JP2024001813A - Clothing fan and clothing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a clothing fan capable of improving a blowing ability without expanding a dimension in an axial direction of a housing, and suppressing an increase in noise.

SOLUTION: A clothing fan 1 to be attached to an opening 102 formed in clothing 100 includes: a hollow housing 10 having a suction port 2 formed with a suction port guard part 11, and a blowout port 3 facing the suction port 2 and formed with a blowout guard part 12; and a fan body 20 having a plurality of blade wings 21b arranged inside the housing 10 and rotated by an electric motor 22. When a direction in which the suction port 2 and the blowout port 3 face each other is an axial direction X, a length L1 in the axial direction X of the blade wings 21b is set to be a length of 32%-38% of a maximum length L2 in the axial direction X of the housing 10.

SELECTED DRAWING: Figure 4

COPYRIGHT: (C)2024,JPO&INPIT

Description

FIELD OF THE INVENTION The present invention relates to clothing fans and clothing.

BACKGROUND ART Conventionally, clothing fans are known that are attached to openings formed in clothing and blow air (outside air) into the clothing (see, for example, Patent Document 1 and Patent Document 2). In a conventional clothing fan, a fan main body is disposed in an internal space of a housing that has an inlet in which an inlet guard is formed and an outlet in which an outlet guard is formed.

Patent No. 6200606 Japanese Patent Application Publication No. 2022-68134

However, in the conventional clothing fan described in Patent Document 1, for example, the axial dimension of the blades included in the fan body is small relative to the size of the internal space of the housing. In other words, there are large gaps between the blades and the suction port guard and between the blades and the outlet guard. Therefore, there is room for improving the air blowing capacity of the fan main body without increasing the axial dimension of the housing.

On the other hand, in order to improve the air blowing capacity of the fan body, for example, when the number of blades is increased as in the conventional clothing fan described in Patent Document 2, turbulence is generated depending on the increase in the number of blades. The noise becomes louder. Therefore, it is conceivable that the wearer of the clothes may feel uncomfortable.

The present invention has been made in view of the above-mentioned problems, and provides a fan for clothing that can improve the air blowing capacity and suppress an increase in noise without increasing the axial dimension of the housing, and clothing to which the fan can be worn. With the goal.

In order to achieve the above object, the clothing fan of the present invention is a clothing fan that is attached to an opening formed in clothing, and includes a suction port in which a suction port guard portion is formed, and an inlet that faces the suction port. and an air outlet in which an air outlet guard part is formed, and a fan body having a plurality of blades disposed inside the housing and rotated by an actuator, the air inlet and The length of the blade in the axial direction is set to 32% to 38% of the maximum length of the housing in the axial direction, when the direction in which the air outlet faces the air outlet is defined as the axial direction. The configuration is as follows.

To achieve the above object, the clothing of the present invention includes a hollow housing having an inlet having an inlet guard formed therein, and an outlet facing the inlet and having an outlet guard formed therein. , a fan body having a plurality of blades disposed inside the housing and rotated by an actuator, and when the direction in which the suction port and the blowout port face each other is defined as an axial direction, The configuration includes an opening into which a clothing fan whose axial length is set to 32% to 38% of the maximum axial length of the housing is formed.

Thereby, the clothing fan of the present invention can improve the air blowing ability and suppress an increase in noise without increasing the axial dimension of the housing. Further, the clothing of the present invention can be equipped with a clothing fan that can improve the air blowing capacity and suppress an increase in noise without increasing the axial dimension of the housing.

FIG. 2 is a diagram illustrating clothing to which the clothing fan of Example 1 is attached. FIG. 2 is a perspective view of the clothing fan of Example 1 with the housing cut away. 1 is an exploded perspective view of the clothing fan of Example 1. FIG. FIG. 2 is a side view of the clothing fan of Example 1 with the housing cut away. FIG. 2 is a plan view of the clothing fan of Example 1, viewed from the suction port side. FIG. 3 is an explanatory diagram showing the positional relationship between the blades and the suction side crosspiece member in Example 1. FIG. 2 is a plan view showing a wing member of Example 1. FIG. It is a graph showing the relationship between the ratio of the blade length to the housing length and the air volume, and the relationship between the ratio of the blade blade length to the housing length and the air blowing efficiency in the first experiment. It is a graph showing the relationship between the ratio of the suction side spatial distance to the housing length and the height difference of the sound pressure level in a second experiment. (a) is a perspective view of the clothing fan of the first comparative example with the housing cut away. (b) is a side view of the clothing fan of the first comparative example with the housing cut away. 2 is a graph showing the relationship between air volume and noise value in the clothing fan of Example 1 and the clothing fan of the first comparative example. It is a graph which shows the relationship between the frequency and the sound pressure level in the clothing fan of a 2nd comparative example. (a) is a graph showing the relationship between frequency and sound pressure level in a clothing fan of a third comparative example. (b) is a graph showing the relationship between frequency and sound pressure level in the clothing fan of the fourth comparative example. It is a graph which shows the relationship between the frequency and the sound pressure level in the clothing fan of a 5th comparative example. It is a graph which shows the relationship between the frequency and the sound pressure level in the clothing fan of a 6th comparative example. It is a sectional view showing the main part of the clothing fan of the first modification.

