JP2007303802A - Motor actuator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a configuration, reducing the size and weight of a first driven member, in a motor actuator loaded with a second driven member to the first driven member. <P>SOLUTION: In a louver device 1 provided with the motor actuator 10, a freely rotating part 81 is provided on a large-diameter gear 65, so that when an arm 21 is driven by a first driving device 60, the freely rotating part 81 is also moved along with the large-diameter gear 65. The rotational output of a second motor 71 is transmitted to the rotary central shaft 650 of the large-diameter gear 65 through a gear 732 disposed coaxially, and transmitted to the tip of the arm 21 through a gear 731 disposed coaxially with the freely rotating part 81 of the arm 21 and the large-diameter gear 65. Accordingly, a second motor 71 can be loaded on a support 5, but needs not to be loaded on the arm 21 and the large-diameter gear 65. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a motor actuator for driving a louver or the like driven by a blowout port of an air conditioner or a hot air heater.

A louver is arranged in a state where the louver is supported by a louver support at a plurality of locations in a longitudinal direction at an outlet of an air conditioner or a warm air heater, and the louver is rotated and driven by a stepping motor and a rotating shaft. Are switched (for example, refer to Patent Document 1).
JP 7-43024 A

  In recent years, in air conditioners and the like, it has been studied to control the louver position and posture in a more complicated manner so that cold air and hot air can be evenly distributed throughout the room. In order to realize such a configuration, for example, the louver (second driven member) is rotatably supported by the tip of the arm (first driven member), and in this state, the first driving device is used. A configuration is conceivable in which the arm is moved and the louver is driven by a second driving device mounted on the arm.

  However, when the second drive device is mounted on the arm itself, the arm is enlarged, and there is a problem that the entire device cannot be reduced in size. Further, when the arm is enlarged, there is a problem that a sufficient movement range cannot be secured for the arm. Further, when the second driving device is mounted on the arm itself, the arm becomes heavy and a load applied to the first driving device increases. As a result, there is a problem that a large motor must be used for the first drive device.

  Such a problem is not limited to the louver device, but is also a problem related to all motor actuators in which the second driven member is mounted on the first driven member.

  In view of the above problems, an object of the present invention is to provide a motor actuator in which a second driven member is mounted on a first driven member without mounting a motor on the first driven member. An object of the present invention is to provide a configuration in which the first driven member can be reduced in size and weight by enabling the second driven member to be driven on the first driven member.

  In order to solve the above-described problems, in the motor actuator according to the present invention, the support, the first motor mounted on the support, and the first motor are rotated around the first rotation center axis. A first driving device including a driving rotating member, a first driven member connected to the driving rotating member via a rotatable portion spaced from the first rotation center axis, A second driven member disposed on the first driven member so as to be rotatable about a second rotation center axis separated from the rotatable portion; and the second driven member is rotated by the second rotation. A second motor for causing a rotation operation around a central axis has a second driving device mounted on the support or the driving rotary member, and in the second driving device, the second motor The rotational output of the motor of the driving rotary member Alternatively, the first driven member is transmitted to the second driven member via a first power transmission rotating member comprising a gear or a roller supported coaxially with the rotatable portion. It is characterized by that.

  In the present invention, the second driven member is a second driving device centered on the second rotation center axis on the first driven member driven by the first driving device via the rotatable portion. Although driven, the rotational output of the second motor is transmitted to the second driven member via the first power transmission rotating member comprising a gear or a roller supported coaxially with the rotatable portion. The Therefore, even if the second motor is not mounted on the first driven member, the first driven member moves to any position when mounted on the support or the driving rotary member. Even in this state, the rotation output of the second motor can be transmitted to the second driven member, and the second driven member can be driven. Therefore, the first driven member can be reduced in size and weight because the second motor need not be mounted on the first driven member.

  In the present invention, when the second motor is mounted on the support, the rotation output of the second motor is the first rotation center axis with respect to the support or the driving rotary member. After passing through a second power transmission rotating member comprising a gear or a roller supported coaxially, it is transmitted to the first power transmission rotating member. With this configuration, the rotatable portion is on the driving rotary member and moves together with the driving rotary member. However, the second motor mounted on the support has any rotational position of the driving rotary member. In this case, the second power transmission rotating member can be driven, and the first power transmission rotating member can be driven via the second power transmission rotating member. Therefore, it is not necessary to mount the second motor on the rotation drive member. Accordingly, since the driving rotary member can be reduced in weight, a small motor can be used as the first motor.

