TWI468597B - Electric blower and vacuum cleaner equipped with electric blower - Google Patents
Electric blower and vacuum cleaner equipped with electric blower Download PDFInfo
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Description
本發明是關於電動送風機及搭載該電動送風機的吸塵器。The present invention relates to an electric blower and a vacuum cleaner equipped with the electric blower.
就以往的吸塵器用的電動送風機而言，例如也揭示於專利文獻1，電動送風機是具備：電動機；與該電動機之旋轉軸同軸的離心葉輪；在電動機與離心葉輪之間，在離心葉輪側具有擴散器葉片，在離心葉輪的相反側具有回流導片的擴散器；以及內含離心葉輪及擴散器的風扇外殼，擴散器，是構成在與風扇外殼之間具有「成為從擴散器葉片側到回流導片側之流路」的間隙，並且在將擴散器葉片側及回流導片側區隔開來的隔板形成有流路，該流路是從擴散器葉片之外周端沿著該擴散器葉片之外周側之面朝內部切入，其終端成為與相鄰的擴散器葉片之外周端一致的凹部。An electric blower for a conventional vacuum cleaner is disclosed, for example, in Patent Document 1, which includes an electric motor, a centrifugal impeller coaxial with a rotating shaft of the electric motor, and a centrifugal impeller side between the electric motor and the centrifugal impeller. a diffuser vane having a diffuser guide on the opposite side of the centrifugal impeller; and a fan casing containing a centrifugal impeller and a diffuser, the diffuser being formed between the fan casing and the "from the diffuser vane side to a gap of the flow path on the side of the return guide, and a partition that partitions the diffuser vane side and the return vane side area is formed with a flow path from the outer peripheral end of the diffuser vane along the diffuser vane The outer peripheral side is cut inwardly, and the end thereof becomes a concave portion that coincides with the outer peripheral end of the adjacent diffuser vanes.
又，習知擴散器的構成例如揭示於以下的非專利文獻1。習知擴散器是厚型葉片的擴散器，葉片之重疊長度L記載為入口寬度(氣流在平面內看到的寬度)a的四倍(在該情況，大約面積比b/a=1.6(b是葉片的重疊出口的出口寬度)、擴散角=8.5°)。Moreover, the configuration of the conventional diffuser is disclosed, for example, in Non-Patent Document 1 below. Conventional diffusers are diffusers of thick blades, and the overlap length L of the blades is described as four times the inlet width (the width seen by the airflow in the plane) a (in this case, the area ratio b/a = 1.6 (b) It is the exit width of the overlapping outlet of the blade), the diffusion angle = 8.5°).
[先行技術文獻][Advanced technical literature]
[專利文獻][Patent Literature]
[專利文獻1]日本專利第3758050號公報(日本特開平9-119396號公報)[Patent Document 1] Japanese Patent No. 3758050 (Japanese Laid-Open Patent Publication No. Hei 9-119396)
[非專利文獻][Non-patent literature]
[非專利文獻1]日刊工業新聞社發行渦輪流體機械與擴散器(日本昭和58年9月30日發行)[Non-Patent Document 1] The Nikkan Kogyo Shimbun issues a turbo fluid machine and a diffuser (issued on September 30, 2015 in Japan)
習知擴散器是厚型葉片的擴散器，若著眼於形狀上，則葉片的最大厚度會是在重疊部(L的範圍)的外徑側。這種厚型葉片擴散器如果在擴散器下游具有理想的流路(例如，無葉片擴散器或渦形殼)，可提高擴散器內部的靜壓回復量。然而，本發明之對象的電動送風機是在擴散器下游具有電動機，用以供應氣流使電動機冷卻。因此，存在有由風扇外殼、擴散器葉片及隔板所構成的彎曲流路。若將非專利文獻1所記載的厚型葉片擴散器適用在這種電動送風機，由於葉片的最大厚是較重疊部更位於外徑側，因此無法確保彎曲部的面積，即使得到了擴散器靜壓回復量，也會因造成彎曲部的損失增加，可能會使電動送風機的性能降低。Conventional diffusers are diffusers for thick blades. If attention is paid to the shape, the maximum thickness of the blades will be on the outer diameter side of the overlapping portion (the range of L). Such a thick vane diffuser can increase the amount of static pressure recovery inside the diffuser if it has an ideal flow path downstream of the diffuser (eg, a vaneless diffuser or a scroll shell). However, the electric blower of the present invention has an electric motor downstream of the diffuser for supplying airflow to cool the electric motor. Therefore, there is a curved flow path composed of a fan casing, a diffuser vane, and a partition. When the thick vane diffuser described in Non-Patent Document 1 is applied to such an electric blower, since the maximum thickness of the vane is located on the outer diameter side of the overlapping portion, the area of the bent portion cannot be secured, and even if the diffuser is obtained, The amount of pressure recovery will also increase the loss of the bending portion, which may degrade the performance of the electric blower.
又，非專利文獻1當中，厚型葉片擴散器的各個葉片的重疊長度L是設為入口寬度(氣流在平面內看到的寬度)a的四倍。另一方面，電動送風機的擴散器當中，流入擴散器的氣流是由圓周方向的速度所支配的氣流，其氣流角度大多在10°以下，因此為了避免在擴散器的重疊部發生氣流的剝離，必須使L/a大於4。Moreover, in Non-Patent Document 1, the overlapping length L of each blade of the thick blade diffuser is four times the inlet width (the width of the airflow seen in the plane) a. On the other hand, among the diffusers of the electric blower, the airflow that flows into the diffuser is a flow that is dominated by the velocity in the circumferential direction, and the airflow angle is often 10 or less. Therefore, in order to avoid the peeling of the airflow at the overlapping portion of the diffuser, It is necessary to make L/a greater than 4.
因此，本發明之目的在於提供一種即使在送風機下游具有電動機，並將送風機的氣流用來冷卻電動機的情況，也可獲得高效率的電動送風機及搭載該電動送風機的吸塵器。Accordingly, an object of the present invention is to provide a highly efficient electric blower and a vacuum cleaner equipped with the electric blower even if an electric motor is provided downstream of the blower and the airflow of the blower is used to cool the electric motor.
本發明是將由吸入流體的葉輪所吐出的流體引導至設在葉輪之外周的環狀擴散器，然後藉由覆蓋擴散器外周的風扇外殼而轉向，再引導至形成於「在形成有擴散器的面之相反側之面」的回流導片，並將其流體的全部或一部分朝向使葉輪旋轉的電動機引導的電動送風機，其特徵為：擴散器，具備複數個配置於圓周方向的擴散器葉片，各擴散器葉片之旋轉軸方向的剖面，具有從各擴散器葉片之內緣朝外緣先鼓起之後再變窄的形狀。According to the present invention, the fluid discharged from the impeller that sucks the fluid is guided to the annular diffuser provided on the outer circumference of the impeller, and then steered by covering the outer casing of the diffuser, and then guided to the "formed in the diffuser." a returning guide on the opposite side of the surface, and an electric blower that guides all or part of the fluid toward the motor that rotates the impeller, wherein the diffuser has a plurality of diffuser vanes disposed in the circumferential direction. The cross section of each of the diffuser blades in the direction of the rotation axis has a shape that is narrowed from the inner edge of each of the diffuser blades toward the outer edge.