EMBODIMENT OF THE INVENTION The form for implementing the clothing fan and clothing of this invention is demonstrated based on Example 1 shown in drawing. In the following description, terms such as "up and down," "left and right," and "front and back" are used with the wearer wearing the garment 100 as a reference.

The garment 100 of Example 1 is a jacket (jumper) worn by the wearer on the upper body. As shown in FIG. 1, the garment 100 has a pair of openings 102 formed in a back body 101 that covers the wearer's back. The opening 102 is a circular through hole that passes through the back body 101. The clothing fan 1 of the first embodiment is removably attached to the opening 102 of the clothing 100 . Air (outside air) is then blown into the inside of the garment 100 by the garment fan 1, thereby cooling the wearer's body.

The clothing fan 1 of Example 1 includes a housing 10, a fan body 20, and a fixing member 30, as shown in FIGS. 2 to 4.

As shown in FIG. 2, the housing 10 is a hollow member having an inlet guard part 11 and an outlet guard part 12 facing each other. Here, the suction port guard part 11 has a plurality of suction side crosspiece members 11b and a plurality of auxiliary crosspiece members 11d, as described later, and the distance between the adjacent suction side crosspiece members 11b and the auxiliary crosspiece members 11d is as follows. This serves as a suction port 2 through which air is sucked. Moreover, the outlet guard part 12 has a plurality of outlet side crosspiece members 12b as described later, and the space between adjacent outlet side crosspiece members 12b becomes the outlet 3 from which air is blown out. That is, the housing 10 has a suction port 2 in which a suction port guard portion 11 is formed, and an air outlet 3 facing the suction port 2 and in which a blowout port guard portion 12 is formed. Further, hereinafter, the direction in which the suction port 2 and the blowout port 3 face each other, that is, the direction in which the suction port guard portion 11 and the blowout port guard portion 12 face each other, is referred to as the “axial direction X”.

As shown in FIG. 3, the housing 10 of the first embodiment includes an inner cylindrical member 10A and an outer cylindrical member 10B. The housing 10 is formed by inserting an inner cylinder member 10A into an outer cylinder member 10B and fixing it via an engagement structure 10C. Note that the diameter of the housing 10 and the length L (see FIG. 4) of insertion into the clothing 100 can be arbitrarily set depending on the type of the clothing 100, the required amount of air, and the like.

The inner cylindrical member 10A is a cylindrical member having a suction port guard portion 11 formed at one end and an open end formed at the other end. A flange portion 13 is formed on the outer peripheral edge of the suction port guard portion 11 (the outer peripheral edge of one end of the inner cylinder member 10A). The flange portion 13 is a flat plate that protrudes from the circumferential surface of the inner cylinder member 10A to the outside of the housing 10 along the radial direction (direction perpendicular to the axial direction X; the same applies hereinafter). Moreover, the inner cylinder member 10A is inserted into the outer cylinder member 10B from the open end.

The outer cylindrical member 10B is a cylindrical member having an air outlet guard portion 12 formed at one end and an open end formed at the other end. A male thread groove 14 (thread groove) is formed on the outer peripheral surface of the outer cylinder member 10B. A fixing member 30 is screwed into the male thread groove 14 as described later.

The engagement structure 10C here is constituted by a combination of a plurality of claw pieces 16a formed on the inner cylinder member 10A and a plurality of recesses 16b formed on the outer cylinder member 10B. When the inner cylinder member 10A is inserted into the outer cylinder member 10B, the claw pieces 16a are elastically deformed toward the inside of the housing 10, and the claw pieces 16a engage with the recesses 16b by their own elastic force. The member 10A and the outer cylinder member 10B are fixed.

The suction port guard portion 11 prevents foreign objects such as fingers from entering the inside of the housing 10 . As shown in FIG. 5, the suction port guard part 11 includes a central support part 11a, a plurality of suction side crosspiece members 11b (crosspiece members), a plurality of connecting crosspiece members 11c, and a plurality of auxiliary crosspiece members 11d ( It has a crosspiece member). Further, the suction port guard portion 11 bulges toward the outside of the housing 10 along the axial direction X around the central support portion 11a (see FIG. 4).

The central support portion 11a is a disk-shaped portion disposed on the axis O of the housing 10, and is set to have approximately the same size as the electric motor 22 of the fan body 20 when viewed along the axial direction X.

The suction side crosspiece member 11b spans between the central support portion 11a and the side wall 10x of the inner cylindrical member 10A and extends in the radial direction, and extends in the rotational direction Y of the blade member 21 (blade blade 21b) of the fan main body 20. They are arranged in parallel at predetermined intervals along the line.

The connecting bar member 11c extends along the rotational direction Y of the wing member 21, and is bridged between adjacent suction side bar members 11b. Further, the connecting beam members 11c are arranged in parallel at a predetermined interval between the central support portion 11a and the side wall 10x of the inner cylinder member 10A.