  In the present invention, the second motor may employ a configuration positioned on the opposite side of the driving rotary member from the first driven member.

  In the present invention, a link-cam mechanism that defines a movement locus of the first driven member when the driving rotary member rotates is configured for the first driven member. preferable. If comprised in this way, a 1st to-be-driven member can be made to perform complicated motion.

  In the present invention, the support body includes a cam groove that defines a movement locus of the first driven member when the driving rotary member is rotated by being engaged with a convex portion of the first driven member. It is preferable that the driving rotary member, the rotatable portion, the convex portion of the first driven member, and the cam groove constitute a link-cam mechanism.

  In the present invention, the cam groove is formed in parallel to each other with respect to the support, and the two cam grooves are formed by two protrusions protruding from different positions of the first driven member. It is preferable to engage with each other. If comprised in this way, a 1st drive member can be supported reliably.

  In the present invention, it is preferable that the second driving device includes a one-way clutch in a power transmission mechanism from the second motor to the second driven member. If comprised in this way, even when setting the origin position by driving the 2nd driven member and making it interfere with other members, the 2nd driven member to the direction which interferes with other members Can block transmission. Therefore, a large impact sound is not generated when the second driven member interferes with other members.

  In the present invention, it is preferable that the second driving device includes a torque limiter in a power transmission mechanism from the second motor to the second driven member. With this configuration, when the second driven member cannot be moved due to restraint, the power transmission mechanism from the second motor to the second driven member can be cut off. Damage to the transmission mechanism can be prevented.

  In the motor actuator according to the present invention, the second driven member is a second member around the second rotation center axis on the first driven member that is driven by the first driving device via the rotatable portion. The rotational output of the second motor is driven by the second driven member via a first power transmission rotating member comprising a gear or a roller supported coaxially with the rotatable portion. Is transmitted to the member. Therefore, even if the second motor is not mounted on the first driven member, the first driven member moves to any position when mounted on the support or the driving rotary member. Even in this state, the rotation output of the second motor can be transmitted to the second driven member, and the second driven member can be driven. Therefore, the first driven member can be reduced in size and weight because the second motor need not be mounted on the first driven member.

  In the motor actuator according to the present invention, a second motor is mounted on the support, and the rotation output of the second motor is the first rotation center with respect to the support or the driving rotary member. After being transmitted to the first power transmission rotating member after passing through the second power transmission rotating member composed of a gear or a roller supported coaxially with the axis, it is mounted on the support. The second motor can drive the second power transmission rotary member regardless of the rotational position of the drive rotary member, and the first power transmission rotary member can be driven via the second power transmission rotary member. The rotating member can be driven. Therefore, it is not necessary to mount the second motor on the rotation drive member. Accordingly, since the driving rotary member can be reduced in weight, a small motor can be used as the first motor.

  An example in which a motor actuator to which the present invention is applied is mounted on a louver device will be described below with reference to the drawings.

[Embodiment 1]
(overall structure)
1A and 1B are a perspective view and a plan view of a louver device according to Embodiment 1 of the present invention. 1A and 1B, a louver device 1 according to this embodiment includes a plate-like louver 2 extending with a predetermined width dimension, and a plurality of louvers 2 that support the louver 2 at a plurality of locations in the longitudinal direction of the louver 2. Arms 21 and 23 are provided. The plurality of arms 212 and 3 are plate-shaped orthogonal to the longitudinal direction of the louver 2 so as not to block the wind passage, and each tip supports the connecting plates 31 and 33 formed on the lower surface of the louver 2. The shafts 41 and 43 are rotatably supported.

(Configuration of motor actuator)
FIG. 2 is a plan view showing the periphery of the arm located at one end of the louver device to which the present invention is applied. 3 (a) and 3 (b) are views of a motor actuator configured with respect to an arm located at one end of a louver device to which the present invention is applied as viewed from the direction indicated by arrow A1 in FIG. 1 (b). It is explanatory drawing when seeing from the direction shown by arrow A2 of FIG.1 (b), and. FIG. 4 is an explanatory view showing the structure of the link-cam mechanism of the first drive device in the motor actuator used in the louver device to which the present invention is applied.