或是，本發明當中，各擴散器葉片的葉片厚度，是從各擴散器葉片之內緣朝外緣先變厚之後再變薄，前述各擴散器葉片的最大葉片厚度位置，是與在圓周方向相鄰的擴散器葉片之重疊部的出口部相鄰。最好是，前述擴散器葉片的最大葉片厚度位置較前述重疊部的出口部更位於內徑側。Or, in the present invention, the blade thickness of each of the diffuser blades is thinned from the inner edge of each diffuser blade toward the outer edge, and the maximum blade thickness position of each of the diffuser blades is at the circumference. The outlet portions of the overlapping portions of the adjacent diffuser vanes are adjacent. Preferably, the maximum blade thickness position of the diffuser blade is located on the inner diameter side of the outlet portion of the overlapping portion.
或是，本發明當中，各擴散器葉片的葉片厚度，是從各擴散器葉片之內緣朝外緣先變厚之後再變薄，前述擴散器葉片的最大葉片厚度位置是位在：由前述風扇外殼及前述凹部所構成的彎曲流路當中，對應於以前述葉輪之旋轉軸中心點為圓之中心的最小徑之位置的位置。Or, in the present invention, the blade thickness of each diffuser blade is thinned from the inner edge of each diffuser blade toward the outer edge, and the maximum blade thickness position of the diffuser blade is at: Among the curved flow paths formed by the fan casing and the concave portion, the position corresponding to the position of the minimum diameter at the center of the circle of the rotation axis of the impeller is corresponding.
或是，本發明當中，前述擴散器葉片之壓力面的葉片角度分布，是從前述擴散器葉片的入口徑朝中央半徑增加，在前述中央半徑以後降低葉片角度，之後再使其增加直到出口徑。Or, in the present invention, the blade angle distribution of the pressure surface of the diffuser blade is increased from the inlet diameter of the diffuser blade toward the center radius, and the blade angle is decreased after the central radius, and then increased until the exit diameter is increased. .
或是，本發明當中，將在圓周方向相鄰的擴散器葉片之重疊部的喉部寬度中點的流路角度，從前述重疊部之入口側到無因次(dimensionless)重疊長度0.2為止的位置設定為大致一定，從前述無因次重疊長度0.2的位置到無因次重疊長度0.7為止的位置使其增加，在前述無因次重疊長度0.7的位置取得流路角度的最大值，之後到無因次重疊長度0.9為止的位置縮小流路角度，然後朝向前述重疊部出口使流路角度之傾斜度的變化縮小。Alternatively, in the present invention, the flow path angle at the midpoint of the throat width of the overlapping portion of the diffuser vanes adjacent in the circumferential direction is from the inlet side of the overlapping portion to the dimensionless overlap length of 0.2. The position is set to be substantially constant, and the position is increased from the position where the dimensionless overlap length is 0.2 to the position where the dimensionless overlap length is 0.7, and the maximum value of the flow path angle is obtained at the position where the dimensionless overlap length is 0.7, and then The position without the dimension overlap length is reduced by the flow path angle, and then the change in the inclination of the flow path angle is reduced toward the overlap portion outlet.
或是，本發明當中，將前述擴散器葉片的最大葉片厚度與前述擴散器葉片之前緣部的葉片厚度的比約為4。Alternatively, in the present invention, the ratio of the maximum blade thickness of the diffuser vane to the blade thickness of the front edge portion of the diffuser vane is about 4.
根據本發明，藉由抑制擴散器重疊部所產生的氣流之剝離，可降低擴散器出口速度，並增加擴散器的靜壓回復量，因此可謀求性能提升，亦可充分確保為了將氣流供應至電動機，而由風扇外殼、擴散器葉片及隔板所構成的彎曲流路的面積，由於擴散器出口速度的降低及面積的確保帶來彎曲部的低損失化，因而可謀求送風機的高效率。According to the present invention, by suppressing the peeling of the airflow generated by the diffuser overlapping portion, the diffuser exit speed can be lowered, and the static pressure recovery amount of the diffuser can be increased, so that the performance can be improved, and the airflow can be sufficiently ensured. In the electric motor, the area of the curved flow path formed by the fan casing, the diffuser vane, and the partition plate can reduce the loss of the diffuser due to the decrease in the outlet speed of the diffuser and the securing of the area. Therefore, the efficiency of the blower can be improved.
又，根據本發明，藉由抑制擴散器重疊部所產生的氣流之剝離，可降低擴散器出口速度，並增加擴散器的靜壓回復量，因此可謀求性能提升，亦可充分確保為了將氣流供應至電動機，而由風扇外殼、擴散器葉片及隔板所構成的彎曲流路的面積，由於擴散器出口速度的降低及面積的確保帶來彎曲部的低損失化，因而可提供能量損失少的高效率電動送風機及搭載該電動送風機的吸塵器。Moreover, according to the present invention, by suppressing the peeling of the airflow generated by the diffuser overlapping portion, the diffuser exit speed can be lowered and the static pressure recovery amount of the diffuser can be increased, so that the performance can be improved and the airflow can be sufficiently ensured. Supply to the motor, and the area of the curved flow path formed by the fan casing, the diffuser vanes, and the partition plate provides a low energy loss due to a decrease in the exit speed of the diffuser and an area ensuring a low loss of the bent portion. A high-efficiency electric blower and a vacuum cleaner equipped with the electric blower.
以下，使用圖面來說明本發明之一實施例。Hereinafter, an embodiment of the present invention will be described using the drawings.
首先，使用第1圖，針對吸塵器全體加以說明。在從第1圖模式顯示的吸塵器主體100上方觀看的橫剖面圖當中，說明吸塵器主體100的構成。假設以安裝吸塵器主體100之管接頭101之側為吸塵器主體100的前側，則在吸塵器主體100的前端具備裝脫自如的管接頭101。First, the entire vacuum cleaner will be described using Fig. 1 . The configuration of the cleaner body 100 will be described in a cross-sectional view as viewed from above the cleaner body 100 shown in the first mode. Assuming that the side of the pipe joint 101 to which the cleaner body 100 is attached is the front side of the cleaner body 100, the pipe joint 101 is detachably attached to the front end of the cleaner body 100.