The auxiliary crosspiece members 11d are bridged between the connecting crosspiece member 11c and the side wall 10x of the inner cylinder member 10A and extend in the radial direction, and are arranged in parallel at predetermined intervals along the rotational direction Y of the wing member 21. ing. The auxiliary crosspiece members 11d are arranged alternately with the suction side crosspiece members 11b along the rotational direction Y of the wing member 21.

In the suction side crosspiece member 11b and the auxiliary crosspiece member 11d, when the blade member 21 (blade blade 21b) rotates, the front end edge 23 of each of the plurality of blades 21b in the rotation direction Y, as viewed from the axial direction It is arranged at a position where the timing of overlapping with the suction side crosspiece member 11b or the auxiliary crosspiece member 11d is asynchronous.

In addition, in the first embodiment, the "rotation direction Y of the blade member 21 (blade 21b)" is a direction that is counterclockwise when the suction port 2 is viewed along the axial direction X. Further, "the timing at which the front end edge 23 of the vane 21b overlaps the suction side crosspiece member 11b or the auxiliary crosspiece member 11d" means, as shown in FIG. Alternatively, it is the timing of passing through the wake region S that occurs on the downstream side of the auxiliary beam member 11d. In the wake region S, the flow of air sucked into the housing 10 is blocked by the suction side crosspiece member 11b or the auxiliary crosspiece member 11d, and the flow rate of the air passing between the suction side crosspiece member 11b and the auxiliary crosspiece member 11d (intake port 2) is reduced. This is a region where the flow velocity is lower than that of the current. "The overlapping timings are asynchronous" means "the overlapping timings are not simultaneous." That is, in the first embodiment, in order to prevent the front edges 23 of the three blades 21b from passing through the wake region S at the same time, the suction side crosspiece member 11b and the auxiliary crosspiece member 11d are arranged at uneven pitches along the circumferential direction. are paralleled.

The outlet guard portion 12 prevents foreign objects such as fingers from entering the housing 10 . As shown in FIG. 3, the outlet guard section 12 includes a motor storage section 12a, a plurality of outlet side beam members 12b, and a connecting beam member 12c (see FIG. 4). Moreover, the air outlet guard part 12 bulges toward the outside of the housing 10 along the axial direction X centering on the motor housing part 12a (see FIG. 4).

The motor storage part 12a is a cylindrical member arranged on the axis O of the housing 10, and one end facing the suction port guard part 11 is closed and the other end is open. A through hole 12e through which the rotating shaft 22a of the electric motor 22 passes is formed in the closed surface 12d of the motor storage portion 12a.

The blowout side crosspiece members 12b are bridged between the motor storage portion 12a and the side wall 10y of the outer cylinder member 10B, extend in the radial direction, and are arranged in parallel at a predetermined interval along the rotational direction Y of the wing member 21. has been done.

The connecting bar member 12c extends along the rotational direction Y of the wing member 21, and is bridged between adjacent blowout side bar members 12b.

As shown in FIG. 3, the fan main body 20 includes a wing member 21 and an electric motor 22 (actuator) that rotates the wing member 21.

The wing member 21 includes a cylindrical hub 21a and a plurality of (here, three) blades 21b provided on the circumferential surface of the hub 21a. The hub 21a has one end facing the suction port guard part 11 closed to form a rotating shaft attachment part 21c, and the other end open. The hub 21a is placed over the motor storage portion 12a with a gap left, and the rotating shaft 22a of the electric motor 22 protruding from the through hole 12e is connected to the rotating shaft mounting portion 21c. Thereby, the hub 21a rotates with the rotation of the rotating shaft 22a, and the plurality of blades 21b rotate integrally.

The plurality of (three) blades 21b are arranged at regular intervals along the rotational direction Y of the blade member 21, as shown in FIG. Here, the chord length Lα, projected area, and mounting angle θ1 of each blade 21b are the same. Note that the "mounting angle θ1" is the angle formed by the blade blade 21b and the rotation direction Y of the blade member 21 when the blade member 21 is viewed from the side, as shown in FIG. The chord length Lα, projected area, mounting angle θ1, etc. of the vane 21b can be arbitrarily set depending on the size of the housing 10, the hub 21a, etc. In Example 1, the diameter (outer diameter) R1 of the blade member 21 is approximately 80 mm, the diameter (outer diameter) R2 of the hub 21a is approximately 33 mm, the chord length Lα is approximately 58 mm, and the projected area of the blade member 21 is approximately 3000 ^mm2. is set to . Furthermore, when the wing member 21 is placed in the housing 10, the radial gap K1 (see FIG. 4) that occurs between the wing member 21 and the housing 10 is set to about 1.3 mm in the first embodiment. There is.

Furthermore, in the clothing fan 1 of Example 1, based on the results of the first experiment shown in FIG. 8, the length in the axial direction X of each blade 21b (hereinafter referred to as "blade length L1") is The length is set to be 32% to 38% of the maximum length of the housing 10 in the axial direction X (hereinafter referred to as "housing length L2"). That is, in the clothing fan 1 of Example 1, the ratio (ratio) of the blade length L1 to the housing length L2 is set in the range of 32% to 38%.

