TWI354735B - - Google Patents

Description

1^54735 IX. Description of the Invention: [Technical Field of the Invention] The present invention relates to a sirocco fan and a (4) air conditioner which uses the fan in particular for the purpose of making a sound for reducing the sound generated. The sirocco fan and the [prior art] Since the past, there has been a multi-blade centrifugation of the seed system, and it is possible to blow a wide strip of wind to the air-conditioned object area. The cylinder I: the fan is often used in the interior of the air-conditioning apparatus. Second Xiluojing cleaning machine and so on. The sub-dehumidifier and the empty plate are arranged on the circumference, and the 敕俨士间& 支, the Tian Chang's blade suction port and the blow-out/round-shaped fan are housed in the formed and human out-out shape. Composed of shells. However, the city mouth draws air into the inner sputum, count... ～ fan can suck in from the N port! 5 and blew the outlet side to the air hu #4_ & . The object area is blown out as the kind of Syracuse fan 'proposal'. A plurality of township blade centrifugal fans connected to each other by space along the blade fan, including: a wind axe... The outer plurality of ^ 4 fan units, h the number of eve leaves centrifugal wind type wind house two, the outer casing is formed to be used for the plurality of multi-blade centrifugal eight fans The β ^ blowout flow path 'the common path of the door of the two-blade centrifugal fan unit of the common multi-blade centrifugal fan unit is blown by the flow path' (for example, refer to the patent document 丨). Patent Document 1: Special Kaiping 1 1 - 324984 π, ^ 7^8 Figure) . 4唬 Bulletin (5th Gong, No.

2148-9915-PF 5 1354735 [Problem to be Solved by the Invention] In the conventional multi-blade fan, the loss coefficient at the operating point is small, and the fan is moved closer to the open side than the unstable region. : The problem that the noise generated when the air volume is large and the volume is increased. That is, in this kind of siro fan, the air volume is supplied in a quantitative manner.

At this time, the sound generated from the fan becomes large, and becomes noise, and the object area is transmitted, making the user feel uncomfortable. Further, when the predetermined beer sound value is lowered, the amount of blown air from the sirocco fan is changed, and if the blown air volume is increased, the noise value is increased, and it is difficult to obtain an appropriate balance between the blown air volume and the sound. X, in the case where the fan width is narrow and the loss coefficient is small, the noise is made small, and there is a problem that the fan diameter must be excessively increased. Further, in the case where such a sirocco fan is used for an air conditioner, if the fan width is narrow, when the heat exchanger is located on the downstream side of the fan, the speed distribution in the width direction of the heat exchanger becomes uneven, and the heat exchanger The thermal conductivity is reduced, and the power consumption of the compressor is also increased. Moreover, there is also a problem that the relationship between the loss coefficient and the fan width is not clear. The present invention has been made in an effort to solve the above problems, and an object of the invention is to provide a sirocco fan and an air conditioner using the same, and the fan is configured to reduce sound generated when a predetermined amount of blown air is supplied. [Means for Solving the Problem] The sirocco fan of the present invention includes: a volute casing having a suction port for taking in air, a blow port for blowing air, and a wind from the suction port to the blow port. a fan; the fan is housed in the volute casing, and is driven by the rotation of 2148-9915-PF 6 1354735 to take in air from the suction port and blow air from the air outlet; and the bell mouth is mounted on the The suction port of the volute casing; characterized in that: the suction port is located on an extension line of the center of rotation of the fan, and the ventilation resistance formed in the air path of the two sides of the volute casing is P [ Pa], the amount of air taken in from the suction port is Q [mVmin], the

The width of the fan in the direction of the rotation axis is L [mm], k is constant, the vortex case has a twist of H = 246 k [mm], and P/Q2 is the loss factor f [pa/(m3/min) 2]. , in the range of 0. 1 S k4 f 〇. 4, made f(k4 F ) = 〇. 34947(k4 f )2 - I - 〇554(k4 ^ ) + ι, 8 , 〇. 75f (k4 ^ L/HS f (k4 f ). The sirocco fan of the present invention includes: a volute casing having a suction port 1 for taking in air to blow out air, and from the suction port to the 忒π person The outlet air passage and the fan are housed in the volute casing, and the air is taken from the suction port A by blowing and the air is blown from the air outlet; and the bell mouth is attached to the worm The suction port of the casing; characterized in that: the suction resistance is located on an extension line of the center of rotation of the fan, and is formed on one side of the volute casing, and the ventilation resistance in the air passage is P[Pa ], the amount of air taken in from the suction port is Q [mVmin], the visibility of the fan in the direction of the axis of rotation is $ L [mm], and k is a constant 'the height of the volute case is H = 246 k [mm] , P/q2 is the loss coefficient f [pa/(m3/min) 2] In the case of 〇. 1 - k4 t客〇·4, make g(k4 ^)-1. 3 9788(k4 ξ )2- 2. ll〇8(k4 ^) + 1.8- 1. 5g( K4 ^ ) ^ L/HS 2g(k4 f ). Further, the air conditioner of the present invention is characterized in that the above-mentioned west is used

