JP6976918B2 - Blower and air conditioner - Google Patents

Description

The present invention relates to a blower and an air conditioner including a blower.

As a blower used in an air conditioner for a vehicle, one using an impeller is known. The impeller is arranged in a scroll housing having a suction port and a discharge port. Then, by rotating the impeller, the blower takes in air into the scroll housing through the suction port and discharges the air through the discharge port.

Since the above-mentioned blower generates noise such as wind noise due to the impeller, it is required to suppress the leakage of the above noise into the interior of the vehicle. In the blower described in Patent Document 1, noise is reduced by providing a resonance chamber. The resonance chamber is adjacent to the scroll housing, and its internal space communicates with the internal space of the scroll housing through an opening.

By the way, the frequency characteristic of the noise generated by the above-mentioned blower changes depending on the operating conditions of the blower and the air conditioner. Therefore, the frequency of the sound to be muted in the resonance chamber in order to effectively reduce the noise also changes depending on the operating conditions of the blower and the air conditioner. However, the above-mentioned resonance chamber can mute only the sound of a predetermined frequency.

Japanese Unexamined Patent Publication No. 7-228128

It is an object of the present invention to provide a blower and an air conditioner having a resonance chamber capable of changing the frequency of the sound to be muted.

According to a preferred embodiment of the invention
A blower used in vehicle air conditioners,
An impeller that has multiple blades forming a circumferential blade row and is rotationally driven by the rotation axis of the motor.
A scroll housing having an internal space for accommodating the impeller, a suction port opening in the axial direction of the rotating shaft, and a discharge port opening in the circumferential direction of the impeller.
An air intake housing having an internal space communicating with the suction port of the scroll housing, the air intake housing having at least one outside air inlet for taking in outside air into the internal space of the air intake housing, and the air intake housing. The air intake housing provided with at least one inside air intake for taking in the inside air into the internal space, and the air intake housing.
At least one switching door that opens and closes the outside air intake and the inside air intake, and
In those equipped with
The inside of the air intake housing communicates with the internal space of the air intake housing through a communication port provided on the suction port side of the outside air intake port and along the raceway surface of the switching door. There is a resonance chamber with space,
The switching door provides a blower capable of closing the communication port at least partially while closing the outside air intake and changing the opening area of the communication port.

Alternatively, according to a preferred embodiment of the present invention, there is provided an air conditioner for a vehicle including the above-mentioned blower and an air conditioning unit that blows air sent from the blower into the interior of the vehicle.

According to the above embodiment of the present invention, it is possible to provide a blower and an air conditioner having a resonance chamber capable of changing the frequency of the sound to be muted.

It is a figure which shows typically the structure of the air conditioner by one Embodiment of this invention. It is a perspective view of the blower shown in FIG. It is a figure which shows typically the cross section of the blower shown in FIG. FIG. 3 is an enlarged view showing a cross section of the air intake housing shown in FIG. 3 and shows a case where the switching door is in the first position. It is a figure which shows the frequency characteristic curve of the noise obtained when the air conditioner is operated in a foot mode and a vent mode. It is a figure which shows the frequency characteristic curve of the noise obtained when the blower which does not provide a resonance chamber is used, and when it is used with the blower shown in FIG. It is a figure corresponding to FIG. 1, and is the figure which shows typically the structure of the air conditioner according to the modification 1 of this invention. It is a figure which shows the frequency characteristic curve of the noise obtained when the rotation speed of an impeller is fast and when it is slow. It is a figure corresponding to FIG. 1, and is the figure which shows typically the structure of the air-conditioning apparatus according to the modification 2 of this invention. FIG. 4 is a view corresponding to FIG. 4, which is an enlarged view showing a cross section of an air intake housing of a blower according to a modification 3 of the present invention. It is a perspective view of the switching door of the blower shown in FIG. FIG. 4 is a view corresponding to FIG. 4, which is an enlarged view showing a cross section of an air intake housing of a blower according to a modification 4 of the present invention. 12 is a partial cross-sectional view showing a cross section of the blower of FIG. 12 along the I-I line.

An embodiment of the present invention will be described below with reference to the accompanying drawings.

FIG. 1 is a diagram schematically showing a structure of an air conditioner according to an embodiment of the present invention. 2 and 3 are a perspective view of the blower shown in FIG. 1 and a diagram schematically showing a cross section of the blower shown in FIG. 2, respectively. FIG. 3 shows a cross section perpendicular to the turning axis Bx of the switching door described later. FIG. 4 is an enlarged view showing a cross section of the air intake housing shown in FIG. 3, and is a view showing a case where the switching door is in the first position. For the sake of clarification, the control device described later is not shown in FIGS. 2 and 3. Further, in FIG. 2, illustration of an impeller, a filter, etc., which will be described later, is omitted. In each figure, U means the upper part of the vehicle, D means the lower part of the vehicle, Fr means the front side of the vehicle, Rr means the rear side of the vehicle, R means the right side of the vehicle, and L means the left side of the vehicle. However, the installation direction of the blower and the air conditioning unit described later with respect to the vehicle is not limited to the illustrated example.

As shown in FIG. 1, the air conditioner 1 for a vehicle includes a blower 2 and an air conditioning unit 3 that blows air sent from the blower 2 into the interior of the vehicle.

As shown in FIGS. 1 and 3, the blower 2 has an impeller 4. The impeller 4 has a plurality of blades 4a forming a row of blades arranged in the circumferential direction on the outer peripheral portion thereof. The impeller 4 is connected to the rotation shaft 5a of the motor 5, is rotationally driven around the rotation axis Ax, and is sucked into the space inside the radial direction of the blade row of the impeller 4 from the upper side in the axial direction (one end side in the axial direction). Blows air outward in the radial direction.

In the present specification, for convenience of explanation, the direction of the rotation axis Ax of the motor 5 and the impeller 4 is referred to as "axial direction". In the following explanation, the explanation is based on the assumption that the axial direction coincides with the vertical direction, but it should be noted that the air conditioner may be incorporated in the vehicle so that the axial direction forms an angle with respect to the vertical direction. Should be. In the present specification, unless otherwise specified, the direction of the radius of a circle drawn on a plane orthogonal to the rotation axis Ax around an arbitrary point on the rotation axis Ax is referred to as a radial direction, and the direction of the radius of the circle is called the radial direction. The circumferential direction is called the circumferential direction or the circumferential direction.

As shown in FIG. 3, the impeller 4 includes a cone portion (inner deflection member) 4b integrally molded with the impeller 4. The cone portion 4b is a rotating body in a geometrical sense. At the central portion of the cone portion 4b, the rotating shaft 5a of the motor 5 is connected to the impeller 4. In the air conditioner 1 shown in FIG. 1, the rotation speed of the motor 5 is controlled by the motor control unit 8a.

As shown in FIG. 1, the impeller 4 is housed inside the scroll housing 6. As shown in FIGS. 2 and 3, the scroll housing 6 has a suction port 6a that opens upward in the axial direction and a discharge port 6b. When the scroll housing 6 is viewed from the axial direction, the discharge port 6b extends substantially in the tangential direction of the outer peripheral surface of the scroll housing 6.

