MULTI-LAYER DISK FAN WITH BLADES

Abstract: A multi-layer disk fan with blades, which is operable quietly. In the multi-layer disk fan with the blades formed by laminating a multiplicity of annular disks at predetermined intervals therebetween, the arrangement having such a feature that a multiplicity of blades are interposed between the annular disks and the outer ends and/or the inner ends of the respective blades are positioned a predetermined distance inward of the outer peripheral edges of the annular disks is adopted. With this arrangement, turbulent flow caused by peeling at the tips of the blades through the effect of laminar flows by the disks can be effectively prevented, and moreover, distortion in the outlet speed at the outer peripheral edges of the annular disks can be controlled to reduce noises due to the turbulent flow and the interference, thus enabling the quiet operation.

Description: This invention relates to a multi-stacked circular plate fan provided with blades which can constantly obtain a sufficient amount of expelling air, while assuring a silent operation. Conventionally as one of the fans which are capable of silent air-expelling operation, there is a multi-stacked circular plate fan X which is disclosed in Japanese laid-open publication 54-89602. Such a multi-stacked plate fan provided with blades, as shown in Figs. 25 and 26, substantially comprises a fan body 101 which is driven by a power operated-motor 100 which in turn is mounted on one end of a fan casing 110. Upon operation of the power-operated motor 100, the fan body 101 is rotated so as to generate the air flow and expels the air from an air outlet 140. Furthermore, as shown in Fig. 25, the fan body 101 comprises a multiplicity of thin annular circular plates 104 which are stacked together with a desired gap therebetween so that when the annular circular plates 104 are rotated, a shearing force is generated on the surface of these circular plates 104 in a circumferential direction. This shearing force works as a centrifugal force so as to generate an air flow thus providing a silent operation of the fan. Furthermore, for providing a desired gap between the annular circular plates 104 and for making the flow of air from the inside to the outside smooth and increase the amount of air flow as shown in Figs. 25 and 26, a plurality of arcuate blades 105 are disposed at a desired circumferential interval between the annular circular plates 104. The blades 105 also work as spacers. However, the above mentioned multi-stacked plate fan X provided with blades still have following tasks to be resolved Namely, as shown in Fig. 26, every blade 105 has the trailing edge or the outermost outlet end extended to the outer peripheral portion of the annular circular plates 104. Therefore, at the outlet of the annular circular plates 104, as shown in Figs. 26 and 27, a considerable distortion of velocity is generated in a circumferential direction and due to this distortion of velocity the pressure adjacent to the tongue portion of the casing fluctuates periodically thus generating the noise by rotation. Furthermore, besides a tongue portion, during the course of rectifying the distortion of velocity, the turbulent flow is generated at the outer periphery of the annular circular plates 104, thus producing noise by the turbulent flow. Furthermore, a portion of the air flow 106 which flows between the annular plates 104, 104 and locates at the rear portion of the blades 105 is peeled off so as to generate an air peeling-off region 108. Due to this peeling-off phenominon, a turbulent flow region 107 occurs at the outer periphery of the circular plate 104 and the turbulent flow noise is generated. On the other hand, as shown in Fig. 26, the blade 105 has the leading edge or the inlet end thereof extended to the inner periphery of the circular plate 104. Therefore, 1 ○ as understood from the distribution curve of the absolute velocity 111 on the surface of the blade 105 as shown in Fig. 26, the velocity reduction ratio is greater on the inner end suction surface of the blade 105 than any other portion and, 2 ○ the velocity reduction ratio at the inlet portion formed between the annular circular plates 104, 104 is greater than any other portion so that the air peeling-off phenomenon is generated at the inner end suction surface of the blade 105. Furthermore, in case there is a velocity distortion relative to a circumferential direction at the inlet portion of the annular circular plates 104,104, an inflow angle of air toward the blade fluctuates and this also forms a part of the cause of the air peeling-off phenomenon. Due to such a phenomenon, a turbulence noise inside the annular circular plates 104, 104 also becomes greater. DE-A-2 602 933 discloses a fan having the features recited in the preamble of the appended independent claims 1, 2 or 3 : at least one of the trailing edge or the leading edge of the blade is positioned at a distance from respectively the inner or the outer periphery of the annular circular plate. The problem of reducing the noise of the fan is not contemplated. Accordingly, it is an object of the invention to provide a multi-stacked circular plate fan which can increase the amount of expelling air while assuring a silent fan operation. This object is reached according to the invention owing to the specific