TWI253491B - Centrifugal blower - Google Patents
Centrifugal blower Download PDFInfo
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- TWI253491B TWI253491B TW93115201A TW93115201A TWI253491B TW I253491 B TWI253491 B TW I253491B TW 93115201 A TW93115201 A TW 93115201A TW 93115201 A TW93115201 A TW 93115201A TW I253491 B TWI253491 B TW I253491B
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- centrifugal blower
- discharge
- discharge port
- casing
- fluid
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
i 1253491 玫、發明說明： 【發明所屬之技術領域】 本發明，係有關使用於空調設備或換氣設備等、具備 旋洞狀之機殼的離心送風機。 【先前技術】 第5圖，係顯不具備習知漩渦狀機殼之離心送風機之 構成的縱截面圖。離心送風機200，係具備機殼1〇、及内 藏於該機殼10之旋渦室的葉片㈣。機殼10之排放口 l〇a之轴向中心線12、與通過葉片輪u之軸線且與排放口 1〇a之軸向同方向之中心線(以下稱為第1中心線)CU，兩 者平行，相隔既定距離。 琢離心送風機200之機殼1〇之排放口 1〇a中，流過其 外周側之流體之流動比流過内周側之流體之流動還快。因 =’若連接於排放口 1()a之配管之彎曲方向與葉片輪^ 疋轉方向相"流體沿配管之彎曲流動，故沒有大的壓[Technical Field] The present invention relates to a centrifugal blower having a screw-shaped casing for use in an air conditioner or a ventilation device. [Prior Art] Fig. 5 is a longitudinal sectional view showing the configuration of a centrifugal blower which does not have a conventional vortex casing. The centrifugal blower 200 is provided with a casing (1) and blades (four) housed in the vortex chamber of the casing 10. The axial center line 12 of the discharge port l〇a of the casing 10 and the center line (hereinafter referred to as the first center line) CU passing through the axis of the vane wheel u and in the same direction as the axial direction of the discharge port 1〇a, Parallel, separated by a given distance. In the discharge port 1 of the casing 1 of the centrifugal blower 200, the flow of the fluid flowing through the outer peripheral side thereof is faster than the flow of the fluid flowing through the inner peripheral side. Because =' if the bending direction of the pipe connected to the discharge port 1()a is in the direction of the blade wheel rotation direction, the fluid flows along the pipe, so there is no large pressure.
損失’而當配管之彎曲古A 向，、葉片輪11之旋轉方向相反 ’則在配管之彎曲部分，、、ώ /爪動快之邛分之流體導致大的壓 貝 因此，有無法獲得既定風量的問題。 對此，以往係如第®芬笛a m ^ 相同方向(圖中，®及主弟6β圖所*，在將流體往 放 达風的情形，與連接於機殼1 0之排 放口 10a的配管之彎曲方向 . . . . ^目對應，分料備2種旋轉方 U右々疋或左旋）不同的葦Μ β ^ ^ _ 茱片輪、及與其對應之機殼10。 该機殼1 0，係與驅動葉 μ 门彻11之馬達1 5 —起設置於 雔心送風機200之基台14 、 右葉片輪11之旋轉方向相 1253491 同，且僅改變流體之排放方向13，則分別如第6A圖、第 6C圖及第6E圖所示’將相同之機殼1〇，以排放口 i〇a之 軸向中心線12與各流體之排放方向13(圖中之上方、左方 及右方）大致-致之方式設置於基台14上。然而，因安裝 互異，故必須對應流體 於機威1 0之基台14的部分之形狀 之排放方向13準備3種基台。 同樣地，若葉片輪11之旋轉方向與上述不同，則如第 6B圖、帛6D圖及g 6F圖所*，將相同之機殼1〇,以排放 口 l〇a之軸向中心線12與各流體之排放方向13 (圖中之 上方、左方及右方）大致一致之方式設置於基台Η上。在 此情形，亦與上述同樣地必須準備3種基台Μ。 【發明内容】 基於上述原因，以往必須準備至少6種有相同性能之 離心送風機200。因此，有離心送風機2〇〇之生產性差、 庫存管理亦繁雜的問題。 對此’可如第7A圖所示，將以2點鏈線代表之習知 =心送風機200之機殼10,以排放口他之軸向中心線12 *近上述葉片㉟11之第1中心線CL1之方式配置於基台 Η上。接著’於該機殼10之排放口 1〇a安裝肘接頭“且 ㈣機殼1〇之排放口 10a之軸向中心線12與葉片輪^之 弟1中心線CL1 -致。因此’於肘接頭16之端部新形成之 排放口 16a之軸向中心線12a與葉片輪n之第i中心線 C L1 -一 致。 藉此 上述流動快之流體便靠近上述新的排放口 l6a 1253491 之中央部附a，即便將連接於該排放σ 16a之配管，往與 葉片輪11之旋轉方向同方向f曲，較往相反方向彎曲’，、 在’曲部分亦難以發生流體之剝離等現象。結果，能防止 大的壓力損失發生。 然而’在此情形’因肘接頭16新安裝於機殼10之排 放口 10a ’故與習知情形相比，有機殼1()變大且壓力損失 變大的問題。 、 對此，在日本特開平u — 294393號公報所揭示之離心 送風機2〇1巾，機殼10，係如第7B圖所示，以排放口心 之軸向中心線靠近葉片輪u之第】中心線cu且朝相 同方向之方式，將機殼1G之排放口 10a附近之-部分17 削掉而形成。藉此，如上述般，不必於機㉟1〇之排放口 W設置肘接!員16便能使新形成之排放口 1〇b之軸向中心 線12:靠近葉片輪11之第1中心線CL1且朝相同方向。 藉此，如上述般，離心送風機201不必變大。麸而， 離心送風請之擴散器 1 18變短，故無法將該部分Μ :流速充分減速，該㈣18之壓力損失增加，而有離心 送風機201之性能降低之問題。 具體來說，如帛8圖所示，相對於習知離心送 :::靜壓之曲線L1’第7B圖所示之離心送風機之風量 评[之曲線L2是往在相同風量下靜壓變小的方向移動 結果;有在既定之靜壓下無法獲得既定風量之問題。。 、，對此，能藉著加長上述擴散器部18來抑制壓力損 曰力仁如上述般有離心送風機變大的問題。 、 1253491 因此，本發明，係用以解決以 目的在Μ#— 、以上之問喊而開發者，其 :種離心运風機，相較於習知離心送風機， 在生此不降低下減少種類。 :發明為—種離心送風機，係於旋渴狀之機殼内藏有 :之L:於機殼具備：排放通路，設置成該通路之排放 =中心線通過葉片輪之轴線；及減速部，形成於該 广路之排放口附近，其流路向外彎曲且沿流體之排放 向逐漸擴大1來使流過其内側之流體高效率地減速。 依據上述構成，在離心送風機之排放通路之排放口， 流動快之流體能接近中央部附近，並且能使在當中流動之 流體高效率地減速。因此，即便將連接於排放通路之配管 往與葉片輪之旋轉方向同方向彎曲或往相反方向弯曲，在 Τ彎曲：分亦難以發生流體之剝離等，故不發生大的壓力 損失。藉此，能在不降低離心送風機之性能之下，使離心 送風機之葉片輪之旋轉方向，從以往之2種變成！種。 此外，該減速部，亦可分別形成於排放通路之排放口 附近之與葉片輪之軸向同方向之兩側。 一般，離心送風機之排放通路之排放口附近之葉片輪 之徑向之兩側之内面，係沿機殼之漩渦形狀來形成，故在 這部分不發生大的Μ力損失。相對於此，在離心送風機之 排放通路之排放口附近之與葉片輪軸向之兩側之内面，離 心送風機之排放通路之排放口之與葉月輪軸向同方向之寬 度尺寸，比機殼之與葉片輪軸向同方向之寬度尺寸還大， 1253491 :内面之相隔距離往排放口逐新擴大。因此，有時在該 =通路内流動之流體從排放通路之内面發生剝離等，而 大的厂堅力損失。