As shown in FIG. 1, the blower 2 also has an air intake housing 10 connected to the scroll housing 6. The internal space of the air intake housing 10 communicates with the suction port 6a of the scroll housing 6. As shown in FIG. 2, the air intake housing 10 has an outside air intake 11 that opens substantially forward and an inside air intake 12 that opens substantially rearward. The shyness inlet 12 may be generally leftward and rightward or open. A cylindrical outside air intake duct 20 having openings at both ends is connected to the outside air intake port 11. The outside air intake duct 20 is connected to the outside air intake port 11 at one of the openings 21, and extends from the outside air intake port 11 to the side opposite to the internal space of the air intake housing 10 (generally forward and upward). There is. As shown in FIG. 2, the outside air intake duct 20 may be integrated with the air intake housing 10. The other opening 22 of the outside air intake duct 20 is connected to or near the outlet (not shown) of the outside air introduction path provided in the vehicle. The outside air (air taken from the outside of the vehicle) can be efficiently introduced into the air intake housing 10 through the outside air intake duct 20. The inside air intake port 12 is open inside the vehicle interior, and the inside air (vehicle interior air) can be introduced into the air intake housing 10.

Inside the air intake housing 10, a switching door 50 for opening and closing the outside air intake port 11 and the inside air intake port 12 is provided. In the illustrated example, the switching door 50 has a type called a rotary switching door, and as can be understood from FIG. 2, it has the shape of a prism having a fan-shaped bottom surface as a whole. The switching door 50 has a peripheral surface 51 having an arc-shaped cross section centered on the turning axis Bx, and fan-shaped side surfaces 52 connected to the left and right sides of the peripheral surface 51. The switching door 50 can be swiveled by an actuator (not shown) about the swivel axis Bx extending in the left-right direction. In the examples shown in FIGS. 3 and 4, the raceway surface S of the peripheral surface 51 of the switching door 50 has an arc shape in a cross section perpendicular to the turning axis Bx. The outside air intake port 11 and the inside air intake port 12 described above are open along the raceway surface S. Then, the switching door 50 closes the outside air intake 11 (inside air intake 12) by making its peripheral surface 51 face the outside air intake 11 (inside air intake 12), and closes the outside air intake 12 (outside air intake 12). 11) can be opened. The switching door 50 has a first position (see FIG. 4) that opens the inside air intake 12 and closes the outside air intake 11 and a second position (see FIG. 3) that opens the outside air intake 11 and closes the inside air intake 12. ), It is possible to move along the inner surface of the air intake housing 10.

When the blower 2 is operated in the inside air mode, the switching door 50 is arranged at the first position as shown in FIG. At this time, the inside air AR is introduced into the air intake housing 10 from the inside air intake port 12. Further, when the blower 2 is operated in the outside air mode, the switching door 50 is arranged at the second position as shown in FIG. At this time, the outside air AE is introduced into the air intake housing 10 from the outside air intake port 11. The inside air AR introduced into the air intake housing 10 from the inside air intake port 12 and the outside air AE introduced into the air intake housing 10 from the outside air intake port 11 are from the suction port 6a of the scroll housing 6 to the impeller 4. It flows into the space inside the radial direction of the blade row.

Between the area of the air intake housing 10 where the outside air intake 11 and the inside air intake 12 are provided and the lower end of the air intake housing 10 (the end connected to the suction port 6a of the scroll housing 6). Is provided with a filter 13 for removing pollutants such as dust and particles and an offensive odor contained in the air. The filter 13 is inserted into a filter support portion 14 formed of a slot or rail provided in the air intake housing 10, and is held at a position close to the suction port 6a of the scroll housing 6.

Next, the air conditioning unit 3 will be described with reference to FIG. The air conditioning unit 3 has an air conditioning case 30 that forms an air passage 3a through which air flows. An inflow port 31 connected to the discharge port 6b of the blower 2 is formed at the upstream end of the air conditioner case 30 (the left end in FIG. 1), and the air sent from the blower 2 is air-conditioned through the inflow port 31. It is designed to flow into the air passage 3a of the case 30. Further, a plurality of outlet passages 32a, 32b, 32c are formed at the downstream end portion (right end portion in FIG. 1) of the air conditioning case 30, and the air flowing into the air passage 3a is formed in the outlet passages 32a, 32b. It is designed to flow out from 32c.

The plurality of outlet passages 32a, 32b, 32c of the air conditioning case 30 include a foot outlet passage 32a, a vent outlet passage 32b, and a defrost outlet passage 32c. As shown in FIG. 1, the foot blowing passage 32a is provided in the lower portion of the downstream end surface 33a of the air conditioning case 30. The downstream end of the foot outlet aisle 32a is connected to a foot outlet (not shown) that blows air toward the feet of occupants sitting in the driver's seat and the passenger seat (and in some cases, the rear seat). Further, the vent blowing passage 32b is provided on the upper portion of the downstream end surface 33a of the air conditioning case 30. The downstream end of the vent outlet aisle 32b is connected to a vent outlet (not shown) that blows air toward the upper body of the occupant sitting in the driver's seat and the passenger seat (and in some cases, the rear seat). Further, the defrost blowing passage 32c is provided on the top surface 33b of the air conditioning case 30. The downstream end of the defrost outlet passage 32c is connected to a defrost outlet (not shown) that blows air toward the inner surface of the windshield in the vehicle interior.

Inside the air passage 3a of the air conditioning case 30, there are a cooling heat exchanger (evaporator) 35, a heating heat exchanger 36, and various doors (air mix door 7) that change the flow of air flowing through the air passage 3a. And blowout passage doors 38a, 38b, 38c) are provided.

The cooling heat exchanger 35 is provided so that all of the air flowing into the air conditioning case 30 passes through the cooling heat exchanger 35. The cooling heat exchanger 35 lowers the humidity of the air by taking heat from the air passing therethrough and condensing the moisture in the air when the humidity of the air is high.

The heating heat exchanger 36 is a detour in the air passage 3a formed by the air conditioning case 30 (above the heating heat exchanger 36 in the example shown in FIG. 1) with the inner side surface 33c of the air conditioning case 30. It is arranged so as to form 3b.

The air mix door 7 is provided between the cooling heat exchanger 35 and the heating heat exchanger 36. In the illustrated example, the air mix door 7 is a plate-shaped member and is arranged substantially parallel to the upstream surface of the heating heat exchanger 36. The air mix door 7 can slide in the air passage 3a in the vertical direction, and the opening degree of the detour 3b can be adjusted by changing the position of the air mix door 7. Then, the air mix door 7 adjusts the ratio of the air toward the heating heat exchanger 36 and the air toward the detour 3b according to the position thereof.

As shown in FIG. 1, each of the air mix doors 7 is connected to a shaft 7s extending in the air passage 3a in the left-right direction, and by rotating the shaft 7s, the air passage 3a is moved up and down in the vertical direction. You can slide along it. More specifically, one surface of each air mix door 7 is provided with a rack (not shown) from the upper end edge to the lower end edge thereof. Further, a pinion that meshes with the rack is provided on the outer peripheral surface of each shaft 7s. Then, when the shaft 7s is rotated in the circumferential direction, the rotational movement of the shaft 7s is converted into a vertical movement by the pinion and the rack, and the air mix door 7 slides up and down. The shaft 7s is rotationally driven directly or indirectly by an actuator (not shown).