features set forth in the characterizing portion of independent claims 1,2 or 3. Subclaims 4 to 10 define preferred embodiments. Fig. 1 is a perspective view of a multi-stacked circular plate fan provided with blades according to the first embodiment wherein the fan is used as a hot air blow fan. Fig. 2 is a cross-sectional side view of the fan. Fig. 3 is a transverse view taken along the line I-I of Fig. 2. Fig. 4 is a perspective view of an annular circular plate. Fig. 5 is a perspective view of a blade. Fig. 6 is an explanatory view showing the flow velocity of air flow at the outer periphery of the annular circular plate. Fig. 7 is a graph showing the specific noise level of the multi-stacked circular plate fan provided with blades. Fig. 8 is a cross-sectional front view of a multi-stacked circular plate fan provided with blades according to the second embodiment. Fig. 9 is a graph showing the specific noise level of the multi-stacked circular plate fan provided with blades. Fig. 10 is a cross-sectional front view of a multi-stacked circular plate fan provided with blades according to the third embodiment. Fig. 11 is an explanatory view showing the desirable backward attack angle of the blade of the multi-stacked circular plate fan provided with blades accoriding to the fourth embodiment. Fig. 12 is an explanatory view showing the undesirable backward elavation angle of the blade of the multi-stacked circular plate fan provided with blades. Fig. 13 is an explanatory view showing the undesirable backward attack angle of the blade of the multi-stacked circular plate fan provided with blades. Fig. 14 is a graph showing the relationship between the attack angle and the specific noise level. Fig. 15 is an explanatory view showing the undesirable backward attack angle of the blade. Fig. 16 is an explanatory view of the multi-stacked circular plate fan provided with blades having no inclination. Fig. 17 is an explanatory view showing the modification of the blade having the backward attack angle. Fig. 18 is an explanatory view showing the modification of the blade having the backward attack angle. Fig. 19 is an enlarged view of the substantial part of the multi-stacked circular plate fan provided with blades according to the fifth embodiment. Fig. 20 is a graph showing the relationship between the rate between pitch of the blade and the blade mounting angle and the specific noise level. Fig. 21 is a graph showing the relationship between the circumferential velocity and the specific noise level according to the sixth embodiment. Fig. 22 is an explanatory view showing the air flow passing through the gap between the annular circular plates according to the seventh embodiment. Fig. 23 is an explanatory view showing the flow of air. Fig. 24 is a graph showing the relationship between the Reynold's number and the specific noise level. Fig. 25 is a cross-sectional side view showing the conventional multi-stacked circular plate fan provided with blades. Fig. 26 is a cross-sectional view taken along the line II-II of Fig. 25. Fig. 27 is an explanatory view showing the air flow on the annular circular plate. Fig. 28 is an explanatory view showing the velocity distribution of the air flow between the annular circular plates. Hereinafter, the multi-stacked circular plate fan provided with blades accoriding to the present invention is described in detail in view of several embodiments shown in the attached drawings. (First Embodiment) The embodiment, as shown in Fig. 1 to Fig. 6, discloses a multi-stacked circular plate fan A provided with blades characterized in that all of the blades have their trailing edge portions located a predetermined distance S 1 to the inner side from the outer circumferential edge of the annular circular plate 24. In this embodiment, a multi-stacked circular plate fan A provided with blades is used as a hot air blow fan. As shown in Fig. 1 to Fig. 3, a fan casing 13 of the multi-stacked circular plate fan A provided with blades comprises a front wall 10 and a rear wall 11 which are substantially circular and the circumferential edges of these walls, except a lower end opening portion ( a drying air outlet port ) 40, are connected to each other by an annular peripheral wall 12. The fan casing 13, in this embodiment, is fixedly connected to a motor casing 15 by way of a support 14. The fan casing 13 is provided with an air intake port 10a formed in the front wall 10, and comprises a fan body 20 disposed concentrically therein. The fan body 20 is connected to an output shaft 22 of a driving motor 21 disposed inside the support frame 14. At the lower portion of the fan casing 13, there is disposed a heater 39 made of a nickel-chromium coil. In the above basic construction, the present invention is characterized by the fan body 20 which is capable of silent air-expelling operation. Namely, as shown in Fig. 2, Fig. 4 and Fig. 5, the fan body 20 is substantially constructed by stacking a multiplicity of thin annular circular plates 24 on a base circular plate 23, with spacers 25 interposed to provide a predetermined gap or spacing δ between adjacent ones of the circular plates. The predetermined gaps δ includes not only equal spacings but also irregular spacings. The annular circular plate 24, as shown in Fig. 3, has a donut-like shape and is provided with apertures 27 for passing connecting