在吸塵器主體100的前側具備用來保持紙袋103的集塵室102，在吸塵器主體100的後側具備用來收納電動送風機106的電動機室105，在集塵室102與電動機室105之間具備有用來抑制集塵室102內的塵埃流入電動機室105的過濾部104。集塵室102與電動機室105是經由過濾部104而連通。在集塵室102具備裝脫自如的紙袋103。紙袋103的開口是連通於管接頭101。當塵埃逐漸堆積在紙袋103內，紙袋103會鼓起，而形成在紙袋103的開口之相反側，底部就會抵接於過濾部104。在電動機室105具備用來產生吸引力的電動送風機106。在電動送風機106的前側之兩端與電動機室105的前側之內壁面之間，具備用來抑制電動送風機106之振動傳達至吸塵器主體100的防震橡膠107(防震構件)。防震構件亦可改為彈簧來取代橡膠。電動送風機106在前端具備用來吸入空氣的送風機入口108，在後側側方具備用來排出空氣的送風機出口109。接著，送風機入口108是相對於過濾部104開口。在電動機室105的側方具備用來捲繞並收納電源線的捲線器110。在電動送風機106的後側兩側方具備車輪。此外，雖未圖示，但是在管接頭101可連接管體，在管體可連接操作管，在操作管可連接延長管，在延長管可連接吸入具。管接頭101存在之側(上游側)是吸塵器主體100的前側，相反側是吸塵器主體100的後側。從上方觀看吸塵器主體100，朝吸塵器主體100之前後方向直行的方向就是吸塵器主體100的左右方向。所謂側方是較吸塵器主體100之左右方向的中心更靠左側或右側之側。A dust collecting chamber 102 for holding the paper bag 103 is provided on the front side of the cleaner main body 100, and a motor chamber 105 for accommodating the electric blower 106 is provided on the rear side of the cleaner main body 100, and is provided between the dust collecting chamber 102 and the motor chamber 105. The dust in the dust collecting chamber 102 is prevented from flowing into the filter portion 104 of the motor chamber 105. The dust collection chamber 102 and the motor chamber 105 are in communication via the filter unit 104. The dust collecting chamber 102 is provided with a paper bag 103 that is detachable. The opening of the paper bag 103 is in communication with the pipe joint 101. When dust is gradually accumulated in the paper bag 103, the paper bag 103 is bulged and formed on the opposite side of the opening of the paper bag 103, and the bottom portion abuts against the filter portion 104. The motor room 105 is provided with an electric blower 106 for generating an attractive force. An anti-vibration rubber 107 (anti-vibration member) for suppressing the vibration of the electric blower 106 from being transmitted to the cleaner body 100 is provided between both ends of the front side of the electric blower 106 and the inner wall surface of the front side of the motor chamber 105. The anti-vibration member can also be replaced by a spring instead of rubber. The electric blower 106 is provided with a blower inlet 108 for taking in air at the front end, and a blower outlet 109 for discharging air at the rear side. Next, the blower inlet 108 is open to the filter unit 104. A cord reel 110 for winding and accommodating a power cord is provided on the side of the motor chamber 105. Wheels are provided on both sides of the rear side of the electric blower 106. Further, although not shown, the pipe joint 101 can be connected to the pipe body, the pipe body can be connected to the pipe, and the extension pipe can be connected to the pipe, and the suction pipe can be connected to the pipe. The side where the pipe joint 101 exists (upstream side) is the front side of the cleaner body 100, and the opposite side is the rear side of the cleaner body 100. The cleaner body 100 is viewed from above, and the direction toward the front and rear of the cleaner body 100 is the left-right direction of the cleaner body 100. The side is the side closer to the left side or the right side than the center of the left and right direction of the cleaner body 100.
接下來，說明吸塵器主體100內的空氣氣流。從管接頭101流入的空氣會進入集塵室102。第1圖當中作為集塵手段所顯示的紙袋103，並不限定袋子的素材。又，如果是旋風(cyclone)方式，旋風室(旋風式集塵箱)便取代紙袋。由紙袋103除去大部分塵埃的空氣會再通過過濾部104，但是在此，細微的塵埃也會被除去。之後，空氣氣流會流入電動機室105。電動送風機106是經由防震橡膠107懸掛在電動機室105，從送風機入口108流入的空氣經過昇壓之後，會從送風機出口109排出。Next, the air flow in the cleaner body 100 will be described. Air flowing in from the pipe joint 101 enters the dust collecting chamber 102. In the first embodiment, the paper bag 103 displayed as the dust collecting means does not limit the material of the bag. Also, in the case of a cyclone, the cyclone chamber (whirlwind dust box) replaces the paper bag. The air from which most of the dust is removed by the paper bag 103 passes through the filter portion 104 again, but here, fine dust is also removed. Thereafter, the air flow will flow into the motor chamber 105. The electric blower 106 is suspended in the motor chamber 105 via the anti-vibration rubber 107, and the air flowing in from the blower inlet 108 is pressurized and then discharged from the blower outlet 109.
接下來，使用第2圖，針對電動送風機106加以說明。電動送風機106是由吸入空氣用的送風機201及驅動送風機201用的電動機202所構成。Next, the electric blower 106 will be described using FIG. The electric blower 106 is composed of a blower 201 for taking in air and a motor 202 for driving the blower 201.
電動機202是在由外殼203及端架204所構成的電動機外殼支持有旋轉軸205，在旋轉軸205可安裝轉子206。在轉子206的外周可配置固定部的定子207。對於旋轉部之轉子206的電氣供應是藉由毛刷208以及與該毛刷接觸的整流器209所傳達。The motor 202 supports a rotating shaft 205 in a motor housing composed of a housing 203 and an end frame 204, and a rotor 206 can be mounted on the rotating shaft 205. A stator 207 of a fixed portion may be disposed on the outer circumference of the rotor 206. The electrical supply to the rotor 206 of the rotating portion is conveyed by the brush 208 and the rectifier 209 in contact with the brush.
