WO2018127970A1 - Ventilateur, soufflante et moteur électrique - Google Patents

Ventilateur, soufflante et moteur électrique Download PDF

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Publication number
WO2018127970A1
WO2018127970A1 PCT/JP2017/000271 JP2017000271W WO2018127970A1 WO 2018127970 A1 WO2018127970 A1 WO 2018127970A1 JP 2017000271 W JP2017000271 W JP 2017000271W WO 2018127970 A1 WO2018127970 A1 WO 2018127970A1
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WIPO (PCT)
Prior art keywords
pitch angle
pitch
blades
fan
angles
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PCT/JP2017/000271
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English (en)
Japanese (ja)
Inventor
裕介 奥出
誠司 羽下
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三菱電機株式会社
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Priority to PCT/JP2017/000271 priority Critical patent/WO2018127970A1/fr
Publication of WO2018127970A1 publication Critical patent/WO2018127970A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes

Definitions

  • the present invention relates to a fan, a blower, and an electric motor.
  • a fan that generates an airflow includes a plurality of blades arranged at an equal pitch in the circumferential direction of the rotation shaft, and the airflow is generated by rotating the plurality of blades around the rotation shaft.
  • a fan in which a plurality of blades are arranged at an equal pitch is a so-called blade cutting sound or pure noise that is a noise whose fundamental frequency is a value obtained by the product of the number of rotations and the number of blades when the plurality of blades are rotated. Tone, which causes discomfort to the user.
  • Patent Document 1 In order to reduce noise, a fan is known in which a plurality of blades arranged in the circumferential direction of a rotating shaft are arranged at unequal pitches (Patent Document 1).
  • the pitch angle of the blades is different for each adjacent blade, and each pitch angle is aperiodically changed.
  • Patent Document 2 a method using a fan in which blades are arranged using a periodic pseudo-random array pattern is known.
  • a fan as a cooling fan for an electric motor that drives a vehicle
  • the cooling fan is connected to the axle, as the axle is rotated forward or reverse, the cooling fan is also rotated forward or reverse.
  • the cooling fan needs to have an equivalent noise reduction effect in both forward and reverse rotations.
  • Fans with blades arranged at unequal pitches and fans with blades arranged in a periodic pseudo-random arrangement are mixed with blades with different pitches. These patterns are different and an equivalent noise reduction effect cannot be achieved.
  • the present invention has been made in view of the above reasons, has a simple structure, is inexpensive, can greatly reduce noise, and exhibits a similar noise reduction effect during forward rotation and reverse rotation of the fan,
  • An object is to provide a blower and an electric motor.
  • a fan according to the present invention provides: A support member that rotates about a rotation axis; and n (n is an integer of 2 or more) blades that are attached to the support member and are arranged radially around the rotation axis.
  • the n blades are arranged around the rotation axis at n pitch angles, Any one of the n blades is used as a reference blade, and a first pitch angle is formed between the reference blade and a blade adjacent to the first direction of the circumference of the rotation shaft,
  • the first pitch angles are arranged in the m direction (m is an integer of 1 or more, n> m) in the first direction,
  • a second pitch angle different from the first pitch angle is formed by the reference blade and a blade adjacent to the second direction that is opposite to the first direction, and the second pitch angle is , N ⁇ m arranged in the second direction,
  • a first summed pitch angle obtained by summing m of the first pitch angles is different from a second summed pitch angle obtained by summing nm of the second pitch angles.
  • a fan, a blower, and an electric motor that have a simple structure, are inexpensive, can greatly reduce noise, and have the same noise reduction effect during forward rotation and reverse rotation of the fan. it can.
  • FIG. 1 is a schematic front view of a blower including a centrifugal fan according to Embodiment 1 of the present invention. Schematic sectional view taken along line AA in FIG. 1A The figure which shows the arrangement
  • FIG. 1A The figure which shows the arrangement
  • FIG. which shows the pitch angle of the blade
  • wing of a comparative example The figure which shows the arrangement
  • FIG. The figure which shows the arrangement
  • Schematic diagram of an electric motor provided with a centrifugal fan according to Embodiment 4 The figure which shows the arrangement
  • FIG. 1A and FIG. 1B show a blower 1 including a centrifugal fan according to the present embodiment.
  • the blower 1 includes a centrifugal fan 10, a housing 20 that houses the centrifugal fan 10, a rotating shaft 30 that rotates the centrifugal fan 10, a motor 40 that drives the rotating shaft 30, Is provided.
  • the centrifugal fan 10 includes a main plate 11 that is a support member and a plurality of blades 12.
  • the main plate 11 is a member that supports the plurality of blades 12, and is a member formed in a disk shape.
