TW200427930A - Centrifugal blower - Google Patents

Abstract

The object of the present invention is to provide a centrifugal blower capable of reducing kinds as compared to the conventional centrifugal blowers without deteriorating performance. The centrifugal blower (100) in accordance with the present invention is a centrifugal blower (100) that comprises an impeller (2) incorporated in a volute casing (1). The casing (1) includes: a delivery passage (1b) formed so that an axial centerline (3) of a delivery port (1c) thereof extends through an axis of the impeller (2) and a speed reduction part (4) formed in the delivery passage (1b) near the delivery port (1c) and the flow passage thereof being outward curved and gradually diverged in the delivery direction of the fluid to efficiently reduce the speed of the fluid flowing therein.

Description

200427930, Description of the invention: [Technical field to which the invention belongs] ^ The present invention relates to a centrifugal blower provided with a gray-like casing for use in air-conditioning equipment or ventilation equipment. [Prior Art] Fig. 5 is a longitudinal sectional view showing a centrifugal blower provided with a conventional vortex-shaped casing. The centrifugal blower 200 is a vane wheel 1 provided with a casing 10 and a vortex chamber with a built-in side and an A machine. The centerline 12 of the axial direction of the discharge opening 10 of the casing 10, and the centerline passing through the axis of the blade wheel 11 and the same direction as the axial direction of the discharge opening 10a (hereinafter referred to as the first centerline) CU, the two are parallel, separated by a predetermined distance. In the discharge port 1Ga of the casing 10 of the centrifugal blower 200, the flow of the body passing through it is faster than the flow of the fluid flowing through the inner peripheral side. Therefore, the bending direction of the pipe connected to the discharge port 10a is the same as the turning direction of the vane wheel u, so the fluid flows along the bending of the pipe, so there is no large pressure loss. Opposite direction 1 In the bent part of the piping, the fluid that flows fast causes a large pressure drop. Therefore, there is a problem that a predetermined air volume cannot be obtained. In this regard, as shown in FIG. 6A and FIG. 6β, in the case where the fluid is sent in the same direction (above the figure), the direction of f-curve is the same as that of the pipe connected to the two ports W of the casing 10 Correspondingly, two kinds of blade wheels with different rotation directions (° 疋 or left 疋) are prepared, and the corresponding casing 10 is prepared. The casing centrifugal blower 10 is arranged on a base 14 of 200 together with a motor 15 driving a blade wheel 11. If the rotation direction of the blade wheel 11 is the same as 200427930, and only the discharge direction 13 of the fluid is changed, as shown in Fig. M, Fig. 6C and Fig. 6E, respectively, the same casing is used as the discharge port. The axial centerline 12 and the discharge direction 13 (upper and right in the figure) of each fluid are arranged on the base 14 in a substantially consistent manner. However, since the shapes of the parts of the abutment 14 mounted on the machine 10 are mutually different, the three types of abutments must be prepared corresponding to the discharge direction 13 of the fluid. Similarly, if the rotation direction of the blade wheel 卩 is different from the above, as shown in Fig. 6B, "D" and "F", the same machine ㈣ is used to discharge the axial centerline 12 of the center of the mouth and the fluid The discharge direction 13 (upper, left, and right in the figure) is set on the abutment "in a uniform manner. In this case, three kinds of abutments must be prepared in the same way as above. [Contents of the invention] Based on For the above reasons, at least 6 kinds of centrifugal fans with the same performance must be prepared in the past. Therefore, there are problems that the centrifugal fans have poor productivity and complicated inventory management. As shown in Figure 7A, sub-b can be linked in two points. The conventional knowledge represented by the line is redundant and is arranged on the abutment in a manner close to the first center line CL1 of the blade wheel 11 in the axial center line 12 of the discharge port 1 Oa. Next, in the casing 10 An elbow joint 16 is installed at the discharge port 10a and the Shihai machine is set to discharge at 10