2148-9915-PF 7 1354735 Roco fan. [Effect of the Invention] According to the sirocco fan of the present invention, the width of the fan is determined according to a predetermined mathematical formula so that the operating point of the fan is located, and the air volume and noise of the air can be equalized, so that the fan can be effectively reduced. The sound produced when a certain amount of air is blown out. [Embodiment] Hereinafter, embodiments of the present invention will be described based on the drawings. (First Embodiment) Fig. 1 is a perspective view of a sirocco fan 1 according to a first embodiment of the present invention. A perspective perspective view of the inside of the cymbal. Fig. 2 is a perspective view showing the overall shape of the fan. Figure 3 is a schematic longitudinal section of the structure of a solid V' 衣西西洛可可11. According to the second low-fidelity i-Fig. 3, the overall structure of the sirocco fan 100 is illustrated. This Xiluo J Fan 10 is used in an internal air conditioner, a dehumidifier, an air, a moon cleaner, etc., which constitutes an air conditioner of an air conditioner or a dehumidifier. In addition, in the following drawings, the relationship between the dimensions of the respective constituent members and the actual ones is included in the following drawings. As shown in Fig. 1, Siro Khanhiko 1Λ The fan 100 is composed of the following members, and the fan 1' is formed by arranging a plurality of elongated 柘 柘 茱 茱 茱 业 业 而 而 而 而 而 排列 , , , , , , , , , , , · · · · · · · · 蜗 蜗 蜗In the inner element, the wind path; and the bell mouth 3, the center of rotation of the winds (hereinafter referred to as the rotating shaft only), and the two sides of the line are installed. The fan "the center of rotation' attracts air by turning, And blow out the air.

2148-9915-PF 8 The volute casing 2 is composed of the following components: 构件 0. The suction port 2a is formed on the rotating shaft, and the opening 丄 blowing port 2b is blown out from the suction port to the target area. "The air to be sucked; and the air passage 2c are formed in a spiral shape (curved shape) toward the circumferential direction of the rotation of the fan 1, and the suction port 2a and the outlet bell 3 are formed by machining openings, and are attached to the crucible. The suction port 2a' of the casing 2 is formed to increase the speed of the air collecting towel taken from the suction σ 2a and supply it to the fan 1. The fan i can constitute a fan diameter D of, for example, "92 mm", and a width dimension l of, for example, 15 Å to 255. The volute case 2 can be formed by 246 mm, for example, by a 4Q piece. The shape of the bell mouth 3 can be determined, for example, according to the length of the fan diameter D, and Fig. 4 is a graph showing the p-Q characteristics and Ks-q characteristics of the sirocco fan. According to Fig. 4, Explain the P-q special f and KS-Q characteristics of the Silo fan 100. Here, P denotes static l[Pa], Q denotes air volume [m /min] 'Ks is not better than noise [dB]. Ks is calculated according to the mathematical formula Ks=SPL—10Μ. (P.Q2 5). In addition, SPL indicates the noise value, which is used along the center of the bell mouth 3 attached to the suction port 2a of the scroll case 2. On the axis of the rotation, the distance from the _lm heart is measured, and the value of the noise generated from the sirocco fan 100 is measured. Further, the black circle mark indicates the p-Q characteristic' and the blank circle mark indicates the Ks-Q characteristic. In addition (1)~ (7) indicates the operating point. P-Q characteristic indicates the static pressure P (left vertical axis) and air volume Q of the ventilation resistance in the state where the fan speed is fixed. The relationship of the axis. As shown in the black circle mark of the 4 2148-9915-PF 9 1354735, the static and the gentleman ^. ^ The quieter the smaller the wind, the wind is more likely to flow, and the static pressure is larger. In the wind road 2c wind Yu cone, Zhang t / 0, θ L cut difficult to move L. That is, at the operating point (3), easy to get the air volume, hot point π (1) at the operating point is difficult to serve air volume. Therefore, the smaller the static pressure is, the larger the air volume is, and the smaller the static air volume is, the smaller the air volume is. In addition, in the following description, the static pressure and the low wind side are referred to as the closing side (the upper left side of the figure), and the static is low. The high air volume side is called the open side (the lower right side of the figure). However, as shown in Fig. 4, there is a localized area where the air volume becomes smaller and the static frequency becomes smaller. The surging area (the area enclosed by the dotted line shown in Fig. 4). x ; In the unstable area, the flow of air in the wind path 2c is liable to change. The heart, that is, the area where the unstable area is highly likely due to the instability of the air flow and becomes the cause of the abnormal sound. In addition, the noise than the noise Ks (right vertical axis) is as shown in Fig. 4 When the mark becomes larger as shown, the wind amount Q increases. This ratio "j Li Wen eight this product than Ks this sound system and taking into account the static pressure P of the air flow rate Q noise value. Fig. 5 shows the L of the sirocco fan. A graph of the relationship between the claw and the loss factor ^. According to Fig. 5, the sirocco fan j 〇 〇 l is illustrated. /^ : The relationship of the loss factor. In the fifth item, the height of the snail shell is fixed to 246, and the fan width dimension L() is changed between 15 and 5, and the loss coefficient is used to call [3/1^) 2]. The specific noise "becomes the most, the width dimension L., which represents the relationship between WH and the loss coefficient ^. In Fig. 5, the vertical axis represents Ld/h. The horizontal axis represents the loss coefficient shovel. Loss factor f D = pD /QD2 'In the p to Q characteristics shown in Fig. 4, the loss coefficient I is shown. The larger the closer to the closing side, the smaller the loss coefficient t. The smaller the closer to the open side, the more the loss coefficient is based on the action point described later. (p Q) The value of the position of 2148-9915-PF 10. Further, L(>/h. indicates the ratio of the case where the height of the volute case is fixed, and the width dimension L is changed. It can be seen from Fig. 5 that according to the loss coefficient, it is known that the width dimension which becomes smaller than the noise Ks is changed, that is, the open side where the smaller the gain coefficient is smaller than the noise Ks becomes the I degree dimension L of the sentence J. The longer the length is. Therefore, from Figure 5, in the case where the loss factor 2 » is in the range of 0. 1 $ $ $ 〇 _ 4, let f ( f ) = 〇. 34947 L〇/H〇 = f(g), ratio The sound Ks becomes the most _ in addition f(f)-〇.34947f2-i.〇554m.8 is the equation calculated from the graph shown in Fig. 5. Secondly, the noise ratio f Ks due to the loss coefficient and the width dimension is explained. L. Reasons for the change. Fig. 6 is a graph showing the PQ characteristics and the Ks-Q characteristics of the sirloin of the case where the width dimension L is 230 or 30 〇 mm and the action point A is passed. Further, the black circular mark indicates the P-Q characteristic of the width dimension 〇 23 ,, and the blank circle mark indicates the width dimension L. The P-Q characteristic of the 3 〇〇 凊 condition 'black triangle mark indicates The Ks-main u· _ ^ S y characteristic in the case where the width dimension L 〇 is 23 〇 mm, and the blank triangle mark indicates the Ks-Q characteristic in the case where the width dimension ^ is 300 _. Further, the action point explained here It is determined according to the design air volume of single %, and the design static pressure (ventilation resistance of the heat exchanger, or the air path of the unit, the ventilation resistance of the air passage of the pipe, the ventilation resistance of the filter, etc.). When β is 23 〇mm or 300 ram, the width is known when the P-Q characteristic of the operating point A is compared. L. inch longer 300mm, female given region do not move to Q characteristic pattern of p- lower right (open