As shown in FIG. 1, the outlet passage doors 38a, 38b, 38c are provided in the outlet passages 32a, 32b, 32c described above, respectively, and open and close the outlet passages 32a, 32b, 32c. Specifically, the foot outlet passage 32a is provided with a foot outlet passage door 38a, the vent outlet passage 32b is provided with a vent outlet passage door 38b, and the defrost outlet passage 32c is provided with a defrost outlet passage door 38c. There is. In the illustrated example, the outlet passage doors 38a, 38b, 38c are plate-shaped members and extend from the shafts 38as, 38bs, 38cs extending in the left-right direction. Then, when the shafts 38as, 38bs, 38cs are rotated in the circumferential direction, the outlet passage doors 38a, 38b, 38c rotate around the rotation axis of the shafts 38as, 38bs, 38cs, and the corresponding outlet passages 32a, 32b, The 32c can be opened and closed. The shafts 38as, 38bs, 38cs are rotationally driven directly or indirectly by an actuator (not shown).

The blowout passage doors 38a, 38b, 38c open or close the corresponding blowout passages 32a, 32b, 32c according to the operation mode (blowout mode) of the air conditioner 1. For example, when the air conditioner 1 is operated in the foot mode, the foot outlet passage 32a is opened, the defrost outlet passage 32c is opened and narrowed, and the vent outlet passage 32b is closed. Further, when the air conditioner 1 is operated in the vent mode, the vent outlet passage 32b is opened, and the foot outlet passage 32a and the defrost outlet passage 32c are closed.

In the example shown in FIG. 1, the air conditioner 1 further controls the door inside the air conditioner case that controls an actuator that rotationally drives the shaft 7s of the air mix door 7 and the shafts 38as, 38bs, 38cs of the outlet passage doors 38a, 38b, 38c. It has a part 8b. The door control unit 8b in the air conditioning case may be integrally configured with the motor control unit 8a.

By the way, a blower using an impeller generates noise such as wind noise due to the impeller. Therefore, it is required for such a blower and an air conditioner using the blower to suppress the noise from leaking into the vehicle interior. As a method of suppressing the noise from leaking into the vehicle interior, a method of providing a resonance chamber communicating through an opening in the scroll housing and attenuating the noise energy in the resonance chamber is known.

The resonance frequency of the resonance chamber (frequency of the sound muted in the resonance chamber) as described above is generally expressed by the following equation. Here, f is the resonance frequency (frequency of the sound muted in the resonance chamber), c is the speed of sound, A is the opening area of the opening of the resonance chamber, V is the volume of the resonance chamber, and L is the length of the opening.

In this way, the resonance chamber can mute the sound having a frequency corresponding to the volume of the resonance chamber and the size of the opening.

However, the frequency characteristics of the noise generated by the blower vary depending on the operating conditions of the blower and the air conditioner. Accordingly, the frequency of the sound to be muted in the resonance chamber in order to effectively reduce the noise also fluctuates depending on the operating conditions of the blower and the air conditioner.

For example, when an air conditioner having a blower without a resonance chamber was operated in the foot mode and the vent mode and the noise obtained in the vicinity of the inside air intake of the blower was measured, the results shown in FIG. 5 were obtained. FIG. 5 is a diagram showing the frequency characteristics of the measured noise. The horizontal axis shows the frequency, and the vertical axis shows the A characteristic sound pressure level of the 1/3 octave bandwidth filter.

As shown in FIG. 5, in the vent mode, the frequency characteristic curve forms a gentle mountain as a whole over the frequency band of 63 to 10000 Hz. In the case of noise having such frequency characteristics, the noise can be effectively reduced by muting the sound having the maximum sound pressure level (sound near 630 Hz in the example shown in FIG. 5). On the other hand, as can be understood from FIG. 5, in the foot mode, the frequency characteristic curve forms a sharp peak near 130 Hz, and forms a gentle mountain as a whole in other frequency bands. In the case of noise having such a frequency characteristic, a sound near 130 Hz in which a sound pressure level forms a sharp peak is perceived as a jarring sound. Therefore, if the sound near 130 Hz is muted, the noise can be effectively reduced. As described above, the frequency of the sound to be muted differs depending on the operation mode of the air conditioner and the like.

In consideration of the above circumstances, the illustrated blower 2 and the air conditioner 1 are provided with a resonance chamber 80 for reducing the noise generated by the blower 2. Further, in the illustrated blower 2 and air conditioner 1, the frequency of the sound muted in the resonance chamber 80 can be changed, and the noise leaks into the vehicle interior according to the operating conditions of the blower and the air conditioner. Ingenuity has been made to effectively suppress it.

First, when the blower 2 is operated in the inside air mode, the inside air intake port 12 that opens into the interior of the vehicle is opened as described above (see FIG. 4). On the other hand, when the blower 2 is operated in the outside air mode, the outside air intake 11 that opens toward the outlet of the outside air introduction path provided in the vehicle is opened, while the inside air intake 12 is closed (FIG. FIG. 3). Therefore, the noise is more likely to reach the interior of the vehicle through the inside air intake port 12 when the blower 2 is operated in the inside air mode than when the blower 2 is operated in the outside air mode. Therefore, if the noise diffused in the room when the blower 2 is operated in the inside air mode is effectively reduced according to the operating conditions of the blower 2 and the air conditioner 1, the noise leaking into the vehicle interior is remarkably suppressed. can do. In consideration of this point, in the illustrated blower 2, the resonance chamber 80 is configured so that the frequency of the sound muted in the resonance chamber 80 can be changed when the blower 2 is operated in the inside air mode. ing.

Specifically, the resonance chamber 80 is provided adjacent to the internal space of the air intake housing 10. The internal space of the resonance chamber 80 communicates with the internal space of the air intake housing 10 through the communication port 81. The communication port 81 is provided on the suction port 6a side of the scroll housing 6 with respect to the outside air intake port 11 along the raceway surface S of the switching door 50. In the example shown in FIGS. 1 to 3, the resonance chamber 80 is provided below the outside air intake duct 20, and the internal space of the resonance chamber 80 and the internal space of the air intake housing 10 are separated by a wall portion 82. ing. The communication port 81 is provided in a region of the wall portion 82 below the outside air intake 11 and above the filter 13.

Such a communication port 81 can be at least partially closed by the switching door 50 when the switching door 50 is in the first position to close the outside air intake 11. Further, the opening area of the communication port 81 can be changed by moving (turning) the switching door 50. Then, as can be understood from the above equation, the frequency of the sound that can be muted in the resonance chamber 80 can be changed by changing the opening area of the communication port 81. As a result, the sound to be muted can be appropriately muted in the resonance chamber 80 according to the operating conditions of the blower 2 and the air conditioner 1.

For example, FIG. 6 shows the blower 2 of the present embodiment shown in FIGS. 1 to 4 and the blower configured in the same manner as the blower 2 shown in FIGS. 1 to 4 except that the resonance chamber is not provided. The frequency characteristics of the noise obtained in the vicinity of the inside air intake of each blower when operated in the inside air mode are shown. In FIG. 6, the horizontal axis indicates the frequency, and the vertical axis indicates the A characteristic sound pressure level of the 1/3 octave bandwidth filter.

In the example shown in FIG. 6, as will be described later, the blower 2 of the present embodiment shown in FIGS. 1 to 4 and the blower without the resonance chamber are adjusted by the blower 2 to adjust the opening degree of the communication port 81. It was operated under similar conditions, except that it was done.

