JP4940924B2 - Indoor unit - Google Patents

Description

  The present invention relates to an indoor unit for an air conditioner.

  Conventionally, an indoor unit of an air conditioner has an indoor unit main body and a blower provided in the indoor unit main body. The blower is pivotally supported on the rotating shaft so as to be rotatable together with the motor fixed to the main body of the indoor unit, a rotating shaft connected to the output shaft of the motor via a coupling, and the rotating shaft. With multiple fans.

  The rotating shaft has a base end portion supported by the coupling, and a tip end portion supported by a bearing fixed to the indoor unit main body, and the fans are disposed between the coupling and the bearing. What is pivotally supported is known.

  However, when both ends of the rotating shaft are supported in this way, it is difficult to realize stable rotational driving of the rotating shaft due to the bending (vibration) of the rotating shaft accompanying the rotational driving.

Therefore, for example, as in Patent Document 1, instead of supporting the tip end portion of the rotating shaft, the middle portion of the rotating shaft (location between the fans) is also supported by a bearing. By supporting the middle part of the rotating shaft in this way, the distance between the coupling supporting the rotating shaft and the bearing can be narrowed, so that the bending (vibration) of the rotating shaft is supported more than when both ends of the rotating shaft are supported. Occurrence can be suppressed.
JP 7-293922 A

  When the middle part of the rotating shaft is supported by a bearing as in Patent Document 1, a high accuracy is required for the diameter dimension and surface treatment of the rotating shaft due to the bearing clearance between the rotating shaft and the bearing. A solid member that has been cut into a shape that satisfies the accuracy is used as the rotating shaft.

  However, if the rotating shaft is formed as a solid as a whole, the rotating shaft itself becomes heavier, so that the performance such as durability required for the bearing is increased, and the cost is increased accordingly. .

  The present invention has been made in view of the above problems, and an object of the present invention is to provide a rotating shaft capable of reducing cost while suppressing generation of vibration and an indoor unit including the rotating shaft.

In order to solve the above problems, the present invention provides a fan rotation shaft, a motor having an output shaft connected to a base end portion of the fan rotation shaft, a bearing that supports the fan rotation shaft, A plurality of fans pivotally supported on the base end side and the tip end side of the bearing with respect to the fan rotation shaft, and the fan rotation shaft is rotated in accordance with the rotational drive of the motor to blow air by each fan. The fan rotation shaft includes a hollow portion configured such that a base end portion can be connected to the output shaft of the motor, and a distal end side coaxially with the hollow portion from a distal end portion of the hollow portion. A solid portion extending to the solid portion, the solid portion being configured to be supported by the bearing and configured to be capable of supporting at least one fan, and the outer diameter of the solid portion being , Smaller than the outer diameter of the hollow portion It is, the bearing provides an indoor unit, characterized in that the support in a movable state solid portion of the fan rotary shaft in the axial direction.

  According to the present invention, the solid portion that can be supported by the bearing has a hollow portion on the base end side of the bearing, and therefore, the volume of the material in the hollow portion is reduced. It is possible to reduce the weight of the rotating shaft, which is solid as a whole, and to reduce the performance required for the bearing.

  Here, in the present invention, since the solid part is configured so as to be supported by the bearing, it is possible to cope with a bearing gap between the bearing and the bearing by performing cutting or the like on the solid part. It becomes possible to ensure the dimensional accuracy.

  Further, by disposing the bearing on the base end side relative to the position where at least one fan is pivotally supported in the solid part, the bearing is supported by the motor as compared with the case where both ends of the rotating shaft are supported. Since the distance between the position to be supported by the bearing and the position supported by the bearing can be shortened, vibration during driving can be suppressed.

  Therefore, according to the present invention, it is possible to suppress the generation of vibration during driving, and to reduce the cost.

Further, in the present invention, the outer diameter of the solid part is set smaller than the outer diameter of the hollow part .

Thus, since the outer diameter of the solid portion is set smaller than the outer diameter of the hollow portion, the proximal end portion of the hollow portion is connected to the output shaft of the motor, and then the distal end side with respect to the solid portion. Each fan can be installed.

Further, the bearing is configured to support a solid part of the fan rotation shaft in a state movable in the axial direction.

As described above, since the solid portion is supported in a state of being movable in the axial direction, the position of the fan rotation shaft relative to the bearing is determined according to the deflection of the fan rotation shaft during rotation driving. When moving in the axial direction or when the fan rotation shaft itself moves in the axial direction, it is possible to prevent the vibrations accompanying these movements from being transmitted to the entire indoor unit, thereby preventing the occurrence of noise and the like. .