因此，本發明，為了防止這現象，而 ::该部分設置減速部。藉此，能防止應力損失之增加，故 月匕防止離心送風磯之性能之降低。 此外’上述減速部之彎曲部分之曲率半徑最好為排放 k路之排放口之内徑之5〜2〇%。Loss 'When the bending of the piping is ancient A direction, and the rotation direction of the vane wheel 11 is opposite', the fluid in the curved portion of the piping, and the ώ/claw movement is fast, resulting in a large pressure shell. Therefore, it is impossible to obtain the predetermined The problem of air volume. In this case, in the past, the same direction as the ® fensam am ^ (in the figure, the ® and the 6β map of the younger brother), in the case where the fluid is released to the wind, and the piping connected to the discharge port 10a of the casing 10 The bending direction of the . . . ^^ corresponds to the two types of rotating square U right or left-handed) different 苇Μ β ^ ^ _ 茱 轮 wheel, and the corresponding casing 10 . The casing 10 is disposed in the same direction as the rotation direction of the base 14 of the core blower 200 and the rotation direction of the right blade wheel 11 with the motor 15 that drives the blade 11 and only changes the discharge direction of the fluid 13 , as shown in Figures 6A, 6C, and 6E, respectively, 'the same casing is 1 〇, with the axial center line 12 of the discharge port i〇a and the discharge direction of each fluid 13 (above the figure) The left and right sides are arranged on the base 14 in a substantially uniform manner. However, since the mounting is different, it is necessary to prepare three kinds of bases in accordance with the discharge direction 13 of the shape of the portion of the base 14 of the fluid. Similarly, if the rotation direction of the vane wheel 11 is different from the above, the same casing is 1 〇 as the axial center line 12 of the discharge port l〇a as shown in FIG. 6B, FIG. 6D and g 6F. It is provided on the base raft so as to substantially coincide with the discharge direction 13 (upper, left, and right in the figure) of each fluid. In this case as well, three types of abutments must be prepared in the same manner as described above. SUMMARY OF THE INVENTION For the above reasons, it has been conventionally required to prepare at least six types of centrifugal blowers 200 having the same performance. Therefore, there is a problem that the centrifugal blower 2 is poor in productivity and complicated in inventory management. This can be as shown in Fig. 7A, which will be represented by a 2-point chain line = the casing 10 of the heart blower 200, with the axial centerline 12 of the discharge port being close to the first centerline of the blade 3511. The CL1 mode is configured on the base station. Then, 'the elbow joint is installed at the discharge port 1〇a of the casing 10' and the axial center line 12 of the discharge port 10a of the casing (1) is the same as the center line CL1 of the blade wheel 1. Therefore, the elbow is The axial center line 12a of the newly formed discharge opening 16a at the end of the joint 16 coincides with the i-th center line C L1 - of the vane wheel n. Thereby the fluid flowing fast is close to the central portion of the new discharge port l6a 1253491. In addition, even if the pipe connected to the discharge σ 16a is bent in the same direction as the rotation direction of the blade wheel 11, it is bent in the opposite direction, and the phenomenon of peeling of the fluid is hard to occur in the curved portion. It is possible to prevent a large pressure loss from occurring. However, in this case, since the elbow joint 16 is newly installed in the discharge port 10a of the casing 10, the organic shell 1 () becomes larger and the pressure loss becomes larger as compared with the conventional case. In this regard, the centrifugal blower 2 〇 1 towel disclosed in Japanese Laid-Open Patent Publication No. H-294393, the casing 10, as shown in Fig. 7B, is close to the blade wheel by the axial center line of the discharge core. The first line cu and in the same direction, the case 1G The portion 17 near the discharge port 10a is formed by cutting off. Thus, as described above, it is not necessary to provide the elbow of the discharge port