft; a diffuser flow path provided downstream of the impeller and including blades arranged in a circumferential direction; and a swirl flow path provided downstream of the diffuser flow path on the opposite side of the diffuser flow path in the axial direction of the rotary shaft, wherein the length of the vane changes with the rotation direction of the impeller with reference to a tongue portion of the swirl flow path.
Effects of the invention
According to the present invention, it is possible to provide a blower that can achieve both miniaturization and high efficiency, and a washing machine including the blower.
Drawings
Fig. 1 is a longitudinal sectional view showing a washing machine mounted with a blower according to a first embodiment.
Fig. 2 is an external perspective view showing the blower according to the first embodiment.
Fig. 3 is an exploded perspective view of the blower as viewed from the fan cover side.
Fig. 4 is an exploded perspective view of the blower as viewed from the motor side.
Fig. 5 is a plan view of a conventional diffuser.
Fig. 6 is a plan view of a blower mounted with a conventional diffuser.
Fig. 7 is a schematic view showing a communication path formed by a conventional diffuser.
Fig. 8 is a plan view of the diffuser of the first embodiment.
Fig. 9 is a plan view of a blower mounted with the diffuser of the first embodiment.
Fig. 10 is a schematic view showing a communication path formed by the diffuser of the first embodiment.
Fig. 11 is a perspective view of a blower mounted with the diffuser of the second embodiment.
Detailed Description
Hereinafter, embodiments for carrying out the present invention will be described in detail with reference to the drawings.
Fig. 1 is a vertical sectional view showing a washing machine mounted with a blower according to the present embodiment. In addition, although the vertical washing and drying machine will be described below as an example, the present invention can also be applied to a drum-type washing and drying machine in which a laundry loading and unloading opening is formed on the front surface side.
As shown in fig. 1, the washing machine S includes an outer frame 1 as a housing, an outer tub 2 for storing washing water, a spin tub 3, a drive motor 10, a blower 22, and the like. The outer tank 2 is built in the outer frame 1 and is supported by the outer frame 1 in a vibration-proof manner. The rotary tub 3 is a washing and dewatering tub for storing laundry such as washed and dried clothes, and is provided inside the outer tub 2. The rotary tub 3 is rotatably supported in the outer tub 2.
A stirring blade 4 for stirring and washing laundry is rotatably provided at the bottom of the rotary tub 3. The stirring blade 4 repeats normal rotation and reverse rotation operations during the washing operation and the drying operation. In addition, the stirring blades 4 rotate at high speed together with the rotary tub 3 during the dehydration operation, and dehydrate the moisture contained in the laundry in the rotary tub 3.
The drive motor 10 is provided in the outer frame 1 and rotationally drives the stirring blade 4 and the rotary tank 3. In addition, a DC brushless motor is used as the drive motor 10, for example. The DC brushless motor is performed by vector control. In the present embodiment, the stirring blade 4 and the rotary tub 3 are directly rotated by the driving motor 10, but may be driven by a belt or the like (not shown).
In addition, an outer cover 5 is provided on the upper portion of the outer frame 1. The outer lid 5 is openably and closably provided on a top cover 6 provided on the upper portion of the outer frame 1. An inner lid 34 is openably and closably provided on the upper portion of the outer tub 2. By opening the outer lid 5 and the inner lid 34, the laundry can be taken in and out of the rotary tub 3.
Further, a water supply unit 7 is provided on the back surface side of the top cover 6 in the outer frame 1. The water supply unit 7 has a water supply tank (not shown) having a plurality of water paths therein, and supplies tap water and bath water from the water supply hose connection port 8 to the outer tub 2. A detergent/finishing agent feeding device 35 is provided on the front side of the top cover 6. The detergent and the finishing agent are injected between the outer tub 2 and the rotary tub 3 through the input hose 36.
The washing machine S is provided with a drying mechanism 9. The drying mechanism 9 performs circulating air blowing and dehumidification of drying air for drying the laundry in the rotary tub 3. In addition, most of the drying mechanism 9 is occupied by a drying air circulation path. The drying air circulation path includes a bottom circulation path 20 communicating with the bottom of the outer tub 2, and a vertical dehumidification passage 21 extending upward from the bottom circulation path 20.
The suction side of the blower 22 is connected to the upper side of the vertical dehumidification passage 21. The discharge side of the blower 22 is connected to communicate with the return connection circulation path 25. Further, a dry filter 45 is disposed between the blower 22 and the vertical dehumidification passage 21, and foreign matter does not flow into the blower 22. The details of the blower 22 will be described later.
The return connection circulation path 25 includes an upper bellows 23, and is connected to the upper portion of the outer tub 2 so as to communicate with the upper portion via the upper bellows 23. The bottom circulation path 20 also has a lower bellows tube 26, and is connected to the bottom of the outer tub 2 so as to communicate with the bottom via the lower bellows tube 26.
The lower bellows 26 is connected to the bottom recess 31 of the outer tub 2. The bottom recess 31 communicates with the washing water discharge path 42 and the washing water circulation path 43 via the lower communication pipe 41. A drain valve 44 is provided in the wash water discharge path 42. A foreign matter removal trap 32 is provided in the washing water circulation water passage 43.
The drain valve 44 is closed during the washing operation and the drying operation. The drain valve 44 is opened when draining the washing water, and drains the washing water and the rinsing water accumulated in the outer tub 2 from the washing water drainage channel 42 to the outside (outside) of the washing machine S.