In the indoor unit, the rotating shaft for the fan is configured such that a base end portion thereof can be connected to the output shaft, and is configured as a cylindrical member that forms the hollow portion, and a member separate from the cylindrical member, It is preferable that an extension member that constitutes the solid portion is provided, and the extension member is formed by being assembled to the distal end portion of the cylindrical member.

  In this way, the fan rotation shaft is composed of two parts, the cylindrical member and the extension member, so that the extension member that requires high accuracy and the cylindrical member that does not require much dimensional accuracy can be separately provided. Once formed, the cylindrical member and the extension member can be assembled to form the fan rotation shaft.

  Therefore, according to the above configuration, unlike the case of handling the entire rotating shaft for a fan in which the hollow portion and the solid portion are integrated, only the extension member constituting the solid portion is subjected to precise processing and the extension member However, a cylindrical member that does not require much dimensional accuracy can be manufactured by drawing or the like, that is, only the extension member needs to be managed with high accuracy, so that process control is possible. An increase in the complexity of the above can be suppressed.

In the indoor unit , it is preferable that the extension member is press-fitted and assembled from the distal end side of the cylindrical member to the inside of the cylindrical member.

  If it does in this way, the said extension member and a cylindrical member can be assembled | attached by press-fitting operation of an extension member, without using special members, such as a volt | bolt.

In the indoor unit , an outer diameter of the extension member is set to be substantially the same as an inner diameter of the cylindrical member, and the cylindrical member is configured to be capable of pivotally supporting at least one fan. It is preferable that an outer diameter size of the cylindrical member in a portion to be pivotally supported is larger than a size 1.189 times larger than an outer diameter size of the extension member.

  If it does in this way, the section secondary moment of the portion which supports the fan of a cylindrical member can be made larger than the section secondary moment of an extension member.

  That is, assuming that the outer diameter of the cylindrical member is D2, the inner diameter of the cylindrical member is D1, and the outer diameter of the extension member press-fitted into the inner diameter of the cylindrical member is also assumed to be D1 (see FIG. 3), the cylindrical shape The cross-sectional secondary moment of the member is expressed by π (D2 ^ 4-D1 ^ 4) ÷ 16, whereas the cross-sectional secondary moment of the extending member is expressed by π (D1 ^ 4) ÷ 16. become. Note that “^” indicates a power, and “^ 4” indicates the fourth power.

  Here, when the cross-sectional secondary moment of the cylindrical member is larger than the cross-sectional secondary moment of the extending member, the relational expression of π (D2 ^ 4-D1 ^ 4) ÷ 16 ≧ π (D1 ^ 4) ÷ 16 From this equation, D2 ≧ 2 ^ (1/4) D1 = 1.189D1 is obtained. In other words, if the outer diameter D2 of the cylindrical member is set to a dimension of 1.189 times or more of the inner diameter of the cylindrical member (outer diameter of the extension member) D1, the sectional moment of inertia of the cylindrical member is theoretically increased. It will be bigger than that.

  In other words, with the above-described configuration, the fan can be pivotally supported on a stronger cylindrical member, so that the fan can be pivotally supported more reliably.

  Specifically, the bearing can be constituted by a sliding bearing.

  In the indoor unit, when the outer diameter of the solid part is set smaller than the outer diameter of the hollow part, the outer diameter of the solid part supported by the slide bearing can be reduced. Therefore, the performance required for the slide bearing can be suppressed. That is, the performance of the plain bearing is defined by the PV value obtained by multiplying the surface pressure [P] received by the plain bearing and the peripheral speed [V] of the shaft, and the peripheral speed [V] is the rotation of the shaft. Since it is defined by a value obtained by multiplying the number and the outer diameter of the shaft, the peripheral speed [V] can be reduced as the outer diameter of the shaft is reduced, thereby reducing the performance required for the slide bearing. Can do. Therefore, according to this configuration, it is possible to achieve a significant cost reduction.

  According to the present invention, the solid portion that can be supported by the bearing has a hollow portion on the base end side of the bearing, and therefore, the volume of the material in the hollow portion is reduced. It is possible to reduce the weight of the rotating shaft, which is solid as a whole, and to reduce the performance required for the bearing.

  Here, in the present invention, since the solid part is configured so as to be supported by the bearing, it is possible to cope with a bearing gap between the bearing and the bearing by performing cutting or the like on the solid part. It becomes possible to ensure the dimensional accuracy.