  In FIG. 2, the support body 5 is comprised by the case which consists of case members 51 and 52 and the ground plate 53 arrange | positioned inside a case in the one side edge part of the louver apparatus 1 of this form, The motor actuator 10 described below is mounted.

  First, on the outside of the case member 51, a first motor 61 (stepping motor) of the first driving device 60 is fixed with the output shaft directed into the case, and a position adjacent to the first motor 61. The second motor 71 (stepping motor) of the second drive device 70 is fixed with the output shaft directed into the case.

  As shown in FIGS. 3A, 3 </ b> B, and 4 </ b> A, the first driving device 60 includes a first motor 61 and a pinion connected to the output shaft of the first motor 61. And a large-diameter gear 65 (driving member for driving) that meshes with a gear located at the end of the train wheel 63. Here, among the plurality of gears constituting the train wheel 63, the gear 633 is fixed to the support shaft 3.

  In the large-diameter gear 65, a rotatable portion 81 is formed at a position away from the rotation center shaft 650 (first rotation center shaft), and the arm 21 (first driven) is formed via the rotation portion 81. The base end side of the member is connected to the large-diameter gear 65. The rotatable portion 81 includes a shaft portion and a shaft hole. In the rotatable portion 81, the arm 21 and the large-diameter gear 65 are rotatable.

  In this embodiment, the case member 52 is formed with a substantially arc-shaped cam groove 521 centered at a position shifted laterally from the rotation center shaft 650 of the large-diameter gear 65, and the cam groove 521 includes A shaft portion 211 (convex portion) protruding from the base end portion of the arm 21 is fitted. For this reason, the cam groove 521, the large-diameter gear 65, and the shaft portion 211 of the arm 21 constitute the link-cam mechanism 11 described with reference to FIG.

  3A and 3B, the arm 21 is disposed in a cover 210 having a shape along the arm 21, and the cover 210 performs a later-described movement integrally with the arm 21.

  In the present embodiment, the second driving device 70 includes a second motor 71 and a speed reduction mechanism including a train wheel 73 including 11 gears including a pinion connected to the output shaft of the second motor 71. have. The gear located at the end of the train wheel 73 is fixed to a support shaft 41 connected to the louver 2 at a position separated from the rotatable portion 81, and the support shaft 41 is a rotation center shaft 82 (first shaft) of the louver 2. 2 rotation center axis).

  In the second drive device 70 configured as described above, the second motor 70 is mounted on the case member 51 (support 5). Of the plurality of gears constituting the train wheel 73, the gear 731 (first power transmission rotating member) is a shaft used for the rotatable portion 81 that rotatably connects the arm 21 and the large-diameter gear 65. The gear 731 is coaxially arranged with respect to the rotatable portion 81.

  Further, among the plurality of gears constituting the train wheel 73, the gear 732 (second power transmission rotating member) positioned in front of the gear 731 is rotatable with respect to the rotation center shaft 650 of the large-diameter gear 65. The gear 732 is arranged coaxially with the rotation center shaft 650 of the large-diameter gear 65. Other gears constituting the train wheel 73 are mounted on the arm 21.

  Here, the second motor 71 is positioned on the side opposite to the arm 21 with respect to the large-diameter gear 65, and the train wheel 73 is connected to the second motor 71 with respect to the large-diameter gear 65 from the middle thereof. Is on the opposite side.

(Configuration around other arms)
FIG. 4 is an explanatory diagram when an arm arranged at the other end of the louver device to which the present invention is applied is viewed from the direction indicated by the arrow D2 in FIG.

  As shown in FIG. 5, the arm 23 arranged at the other end of the louver device 1 is not configured with a motor actuator, but is configured with a mechanism for moving the arm 23 following the arm 21. Yes. That is, a base plate 251 and a base plate 252 are configured for the arm 23, and a rotatable portion 281 is configured at a position away from the rotation center of the large-diameter gear 265. The base end side of the arm 23 is connected to the large-diameter gear 265. Here, the rotatable part 281 includes a shaft part and a shaft hole. In the rotatable part 281, the arm 23 and the large-diameter gear 265 are rotatable. The base plate 251 is formed with a substantially arc-shaped cam groove 255 centered on a position shifted laterally from the rotation center of the large-diameter gear 265, and the cam groove 255 has a base of the arm 23. A shaft portion 231 (convex portion) protruding from the end portion is fitted. Therefore, the cam groove 255, the large-diameter gear 265, and the shaft portion 231 of the arm 23 are provided with the link-cam mechanism 112 similar to the link-cam mechanism 11 of the first drive device 60 described with reference to FIG. It is composed. The arm 23 arranged at the other end portion of the louver device 1 is not configured with the second driving device, but the louver 2 is attached by the second driving device 70 at one end portion of the louver device 1. When driven, the louver 2 rotates around the support shaft 43 even at the tip of the arm 23.