The washing water circulation water path 43 is connected to a washing water circulation water longitudinal water path 46. The washing water circulating water vertical water passage 46 rises along the outer surface of the outer tub 2, extends to the upper side of the rotary tub 3, and is connected to communicate with the washing lint removing device 33 provided on the upper side of the rotary tub 3.
The washing water and the rinsing water accumulated in the outer tub 2 are injected so as to flow in the washing water circulating water longitudinal water path 46 and be dispersed from the washing lint removing device 33 to the rotary tub 3. Since washing and rinsing are performed during the continuous water supply, washing and rinsing are performed with a small amount of water.
Washing machine S is further provided with a water level sensor 47 for detecting the water level of the washing water and the rinsing water accumulated in outer tub 2. An air trap 50 is provided near the bottom of the outer tub 2. An air pipe 49 is connected to communicate with the air trap 50. A water level sensor 47 is connected to the upper end of the air pipe 49 in a communicating manner. The water level sensor 47 detects the water level by sensing the water level fluctuation in the outer tub 2.
In the washing machine S, the centrifugal impeller 300 (see fig. 2) of the blower 22 rotates, so that the drying air flows through the rotary tub 3, and the laundry in the rotary tub 3 is dried. Further, the drying air in which moisture is condensed in the dehumidification region is reheated by the electric heater 24 (see fig. 3) of the blower 22 and flows in the rotary tub 3, so that moisture in the laundry is further evaporated. The laundry is dried by repeating this moisture removal in a circulation of the drying air.
Fig. 2 is an external perspective view showing the blower according to the first embodiment.
As shown in fig. 2, the blower 22 includes a fan cover 51, a fan case 52, a 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), the fan cover 51 of the blower 22 is disposed substantially downward in the outer frame 1 (see fig. 1), for example.
The fan cover 51 has an intake port 57 and an exhaust port 58. The suction port 57 is connected to the vertical dehumidification passage 21 (see fig. 1) via the dry 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 as viewed from the fan cover side.
As shown in fig. 3, the fan cover 51 has a shape elongated in one direction, and has an intake port 57 formed in one longitudinal direction and an exhaust port 58 formed in the other 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. The diameter of the discharge port 58 is larger than the diameter of the suction port 57. The suction port 57 and the discharge port 58 are formed to face in substantially the same direction.
The fan cover 51 has an annular projecting portion 51a projecting in the axial direction Ax around the suction port 57. The axial direction Ax refers to a direction in which the rotary shaft 101 of the motor 100 extends. In addition, the fan cover 51 has a substantially rectangular protrusion 51b formed at a position where the electric heater 24 is provided.
Further, screw fixing portions 91 to be fixed to the fan case 52 by screws are formed at a plurality of locations on the peripheral edge portion of the fan cover 51.
The fan case 52 has a shape corresponding to the fan cover 51. When the fan case 52 and the fan cover 51 are combined, a space in which the centrifugal impeller 300, the diffuser 400, and the electric heater 24 are arranged is formed between the fan cover 51 and the fan case 52.
Further, the fan housing 52 is formed with an introduction passage 72a that introduces air from the scroll passage 70 to the electric heater 24. The electric heater 24 includes a plurality of fins, and heats the air flowing out of the scroll passage 70 and passing through the introduction passage 72 a. The introduction passage 72a is configured such that the passage width is expanded toward the electric heater 24. Specifically, the introduction passage 72a is configured to extend to a width substantially equal to the width of the heating portion 24a of the electric heater 24. The introduction passage 72b (see fig. 4) of the fan cover 51 is also configured to have a flow path width that widens downstream, similarly to the introduction passage 72 a. By combining the fan housing 52 and the fan cover 51, an introduction passage 72 (see fig. 2) is formed along the shape of the rectangular heating portion 24a of the electric heater 24.
The fan case 52 has a concave flow path 77 communicating with the discharge port 58 of the fan cover 51 formed downstream of the electric heater 24. The flow path 77 is inclined upward toward the discharge port 58.
In addition, the fan housing 52 has a shape that protrudes in the width direction so that a position deviated from the heating portion of the electric heater 24 does not interfere with the air flow.
Further, a shaft insertion hole 80 into which a rotary shaft 101 of the motor 100 is inserted is formed in the center of the scroll passage 70 in the fan case 52. Further, 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 at the outer peripheral edge portion of the fan case 52.
Further, in fan case 52, screw holes 93 for fixing diffuser 400 to fan case 52 are formed at a plurality of locations (4 in the present embodiment) between shaft insertion hole 80 and scroll flow path 70. These screw holes 93 are formed so as to surround the shaft insertion hole 80. Fan case 52 has circular recess 93a formed in the periphery of screw hole 93.
Further, fan case 52 is formed with fan case recess 94 (concave groove portion) on the radial outer peripheral side of screw hole 93. The fan case recess 94 is formed in an annular shape.
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 at 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 housing 52. In addition, the bottom plate 400a has screw insertion holes 430 formed at a plurality of locations around the through hole 400b, through which screws (not shown) for fixing the diffuser 400 to the fan case 52 are inserted. The screw insertion holes 430 are formed at positions corresponding to (facing) the screw holes 93 of the fan case 52.