  Further, by disposing the bearing on the base end side relative to the position where at least one fan is pivotally supported in the solid part, the bearing is supported by the motor as compared with the case where both ends of the rotating shaft are supported. Since the distance between the position to be supported by the bearing and the position supported by the bearing can be shortened, vibration during driving can be suppressed.

  Therefore, according to the present invention, it is possible to suppress the generation of vibration during driving, and to reduce the cost.

  Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings.

  FIG. 1 is a side sectional view showing an overall configuration of an indoor unit according to an embodiment of the present invention. 2 is a cross-sectional view taken along line II-II in FIG.

  Referring to the drawings, an indoor unit 1 includes an indoor unit main body 2 and a blower 3 built in the indoor unit main body 2, and the indoor unit main body 2 is attached to a ceiling R.

  The indoor unit main body 2 includes a main body case 4 and a heat exchanger 5 and a wind direction plate 6 built in the main body case 4. The main body case 4 has an upper plate 4c attached to the ceiling, an inlet 4a through which air can be introduced from below, and an outlet through which air introduced from the inlet 4a can be blown out horizontally. 4b. In addition, the side in which the said blower outlet 4b is formed is made into the front, and the direction orthogonal to this front-back direction in a horizontal direction is demonstrated below as the left-right direction.

  The wind direction plate 6 is disposed at an inner position of the air outlet 4b, and is rotatable with respect to the main body case 4 about a horizontal axis so that the air direction flowing through the air outlet 4b can be adjusted up and down. ing.

  The air blower 3 is disposed behind the air outlet 4b in the main body case 4, and the air introduced from the inlet 4a passes through the heat exchanger 5 and then passes through the air outlet 4b. It leads to the outside.

  Specifically, the blower 3 includes a motor 7, a rotary shaft 8 connected to the right end of the output shaft 7 a of the motor 7, three fans 9, a fan 10, and a fan 11 supported on the rotary shaft 8. And a fan 12 pivotally supported at the left end of the output shaft 7a, and a slide bearing 14 for supporting the rotary shaft 8.

  The left and right ends of the motor 7 are fixed to a pair of left and right brackets 15 suspended from the upper plate 4c of the main body case 4. The output shaft 7a of the motor 7 extends through the brackets 15 in the left and right directions.

  FIG. 3 is a partial schematic cross-sectional view showing the rotation axis of FIG. 2 in an enlarged manner.

  With reference to FIGS. 1 to 3, the rotating shaft 8 includes a cylindrical member 16 formed in a hollow shape and a solid extending member 17 attached to the cylindrical member 16. The cylindrical member 16 has a left end portion (base end portion) coaxially connected to the output shaft 7 a of the motor 7 via a coupling 18. The extension member 17 is press-fitted into the right end portion of the cylindrical member 16 from the right side.

  Specifically, the extension member 17 has a flange portion 17a in which a part in the axial direction bulges in the radial direction, and a portion on the left side of the flange portion 17a is press-fitted into the tubular member 16. . In other words, the extension member 17 can be press-fitted into the tubular member 16 to a depth position where the left end surface of the flange portion 17a contacts the right end surface of the tubular member. The right side portion is a shaft portion 17 b extending rightward from the tubular member 16. The outer diameter D1 of the shaft portion 17b is set smaller than the outer diameter D2 of the cylindrical member 16.

  More specifically, the outer diameter D1 of the shaft portion 17b is set to φ10 mm, while the outer diameter D2 of the cylindrical member 16 is set to φ15 mm, and D2 is set to a dimension 1.5 times as large as D1. . Therefore, the cross-sectional secondary moment of the cylindrical member 16 is larger than the cross-sectional secondary moment of the shaft portion 17b. That is, the cross-sectional secondary moment of the cylindrical member 16 is expressed by π (D2 ^ 4-D1 ^ 4) ÷ 16, whereas the cross-sectional secondary moment of the shaft portion 17b is π (D1 ^ 4) ÷ 16. 16 is represented.

  Here, when the cross-sectional secondary moment of the cylindrical member 16 becomes larger than the cross-sectional secondary moment of the shaft portion 17b, the relational expression of π (D2 ^ 4-D1 ^ 4) ÷ 16 ≧ π (D1 ^ 4). From this equation, D2 ≧ 2 ^ (1/4) D1 = 1.189D1 is obtained. That is, if the outer diameter D2 of the cylindrical member 16 is set to a dimension that is 1.189 times or more larger than the inner diameter (outer diameter of the shaft portion 17b) D1 of the cylindrical member 16, the sectional secondary moment of the cylindrical member 16 is theoretically. Becomes larger than that of the shaft portion 17b. In the present embodiment, as described above, since D2 is set to a size 1.5 times larger than 1.189 times as large as D1, the sectional moment of inertia of the cylindrical member 16 is the shaft portion 17b. The moment of inertia of the cross section becomes larger.