pins 26 therethrough in predetermined cirumferential pitches. The predetermined circumferential pitch includes not only the equal pitch but also the irregular pitch. The blade 25 is, as shown in Fig. 5, made of a thin arcuate piece and is provided with an aperture 28 through which the connecting pin 26 passes. In assembling the fan body 20 shown in Fig. 2, a multiplicity of annular circular plates 24 and a multiplicity of blades 25 are stacked alternatively on the base circular plates 23 by making the connecting pins 26 pass through the apertures 26, 27 and then the ends of connecting pins 26 are coaked on the surface of the last annular circular plates 24. Furthermore, in this embodiment, as shown in Fig. 3, the trailing edges 25a of all the blades 25 are positioned a predetermined distance S 1 to the inside from the outer periphery end of the annular circular plate 24. Due to such a construction, upon rotation of the fan body 20, the air is radially flown to the outside of the fan body 20 from the central space C defined inside the multiplicity of stacked annular circular plates 24 passing through the air passage 30 formed between the annular circular plates 24, 24. Thereafter, the air is expelled outside from the annular circular plates 24. In this operation, the turbulence 31 generated by the peeling-off of air at the rear portion of the blades 25,25 between the annular circular plates 24, 24 can be suppressed due to the influence of viscocity caused by the wall surface of the annular circular plates 24, thus effectively preventing the occurence of turbulent flow 31 and the turbulent flow noise caused by the turbulent flow. Furthermore, within a predetermined distance S 1 to the outer periphery of the annular circular plates 24, owing to the influence of a shearing force generated on the wall surface of the annular circular plates 24, 24, the velocity distortion caused between the trailing edges of the adjacent blades 25, 25 is alleviated as shown in Fig. 6 and the velocity distribution curve becomes uniform at the outlet of annular circular plates 24. Accordingly, the pressure fluctuation adjacent to the tongue portion is disappeared and the interference noise is attenuated thus preventing the occurence of the turbulent noise caused by the velocity distortion. Furthermore, due to the influence of the outside portion of the circular plates 24 such as the tongue portion or the blow-out portion, the flow of air insides the row of blades is periodically changed and causes the lowering of pressure and velocity. However, since the trailing edge of the blade 25 is positioned a predetermined distance S, inside from the outer periphery of the annular circular plate 24, the boundary condition at the outlet of the blade 25 becomes stable and the flow angle of air expelled from the blade 25 becomes always constant so that the stable air expelling operation is achieved. The distance S 1 from the trailing edge 25a of the blade 25 to the outer periphery of the annular circular plate 24 should meet the value expressed by a following formula according to an experiment carried out by the applicant. 0.3< S 1 ℓ ·[ Vu 1 Vr 1 ] 1/3 <1.2 In the above fundamental formula, ℓ: pitch between blades (mm) Vu 1 : tangential velocity of fluid at the radius of the trailing edge of the blade (m/s) Vr 1 : radial velocity of fluid at the radius of the trailing edge of the blade (m/s) Here, the pitch ℓ between blades, the tangential velocity Vu 1 of fluid and the radial velocity Vri of fluid can be obtained with following formulae respectively. ℓ=2πr 1 /Z In the above formula, r 1 : radius of trailing edge of the blade Z : number of blades Vu 1 u 1 =1- A 12πR 2 + ( A 12π -1) 1 R 2 . e 12π·(1-R 2 )/A In the above formula, u 1 : circumferential speed of annular circular plate 24 at the radius of the trailing edge of the blade (= 2πrn/60 ) n : number of rotation of annular circular plate (rpm) A : non-dimentional flow amount ( = qδ/ ν r i 2 ) q : amount of air flow which passes between the annular circular pla tes (m 3 /s) δ : gap between the annular circular plates (m) ν: kinematic viscosity (m 2 /s) ri : radius of annular circular plate at inlet (m) R : r 1 /r i Vr 1 = q 2πr 1 ·δ In the above fundamental formula (1), (S 1 /ℓ) is a value which relates to making the flow velocity distribution curve uniform with the presence of the distance S 1 as shown in Fig.6, while (Vu 1 /Vr 1 ) is an air mixing effect by the tangential velocity. Meanwhile, in Fig. 7, a graph is shown in which the above-mentioned (S 1 /ℓ) · (Vu 1 /Vr 1 ) 1/3 is taken on the abscissa and the specific noise level ks (dB(A)) is taken on the ordinate. The specific noise level ks can be obtained by a formula ( ks = Lsp-10 log QP 2 . In the formula, Q = expelling air amount of blower or fan (m 3 /s) P = pressure head of blower of fan (mmAq) Lsp = sound pressure level of blower or fan (dB (A)) As can be readily understood from the graph, in case of 0.3 <(S 1 /ℓ). (Vu 1 /Vr 1 ) 1/3 <1.2, the specific noise ks is reduced, and especially, in case of 0.5<(S 1 /ℓ) . (Vu 1 /Vr 1 ) 1/3 <1.0, the specific noise is considerably reduced. From this result, it is found that the distance S 1 is interrelated with the pitch ℓ between blade, the tangential velocity Vu 1 of fluid and the radial velocity Vr 1 of fluid and that the distance S 1 should be smaller relative to the pitch between