As shown in FIG. 6, the frequency characteristic curve of the noise generated by the blower without the resonance chamber forms a gentle mountain as a whole over the frequency band of 100 to 12500 Hz. In the case of noise having such frequency characteristics, the noise can be effectively reduced by muting the sound having the maximum sound pressure level (sound near 630 Hz in the example shown in FIG. 6). Therefore, when operating the blower 2 of the present embodiment shown in FIGS. 1 to 4, the opening area of the communication port 81 is adjusted so that the sound having a frequency near 630 Hz is muted in the resonance chamber 80, and the inside air intake port is adjusted. Noise was measured in the vicinity of 12. As a result, as shown in FIG. 6, the sound pressure level of the noise obtained in the vicinity of the inside air intake port 12 of the blower 2 is suppressed in the vicinity of 630 Hz as compared with the blower not provided with the resonance chamber, and is 100 to 100. The overall value in the frequency band of 12500 Hz was also reduced.

As can be understood from the example shown in FIG. 6, according to the blower 2 of the present embodiment shown in FIGS. 1 to 4, when the blower 2 is operated in the inside air mode, the sound muted in the resonance chamber 80 is heard. The frequency can be adjusted appropriately to effectively suppress the noise leaking into the vehicle interior. As can be understood from the above equation, the frequency of the sound muted in the resonance chamber 80 becomes lower as the opening area of the communication port 81 becomes smaller.

Further, according to the blower 2 of the present embodiment shown in FIGS. 1 to 4, the opening area of the communication port 81 is adjusted by the door 50 for opening and closing the outside air intake port 11 and the inside air intake port 12, so that the blower is used. No. 4 does not need to be provided with an additional door for adjusting the opening area of the communication port 81. Therefore, it is possible to prevent the structure of the blower 4 from being complicated in order to adjust the opening area of the communication port 81.

In the present embodiment, the control device 60 determines the first position according to the operating conditions of the blower 2 and the air conditioner 1. In the example shown in FIG. 1, the control device 60, in consideration of the result shown in FIG. 5, depends on the position of the blowing mode of the air conditioning unit 30 (in other words, depending on the position of at least one blowing passage door 38a, 38b, 38c). The first position of the switching door 50 is determined. Then, when the blower 2 is operated in the inside air mode, the switching door 50 is arranged at the determined first position.

Specifically, as shown in FIG. 5, and as described above, when the air conditioner 1 is operated in the vent mode and the foot mode, the sound should be muted when the air conditioner 1 is operated in the foot mode. The frequency of the sound is low. Therefore, the control device 60 of the present embodiment opens the communication port 81 when the switching door 50 is arranged at the first position when the air conditioner 1 is operated in the foot mode rather than in the vent mode. The first position is determined so that the area is small. In other words, it is movable between the foot outlet passage 32a, the upper outlet passage (vent outlet passage) 32b provided above the foot outlet passage 32a, and the position where the foot outlet passage 32a is opened and closed. In the air conditioner 1 including a foot outlet passage door 38a and an upper outlet passage door (vent outlet passage door) 38b that can be moved between a position where the upper outlet passage (vent outlet passage) 32b is opened and a position where the upper outlet passage (vent outlet passage) 32b is closed. The control device 60 is in a position where the foot outlet passage door 38a closes the foot outlet passage 32a, and the upper outlet passage door (vent outlet passage door) 38b opens the upper outlet passage (vent outlet passage) 32b. When the foot outlet passage door 38a is in a position to open the foot outlet passage 32a and the upper outlet passage door 38b is in a position to close the upper outlet passage (vent outlet passage) 32b, the switching is performed. The first position is determined so that the opening area of the communication port 81 when the door 50 is arranged at the first position is small. As a result, as can be understood from the above equation, the sound is muted in the resonance chamber 80 when the air conditioner 1 is operated in the foot mode, rather than the frequency of the sound muted in the resonance chamber 80 when the air conditioner 1 is operated in the vent mode. The frequency of the sound can be lowered.

In the example shown in FIG. 1, in the control device 60, the positions of the outlet passage doors 38a, 38b, 38c (each outlet passage door 38a, 38b, 38c are set based on the information obtained from the door control unit 8b in the air conditioning case. Whether the corresponding outlet passages 32a, 32b, 32c are in the open position or the closed position) is determined, and the first position of the switching door 50 is determined. When the control device 60 and the door control unit 8b in the air-conditioning case are integrally configured to form a composite control device (not shown), the composite control device indicates the positions of the outlet passage doors 38a, 38b, 38c. Based on the information, the first position of the switching door 50 is determined.

It is also understood that the difference in the frequency of the sound to be muted due to the difference in the operation mode shown in FIG. 5 is due to the difference in the arrangement of the air mix doors. That is, in general, the air mix door is arranged so as to maximize the opening area of the detour between the heat exchanger for heating and the inner surface of the air conditioner case when the air conditioner is operated in the vent mode. On the other hand, when operating in the foot mode, the detour is arranged so as to minimize the opening area. Also in the example shown in FIG. 5, the air mix door is arranged so as to maximize the opening area of the detour while operating in the vent mode, and minimizes the opening area of the detour while operating in the foot mode. Arranged to do. Therefore, FIG. 5 is arranged so as to minimize the opening area depending on whether the air mix door is arranged so as to maximize or minimize the opening area of the detour. It can also be understood that the case indicates that the frequency of the sound to be muted is low.

In consideration of this point, the control device 60 may determine the first position of the switching door 50 according to the position of the air mix door 7. In other words, the control device 60 is the outside air intake 11 when the switching door 50 is arranged in the first position when the air mix door 7 is in the position of closing rather than in the position of opening the detour 3b. The first position may be determined so that the opening area of the door is small. Thereby, as can be understood from the above equation, the detour is higher than the frequency of the sound muted in the resonance chamber 80 when the air mix door 7 is arranged so as to maximize the opening area of the detour 3b. When arranged so as to minimize the opening area of 3b, the frequency of the sound muted in the resonance chamber 80 can be lowered.

In this case, the control device 60 is at the position of the air mix door 7 (the position where the air mix door 7 maximizes the opening area of the detour 3b) based on the information obtained from the door control unit 8b in the air conditioning case. Or is it in the position to minimize). Further, when the control device 60 and the door control unit 8b in the air conditioning case are integrally configured to form a composite control device, the composite control device is a switching door based on the instruction information of the position of the air mix door 7. The first position of 50 may be determined.

Further, it is also understood that the difference in the frequency of the sound to be muted due to the difference in the operation mode shown in FIG. 5 is due to the difference in the ventilation resistance in the air conditioning case. That is, as described above, in the example shown in FIG. 5, when the air conditioner is operated in the vent mode, the air mix door is arranged so as to maximize the opening area of the detour, so that the ventilation resistance in the air conditioner case is maximized. However, when operating in foot mode, the air mix door was arranged so as to minimize the opening area of the detour, so the ventilation resistance inside the air conditioning case became relatively high. .. Therefore, it can be understood that FIG. 5 shows that the frequency of the sound to be muted is lower when the ventilation resistance in the air conditioning case is low and when the ventilation resistance is high. ..

In consideration of this point, in the control device 60, the higher the ventilation resistance in the air conditioning case 30, or the higher the ventilation resistance received by the air flowing out of the discharge port 6b of the scroll housing 6, the more the switching door 50 is in the first position. The first position may be determined so that the opening area of the outside air intake 11 when arranged in is small. As a result, as can be understood from the above equation, the higher the ventilation resistance, the lower the frequency of the sound muted in the resonance chamber 80.