Here, the "blade length L1" is the length of each blade 21b along the axial direction X, as shown in FIG. Moreover, "housing length L2" is the maximum length from the outer surface 11x of the suction port guard part 11 to the outer surface 12x of the outlet guard part 12, as shown in FIG.

In addition, the "first experiment" refers to the housing length L2 and the maximum length in the axial direction In this experiment, the air volume was measured by setting the blade length L1 as a fixed value (see FIG. 4) and appropriately setting the blade length L1. Specifically, in the first experiment, the housing length L2 was set to the same length as an existing clothing fan (approximately 50 mm), and the ratio of the suction side spatial distance L3 to the housing length L2 was set to 18. Set to 5%. Then, the air volume was measured by appropriately changing the ratio of the blade length L1 to the housing length L2.

Note that if the housing length L2 increases, the size and mass of the clothes fan 1 inside the clothes will increase, and the comfort of use will deteriorate. Moreover, when the housing length L2 is reduced, the size of the blade length L1 is regulated. Therefore, the housing length L2 is set to a fixed value. Further, the suction side spatial distance L3 is set to a fixed value because increasing or decreasing it affects abnormal noise.

In addition, in the first experiment, in addition to measuring the air volume, the tip of a test finger was inserted into the air outlet 3 to verify whether the tip came into contact with the blade 21b. Note that the "test finger" is a test finger defined by JIS (Japanese Industrial Standards) regulations (for example, JIS C0920), and here, it is a joint with a diameter of 12 mm and a length of 80 mm. The test finger shall be

As a result of the first experiment, when the electric motor 22 is set to a predetermined output (7.8 V in this case), the air volume is equal to or greater than the amount of air (2.1 m ³ /min in this case) equivalent to the strong operation of an existing clothing fan. It has been found that the "ratio of the blade length L1 to the housing length L2" at which the air volume of 1000 is obtained is in the range of 32% or more. In addition, in FIG. 8, the relationship between the ratio of the blade length L1 to the housing length L2 and the air volume is shown by a solid line. On the other hand, it was found that the "ratio of the blade length L1 to the housing length L2" at which the blade 21b is not touched when a test finger is inserted through the air outlet 3 is in the range of 38% or less.

As a result, in the clothing fan 1 of Example 1, the blade length L1 was set to 32% to 38% of the housing length L2. Note that the blade length L1 shown in FIG. 4 is set to about 37.3% of the housing length L2.

Moreover, in FIG. 8, the relationship between the "ratio of the blade length L1 to the housing length L2" and the "air blowing efficiency" is shown by a broken line. “Air blowing efficiency” is a value obtained by dividing the air volume Q by the load torque Tr acting on the electric motor 22. As is clear from FIG. 8, from the relationship between the "ratio of the blade length L1 to the housing length L2" and the "blow efficiency" indicated by the broken line, the ratio of the blade length L1 to the housing length L2 is determined. It was found that the slope (rate of change) of air blowing efficiency becomes gentle when the ratio is in the range of 32% to 38%.

Furthermore, in the clothing fan 1 of Example 1, the suction side spatial distance L3 is set to be 18% or more of the housing length L2, based on the results of the second experiment shown in FIG.

Here, the "second experiment" is based on the blade length L1 and the maximum length in the axial direction (see FIG. 4) is set as a fixed value, the suction side spatial distance L3 is appropriately set, and the difference in height of the sound pressure level at a specific frequency is measured.

In general, humans are particularly sensitive to sounds at frequencies of 1000 to 4000 Hz within the audible frequency range (20 Hz to 200000 Hz). Further, at specific frequencies (Nz×10 [Hz] and Nz×11 [Hz]), if the height difference in the sound pressure level exceeds 10 dB, it is likely to be recognized as abnormal noise. Note that "Nz" is an integrated value of the number of rotations of the blade member 21 and the number of blades 21b.

On the other hand, as a result of the second experiment, it was found that the "housing" can suppress the difference in sound pressure level to around 10 dB at specific frequencies (Nz × 10 [Hz] and Nz × 11 [Hz]), which is not recognized as abnormal noise. It was found that the ratio of the suction side spatial distance L3 to the length L2 was in the range of 18% or more. As a result, in the clothing fan 1 of Example 1, the suction side spatial distance L3 was set to be 18% or more of the housing length L2. Note that the suction side spatial distance L3 shown in FIG. 4 is set to approximately 18.5% of the housing length L2.

In the clothing fan 1 of Example 1, the blowout side spatial distance L4 is defined depending on the blade length L1, the housing length L2, and the suction side spatial distance L3. The air outlet side spatial distance L4 shown in FIG. 4 is set to approximately 38.2% (35% or more) of the housing length L2.

The electric motor 22 is driven by receiving power from a battery (not shown), and rotates a rotating shaft 22a. The electric motor 22 is housed in the motor housing part 12a of the outlet guard part 12, and the rotating shaft 22a protrudes from the through hole 12e. Further, in the first embodiment, the lid body 22b that closes the motor storage part 12a is attached to the outer cylinder member 10B while the electric motor 22 is stored in the motor storage part 12a.