  • the main plate 11 is attached to the rotary shaft 30 when the rotary shaft 30 of the motor 40 is fixed through the center of the main plate 11.
  • the plurality of blades 12 are attached to one surface of the main plate 11 radially in the circumferential direction around the rotation shaft 30.
  • the plurality of blades 12 are radial blades in which each blade faces the radial direction.
  • the centrifugal fan 10 provided with such blades can be applied to a plate blower.
  • the attachment angle between the main plate 11 and the blades 12 is set to 90 °.
  • the housing 20 is a flat box-shaped member and accommodates the centrifugal fan 10 therein.
  • the housing 20 includes main walls 20a and 20b facing each other, and a side wall 20c surrounding a region between the main walls 20a and 20b.
  • Centrifugal fan 10 is housed inside housing 20 with rotating shaft 30 along the thickness direction of housing 20.
  • a suction port 21 is provided in the main wall 20 b of the housing 20 at a position facing the centrifugal fan 10.
  • a discharge port 22 is provided in a part of the side wall 20 c of the housing 20.
  • the blower 1 sucks air from the suction port 21 located on the extension line of the rotary shaft 30 of the centrifugal fan 10 as indicated by an arrow AR1 in FIG. 1B.
  • the sucked air is compressed in the housing 20 and discharged from a discharge port 22 provided in a direction orthogonal to the rotation shaft 30 of the housing 20 as indicated by an arrow AR2 in FIG. 1A.
  • the blower 1 is applied to various devices such as a ventilation fan and an air curtain. Moreover, the air blower 1 is applied to an air conditioner by disposing a heat exchanger in the vicinity of the discharge port 22 of the air blower 1.
  • the blades 12 and the main plate 11 of the centrifugal fan 10 are made of, for example, stainless steel, aluminum, titanium, or synthetic resin depending on the size or type of the device to be applied.
  • the arrangement of the blades 12 of the centrifugal fan 10 is as follows: (1) the total number n of blades is an odd number; (2) the pitch angle types are the first pitch angle ⁇ 1 and the second pitch. There are two types of angles ⁇ 2, the first pitch angle ⁇ 1 and the second pitch angle ⁇ 2 are different, and (3) m first pitch angles ⁇ 1 are arranged side by side in the first direction. Pm pitch angles ⁇ 2 are arranged side by side in the second direction, and (4) there is one difference between the number of first pitch angles ⁇ 1 and the number of second pitch angles ⁇ 2. (5) The first summed pitch angle obtained by adding m first pitch angles ⁇ 1 is different from the second summed pitch angle obtained by adding nm second pitch angles ⁇ 2.
  • the number of blades of the centrifugal fan 10 is set to 11, and the blades W1 to W11 are arranged around the rotating shaft 30.
  • the blades W1 to W11 are arranged around the rotation axis 30, eleven pitch angles are formed.
  • the first pitch angle ⁇ 1 and the second pitch angle ⁇ 2 are defined with any one of 11 blades as a reference blade.
  • the blade W1 is set as a reference blade
  • the blade W1 and the clockwise direction of the circumference of the blade W1 and the rotating shaft 30 (the X direction in the figure: hereinafter “first The pitch angle formed by the blades W2 adjacent to each other in the “direction X”) is defined as a first pitch angle ⁇ 1.
  • the pitch angle formed by the blade W1 and the blade W11 adjacent to the blade W1 and the counterclockwise direction of the circumference of the rotating shaft 30 (the Y direction in the drawing: hereinafter referred to as “second direction Y”). Is defined as a second pitch angle ⁇ 2.
  • the definition of the first pitch angle ⁇ 1 and the second pitch angle ⁇ 2 is also defined in the following second to fourth embodiments.
  • the first pitch angle ⁇ 1 and the second pitch angle ⁇ 2 are uniquely determined by the following expression by determining the total number of blades and the ratio of the first pitch angle ⁇ 1 and the second pitch angle ⁇ 2.
  • n is set to 11 and ⁇ is set to 1.3. Then, these values are applied to Equation 2 under the condition that the number of small pitch angles is increased by one. Then, since ⁇ can be derived as 28.8 °, a small pitch angle is determined to be 28.8 ° and a large pitch angle is determined to be 37.44 °. Assuming that the large pitch angle is the first pitch angle ⁇ 1 and the small pitch angle is the second pitch angle ⁇ 2, as shown in FIG. 2, the first pitch angle ⁇ 1 is the first pitch angle between the blades W1 and W6. Are arranged side by side in the direction X, and six second pitch angles ⁇ 2 are arranged in the second direction Y between the blades W1 and W6.