W of the machine 351, and the axial direction of the newly formed discharge port 1〇b can be made. The center line 12 is close to the first center line CL1 of the vane wheel 11 and faces in the same direction. Therefore, as described above, the centrifugal blower 201 does not have to be large. The braze and the diffuser 1 18 for centrifugal air supply are shortened, so that it is impossible to The portion Μ: the flow rate is sufficiently decelerated, the pressure loss of the (four) 18 is increased, and the performance of the centrifugal blower 201 is lowered. Specifically, as shown in FIG. 8 , the curve is compared with the conventional centrifugal feed::: static pressure L1' Figure 7B shows the air volume of the centrifugal blower [The curve L2 is the result of moving in the direction where the static pressure becomes smaller under the same air volume; there is a problem that the given air volume cannot be obtained under the given static pressure. Therefore, by lengthening the diffuser portion 18, it is possible to suppress the pressure loss and the force of the centrifugal blower as described above. 1253491 Therefore, the present invention is for solving the problem of Μ#-, above. Shouting the developer, its: a kind of centrifugal fan, Compared with the conventional centrifugal blower, the type is reduced without reducing it. The invention is a kind of centrifugal blower, which is contained in the thirst-shaped casing: L: the casing has: a discharge passage, which is set to Discharge of the passage = the center line passes through the axis of the vane wheel; and the deceleration portion is formed near the discharge port of the wide road, and the flow path is outwardly curved and gradually expanded along the discharge of the fluid 1 to make the fluid flowing through the inner side thereof high According to the above configuration, in the discharge port of the discharge passage of the centrifugal blower, the fluid flowing quickly can approach the vicinity of the center portion, and the fluid flowing therein can be decelerated efficiently. Therefore, even if it is connected to the discharge passage The piping is bent in the same direction as the direction of rotation of the vane wheel or bent in the opposite direction, and it is difficult to cause peeling of the fluid in the bending of the crucible, so that no large pressure loss occurs. In this way, the rotation direction of the vane wheel of the centrifugal blower can be changed from the conventional two types without lowering the performance of the centrifugal blower! Kind. Further, the speed reducing portions may be formed on both sides in the same direction as the axial direction of the vane wheel in the vicinity of the discharge port of the discharge passage. Generally, the inner faces of the radial sides of the vane wheel near the discharge port of the discharge passage of the centrifugal blower are formed along the spiral shape of the casing, so that no large loss of force occurs in this portion. In contrast, in the vicinity of the discharge port of the discharge passage of the centrifugal blower and the inner side of the axial direction of the vane wheel, the width of the discharge port of the discharge passage of the centrifugal blower is the same as the axial direction of the leaf lug, and the ratio of the shell to the blade The width of the wheel in the same direction of the axial direction is still large, and the 1253491: the inner surface is separated from the discharge port by a new distance. Therefore, sometimes the fluid flowing in the = passage is peeled off from the inner surface of the discharge passage, and the large plant is lost. Therefore, in order to prevent this phenomenon, the present invention provides a deceleration portion in this portion. Thereby, the increase in stress loss can be prevented, so that the performance of the centrifugal blower is prevented from being lowered. Further, the radius of curvature of the curved portion of the above-described decelerating portion is preferably 5 to 2% of the inner diameter of the discharge port of the discharge k-way.