2148-9915-PF 1354735 side), and: near action point A. It is known from the Bu Q special diagram shown in Fig. 6 that the action point that becomes smaller than the arm sound Ks is located in the unstable position = two denier's action point is located in the unstable area or the unstable area:: - The movement becomes unstable, occurs Reverse inhalation or abnormal sound, = large. Therefore, in the case where the steady flow is surely formed: the operating point is located closer to the open side than the unstable area. That is, for a certain operating point (p, Q), the volume Q characteristic map of the fan is gradually moved to the lower right side of the unstable area. At this time, the action is in the second, or the slap in the mouth: the // figure is large. In the present invention, the field of the opening is made, the static change variable becomes larger, and the rest is unstable... the action point 'by making the capacity of the fan close, so that the action point and the instability are made here, a The volume becomes louder, larger, or widens the width of the fan. The height of the direct control variable can be too high. In the present invention, it is possible to:: = diameter: large, the height of the single unit becomes too high, and the width of the fan & === is not used to make the action point and the square of the unstable area of the unstable area, Less restrictions, and can reduce the sound. Fig. 7 showing the optimum early element is a graph showing the relationship of the position of each blade of the fan 2. According to "the air volume between the blades and the fan of the fan 100! Each leaflet's figure shows the relationship between the positions of the West Plate. In this first blade air volume and blade 7 diagram, the vertical axis represents each leaf

2148-9915-PF 12 1354735 The air flow between the blades (mVinin), and the horizontal axis represents the position of the blade. Further, in Fig. 7, the black circular mark indicates the relationship between the air volume between the blades of each blade of the blade and the position of the blade plate at the operating point, and the blank diamond symbol indicates each blade blade at the operating point (2). The relationship between the air volume between the blades and the position of the blade plate, the black triangle symbol indicates the relationship between the air volume between the blades of each blade plate at the operating point (3) and the position of the blade plate.