  • the pitch angles are 37.44 °, 37.44 °, 37.44 °, 37.44 °, 37.44 °, 28.8 °, 28.8 °, 28.8 °, 28.8 ° and 28.8 °.
  • the position of the pitch angle is specified by attaching numbers 1 to 11 along the first direction X.
  • the first total pitch angle is formed by arranging five first pitch angles ⁇ 1, and the second total pitch angle is formed by arranging six second pitch angles ⁇ 2.
  • the first summed pitch angle is different from the second summed pitch angle, and the first summed pitch angle and the second summed pitch angle are around the rotation axis 30 as shown in FIG. Are arranged with the boundary line D1 as a boundary.
  • the blade characteristics of the centrifugal fan 10 having such a blade arrangement will be described in comparison with a comparative example.
  • blades of the centrifugal fan of the comparative example blades in which 11 blades are arranged at an equal pitch around the rotation axis (hereinafter referred to as “equal pitch blades”), and 11 blades are periodically simulated around the rotation axis.
  • Blades arranged according to a random arrangement hereinafter referred to as “periodic pseudo-random arrangement blades”.
  • FIG. 3 is a table showing the pitch angles of the equi-pitch blades, the periodic pseudo-random array blades, and the blades of the present embodiment in association with the pitch angle position numbers.
  • the numbers shown in the column of the pitch angle positions are numbers corresponding to the numbers of the pitch angle positions in FIG.
  • the pitch angle of the equal pitch blades is the same for all pitch angles. Specifically, eleven blades are arranged with a pitch angle of 32.73 °.
  • an M-type array is used as the periodic pseudo-random array of the periodic pseudo-random array blades.
  • the M system array is a binary number sequence of 0 and 1 having a period of 2 n ⁇ 1, the number of number sequences in one period is an odd number, and the difference between the numbers of “0” and “1” Is defined as 1.
  • “0” is associated with a large pitch angle
  • “1” is associated with a small pitch angle
  • the period is set to 11.
  • the numerical sequence indicated by the M-sequence is 110111100010. As shown in FIG.
  • the pitch angle based on this number sequence corresponds to the position of the pitch angle, 28.8 °, 28.8 °, 37.44 °, 28.8 °, 28.8 °, 28 8 °, 37.44 °, 37.44 °, 37.44 °, 28.8 ° and 37.44 °.
  • FIGS. 4A, 4B, and 4C show changes in sound pressure Pn (t) with the passage of time at arbitrary observation points of the equi-pitch blades, the periodic pseudo-random array blades, and the blades of the present embodiment, respectively.
  • FIG. 4A is a graph in which sound pressure P1 (t) of equal pitch blades is measured along time lapse t
  • FIG. 4B is a graph in which sound pressure P2 (t) of periodically pseudorandom array blades is measured along time lapse t
  • FIG. 4C is a graph obtained by measuring the sound pressure P3 (t) of the blade according to the present embodiment over time.
  • the vertical axis represents the value of the sound pressure P with the maximum value of the sound pressure set to 1 and the minimum value set to 0, and the horizontal axis represents the time t.
  • P1 (t) sin ( ⁇ t)
  • the maximum value of the sound pressure P1 is periodically generated when the blade passes through the observation point. Therefore, the maximum sound pressure is generated when each of the blades W1 to W11 passes through the observation point. Since the pitch angles of all the blades are equal, the maximum sound pressure is generated at equal time intervals.
  • the maximum sound pressure is generated at the timing when each of the blades W1 to W11 arrayed according to the M-system array passes the observation point. Since the blades are arranged in a periodic pseudo-random arrangement, the maximum sound pressure is generated according to the arrangement interval.
  • the blades W1 to W6 arranged at the first pitch angle ⁇ 1 and the blades W6 to W11 arranged at the second pitch angle ⁇ 2 The maximum sound pressure is generated at the timing of passing through.
  • the maximum sound pressure is generated according to the arrangement interval of the blades arranged at the first pitch angle ⁇ 1 and the arrangement interval of the blades arranged at the second pitch angle ⁇ 2.
  • FIG. 5 is a graph showing the relationship between amplitude and frequency obtained by FFT analysis.
  • the vertical axis represents amplitude
  • the horizontal axis represents frequency.
  • the equi-pitch blades showed a peak spectrum of 0.5 at a frequency of 550 Hz, which is a fundamental frequency obtained from a frequency of 50 Hz ⁇ total number of blades of 11.
  • the periodically pseudorandom array of vanes showed a peak spectrum of 0.3741005 at a frequency of 550 Hz.
  • the blade used in the present embodiment showed two peak spectra on the low frequency side and the high frequency side with a frequency of 550 Hz, and the higher peak spectrum was 0.28127575.