(Operation)
In FIG. 4, in the louver device 1 of the present embodiment, when the first motor 61 of the first drive device 60 rotates, the large-diameter gear 65 rotates. Here, the large diameter gear 65 constitutes the link-cam mechanism 11 having the rotatable portion 81 as a joint together with the cam groove 521 and the shaft portion 211 of the arm 21, and the rotation center shaft 650 of the large diameter gear 65. The distance between the rotary portion 81 and the rotatable portion 81 is always constant, and the distance between the shaft portion 211 of the arm 21 located in the cam groove 521 and the position of the rotation center shaft 82 formed at the distal end portion of the arm 21 is always constant. It is constant. For this reason, when the large-diameter gear 65 rotates and the position of the rotatable portion 81 changes, the position of the shaft portion 211 of the arm 21 in the cam groove 521 and the rotation center shaft 82 formed at the distal end portion of the arm 21. The position of also changes. Accordingly, the position of the louver 2 supported at the tip of the arm 21 changes.

  Thus, when the second motor 61 is operated while changing the position of the louver 2 by changing the posture of the arm 21, the rotation output of the second motor 71 is the rotation center axis of the large-diameter gear 65. After being transmitted via a gear 732 arranged coaxially with respect to 650, it is transmitted to the tip of the arm 2 via a gear 731 arranged coaxially with respect to the rotatable portion 81. . Therefore, the louver 2 rotates around the rotation center shaft 82 (support shaft 41).

(Main effects of this form)
As described above, in the present embodiment, the louver 2 is the second centered around the rotation center shaft 82 (support shaft 41) on the arm 21 that is driven to rotate about the rotatable portion 81 by the first drive device 60. The rotational output of the second motor 71 is driven by a gear 731 arranged coaxially with respect to a rotatable portion 81 that rotatably connects the arm 21 and the large-diameter gear 65. Via, it is transmitted to the tip of the arm 21. Therefore, even if the second motor 71 is not mounted on the arm 21, the louver 2 can be driven even when the arm 21 is moved to any position and even when the arm 21 is moving. Therefore, the arm 21 can be reduced in size and weight because the second motor 71 need not be mounted on the arm 21.

  In this embodiment, since the rotatable portion 81 is on the large-diameter gear 65, the rotatable portion 81 also moves together with the large-diameter gear 65 when the arm 21 is driven by the first drive device 60. The second motor 71 is mounted on the support 5. Even with such a configuration, in this embodiment, the rotational output of the second motor 71 is transmitted via the gear 732 arranged coaxially with the rotation center shaft 650 of the large-diameter gear 65, and then rotated. It is transmitted to the tip of the arm 21 via a gear 731 arranged coaxially with respect to the free portion 81. Therefore, even when the second motor 71 is mounted on the support 5, the louver 2 can be driven even when the large-diameter gear 65 and the arm 21 are moving. Therefore, since it is not necessary to mount the second motor 71 on the large-diameter gear 65, the large-diameter gear 65 can also be reduced in weight. Therefore, the first motor used in the first driving device 60 can be reduced. A small one can be used as 61.

  In this embodiment, in the first drive device 60, the cam groove 521, the large-diameter gear 65, and the shaft portion 211 of the arm 21 constitute the link-cam mechanism 11 having the rotatable portion 81 as a joint. Therefore, the arm 21 can be made to perform a complicated operation only by driving by the first motor 61.

  In this embodiment, the gear 731 is supported by the large-diameter gear 65, but a configuration in which the gear 731 is supported on the arm 21 side may be employed.