1. The air volume between the blades of the female slab of the wind collar is positively indicating the flow of wind from the inner peripheral side of the blade (blade plate) on the outer peripheral side, and negatively indicating the wind from the outer peripheral side of the blade ^ Side ^ ^ Expressed by the short needle of the clock:: Jin: The leaf: the position of the plate, the position of the blade plate is replaced by the position of the short needle of the clock of the knife. Further, the operating point (1) and the point (3) shown in the second figure indicate the same operating point as the operating point (1) to the operating point shown in the second drawing. As shown in Fig. 7, it is found that the position of the blade plate is located nearby. The larger the air volume between the blades on the open side, the smaller the air volume between the blades. Also, it is known that at 9:30 to U. In the area, the air volume between the blades did not appear significant, except 77. The left armor set the blade between the blades; the case of "the number of plates is 40" i = 1, the value of the hungry, the fan input value W, roughly as shown below; J 曰 (2) Formula is established. Formula (1) and Equation (1) SPLd 1〇·log.6 Equation (2) w〇c2 Qi3 Noise value SPL and, therefore, the air volume between the blades Qi The more uniform the distribution sentence 2148-99is-pr 13 1354735 The smaller the fan input value w is, that is, as shown in Fig. 4, in the case of the action point (1) close to the unstable zone, the distribution of the air volume Qi between the blades is uniform. Therefore, the specific noise Ks becomes the minimum value. Here, as shown above, the closer the action point is to the unstable region, the closer to h/IU=f(p), although d becomes smaller than the noise Ks, but exceeds f ( f), the action point is located in the unstable area, which is worse than the noise Ks. On the other hand, the action point is farther away from the open side than the non-female area, at the tongue of the shell (2bl in Fig. 3) Or the area where the distance between the bell mouth and the fan is short, because the static change becomes large, it is easy to generate abnormal sound. Therefore, let 00&n;nS 1 ' L〇/He= nxf( I:.), in the case where the loss coefficient is small (the air volume is large and the ventilation resistance is small), that is, in the range of 〇1' $ 4 0.4, the minimum η of the abnormal sound is not generated. It is 5. Therefore, in the case where the loss-of-loss coefficient is small (the air volume is large and the ventilation resistance is small), that is, in the range of 0.1^60.4, if 〇75f (D^L./^f (b), it can be formed. It is smaller than the arm sound Ks and does not cause the flow of the different f sounds. "In the above description, the case where the volute case height Hd = 246 is described, and the case where the size of the snail shape is generalized will be described. k is a constant, H kH 〇 L-kL 〇, D = kD. In the case of dimensional change, the self-similarity rule, about P & Q, the mathematical formula shown below (paragraphs (3) and (4)) Established here. N series speed. Equation (3) P = P〇(D/D〇)2(N/N〇)2 Equation (4) Q = Qd(D/D〇3(N/N .) 攸 Equations (3) and (4), eliminate N/n. After finishing, get the formula (5).

2148-9915-PF 14 1354735 Equation (5) P〇/Q〇2= p/q2(d/d.)3 The equation (8) is obtained by substituting ^ Ρ / (ΤΉΙ) β for the equation (5). Equation (6) f〇 = k4f Using Equation (6) and H = kH〇, L=kL❶, 0.1S f can be used. Guest 0.4 is generalized into o.isvi; each 〇 4, O.HfCfOsLo/HdfCf. Generalized into 〇75f (k $ L/HSf(k4f). - that is, in the case where the fan 1 is used for an air conditioner including a heat exchange write on the downstream side of the fan', the condition with a small loss coefficient (large air flow resistance) In the case of "small", the width of the fan is widened, and since the noise is reduced, and the velocity distribution in the width direction of the heat exchanger is nearly uniform, the power consumption of the compressor can be prevented from being unnecessarily increased. The case where the fan 100 is a single suction type. 2. 1108(k4^ ) + 1.8^ 1. 5g(k4F )^L/H^ 2g(k^ In the case where the sirocco fan 100 is a single suction type, The range 'by making, and - can be raised: into a unit that is smaller than the noise Ks and does not produce abnormal sounds. v In the above description, although the siro fan 1 is single, but for the siro fan (10) The operation point of the unit mounted on the unit of the air conditioner, such as the air conditioner, can also be the same:: In this case, 'the rotation speed N| of the unit and the air volume h of the unit, and then the p- of the fan 1GG alone Q characteristics, use the speed & and the air volume q " to replace the above L with l/2, replace Q It can be Q/2. However, if f{ P/(Q/2" } is set, then g(k彳)=139? ;2 ).