  • the peak spectrum value can be kept low and the peak value can be dispersed and the noise of the centrifugal fan 10 can be reduced as compared with the blades of the equal pitch blade and the periodic pseudo-random arrangement. It can be greatly reduced.
  • the centrifugal fan 10 is arranged such that the first summed pitch angle and the second summed pitch angle are biased around the rotation shaft 30. Noise can be greatly reduced. Further, since the centrifugal fan 10 is manufactured by applying only two types of pitch angles, the first pitch angle ⁇ 1 and the second pitch angle ⁇ 2, the design of the centrifugal fan 10 is simplified and the manufacturing cost is reduced. Can be reduced.
  • the centrifugal fan 10 according to the present embodiment can be applied to various products that use the blower 1, for example, a ventilation fan or an air conditioner, by being incorporated in the blower 1, so that when these products are operated, Noise can be greatly reduced.
  • the first pitch angle ⁇ 1 and the second pitch angle ⁇ 2 are set under the condition that the number of small pitch angles is increased by one.
  • the same effect can be obtained in another example (not shown) in which the first pitch angle ⁇ 1 and the second pitch angle ⁇ 2 are set.
  • n is set to 11 and ⁇ is set to 1.3. These values are applied to the above equation 1. Then, since ⁇ can be derived as 28.12 °, a small pitch angle is calculated as 28.12 ° and a large pitch angle is determined as 36.56 °. If the large pitch angle is the first pitch angle ⁇ 1 and the small pitch angle is the second pitch angle ⁇ 2, six first pitch angles ⁇ 1 are arranged in the first direction X between the blades W1 and W7. In addition, five second pitch angles ⁇ 2 are arranged in the second direction Y between the blades W7 and W1.
  • the pitch angle is 36.56 °, 36.56 °, 36.56 °, 36.56 °, 36.56 °, 36.56 °, 28.12 °, 28.12 °, 28.12 °, 28.12 °, and 28.12 °.
  • the first total pitch angle is formed by arranging six first pitch angles ⁇ 1, and the second total pitch angle is formed by arranging five second pitch angles ⁇ 2.
  • the first summed pitch angle and the second summed pitch angle are different from each other, and the first summed pitch angle and the second summed pitch angle are arranged around the rotating shaft 30 in a biased manner.
  • the pitch angle is set under the condition that the number of large pitch angles is increased by one, the first combined pitch angle and the second combined pitch angle are biased around the rotating shaft 30, so that the centrifugal fan 10 noise can be greatly reduced.
  • centrifugal fan 10 of the present embodiment has an equivalent noise reduction effect in both cases where the rotating shaft 30 of the centrifugal fan 10 rotates forward and reverse.
  • the blade characteristics in the case of normal rotation and reverse rotation will be described below in comparison with a periodic pseudo-random array blade.
  • the pitch angle arrangement of the periodically pseudo-random array blades can be represented by an array of 110101100010, with a large pitch angle corresponding to “0” and a small pitch angle corresponding to “1”.
  • the centrifugal fan When the centrifugal fan is rotated forward once, the blades pass through the observation points in this order of arrangement, and the pattern of the sound pressure P2 (t) shown in FIG. 4B is shown.
  • the centrifugal fan is reversed once, the blades pass through the observation points in an arrangement order different from normal rotation of 01000111011. Therefore, the pattern of sound pressure generated differs between forward rotation and reverse rotation, and the noise reduction effect is also different.
  • the noise reduction effect may be reduced when the centrifugal fan is reversed.
  • the centrifugal fan 10 can be rotated in both the first direction X that is the forward rotation direction and the second direction Y that is the reverse rotation direction.
  • the direction of rotation is determined according to the application of the centrifugal fan 10 and the user's request.
  • the pitch angle of the blades of the present embodiment is set to “0” as in the case of the pitch angle of the periodic pseudo-random array blades.
  • the small pitch angle is made to correspond to “1”.
  • the pitch angles of the blades of the present embodiment shown in FIG. 3 can be represented by an arrangement of 00000111111 from the pitch angle positions “1” to “11”.
  • the blade pattern when the centrifugal fan 10 continuously rotates forward or backward can be explained as follows.
  • the area around the rotation axis 30 is indicated by a first summed pitch angle area (hereinafter referred to as “A area”) obtained by adding five first pitch angles ⁇ 1 indicated by an array of 00000 and an array of 111111.
  • a area a first summed pitch angle area
  • B region a second summed pitch angle region obtained by summing six second pitch angles ⁇ 2.
  • the total number of blades is an odd number
  • the first pitch angle ⁇ 1 and the second pitch angle ⁇ 2 are set to different angles
  • the difference from the number of ⁇ 2 was 1.