In the diffuser 400, a recessed portion 430a is formed at the periphery of the screw insertion hole 430 so that the head of a screw (not shown) does not protrude from the surface (upper surface) of the bottom plate 400 a. Thus, when the centrifugal impeller 300 rotates, the centrifugal impeller 300 does not contact a screw (not shown) while reducing the distance between the bottom plate 400a and the centrifugal impeller 300.
A diffuser outer bottom surface portion (base portion) 400c formed higher than the bottom plate 400a in the axial direction Ax is formed on the entire outer peripheral edge portion of the bottom plate 400 a. On the upper surface (the surface on the fan cover 51 side) of the diffuser outer bottom surface portion 400c in the axial direction Ax, diffuser blades 401 (blades) are formed at equal intervals in the circumferential direction.
Fig. 4 is an exploded perspective view of the blower as viewed from the motor side.
As shown in fig. 4, a bell mouth portion 57a is formed at the suction port 57 of the fan cover 51. The fan cover 51 has a recess 51c formed around the bell-mouth portion 57a to accommodate an annular seal member (not shown). The fan cover 51 is provided with an annular restraining member (not shown) for holding a sealing member (not shown) in the recess 51 c. The suppressing member (not shown) is formed around the recess 51c and is placed on the annular recess 51d one step higher (shallower) than the recess 51 c. The suppressing member (not shown) is fixed via a fixing portion 51e formed around the recess 51 d.
Further, the fan cover 51 is provided with an elastic member 90 formed in an annular shape. Fig. 4 shows a state in which the elastic member 90 is attached to the fan cover 51. The elastic member 90 is disposed at a position facing the tip (upper end) of the diffuser vane 401.
The fan cover 51 is formed with an introduction passage 72b extending from the scroll passage 70 (see fig. 3) toward the electric heater 24. The introduction passage 72b is formed along the introduction passage 72a (see fig. 3). The introduction passage 72b is configured such that the depth dimension H (passage height) of the passage is increased (higher) from the scroll passage 70 (see fig. 3) side to the electric heater 24.
The scroll flow path 70 of the fan case 52 is configured to expand toward the side where the motor 100 is provided (motor installation side). The scroll passage 70 is configured such that the passage depth (depth in the axial direction Ax) gradually increases from the passage on the tongue end portion 71 (see fig. 3) side toward the introduction passage 72a (see fig. 3). The introduction passage 72a is configured such that the passage depth is substantially constant toward the electric heater 24. The flow path 77 on the downstream side of the electric heater 24 is configured to be raised toward the fan cover 51.
Further, screw bosses 78 for fixing the motor 100 to the fan case 52 are formed at a plurality of locations (4 in the present embodiment) on the fan case 52.
The diffuser 400 has a convex portion 440 formed on the side (back side) opposite to the side on which the diffuser vane 401 is provided. The ridge 440 is fitted in the fan case recess 94 (see fig. 3) of the fan case 52.
In addition, in the screw insertion hole 430 of the diffuser 400, a protrusion 430b that is fitted in a concave portion 93a (see fig. 3) of the fan case 52 is formed. Each protrusion 430b is fitted into a recess 93a corresponding to the fan case 52.
Further, screw insertion holes 430 of diffuser 400 and screw holes 93 of fan case 52 are fixed by screws (not shown). A rotary shaft 101 (see fig. 3) of the motor 100 is inserted through the shaft insertion hole 80 of the fan housing 52. The rotary shaft 101 is inserted through 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 case 52 are coupled to each other by screws (not shown) inserted through the screw insertion portions 92 and fixed to the screw fixing portions 91. Thus, the blower 22 forms a housing portion 61 (see fig. 2) in which the centrifugal impeller 300 and the diffuser 400 are disposed and a heater portion 62 (see fig. 2) in which the electric heater 24 is disposed. A boundary surface of a connection space between the case 61 and the heater 62 is defined as a case discharge port 59 (see fig. 3).
Further, the inner diameter end of the vane 321 of the centrifugal impeller 300 is positioned radially outward of the suction opening 302 (see fig. 3). Further, the centrifugal impeller 300 is configured such that the outer diameter end of the blade 321 substantially coincides with the outer peripheral edge of the shroud plate 301 and the outer peripheral edge of the hub plate 311.
In the first embodiment, the closed centrifugal impeller 300 having the shroud plate 301 is described as an example, but an open centrifugal impeller in which the hub plate 311 and the blades 321 are integrally molded with resin may be used. This reduces the number of components and reduces the cost. Further, by using a resin type, it is possible to easily make a three-dimensional structure and to achieve high efficiency. The three-dimensional structure is formed by further twisting the blade. This can further improve efficiency.
In the first embodiment, a turbofan having backward blades is described as an example, but a sirocco fan having forward blades may be applied. The shape of the impeller is not limited to a centrifugal type, and may be a diagonal flow type. By providing the diagonal flow pattern, the outer diameter of the impeller can be reduced, and the fan 22 can be reduced in size.
Next, a blower including 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 mounted with a conventional diffuser. Fig. 7 is a schematic view showing a communication path formed by a conventional diffuser.
As shown in fig. 5, the diffuser 1400 is configured such that a plurality of diffuser blades 1401 are arranged at equal intervals in the circumferential direction on the entire circumference of the bottom plate 1400 a. The diffuser vane 1401 is formed to stand in the axial direction Ax (see fig. 3 and 4) with respect to a diffuser outer bottom surface portion 1400c formed around the bottom plate 1400 a. The diffuser blades 1401 are located outside the outer peripheral edge of the centrifugal impeller 300 (see fig. 3 and 4).