2148-9915-PF 15 Static pressure Pi can be used. Here, in the case where the air volume A0 of the unit-mounted fan/one fan is set, J winds and static pressures are set, and the loss situation is obtained, which is handsome 7::=^ 'L/HSf("), and It can form a ratio of abundance Ks : 5f (k Β in the case of the sirocco fan _ is a single-inhalation type, by making 匕 (four) 乂). / The flow is smaller and stable than the noise Ks. (1), and the shape is shown in Fig. 8 is a vertical sectional view of the mouthpiece 3. Fig. 9 is a schematic sectional view showing the bell mouth 3. Figure... The graph indicates the area without step: = the rms value of the pressure change is the value of the static value of the boring tool on the wall. The enlarged part of the section has the section of the section α on the wall surface. Enlarge the area of the rms value of the κ static i parent's motion] 孜 big picture. According to Fig. 8 - the figure in which the step is formed in the volute casing 2, the side of the bell-shaped casing 2 is mounted on the side of the Z-shaped side to form a bell mouth. The characteristics of the bell mouth 3 of 1 inch. ' -- The longitudinal section structure of the bell mouth 3 shown in Fig. 8, the end point of the fan 1〇〇 side (the smallest at the front end 3: point 2 A (becoming a private interest. 丨) and points) For point A and

I becomes the center of the mouth 3 and the end point of the point A (the point at the maximum opening of the bell mouth 3), the other is the center and the point of the remaining mouth 3: the point is the point B and the direction The straight line drawn and the parent point from the point B to the fan 1 B' to the direction of the fan 1 are point C, and the point is set. The intersection of the straight line of the thrust and the side of the volute casing 2 is

2148-9915-PF 16 1354735 Point c', line AA, and fan! The intersection of the extension of the shaft is a point, which is explained. That is, at the time of BC > 0, the bell mouth 3 is attached so that the step is formed on the side of the scroll case 2, and BC = 0 ef to mount the mouthpiece 3 on the side of the worm (4) 2 since no step is formed. In addition, 'the length of BC when BC>0 is 5 [following], and the nns value of the static pressure variation of the region is about 0 [Pa]. In the figure 9 of the figure u, as shown in Fig. 8 The mounting method of the nozzle 3 compares and shows the static pressure fluctuation of the step formed on the side surface of the scroll case 2 and the static pressure fluctuation of the case where the * segment difference is not formed on the side surface of the dome case 2. Hereinafter, the rms value of the static pressure variation is shown. Formula (7) Ps(t)= ps + ps,=(t) Equation (8) rms value={ ( ς ps, (t)2) }0 5 Here, ps represents the time average , ps' (t) indicates the variation value of the static pressure. The larger the rms value of the static pressure fluctuation on the wall surface, the greater the noise generated from the wall surface. From the first map and the u-th diagram, the snail shape is obtained. The static pressure variation of the side surface shape φ of the shell 2 is smaller than that of the static side of the volute casing 2, so that the noise generated on the side of the volute casing 2 can reduce the noise generated. 12 is a longitudinal sectional view showing a schematic sectional structure of a sirocco fan 1 , and a 13 is a perspective perspective view showing a perspective view of a sirocco fan. According to FIG. 12 and FIG. The area where the rms value of the static pressure change of the sirocco fan is large. Also, in Fig. 12, the bending from the wind path of the volute casing 2 constituting the siro fan 1 to the blowout port 2b The portion 'will be closest to the fan! The outer peripheral portion is illustrated as the tongue 4.