  • the present invention is not limited to the number of blades and the number of pitch angles, and the total number of blades is an even number, and the number of first pitch angles ⁇ 1 is equal to the number of second pitch angles ⁇ 2. Also applies.
  • the arrangement of the blades of the centrifugal fan according to the present embodiment is as follows: (1) The total number n of blades is an even number; (2) The pitch angle types are the first pitch angle ⁇ 1 and the second pitch angle. There are two types, the first pitch angle ⁇ 1 and the second pitch angle ⁇ 2 are different, and (3) m first pitch angles ⁇ 1 are arranged side by side in the first direction, and the second pitch angle ⁇ 2 Are arranged side by side in the second direction, (4) the number of first pitch angles ⁇ 1 is the same as the number of second pitch angles ⁇ 2, and (5) first The first total pitch angle obtained by adding m pitch angles ⁇ 1 and the second total pitch angle obtained by adding nm second pitch angles ⁇ 2 are different from each other.
  • the centrifugal fan of the present embodiment has the same basic configuration as the centrifugal fan 10 of the first embodiment.
  • the centrifugal fan 10 of the present embodiment can be rotated in both the first direction X that is the forward rotation direction and the second direction Y that is the reverse rotation direction.
  • the direction of rotation is determined according to the application of the centrifugal fan 10 and the user's request.
  • the first pitch angle ⁇ 1 and the second pitch angle ⁇ 2 are uniquely determined by the following expression by determining the total number of blades and the ratio of the first pitch angle ⁇ 1 and the second pitch angle ⁇ 2.
  • n / 2 ⁇ ⁇ + n / 2 ⁇ ⁇ ⁇ ⁇ 360 ° (Formula 3)
  • n is the total number of blades
  • ⁇ is the angle of the small pitch angle
  • ⁇ is the ratio of the large pitch angle to the small pitch angle.
  • n is set to 10 and ⁇ is set to 1.3, and these values are applied to Equation 3. Then, since ⁇ can be derived as 31.3 °, a small pitch angle is determined to be 31.3 ° and a large pitch angle is determined to be 40.69 °. If the large pitch angle is the first pitch angle ⁇ 1 and the small pitch angle is the second pitch angle ⁇ 2, as shown in FIG. 6, the first pitch angle ⁇ 1 is the first pitch angle between the blades W1 and W6. The second pitch angle ⁇ 2 is arranged side by side in the second direction Y between the blades W1 and W6.
  • the pitch angle is 40.69 °, 40.69 °, 40.69 °, 40.69 °, 40.69 °, 40.69 °, 31.3 °, It is defined as 31.3 °, 31.3 °, 31.3 °, 31.3 °.
  • the first total pitch angle is formed by arranging five first pitch angles ⁇ 1, and the second total pitch angle is formed by arranging five second pitch angles ⁇ 2.
  • the first summed pitch angle and the second summed pitch angle are different, and the first summed pitch angle and the second summed pitch angle are around the rotation axis 30 as shown in FIG. , They are arranged biased with respect to the boundary line D2.
  • the noise of the centrifugal fan 10 can be greatly reduced.
  • first total pitch angle in which five first pitch angles ⁇ 1 are arranged and the second total pitch angle in which five second pitch angles ⁇ 2 are arranged are arranged around the rotation axis 30, In both cases where the centrifugal fan 10 rotates forward and reversely, the same sound pressure pattern is generated, and an equivalent noise reduction effect is achieved.
  • the blade arrangement of the centrifugal fan according to the present embodiment is as follows: (1) The total number n of the blades is odd or even; (2) The pitch angle types are the first pitch angle ⁇ 1 and the second pitch. The first pitch angle ⁇ 1 and the second pitch angle ⁇ 2 are different, and (3) m first pitch angles ⁇ 1 are arranged in the first direction, and the second pitch angle The angle ⁇ 2 is arranged in a number of nm in the second direction, and (4) the difference between the number of the first pitch angles ⁇ 1 and the number of the second pitch angles ⁇ 2 is 2 or more, (5) The first summed pitch angle obtained by summing m first pitch angles ⁇ 1 is different from the angle of the second summed pitch angle obtained by summing nm second pitch angles ⁇ 2. It is characterized by.
  • the centrifugal fan of the present embodiment has the same basic configuration as the centrifugal fan 10 of the first embodiment.
  • the centrifugal fan 10 of the present embodiment can be rotated in both the first direction X that is the forward direction and the second direction Y that is the reverse direction.
  • the direction of rotation is determined according to the application of the centrifugal fan 10 and the user's request.