The axial centerline 12 of Wa coincides with the centerline CL1 of the younger brother 1 of the blade wheel 11. Therefore, the axial direction of the discharge opening 16a newly formed at the end of the elbow joint 16 is +, and the center line 12a is consistent with the first center line IL1 of the blade wheel 11. The above-mentioned fast-flowing fluid will be near the central part of the new discharge port 16a 200427930. Even if you connect Lian Zhengyu Secret 4 "% to the side discharge σ 16a, go to the side of the round 11 The direction of rotation is the same as the bending direction. ^ The bow is bent in the opposite direction, and it is difficult to cause the peeling of the flowing peach in the song. As a result, large pressure loss can be prevented. However, in this case, because The elbow joint connector 16 is newly installed at the discharge port 10 a of the casing 10. Therefore, it ’s familiar and familiar with flying. Μ μ “The organic casing 10 becomes larger and the pressure loss becomes larger. Beitian responds to this” in Japanese Patent Application Laid-Open I 〗… The door ^ U U4393 disclosed in the centrifugal fan 201, the casing 10, ^ Α Ning Rudi 7β diagram, the axial centerline 12 of the discharge port 10a is close to the cymbal private π The first centerline CL1 of the twelve dog disc wheels 11 faces the same direction as the first center line CL1, and a portion 17 near the discharge port 10a of the casing 17

Shaved to form. With this, as described above, there is no τ W 10a._B + 4i, and it is not necessary to set the elbow joint 16 for the discharge σ 机 Ua of the cabinet 10 to ampoule # > Green 19 ▲ This makes the newly formed discharge port l〇 The axial centerline 12a of b is near the blade wheel η 筮 筮 + U of the magic centerline CL1 and faces the same direction. Hunting this ’as described above, the diffusion write of the centrifugal blower 2 and the centrifugal blower 201” However,

> $ & 〃policy state 18 is shorter, so the flow velocity of this part] S cannot be fully decelerated, the pressure loss of this part 18… 18 is increased, and the performance of the fan 201 is reduced. Specifically, as the 8th η _ 所 7F ′ compared to the conventional centrifugal blower

The curve of Bali dust dust L1, the centrifugal fan shown in figure 7D ^ 1—static pressure curve L2 counties are divided into ten knowledge m < wind set moss fruit and the direction of static pressure becomes smaller under the same air flow. ,, ... There is a problem that the established air volume cannot be obtained under the relocation. This lengthens the diffuser portion 18 to suppress the pressure loss W port ′, but there is a problem that the centrifugal blower becomes large as described above. 200427930 Indications Therefore, the present invention was developed to solve the above problems. Second: Provide a centrifugal blower. Compared with the conventional centrifugal blower, b) reduce the types without reducing the moon dagger. : The invention is a centrifugal blower, which is attached to a vortex-shaped casing with a vane wheel, and the casing is provided with: a discharge passage, which is arranged so that the axial centerline of the discharge port of the passage passes through the axis of the vane wheel, and = passage Near the discharge port, the flow path is curved outward and gradually expanded along the discharge direction of the fluid, which is used to efficiently decelerate the fluid flowing through its inside. According to the above configuration, at the discharge port of the discharge path of the centrifugal blower, a fast-flowing fluid can approach the vicinity of the central portion, and the fluid flowing therein can be efficiently decelerated. Therefore, even if the pipe connected to the discharge passage is bent in the same direction as the direction of rotation of the vane wheel or bent in the opposite direction, the peeling of the fluid is difficult to occur in the far back curved portion, so no large pressure loss occurs. Thereby, the rotation direction of the blade wheel of the centrifugal blower can be changed from the conventional two types to the second type without reducing the performance of the centrifugal blower. In addition, the "deceleration portion" may be formed on both sides of the discharge passage in the same direction as the axial direction of the blade wheel, respectively. Generally, the inner surfaces of both sides of the radial direction of the blade wheel near the discharge opening of the centrifugal blower are formed by> VL 漩涡 M a, ^ you ^ shouting vortex shape, so it does not occur in this part Great loss of will. On the other hand, the inner and outer sides of the discharge path of the centrifugal blower near the two sides of the blade wheel in the axial direction, and the width and size ratio of the discharge port of the centrifugal blower's discharge path in the same direction as the axial direction of the blade wheel are compared The width of the wheel in the same direction is still large. 200427930 Therefore, the distance between the two inner surfaces gradually increases toward the discharge port. Therefore, the fluid flowing in the discharge path may be peeled off from the inner surface of the discharge path, and Λ may cause a large pressure loss. Because of the & ' s present invention, in order to prevent this phenomenon, a :: 6hai portion is provided with a deceleration portion. Thereby, an increase in pressure loss can be prevented, and thus a decrease in performance of the centrifugal fan can be prevented. In addition, it is preferable that the radius of curvature of the f-curved portion of the deceleration portion is 5 to 20% of the inner diameter of the discharge opening of the discharge passage.