As shown in FIG. 3, the fixing member 30 has an annular ring portion 31 and a female thread groove 32 formed on the inner peripheral surface of the ring portion 31. The inner diameter of the ring portion 31 substantially matches the outer diameter of the outer cylinder member 10B, and the female thread groove 32 can be screwed into the male thread groove 14. Further, the outer diameter of the ring portion 31 is larger than the inner diameter of the opening 102 formed in the garment 100. Therefore, as shown in FIGS. 2 and 4, the fixing member 30 is fitted into the housing 10 with the outlet 3 side of the housing 10 inserted into the opening 102, and the female thread groove 32 is inserted into the male thread groove 102. When screwed together, the ring portion 31 presses the peripheral edge 103 of the opening 102 toward the flange portion 13 of the housing 10 .

Note that a plurality of concave portions 31a are formed on the outer circumferential surface of the ring portion 31 and are concave inwardly in an arc shape. The recesses 31a are used for the user to hang his or her fingers when grasping the ring portion 31, and are arranged at regular intervals over the entire circumference of the ring portion 31.

Hereinafter, the functions of the clothing fan 1 and the clothing 100 of Example 1 will be explained.

In the clothing fan 1 of Example 1, a fan main body 20 is disposed inside a housing 10 having an inlet 2 and an outlet 3 facing the inlet 2. The length in the axial direction X of the blades 21b of the fan body 20 (blade length L1) is 32% to 38% of the maximum length in the axial direction X of the housing 10 (housing length L2). It is set to

As a result, in the clothing fan 1 of Example 1, as is clear from the results of the first experiment shown in FIG. 8, when the electric motor 22 is set to a predetermined output (7.8V), It is possible to obtain an air volume equal to or greater than the air volume (2.1 m ³ /min) equivalent to when a commercial fan is operated at high speed, and to prevent the test finger from entering through the air outlet 3.

The clothing fan 1 of Example 1 has the ability to extend the mounting portion of the blade 21b, as compared to the clothing fan A of the first comparative example shown in FIGS. 10(a) and 10(b), for example. Therefore, the number of blades 21b can be reduced. Moreover, the clothing fan 1 of Example 1 can have a larger mounting angle θ1 of the blades 21b than the clothing fan A of the first comparative example. Note that the clothing fan A of the first comparative example has nine blades 21b, and the blade length L1 is set to be 32% or less (approximately 16.1%) of the housing length L2. be. Furthermore, the insertion length L of the clothing fan A of the first comparative example into the clothing 100 is set to be the same length as the insertion length L of the clothing fan 1 of the first embodiment.

In the clothing fan 1 of Example 1, since the mounting angle θ1 can be increased, an efficient (highly efficient) mounting angle θ1 can be set for blowing air. Therefore, as shown in FIG. 11, the clothing fan 1 of Example 1 increases the air volume more than the clothing fan A of the first comparative example even if the motor output of the electric motor 22 is the same. be able to. That is, the clothing fan 1 of Example 1 can improve the air blowing ability more than the clothing fan A of the first comparative example. In addition, in FIG. 11, the relationship between the air volume and the noise value in the clothing fan 1 of Example 1 is shown by a solid line, and the relationship between the air volume and noise value in the clothing fan A of the first comparative example is shown by a broken line. ing. In FIG. 11, when the motor output of the electric motor 22 is the same for the clothing fan 1 of Example 1 and the clothing fan A of the first comparative example, the relationship between the air volume and the noise value is shown in the same plot shape. ing.

Moreover, the number of blades 21b that the clothes fan 1 of Example 1 has is three, which is smaller than the number (nine) of blades 21b that the clothes fan A of the first comparative example has. In other words, the clothes fan 1 of the first embodiment can increase the air volume without increasing the number of blades 21b. Therefore, it is possible to suppress an increase in turbulence noise depending on the number of blades 21b.

Moreover, in the clothing fan A of the first comparative example, the insertion length L into the clothing 100 is set to be the same length as the insertion length L of the clothing fan 1 of the first embodiment. Therefore, in the clothing fan 1 of Example 1, the axial dimension of the housing 10 inside the clothing 100 (dimension inside the clothing) is different from that of the clothing fan A of the first comparative example in the axial direction of the housing 10 inside the clothing 100. The dimensions are the same.

Therefore, the clothing fan 1 of Example 1 can improve the air blowing ability without increasing the axial dimension of the housing 10, and can suppress an increase in noise.

Furthermore, in the clothing fan 1 of Example 1, since the blade length L1 was set to 32% to 38% of the housing length L2, the slope (rate of change) of the air blowing efficiency was made gentler. (See Figure 8). Therefore, the clothing fan 1 of Example 1 can suppress a decrease in air blowing efficiency with respect to an increase in air volume.

In addition, in the clothing fan 1, in the wake region S that occurs downstream of the suction side crosspiece member 11b or the auxiliary crosspiece member 11d, the flow velocity of air passing between the suction side crosspiece member 11b and the auxiliary crosspiece member 11d (intake port 2) The flow velocity is lower than that of Therefore, the external force acting on the blade 21b is different when the blade 21b passes through the wake region S and when the blade 21b passes through the suction port 2. Generally, when the external force acting on the blade 21b changes periodically, the blade 21b is excited and vibrates at a constant frequency. Then, the air propagated by the blades 21b vibrating at a constant frequency generates a sound with a specific frequency component, which is recognized as abnormal noise.