  • the first pitch angle ⁇ 1 and the second pitch angle ⁇ 2 are uniquely determined by the following expression by determining the total number of blades and the ratio of the first pitch angle ⁇ 1 and the second pitch angle ⁇ 2.
  • n is set to 11
  • ⁇ is set to 1.3
  • a is set to 3 (the number of large pitch angles is three more than the number of small pitch angles).
  • ⁇ can be derived as 27.5 °, so that a small pitch angle is 27.5 ° and a large pitch angle is 35.7 °.
  • the first pitch angle ⁇ 1 is the first pitch angle between the blades W1 and W5.
  • the second pitch angle ⁇ 2 is arranged in the second direction Y between the blades W1 and W5.
  • the pitch angle is 27.5 °, 27.5 °, 27.5 °, 27.5 °, 35.7 °, 35.7 °, It is defined as 35.7 °, 35.7 °, 35.7 °, 35.7 °, and 35.7 °.
  • a first summed pitch angle is formed by adding four first pitch angles ⁇ 1
  • a second total pitch angle is formed by adding seven pitch angles ⁇ 2.
  • the first summed pitch angle is different from the second summed pitch angle
  • the first summed pitch angle and the second summed pitch angle are around the rotation axis 30 as shown in FIG. Are arranged with the boundary line D3 as a boundary.
  • the centrifugal fan 10 is arranged so that the first summed pitch angle and the second summed pitch angle are biased around the rotation shaft 30.
  • the generated noise can be greatly reduced.
  • first total pitch angle in which four first pitch angles ⁇ 1 are arranged and the second total pitch angle in which seven second pitch angles ⁇ 2 are arranged are arranged around the rotation axis 30, In both cases where the centrifugal fan 10 rotates forward and reversely, the same sound pressure pattern is generated, and an equivalent noise reduction effect is achieved.
  • the first combined pitch angle and the second combined pitch angle are arranged so as to surround the entire circumference of the rotating shaft 30, and the first combined pitch angle and the second combined pitch angle are arranged. It was explained that the combined pitch angle is different.
  • the present invention is not limited to surrounding the entire circumference of the rotating shaft with only the first summing angle and the second summing angle, and the third summing of the first summing pitch angle and the second summing pitch angle is the third. May be formed, and two or more of the third total angles may be arranged around the rotation axis.
  • the centrifugal fan according to the present embodiment is mainly used as a cooling fan for electric motors for railway vehicles.
  • An electric motor for a railway vehicle including a centrifugal fan will be described with reference to FIG.
  • the electric motor 100 includes a frame 200, a stator 300, a rotor 400, a rotating shaft 500 that rotates integrally with the rotor 400, and a centrifugal fan 600 attached to the rotating shaft 500.
  • the frame 200 is disposed so as to surround the stator 300 and the rotor 400, and is formed with a suction port 201 through which air is sucked and a discharge port 202 through which the sucked air is discharged.
  • the stator 300 includes a stator core 301 and a stator coil 302 wound around the stator core 301, and the rotor 400 is disposed to face the stator 300.
  • a rotation shaft 500 is fixed through the central portion of the rotor 400.
  • One end of the rotating shaft 500 is connected to an axle (not shown) of the vehicle, and the rotating shaft 500 is rotated to rotate the axle. Both ends of the rotating shaft 500 are supported by bearings 501 provided on the frame 200.
  • the centrifugal fan 600 includes a plurality of blades 601, and the plurality of blades 601 are arranged radially around the rotation shaft 500.
  • centrifugal fan 600 attached to the rotating shaft 500 also rotates. While the rotating shaft 500 is rotating, the temperature of the components of the electric motor 100 rises due to the copper loss generated in the stator coil 302 and the iron loss due to the induced current generated in the rotor 400. Centrifugal fan 600 is rotated in accordance with rotation of rotating shaft 500, and air is introduced from suction port 201 by rotating centrifugal fan 600. As the introduced air passes through the electric motor 100 and is discharged from the discharge port 202, the inside of the electric motor 100 is cooled.
  • the electric motor 100 rotates the rotary shaft 500 according to the driving direction.
  • the rotary shaft 500 is rotated in the P direction as shown in FIG. 8 in the case of driving in the forward direction, and is rotated in the Q direction that is opposite to the P direction in the case of driving in the backward direction.
  • the arrangement of the blades of the centrifugal fan 600 is an unequal pitch arrangement or a periodic pseudo-random arrangement, when the rotary shaft 500 is viewed in a certain direction of the rotor 400 and from the opposite direction, The arrangement of the pitch angles of the blades is different.
  • Centrifugal fan 600 in the present embodiment can be suitably applied to a centrifugal fan that needs to rotate in the P direction and Q direction, specifically, to rotate forward and backward.