According to the above configuration, the fluid flowing in the discharge path of the centrifugal blower is efficiently decelerated in the deceleration section. Thereby, an increase in pressure loss can be prevented, and a decrease in performance of the centrifugal blower can be prevented. In addition, if the radius of curvature of the deceleration portion: the curved portion is less than 5% of the inner diameter of the discharge port of the discharge passage, the deceleration portion is too short to decelerate the fluid efficiently. The radius of curvature of the X-curved portion is larger than the inside of the discharge opening of the discharge path ′, the case becomes larger. [Embodiment] The most deformable form of the invention The following embodiment of the present invention will be described with reference to the figure. ^ Figure 1A [Centrifugal, blower_ is a blade-shaped casing and a blade wheel 2 placed in a vortex chamber u of the casing i. The flow path of the path 113 provided with the discharge path lb 'exits from the vortex chamber 1 & As shown in FIG. 1B, the cross section of the flow path of the vortex chamber la is generally rectangular. The cross section of the flow path gradually turns from the vortex chamber la through the discharge passage to a circular shape, and the discharge port 1C of the discharge passage 1 b becomes circular. . Secondly, the axial centerline 3 of the discharge port lc is related to the axis passing through the blade wheel 10 and the discharge port lc MAM ^ The heart is formed by the centerline in the same direction (hereinafter, the centerline of the private I) CU First, at 1 a, that is, the above-mentioned axial center line [passes through the axis of the blade wheel 2. Thereby, the Huxian M ^ r, Ί] / scorpion, which flows relatively quickly, can be brought close to the central part of the opening 1 c of the centrifugal blower 100.果 ~ 本 ,、 °, even if a matching officer (not shown) connected to the discharge port lc is bent in the same direction as the rotation direction of Ye Yue at μ 4 ± ±, and the attacker is bent in the opposite direction, It is also difficult to find the peeling of the fluid in Continued #, ^ σ bow, σ 卩 points, so to prevent the occurrence of large pressure loss. This can unify the turning direction of the blade wheel 2 from the previous two types into !! Species. As shown in detail, the discharge path ib is the first one. As shown in the figure, "i" is the axial direction of the path 1B of the deceleration part 4 for efficiently decelerating the fluid flowing through the inside thereof, and the width direction of the casing 1 (the same direction as the blade wheel 2: see the symbol in the figure). w.) The inclined portion C ′, ^ formed by a large expansion angle, and the contact portion formed by bending the inclined portion 5 and the decelerating portion 4 with a curvature radius 2R, is the inclined portion 5 Xijie EE — and also inside Occurrence "-The angle is set in advance to avoid the phenomenon of 5 MH body peeling at the site. 忒 The deceleration part 4 is a discharge opening formed in the discharge path lb of the centrifugal supply air 10 ° as shown in Fig. 1B. Chassis near lc] The speed parts of the two sides of the wide production side (the oblique line in Fig. 1B) are shown by the AA line shown in Fig. 1B and the AA line. ^ The direction of the wheel is curved. The right side is symmetrical, and the radius of curvature of the deceleration part 4 of the f-curve 4 is curved outward with a predetermined radius of curvature R, as shown in Figure 2a ~ z tf Figure 11 200427930, X3 — X3 and X4 are viewed from the XI-X1, X2 ~ χ2, and AX4 cross-sections in Figure 1B, and are respectively R1, R2, r, ^, and R4. The relationship between these radii and the right R1 > R2 > R, and R4 > R3 > R. Also gp, # 一 ^ ^ Λ, that is, the position of the cross section is more to the left and right from the center of the discharge port lc (Taxi 4 < & direction vertical direction) away, corresponding to the position of the deceleration section 4 of the deflection section 4 main yak cattle gradually increased. In addition, the left and right ends of the deceleration section 4 are connected