Note that FIG. 12 shows the relationship between the frequency and the sound pressure level in the clothing fan of the second comparative example. The clothing fan of the second comparative example has three blades 21b and the suction side spatial distance L3 is set to 7.2 mm. In the case of the clothing fan of the second comparative example, as shown by the broken line in FIG. 12, when the height difference H in the sound pressure level becomes large at a specific frequency (approximately 2500 Hz), it is recognized as a harsh abnormal noise. Put it away.

On the other hand, FIG. 13(a) shows the relationship between the frequency and the sound pressure level in a third comparative example of a clothing fan in which the number of blades 21b is three and the suction side spatial distance L3 is set to 9.7 mm. There is. Further, FIG. 13(b) shows the relationship between the frequency and the sound pressure level in a fourth comparative example of a clothing fan in which the number of blades 21b is three and the suction side spatial distance L3 is set to 12.2 mm. There is.

Here, as is clear from FIGS. 12 and 13(a) and (b), in the clothing fan, the larger the suction side spatial distance L3 is set, the lower the sound pressure level at a specific frequency (approximately 2500 Hz). The height difference H can be suppressed. In other words, in the clothing fan, the larger the suction side spatial distance L3, the more the generation of abnormal noise can be suppressed.

On the other hand, in the clothing fan 1 of Example 1, the maximum length in the axial direction X from each blade 21b to the inner surface 11y of the suction port guard portion 11 (suction side spatial distance L3) is The length is set to 18% or more of the Therefore, the clothing fan 1 of Example 1 prevents the suction side spatial distance L3 from becoming too small, and as is clear from the results of the second experiment shown in FIG. Hz] and Nz×11 [Hz]), the height difference H of the sound pressure level can be suppressed to about 10 dB. Thereby, the clothing fan 1 of Example 1 can suppress the height difference H of the sound pressure level at a specific frequency (approximately 2500 Hz) and suppress the generation of abnormal noise.

In the clothing fan 1, when the blades 21b are close to the air outlet 3 and the air outlet side spatial distance L4 becomes small, the air outlet side It becomes necessary to reduce the slope of the crosspiece member 12b. In other words, it is necessary to suppress the amount of bulge of the outlet guard portion 12 toward the outside of the housing 10 . However, if the inclination of the blow-off side crosspiece members 12b is made gentler, the interval between the blow-off side crosspiece members 12b becomes narrower, and the opening area of the blower outlet 3 becomes smaller. As a result, a problem arises in that the air blowing performance of the clothing fan 1 deteriorates. That is, in the clothing fan 1, generally, the smaller the air outlet side spatial distance L4 becomes, the smaller the opening area of the air outlet 3 becomes, and the air blowing performance deteriorates.

On the other hand, in the clothing fan 1 of Example 1, the maximum length in the axial direction The length is set to approximately 38.2% (more than 35%) of the total length. Therefore, in the clothing fan 1 of the first embodiment, there is no need to make the slope of the blow-out side cross member 12b gentle, and the blow-out side spatial distance L4 is prevented from becoming too small, thereby suppressing the deterioration of the air blowing performance. I can do it.

Further, in the clothing fan 1 of the first embodiment, three blades 21b are provided around the hub 21a at equal intervals along the rotational direction Y of the blade member 21. This makes it possible to suppress turbulence noise, which increases depending on the number of blades 21b. Note that, as is clear from FIG. 11, the clothing fan 1 of Example 1 has the same motor output of the electric motor 22 as the clothing fan A of the first comparative example, which has nine blades 21b. It is possible to reduce the noise value more than Moreover, the clothing fan 1 of Example 1 can reduce the noise value compared to the clothing fan A of the first comparative example even if the air volume is the same.

Furthermore, in the clothing fan 1 of Example 1, when the blade member 21 (blade 21b) rotates, the front end edge 23 of each of the plurality of (three) blades 21b in the rotation direction Y is moved from the axial direction The suction side crosspiece member 11b or the auxiliary crosspiece member 11d is arranged at a position where the timing of overlapping with the suction side crosspiece member 11b or the auxiliary crosspiece member 11d is asynchronous. That is, the suction side crosspiece member 11b or the auxiliary crosspiece member 11d of the first embodiment are arranged at uneven pitches along the rotational direction Y of the blade member 21 (blade blade 21b).

Here, in FIG. 14, there are three blades 21b, and the suction side crosspiece member 11b or the auxiliary crosspiece member 11d are arranged at equal pitches along the rotational direction Y of the blade member 21 (the blade 21b). The relationship between the frequency and the sound pressure level in the clothing fan of the fifth comparative example is shown. In the clothing fan of the fifth comparative example, the suction side crosspiece member 11b or the auxiliary crosspiece member 11d are arranged at equal pitches along the rotational direction Y of the blade member 21 (blade blade 21b), so that the blade member 21 When rotated, the timing at which the front edge 23 of each of the three blades 21b in the rotational direction Y overlaps with the suction side bar member 11b or the auxiliary bar member 11d when viewed from the axial direction X is synchronized. Therefore, as shown by the broken line in FIG. 14, the range in which the height difference H of the sound pressure level is relatively large is concentrated around a specific frequency (approximately 2500 Hz), and is recognized as an abnormal sound.