  • the P direction corresponds to the first direction shown in FIG. 9, and the Q direction corresponds to the second direction Y.
  • the blade arrangement of the centrifugal fan 600 is as follows: (1) the total number n of blades is an even number; (2) pitch angle types are the first pitch angle ⁇ 1 and the second pitch angle. There are two types of ⁇ 2, and the first pitch angle ⁇ 1 and the second pitch angle ⁇ 2 are different, and (3) the first pitch angle ⁇ 1 is arranged side by side in the first direction, and the second pitch angle The angle ⁇ 2 is arranged side by side in the second direction, and (4) the first summed pitch angle obtained by adding the first pitch angle ⁇ 1 and the second pitch angle ⁇ 2 summed by q. (4) The first summed pitch angle and the second summed pitch angle are summed to form a third pitch angle, and the third pitch angle is set to the rotational axis. It is characterized by arranging two or more around.
  • the first pitch angle ⁇ 1 and the second pitch angle ⁇ 2 are uniquely determined by the above formula 4 or formula 5 by determining the total number of blades and the ratio of the first pitch angle ⁇ 1 and the second pitch angle ⁇ 2. Determined.
  • the number of first pitch angles ⁇ 1 and the number of second pitch angles ⁇ 2 are the same, and n is set to 12 and ⁇ is set to 1.3.
  • ⁇ can be derived as 26.1 °, so that the small pitch angle is 26.1 ° and the large pitch angle is 33.9 °.
  • the first pitch angle ⁇ 1 is between the blades W1 and W4 as shown in FIG. Are arranged side by side in the direction X, and the second pitch angle ⁇ 2 is arranged side by side in the second direction Y between the blades W1 and W11.
  • a first total pitch angle is formed by arranging three first pitch angles ⁇ 1, and a second total pitch angle is formed by arranging three second pitch angles ⁇ 2.
  • the first combined pitch angle is And the second total pitch angle are formed differently.
  • first summed pitch angle and the second summed pitch angle are summed to form a third summed pitch angle.
  • the third combined pitch angle is formed between W10 and W4 in the first direction X in FIG. Then, by forming this third combined pitch angle in the second direction Y of W10 and W4, two third combined pitch angles are formed around the rotation axis 500.
  • a region where the first summed pitch angle is formed is an A region
  • a region where the second summed pitch angle is formed is a B region
  • the method of arranging the A region and the B region is a method in which the periphery of the rotation axis 500 is first divided into four or more even regions, and then A and B are alternately arranged in the divided regions.
  • wing of FIG. 9 is demonstrated below using the said method.
  • FIG. 10A the region around the rotation axis 500 is divided into four regions. Then, the A area and the B area are alternately arranged in the four divided areas.
  • FIG. 10B shows an arrangement of areas when the area to be divided is 8 which is an even number of 4 or more. As shown in FIG. 10B, the region around the rotation axis 500 is divided into eight. In the area divided into eight, the A area and the B area are alternately arranged.
  • the noise of the centrifugal fan 600 is reduced. It can be greatly reduced.
  • the centrifugal fan 600 when the centrifugal fan 600 is continuously rotated, the A area and the B area appear alternately. That is, since the A region and the B region appear in the same pattern during forward rotation and reverse rotation of the centrifugal fan 600, the same noise reduction effect can be achieved in both the forward driving and the returning driving of the railway vehicle. .
  • Embodiments 1 to 4 the present invention has been described using a centrifugal fan, but the present invention can also be applied to fans other than the centrifugal fan.
  • the fan of the present invention can be applied to an axial fan, a diagonal fan, and a cross fan.
  • the attachment angle between the main plate 11 and the blade 12 is set to 90 °, but the present invention is not limited to such an attachment angle. It can be set as appropriate according to the type of fan.
  • the blades 12 are radial blades facing in the radial direction, but the present invention is not limited to such blades.
  • the present invention can also be applied to forward blades facing in the direction of rotation, and the forward blades can be applied to a multiblade fan.
  • the present invention can also be applied to a backward blade in which the blade is directed in the direction opposite to the rotation direction, and the backward blade can be applied to a turbofan.
  • the disk-shaped main plate 11 has been described as a support member, but the present invention is not limited to such a support member.
  • a cylindrical rotating shaft may be used as a support member, and a plurality of blades may be attached around the rotating shaft.
  • the value of a is set as a value where the number of large pitch angles is larger than the number of small pitch angles, but the number of small pitch angles may be set larger than the number of large pitch angles. .
  • the electric motor for the railway vehicle has been described as an example, but the vehicle driven by the electric motor is not limited to the railway vehicle.