  The shaft portion 17b is supported by a slide bearing 14 fixed to a mounting plate 19 suspended from the upper plate 4c of the main body case 4. Specifically, the shaft portion 17b is supported by the plain bearing 14 at a position slightly to the right of the flange portion 17a. The sliding bearing 14 supports the shaft portion 17b so that the shaft portion 17b can move in the left-right direction (axial direction).

  Each of the fans 9 to 12 includes a drum 20 having a plurality of wing portions 20a formed on the outer surface, and a casing 21 that accommodates the drum 20. Inside each drum 20, a sleeve 22 for attaching the rotating shaft 8 is provided. These sleeves 22 are fixed to the rotating shaft 8 received coaxially with the drum 20. Accordingly, the fans 9 to 12 rotate integrally according to the rotational drive of the rotary shaft 8. The casing 21 includes an accommodating portion 21a that accommodates the fans 9 to 12 in a state where the rotating shaft 8 is inserted, and an accommodating portion 21a that directs the airflow generated by the rotation of the fans 9 to 12 toward the air outlet 4b. And a duct portion 21b extending forward.

  In the present embodiment, the fan 9 is pivotally supported by the cylindrical member 16 at a position slightly on the right side of the coupling 18, and the fan 10 is pivoted on the cylindrical member 16 between the fan 9 and the slide bearing 14. The fan 11 is pivotally supported at the distal end portion of the shaft portion 17b of the extension member 17 at a position on the right side of the slide bearing 14. That is, the rotating shaft 8 is supported by the plain bearing 14 in the middle part between the fan 10 and the fan 11. Therefore, compared with the case where both ends of the rotating shaft 8 are supported by the motor 7 (coupling 18) and the slide bearing 14, the distance D3 between the support position by the motor 7 and the support position by the slide bearing 14 is shortened. Therefore, the bending (vibration) of the rotating shaft 8 at the time of rotational driving can be suppressed.

  As described above, according to the above-described embodiment, the solid shaft portion 17 b that can be supported by the slide bearing 14 is provided, and the hollow cylindrical member 16 is provided on the left side of the slide bearing 14. Therefore, the weight required for the sliding bearing 14 can be reduced by reducing the weight of the cylindrical member 16 as much as the solid rotating shaft as much as the volume of the material is reduced.

  Here, in the above-described embodiment, the solid shaft portion 17b is formed so as to be supported by the bearing 14, and therefore, the sliding portion 14 It is possible to ensure a dimensional system corresponding to the bearing gap between the two.

  Further, the sliding bearing 14 is arranged on the left side of the shaft portion 17b from the position where the fan 11 is pivotally supported, so that the motor 7 can be compared with the case where both ends of the rotating shaft 8 are supported. Since the distance D3 between the supported position (the position of the coupling 18) and the position supported by the slide bearing 14 can be reduced, vibration during driving can be suppressed.

  Therefore, according to the embodiment, the cost can be reduced while suppressing the occurrence of vibration during driving.

  If the outer diameter D1 of the shaft portion 17b is set smaller than the outer diameter D2 of the cylindrical member 16 as in the above embodiment, the right end portion (base end portion) of the cylindrical member 16 is used as the output shaft 7a of the motor 7. After the connection, the sleeves 22 of the fans 9 to 11 can be inserted from the right side (tip side) with respect to the shaft portion 17b.

  As in the above-described embodiment, the rotating shaft 8 is composed of two parts, that is, the cylindrical member 16 and the extending member 17, so that the extending member 17 (shaft portion 17b) that requires high accuracy and the requirement for dimensional accuracy that much are required. It is possible to form the rotary shaft 8 by assembling the cylindrical member 16 not to be separately formed and assembling the cylindrical member 16 and the extension member 17.

  Therefore, according to the embodiment, unlike the case where the entire rotating shaft 8 is handled, only the extension member 17 having the shaft portion 17b can be precisely processed to ensure the dimensional accuracy of the extension member 17. The cylindrical member 16 that does not require so much dimensional accuracy can be manufactured by drawing or the like. That is, since only the extension member 17 needs to be managed with high accuracy, it is possible to suppress an increase in complexity in process management.