the blades while the velocity Vu 1 should be greater relative to the velocity Vr 1 . However, if the distance S 1 is excessively greater, the length of line which connects blades becomes short so that the working effected by the blade is lowered and thus the air expelling capacity is lowered resulting in the greater noise. Accordingly, the optimal range exists in the above formula. Hereinafter, the operation of the multi-stacked circular plate fan A provided with blades which is used as the hot air blow fan will be explained in view of Fig.2 and Fig. 3. When the operator pushes an operation switch which is not shown in the drawing, the fan operating motor 21 and the heater 39 are operated. As the fan operating motor 21 is driven, the fan body 20 is rotated and the air is sucked into the fan casing 10 from the outside through the air inlet 10a and the air passes through the gaps formed between multi-stacked circular plates 24, 24 , while exhibiting the uniform distribution in terms of amount or air from the inlet opening to the bottom of the fan blade. Thereafter, the downward air flow is generated and the air is heated by the heater 39 and is blown outside from the hot air blow-off outlet 40. Furthermore, in the above rotation of the fan body 20, since the trailing edge 25a of the blade 25 is positioned a predetermined distance S 1 to the inside from the outer periphery 24a of the annular circular plate 24, at the trailing edge of the blade 25, any turbulent flow which may be caused by the peeling-off phenominon can be effectively suppressesd and furthermore since no outlet velocity distortion occurs at the outer periphery 24a of the annular circular plate 24a, the turbulent noise and the interference noise are attenuated thus enabling the silent air-expelling operation. (Second Embodiment) The multi-stacked circular plate fan A provided with blades according to this embodiment, as shown in Fig. 8, substantially has the same construction as that of the first embodiment. Namely, the multi-stacked circular plate fan A provided with blades is constructed by stacking a multiplicity of annular circular plates 24 while forming a desired gap δ therebetween. Accordingly, in Fig. 8, the like construction and like parts are denoted by the same numerals. However, in this embodiment, different from the first embodiment, as shown in Fig. 8, the occurrence of the turbulent flow caused by the peeling-off of air is prevented only at the inner periphery of the annular circular plates 24,24. Namely, a multiplicity of blades 25 which are interposed between the annular circular plates 24,24 have their respective leading edge 25b positioned a predetermined distance S 2 to the outside from the inner periphery of the annular circular plate 24. Due to such a construction, the turbulent flow noise which tends to occur at the inner peripheral side of the annular circular plate 24 by the peeling-off of air can be effectively suppressed. Even in case that the distortion of velocity in a circumferential direction exists at the inlet opening of the annular circular plates 24, the velocity distribution becomes uniform within the predetermined distance S 2 so that the inflow angle of air toward the blade becomes stable thereby enabling the stable and silent fan operation without the peeling-off of air. According to an experiment carried out by the applicant, it was found that the distance S 2 from the leading edge 25b of the blade 25 to inner peripheral side 24b of the annular circular plate 24 should take following value. 0.025 < S 2 / r 2 < 0.125 In the formula, r 2 : radius at the leading edge of the blade Namely, in a table ( Table 1 ) below, specific noise levels ks which were the result of the experiment carried on by varying the distance S 2 (mm) from the leading edge 25b of the blade 25 to the inner peripheral side 24b of the annular circular plate 24 and the radius (mm) of the leading edge of the blade respectively are described, while Fig. 9 is a graph prepared by taking the S 2 /r 2 on the abscissa and the specific noise level ks ( dB (A) ) on the ordinate. The specific noise level ks is obtained by the formula ks = Lsp-10 log QP 2 as in the case of the first embodiment. S 2 r 2 S 2 /r 2 × 100 k s 0 70 0 50 1.8 71.8 2.5 45 4 74 5.4 44 7.5 77.5 9.7 44 10 80 12.5 45 As can be understood from the above table and the graph in Fig. 9, in case S 2 /r 2 is 0.025 <S 2 /r 2 <0.125, the specific noise ks was attenuated. Especially, in case S 2 /r 2 is 0.05<S 2 /r 2 <0.10, the specific noise ks was considerably attenuated. For preventing the noise, it is desirable to make the distance S 2 from the leading edge 25b of the blade 25 to the inner peripheral side 24b of the annular circular plate 24 longer relative to the radius r 2 of the leading edge 25b of the blade 25. However, if the distance S 2 is too long, the straight line which spans both ends of the blade 25 is shortened and the function of the blade 25 is deteriorated and eventually the specific noise ke is increased. Accordingly, S 2 /r 2 should be chosen in the above determined most optimal range. ( Third embodiment ) The multi-stacked circular plate fan A provided with blades according to this embodiment, as shown in Fig. 10, substantially has the same construction as that of the first embodiment. Namely, the multi-stacked circular plate fan A provided with blades is