[Embodiment 2]
(overall structure)
FIGS. 6A and 6B are a side view of the louver device according to Embodiment 2 of the present invention as viewed from one end, and a front view of the one end of the louver device as viewed from the louver. FIGS. 7A and 7B are a DD sectional view of FIG. 6B and a dd sectional view of FIG. 7A, respectively. FIGS. 8A and 8B are a cross-sectional view taken along line EE in FIG. 6B and a cross-sectional view taken along UVVXZa-b in FIG. FIGS. 9A and 9B are a BB cross-sectional view of FIG. 6B and an NPQRST cross-sectional view of FIG. 9A, respectively. FIGS. 10A and 10B are an AA cross-sectional view of FIG. 6B and an FGHHJKL cross-sectional view of FIG. 10A, respectively. The overall configuration of the louver device according to the present embodiment is substantially the same as that of the first embodiment, and therefore, the configuration of the motor actuator will be mainly described. Moreover, in the following description, the part which has a function common to Embodiment 1 is attached | subjected and demonstrated with the same code | symbol.

  6A and 6B, at one end portion of the louver device 1 of the present embodiment, the louver device 1 is disposed between a case composed of four case members 55, 56, 57, 58 and the case members 57, 58. The base plate 59 constitutes the support 5, and a motor actuator 10 described below is mounted on the support 5.

  First, as shown in FIGS. 7A and 7B, a first motor 61 (stepping motor) of the first driving device 60 is fixed to the case member 55 with the output shaft directed into the case. At the same time, a second motor 71 (stepping motor) of the second drive device 70 is fixed at a position adjacent to the first motor 61 with the output shaft directed into the case.

  As shown in FIGS. 8A and 8B, between the case member 56 and the case member 57, four pieces of rotational output are transmitted from a pinion connected to the output shaft of the first motor 61. 9 (a) and 9 (b), there are a total of four gears 634 passing through the case member 57 between the case member 57 and the case member 58, as shown in FIGS. Are arranged in order, and a train wheel 63 (deceleration mechanism) of the first driving device 60 is configured. In the gear train 63, a large-diameter gear 65 (drive rotary member) is engaged with the gear that is finally located. Here, among the plurality of gears constituting the train wheel 63, the gear 633 is fixed to the support shaft 3.

  In the large-diameter gear 65, a rectangular frame-shaped connecting portion 652 having an opening 651 extends from the rotation center shaft 650 toward one side, and a vertical plate portion 653 stands on the distal end side of the connecting portion 652. Yes. A horizontal plate portion 654 that partially covers the opening 651 is formed from the upper end portion of the vertical plate portion 653.

  The distal end side of the connecting portion 652 constitutes a rotatable portion 81, and the proximal end side of the arm 21 (first driven member) is large via the rotatable portion 81 as shown in FIG. It is connected to a radial gear 65. That is, in the rotatable portion 81, the outer peripheral surface of the vertical plate portion 653 has a semicircular arc shape, and on the proximal end side of the arm 21, a connection is provided with a circular recess into which the vertical plate portion 653 is inserted. A portion 215 is formed, and in the rotatable portion 81, the outer peripheral surface of the vertical plate portion 653 and the inner peripheral surface of the circular recess of the arm 21 slide, so that the connecting portion 215 of the arm 21 and the large-diameter gear 65. The connecting portion 652 is rotatably connected.

  In the present embodiment, the inner surface of the case member 58 shown in FIG. 6B has a substantially arc shape centered on a position shifted laterally from the rotation center shaft 650 of the large-diameter gear 65 as in the first embodiment. Two cam grooves (not shown) are formed, and two shaft portions 211 (convex portions) protruding from the base end portion of the arm 21 are fitted in these cam grooves. For this reason, the cam groove, the large-diameter gear 65, the shaft portion 211 of the arm 21 and the rotatable portion 81 constitute the link-cam mechanism 11 described with reference to FIG.

  10 (a) and 10 (b), the arm 21 is configured by bonding two cover members 216 and 217, and on the inner side thereof, the rear stage of the train wheel 73 of the second drive unit 70 is provided. A total of six gears constituting the side are arranged. Further, as shown in FIGS. 8A and 8B, a total of four sheets of rotation output are transmitted between the case member 56 and the case member 57 from the pinion connected to the second motor 71. Gears are arranged, and these gears are also included in the train wheel 73. Here, of the four gears arranged between the case member 56 and the case member 57, the final gear 733 is formed on the lower end side of the two-stage gear 732 that penetrates the case member 57. The two-stage gear 732 includes a gear 734 between the case member 57 and the case member 58, as shown in FIGS. 9 (a) and 9 (b).