送風機201是在風扇外殼214內集中有以下構件的構成：直接連結於旋轉軸205的離心葉輪210、設在葉輪210之外周側的環狀擴散器211、以及相對於擴散器211隔著隔板212配置在對面的回流導件213。葉輪210在眼部215與風扇外殼214側所具備的密封材216形成概略接觸，具有防漏構造。藉由驅動電動機202使旋轉軸205旋轉，葉輪210會旋轉。擴散器211最好是由樹脂構成。擴散器211亦可與隔板212一體藉由射出成形來製作。葉輪210具備：大致圓板狀的輪轂、圓環狀的護圈、以及形成在輪轂與護圈之間並且配置於圓周方向的複數個葉片。The blower 201 has a configuration in which a fan impeller 210 that is directly coupled to the rotating shaft 205, an annular diffuser 211 provided on the outer peripheral side of the impeller 210, and a partition plate with respect to the diffuser 211 are disposed in the fan casing 214. 212 is disposed on the opposite return guide 213. The impeller 210 is in a rough contact with the seal member 216 provided on the fan casing 214 side in the eye portion 215, and has a leakproof structure. The impeller 210 rotates by rotating the rotating shaft 205 by the drive motor 202. The diffuser 211 is preferably made of a resin. The diffuser 211 can also be fabricated integrally with the separator 212 by injection molding. The impeller 210 includes a substantially disk-shaped hub, an annular retainer, and a plurality of blades formed between the hub and the retainer and disposed in the circumferential direction.
通過相當於第1圖之送風機入口108的電動送風機入口217的空氣，先通過眼部215附近之後，會由葉輪210升壓及加速。接下來，通過擴散器211的氣流會碰到風扇外殼214的內面而轉向大致180°，並流入回流導件213，但是在該過程當中，氣流會減速，因此壓力會上升。通過回流導件213的氣流的全部或一部分會流入電動機的外殼203內，並在使轉子206、定子207、毛刷208、整流器209等冷卻之後排出。旋轉軸205的軸方向是與吸塵器主體100的前後方向大略一致。以旋轉軸205為基準，朝軸方向直行的方向是半徑方向。送風機201存在之側是電動送風機106的前側，電動機202存在之側是電動送風機106的後側。The air passing through the electric blower inlet 217 corresponding to the blower inlet 108 of Fig. 1 passes through the vicinity of the eye portion 215 and is then boosted and accelerated by the impeller 210. Next, the airflow passing through the diffuser 211 hits the inner surface of the fan casing 214 and turns to approximately 180°, and flows into the return guide 213, but during this process, the airflow is decelerated, so the pressure rises. All or a part of the airflow passing through the return guide 213 flows into the outer casing 203 of the motor, and is discharged after cooling the rotor 206, the stator 207, the brush 208, the rectifier 209, and the like. The axial direction of the rotating shaft 205 is substantially coincident with the front-rear direction of the cleaner body 100. The direction in which the straight line is oriented in the axial direction is the radial direction with reference to the rotating shaft 205. The side where the blower 201 is present is the front side of the electric blower 106, and the side where the electric motor 202 exists is the rear side of the electric blower 106.
本發明之對象的吸塵器用電動送風機的葉輪外徑大約在φ60mm～φ120mm的範圍，葉片出口高度大約在6～12mm的範圍，葉片的板厚大約在0.5～1.5mm的範圍，葉片數量大約在6～9片的範圍，輸入大約在500W～1500W的範圍，最高轉速大約在每分鐘35000～50000旋轉的範圍。The outer diameter of the impeller of the electric air blower for vacuum cleaner of the present invention is approximately in the range of φ60 mm to φ120 mm, the blade outlet height is approximately in the range of 6 to 12 mm, the blade thickness is approximately in the range of 0.5 to 1.5 mm, and the number of blades is approximately 6 In the range of ~9 pieces, the input is in the range of about 500W to 1500W, and the maximum speed is about 35,000 to 50,000 rotations per minute.
接下來，使用第3圖，針對擴散器300的形狀加以說明。第3圖是從軸方向前側觀看擴散器300的正面圖。第3圖的擴散器300是從擴散器入口徑309到擴散器出口徑310，在圓周方向以等間隔配置有複數個不同葉片厚度的擴散器葉片301。亦即，從軸方向看來，擴散器葉片301具有：從位在內周側的前緣朝位在外周側的後緣使葉片厚度逐漸變大之後再逐漸變小(先變厚之後再變窄)的形狀。此處所示的擴散器300的尺寸之一例為：擴散器入口徑309約91mm，擴散器出口徑310約125mm，葉片(翼片)片數是13片。擴散器葉片301的配置間隔為360°/13=約27.7°。擴散器300是由擴散器葉片301之凸面側的壓力面306以及相鄰的擴散器葉片301之凹面側的負壓面305所形成，並且具有以擴散器葉片301之前緣部定義的入口喉部302以及以相鄰的擴散器葉片301之後緣部定義的出口喉部303所包圍的重疊部304。重疊部304當中，擴散器葉片301之壓力面306的一部分(除了後緣部以外的部分)與相鄰的擴散器葉片301之負壓面305的一部分(除了前緣部以外的部分)是大致相對向。又，擴散器內部的氣流，其從葉輪出來的氣流311通過入口喉部302之前的半開部及重疊部304，使氣流減速，然後藉由在擴散器出口由風扇外殼214及隔板212之間的間隙所構成的彎曲流路308，使朝向第3圖之紙面深度方向的彎曲流路的氣流312彎曲，再通過回流導件213並流到電動機202。此外，擴散器葉片301的高度亦可從前緣到後緣大致均一，亦可從前緣到後緣變高。Next, the shape of the diffuser 300 will be described using FIG. Fig. 3 is a front view of the diffuser 300 viewed from the front side in the axial direction. The diffuser 300 of Fig. 3 is a diffuser vane 301 having a plurality of different blade thicknesses arranged at equal intervals in the circumferential direction from the diffuser inlet diameter 309 to the diffuser outlet diameter 310. That is, from the axial direction, the diffuser vane 301 has a thickness from the leading edge on the inner peripheral side toward the trailing edge on the outer peripheral side, and then gradually becomes smaller after the thickness of the vane is gradually increased (first becomes thicker and then becomes longer). Narrow) shape. One example of the size of the diffuser 300 shown here is that the diffuser inlet diameter 309 is about 91 mm, the diffuser exit diameter 310 is about 125 mm, and the number of blades (flap) is 13. The arrangement interval of the diffuser blades 301 is 360°/13=about 27.7°. The diffuser 300 is formed by the pressure side surface 306 on the convex side of the diffuser vane 301 and the negative pressure side surface 305 on the concave side of the adjacent diffuser vane 301, and has an inlet throat defined by the leading edge portion of the diffuser vane 301. 302 and an overlap portion 304 surrounded by an exit throat 303 defined by a trailing edge portion of an adjacent diffuser vane 301. Among the overlapping portions 304, a part of the pressure surface 306 of the diffuser vane 301 (portion other than the trailing edge portion) and a portion of the negative pressure surface 305 of the adjacent diffuser vane 301 (except for the portion other than the leading edge portion) are approximate Relative. Moreover, the airflow inside the diffuser, the airflow 311 from the impeller passes through the half opening portion and the overlapping portion 304 before the inlet throat 302, decelerating the airflow, and then between the fan casing 214 and the partition 212 at the diffuser outlet. The curved flow path 308 formed by the gap bends the air flow 312 of the curved flow path toward the depth direction of the paper in FIG. 3, and passes through the return guide 213 to the motor 202. In addition, the height of the diffuser vane 301 may be substantially uniform from the leading edge to the trailing edge, or may be increased from the leading edge to the trailing edge.