The diffuser vane 1401 is formed in a thin plate shape and extends in the circumferential direction in a plan view. The diffuser vane 1401 is configured such that the trailing edge 1402 (the other end) is positioned radially outward of the leading edge 1412 (the one end). In addition, in the diffuser vane 1401A (1401), the leading edge 1412 of the diffuser vane 1401B (1401) adjacent in the circumferential direction is located substantially at the center in the circumferential direction and radially inward 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 in the circumferential direction is located substantially at the center in the circumferential direction and radially outward of the diffuser vane 1401B. Further, a diffuser flow channel 1410, which will be described later, is formed between the adjacent diffuser vanes 1401A and 1401B. The diffuser flow channel 1410 is configured to have a radial width gradually increasing from the leading edge 1412 side toward the trailing edge 1402 side.
The diffuser vane 1401A (1401) has a cut-out portion 1404 formed so that the outer peripheral edge of the diffuser outer bottom surface portion 1400c extends substantially perpendicularly from the trailing edge 1402 to the pressure surface 1403 of the adjacent diffuser vane 1401B. The pressure surface 1403 is an entire surface from the leading edge 1412 to the trailing edge 1402 of the diffuser blade 1401 facing the radially outer side. By forming the cut-out portion 1404, a substantially triangular cut-out portion 1405 penetrating in the axial direction Ax (see fig. 3 and 4) is formed in the outer peripheral edge portion of the diffuser outer bottom surface portion 1400 c. In other words, the outer circumferential edge of the diffuser 1400 is formed in a zigzag shape along the circumferential direction.
As shown in fig. 6, when the diffuser 1400 is attached to the fan casing 52, the substantially triangular communication passage 1420 formed by the fan casing 52, the diffuser blades 1401, and the cut-outs 1404 is formed. Further, on the outer periphery of the diffuser 1400 in the radial direction, substantially triangular communication passages 1420 are formed in a row in the circumferential direction. The upstream side of the communication passage 1420 communicates with a diffuser flow passage 1410 surrounded by the adjacent diffuser blades 1401 and 1401, the diffuser outer bottom surface portion 1400c, and the fan cover 51 (see fig. 3 and 4). When the centrifugal impeller 300 rotates in the W direction, air (fluid) is discharged from the outer periphery of the centrifugal impeller 300.
The discharged air flows into the substantially triangular communication passage 1420 through the diffuser passage 1410 (see the arrow), and flows into the scroll passage 70 (the back side in the direction perpendicular to the paper surface of fig. 6) provided on the back surface side of the diffuser 1400.
The air flowing through the scroll passage 70 is discharged to the discharge portion 76 through the scroll portion 75. Then, the air having passed through the discharge portion 76 is introduced into the introduction passage 72 through the housing discharge port 59. The discharge portion 76 means the scroll flow path 70 from the point B to the casing discharge port 59.
As shown in fig. 7, in the conventional blower including the diffuser 1400, the distance S100 between the trailing edge 1402 and the radially outer wall surface 74 increases in the rotation direction W of the centrifugal impeller 300 because the outer diameter of the trailing edge 1402 of the diffuser vane 1401 is constant regardless of whether the cross-sectional area of the communication passage 1420 is constant. Accordingly, the flow of air passing through the diffuser flow channel 1410 between the trailing edge 1402 of the diffuser vane 1401 and the radially outer wall surface 74 of the fan casing 52 is not restricted by the radially outer wall surface 74, and therefore a high pressure recovery rate cannot be obtained in this region (gap at the distance S100).
In order to obtain pressure recovery more efficiently under the constraints of installing such a blower, it is very important to design the blower to extend the length of the diffuser vane 1401 as much as possible and to increase the pressure recovery rate in the diffuser 1400. In this case, the flow path cross-sectional area of the communication passage 1420 for guiding the flow from the outlet of the diffuser flow path 1410 to the scroll flow path 70 also needs to be changed in the circumferential direction (in the rotation direction W). This is to suppress pressure loss accompanying rapid contraction and expansion when passing through the communication passage 1420.
Next, the structure of the blower 22 of the first embodiment will be described with reference to fig. 8 to 10. Fig. 8 is a plan view of the diffuser of the first embodiment. Fig. 9 is a plan view showing the blower on which the diffuser of the first embodiment is mounted with the fan cover removed. Fig. 10 is a schematic view showing a communication path formed by the diffuser of the first embodiment. The shape of the diffuser 400 described below is an example, and is not limited to the first embodiment.
As shown in fig. 8, the blower 22 (see fig. 3 and 4) of the first embodiment includes a diffuser 400 instead of the diffuser 1400 of the conventional example (see fig. 5 and 7). The lengths of the diffuser blades 401 of the diffuser 400 are different in the circumferential direction. More specifically, the positions of the leading edges 412 of the diffuser blades 401 are the same in the circumferential direction, but the positions of the trailing edges 402 are different in the radial direction.
In the diffuser 400, in a region (90 ° range) indicated by reference numeral R1, a plurality of diffuser blades 401 are arranged at equal intervals in the circumferential direction around the bottom plate 400a, as in the conventional example. The reference position (position of 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 is formed so as to stand in the direction of the axial direction Ax (see fig. 3 and 4) (the direction of 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 400 a. The diffuser vane 401 is located outside the outer peripheral edge of the centrifugal impeller 300 (see fig. 3 and 4).