依據上述構成，在離心送風機之排放通路内 體在減速部高效率地減速。藉此’能防止塵力損失之增加 二文能防止離心送風機之性能之降低。又，若減速部之彎 p刀之曲率半桎小於排放通路之排放口之内徑之5%，則 ^速部太短而無法使流體高效率地減速。又，若減速部之 号曲部分之曲率半徑大於排放通路之排放口之内徑之2〇% ’則機殼變大。 【實施方式】 施發明之最佳形tAccording to the above configuration, the inner body of the discharge passage of the centrifugal blower is efficiently decelerated in the speed reducing portion. This can prevent the increase in dust loss and prevent the performance of the centrifugal blower from deteriorating. Further, if the curvature of the bending blade of the speed reducing portion is less than 5% of the inner diameter of the discharge port of the discharge passage, the speed portion is too short to decelerate the fluid efficiently. Further, if the radius of curvature of the portion of the decelerating portion is larger than 2% of the inner diameter of the discharge port of the discharge passage, the casing becomes large. [Embodiment] The best shape of the invention
以下’芩照圖式說明本發明之實施形態。 i如第1A圖所示，離心送風機100，係具備漩渦狀機殼 复、及設置於該機殼1之漩渦室u内的葉片輪2。於機殼i ”備排放通路lb，該通路lb之流路從漩渦室之出口擴 大二=第1B圖所示，漩渦室la之流路截面大致至矩形狀 ，该流路戴面從漩渦室la經排放通路lb漸漸變為圓形， 在排放通路lb之排放口 lc成為圓形。 其次，該排放口 lc之軸向中心線3，係與通過葉片輪 10 1253491 2之軸線、且與排放口 le 稱為第1中心線）CL1大致1 方向之令心線（以下， ，係通過葉片輪2之軸線。’、即’上述軸向中心線3 藉此，能使流動比較快的^ 排放口 止Μ ^丨〔體接近離心送風機100之 1 C之中央部附近。妹 之配管（未ffl - 1 ,± p便將連接於排放口 1 c 或往相反方!如 '2之旋轉方向同方向彎曲， 等，故彎曲部分亦難以發生流體之剝離 寺故此防止發生大的壓力 m 旋轉方向一 2種上失;：此’能將葉片… 二一，…- .>VL Μ Μ ^ ^ ΊΌ /现體阿效率地減速之減速部4 /口排放通路1B之軸向以 ^ 1 之軸向同方Θ ""又之寬度方向（與葉片輪2 之轴向同方向。翏照第之符號w。)之 大形成之傾斜部位5、及 〃 又51擴 用以連絡該傾斜部位5盥減 之於徑向内方以曲率半徑2Rf =速^ ，傾斜部位5之擴張角度〇，儀箱^^“位6。還有 内發生流體剝離等現象之角度。-疋成避免在部位5 \、、： ^ 4係、如第1B圖所示形成於該離心送風機 _之排放通路lb之排放口卜附近之機 之 兩側（第1B圖中之斜錄 又万向之 斤 ”、本邛）。該減速部4，係如第1(： -，由第1B圖之A—A線截面視，相對排放口 二 心線3呈左右對稱，0 ·、， 袖向中 曲。 既定之曲率半徑β往徑向外方彎 圖 其次’彎曲之減速部4之曲率半徑，係如第^〜2£ 11 1253491 所示，由第1B圖之XI — XI、X2〜Y9 a λ2、A-A、X3-X3、X4 -X4線截面視，分別為w、R2、R、PQ n 以、1M。這些半徑且有 R1>R2>R、及R4>R3>R之關係。亦即， 丨 截面視之位置從排放 口 lc之中心越往左右方（機殼1之 方向垂直方向）遠 離，對應該位置之減速部4之曲銮生/一 / 萌羊+徑便漸大。此外，該 減速部4之左右端，係與排放通路 、、 乂崎1 b之排放口 1 c附近之 減速部4之外的部位7分別連續。Embodiments of the present invention will be described below with reference to the drawings. As shown in Fig. 1A, the centrifugal blower 100 includes a spiral casing and a vane wheel 2 provided in the swirl chamber u of the casing 1. In the casing i", the discharge passage lb, the flow path of the passage lb is expanded from the outlet of the vortex chamber; as shown in Fig. 1B, the flow path of the vortex chamber la is substantially rectangular, and the flow path is worn from the vortex chamber. La is gradually rounded through the discharge passage lb, and the discharge port lc of the discharge passage lb becomes circular. Second, the axial center line 3 of the discharge port lc is connected to the axis passing through the vane wheel 10 1253491, and discharged The mouth is called the first center line. CL1 is a one-way direction of the heart line (hereinafter, it passes through the axis of the blade wheel 2), that is, the above-mentioned axial center line 3, thereby enabling the flow to be faster. Μ Μ 丨 丨 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 体 离心The direction is curved, etc., so the bending part is also difficult to cause the separation of the fluid. Therefore, the large pressure m is prevented from occurring. The rotation direction is one or two kinds of loss; this 'can be used for the blade... 21, ...-.> VL Μ Μ ^ ^ ΊΌ / The current body is decelerated by the efficiency of the deceleration part 4 / port discharge passage 1B axial direction with the axis of ^ 1 The same direction Θ "" and the width direction (the same direction as the axial direction of the blade wheel 2. The reference symbol w.) is formed by the large inclined portion 5, and 〃 51 is used to connect the inclined portion 5盥Reduced to the inner side of the radial direction with a radius of curvature 2Rf = speed ^, the angle of expansion of the inclined portion 5 〇, the box ^ ^ "bit 6. There is also the phenomenon of fluid peeling inside the phenomenon. - 疋 避免 avoid at the location 5 \ , ,: ^ 4, as shown in Figure 1B, formed on both sides of the machine near the discharge port of the discharge blower lb of the centrifugal blower (the oblique note and the universal pinch in Figure 1B), Benedict The deceleration portion 4 is, for example, the first (: -, viewed from the A-A line of Fig. 1B, and is bilaterally symmetrical with respect to the discharge center line 2, 0 ·, and the sleeve is oriented to the middle curve. The radius β is curved outward in the radial direction. The radius of curvature of the second 'bending deceleration portion 4 is as shown in Fig. 1-2, and is represented by XI-XI, X2~Y9 a λ2, AA, X3 of Fig. 1B. -X3, X4 - X4 line cross-section, respectively, w, R2, R, PQ n to, 1 M. These radii have the relationship of R1 > R2 > R, and R4 > R3 > R. That is, 丨The position of the face is farther from the center of the discharge port lc to the left and right (the direction perpendicular to the direction of the casing 1), and the curve of the deceleration portion 4 corresponding to the position is gradually increased. The left and right ends of the speed reducing portion 4 are continuous with the discharge passages and the portions 7 other than the speed reducing portion 4 in the vicinity of the discharge port 1 c of the Miyazaki 1 b.