本擴散器300是使擴散器葉片301的最大葉片厚度位置313與重疊部304的出口喉部303相鄰。這是為了確保位於擴散器出口的彎曲流路308的面積，而使其不在擴散器300之重疊部304的出口的外徑側，而是形成相鄰。此外，從軸方向觀看彎曲部的擴散器300的總面積約為2000mm2 ，擴散器300之出口喉部303的寬度b與出口高度h所形成的喉部出口面積的比是大約3倍，可謀求在彎曲流路308的低損失化。又，擴散器葉片301的最大葉片厚度位置313亦可在出口喉部303的內徑側。而入口喉部302的寬度a到出口喉部303的寬度b的重疊長度307L，與入口喉部302的寬度a的比(L/a)約為12，入口喉部302的寬度a與出口喉部303的寬度b的比b/a約為2.1。如第3圖所示，擴散器葉片301的負壓面305是與最大葉片厚度位置313無關地從前緣到後緣平穩地彎曲，另一方面，壓力面306是從前緣到最大葉片厚度位置313以比負壓面305之曲率大的曲率平穩地彎曲，在最大葉片厚度位置313以小曲率彎曲，從最大葉片厚度位置313到後緣則以比負壓面305之曲率大的曲率平穩地彎曲。亦即，壓力面306在最大葉片厚度位置313是急遽地轉向。The present diffuser 300 is such that the maximum blade thickness position 313 of the diffuser vane 301 is adjacent to the outlet throat 303 of the overlapping portion 304. This is to ensure the area of the curved flow path 308 at the outlet of the diffuser so as not to be adjacent to the outer diameter side of the outlet of the overlapping portion 304 of the diffuser 300, but to be adjacent. Further, the total area of the diffuser 300 viewing the curved portion from the axial direction is about 2000 mm 2 , and the ratio of the width b of the outlet throat 303 of the diffuser 300 to the throat outlet area formed by the outlet height h is about 3 times. The low loss in the curved flow path 308 is sought. Also, the maximum blade thickness position 313 of the diffuser vane 301 may also be on the inner diameter side of the outlet throat 303. The ratio (L/a) of the overlap length 307L of the width a of the inlet throat 302 to the width b of the outlet throat 303 to the width a of the inlet throat 302 is about 12, and the width a of the inlet throat 302 and the outlet throat. The ratio b/a of the width b of the portion 303 is about 2.1. As shown in Fig. 3, the negative pressure surface 305 of the diffuser vane 301 is smoothly curved from the leading edge to the trailing edge regardless of the maximum blade thickness position 313, and on the other hand, the pressure surface 306 is from the leading edge to the maximum blade thickness position 313. The curvature is smoothly curved with a curvature larger than the curvature of the negative pressure surface 305, and is curved with a small curvature at the maximum blade thickness position 313, and smoothly curved from the maximum blade thickness position 313 to the trailing edge with a curvature larger than the curvature of the negative pressure surface 305. . That is, the pressure face 306 is jerked at the maximum blade thickness position 313.
又，亦可以降低葉片通過頻率噪音為目的，使其與最大葉片厚度位置313大略一致地設置用來連結相鄰之葉片間的角孔。藉此，可謀求性能提升及葉片通過頻率噪音的降低。亦即，亦可在擴散器葉片301之最大葉片厚度位置313的附近，設置從擴散器葉片301之負壓面305貫穿至壓力面306的角孔。亦可設置圓孔來取代角孔。然而，該角孔或圓孔並不是必須的。Further, it is also possible to reduce the passage of the blade through the frequency noise so as to be substantially aligned with the maximum blade thickness position 313 for connecting the corner holes between the adjacent blades. Thereby, performance improvement and blade pass frequency noise reduction can be achieved. That is, an angular hole penetrating from the negative pressure surface 305 of the diffuser vane 301 to the pressure surface 306 may be provided in the vicinity of the maximum blade thickness position 313 of the diffuser vane 301. A round hole can also be provided instead of the corner hole. However, the corner or round hole is not necessary.
與習知擴散器300比較，本實施例是使擴散器葉片301的最大葉片厚度位置313與重疊部304的出口喉部303相鄰。藉此，由於抑制了在重疊部304所產生的氣流之剝離，因而可降低擴散器出口速度，並增加擴散器300的靜壓回復量，而且亦可充分確保為了對電動機202供應氣流而由風扇外殼214、擴散器葉片301及隔板212所構成的彎曲流路308的面積，因為擴散器出口速度的降低及面積的確保帶來彎曲部的低損失化，可同時提升重疊部304的性能並謀求彎曲部的低損失化，因而可謀求送風機201的高效率化。In contrast to the conventional diffuser 300, the present embodiment is such that the maximum blade thickness position 313 of the diffuser vane 301 is adjacent to the outlet throat 303 of the overlap portion 304. Thereby, since the peeling of the airflow generated in the overlapping portion 304 is suppressed, the diffuser exit speed can be lowered, and the static pressure recovery amount of the diffuser 300 can be increased, and the fan can be sufficiently ensured to supply the airflow to the motor 202. The area of the curved flow path 308 formed by the outer casing 214, the diffuser vane 301, and the partition plate 212 can improve the performance of the overlapping portion 304 at the same time because the decrease in the outlet speed of the diffuser and the securing of the area result in a low loss of the bent portion. Since the low loss of the bending portion is achieved, the efficiency of the blower 201 can be improved.