The diffuser vane 401 is formed in a thin plate shape and extends in the circumferential direction in a plan view. The trailing edge 402 (the other end or the end on the outer diameter side) of the diffuser vane 401 is located radially outward of the leading edge 412 (the one end or the end on the inner diameter side). In the diffuser vane 401A (401) of the region R1, the leading edge 412 of the diffuser vane 401B (401) adjacent in the circumferential direction is located substantially at the center in the circumferential direction and radially inward of the diffuser vane 401A. In other words, in the diffuser vane 401B (401), the trailing edge 402 of the diffuser vane 401A (401) adjacent in the circumferential direction is located substantially at the center in the circumferential direction and radially outward of the diffuser vane 401B. Further, a diffuser flow path 410, which will be described later, is formed between the adjacent diffuser blades 401A, 401B. The diffuser flow path 410 is configured to have a radial width gradually increasing from the leading edge 412 side toward the trailing edge 402 side.
Further, the diffuser vane 401A (401) has a cut-out portion 404 formed so that the outer peripheral edge of the diffuser outer bottom surface portion 400c extends substantially perpendicularly from the trailing edge 402 to the pressure surface 403 of the adjacent diffuser vane 401B. The pressure surface 403 is an entire surface extending from the radially outward leading edge 412 to the trailing edge 402 of the diffuser vane 401. By forming such a cut portion 404, a substantially triangular cut portion 405 penetrating in the axial direction Ax is formed on the outer peripheral edge portion of the diffuser outer side bottom surface portion 400 c. In other words, the outer peripheral edge portion of the diffuser 400 in the region R1 is formed in a zigzag shape along the circumferential direction.
In addition, as with the reference symbol R1, diffuser vanes 401 having the same circumferential length are arranged at equal intervals in the circumferential direction (the rotational direction W) in the diffuser 400 in the region R2 (the 90 ° range).
In addition, the diffuser 400 in the region R3 (the range of 90 °) is configured such that the diffuser vanes 401 become longer as they go toward the rotation direction W. Specifically, the diffuser vane 401D is formed longer than the adjacent diffuser vane 401C in the rotational direction W. The diffuser blade 401E is formed longer than the adjacent diffuser blade 401D in the rotational direction W. The diffuser vane 401F is formed longer in the rotational direction W than the adjacent diffuser vane 401E. The diffuser vane 401G is formed longer in the rotation direction W than the adjacent diffuser vane 401F. The diffuser vane 401H is formed longer in the rotation direction W than the adjacent diffuser vane 401G.
In addition, the diffuser 400 in a part of the region R4 (the range of 90 °) is configured such that the diffuser blades 401 become longer toward the rotation direction W. Specifically, the diffuser vane 401J is formed longer than the adjacent diffuser vane 401I in the rotational direction W. The diffuser vane 401K is formed longer than the adjacent diffuser vane 401J in the rotation direction W. The diffuser blade 401L is formed longer in the rotation direction W than the adjacent diffuser blade 401K.
In addition, the diffuser 400 in the other portion in the region R4 (the range of 90 °) is configured such that the diffuser blades 401 become shorter toward the rotation direction W. Specifically, the diffuser blade 401M is formed shorter than the adjacent diffuser blade 401L in the rotational direction W. The diffuser vane 401N is formed to have the same length as the adjacent diffuser vane 401M in the rotation direction W. The diffuser blades 401M and 401N are formed longer in the rotation direction W than the diffuser blades 401 in the region indicated by the symbol R1.
In the diffuser 400, in the region R4, the diffuser outer bottom surface portion 400c is formed to extend to the trailing edge 402 of the diffuser blades 401J, 401K, 401L. Further, the diffuser 400 extends to a position radially outward of the trailing edge 402 of the diffuser blade 401M in the region R4. In this way, in the diffuser 400, in the region R4, the diffuser outer bottom surface portion 400c has an arc portion 400c1 formed in a substantially arc shape from the diffuser blades 401J, 401K, 401L, 401M, 401N. In other words, the diffuser 400 has a shape (the shape other than the zigzag shape described above) in which the communication paths 420 described above are not formed in a part of the region R4.
As shown in fig. 9, when the diffuser 400 is mounted on the fan case 52, the leading end (trailing edge 402) of the diffuser blade 401N abuts on the tongue end portion 71. 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).
In the first embodiment, the diffuser vane 401 has a circumferential length that is longer in the rotation direction W of the centrifugal impeller 300 from the position of the tongue end 71 of the scroll passage 70. Specifically, in the first embodiment, when the position P1 between the tip end of the coupling tongue end portion 71 and the rotation center O of the centrifugal impeller 300 is set as the reference (0 °), the position rotated 90 ° in the rotation direction W from the reference position P1 is set as P2, the position rotated 180 ° in the rotation direction W from the reference position P1 is set as P3, and the position rotated 270 ° in the rotation direction W from the reference position P1 is set as P4. The region from the position P1 to the position P2 corresponds to the region R1 described above. The range from the position P2 to the position P3 corresponds to the region R2 described above. The range from the position P3 to the position P4 corresponds to the region R3 described above. The range from the position P4 to the position P1 corresponds to the region R4 described above.