在此，該減速部4之曲率半徑R最好設定成0.05D〜 〇.2D(D為排放通路ib之排放口 lc之内徑）。理由是，當 減速部4之曲率半徑R小於排放通路lb之排放口 ic之内 “ D之5/。日寸/咸速部4太紐，無法使流體高效率地減速。 此外，若減速部4之曲率半徑R大於排放口卜之内徑〇之 2〇%，則機殼1變大。另外，最好與該減速部4之曲率半徑 R相對應，將減速部4之軸向之高度H2設定成〇 〇5])〜 0· 2D 〇 ^還有，減速部4之彎曲曲線，實際上是依據離心送風 _ 機之風里、待送風之流體之種類等預先由實驗等來設定。 上述減速部4，在當中流動之流體高效率地減速，故 月匕將/爪肢減速所必要的排放通路丨b之軸向之距離設定的比 、4的還小。反過來說，若於排放口丨c附近不設置減速部 4 ’則必須加長上述距離。 更具體來說，可將通過葉片輪2之軸線、且與排放口 1C大致平行的中心線（以下稱為第2中心線）CL2到排放口 门度Η ’例如設定在排放口 1 £之内徑d之1 · 5倍以下 12 1253491 100之機殼 1之吸入口 藉上述之方式，本實施形態之離心送風機 能比習知送風機更小型。 此外，亦可使排放口 lc之内徑D，與機崎 之内徑D1相同。藉此，亦可將連接於這些排放口之配管 之種類加以統_。 另外，在此，雖使機殼1之排放通路lb之排放口 之軸向中心線3，與葉片輪2之第1中心線α丨一致 lc ，不 ^ 也可視連接於該排放口 1 c之配管之配置 心線3與葉片輪2之第2中心線CL2大致一致 使該軸向中Here, the radius of curvature R of the speed reducing portion 4 is preferably set to 0.05D to 〇.2D (D is the inner diameter of the discharge port lc of the discharge passage ib). The reason is that when the radius of curvature R of the speed reducing portion 4 is smaller than the discharge port ic of the discharge passage lb, "D of 5/. day inch/salt speed portion 4 is too large, the fluid cannot be decelerated efficiently. In addition, if the speed reduction portion When the radius of curvature R of 4 is larger than 2% of the inner diameter 排放 of the discharge port, the casing 1 becomes larger. Further, it is preferable to correspond to the radius of curvature R of the speed reducing portion 4, and the axial height of the speed reducing portion 4 is set. H2 is set to 〇〇5])~0·2D 〇^ Further, the bending curve of the speed reducing portion 4 is actually set in advance by experiments or the like depending on the type of the air in the centrifugal blower, the type of the fluid to be blown, and the like. In the above-described speed reducing portion 4, the fluid flowing therethrough is decelerated efficiently, so that the ratio of the distance between the axial direction of the discharge passage 丨b necessary for decelerating the claw limb is smaller than that of 4. It is necessary to lengthen the above distance without providing the speed reducing portion 4' in the vicinity of the discharge port c. More specifically, a center line passing through the axis of the vane wheel 2 and substantially parallel to the discharge port 1C (hereinafter referred to as a second center line) CL2 to the discharge port degree Η 'For example, set the inner diameter d of the discharge port 1 £ to 1 · 5 times In the above-mentioned manner, the centrifugal blower of the present embodiment can be made smaller than the conventional blower. In addition, the inner diameter D of the discharge port lc and the inner diameter D1 of the machine can be made. In this way, the type of the pipe connected to the discharge ports can be integrated. Further, here, the axial center line 3 of the discharge port of the discharge passage 1b of the casing 1 and the blade wheel 2 are The first center line α丨 is uniform lc, and the arrangement center line 3 of the pipe connected to the discharge port 1c is substantially coincident with the second center line CL2 of the blade wheel 2 in the axial direction.
以下，根據實施例來詳述本發明。 實施例 係具備漩滿狀 如第1A〜1C圖所示，離心送風機1〇〇 機殼1、及設置於該機殼i之旋渦室la内的葉片輪2。機 殼1之排放通路lb之排放口 lc之軸向中心線3與葉片輪Hereinafter, the present invention will be described in detail based on examples. EXAMPLES A swirling shape is shown in Figs. 1A to 1C, a centrifugal blower 1 casing 1, and a vane wheel 2 provided in the swirl chamber 1a of the casing i. The discharge port of the casing 1 and the discharge port of the lc are axial center line 3 and the blade wheel
2之垂直方向中心線CL1大致-致。該排放〇 ^附近具備 減速部4。 此外，有關該離心送風機100之設定，相對機殼丨之 排放口 lc之内徑D’葉片輪2之第2中心線CL2到排放口 lc之高度H=〇.95D，減速部4之曲率半徑r=〇 〇7d，減 速部4之高度H2=0.07D，排放通路lb之擴張角度占卜 28° 。 比較例1 比較例1，如第5圖所示，與實施例不同的是： 13 1253491 機叙10之排放口 1 Oa之轴向中心線】2、與通過葉片輪i i 之軸線且與排放口 10a之軸向同方向之中心線（以下，垂直 方向中心線相隔既定距離平行，二、未具備上述減速 邛4 ’ 一相對表機喊10之排放口 i 〇a之内徑D2 (大約 0.85D)，葉片輪11之第2中心線⑴到排放口 .之高度 H3= 0. 92D2。其他則與實施例相同。 比較例2 比較例2,如帛7B圖所*，與實施心㈣h㈣ 上述減速部4°因此’如以第1C圖之2點鏈線所示，上述 之排放通路ib之擴張角度5 "足28。擴張成3〇。。其他則 與貫施例相同。 特性之評估 使用上述實施例、比較例i及比較例2之離心送風機 ’測定離"送風機之性能，進行了該評估。將其結果顯示 於m ®中’符號U、L2、L3’為分別對應比較例i 比較例2、及實施例的性能曲線。 r如第3圖所示，若將比較例ι(性能曲'線⑴與實施例 性能曲線L3)相比，則得知與比較例i相比實施例之性能 未明顯降低。由此可說實施例與比較合"有相同之性能。 而且，本實施例之離心送風機，如上述，丨必如比較例上 之離心送風機般，與連接於排放^ 1〇a之配管之配置相對 =準備許多種類。具體來說，如第4A〜4c圖所示，能將本 只施例之離心送風機之完成品之種類，從以往< 6種減至 3種。 14 1253491 另一方面’比較例2,與實施例相同，可減少離心送 風機之種類，但如第3圖所示，離心送風機之性能降低。 尤其，在離心送風機之高風量域，相對實施例(性能曲線 L3)，比較例2(性能曲線L2)之靜塵大崎低，發生大的塵 力損失。理由是’於上述之排放通路lb未設置減速部〇 故在當中流動之流體未充分減速’以及，排放通路化之擴 張角度川定擴張至30。，故在排放通路^内面易 於發生流體之剝離等。由此可知，於離心送風請之排 放通路ib設置減速部4，對於降㈣力損失是有效的。 此外，上述之實施形態為一個例子，在未超出本發明 :要旨：範圍’可作各種變更，本發明並未限定於上述之 員知形悲。 可能性 相較於習知離心送風機 結果，本發明之離心送風 依據本發明之離心送風機 可在不降低性能之下減少種類 機，係生產性佳，庫存管理亦一… 風機。 子s里亦今易，為-種有用的離心送 【圖式簡單說明】 (一）圖式部分 弟1A圖，係顯示本發明 本構成例的縱戴面圖。 第1B圖，係顯示本發明 本構成例之俯視圖。 第1C圖，係第1B圖所 一實施形態之離心送風機之基 一實施形態之離心送風機之基 示離心送風機之排放通路之△ 15 1253491 一 A線局部截面圖。 第2A圖，係第1B圖之^一乂丨線局部裁面圖。 第2Β圖，係第1Β圖之以一以線局部截面圖。 第2C圖，係第1Β圖之a—Α線局部截面圖。 第⑼圖，係第1Β圖之Χ3—Χ3線局部截面圖。 =2Ε圖，係第1Β圖之Χ4 一以線局部截面圖。 第3圖，係顯示離心送風機之風量與靜壓之關係的曲 線圖。