  According to the configuration in which the extension member 17 is press-fitted into the tubular member 16 and assembled as in the above-described embodiment, the extension member 17 and the tubular shape can be formed by press-fitting the extension member 17 without using a special member such as a bolt. The member 16 can be assembled.

  By setting the outer diameter D2 of the cylindrical member 16 to a dimension of 1.5 × D1, which is larger than 1.189 times the outer diameter D1 of the shaft portion 17b, as in the above embodiment, the cylinder Since the cross-sectional secondary moment of the shaped member 16 can be made larger than the cross-sectional secondary moment of the shaft portion 17b, the shafts of the fans 9 and 10 can be more reliably supported.

  According to the configuration in which the shaft portion 17b is supported by the slide bearing 14 so as to be movable in the axial direction (left-right direction) as in the above-described embodiment, the slide bearing 14 is responsive to the deflection of the rotating shaft 8 during rotational driving. When the position of the rotary shaft 8 moves in the axial direction (left-right direction) of the rotary shaft 8 or when the rotary shaft 8 moves in the axial direction, vibrations associated with these movements cause the indoor unit 1 (particularly the main body Case 4) It is possible to prevent generation of noise and the like by suppressing transmission to the whole.

  Furthermore, when the slide bearing 14 is employed and the outer diameter D1 of the shaft portion 17b is set smaller than the outer diameter D2 of the cylindrical member 16 as in the present embodiment, the shaft portion 17b supported by the slide bearing 14 is used. Therefore, the performance required for the slide bearing 14 can be suppressed accordingly. That is, the performance of the plain bearing 14 is defined by the PV value obtained by multiplying the surface pressure [P] received by the plain bearing 14 and the peripheral speed [V] of the shaft. Therefore, the peripheral speed [V] can be reduced as the outer diameter D1 of the rotating shaft 8 is reduced, and this is required for the slide bearing 14. Performance can be reduced. Therefore, according to the said embodiment, it becomes possible to aim at the significant reduction of cost.

  In the above-described embodiment, the so-called ceiling-suspended indoor unit 1 in which the indoor unit body 2 is attached to the ceiling R has been described. However, the rotary shaft 8 has the back surface of the indoor unit body 2 attached to an indoor wall surface. It can also be employed in so-called wall-mounted indoor units.

It is side surface sectional drawing which shows the whole indoor unit structure which concerns on embodiment of this invention. It is the II-II sectional view taken on the line of FIG. FIG. 3 is a partial schematic cross-sectional view showing an enlarged rotation axis of FIG. 2.

D1 Outer diameter of solid part D2 Outer diameter of hollow part 1 Indoor unit 7 Motor 7a Output shaft 8 Rotating shaft (Rotating shaft for fan)
9 to 11 Fan 14 Bearing 16 Cylindrical member 17 Extension member 17b Shaft portion 18 Coupling

Claims (5)

A fan rotation shaft, a motor having an output shaft coupled to a base end portion of the fan rotation shaft, a bearing supporting the fan rotation shaft, and a base end side of the bearing with respect to the fan rotation shaft And a plurality of fans pivotally supported on the front end side, an indoor unit that blows air by each of the fans by rotating the fan rotation shaft according to the rotational drive of the motor,
The fan rotation shaft includes a hollow portion configured to be coupled to a base end portion of the output shaft of the motor, and a solid portion extending from the distal end portion of the hollow portion to the distal end side coaxially with the hollow portion. ,
The solid part is configured to be supported by the bearing and configured to support at least one fan .
The outer diameter of the solid part is set smaller than the outer diameter of the hollow part,
The indoor unit is characterized in that the bearing supports a solid part of the fan rotation shaft in a state of being movable in the axial direction . The fan rotation shaft is configured such that a base end portion is connectable to the output shaft, and is configured as a cylindrical member that forms the hollow portion, and a member that is separate from the cylindrical member, and the solid portion is The indoor unit according to claim 1, further comprising: an extending member that is configured, and the extending member is formed by being assembled to a distal end portion of the cylindrical member. The indoor unit according to claim 2, wherein the extension member is press-fitted and assembled from the distal end side of the cylindrical member to the inside of the cylindrical member. The outer diameter of the extension member is set to be approximately the same as the inner diameter of the cylindrical member, and the cylindrical member is configured to be able to support at least one fan, and in a portion that supports the fan. The indoor unit according to claim 3, wherein an outer diameter dimension of the cylindrical member is larger than a dimension that is 1.189 times larger than an outer diameter dimension of the extension member. The indoor unit according to any one of claims 1 to 4, wherein the bearing is a slide bearing.

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