接下來，使用第4圖，針對擴散器葉片401的形狀加以說明。第4圖是擴散器400的放大圖，是從軸方向前側觀看的正面圖。第4圖是在擴散器葉片401的葉片厚度當中，以最大葉片厚度位置405為中心來顯示。令第4圖的最大葉片厚度位置405與：由風扇外殼406及隔板408所構成的彎曲流路403(第4圖中的斜線部)的形狀當中，以旋轉軸205之旋轉軸中心點407為圓(第4圖中的虛線)之中心的彎曲流路的最小徑位置402一致。此外，符號404是彎曲流路的最小徑。隔板408具備：從擴散器葉片401之後緣沿著該擴散器葉片401之後緣部的凸面朝隔板408之內周側切入的凹部。凹部是設在隔板408之外周端部的開口。凹部的形狀大致呈三角形。在環狀隔板408的外周端部是在每個相鄰的擴散器葉片401間形成有這種凹部，該結果，環狀隔板408的外周會形成凹凸狀。彎曲流路403是形成在隔板408的凹部與風扇外殼406的內周面之間，彎曲流路403的剖面是大致菱形或大致三角形。Next, the shape of the diffuser vane 401 will be described using FIG. Fig. 4 is an enlarged view of the diffuser 400, which is a front view as seen from the front side in the axial direction. Fig. 4 is a view showing the maximum blade thickness position 405 among the blade thicknesses of the diffuser blades 401. The maximum blade thickness position 405 of FIG. 4 and the curved flow path 403 (hatched portion in FIG. 4) constituted by the fan case 406 and the partition plate 408 are the rotation axis center point 407 of the rotary shaft 205. The minimum diameter position 402 of the curved flow path at the center of the circle (the broken line in Fig. 4) coincides. Further, the symbol 404 is the minimum diameter of the curved flow path. The partition plate 408 includes a recessed portion that is cut from the rear edge of the diffuser vane 401 along the convex surface of the rear edge portion of the diffuser vane 401 toward the inner peripheral side of the partition plate 408. The recess is an opening provided at the outer peripheral end portion of the partition 408. The shape of the recess is substantially triangular. Such a concave portion is formed between each adjacent diffuser vane 401 at the outer peripheral end portion of the annular partition plate 408, and as a result, the outer periphery of the annular partition plate 408 is formed in a concavo-convex shape. The curved flow path 403 is formed between the concave portion of the partition 408 and the inner circumferential surface of the fan casing 406, and the curved flow path 403 has a substantially rhombic shape or a substantially triangular shape.
接下來，利用第5圖～第7圖，使用擴散器葉片501的葉片厚度502、翼面上之葉片角度509之一例加以說明。第5圖是擴散器葉片501之葉片厚度502及擴散器葉片之葉片表面上之葉片角度509之定義的說明圖。葉片角度509是畫出連結翼面上之點503(圖面中為壓力面510)與旋轉軸中心點507的直線504，並畫出相對於直線504的正交線505，將該正交線505與外側之翼表面506之接線508所形成的葉片角度509設定為葉片角度「β」。此外，負壓面511的葉片角度的定義也相同。Next, an example of the blade thickness 502 of the diffuser blade 501 and the blade angle 509 of the airfoil surface will be described using Figs. 5 to 7 . Figure 5 is an illustration of the definition of the blade thickness 502 of the diffuser vane 501 and the vane angle 509 on the vane surface of the diffuser vane. The blade angle 509 is a line 504 that draws a point 503 (pressure surface 510 in the drawing) and a center point 507 of the rotating shaft on the connecting airfoil, and draws an orthogonal line 505 with respect to the straight line 504. The blade angle 509 formed by the wire 508 of the 505 and the outer wing surface 506 is set to the blade angle "β". Further, the definition of the blade angle of the negative pressure surface 511 is also the same.
第6圖是利用第5圖所定義的葉片厚度502、以及將定義了葉片厚度502的圓之中心點上與旋轉軸中心點507連結的半徑來顯示葉片厚度分布。本擴散器葉片501的葉片厚度分布，是在入口徑具有最小葉片厚度602，朝出口徑增加，並且在略中央附近具有最大葉片厚度601，並朝擴散器出口徑減少葉片厚度。在此，在入口徑之葉片厚度502的前緣葉片厚度是0.6mm，與最大葉片厚度的比約為4。Fig. 6 is a view showing the blade thickness distribution by using the blade thickness 502 defined in Fig. 5 and the radius at which the center point of the circle defining the blade thickness 502 is coupled to the rotation axis center point 507. The blade thickness profile of the present diffuser vane 501 has a minimum vane thickness 602 at the inlet diameter, increases toward the exit diameter, and has a maximum vane thickness 601 near the center, and reduces the vane thickness toward the diffuser exit diameter. Here, the leading edge blade thickness at the blade diameter 502 of the inlet diameter is 0.6 mm, and the ratio to the maximum blade thickness is about 4.
再者，第7圖是利用第5圖所定義的壓力面510與負壓面511的葉片角度509、以及以旋轉軸中心點為圓之中心的各點的半徑，來顯示出擴散器葉片500的葉片角度分布。在負壓面511的葉片角度是從入口徑朝出口徑簡單地增加，在出口徑的內徑側是形成一定的葉片角度，然後朝出口徑急遽地縮小葉片角度509。出口徑前急遽的角度之減少是為了使擴散器500的主要氣流容易靠葉片之負壓面511側流動，以縮小與位在擴散器出口的風扇外殼之衝突角度，而進行急遽的氣流之轉向。此外，在負壓面511使葉片角度509急遽變化這點是設定為出口徑的大約97%。另一方面，壓力面510的葉片角度分布，從入口徑起雖然角度有增減，但是朝入口徑及出口徑的中央是增加的。之後，在中央半徑以後使葉片角度509急遽縮小，然後再增加直到出口徑。此外，使壓力面的葉片角度509急遽降低，並再度增加的變彎點701的半徑是擴散器入口半徑的大約1.2倍。Further, Fig. 7 shows the diffuser vane 500 by using the vane angle 509 of the pressure surface 510 and the negative pressure surface 511 defined in Fig. 5 and the radius of each point centered on the center of the rotation axis. The angular distribution of the blades. The blade angle on the negative pressure surface 511 is simply increased from the inlet diameter to the outlet diameter, and a certain blade angle is formed on the inner diameter side of the outlet diameter, and then the blade angle 509 is sharply reduced toward the outlet diameter. The sharp decrease in the angle before the exit path is to make the main airflow of the diffuser 500 easily flow on the side of the negative pressure surface 511 of the vane to narrow the collision angle with the fan casing located at the outlet of the diffuser, and to make an urgent turn of the airflow. . Further, the point at which the blade angle 509 changes sharply on the negative pressure surface 511 is set to be about 97% of the outlet diameter. On the other hand, the blade angle distribution of the pressure surface 510 increases or decreases from the inlet diameter, but increases toward the center of the inlet diameter and the outlet diameter. After that, the blade angle 509 is sharpened and reduced after the central radius, and then increased until the exit diameter. In addition, the blade angle 509 of the pressure face is sharply lowered, and the radius of the increased bending point 701 is about 1.2 times the radius of the diffuser inlet.