In this way, in the first embodiment, the diffuser blades 401 having the same length in the rotational direction W are arranged between 0 ° and 180 ° (regions R1 and R2 in fig. 8), and the length of the diffuser blades 401 is gradually increased in the rotational direction W between 180 ° and 270 ° (region R3 in fig. 8). In the first embodiment, the length of the diffuser vane 401 is gradually increased toward the rotation direction W in a part of the range from 270 ° to 360 ° (0 °) (region R4 in fig. 8). In addition, in the first embodiment, in the range between 270 ° and 360 ° (0 °) (the region R4 of fig. 8), the length of the diffuser vane 401 becomes shorter in another portion (the remaining portion) toward the rotational direction W.
In addition, in the first embodiment, the lengths in the circumferential direction of the diffuser vanes 401 are formed to be the same at the position P1 of 0 ° and the position P2 of 90 °. In addition, the circumferential lengths of the diffuser vanes 401 are formed to be the same at the position P2 of 90 ° and the position P3 of 180 °. The diffuser vane 401 at the positions P3 and P4 and P4 of 270 ° is formed longer than the diffuser vane 401 at the position P3 of 180 °.
In the first embodiment, the diffuser vane 401 is formed to be 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 (see fig. 3 and 4) according to the first embodiment is particularly effective when the radially outer wall surface 74 (see fig. 9) of the fan casing 52 changes in the circumferential direction. In addition, when the installation space for installing the blower 22 (see fig. 3 and 4) into the product is limited as in the washing machine S (see fig. 1), the radial outer wall surface 74 of the fan case 52 cannot secure a circular shape.
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 path 420 needs to be. That is, the flow path cross-sectional area of the communication path 420 is increased in the circumferential direction (the rotational direction W) so as to correspond to the diffuser vane 401 which is elongated in the circumferential direction (the rotational direction W).
In this case, the trailing edge 402 of the diffuser vane 401 may be in contact with or separated from the radially outer wall surface 74 of the swirling flow path 70. The diffuser vane 401 can be further lengthened for the contact side, resulting in higher efficiency. However, since it is often difficult to touch the touch panel from the viewpoint of product assembly, a structure in which a gap of about several mm is provided may be adopted. When such a gap is provided, a gap width S1 (see fig. 9) between the trailing edge 402 of the diffuser vane 401 and the radially outer wall surface 74 is preferably constant in the circumferential direction.
When the fluid flows from the diffuser flow path 410 to the inlet passage 72 (see fig. 9) through the communication path 420 and the scroll flow path 70, the pressure recovery rate of the fluid flowing directly into the inlet passage 72 is increased at a portion (see region R4a in fig. 9) where the fluid can flow directly into the inlet passage 72 without passing through the communication path 420 from the diffuser flow path 410, and the efficiency is increased. In other words, the diffuser 400 is provided with a diffuser flow path 410A (see fig. 9) having no communication path 420 in a region R4a that can be directly connected to the introduction path 72 in the diffuser flow path 410. Thus, the flow of the air passing through the diffuser flow path 410A is guided directly to the introduction path 72 without turning from the radial direction to the axial direction Ax. As a result, the pressure loss associated with the turning of the air flow can be suppressed, and the efficiency of the blower 22 can be increased.
As described above, the blower 22 of the first embodiment includes the motor 100, the rotary shaft 101 rotatably provided to the motor 100, the centrifugal impeller 300 provided to the rotary shaft 101, the diffuser flow path 410 provided downstream of the centrifugal impeller 300 and including the diffuser blades 401 arranged in the circumferential direction, and the scroll flow path 70 provided downstream of the diffuser flow path 410 on the opposite side of the diffuser flow path 410 from the axial direction Ax. The circumferential length of the diffuser vane 401 changes in the rotation direction W of the centrifugal impeller 300 with reference to the tongue end portion 71 of the scroll passage 70 (see fig. 9). That is, in the region R3, the diffuser vane 401 is formed to be longer toward the rotation direction W. In addition, in a part of the region R4, the diffuser vane 401 is formed to be longer toward the rotation direction W. Accordingly, when the radially 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 flow of air passing through the diffuser flow path 410 can be restricted, and a high pressure recovery rate can be obtained. As a result, even when the scroll flow path 70 is disposed on the opposite side of the diffuser vane 401 from the axial direction Ax to reduce the size of the blower 22, the efficiency of the blower 22 can be increased.
In the first embodiment, the length of the diffuser vane 401 in the circumferential direction is increased in the rotation direction W of the centrifugal impeller 300 with the tongue end portion 71 as a reference position (see fig. 9). Accordingly, in the 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 restricted, and a high pressure recovery rate can be obtained.
In the first embodiment, the cross-sectional area of the communication passage 420 connecting the diffuser flow passage 410 and the scroll flow passage 70 changes in the rotation direction W of the centrifugal impeller 300 (see fig. 10). This can suppress pressure loss associated with rapid contraction and expansion when passing through the communication passage 420, and can further increase the efficiency of the blower 22.
In the first embodiment, the cross-sectional area of the communication passage 420 connecting the diffuser flow passage 410 and the scroll flow passage 70 is increased in the rotation direction W of the centrifugal impeller 300 (see fig. 10). Accordingly, in the shape in which the scroll flow path 70 expands in the rotation direction W, the pressure loss associated with rapid contraction and expansion when passing through the communication path 420 can be suppressed, and further high efficiency of the blower 22 can be achieved.