In the embodiment described above, the blower 2 used in the air conditioner 1 for a vehicle has a plurality of blades 4a forming a circumferential blade row, and is an impeller that is rotationally driven by the rotating shaft 5a of the motor 5. Has 4. Further, the blower 2 has a scroll housing 6 having an internal space for accommodating the impeller 4, a suction port 6a opening in the axial direction of the rotary shaft 5a, and a discharge port 6b opening in the circumferential direction of the impeller 4. have. Further, the blower 2 has an air intake housing 10 having an internal space communicating with the suction port 6a of the scroll housing 6. The air intake housing 10 has at least one outside air intake 11 for taking in outside air into the internal space of the air intake housing 10, and at least one inside air intake for taking in inside space in the internal space of the air intake housing 10. An entrance 12 is provided. Further, the blower 2 has at least one switching door 50 for opening and closing the outside air intake port 11 and the inside air intake port 12. Further, the air intake housing 10 is further connected to the inside of the air intake housing 10 through a communication port 81 provided on the suction port 6a side of the outside air intake port 11 and along the raceway surface S of the switching door 50. A resonance chamber 80 having an internal space communicating with the space is provided, and the switching door 50 can at least partially close the communication port 81 while closing the outside air intake port 11, and the opening of the communication port 81. The area can be changed.

According to the blower 2 described above, the noise generated by the blower 2 can be reduced in the resonance chamber 80. Therefore, it is possible to prevent the noise from leaking into the interior of the vehicle. Further, the noise generated by the blower 2 tends to leak into the vehicle interior when the blower 2 is operated in the inside air mode, but according to the above-mentioned blower 2, the above noise is effective when the blower 2 is operated in the inside air mode. The noise can be effectively suppressed from leaking into the vehicle interior. Specifically, according to the blower 2 described above, when the blower 2 is operated in the inside air mode, the opening area of the communication port 81 can be changed by the switching door 50, and the frequency of the sound muted in the resonance chamber 80. Can be changed. As a result, when the blower 2 is operated in the inside air mode, the frequency characteristics of the noise generated by the blower 2 fluctuate according to the operating conditions of the blower 2 and the air conditioner 1, and the noise is resonated in order to effectively reduce the noise. Even if the frequency of the sound to be muted in the chamber 80 fluctuates, the sound to be muted in the resonance chamber 80 can be appropriately muted.

Further, according to the blower 2 described above, the opening area of the communication port 81 is adjusted by the switching door 50 for opening and closing the outside air intake port 11 and the inside air intake port 12, so that the opening area of the communication port 81 is adjusted to the blower 4. There is no need to provide additional doors to adjust. Therefore, it is possible to prevent the structure of the blower 4 from being complicated in order to adjust the opening area of the communication port 81.

Specifically, in the above-described embodiment, the switching door 50 has a first position for opening the inside air intake 12 and a second position for closing the inside air intake 12 along the inner surface of the air intake housing 10. It is a rotary type switching door that can move between. According to such a switching door 50, the opening area of the communication port 81 can be easily changed while closing the outside air intake port 11.

Further, in the embodiment described above, the air conditioner 1 for a vehicle includes the above-mentioned blower 2 and an air conditioning unit 3 for blowing out the air sent from the blower 2 into the interior of the vehicle.

Further, in the above-described embodiment, the blower 2 further includes a control device 60 that controls the switching door 50 and arranges it at the first position or the second position. The air conditioning unit 3 of the air conditioner 1 has an air conditioner case 30 that forms an air passage 3a through which air flows. The air conditioning case 30 has an inflow port 31 connected to the discharge port 6b of the scroll housing 6 to allow air from the blower 2 to flow in, and at least one outlet passage 32a, 32b, 32c to which air passing through the air passage 3a is blown out. And have. Further, the air conditioning unit 3 is provided for each of at least one outlet passage 32a, 32b, 32c, and at least one outlet passage that can be moved between the position where the corresponding outlet passage is opened and the position where the corresponding outlet passage is closed. It has doors 38a, 38b, 38c. Then, the control device 60 determines the first position according to the position of at least one outlet passage door 38a, 38b, 38c.

According to such an air conditioner 1, when the blower 2 is operated in the inside air mode, different sounds to be muted depending on the positions of the blowout passage doors 38a, 38b, 38c (in other words, any of the blowout passages 32a, 32b, Different sounds to be muted depending on whether 32c is opened (closed)) can be muted appropriately.

Specifically, at least one outlet passage 32a, 32b, 32c includes a foot outlet passage 32a and an upper outlet passage (vent outlet passage) 32b provided above the foot outlet passage 32a. Further, at least one outlet passage door 38a, 38b, 38c has a foot outlet passage door 38a that can move between a position where the foot outlet passage 32a is opened and a position where the foot outlet passage 32a is closed, and an upper outlet passage (vent outlet passage) 32b. Includes an upper outlet passage door (vent outlet passage door) 38b, which is movable between a position of opening and a position of closing. Then, the control device 60 is in a position where the foot outlet passage door 38a closes the foot outlet passage 32a, and the upper outlet passage door (vent outlet passage door) 38b opens the upper outlet passage (vent outlet passage) 32b. The foot outlet passage door 38a is in a position to open the foot outlet passage 32a, and the upper outlet passage door (vent outlet passage door) 38b closes the upper outlet passage (vent outlet passage) 32b, as compared with the case where it is in the position. When the switching door 50 is in the position, the first position is determined so that the opening area of the communication port 81 when the switching door 50 is arranged in the first position becomes small.

Generally, the noise generated by the blower 2 is higher than when the air conditioner 1 is operated in an operation mode (for example, a vent mode) in which the foot blowout passage 32a is closed and the upper blowout passage (vent blowout passage) 32b is open. When operating in an operation mode (for example, foot mode) in which the passage 32a is opened and the upper outlet passage (vent outlet passage) 32b is closed, the frequency of the sound to be muted is lower. According to the above-mentioned air-conditioning device 1, the foot-blowing device 1 is operated in an operation mode (for example, a venting mode) in which the foot blowing-out passage 32a is closed and the upper blowing-out passage (vent blowing-out passage) 32b is opened. When operating in an operation mode (for example, foot mode) in which the passage 32a is opened and the upper outlet passage (vent outlet passage) 32b is closed, the frequency of the sound muted in the resonance chamber 80 can be lowered.

Alternatively, in the above-described embodiment, the air conditioner 1 includes a blower 2 having the control device 60, and an air conditioning unit 3 for blowing air sent from the blower 2 into the interior of the vehicle. The air conditioning unit 3 is arranged so as to form a detour 3b between the air conditioning case 30 forming the air passage 3a through which air flows inside and the inner side surface 33a of the air conditioning case 30 in the air passage 3a. The air and the detour 3b, which are arranged in the air passage 3a and move between the position where the detour 3b is opened and the position where the detour 3b is closed, toward the heating heat exchanger 36 and the heat exchanger 36 for heating. It includes an air mix door 7 that adjusts the ratio of air to the air. Then, in the control device 60, the switching door 50 is in the first position when the air mix door 7 is in the position where the detour 3b is closed, rather than when the air mix door 7 is in the position where the detour 3b is opened. The first position is determined so that the opening area of the communication port 81 when arranged is small.

Generally, the noise generated by the blower 2 is generated by arranging the air mix door 7 at a position where the detour 3b is closed, rather than arranging the air mix door 7 at a position where the detour 3b is opened and operating the air conditioner 1. When the air conditioner 1 is operated, the frequency of the sound to be muted is lower. According to the air conditioner 1 described above, the sound is muted in the resonance chamber 80 when the air mix door 7 is in the position where the detour 3b is closed, rather than when the air mix door 7 is in the position where the detour 3b is opened. The frequency of the sound can be lowered.