與習知擴散器比較，本實施例是使壓力面的葉片角度分布是形成以下的形狀：從入口徑朝中央半徑增加，在中央半徑以後急遽降低葉片角度，然後再增加直到出口徑。藉此，由於抑制了在擴散器重疊部所產生的氣流之剝離，因而可降低擴散器出口速度並增加擴散器的靜壓回復量，而且亦可充分確保為了對電動機供應氣流而由風扇外殼、擴散器葉片及隔板所構成的彎曲流路的面積，因為擴散器出口速度的降低及面積的確保帶來彎曲部的低損失化，可同時提升擴散器重疊部的性能並謀求彎曲部低損失化，因而可謀求送風機的高效率化。Compared with the conventional diffuser, this embodiment is such that the blade angular distribution of the pressure surface is formed into a shape in which the radius increases from the inlet diameter toward the center, the blade angle is sharply lowered after the central radius, and then increased until the outlet diameter. Thereby, since the peeling of the airflow generated at the overlapping portion of the diffuser is suppressed, the diffuser exit speed can be reduced and the static pressure recovery amount of the diffuser can be increased, and the fan casing can be sufficiently ensured to supply the airflow to the motor. The area of the curved flow path formed by the diffuser vane and the partition plate reduces the loss of the bent portion due to the decrease in the exit speed of the diffuser and the securing of the area, thereby simultaneously improving the performance of the overlapping portion of the diffuser and achieving a low loss in the bent portion. Therefore, the efficiency of the blower can be improved.
接下來，使用第8圖、第9圖，針對重疊部之流路中心的流路角度805加以敘述。第8圖是使用擴散器800，定義由擴散器葉片801之壓力面802及相鄰的擴散器葉片801之負壓面803所形成的喉部寬度之中點804當中的流路之角度分布的圖。中點804是與由擴散器葉片801之壓力面802及相鄰的擴散器葉片801之負壓面803所形成的喉部內接的圓的中心。流路角度805，是畫出直交於直線806的直交線807，並將該直交線807與「將流路間予以連結」的直線所形成的角度，設為流路角度805，上述直線806是將「由擴散器葉片801的壓力面802、及相鄰的擴散器葉片801的負壓面803所形成的喉部寬度」的中點804、及旋轉軸中心點808予以連結。第9圖顯示出以總重疊部長度809使各重疊部的位置無因次化的無因次重疊長度、以及由喉部寬度之中點所形成的流路角度805的分布。本擴散器800，是將從重疊部之入口側到無因次重疊長度0.2為止的流路角度805設定為大致固定，從無因次重疊長度0.2到0.7為止增加。之後，在無因次重疊長度0.7是形成最大角度901，之後到無因次重疊長度0.9為止使流路角度805急遽縮小，在重疊部出口再縮小流路角度805的傾斜度。Next, the flow path angle 805 of the flow path center of the overlapping portion will be described using Figs. 8 and 9 . Figure 8 is a perspective view showing the angular distribution of the flow path among the points 804 of the throat width formed by the pressure surface 802 of the diffuser vane 801 and the negative pressure surface 803 of the adjacent diffuser vane 801 using the diffuser 800. Figure. The midpoint 804 is the center of a circle inscribed with the throat formed by the pressure surface 802 of the diffuser vane 801 and the negative pressure surface 803 of the adjacent diffuser vane 801. The flow path angle 805 is a straight line 807 drawn straight to the straight line 806, and an angle formed by the straight line 807 and a line connecting the flow paths is defined as a flow path angle 805, and the straight line 806 is The midpoint 804 of the "throat width formed by the pressure surface 802 of the diffuser vane 801 and the negative pressure surface 803 of the adjacent diffuser vane 801" and the rotating shaft center point 808 are connected. Fig. 9 shows the distribution of the dimensionless overlap with the total overlap portion length 809 such that the positions of the overlapping portions are not dimensioned, and the distribution of the flow path angle 805 formed by the midpoint of the throat width. In the present diffuser 800, the flow path angle 805 from the inlet side of the overlapping portion to the dimensionless overlap length of 0.2 is set to be substantially constant, and is increased from the dimensionless overlap length of 0.2 to 0.7. Thereafter, the maximum angle 901 is formed at the dimensionless overlap length of 0.7, and then the flow path angle 805 is sharply reduced until the dimensionless overlap length is 0.9, and the inclination of the flow path angle 805 is further reduced at the exit of the overlap portion.
與習知擴散器比較，本實施例是將重疊部之喉部寬度中點的流路角度，從重疊部的入口側到無因次重疊長度0.2為止設定為大致固定，從無因次重疊長度0.2到0.7為止增加，在無因次重疊長度0.7取得流路角度的最大值，之後到無因次重疊長度0.9為止使流路角度急遽縮小，然後朝重疊部出口縮小流路角度的傾斜度。藉此，由於抑制了在擴散器重疊部所產生的氣流之剝離，因而可降低擴散器出口速度並增加擴散器的靜壓回復量，而且亦可充分確保為了對電動機供應氣流而由風扇外殼、擴散器葉片及隔板所構成的彎曲流路的面積，因為擴散器出口速度的降低及面積的確保帶來彎曲部的低損失化，可同時提升擴散器重疊部的性能並謀求彎曲部低損失化，因而可謀求送風機的高效率化。Compared with the conventional diffuser, in the present embodiment, the flow path angle at the midpoint of the throat width of the overlapping portion is set to be substantially constant from the inlet side of the overlapping portion to the dimensionless overlap length of 0.2, and the dimension difference is not fixed. Increasing from 0.2 to 0.7, the maximum value of the flow path angle is obtained at the dimensionless overlap length of 0.7, and then the flow path angle is sharply reduced until the dimensionless overlap length is 0.9, and then the inclination of the flow path angle is reduced toward the overlap portion exit. Thereby, since the peeling of the airflow generated at the overlapping portion of the diffuser is suppressed, the diffuser exit speed can be reduced and the static pressure recovery amount of the diffuser can be increased, and the fan casing can be sufficiently ensured to supply the airflow to the motor. The area of the curved flow path formed by the diffuser vane and the partition plate reduces the loss of the bent portion due to the decrease in the exit speed of the diffuser and the securing of the area, thereby simultaneously improving the performance of the overlapping portion of the diffuser and achieving a low loss in the bent portion. Therefore, the efficiency of the blower can be improved.