  The gear 734 meshes with a gear 735 that is rotatably supported between the upper surface portion 656 and the bottom plate portion 657 of the large-diameter gear 65, and the gear 735 includes a bottom plate portion 657 and a horizontal plate portion 654 of the large-diameter gear 65. The gear 731 meshes with the gear of the first stage among the gears arranged on the inner side of the arm 21.

  Here, the gear located at the end of the train wheel 73 is fixed to a support shaft 71 connected to the louver at a position separated from the rotatable portion 81, and the support shaft 41 is a rotation center shaft 82 ( 2nd rotation center axis).

  In the thus configured train wheel 73, the support shaft 738 that supports the gear 731 (the first power transmission rotating member) is the center of the rotatable portion 81 that rotatably connects the arm 21 and the large-diameter gear 65. The gear 731 is disposed coaxially with the rotatable portion 81.

  Further, among the plurality of gears constituting the train wheel 73, the two-stage gear 732 (second power transmission rotating member) is rotatably supported with respect to the rotation center shaft 650 of the large-diameter gear 65. 732 is arranged coaxially with the rotation center shaft 650 of the large-diameter gear 65.

  In the louver device 1 including the motor actuator configured as described above, when the first motor 61 of the first drive device 60 rotates, the large-diameter gear 65 rotates. Here, as described with reference to FIG. 4, the large-diameter gear 65 constitutes the link-cam mechanism 11 together with the cam groove 521, the shaft portion 211, and the rotatable portion 81. The distance between the rotation center shaft 650 and the rotatable portion 81 is always constant. Further, the distance between the shaft portion 211 of the arm 21 located in the cam groove 521 and the position of the rotation center shaft 82 formed at the distal end portion of the arm 21 is always constant. For this reason, when the large-diameter gear 65 rotates and the position of the rotatable portion 81 changes, the position of the shaft portion 211 of the arm 21 in the cam groove 521 and the rotation center shaft 82 formed at the distal end portion of the arm 21. The position of changes. Accordingly, the position of the louver 2 supported at the tip of the arm 21 changes.

  Thus, when the second motor 61 is operated while changing the position of the louver 2 by changing the posture of the arm 21, the rotation output of the second motor 71 is the rotation center axis of the large-diameter gear 65. After being transmitted via a gear 732 arranged coaxially with respect to 650, a gear 731 arranged coaxially with respect to a rotatable portion 81 that rotatably connects the arm 21 and the large-diameter gear 65. Is transmitted to the tip of the arm 2 via. Therefore, the louver 2 rotates around the rotation center shaft 82 (support shaft 41).

  As described above, in this embodiment as well, the louver 2 is driven by the second driving device 70 around the rotation center shaft 82 (support shaft 41) on the arm 21 as in the first embodiment. The rotational output of the motor 71 is transmitted to the distal end portion of the arm 21 via a gear 731 that is coaxially disposed with respect to the rotatable portion 81 that rotatably connects the arm 21 and the large-diameter gear 65. Therefore, even if the second motor 71 is not mounted on the arm 21, the louver 2 can be driven even when the arm 21 is moved to any position and even when the arm 21 is moving. Therefore, the arm 21 can be reduced in size and weight because the second motor 71 need not be mounted on the arm 21.

  Further, since the rotatable portion 81 is on the large diameter gear 65, the rotatable portion 81 moves together with the large diameter gear 65 when the arm 21 is driven by the first driving device 60. The second motor 71 is mounted on the support 5. Even with such a configuration, in this embodiment, the rotational output of the second motor 71 is transmitted via the gear 732 arranged coaxially with the rotation center shaft 650 of the large-diameter gear 65, and then rotated. It is transmitted to the tip of the arm 21 via a gear 731 arranged coaxially with respect to the free portion 81. Therefore, even when the second motor 71 is mounted on the support 5, the louver 2 can be driven even when the large-diameter gear 65 and the arm 21 are moving. Therefore, since it is not necessary to mount the second motor 71 on the large-diameter gear 65, the large-diameter gear 65 can also be reduced in weight. Therefore, the first motor used in the first driving device 60 can be reduced. A small one can be used as 61.