constructed by stacking a multiplicity of annular circular plates 24 while forming a desired gap δ therebetween. Accordingly, in Fig. 8, the like construction and like parts are denoted by the same numerals. However, in this embodiment, different from the first embodiment, as shown in Fig. 10, the occurrence of the turbulent flow caused by peeling-off of the air is prevented not only at the inner periphery of the annular circular plates 24,24 but also at the outer periphery of the annular circular plates 24,24. Namely, a multiplicity of blades 25b which are interposed between the annular circular plates 24,24 have their respective trailing edges 25a positioned a predetermined distance S 1 to the inside from the outer periphery 24a of the annular circular plate 24 and have their respective leading edges 25b positioned a predetermined distance S 2 to the outside from the inner periphery 24b of the annular circular plate 24. Due to such a construction, the turbulent flow noise and the interference noise which respectively tend to occur at the inner and outer peripheral sides of the annular circular plate 24 by the velocity distortion and the peeling-off of air can be effectively suppressed. ( Fourth embodiment) The multi-stacked circular plate fan A provided with blades according to this embodiment is characterized by the desirable mounting angle of the blades 25 on the annular circular plates 24 which gives rise to the silent air-expelling operation of the circular plate fan A. The present embodiment is explained in detail hereinafter in conjuntion with the attached drawings Fig. 2, Fig. 3 and Fig. 11 to Fig. 15. As shown in Fig. 2 and Fig. 3, in the multi-stacked circular plate fan A provided with blades, when the fan A is driven, the air is sucked into the central space C defined at the center of the fan body 20 by stacking a multiplicity of annular circular plates 24 and air passes through the air passages defined between the annular circular plates 24,24 and air flows out in all radial directions. Then, air is heated by the heater H and is smoothly blown off from the hot air outlet 40. In the above flow of air, the propulsion of air to the outside is enhanced by the provision of the blades 25. As shown in Fig. 11, the blade 25 has the trailing edge 25a thereof backwardly inclined which is opposite to the rotating direction of the annular circular plate 24. The reason for adoption of the rearwadly inclined blade as the blade 25 of the fan is that with the frontwardly inclined blade 25 shown in Fig. 15 or the radially extending blade 25, the fluid disposed at the range of the blade flows at the tangetial speed which is equal to or more than the rotational speed of the annular circular plate 24, while once the fluid is out of the range of the blade 25, the speed of the fluid is reduced by the friction on the surface of the annular circular plate 24 and causes loss. To the contrary, as shown in Fig. 11, in case the backwardly inclined blade is adopted as the blade 25, not only the centrifugal force generated by the frictional force between the annular circular plate 24 and the fluid but also the air blow force generated by the working of the blade 25 is increased thus enabling the air propulsion with the least occurrence of the turbulence. The applicant also has found that when the backwardly inclined angle, namely a blade mounting angle ϑ relative to the annular circular plate 24 is chosen appropriately relative to the locus R of air which flows in the air passage between the annular circular plates 24,24, the noise reduction caused by the rotation of the multi-stacked circular plate fan A provided with blades can be effectively enhanced. Namely, it was found by the experiment that in case the blade mounting angle  at the inlet side of the annular circular plate 24 formed by the locus R of the air flowing between the annular circular plates 24,24 and a chord L which connects thetrailing edge 25a and theleading edge 25b is set at 20 ° ±15° , the noise can be reduced greatly while assuring a sufficient air blow amount. The reason for setting the blade mounting angle ϑ at 20° ±15° is as follows. Namely, as shown in Fig. 12, in case the blade mounting angle ϑ is greater than the maximum angle of 35° , the turbulence including the voltices is generated by the peeling off of air on the suction surface k 3 so that the air expelling sound is greatly increased or the air expelling performance becomes unstable thus remarkably increasing the noise. On the other hand, as shown in Fig. 13, in case the blade mounting angle  is smaller than the minimum angle of 5°, the blade can hardly carry out its function or the blade 25 works as the resistance against the flow of air thus deteriorating the performance of the fan and increases the specific noise. The locus R of air which flows in the air passage can be readily obtained in a following manner. Firstly, with the following formulae (6) and (7), the circumferential velocity (Vu-U) and the radial velocity Vr relative to the air flow which passes through the annular circular plates 24,24 are obtained. [circumferential velocity (Vu - U)] Vu U =1- A 12π(r/r i ) 2 +( A 12π -1) 1 (r/r i ) 2 × e 12π·(1-(r/r))/A From the velocity Vu obtained from the formula (6), the circumferential velocity (Vu - U) can be obtained. [radial velocity Vr] From Bernoulli's equation of continuity, V