Alternatively, in the above-described embodiment, in the control device 60, the higher the ventilation resistance received by the air flowing out of the discharge port 6b, the smaller the opening area of the communication port 81 when the switching door 50 is arranged at the first position. In addition, the first position is determined. In general, the noise generated by the blower 2 has a lower frequency of sound to be muted in order to effectively reduce the noise in the case where the ventilation resistance is high and in the case where the ventilation resistance is high. Therefore, the sound to be muted by determining the first position so that the higher the ventilation resistance, the smaller the opening area of the outside air intake 11 when the switching door 50 is arranged at the first position. Can be appropriately muted in the resonance chamber 80.

<Modification 1>
Next, a modification 1 of the air conditioner of the above-described embodiment will be described with reference to FIGS. 7 and 8. FIG. 7 is a diagram schematically showing the configuration of the air conditioner 1a according to the modified example 1. Further, FIG. 8 is a diagram showing the difference in frequency characteristics of the noise generated by the blower without the resonance chamber due to the difference in the rotation speed of the impeller. The blowout mode is the foot mode.

In the modification 1 shown in FIGS. 7 and 8, the control device 60a controls the switching door 50 based on the rotation speed of the motor 5 as compared with the air conditioner 1 of the embodiment shown in FIGS. 1 to 6. It is different in that it does. Other configurations of the blower 2a and the air conditioner 1a are substantially the same as those of the blower 2 and the air conditioner 1 of the embodiment shown in FIGS. 1 to 6. In the modified example 1 shown in FIGS. 7 and 8, the same parts as those of the embodiment shown in FIGS. 1 to 6 are designated by the same reference numerals, and detailed description thereof will be omitted.

First, with reference to FIG. 8, the difference in frequency characteristics of the noise generated by the blower without the resonance chamber due to the difference in the rotation speed of the impeller will be described. FIG. 8 is obtained in the vicinity of the inside air intake of the blower when the impeller of the blower without the resonance chamber described above is rotated at a rotation speed of 2900 rpm and a rotation speed of 2000 rpm. It is a figure which shows the frequency characteristic of the noise. The horizontal axis shows the frequency, and the vertical axis shows the A characteristic sound pressure level of the 1/3 octave bandwidth filter.

As shown in FIG. 8, the frequency characteristic curve of noise obtained when the impeller is rotated at a rotation speed of 2000 rpm forms a gentle mountain as a whole over 80 to 6300 Hz. In the case of noise having such frequency characteristics, the noise can be effectively reduced by muting the sound having the highest sound pressure level (sound near 800 Hz in the example shown in FIG. 8). On the other hand, the frequency characteristic curve of noise obtained when the impeller is rotated at a rotation speed of 2900 rpm forms a sharp peak near 130 Hz, and forms a gentle mountain as a whole in other frequency bands. There is. In the case of noise having such a frequency characteristic, a sound near 130 Hz in which a sound pressure level forms a sharp peak is perceived as a jarring sound. Therefore, if the sound near 130 Hz is muted, the noise can be effectively reduced.

As described above, the characteristics of the noise generated by the blower differ depending on the rotation speed of the impeller, and therefore the frequency of the sound to be muted also differs depending on the rotation speed of the impeller. Then, as shown in FIG. 8, the frequency of the sound to be muted is lower in the case where the rotation speed of the impeller is high and in the case where the rotation speed is slow.

In consideration of this point, the control device 60a of the first modification determines the first position according to the rotation speed of the motor 5 that rotates the impeller 4.

Specifically, the control device 60a determines the first position so that the faster the rotation speed of the motor 5, the smaller the opening area of the communication port 81 when the switching door 50 is arranged at the first position. As a result, as can be understood from the above equation, when the blower 2a is operated in the inside air mode, the faster the rotation speed of the motor 5, the lower the frequency of the sound muted in the resonance chamber 80 can be.

In the example shown in FIG. 7, the control device 60a determines the rotation speed of the motor 5 based on the information obtained from the motor control unit 8a.

As described above, in the blower 2a according to the first modification, in the control device 60a, the faster the rotation speed of the motor 5, the smaller the opening area of the communication port 81 when the switching door 50 is arranged at the first position. Determine the first position. Generally, as for the noise generated by the blower 2, the faster the rotation speed of the motor 5, the lower the frequency of the sound to be muted. According to the blower 2a described above, when the blower 2a is operated in the inside air mode, the faster the rotation speed of the motor 5, the lower the frequency of the sound muted in the resonance chamber 80 can be.

<Modification 2>
Next, a modification 2 of the air conditioner of the above-described embodiment will be described with reference to FIG. 9. FIG. 9 is a diagram schematically showing the configuration of the air conditioner 1b according to the modified example 2.

In the modification 2 shown in FIG. 9, as compared with the blower 2 of one embodiment shown in FIGS. 1 to 6, the blower 2b has the noise detecting means 65, and the control device 60b has the noise detecting means 65. The difference is that the first position can be determined based on the detection result of. Other configurations of the blower 2b and the air conditioner 1b are substantially the same as those of the blower 2 and the air conditioner 1 of the embodiment shown in FIGS. 1 to 6. In the modified example 2 shown in FIG. 9, the same parts as those of the embodiment shown in FIGS. 1 to 6 are designated by the same reference numerals, and detailed description thereof will be omitted.

As described above, the blower 2b further includes a noise detecting means 65 for detecting the noise level. In the example shown in FIG. 9, the noise detecting means 65 is arranged in the vicinity of the inside air intake port 12 and detects the noise level at the inside air intake port 12 for each frequency. Then, the control device 60b determines the first position according to the noise level for each frequency detected by the noise detecting means 65. Specifically, the lower the frequency of the sound to be muted in order to effectively reduce the noise, the smaller the opening area of the communication port 81 when the switching door 50 is arranged at the first position. Determine the first position.

As described above, the blower 2b according to the modified example 2 further includes a noise detecting means 65 for detecting the noise level at the inside air intake port 12 for each frequency. Then, the control device 60b determines the first position according to the noise level for each frequency detected by the noise detecting means 65. According to such a blower 2b, when the blower 2b is operated in the inside air mode, the sound to be muted in the noise generated by the blower 2b can be appropriately muted in the resonance chamber 80.

<Modification 3>
Next, a modification 3 of the air conditioner of the above-described embodiment will be described with reference to FIGS. 10 and 11. FIG. 10 is a cross-sectional view schematically showing the air intake housing 10c of the blower 2c according to the modified example 3. Further, FIG. 11 is an exploded perspective view of the switching door 55 of the air intake housing 10.

The modification 3 shown in FIGS. 10 and 11 differs from the blower 2 of the embodiment shown in FIGS. 1 to 6 in that the switching door 55 is a sliding switching door. Further, it is different in that the rib 70 is arranged inside the resonance chamber 80. Other configurations of the blower 2b and the air conditioner 1b are substantially the same as those of the blower 2 and the air conditioner 1 of the embodiment shown in FIGS. 1 to 6. In the modified example 3 shown in FIGS. 10 and 11, the same parts as those of the embodiment shown in FIGS. 1 to 6 are designated by the same reference numerals, and detailed description thereof will be omitted.

First, the switching door 55 will be described. As described above, the switching door 55 is of a type called a sliding switching door. As can be understood from FIGS. 10 and 11, the switching door 55 is a plate-shaped member, and the air intake housing is placed on the raceway surface Sc close to the inside air inlet 12 and the outside air intake 11 of the air intake housing 10c. It moves along the inner surface of 10c. The switching door 55 has a first position (position shown by a solid line in FIG. 9) that opens the inside air intake 12 and closes the outside air intake 11, and a second position that closes the inside air intake 12 and opens the outside air intake 11. It is possible to move between the position (the position shown by the broken line in FIG. 9).