On the other hand, in FIG. 15, there are three blades, and the suction side crosspiece member 11b or the auxiliary crosspiece member 11d are arranged at uneven pitches along the rotational direction Y of the blade member 21 (blade blade 21b). The relationship between frequency and sound pressure level in the clothing fan of the sixth comparative example is shown. Here, in the clothing fan of the sixth comparative example, since the suction side crosspiece member 11b or the auxiliary crosspiece member 11d has an uneven pitch, the front end edge 23 of each of the three blades 21b in the rotation direction Y is When viewed from the axial direction X, the timing at which the suction side crosspiece member 11b or the auxiliary crosspiece member 11d overlaps is asynchronous. Therefore, as shown by the broken line in FIG. 15, in the clothing fan of the sixth comparative example, the range in which the height difference H of the sound pressure level is relatively large is concentrated around a specific frequency (approximately 2500 Hz). It also disperses to other frequencies. Therefore, sounds generated at specific frequencies are less noticeable and are less likely to be recognized as abnormal sounds.

Also in the clothing fan 1 of the first embodiment, when the blades 21b rotate, the front end edges 23 of each of the plurality of (three) blades 21b in the rotation direction Y are aligned with the suction side crosspiece member when viewed from the axial direction X. The suction side crosspiece member 11b and the auxiliary crosspiece member 11d are arranged at positions where the timing of overlapping with the suction side crosspiece member 11b or the auxiliary crosspiece member 11d is asynchronous. Therefore, in the clothing fan 1 of the first embodiment, similarly to the blower fan of the sixth modification, the range in which the height difference H of the sound pressure level is relatively large is not concentrated around a specific frequency (approximately 2500 Hz). , can also be distributed over other frequencies. As a result, the clothing fan 1 of Example 1 can suppress the generation of abnormal noise.

To attach the clothing fan 1 to the clothing 100 of the first embodiment, the user first separates the housing 10 and the fixing member 30, grips the housing 10 with one hand, and uses the other hand to Grip the fixing member 30. At this time, the user holds the housing 10 with the outlet guard section 12 facing the clothing 100.

Next, the user inserts the housing 10 into the opening 102 formed in the clothing 100 from the outside of the clothing 100, and inserts the housing 10 into the clothing 100 through the outlet guard part 12. Then, the user fits the ring portion 31 of the fixing member 30 into the housing 10 inside the garment 100, and screws the female thread groove 32 formed on the inner peripheral surface of the ring portion 31 into the male thread groove 14.

As a result, the ring portion 31 presses the peripheral edge 103 of the opening 102 formed in the garment 100 toward the flange portion 13 of the housing 10 . Then, the peripheral edge 103 of the opening 102 is sandwiched between the ring part 31 and the flange part 13, and the clothing fan 1 is attached to the clothing 100.

That is, the clothing 100 of Example 1 is formed with an opening 102 into which the clothing fan 1 of Example 1 described above can be attached. Then, as described above, when the user inserts the housing 10 of the clothing fan 1 into the opening 102 and screws the ring part 31 into the housing 10, the peripheral edge of the opening 102 formed in the clothing 100 103 is sandwiched between the flange portion 13 and the ring portion 31, and the clothing fan 1 is attached to the clothing 100. As a result, the garment 100 of the first embodiment can be equipped with the clothing fan 1 of the first embodiment, which can improve the air blowing ability and suppress an increase in noise without increasing the axial dimension of the housing 10.

Although the clothing fan 1 and clothing 100 of the present invention have been described above based on the first embodiment, the specific configuration is not limited to the first embodiment, and the gist of the invention according to each claim is explained below. Changes and additions to the design are permitted as long as they do not deviate.

In the clothing fan 1 of the first embodiment, when the fixing member 30 is fitted into the housing 10 and the female screw groove 32 is screwed into the male screw groove 14, the ring portion 31 connects the peripheral edge 103 of the opening 102 to the housing. 10 toward the flange portion 13 side. At this time, since the flange portion 13 is also pressed, a force directed toward the outside of the housing 10 acts on the inner cylinder member 10A in which the flange portion 13 is formed. As a result, the housing 10 is deformed, and the claw pieces 16a forming the engagement structure 10C interfere with the recesses 16b formed in the outer cylinder member 10B. For this reason, there is a possibility that the side wall 10x of the inner cylinder member 10A will fall down inside the housing 10, the claw piece 16a will come off, and the inner cylinder member 10A and the outer cylinder member 10B will separate.

Therefore, as in a clothing fan 1A of a first modification example shown in FIG. 16, an auxiliary flange portion 15 may be formed at the outer peripheral edge of the open end of an outer cylinder member 10B into which the inner cylinder member 10A is inserted. Here, the auxiliary flange portion 15 is a flat plate that projects outward from the housing 10 along the radial direction from the circumferential surface of the open end of the outer cylinder member 10B, and here, the auxiliary flange portion 15 has a shorter radial length than the flange portion 13. (See Figure 16).