r = q /2πrδ From the formulae (6) and (7), the position of air at one point of the annular circular plate 24 after Δt seconds is obtained as x=x s + ΔtVr, y=y s + Δt (Vu ·U). Here, Δt is≒0. The position of air obtained in the above manner is continuosly connected and the locus R can be readily obtained. In the above formula, A: non-dimentional flow amount (=qδ D /νr i 2 ) Vu: circumferential velocity of air at a desired radius m/s Vr: radial velocity of air at a desired radius m/s U: circumferential velocity of circular plate at a desired radius m/s δ: gap between two annular circular plates m q: amount of air which passes through two annular circular plates m 3 /s r: a desired radius m ri: radius at the inlet of annular circular plate m ν: kinematic viscosity m 2 /s µ: viscosity coefficient kgs/s In Table 2, the specific noise levels ks which are measured by varying the blade mounting angle ( attack angle )  while in Fig. 14, the above-measured specific noise level is taken on the ordinate. attack angle specific noise ks 5° 42.5 10.5° 42 27.5° 42 35° 42.5 45° 47 As can be understood from the Table 2 and the graph in Fig. 14, when the blade mounting angle  is within the range of 5 ° , the specific noise is decreased and especially, when the blade mounting angle  is within the range of 5 ° , the specific noise is noticeably decreased. As described above, this embodiment is, as shown in Fig. 11, characterized in that the blade 25 is backwardly inclined and the attack angle  is set to be 20° ±15. However, the shape and the manner of arrangement are not limited to those which are shown in Fig. 11. For example, the multi-stacked circular plate fan A can adopt the blades 25 which are shown in Fig. 17 and Fig. 18. Namely, in Fig. 17, the blade 25 has a completely straight linear shape, while in Fig. 18, the blade 25 has a slightly arcuate shape. (FIFTH EMBODIMENT) This embodiment is characterized in that, as shown in Fig. 19, the relationship between an angle α between blades 25,25 and an angle β which is defined by lines L 3 and L 4 made by connecting the leading edge and the trailing edge of the blade 25 with the center of the annular circular plate 24 is set to be 0.5<β/α< 1. The reason for predetermining the circumferential pitch angle α between the blade 25,25 at 0.5<β/α< 1 is as follows. Namely, if β/α is smaller than 0.5 or the circumferential pitch angle between the blades 25,25 is greater than β/0.5, the working of the blades 25,25 is lowered as shown in the table below ( Table 3 ) and the graph shown in Fig. 20 so that the amount and the pressure of air are both decreased and the velocity distortion between the trailing edge s of the blades 25,25 is increased and the turbulence noise and the interference noise are increased. If β/α is greater than 1 or if the circumferential pitch angle between the blades 25,25 is narrower than β, the passage of air flow which passes through the blades 25,25 is narrowed and the pressure loss in the passage is increased so that the pressure is rapidly decreased. Accordingly, the optimal value should be in the above range. β/α specific noise 1.2 48 1.0 44 0.8 43 0.5 44 0.4 47 (Embodiment 6) This embodiment is characterized in that in the multi-stacked circular plate fan A provided with blades, if the relationship among the gap δ, the kinematic viscosity of air and the angular velocity of the annular circular plate 24 is chosen at a predetermined rate, the operational noise of the multi-stacked circular plate fan A provided with blades can be reduced. Namely, in the multi-stacked circular plate fan A, Breiter et al suggests the optimal gap between the annular circular plates 25,25 in the following formula. δ π(ν/ω) 1/2 =1 In the formula, ν = kinematic viscosity (m 2 /s) ω= angular velocity (rad/s) The applicant carried out an experiment to examine the validity of the above formula in the multi-stacked circular plate fan A provided with blades on the condition that the number of the blades 25 is set at Z ≧ 8 and obtained the result exhibited in the graph shown in Fig. 21. As can be understood from the graph, in the multi-stacked circular plate fan provided with blades, if the δ/(ν/ ω) 1/2 is in the range of 0.8 to 4.0, more specifically in the range of 1.2 to 3.0, the specific noise level was remarkably decreased. In this manner, the reason why the appropriate gap δ between the annular circular plates 25,25 was increased if the multi-stacked circular plate fan A provided with blades increases the number of blades 25 is that as the gap δ is widened, the blade 25 can work more efficiently so that the air dynamic performance can be increased and the specific noise level ks was decreased. On the other hand, if the gap δ is widened excessively, the laminar flow effect caused by the circular plates 25 is lost and the noise is increased. Accordingly, the value should be in the optimal range. (Seventh Embodiment ) This embodiment is characterized in that the gap δ between the annular circular plates 25,25 in the multi-stacked circular plate fan A provided with blades is determined in view of the Reynold's number of air. In the sirocco fan, the flow of fluid tends to generate vortices at the blade portion, whereas in the multi-stacked circular plate fan provided with blades, a multiplicity of annular circular plates 24 are stacked so that such vortices can restrict the