In the first embodiment, a diffuser flow path 410A (see fig. 9) not having a communication path 420 connecting the diffuser flow path 410 and the scroll flow path 70 is present at the outlet of the scroll flow path 70. Thus, the flow of the air passing through the diffuser flow path 410 is guided directly to the introduction path 72 without turning from the radial direction to the axial direction. As a result, the pressure loss associated with the turning of the air flow can be suppressed, and the efficiency of the blower 22 can be increased.
The first embodiment further includes a motor 100, a rotary shaft 101 rotatably provided to the motor 100, a centrifugal impeller 300 provided to the rotary shaft 101, a diffuser passage 410 provided downstream of the centrifugal impeller 300 and including diffuser blades 401 arranged in the circumferential direction, and a scroll passage 70 provided downstream of the diffuser passage 410 on the opposite side of the diffuser passage 410 from the axial direction Ax. When the straight line connecting the rotation center O of the centrifugal impeller 300 and the tongue end portion 71 of the scroll flow path 70 is set to 0 °, the length L (see fig. 8) of the diffuser vane 401 is positive in the rotation direction W of the centrifugal impeller 300, and the 270 ° position P4 is different from the 90 ° positions P2 and P3 of 180 ° (the 90 ° position, the 180 ° position, and at least 1 of the 270 ° positions are different). Accordingly, when the radially 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 flow of air passing through the diffuser flow path 410 can be restricted, and a high pressure recovery rate can be obtained. As a result, even when the blower 22 is downsized by disposing the scroll flow path 70 on the opposite side of the diffuser vane 401 from the axial direction Ax, the blower 22 can be made more efficient.
In the first embodiment, the length L (see fig. 8) of the diffuser vane 401 satisfies the relationship of the position P4 where the position P2 at 0 ° P1 is 90 ° is 180 ° and the position P3 < 270 °. Accordingly, in the 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 restricted, and a high pressure recovery rate can be obtained.
(second embodiment)
Fig. 11 is a perspective view of a blower mounted with the diffuser of the second embodiment. Fig. 11 shows a state where 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 400A includes a diffuser outer extended bottom surface portion 400d formed by extending the diffuser outer bottom surface portion 400c to the introduction passage 72 on the outer diameter side of the discharge portion 76, in addition to the structure in which the diffuser outer bottom surface portion 400c is close to the radially outer wall surface 74 of the scroll flow path 70. The diffuser outer extended bottom surface portion 400d is formed so as to be close to a wall surface 74a formed to extend continuously from the discharge portion 76 toward the introduction passage 72 and to the radially outer wall surface 74, and is formed so as to be close to a wall surface 74b extending from the tongue end portion 71 toward the introduction passage 72 and to face the wall surface 74 a.
Thus, the diffuser outer extended bottom portion 400d functions as some kind of guide vane in the introduction passage 72, and pressure recovery can be performed more efficiently also in the introduction passage 72. In particular, when the installation space of the blower 22 is limited as in the case of the washing machine S, the rate of change in the flow path cross-sectional area from the housing discharge port 59 to the outlet of the introduction path 72 tends to be large. This causes the flow in the introduction passage 72 to separate from the wall surface, thereby increasing the pressure loss. In order to prevent this pressure loss, the control of the flow by extending the diffuser outer extended bottom surface portion 400d to the introduction passage 72 is effective in terms of high efficiency.
The diffuser outer-side extended bottom surface portion 400d includes a diffuser vane extension 406 that extends a portion of the diffuser vane 401 to the inlet passage 72 on the further outer diameter side of the discharge portion 76. The diffuser vane extension 406 is formed to an edge (end) of the diffuser outer side extended bottom surface portion 400d on the side of the introduction passage 72. By additionally providing such a diffuser vane extension 406, a higher flow straightening effect can be obtained.
The diffuser outer extended bottom surface portion 400d includes guide vanes 407 continuously formed from the inside of the scroll passage 70 to the inlet passage 72 via the discharge portion 76 on the scroll passage 70 side of the rear surface. The addition of the guide vane 407 is also effective in obtaining a high flow straightening effect.
In the first and second embodiments, the blower 22 is provided in the washing machine S (see fig. 1). This provides good mountability, and can reduce the input power to the blower 22 during the drying operation, thereby providing the washing machine S with suppressed power consumption. Further, since the size can be reduced in the radial direction, when the air blower 22 of the first and second embodiments is mounted on a washing machine having the same housing, a sound absorbing material or the like can be provided in an empty space in the radial direction, and noise reduction of the washing machine can be achieved.
The present invention is not limited to the above-described embodiments, and includes various modifications. For example, in the above-described embodiment, the case where the circumferential length of the diffuser vane 401 is increased in the rotational direction W has been described as an example, but a configuration may be provided in which the circumferential length of the diffuser vane 401 is decreased in the rotational direction W.
In the second embodiment, the case where 1 diffuser blade extension portion 406 is provided has been described as an example, but a plurality of diffuser blade extension portions may be provided.
In the second embodiment, the case where 1 guide vane 407 is provided has been described as an example, but a plurality of guide vanes may be provided.
Further, the diffuser vane 401 at the position P2 of 90 ° may have a longer circumferential length than the diffuser vane 401 at the position P1 of 0 °. Further, the diffuser vane 401 at the position P3 of 180 ° may have a longer circumferential length than the diffuser vane 401 at the position P2 of 90 °.