to the discharge path 1 ^, 峪 1b The parts 7 other than the deceleration part 4 near the discharge port lc are continuous respectively. Here, the radius of curvature R of the deceleration part 4 is preferably set to 0.05d to 0.2D (D is the discharge port lr of the discharge passage lb. ", the inner branch of 丄 c). The reason is that when the radius of curvature R of the deceleration portion 4 is less than 5% of the inner diameter D of the discharge port ic of the discharge passage lb, the 'deceleration portion 4 is too short to make the fluid efficiently In addition, if the radius of curvature R of the deceleration part 4 is larger than the inner diameter of the discharge port lc by 20% ', the casing 1 becomes larger. In addition, it is preferable to correspond to the radius of curvature R of the deceleration part 4 The height H2 in the axial direction is set to 0.05D to 0.2D. In addition, the bending curve of the deceleration section 4 is actually based on the centrifugal blower. The amount and type of the fluid to be blown are set in advance by experiments, etc. The above-mentioned decelerating section 4 efficiently decelerates the fluid flowing therein, so that the axial distance of the discharge path 1 b necessary for decelerating the fluid can be set. It is smaller than before. On the other hand, if the speed-out portion 4 is not provided near the discharge port 1C, the distance must be increased. More specifically, the axis passing through the blade wheel 2 and the discharge port 1 c can be roughly The height Η of the parallel center line (hereinafter referred to as the second center line) CL2 to the discharge port 1 c, for example, is set to be 1 · 5 times or less the inner diameter D of the discharge port 1 c 12 200427930 According to the above method, this embodiment The casing 1 of the centrifugal blower 100 can be smaller than the conventional blower. In addition, the inner diameter D of the discharge port lc can be made the same as the inner service D1 of the suction port 8 of the casing 1. In this way, the types of pipes connected to these discharge ports can be unified. In addition, although the axial centerline 3 of the discharge port ic of the discharge path 1 b of the casing 1 is made the same as the first centerline cli of the blade wheel 2, the piping connected to the discharge port lc may be seen. The arrangement is such that the axial centerline 3 substantially coincides with the second centerline CL2 of the blade wheel 2. Hereinafter, the present invention will be described in detail based on examples. Example As shown in Figs. 1A to 1C, a centrifugal fan ⑽ is provided with a vortex casing i, and is installed in the casing! The vane wheel 2 inside the vortex chamber u. Chassis! The axial center line 3 of the discharge port lc of the discharge path lb is substantially the same as the vertical center and line CL1 of the blade wheel 2. The emission is near 0 k deceleration section 4. In addition, regarding the setting of the centrifugal blower 100, 戍 UU, relative to the inner diameter D of the discharge port lc of the casing 1, the blade wheel] 々1 heart 4 2 center line CL2 to the discharge port lc H = 0.95D, the radius of curvature R of the decelerating section 4,, ^ ^ I 4 R = 0.07D, and the south degree of the decelerating section 4 Η2 = 0.07I) 28. ^ Expansion angle of the release path lb 5 1 = Comparative Example 1 The difference between the example and Comparative Example 1 is shown in Figure 5. 13 200427930 The axis of the discharge port of the casing 10 and the direction of the vehicle from the discharge port 10a The centerline 12 is separated from the center line CL1 in the same direction (hereinafter, the vertical centerline) CL1 by the vehicle passing through the blade wheel 11 1 〇a. The distance is parallel to the case J. The distance is parallel. The inner diameter D2 (approximately 0.85D) of the above-mentioned decelerated discharge port 10a has a height H3 = 0.92D2 from the second center line ⑴ of the blade wheel u to the discharge port ⑽. Others are the same as the embodiment. Comparative Example 2 Comparing Example 2 ′ As shown in FIG. 7B, it is different from the example in that it is not provided