The vertical center line CL1 of 2 is substantially uniform. The deceleration portion 4 is provided in the vicinity of the discharge 〇 ^. Further, regarding the setting of the centrifugal blower 100, the inner diameter D of the discharge port lc of the casing lc is the height H of the second center line CL2 of the blade wheel 2 to the discharge port lc H=〇.95D, and the radius of curvature of the speed reducing portion 4 r = 〇〇 7d, the height of the speed reducing portion 4 is H2 = 0.07D, and the expansion angle of the discharge passage lb is 28 degrees. Comparative Example 1 Comparative Example 1, as shown in Fig. 5, differs from the embodiment in that: 13 1253491 The axial center line of the discharge port 1 Oa of the machine 10 is 2, and the axis passing through the vane wheel ii and the discharge port The center line of the axial direction of 10a (hereinafter, the center line of the vertical direction is parallel to the predetermined distance, and the second speed is not provided with the above-mentioned deceleration '4'. The relative diameter of the discharge port i 〇a of the opposite machine is 10 (about 0.85D) The height from the second center line (1) of the blade wheel 11 to the discharge port is H3 = 0.92D2. Others are the same as in the embodiment. Comparative Example 2 Comparative Example 2, as shown in Fig. 7B, and the implementation of the heart (four) h (four) 4° Therefore, as shown by the 2-point chain line in Fig. 1C, the expansion angle 5 "foot 28 of the above-mentioned discharge passage ib is expanded to 3 〇. Others are the same as the examples. The evaluation of the performance of the centrifugal blower 'measurement of the air blower' of the above-mentioned embodiment, the comparative example i, and the comparative example 2 was carried out, and the result was shown in m* 'the symbols U, L2, L3' correspond to the comparative example i, respectively. Comparative Example 2, and the performance curves of the examples. r as shown in Figure 3, if the ratio is Example ι (performance curve 'line (1) compared with the example performance curve L3) shows that the performance of the embodiment is not significantly reduced compared with the comparative example i. It can be said that the embodiment has the same performance as the comparative example. Further, the centrifugal blower of the present embodiment, as described above, is in the same manner as the centrifugal blower of the comparative example, and is arranged in comparison with the arrangement of the piping connected to the discharge unit 1 = a plurality of types are prepared. Specifically, as in 4A~ As shown in Fig. 4c, the type of the finished product of the centrifugal blower of the present embodiment can be reduced from the conventional <6 types to three types. 14 1253491 On the other hand, 'Comparative Example 2, as in the embodiment, can reduce the centrifugal blower The type, but as shown in Fig. 3, the performance of the centrifugal blower is reduced. In particular, in the high air volume range of the centrifugal blower, the static dust of the comparative example 2 (performance curve L2) is lower than that of the embodiment (performance curve L3). A large dust loss occurs. The reason is that 'there is no deceleration part in the above discharge passage lb, so the fluid flowing therethrough is not sufficiently decelerated' and the expansion angle of the discharge passage is expanded to 30. Therefore, in the discharge passage ^The inside is easy It is understood that the deceleration portion 4 is provided in the discharge passage ib for centrifugal air blowing, and it is effective for reducing the force loss. Further, the above-described embodiment is an example, and the present invention is not exceeded: The scope can be variously modified, and the present invention is not limited to the above-mentioned members. The possibility is that the centrifugal blower of the present invention can be reduced without degrading performance according to the centrifugal blower result of the present invention. The type of machine is good in productivity, and the inventory management is also a... Fan. Subs s is also easy to use, for a kind of useful centrifugal delivery [Simple description of the diagram] (1) Part of the diagram 1A diagram, showing the present invention A longitudinal wear diagram of a configuration example. Fig. 1B is a plan view showing the configuration example of the present invention. Fig. 1C is a perspective view of a centrifugal blower according to an embodiment of Fig. 1B. The centrifugal blower of the embodiment shows a partial cross-sectional view of the discharge passage of the centrifugal blower Δ 15 1253491. Fig. 2A is a partial plan view of the line of Fig. 1B. The second figure is a partial cross-sectional view of the first figure. Figure 2C is a partial cross-sectional view of the a-Α line of the first figure. Figure (9) is a partial cross-sectional view of the Χ3—Χ3 line of the first figure. = 2 Ε diagram, is the first section of the figure 一 4 a partial section of the line. Fig. 3 is a graph showing the relationship between the air volume of the centrifugal blower and the static pressure.