occurrence of the turbulence. As shown in Fig. 22(a), however, when the gap δ between the annular circular plates 24,24 is excessively widened, the vortices and the turbulence are generated between the annular circular plates 24,24, while as shown in Fig. 22(c), if the gap δ between the annular circular plates 24,24 is excessively narrow, although no vortices or turbulence occurs between the annular circular plates 24,24, the fan provides little air blow function due to flow resistance in the air passage. Accordingly, the applicant has evaluated the optimal gap which can assure the sufficient amount of expelling air while minimizing the occurrence of the vortices and the turbulence and found that if the gap δ between the annular circular plates 24,24 with respect to the Reynold's number is set in a predetermined range, the fan can exhibit the sufficient amount of expelling air and little vortices or turbulence. Namely, in the multi-stacked circular plate fan A provided with blades, a following relationship exists between the gap δ and the Reynold's number. Namely, assuming that the number of annular circular plates 24 being B and the air amount being Q ( m 3 /min ), the relative velocity at the inlet can be obtained by a following formula provided that air enters radially relative to the multi-stacked circular plate fan A. ω m1 = Q 60π·2r i ·δ·B If the air completely slips in a circumferential direction, ω u1 = 2π r i n 60 ω 1 = ω m1 2 +ω u1 2 From above formulae, the relationship between the Reynold's number Re and the gap between the annular circular plates 24,24 can be obtained by a following formula. Re = ω 1 · δ ν In the above formula, each symbol has following meanings. ωm 1 : relative angular velocity of air at the inlet ωm 1 : circumferential angular velocity of air at the inlet ω 1 : relative velocity of air at the inlet ν: kinematic viscosity of air r 1 : inlet radius of annular circular plate Meanwhile, the result of the experiment carried by the applicant in which the gap between the annular circular plates 24,24 was varied within the range of 200 to 10000 of the Reynold's number is shown in Fig. 24. From the graph shown in Fig. 24, for effectively lowering the noise level, it is desirable to take the relationship between the Reynold's number and the gap δ in a following range. 200 < ω 1 ·δ ν (=Re) < 3000 Due to above-mentioned construction, the present invention has following advantages. Namely, The present invention discloses a multi-stacked circular plate fan provided with blades which is formed by stacking a multiplicity of annular plate while maintaining a desired gap therebetween, characterized in that a multiplicity of blades are interposed between the annular circular plates and at least either of the trailing edge or the leading edge of the blade is positioned a predetermined distance to the inside from the outer periphery of the annular circular plate or a predetermined distance to the outside from the inner periphery of the annular circular plate. Due to the laminar flow effect caused by the annular circular plates, the turbulent flow which is produced at the leading and trailing edges of the blades by peeling-off of air can be minimized and furthermore, since no outlet velocity distortion occurs at the outer periphery of the annular circular plates, the turbulent noise and the interference noise can be lowered thus providing the silent fan operation. Furthermore, with the provision of backwardly inclined blade or by making an angle which is formed at the leading edgeof the blade by a locus of the fluid obtained by the circumferential velocity and the radial velocity as relative velocities of fluid which flows between annular plates and a chord which connect theleading edge and thetrailing edge of the blade is determined at 20 ° ± 15 ° , the fan can increase the air expelling capacity while assuring the silent operation. Furthermore, the relationship between a circumferential pitch angle between blades and an angle defined by lines formed by connecting the leading edgeand the trailing edge of the blade with the center of the annular circular plate is determined at 0.5 to 1 so that an optimal air flow passage is established. Therefore, the fan can increase the air expelling capacity while assuring the silent operation. Furthermore, the optimal operation range exists in the relationship between the gap between the annular circular plates and the rotation of the fan or the velocity of air flow at the outlet of the circular plate, wherein in the above range, due to the laminar effect of the circular plates, the turbulent flow which is produced at the leading and trailing edges of the blades by peeling-off of air can be minimized and the the outlet velocity distortion occurs at the outer periphery of the annular circular plates can be suppressed, the turbulent noise and the interference noise can be lowered thus providing the silent fan operation. Although the present invention is explained specifically with respect to several embodiments, the present invention is not restricted to the invention disclosed in those embodiments and rather the multi-stacked circular plate fan according to the present invention can be preferably used in any other technical fields or applications which require the silent air expelling operation such as the heat exchanger besides the hot air blow fan.