2148-9915-PF 17 plane and ... = point A, point 0 and point A shown in Fig. 8, the point is shown as point D, and the distance between the two and the fan 1 is minimized. The center is illustrated from the nearest point as the reverse direction 65 of the fan 1 whose position is /. The point where the iiS_ 'point F' is located at the point of the fan 1 which is located at the point F, is shown as the point G, and is located at the point 4 in the direction of the click. _ _ & The rotation of the fan 1 from point F is not the point H, and is located 180 degrees from the point ^ in the direction of the point. The point is shown as a point. In the case of such a derogatory area, the complex y* jr pressure change M g brother pays to know that in the area of the Silo fan 1G0 static = moving (four) value, the connection point H, the point f and the point roughly circular arc HFG region. Therefore, π is in the long-term production Ax h 匕δ and in the line BC of the arc HFG..., when the length of the circular arc HIG (connection point ^ point) and the round line segment BC of the point G is ¥, at L/HSfU) Or the price of ::): If it is the bell mouth 3 of mu, the (4) value of the static pressure change can be made small, and the noise can be made smaller. As shown in Fig. 10 and Fig. 11, in the case where no step is formed on the side of the volute casing 2, the value of the static pressure variation in the region of the arc muscle is the largest, and the step on the side of the volute casing 2 is formed. In the case, the rms value of the static pressure fluctuation in the area of the circular sail is maximum below the center. That is, by forming a step on the side surface of the volute casing 2, the sound of the mouthpiece 3 as a sound source is lowered. The reason is considered to be because the distance from the fan i is only increased by the amount of the step, that is, the length of the line BC, and the static pressure fluctuation caused by the rotation of the fan is suppressed. Fig. 14 is a graph showing the P~Q characteristics of the sirocco fan ι〇〇 2148-9915-PF 18 1354735 as it passes through the operating point B. According to Fig. 14, the p-Q characteristic of the case where the sirocco fan 形成 passing through the side of the volute casing 2 is passed, and the sirocco fan 100 passing through the point on the side of the volute casing 2 is not shown. P-Q characteristics of the case of B. In Fig. 14, the black circular mark indicates the p_Q characteristic of the sirocco fan 形成 which forms a step on the side of the volute casing 2, and the blank circular mark indicates that the sirocco is not formed on the side of the volute casing 2 The p-q characteristic of the fan 1〇〇. Further, in Fig. 14, the vertical axis represents the static pressure p [Pa], and the horizontal axis represents the air volume Q [m3 / min]. As shown in Fig. 14 'When the volute shell 2 forms a step difference, the sirocco fan 1 〇 0 and the snail shell 1 side of the snail shell 2 do not form a step difference, the sirocco fan 1 〇〇 relatively unstable area, I learned that the former is on the open side. In the case where a sirocco fan 1 having a step formed on the side surface of the scroll case 2 is mounted on a unit such as an air conditioner or a dehumidifier or an air cleaner, the siro fan 100 may not be possible due to the size limitation of the unit. The width of the width becomes longer. In other words, since the width dimension is short, the Η乍 Η乍 点 点 点 胁 胁 胁 胁 胁 胁 胁 胁 ' 因为 因为 因为 因为 因为 因为 因为 因为 因为 因为 因为 因为 因为 因为 因为 因为 因为 因为 因为 因为 因为 因为 因为 因为 因为 因为 因为 因为 因为 因为 因为 因为A plan view showing a schematic overall structure of a suspended indoor unit 110 carrying a sirocco fan. Fig. 16 is a cross-sectional view showing a longitudinal sectional structure of a suspended indoor unit 11 。. According to Figs. 15 and 16 In the case of the sirocco fan which is formed on the side of the volute casing 2, the static pressure diagram of the case where it is mounted on the suspended indoor unit 110 is loaded with two sets of sirocco fans, and the change is made. Fig. 15 shows the case where the suction space 5 is formed on the side surfaces of the respective width directions. In Fig. 16, the flow of air of 2148-9915-PF 19 1354735 is indicated by an arrow. The west of the step is formed on the side of the scroll case 2. When the Luoke fan 1 is mounted on the suspended indoor unit 110, the suction space 5 is reduced by the amount of the step difference due to the step formed, and there is a case where the noise is increased. Zone with large rms value of static pressure variation The field system arc hfg, in other areas, the static pressure fluctuation irms value is less affected by the distance from the fan. Therefore, if the sirocco fan 100 that forms a step in the arc HFG region is placed in the suspended room The machine 110 can make the step difference on the downstream side of the suction port 2a, and can reduce the amount of decrease in the suction space 5. Fig. 17 is a table showing the noise value of the suspended indoor unit 11 。. The noise value generated from the suspended indoor unit i丨〇 of the sirocco fan 1 形成 which is formed on the side of the volute casing 2, and the sirocco fan which is not formed on the side of the volute casing 2 The noise value generated by the suspended indoor unit 110. In addition, it is assumed that the step is formed in the area of the circular arc HFG, and each represents a noise value in the case where the blown air volume is 16 m3/min. As shown in the figure, when the air volume is 16 m3/min, the noise value of the step in the area of the arc HFG is 42.4 [dB], and the noise value of the step is not formed in the area of the arc HFG. [dB]. So 'by making a step in the area of the arc HFG, the noise can be made The sound value is reduced. From the above, by providing a step in the area of the circular arc HFG, the decrease in the suction space 5 is suppressed, and the arm sound value can be made small. Fig. 18 is a second embodiment of the present invention. A schematic structural view of a schematic structure of an air conditioner 丄 5〇 2148-9915-PF 20 1354735 according to the embodiment. The structure of the air conditioner 150 will be described based on Fig. 18. The air conditioner ι5 is loaded with the Siro of the first embodiment. The sirocco fan 1 is used to mount an indoor unit (indoor unit) constituting the air conditioner 15 in the vicinity of the heat exchanger. In addition, in the second embodiment, the main description and the above are described. In the first embodiment, the same portions as those in the first embodiment are denoted by the same reference numerals and will not be described. The air conditioner (150) is configured by sequentially connecting the condensation heat exchanger (152), the expansion device (153), and the evaporative heat exchanger (154) with a refrigerant pipe. Here, the sirocco fan 1 第 of the first embodiment is provided for the indoor unit in which the condensing heat exchanger 152 or the condensing heat exchanger 154 is provided. That is, the sirocco fan 100 is disposed in the vicinity of the condensing heat exchanger 152 or the evaporative heat exchanger 154 provided in the indoor unit, and has a function of supplying air to the condensing heat exchanger 152 or the evaporative heat exchanger 154. . The compressor 151 sucks in the refrigerant flowing through the refrigerant pipe, and compresses the refrigerant to a high temperature and a high pressure state. The condensing heat exchanger 15 2 is a heat exchange between air and refrigerant to cause the refrigerant to condense or liquefy. The throttle device 1 53 depressurizes the refrigerant to expand the person. The evaporative heat exchanger 154 is a type in which heat is exchanged between air and a refrigerant to evaporate or vaporize the refrigerant. By mounting the sirocco fan 1 of the first embodiment to the indoor unit in which the condensing heat exchanger 152 or the evaporative heat exchanger 154 is installed in the air conditioner 150, the noise transmitted to the room can be reduced. . Here, the operation of the air conditioner 150 will be briefly described. The arrow ' shown in Fig. 8' indicates the flow of the refrigerant. The compressor 151 is compressed to become a high 2148-9915-PF 21 1354735 shirt, and the refrigerant gas of the south pressure flows into the condensing heat exchanger 152. In the condensing heat exchanger 152, the refrigerant and the air exchange heat by condensation, and become a liquid refrigerant or a gas-liquid two-phase refrigerant which is low in pressure and pressure. The refrigerant flowing out of the condensing heat exchanger 152 is then depressurized into a low-temperature, low-pressure liquid refrigerant or a gas-liquid two-phase refrigerant at the expansion device 丨5 3, and then flows into the evaporative heat exchanger 154. The evaporation wire exchanges the stomach 154, and the refrigerant and the wire are heat-exchanged to evaporate into a high-temperature, low-temperature refrigerant gas, which is then sucked by the retort 151. When the greenhouse is in operation, the evaporative heat exchanger 154 is mounted on the indoor unit. In the case where the loss coefficient is small and the fan width is wide, the velocity distribution in the wide production direction of the heat exchanger is nearly uniform, and the heat transfer area of the heat exchanger can be effectively used compared with the case where the fan width is narrow and the speed distribution is unevenly hooked. . Because of the =, the temperature difference between the air and the refrigerant required to obtain the predetermined air-conditioning performance becomes small, the input power of the wire machine becomes small, and it becomes low noise. χ, in the case of small damage, even if the fan diameter does not become large, : ', the number is wide, the noise can be made smaller. In addition, in the inclusion of Fu:; eight widths change the air-conditioning device including a plurality of fan wide-sound fans, by replacing the fan with the wind fan X wind 1 wide fan visibility, and: the number of fans, It can also make the air-conditioning farms at a given operating point less variable, and can make the heat exchanger's wide-ranging value. The velocity distribution in the direction of the twist is close to that of the single figure ΙΛί' Τ/ϋ ^ ^ and the perspective view is 214B'9915-pf 22 1354/33 Ϊ; = the perspective view of the overall shape of the fan. Figure. The cross-section of the schematic longitudinal section of the Dingsilo fan is shown in Figure 4 as a 矣-port 1 糸 not a graph of the siro fan. Q characteristics and Ks~Q characteristics