The speed reduction unit 4 described above. Therefore, as shown by the two-point chain line in FIG. 1C, the expansion angle 51 of the above-mentioned discharge passage 1b is from 28 to 28. Expansion to 30. . Others are the same as those of the embodiment. Characteristics Using the centrifugal blowers of the above Examples, Comparative Examples, and Comparative Examples 2, the performance of the centrifugal blowers was measured, and the evaluation was performed. The results are shown in Fig. 3. In the figure, symbols L1 and L2 are performance curves corresponding to Comparative Example ^, Comparative Example 2, and Example, respectively.

As shown in Fig. 3, if the comparison example (performance curve L1) is compared with the example (performance curve L3), it is understood that the performance of the example is not significantly lower than that of the comparison example. From this, it can be said that the example has the same performance as the comparative example 1. In addition, as described above, the centrifugal blower of the present embodiment does not need to be prepared in many types corresponding to the arrangement of the piping connected to the discharge port 10a as in the heart blower of Comparative Example 1. Specifically, as shown in Figs. 4A to 4c, the type of the finished product of the centrifugal blower in the present embodiment can be reduced from six to three in the past. 14 200427930 On the other hand, Comparative Example 2 can reduce the number of centrifugal blowers and fans similar to the examples, but as shown in Figure 3, the performance of the centrifugal blowers is reduced. In particular, in the high air volume range of the centrifugal blower, the static pressure was significantly lower than that of the embodiment (performance curve L3) 'and comparative example 2 (performance curve L2), and a large pressure loss occurred. The reason is that the deceleration section 4 is not provided in the above-mentioned discharge passage lb, so the fluid flowing therein is not sufficiently decelerated, and the expansion angle 51 of the discharge passage ib is from 28. Expansion to 30. Therefore, the internal surface of the discharge passage is prone to fluid peeling and the like. From this, it can be seen that the provision of the speed reduction section 4 in the discharge passage lb of the centrifugal blower is effective for reducing the pressure loss. _ In addition, the above-mentioned embodiment is an example, and various changes can be made without departing from the scope of the present invention, and the present invention is not limited to the above-mentioned embodiment. Industrial Applicability ^ Possibility The centrifugal blower according to the present invention can reduce the variety without reducing performance compared to the conventional centrifugal blower. As a result, the centrifugal fan according to the present invention has good productivity and easy inventory management, and is a useful centrifugal fan. g [Schematic description] (I) Schematic part Fig. 1A is a longitudinal sectional view showing a basic configuration example of a centrifugal fan according to an embodiment of the present invention. Figure 1β is a plan view showing a basic configuration example of a centrifugal fan according to an embodiment of the present invention. earth

Figure 1C is a partial cross-sectional view of line A 15 200427930-A of the discharge path of the centrifugal blower shown in Figure 1B. Figure 2A is a partial cross-sectional view taken along line XI-XI in Figure 1B. Figure 2B is a partial cross-sectional view taken along line X2-X2 in Figure 1B. Fig. 2C is a partial cross-sectional view taken along line A- -A in Fig. 1B. 〇 Fig. 2D is a cross-sectional view taken along line X3-X3 in Fig. 1B. Fig. 2E is a partial cross-section of line X4-X4 in Fig. 1B. Fig. 0 and Fig. 3 'are graphs showing the relationship between the air volume and static pressure of the centrifugal blower.