100．．．吸塵器主體100. . . Vacuum cleaner body
101．．．管接頭101. . . Pipe joint
102．．．集塵室102. . . Dust chamber
103．．．紙袋103. . . Paper bag
104．．．過濾部104. . . Filter section
105．．．電動機室105. . . Motor room
106．．．電動送風機106. . . Electric blower
107．．．防震橡膠107. . . Anti-vibration rubber
108．．．送風機入口108. . . Blower inlet
109．．．送風機出口109. . . Blower outlet
110．．．捲線器110. . . Reel
111．．．車輪111. . . wheel
201．．．送風機201. . . Blower
202．．．電動機202. . . electric motor
203．．．外殼203. . . shell
204．．．端架204. . . End frame
205．．．旋轉軸205. . . Rotary axis
206．．．轉子206. . . Rotor
207．．．定子207. . . stator
208．．．毛刷208. . . brush
209．．．整流器209. . . Rectifier
210．．．葉輪210. . . impeller
211,300,400,500,800．．．擴散器211,300,400,500,800. . . Diffuser
212,408．．．隔板212,408. . . Partition
213．．．回流導件213. . . Reflux guide
214,406．．．風扇外殼214,406. . . Fan housing
215．．．眼部215. . . Eye
216．．．密封材216. . . Sealing material
217．．．電動送風機入口217. . . Electric blower inlet
301,401,501,801．．．擴散器葉片301,401,501,801. . . Diffuser blade
302．．．入口喉部302. . . Inlet throat
303．．．出口喉部303. . . Export throat
304．．．重疊部304. . . Overlap
305,511,803．．．負壓面305,511,803. . . Negative pressure surface
306,510,802．．．壓力面306,510,802. . . Pressure surface
307．．．重疊長度307. . . Overlap length
308,403．．．彎曲流路308,403. . . Curved flow path
309．．．擴散器入口徑309. . . Diffuser inlet diameter
310．．．擴散器出口徑310. . . Diffuser exit path
311．．．從葉輪出來的氣流311. . . Airflow from the impeller
312．．．彎曲流路的氣流312. . . Curved flow of air
313,405,601．．．最大葉片厚度位置313,405,601. . . Maximum blade thickness position
402．．．彎曲流路的最小徑位置402. . . Minimum path position of the curved flow path
404．．．彎曲流路的最小徑404. . . Minimum path of curved flow path
407,507,808．．．旋轉軸中心點407,507,808. . . Rotation axis center point
502．．．葉片厚度502. . . Blade thickness
503．．．翼面上的點503. . . Point on the airfoil
504．．．(連結旋轉軸中心點及葉片表面之點的)直線504. . . a straight line connecting the center point of the rotating shaft and the point of the blade surface
505,807．．．正交線505,807. . . Orthogonal line
506．．．葉片表面506. . . Blade surface
508．．．接線508. . . wiring
509．．．葉片角度509. . . Blade angle
600．．．葉片厚度分布600. . . Leaf thickness distribution
602．．．最小葉片厚度602. . . Minimum blade thickness
700．．．葉片角度分布700. . . Blade angle distribution
701．．．壓力面之葉片角度分布的變彎點701. . . Bending point of the blade angle distribution of the pressure surface
805．．．流路角度805. . . Flow path angle
806．．．(連結旋轉軸中心點及喉部中心點的)直線806. . . a line connecting the center point of the rotating shaft and the center point of the throat
809．．．總重疊部長度809. . . Total overlap length
900．．．流路角度分布900. . . Flow path angular distribution
901．．．最大角度901. . . Maximum angle
第1圖是吸塵器主體的示意橫剖面圖。Fig. 1 is a schematic cross-sectional view of the main body of the cleaner.
第2圖是吸塵器用電動送風機的剖面圖。Fig. 2 is a cross-sectional view of the electric blower for a vacuum cleaner.
第3圖是實施例1之擴散器的形狀圖。Fig. 3 is a view showing the shape of the diffuser of the first embodiment.
第4圖是擴散器葉片的最大厚度與隔板最小徑的位置關係圖。Figure 4 is a diagram showing the positional relationship between the maximum thickness of the diffuser vanes and the minimum diameter of the diaphragm.
第5圖是擴散器葉片之各半徑的葉片厚度及翼面上之葉片角度的定義圖。Figure 5 is a definition of the blade thickness for each radius of the diffuser vanes and the vane angle on the airfoil.
第6圖是擴散器葉片之各半徑的葉片厚度分布圖。Figure 6 is a graph of blade thickness distribution for each radius of the diffuser vanes.
第7圖是擴散器葉片之各半徑的葉片壓力面及負壓面的角度分布圖。Fig. 7 is an angular distribution diagram of the blade pressure surface and the negative pressure surface of each radius of the diffuser vane.
第8圖是擴散器葉片之重疊部的流路之喉部寬度的中心點所形成的流路角度的定義圖。Fig. 8 is a view showing the definition of the flow path angle formed by the center point of the throat width of the flow path of the overlapping portion of the diffuser vanes.
第9圖是擴散器葉片之重疊部的流路角度分布圖。Fig. 9 is a flow path angle distribution diagram of the overlapping portion of the diffuser vanes.
300．．．擴散器300. . . Diffuser
301．．．擴散器葉片301. . . Diffuser blade
302．．．入口喉部302. . . Inlet throat
303．．．出口喉部303. . . Export throat
304．．．重疊部304. . . Overlap
305．．．負壓面305. . . Negative pressure surface
306．．．壓力面306. . . Pressure surface
307．．．重疊長度307. . . Overlap length
308．．．彎曲流路308. . . Curved flow path
309．．．擴散器入口徑309. . . Diffuser inlet diameter
310．．．擴散器出直徑310. . . Diffuser diameter
311．．．從葉輪出來的氣流311. . . Airflow from the impeller
312．．．彎曲流路的氣流312. . . Curved flow of air
313．．．最大葉片厚度位置313. . . Maximum blade thickness position
Claims (6)
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011043467A JP5544318B2 (en) | 2011-03-01 | 2011-03-01 | Electric blower and vacuum cleaner equipped with the same |
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| TW201237280A TW201237280A (en) | 2012-09-16 |
| TWI468597B true TWI468597B (en) | 2015-01-11 |
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| CN (1) | CN102654140B (en) |
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| TWI651474B (en) * | 2017-11-01 | 2019-02-21 | 日商夏普股份有限公司 | Air supply device |
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| JP6101551B2 (en) * | 2013-04-26 | 2017-03-22 | 日立アプライアンス株式会社 | Household vacuum cleaner |
| JP6381983B2 (en) * | 2014-06-13 | 2018-08-29 | 日立アプライアンス株式会社 | Electric blower for vacuum cleaner and electric vacuum cleaner provided with the same |
| CN104912850B (en) * | 2015-05-21 | 2017-03-01 | 合肥通用机械研究院 | Radial guide vane structure with streamline structure |
| JP2018003806A (en) * | 2016-07-08 | 2018-01-11 | 日立アプライアンス株式会社 | Electric blower and vacuum cleaner including the same |
| CN113074138B (en) * | 2020-01-06 | 2022-05-17 | 广东威灵电机制造有限公司 | Diffusion device, fan and dust catcher |
| JP7299188B2 (en) * | 2020-03-26 | 2023-06-27 | 日立グローバルライフソリューションズ株式会社 | blower and washing machine |
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| CN102654140B (en) | 2015-05-20 |
| TW201237280A (en) | 2012-09-16 |
| CN102654140A (en) | 2012-09-05 |
| JP5544318B2 (en) | 2014-07-09 |
| JP2012180777A (en) | 2012-09-20 |
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