Figure 5 is the system 矣 + I you Xitong, '^, Xiluo fan U / H. And the pattern of loss. Bei Tian knows the number t. The figure of Fig. 6 shows a graph showing the y characteristic of the sirocco fan by the action of the Q characteristic and the Ksm 』a. Two = ::: each, one leaf and one leaf = a schematic sectional view of the cross-sectional structure. ...the table: Γ; the perspective view of the sirocco fan of the difference area α. The portion of the bar field W of the pressure variation (10) is static on the wall m i & field 0: a magnified view of the portion. Fig. 11 is an enlarged view showing a portion of the region α of the static (four) moving (four) portion of the region having the step α in the step. It is understood that the 12th figure shows the west and the π ^ _ surface map. Longitudinal section of the schematic cross-sectional structure of the fan. Fig. 13 is a perspective perspective view showing the sirocco fan. : 14 The graph shows the graph of the sirocco p-Q characteristics in the case where the action point b is not passed. 〈 15 图 图 图 · · 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 Ding 2148-9915-pf 23 1354735 Fig. 16 is a cross-sectional view showing the longitudinal sectional structure of the suspended indoor unit. Figure 17 is a table showing the noise values of the suspended indoor unit. Fig. 18 is a schematic structural view showing an unintentional structure of an air-conditioning apparatus according to a second embodiment of the present invention. [Main component symbol description] 1 fan, 2 volute casing, 2 a suction port, 2b air outlet, 2M tongue, 2c air path, 3 mouth, 4 tongue, 5 suction space, 1 0 0 siro fan , 110 suspended indoor unit, 150 air conditioner, 1 51 compressor, 152 condensing heat exchanger, 1 5 3 throttling device, 154 evaporative heat exchanger

2148-9915-PF 24

Claims (1)