a第4Α圖，係本發明一實施形態之離心送風機之完成品 之前視圖，顯示在流體之排放方向為鉛直上方之情形下之 構成例。 一第4B圖’係本發明一實施形態之離心送風機之完成品 之前視圖’顯示在流體之排放方向為右方之情形下之構成 例。 第4C圖，本發明一實施形態之離心送風機之完成品之A fourth drawing is a completed example of the centrifugal blower according to an embodiment of the present invention. The front view shows a configuration example in the case where the discharge direction of the fluid is vertically upward. Fig. 4B is a view showing a configuration of a centrifugal blower according to an embodiment of the present invention. The front view ’ shows a configuration in the case where the discharge direction of the fluid is right. Figure 4C is a view showing the finished product of the centrifugal blower according to an embodiment of the present invention.
前視圖’顯示在流體之排放方向為左方之情形下之構成例 〇 第5圖，係習知之具備旋洞狀機殼之離心送風機之構 成的縱截面圖。 第6A圖’係習知離心送風機之完成品之縱截面圖，顯 示在流體之排放方向為鉛直上方、且葉片輪之旋轉方向為 往左繞之情形下之構成例。 第6B圖’係習知離心送風機之完成品之縱截面圖，顯 示在流體之排放方向為錯直上方、m之旋轉方向為 16 送風機之完成品之縱截面 且葉片輪之旋轉方向 圖，顯 ”、、只 為往左 圖，顯 為往右The front view' shows a configuration example in the case where the discharge direction of the fluid is left. Fig. 5 is a longitudinal sectional view showing a configuration of a centrifugal blower having a spiral-shaped casing. Fig. 6A is a longitudinal sectional view showing the finished product of the conventional centrifugal blower, showing a configuration example in the case where the discharge direction of the fluid is vertically upward and the direction of rotation of the vane is wound to the left. Fig. 6B' is a longitudinal sectional view of the finished product of the conventional centrifugal blower, showing that the discharge direction of the fluid is staggered upward, and the direction of rotation of m is 16 the longitudinal section of the finished product of the blower and the rotation direction of the vane wheel, ", only for the left picture, it is shown to the right
，顯 往右 機之完成品之縱截面 且葉片輪之旋轉方向 迗風機之完成品之縱截面圖，顯 方、且葉片輪之旋轉方向為往左 之完成品之縱截面圖 葉片輪之旋轉方向為 1253491 往右繞之情形下之構成例 第6C圖，係習知離心 示在流體之排放方向為左 繞之情形下之構成例。 第6D圖，係習知離心送風 示在流體之排放方向為左方、 繞之情形下之構成例。 弟6E圖，係習知離心 示在流體之排放方向為右 繞之情形下之構成例。 第6F圖，係習知離心送風機 示在流體之排放方向為右方、且 繞之情形下之構成例。 以排：U圖係'將弟5圖所示之習知離心送風機之機殼 口之二之軸向中心線靠近通過葉片輪之轴線、且盘排 ==向之中心線之方式配置於基台，並於排: 、二 /構成之另一離心送風機之縱截面圖。 弟7B圖，係將第$圖所示之習知雜心接门」 以排放口之軸“ 6 風機之機殼 口之轴白二“近通過葉片輪之轴線、且與排 :=向之中心線之方式配置於基台1削掉機 圖。W 寸近之—部分來構成之另-離心送風機之縱截 係顯示習知離心送風機之風量與靜壓之關係The longitudinal section of the finished product of the finished product of the finished product of the right machine and the direction of rotation of the blade wheel, the square of the finished product, and the rotation direction of the blade wheel is the rotation of the blade of the longitudinal section of the finished product to the left The sixth embodiment of the configuration example in the case where the direction is 1,254,491 to the right is a configuration example in which the centrifugal direction of the fluid is left-wound. Fig. 6D shows a configuration example in which the centrifugal discharge air is left and wound in the direction in which the fluid is discharged. The 6E figure is a conventional example in which the centrifugal direction of the fluid is right-wound. Fig. 6F shows a configuration example in which the centrifugal blower is shown in the case where the discharge direction of the fluid is right and is wound. In the row: U map system, the axial center line of the second casing of the conventional centrifugal blower shown in the figure 5 is placed close to the axis passing through the vane wheel, and the disc row == toward the center line. Abutment, and in the row: 2, the longitudinal section of another centrifugal blower. Brother 7B, the familiar figure shown in Figure # is connected to the shaft of the discharge port. "6 The shaft of the casing of the fan is white 2" near the axis of the blade wheel, and the row: = direction The center line is arranged on the base 1 to cut off the machine map. W inch is close to - part of the other - the longitudinal section of the centrifugal blower shows the relationship between the air volume and the static pressure of the conventional centrifugal blower