As a result, in the clothing fan 1A of the first modification, as the ring portion 31 is tightened, the ring portion 31 presses the flange portion 13 via the auxiliary flange portion 15. As a result, the inner cylindrical member 10A and the outer cylindrical member 10B are pushed together, so that the side wall 10x of the inner cylindrical member 10A, on which the flange portion 13 is formed, does not fall inside the housing 10. As a result, the clothing fan 1 of Example 1 can prevent the claw pieces 16a constituting the engagement structure 10C from coming off the recess 16b, and by tightening the ring part 31, the inner cylinder member 10A and the outer cylinder member Separation from 10B can be prevented.

Further, in the clothing fan 1 of Example 1, there are three blades 21b, the diameter (outer diameter) R1 of the blade member 21 is about 80 mm, the diameter (outer diameter) R2 of the hub 21a is about 33 mm, and the chord length Lα. An example was shown in which the projected area of the wing member 21 was set to about 58 mm, the projected area of the wing member 21 was set to about 3000 mm ² , and the radial gap K1 created between the wing member 21 and the housing 10 was set to about 1.3 mm. Further, the blade length L1 is set to about 37.3% of the housing length L2, the suction side space distance L3 is set to about 18.5% of the housing length L2, An example is shown in which the air outlet side spatial distance L4 is set to approximately 38.2% of the housing length L2.

However, these values are not limited to the values described in Example 1, and the clothing fan of the present invention has at least a blade length L1 of 32% to 38% of the housing length L2. The number of blades 21b, the suction side spatial distance L3, the blowout side spatial distance L4, etc. can be set arbitrarily.

Moreover, although the example of the clothing 100 of Example 1 is shown as a jacket worn by the wearer on the upper body, the clothing 100 is not limited to this. The clothing 100 only needs to have an opening 102 to which the clothing fan 1 can be attached, and may be, for example, pants or coveralls.

1 Clothes fan 2 Suction port 3 Air outlet 10 Housing 10A Inner cylinder member 10B Outer cylinder member 10C Engagement structure 11 Suction port guard portion 11b Suction side crosspiece member (crosspiece member)
12 Outlet guard part 13 Flange part 14 Male thread groove (thread groove)
15 Auxiliary flange portion 20 Fan main body 21 Wing member 21a Hub 21b Blade blade 22 Electric motor 23 Front edge 24 Rear edge 30 Fixed member K1 Radial gap L1 generated between the blade member and housing Blade length (vane blade axial length)
L2 Housing length (maximum axial length of housing)
L3 Suction side spatial distance (maximum length from the blade to the inner surface of the suction port guard)
L4 Air outlet side distance (maximum length from the blade to the outer surface of the outlet guard part)
100 Clothes 101 Back Body 102 Opening

Claims (6)

A clothing fan attached to an opening formed in clothing,
a hollow housing having a suction port in which a suction port guard portion is formed; and an air outlet facing the suction port and in which a blowout port guard portion is formed;
a fan body disposed inside the housing and having a plurality of blades rotated by an actuator;
When the direction in which the suction port and the blowout port face each other is defined as the axial direction, the length of the blade in the axial direction is 32% to 38% of the maximum length of the housing in the axial direction. A clothing fan characterized by being set to . The clothing fan according to claim 1,
The maximum length in the axial direction from the blade to the inner surface of the suction port guard portion is set to be 18% or more of the length of the housing in the axial direction. fan. In the clothing fan according to claim 1 or claim 2,
A fan for clothing, characterized in that the blades are provided in three pieces at equal intervals along the rotation direction. In the clothing fan according to claim 1 or claim 2,
The suction port guard portion includes a plurality of crosspiece members extending in the radial direction and arranged in parallel along the rotational direction of the blade,
The crosspiece member is arranged at a position such that when the blade rotates, the timing at which the front end edge of each of the plurality of blades in the rotation direction overlaps the crosspiece member when viewed from the axial direction is asynchronous. A clothing fan characterized by: In the clothing fan according to claim 1 or claim 2,
In the housing, a cylindrical inner cylinder member having the suction port guard formed at one end is inserted into a cylindrical outer cylinder member having the air outlet guard formed at one end through an engagement structure. formed by being fixed,
The inner cylindrical member has a flange formed on the outer peripheral edge of the suction port guard portion, and the outer cylindrical member has a threaded groove formed on its outer peripheral surface into which a fixing member for attaching the housing to the clothing is screwed. A fan for clothes, characterized in that an auxiliary flange portion that abuts the flange portion is formed on the outer peripheral edge of the other end into which the inner cylindrical member is inserted. a hollow housing having a suction port having a suction port guard portion formed therein; and an air outlet facing the suction port and having a blowout port guard portion formed therein; and a hollow housing arranged inside the housing and rotated by an actuator. a fan body having a plurality of blades, and when the direction in which the suction port and the blowout port face each other is defined as an axial direction, the length of the blade in the axial direction is equal to the length of the fan body in the axial direction of the housing. A garment characterized in that an opening is formed into which a garment fan having a length of 32% to 38% of the maximum length of the garment can be attached.