Claims: A multi-stacked circular plate fan provided with blades which is formed by stacking a multiplicity of annular circular plates (24) while maintaining a desired gap (δ) therebetween and interposing a multiplicity of blades (25) between the annular circular plates (24) wherein at least one of the trailing edge or the leading edge of the blade (25) is positioned at a distance from respectively the inner or the outer periphery of the annular circular plate (24), characterized in that the trailing edge of the blade (25) is positioned a distance (S 1 ) to the inside from the outer periphery of the annular circular plate (24) and said distance (S 1 ) is expressed by a following formula 0.3 < S 1 ℓ ·[ Vu 1 Vr 1 ] 1/3 < 1.2 In the formula, l: pitch between blades (mm) Vu 1 : tangential velocity of fluid at the radius of the trailing edge of the blade (m/s) Vr 1 : radial velocity of fluid at the radius of the trailing edge of the blade (m/s). A multi-stacked circular plate fan provided with blades which is formed by stacking a multiplicity of annular circular plates (24) while maintaining a desired gap (δ) therebetween and interposing a multiplicity of blades (25) between the annular circular plates (24) wherein at least one of the trailing edge or the leading edge of the blade (25) is positioned at a distance from respectively the inner or the outer periphery of the annular circular plate (24), characterized in that the leading edge of the blade (25) is positioned a distance (S 2 ) to the outside from the inner periphery of the annular circular plate (24) and said distance (S 2 ) is determined at a value of 0.025<S 2 /r 2 <0.125 with relation to the radius (r 2 ) of the annular circular plate (24) at the leading edge of the blade (25). A multi-stacked circular plate fan provided with blades which is formed by stacking a multiplicity of annular circular plates (24) while maintaining a desired gap (δ) therebetween and interposing a multiplicity of blades (25) between the annular circular plates (24) wherein at least one of the trailing edge or the leading edge of the blade (25) is positioned at a distance from respectively the inner or the outer periphery of the annular circular plate (24), characterized in that the trailing edge of the blade (25) is positioned a distance (S 1 ) to the inside from the outer periphery of the annular circular plate (24) while the leading edge of the blade (25) is positioned a distance (S 2 ) to the outside from the inner periphery of the annular circular plate (24) and said distance (S 1 ) is expressed by a following formula 0.3 < S 1 ℓ ·[ Vu 1 Vr 1 ] 1/3 < 1.2 In the formula, l : pitch between blades (mm) Vu 1 : tangential velocity of fluid at the radius of the trailing edge of the blade (m/s) Vr 1 : radial velocity of fluid at the radius of the trailing edge of the blade (m/s), and, said distance (S 2 ) is determined at a value of 0.025 <S 2 /r2 <0.125 with relation to the radius (r 2 ) of the annular circular plate (24) at the leading edge of the blade (25). A multi-stacked circular plate fan provided with blades according to one of any preceding claims 1 to 3, wherein said blade (25) is mounted in such a manner that it is inclined in a backward direction. A multi-stacked circular plate fan provided with blades according to one of any preceding claims 1 to 4, wherein an attack angle () which is formed at the leading edge of the blade (25) by a chord (L) which connects the leading edge and the trailing edge of the blade (25) and a locus (R) of the fluid obtained by the circumferential velocity and radial velocity as relative velocities of fluid which flows between annular circular plate (24) is determined at 20° ± 15°. A multi-stacked circular plate fan provided with blades according to one of any preceding claims 1 to 5, wherein the relationship between a pitch angle (α) between blades (25) and an angle (β) defined by lines (L 3 ), (L 4 ) formed by connecting the leading edge and the trailing edge of the blade (25) with the center of the annular circular plate (24) is determined at 0.5 < β /α<1, A multi-stacked circular plate fan provided with blades according to one of any preceding claims 1 to 6, wherein the gap (δ) between the annular circular plates (24) is determined at a value which is expressed by a following formula 0.8 < δ π(ν/ω) 1/2 <4.0 In the formula, v = kinematic viscosity (M 2 /S) w = angular velocity (rad/S) A multi-stacked circular plate fan provided with blades according to one of any preceding claims 1 to 7, wherein the gap (δ) between the annular circular plates (24) is determined at a value which is expressed by a following formula 200 < ω 1 ·δ ν (=Re) < 3000 In the formula, w 1 = relative angular velocity at the inlet portion between air and annular circular plate (m/S) v = kinematic viscosity (M 2 /S) Re = Reynold's number A multi-stacked circular plate fan provided with blades according to one of any preceding claims 1 to 8, wherein the blade (25) has a shape of a conformal transformation. A multi-stacked circular plate fan provided with blades according to one of any preceding claims 1 to 9, wherein the blade (25) has a streamline shape.

Inventors: AKAMATSU KATSUSHI, HAMADA YASUO, HARAGA HISATO, AKAMATSU, KATSUSHI, HAMADA, YASUO, HARAGA, HISATO
Applicants: TOTO LTD, TOTO LTD.
Application year: 1992
Main classification: F04D17
IPC codes: F04D17