  • the present invention may be any vehicle that uses an electric motor that rotates the axle forward and backward, and can be applied to, for example, an automobile.
  • the number of first pitch angles ⁇ 1 and the number of second pitch angles ⁇ 2 have been described as being the same number, but the number is not limited to the same number.
  • the difference in the number of the first pitch angle ⁇ 1 and the second pitch angle ⁇ 2 may be 1 or more.
  • the fan is described using the electric motor applied to the railway vehicle, but the fan described in the first to third embodiments may be used as the fan of the railway vehicle.
  • the present invention can be suitably used for a fan mounted on a blower or an electric motor.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne un ventilateur centrifuge (10) dans lequel : une pale parmi 11 pales est définie comme étant une pale de référence (W1) ; un premier angle de pas (θ1) est formé entre la pale de référence (W1) et une pale qui est adjacente dans une première direction (X) autour d'un arbre de rotation (30) ; et cinq des premiers angles de pas (θ1) sont agencés de manière adjacente dans la première direction (X). Un second angle de pas (θ2) qui diffère du premier angle de pas (θ1) est formé entre la pale de référence (W1) et une pale qui est adjacente dans une seconde direction (Y) opposée à la première direction (X), et six des seconds angles de pas (θ2) sont agencés de manière adjacente dans la seconde direction (Y). Un premier angle de pas combiné obtenu par addition des cinq premiers angles de pas (θ1) et un second angle de pas combiné obtenu par addition des six seconds angles de pas (θ2) sont différents l'un de l'autre, et ainsi le bruit du ventilateur centrifuge (10) est réduit.
PCT/JP2017/000271 2017-01-06 2017-01-06 Ventilateur, soufflante et moteur électrique WO2018127970A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/JP2017/000271 WO2018127970A1 (fr) 2017-01-06 2017-01-06 Ventilateur, soufflante et moteur électrique

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2017/000271 WO2018127970A1 (fr) 2017-01-06 2017-01-06 Ventilateur, soufflante et moteur électrique

Publications (1)

Publication Number Publication Date
WO2018127970A1 true WO2018127970A1 (fr) 2018-07-12

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3623637A1 (fr) * 2018-09-14 2020-03-18 Yen Sun Technology Corp. Ventilateur centrifuge
CN114223111A (zh) * 2019-08-22 2022-03-22 日本电产株式会社 外转子型马达

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1893184A (en) * 1929-01-24 1933-01-03 Hoover Co Fan
GB2046360A (en) * 1979-03-31 1980-11-12 Aes Plastics Ltd Fluid impeller
JPS5716297A (en) * 1980-07-02 1982-01-27 Toshiba Corp Multiblade fan
JPH05195996A (ja) * 1992-01-16 1993-08-06 Hitachi Ltd 空気圧縮機
JP2003269363A (ja) * 2002-03-15 2003-09-25 Mitsubishi Heavy Ind Ltd タンゼンシャルファン羽根車及び空気調和機
JP2005282500A (ja) * 2004-03-30 2005-10-13 Toshiba Corp 流体ポンプ、冷却装置及電気機器
JP2011231775A (ja) * 2001-05-11 2011-11-17 Snecma ロータと固定擾乱源とを備えた構造物、および該構造物の振動を低減する方法
JP2015228768A (ja) * 2014-06-02 2015-12-17 株式会社東芝 回転機械

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1893184A (en) * 1929-01-24 1933-01-03 Hoover Co Fan
GB2046360A (en) * 1979-03-31 1980-11-12 Aes Plastics Ltd Fluid impeller
JPS5716297A (en) * 1980-07-02 1982-01-27 Toshiba Corp Multiblade fan
JPH05195996A (ja) * 1992-01-16 1993-08-06 Hitachi Ltd 空気圧縮機
JP2011231775A (ja) * 2001-05-11 2011-11-17 Snecma ロータと固定擾乱源とを備えた構造物、および該構造物の振動を低減する方法
JP2003269363A (ja) * 2002-03-15 2003-09-25 Mitsubishi Heavy Ind Ltd タンゼンシャルファン羽根車及び空気調和機
JP2005282500A (ja) * 2004-03-30 2005-10-13 Toshiba Corp 流体ポンプ、冷却装置及電気機器
JP2015228768A (ja) * 2014-06-02 2015-12-17 株式会社東芝 回転機械

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3623637A1 (fr) * 2018-09-14 2020-03-18 Yen Sun Technology Corp. Ventilateur centrifuge
CN114223111A (zh) * 2019-08-22 2022-03-22 日本电产株式会社 外转子型马达
CN114223111B (zh) * 2019-08-22 2024-05-31 日本电产株式会社 外转子型马达

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