More specifically, the switching door 55 is inserted into a door support portion (not shown) composed of a slot or a rail provided at a position close to the inside air intake port 12 and the outside air intake port 11 in the air intake housing 10c. It is held movably between the first position and the second position. A rack 55a is provided on one surface of the switching door 55 (the surface opposite to the side facing the inside air inlet 12 or the outside air intake 11) 55 m. The rack 55a extends from one end edge 55f located on one side of the switching door 55 in the moving direction to the other end edge 55r located on the other side. Further, in the air intake housing 10c, a shaft 56 extending in the left-right direction is provided facing the one surface 55m of the switching door 55. A pinion 56a that meshes with the rack 55a is provided on the outer peripheral surface of the shaft 56. Then, when the shaft 57 is rotated in the circumferential direction, the switching door 55 is driven via the pinion 56a and the rack 55a, and slides between the first position and the second position. The shaft 56 is rotationally driven by an actuator (not shown).

Next, the rib 70 arranged inside the resonance chamber 80 will be described. In the illustrated example, the rib 70 is a plate-shaped member, and the direction intersecting the raceway surface Sc of the switching door 55 from the wall portion 82 provided with the communication port 81 toward the internal space of the resonance chamber 80. It extends to. The rib 70 extends along the inner surface 80a of the resonance chamber 80 (more specifically, the upper surface 80au located above the inner surface 80a). The rib 70 is arranged so that the end portion of the air intake housing 10c on the internal space side is along the lower end edge of the switching door 55 arranged at the first position (in the illustrated example, the one end edge 55f). The door. Further, the rib 70 forms a passage 71 between the rib 70 and the upper surface 80au of the inner side surface 80a. One end of the passage 71 is open toward the internal space of the air intake housing 10c, and the other end is open toward the internal space of the resonance chamber 80.

The length L70 of the rib 70 corresponds to the length L of the opening in the above equation. Therefore, according to such an air intake housing 10c, as can be understood from the above equation, the frequency of the sound muted in the resonance chamber 80 is adjusted by adjusting the length L70 of the rib 70. Can be done. That is, the noise can be reduced without depending on the thickness of the wall portion 82 provided with the communication port 81 for the frequency of the sound muted in the resonance chamber 80. The longer the length L70, the smaller the frequency of the sound muted in the resonance chamber 80.

As described above, in the blower 2c according to the modification 3, the switching door 55 has a first position for opening the inside air intake 12 and a second position for closing the inside air intake 12 along the inner surface of the air intake housing 10c. It is a sliding switching door that can be moved between. With such a switching door 55, the opening degree of the communication port 81 can be changed while closing the outside air intake port 11.

Further, in the blower 2c according to the modified example 3, the blower 2c extends inside the resonance chamber 80 so as to intersect the raceway surface Sc of the switching door 55, and one end thereof takes in air from the inner surface 80a of the resonance chamber 80. A rib 70 is arranged that forms a passage that is open towards the interior space of the housing 10c and the other end is open towards the interior space of the resonance chamber 80. According to such a blower 2c, the frequency of the sound muted in the resonance chamber 80 can be adjusted by adjusting the length L70 of the rib 70.

<Modification example 4>
Next, a modification 4 of the air conditioner of the above-described embodiment will be described with reference to FIGS. 12 and 13. FIG. 12 is a cross-sectional view schematically showing the air intake housing 10d of the blower 2d according to the modified example 4. Further, FIG. 13 is a diagram showing a cross section of the air intake housing 10d along the line I-I of FIG.

In the modified example 4 shown in FIGS. 12 and 13, a plurality of resonance chambers 85 and 86 are provided in the air intake housing 10d as compared with the air intake housing 10 of the embodiment shown in FIGS. 1 to 6. It is different in that it is. Other configurations of the air intake housing 10d and the blower 2d are substantially the same as those of the air intake housing 10 and the blower 2 of the embodiment shown in FIGS. 1 to 6. In the modified example 4 shown in FIGS. 12 and 13, the same parts as those of the embodiment shown in FIGS. 1 to 6 are designated by the same reference numerals, and detailed description thereof will be omitted.

As described above, in the examples shown in FIGS. 12 and 13, the blower 2d has a plurality of resonance chambers 85 and 86. Each resonance chamber 85, 86 has an internal space communicating with the internal space of the air intake housing 10d through the communication ports 87, 88. The communication ports 87 and 88 are provided on the suction port 6a side of the scroll housing 6 with respect to the outside air intake port 11 along the raceway surface S of the switching door 50. In the illustrated example, the blower 2d has a first resonance chamber 85 and a second resonance chamber 86. The first resonance chamber 85 and the second resonance chamber 86 are provided side by side in the left-right direction (direction intersecting the moving direction of the switching door 50) below the outside air intake duct 20, and the internal space thereof is separated by a partition wall 90. ing. Further, the internal space of the first resonance chamber 85 and the second resonance chamber 86 and the internal space of the air intake housing 10c are separated by wall portions 82a and 82b, respectively. The volumes of the first resonance chamber 85 and the second resonance chamber 86 are different from each other. The first resonance chamber 85 and the second resonance chamber 86 have a first communication port 87 and a second communication port 88 that open into the internal space of the air intake housing 10d, respectively. The first communication port 87 and the second communication port 88 are provided in regions of the wall portions 82a and 82b below the outside air intake 11 and above the filter 13, respectively. The first communication port 87 and the second communication port 88 are arranged in the left-right direction (the direction intersecting the moving direction of the switching door 50).

The volumes of the first resonance chamber 85 and the second resonance chamber 86 correspond to the volume V of the resonance chamber in the above equation, respectively. Therefore, according to such a blower 2d, as can be understood from the above equation, the first resonance chamber 85 and the second resonance chamber 86 can mute sounds having different frequencies from each other. That is, the noise generated by the blower 2d can be reduced over a wider frequency band by the first resonance chamber 85 and the second resonance chamber 86.

In the illustrated example, the volumes of the first resonance chamber 85 and the second resonance chamber 86 are different, and the sizes (maximum opening area) of the first communication port 87 and the second communication port 88 are different. However, the sizes of the first communication port 87 and the second communication port 88 may be the same. Further, the volumes of the first resonance chamber 85 and the second resonance chamber 86 may be equal to each other, and the sizes (maximum opening area) of the first communication port 87 and the second communication port 88 may be different from each other. Since the sizes of the first communication port 87 and the second communication port 88 are different from each other, the opening area of the first communication port 87 and the second communication port 88 when the switching door 50 is arranged at the first position is increased. Can be different from each other. Here, the opening areas of the first communication port 87 and the second communication port 88 correspond to the opening area A of the opening of the resonance chamber in the above formula, respectively. Therefore, even if the volumes of the first resonance chamber 85 and the second resonance chamber 86 are equal, the opening areas of the first communication port 87 and the second communication port 88 are made different from each other, so that the first resonance chamber 85 and the second resonance chamber 85 and the second resonance chamber are resonated. The frequencies of the sounds muted in the chamber 86 can be different from each other.