第8圖 的曲線圖。 17 1253491 (二）元件代表符號 1 機殼 la 旋涡室 lb 排放通路 1 c 排放口 2 葉片輪 3 軸向中心線 4 減速部 5 傾斜部位 6 連絡部位 7 排放通路1 b之排放口 1 c附近之減速部4之 外的部位 10 機殼 10a 排放口 10b 新形成之排放口 11 葉片輪 12 排放口 10a之軸向中心線 12a 排放口 1 Ob之軸向中心線 13 流體之排放方向 14 基台 15 馬達 16 肘接頭 16a 新形成之排放口 17 機殼1 0之排放口 10a附近之一部分 18 1253491 18 擴 散 器 部 100 離 心 送風 機 200 習 知 離 心 送風 機 201 習 知 離 心 送風 機 CL1 第 1 中 心 線 CL2 第 2 中 心 線Figure 8 is a graph. 17 1253491 (2) Component symbol 1 Enclosure la Vortex chamber lb Discharge path 1 c Discharge port 2 Vane wheel 3 Axial center line 4 Deceleration part 5 Inclined part 6 Contact part 7 Drainage path 1 b near discharge port 1 c A portion other than the deceleration portion 4 The casing 10a The discharge port 10b The newly formed discharge port 11 The axial center line 12a of the vane wheel 12 discharge port 10a The axial center line 13 of the discharge port 1 Ob 13 The discharge direction of the fluid 14 Abutment 15 Motor 16 Elbow joint 16a Newly formed discharge port 17 One part of the vicinity of the discharge port 10a of the casing 1 0 18135349 18 Diffuser part 100 Centrifugal blower 200 Conventional centrifugal blower 201 Conventional centrifugal blower CL1 1st center line CL2 2nd center line
1919
Claims (1)
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2003160153A JP4590167B2 (en) | 2003-06-05 | 2003-06-05 | Centrifugal blower |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| TW200427930A TW200427930A (en) | 2004-12-16 |
| TWI253491B true TWI253491B (en) | 2006-04-21 |
Family
ID=33508568
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| TW93115201A TWI253491B (en) | 2003-06-05 | 2004-05-28 | Centrifugal blower |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP4590167B2 (en) |
| CN (1) | CN100404878C (en) |
| TW (1) | TWI253491B (en) |
| WO (1) | WO2004109120A1 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104420431B (en) * | 2013-08-28 | 2016-08-10 | 苏州宝时得电动工具有限公司 | Blowing device |
| CA3139766C (en) | 2019-10-17 | 2023-10-31 | Zhongshan Broad-Ocean Motor Co., Ltd. | Volute assembly and induced draught fan using same |
| CN211082385U (en) * | 2019-10-17 | 2020-07-24 | 中山大洋电机股份有限公司 | Volute component and induced draft fan applying same |
| WO2022024267A1 (en) * | 2020-07-29 | 2022-02-03 | 三菱電機株式会社 | Scroll casing of centrifugal blower, centrifugal blower provided with scroll casing, air conditioner, and refrigeration circuit device |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB733533A (en) * | 1952-08-26 | 1955-07-13 | Establissements Neu Sa Des | Improvements in or relating to centrifugal blowers, compressors, pumps and the like |
| US3860360A (en) * | 1973-09-04 | 1975-01-14 | Gen Motors Corp | Diffuser for a centrifugal compressor |
| JPS5529381Y2 (en) * | 1976-01-19 | 1980-07-12 | ||
| JPS5313610U (en) * | 1976-07-19 | 1978-02-04 | ||
| JPS59131799A (en) * | 1983-12-19 | 1984-07-28 | Hitachi Ltd | Casing for centrifugal hydraulic machine |
| JPH03217699A (en) * | 1990-01-23 | 1991-09-25 | Nissan Motor Co Ltd | Scroll structure of compressor |
| DE50011843D1 (en) * | 1999-06-14 | 2006-01-19 | Waertsilae Schweiz Ag Winterth | Charging group for a large diesel engine |
| JP2001193682A (en) * | 2000-01-06 | 2001-07-17 | Ebara Corp | Voltex pump |
-
2003
- 2003-06-05 JP JP2003160153A patent/JP4590167B2/en not_active Expired - Fee Related
- 2003-11-26 WO PCT/JP2003/015060 patent/WO2004109120A1/en active Application Filing
- 2003-11-26 CN CNB200380110333XA patent/CN100404878C/en not_active Expired - Fee Related
-
2004
- 2004-05-28 TW TW93115201A patent/TWI253491B/en not_active IP Right Cessation
Also Published As
| Publication number | Publication date |
|---|---|
| TW200427930A (en) | 2004-12-16 |
| JP4590167B2 (en) | 2010-12-01 |
| CN1788168A (en) | 2006-06-14 |
| JP2004360579A (en) | 2004-12-24 |
| WO2004109120A1 (en) | 2004-12-16 |
| CN100404878C (en) | 2008-07-23 |
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