1354735 X. Patent application scope: 1. A sirocco fan' includes: a volute casing having a suction port for taking in air, a blow port for blowing air, and a blow port from the suction port to the blow port. a wind passage; the fan is housed in the volute casing, and is driven by rotation to take in air from the suction port and blow air from the air outlet; and the bell mouth is attached to the suction cup mouth; The utility model is characterized in that: the suction port is located on an extension line of the rotation center of the fan, and is formed on both sides of the spiral case, and the ventilation resistance in the air path is p[pa], from the suction port The amount of air entering is Q [mvmin], the width of the fan in the direction of the axis of rotation L[_], k is constant, the height of the dome is η, ·]: is the loss coefficient |: [Pa / (mVmin) In the case of 2], in the range of 〇.l$k4f $〇_4, create WH = 0.3494W h 〇.75f(k^)^L/H^f(k4n〇ΗΗ.8 2· as in the scope of patent application The wind road of the 西 洛 埚 埚 至 至 至 至 至 至 至 的 的 的 ” ” ” ” ” ” ” ” ” ” ” ” ” ” ” ” ” ” ” “ “ “ “ “ “ “ “ “ “ “ “ “ “ “ The end of the smallest opening of the mouth is set to be the center of the mouth and the point is eight o'clock, and the point at the point of the mouth is Α, the point of the largest opening of the mouth, 2148 -9915-PF 25 is a point B which is symmetrical with respect to the point and the point in the bell mouth, and a line from the point β to the direction of the fan is a point c, and the side of the scroll case is set from the side Point In the direction of the fan, the intersection point of the (four) plane is point c, the snail shackle side » the line slave, and the intersection of the fan's shaft extension line is point 〇, at the point of passing the point, the point 〇 and the On the intersection line of the point, the door will be fainted and the tongue. ρ ^ The point at which the distance from the fan becomes the minimum is set to point D, and the point closest to the point D of the bell is set to point E, The point at which the point is 65 is the point F, and the direction of the reverse direction of the fan of the point E is set to be the center cut at the point 。. The point is the point G, which is the fan of the point F at the point 4 The reverse direction is at this point. It is in the middle. The point of the rotation of the fan from the point F is the point H' located at the point 180 from the point of rotation of the point two. 】, ^ is « is connected to the point H, the point F and the length of the line BC of the point G is 4 χ, HFG ° is connected to the point H, the point I and the point of the general arc H of the point G When the length of the line segment BC is ¥, the arc HIG is in the range of L/HS f(k4p), and is made into X>γ-〇〇3.-Sirocco fan, including: volute, moon, ',-, useful a suction port for taking in air, an air outlet for blowing 2148-9915-PF 26 1354735 gas, and a wind passage from the suction port to the air outlet; the fan is housed in the spiral case, Driving the air from the suction port and blowing air from the air outlet; and the bell mouth is attached to the suction port of the scroll case; and the suction port is located at the center of rotation of the fan The extension line is formed on one side of the volute casing, the ventilation resistance in the air passage is P [Pa], the amount of air taken in from the suction port IQ [mVmin], the fan The width in the direction of the rotation axis is L[〇m], k is constant, the height of the scroll case is H = 246k [mm], and p/Q2 is the loss factor f [pa/(m3/min) 2]. 〇. IS k4f $ 〇·4 range, made) = 1.39788(k^ 2.H〇8(k^ ) + 1 g , 1. 5g(k4f hL/HS 2g(k4f ). 4. The sirocco fan of claim 3, wherein the v is in the curved portion from the air passage of the clamshell to the air outlet, and the portion closest to the outer circumference of the fan is used as The tongue, in the longitudinal section of the mouth, the point at the end of the smallest opening of the mouth is point A, = the point which is pointy to the center of the bell mouth and the point A is point A, and The end point of the largest opening of the mouth is point B, and the point of the center of the bell mouth and the point symmetry is point B, and the point where the point is pulled toward the fan is point C, & The straight line and the side of the volute casing 2Ί 2148-9915-PF are set from the point B, & g! # A i the intersection of the two points is point C,, · the straight line drawn to the side of the scroll and the side of the scroll: And the intersection of the fan's axis extension line is point 〇, < = the point at which the point A, the point 0, and the point A, the plane, and the tongue 'the minimum distance with the fan are set to a point D, the point closest to the point D of the bell mouth is point E, and 5 is located at the point Re in the point Re. From the point E, the point of the reverse direction G b of the fan is point F, set The point from the point F in the reverse direction 40 of the fan from the point F is the point G, and «the rotation of the fan from the point f centered on the point 4 is 4 Π. Point Η, is not located in the direction of rotation of the fan from the point F centered at the point F. The point is point j, ° is connected to the point H, the point F and the substantially circular arc HFG of the point G The length of the line segment BC is X, and s is in the range of L/HS g(k4 f ) when the point Η, the point I, and the approximate arc η I of the point g (the length of the line segment BC of J is γ) , X>Y$0. 5. An air conditioning apparatus characterized by using a sirocco fan as claimed in any one of claims 1 to 4. 2148-9915-PF 28