Further, in the illustrated example, the first communication port 87 and the second communication port 88 are arranged in the left-right direction (the direction intersecting the moving direction of the switching door 50), and when the first position of the switching door 50 is changed, the first communication port is first. The opening areas of the communication port 87 and the second communication port 88 are both changed. However, it is not limited to this. The first communication port 87 and the second communication port 88 are arranged in the moving direction of the switching door 50 (upper and lower direction in the illustrated example), and when the first position of the switching door 50 is changed, the first communication port 87 and the second communication port 87 are arranged. Only one opening area of 88 may be modified.

As described above, the blower 2d according to the modified example 4 has a plurality of resonance chambers 85 and 86, and the volumes of the plurality of resonance chambers 85 and 86 are different from each other. According to such a blower 2d, in the first resonance chamber 85 and the second resonance chamber 86, sounds having different frequencies can be muted. Therefore, the noise generated by the blower 2d can be reduced over a wider frequency band.

The vehicle air conditioner and the blower used in the vehicle air conditioner according to the present invention can be industrially manufactured and can be the subject of commercial transactions, and therefore have economic value and are industrially available. It can be used.

1, 1a, 1b Air conditioner for vehicles 2, 2a, 2b, 2c, 2d Blower 3 Air harmonizer 4 Impeller 6 Scroll housing 7 Air mix door 10, 10c, 10d Air intake housing 11 Outside air intake 12 Inside air intake Inlet 20 Outside air intake duct 30 Air conditioning case 32a, 32b, 32c Blowout passage 36 Heat exchanger for heating 38a, 38b, 38c Blowout passage door 50, 55 Switching door 60, 60a, 60b Control device 65 Noise detection means 70 Rib 80, 85,86 Resonance chamber

Claims (12)

Blowers (2,2a, 2b, 2c, 2d) used in vehicle air conditioners.
An impeller (4) having a plurality of blades (4a) forming a circumferential blade row and being rotationally driven by the rotation shaft (5a) of the motor (5).
It has an internal space for accommodating the impeller (4), a suction port (6a) that opens in the axial direction of the rotation shaft (5a), and a discharge port (6b) that opens in the circumferential direction of the impeller. Scroll housing (6) and
An air intake housing (10) having an internal space communicating with the suction port (6a) of the scroll housing (6), and at least one outside air intake for taking in outside air into the internal space of the air intake housing. The air intake housing (10, 10c, 10d) provided with an inlet (11) and at least one inside air intake port (12) for taking in the inside air into the internal space of the air intake housing.
At least one switching door (50, 55) for opening and closing the outside air intake (11) and the inside air intake (12), and
In those equipped with
The air intake housing (10, 10c, 10d) is further on the suction port (6a) side of the outside air intake (11) and on the raceway surface (S,) of the switching door (50, 55). A resonance chamber (80; 85, 86) having an internal space communicating with the internal space of the air intake housing (10, 10c, 10d) through a communication port (81; 87, 88) provided along the Sc). It is provided,
The switching door can at least partially close the communication port (81; 87,88) while closing the outside air intake, and the opening area of the communication port (81; 87,88) can be changed. There is a blower (2,2a, 2b, 2c, 2d). The switching door (50, 55) has a first position for opening the inside air intake (12) and the inside air intake (12) along the inner surface of the air intake housing (10, 10c, 10d). The blower (2,2a, 2b, 2c, 2d) according to claim 1, which is a rotary switching door or a sliding switching door that can move between the second position to be closed. The blower (2,2a, 2b, 2c, 2d). In the control device (60), the higher the ventilation resistance received by the air flowing out of the discharge port (6b), the more the communication port (81; The blower (2) according to claim 3, wherein the first position is determined so that the opening area of 87,88) is reduced. The control device (60a) opens the communication port (81; 87, 88) when the switching door (50, 55) is arranged at the first position as the rotation speed of the motor (5) increases. The blower (2a) according to claim 3, wherein the first position is determined so that the area is small. Further, a noise detecting means (65) for detecting the noise level at the inside air intake (12) for each frequency is further provided.
The blower (2b) according to claim 3, wherein the control device (60b) determines the first position according to the noise level for each frequency detected by the noise detecting means (65). One end thereof extends into the resonance chamber (80) so as to intersect the raceway surface (Sc) of the switching door (50, 55) and is connected to the inner surface of the resonance chamber (80). Ribs (70) are arranged that form a passage that is open towards the interior space of the air intake housing (10c) and the other end is open towards the interior space of the resonance chamber (80). The blower (2c) according to any one of claims 1 to 6. It has a plurality of resonance chambers (85,86) and has a plurality of resonance chambers (85,86).
The blower (2d) according to any one of claims 1 to 7, wherein the volumes of the plurality of resonance chambers (85, 86) are different from each other. The blower (2,2a, 2b, 2c, 2d) according to any one of claims 1 to 8 is provided, and an air conditioning unit (3) for blowing out air sent from the blower into the vehicle interior is provided. Air conditioner for vehicles (1,1a, 1b). An air conditioner (1) for a vehicle, comprising the blower (2) according to claim 3 and an air conditioning unit (3) for blowing out air sent from the blower into the interior of the vehicle.
The air conditioning unit (3) is
An air conditioning case (30) that forms an air passage (3a) through which air flows, and is connected to a discharge port (6b) of the scroll housing (6) to allow air from the blower (2) to flow in. The air conditioning case (30) having an inlet (31) and at least one blowing passage (32a, 32b, 32c) from which air that has passed through the air passage (3a) is blown out.
At least one outlet door (38a, 38b) provided for each of the at least one outlet passage (32a, 32b, 32c) and movable between a position where the corresponding outlet passage is opened and a position where the corresponding outlet passage is closed. , 38c),
Have,
The control device (60) is an air conditioner (1) that determines the first position according to the position of the at least one outlet passage door. The at least one outlet passage (32a, 32b, 32c) includes a foot outlet passage (32a) and an upper outlet passage (32b) provided above the foot outlet passage.
The at least one outlet door opens a foot outlet door (38a) that is movable between a position where the foot outlet passage (32a) is opened and a position where the foot outlet passage (32a) is closed, and an upper outlet passage (32b). Includes an upper aisle door (38b) that can be moved between positions and closed positions.
The control device (60) is in a position where the foot outlet passage door (38a) closes the foot outlet passage (32a), and the upper outlet passage door (38b) has the upper outlet passage (32b). The foot outlet passage door (38a) is in a position to open the foot outlet passage (32a), and the upper outlet passage door (38b) is in the upper outlet passage (32b), as compared with the case where the foot outlet passage door (38a) is in the opening position. The first position is determined so that the opening area of the communication port (81) becomes smaller when the switching door (50, 55) is arranged at the first position when the door (50, 55) is closed. The air conditioner (1) according to claim 10. An air conditioner (1) for a vehicle, comprising the blower (2) according to claim 3 and an air conditioning unit (3) for blowing out air sent from the blower into the interior of the vehicle.
The air conditioning unit (3) is
An air conditioning case (30) that forms an air passage (3a) through which air flows,
A heat exchanger (36) for heating, which is arranged in the air passage (3a) so as to form a detour (3b) with the inner surface of the air conditioning case (30).
The air and the detour (36) arranged in the air passage (3a) and moving between the opening position and the closing position of the detour (3b) toward the heating heat exchanger (36). The air mix door (7) that adjusts the ratio of the air toward 3b) and
Including
The control device (60) is in a position where the air mix door (7) closes the detour (3b) than when the air mix door (7) is in a position where the detour (3b) is opened. The air conditioner (50, 55) determines the first position so that the opening area of the communication port (81) becomes smaller when the switching door (50, 55) is arranged at the first position. 1).

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