Description of the symbols
1-outer frame, 2-outer tank, 3-rotation tank, 22-blower, 51-fan cover, 52-fan housing, 57-suction inlet, 59-housing discharge outlet (outlet portion of scroll flow path), 61-housing portion, 70-scroll flow path, 71-tongue end portion (tongue), 72a, 72 b-introduction path, 74-radial outer side wall surface, 75-scroll portion, 76-discharge portion, 90-elastic member, 100-motor, 101-rotation shaft, 300-centrifugal impeller (impeller), 400A-diffuser, 400 c-diffuser outer side bottom surface portion, 400 d-diffuser outer side long bottom surface portion, 401A-diffuser blade (vane), 402-trailing edge, 406-diffuser blade extension (vane extension), 407-guide vane, 410-diffuser flow path, 412-leading edge, 420-communication path, Ax-axial direction, P1-0 degree position, p2-90 °, P3-180 °, P4-270 °, S-washing machine, W-direction of rotation.
Claims (11)
1. A blower is characterized by comprising:
an electric motor;
a rotating shaft rotatably provided to the motor;
an impeller provided on the rotating shaft;
a diffuser flow path provided downstream of the impeller and including blades arranged in a circumferential direction; and
a swirl flow path provided downstream of the diffuser flow path on a side opposite to the axial direction of the rotary shaft with respect to the diffuser flow path,
the length of the vane changes in the direction of rotation of the impeller with reference to the tongue of the scroll flow path.
2. The blower according to claim 1,
with the tongue portion as a reference position, the circumferential length of the blade is increased in the direction of rotation of the impeller.
3. A blower is characterized by comprising:
an electric motor;
a rotating shaft rotatably provided to the motor;
an impeller provided on the rotating shaft;
a diffuser flow path provided downstream of the impeller and including blades arranged in a circumferential direction; and
a swirl flow path provided downstream of the diffuser flow path on a side opposite to the axial direction of the rotary shaft with respect to the diffuser flow path,
when a straight line connecting the rotation center of the impeller and the tongue portion of the scroll flow path is set to 0 °, the length of the vane is positive in the rotation direction of the impeller, and is different at least one of a 90 ° position, a 180 ° position, and a 270 ° position.
4. The blower according to claim 3,
the length of the blade satisfies the relationship of the position of less than or equal to 180 degrees and less than 270 degrees, wherein the position of less than or equal to 90 degrees is the position of 0 degrees.
5. The blower according to claim 1 or 3,
the cross-sectional area of a communication passage connecting the diffuser flow path and the scroll flow path changes in the rotation direction of the impeller.
6. The blower according to claim 5,
the cross-sectional area of a communication passage connecting the diffuser flow path and the scroll flow path increases in a rotation direction of the impeller.
7. The blower according to claim 1 or 3,
at least one diffuser flow path is present at the outlet of the scroll flow path, the diffuser flow path having no communication path connecting the diffuser flow path and the scroll flow path.
8. The blower according to claim 1 or 3,
the hub wall surface forming the diffuser flow path is formed to extend outward beyond the outlet portion of the scroll flow path.
9. The blower according to claim 8,
a blade extension portion for extending the blade is formed on the hub wall surface.
10. The blower according to claim 8,
guide vanes are formed on the hub wall surface on the surface opposite to the vanes from the scroll flow path toward the outside of the outlet portion.
11. A washing machine is characterized in that a washing machine is provided,
a blower according to claim 1 or 3.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2019213939A JP7452989B2 (en) | 2019-11-27 | 2019-11-27 | Blower and washing machine |
| JP2019-213939 | 2019-11-27 | ||
| PCT/JP2020/034439 WO2021106317A1 (en) | 2019-11-27 | 2020-09-11 | Blower and washing machine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN114729648A true CN114729648A (en) | 2022-07-08 |
Family
ID=76087149
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202080078780.5A Pending CN114729648A (en) | 2019-11-27 | 2020-09-11 | Blower and washing machine |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP7452989B2 (en) |
| CN (1) | CN114729648A (en) |
| WO (1) | WO2021106317A1 (en) |
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| JP2018080653A (en) * | 2016-11-17 | 2018-05-24 | 株式会社日立製作所 | Fluid machinery |
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| JP2019167871A (en) * | 2018-03-23 | 2019-10-03 | 株式会社Ihi | Vaned diffuser and centrifugal compressor |
| CN110552899A (en) * | 2019-08-21 | 2019-12-10 | 天津大学 | multi-wing centrifugal fan for ventilator with built-in guide vanes |
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- 2019-11-27 JP JP2019213939A patent/JP7452989B2/en active Active
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- 2020-09-11 WO PCT/JP2020/034439 patent/WO2021106317A1/en active Application Filing
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| JP2007002769A (en) * | 2005-06-24 | 2007-01-11 | Hitachi Appliances Inc | Electric blower and electric vacuum cleaner equipped with the same |
| CN101298871A (en) * | 2008-05-15 | 2008-11-05 | 寿光市康跃增压器有限公司 | Rotary vane type air compressor with blade to enlarge pressure |
| US20130133156A1 (en) * | 2011-01-05 | 2013-05-30 | Panasonic Corporation | Electric blower and electric cleaner with same |
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Also Published As
| Publication number | Publication date |
|---|---|
| WO2021106317A1 (en) | 2021-06-03 |
| JP7452989B2 (en) | 2024-03-19 |
| JP2021085347A (en) | 2021-06-03 |
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