Fig. 4A is a front view of a finished product of a centrifugal blower according to an embodiment of the present invention, and shows a configuration example in a case where the discharge direction of the fluid is vertically above. Fig. 4B is a front view of a finished product of a centrifugal blower according to an embodiment of the present invention, and shows a configuration example in a case where the discharge direction of the fluid is right. Fig. 4C is a front view of a finished product of a centrifugal blower according to an embodiment of the present invention, showing a configuration example in a case where the discharge direction of the fluid is left

Into a longitudinal section. Fig. 6A 'is a longitudinal sectional view of a finished product of a conventional centrifugal blower, showing a configuration example in a case where the discharge direction of the fluid is vertically above, and the rotation direction of the blade wheel is wound to the left. -Figure 6B is a vertical cross-sectional view of the finished product of the Baizhi centrifugal blower. It shows a configuration example of a case where the discharge direction of the fluid is vertically above and the rotation direction of the vane wheel is 2004 right. —Figure 6C is a longitudinal sectional view of the finished product of the Baizhi centrifugal blower, showing a configuration example in a case where the discharge direction of the fluid is left and the rotation direction of the blade wheel is good. Fig. 6D shows the longitudinal wearing surface of the finished product of the conventional centrifugal blower, showing the configuration example in the case where the discharge direction of the fluid is to the left and the rotation direction of the blade wheel is toward. Fig. 6E 'is a longitudinal sectional view of a finished product of a conventional centrifugal blower, and shows a configuration example in a case where the discharge direction of the fluid is right and the rotation direction of the blade wheel is leftward. Fig. 6F is a longitudinal sectional view of a finished product of a conventional centrifugal blower, showing a configuration example in a case where the discharge direction of the fluid is right, and the rotation direction of the blade wheel is rightward. Figure 7A is the method of moving the casing of the conventional centrifugal blower shown in Figure 5 to the axial centerline of the discharge port near the axis line passing through the axis of the blade wheel and in the same direction as the axis of the discharge: Arranged on the abutment and installed at the exhaust port to elbow joints to form another—a longitudinal section view of a centrifugal blower. Fig. 7B is the center line of the conventional centrifugal blower shown in Fig. 5 with the discharge port from the center of Shaw, close to the light line passing through the vane wheel and in the same direction as the axis of the discharge port. The method is arranged on the abutment, and a longitudinal section view of another centrifugal blower formed by cutting out a part near the discharge opening of the casing. Fig. 8 is a graph showing the relationship between the air volume and the static pressure of a conventional centrifugal blower. 17 200427930 (II) Symbols for components 1 Enclosure la Rotating chamber lb Drainage path 1 c Drainage port 2 Vane wheel 3 Axial centerline 4 Deceleration part 5 Inclined part 6 Contact position 7 Near the discharge port lc of the discharge path lb Parts other than the deceleration part 4 10 Case 10a Discharge port 10b Newly formed discharge port 11 Blade wheel 12 Discharge port 1 Axial centerline of Oa 12a Discharge port 1 Axial centerline of Ob 13 Discharge direction of fluid 14 Abutment 15 Motor 16 Elbow joint 16a Newly formed exhaust port 17 Part of the casing 10 near the exhaust port 10a 18 200427930 18 Diffuser section 100 Centrifugal blower 200 Known centrifugal blower 201 Known centrifugal blower CL1 1st centerline CL2 2nd Center line

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Claims (1)

200427930 Scope of patent application: 1. A centrifugal blower is attached to a vortex casing with a blade wheel inside; it is characterized in that the casing is provided with: a discharge channel, which is set as the axial center of the discharge port of the channel The line passes through the axis of the blade wheel; and a deceleration portion is formed near the discharge opening of the discharge path, and its flow path is curved outward and gradually expands along the discharge direction of the fluid, so as to efficiently decelerate the fluid flowing through the inside thereof. 2. The centrifugal blower according to item 1 of the scope of patent application, wherein the decelerating portions ′ are formed near the discharge opening of the discharge passage, and are formed on both sides in the same direction as the axial direction of the blade wheel. 3. If the centrifugal blower in item 1 of the scope of patent application, the radius of curvature of the test curve part of the quenching speed σ 卩 is 5 ~ 20% of the inner diameter of the discharge opening of the discharge path. The centrifugal blower of item 2, wherein the curvature radius of the curved portion of the deceleration part is 5 to 20% of the inner diameter of the discharge opening of the discharge passage. Pick up, schema: as next page 20