  In this embodiment, in the first drive device 60, the cam groove 521, the large-diameter gear 65, and the shaft portion 211 of the arm 21 constitute the link-cam mechanism 11 having the rotatable portion 81 as a joint. Therefore, the arm 21 can be made to perform a complicated operation only by driving by the first motor 61.

  In this embodiment, the gear 731 is supported by the large-diameter gear 65, but a configuration in which the gear 731 is supported on the arm 21 side may be employed.

[Additional mechanism to the second embodiment]
(Origin position detection measures)
FIG. 11 is an explanatory diagram of a one-way clutch mechanism, a torque limiter, and a brake mechanism added to the louver device according to Embodiment 2 of the present invention.

  In this embodiment, since a stepping motor is used as the second motor 71, when the operation of the louver device 1 is started, it is necessary to set the origin position by operating the second motor 71 by a predetermined number of steps. is there. In this embodiment, the louver 2 is rotated downward, and the timing at which the louver 2 abuts on the lower end portion of the arm 21 or the lower end portion of the support 5 and the movement thereof is restricted is defined as the origin position. However, when such an operation is performed, the louver 2 does not collide with the lower end of the arm 2 or the lower end of the support 5 until the second motor 71 has completed a predetermined number of steps. As it repeats, a loud sound is generated.

  Therefore, in this embodiment, the gear meshed with the pinion fixed to the output shaft of the second motor 71 in the gear train 73 of the second drive device 70 shown in FIGS. It is configured as a compound gear 91 incorporating a clutch. More specifically, as shown in FIG. 11A, the composite gear 91 includes a first gear 91a and a second gear 91g, and the first gear 91a meshing with the pinion on the lower side is A small-diameter cylindrical portion 91c into which the support shaft fits is formed on the upper surface of the disk portion 91b on which the tooth portion is formed, and a large-diameter cylindrical portion provided with a slit 91d on the outside of the cylindrical portion 91c. 91e is formed coaxially. On the other hand, the upper second gear 91g is formed with a cylindrical portion 91i into which the small-diameter cylindrical portion 91c of the first gear 91a is fitted on the lower surface of the disk portion 91h having a tooth portion. A coil spring 91x is attached to the portion 91i. Therefore, when inserting the cylindrical portion 91i of the second gear 91g together with the coil spring 91x between the cylindrical portions 91c and 91e of the first gear 91a, if one end 91y of the coil spring 91x is inserted into the slit 91d, A one-way clutch is configured.

  That is, when the first gear 91a rotates in the direction in which the coil spring 91x is tightened, the rotation of the first gear 91a is transmitted to the second gear 91g. Further, even when the first gear 91a rotates in the direction of loosening the coil spring 91x, if a large torque is not applied to the second gear 91g, the rotation of the first gear 91a is transmitted to the second gear 91g. However, when a large torque is applied to the second gear 91g and the first gear 91a rotates in the direction of loosening the coil spring 91x, the first gear 91a rotates idle.

  Therefore, when detecting the origin position, when the louver 2 is in contact with the lower end portion of the arm 21 or the lower end portion of the support 5 and a large torque is applied to the second gear 91g, the first gear 91a. Since the rotation of the first gear 91a is not transmitted to the second gear 91g, even if the louver 2 comes into contact with the lower end portion of the arm 21 or the lower end portion of the support 5 when detecting the origin position, There is no sound.

(Measures against vibration caused by wind pressure)
In this embodiment, the second drive device 70 includes a gear train 73 composed of a plurality of gears, and backlash exists between the gears. Therefore, when the air is blown from the air conditioner, the louver 2 may vibrate and abnormal noise may be generated. Therefore, in this embodiment, the gear 92 fixed to the support shaft 41 at the final stage of the train wheel 73 of the second drive device 70 shown in FIGS. 10A and 10B is shown in FIG. A first brake mechanism is configured. That is, the gear 92 has a tooth portion formed on the outer peripheral surface of the outer cylindrical portion 92a, while a cylindrical portion 92b having a smaller diameter than the cylindrical portion 92a is formed inside the cylindrical portion 92a. The inner cylindrical portion 92b is formed with a plurality of slits 92a extending in the axial direction, and the cylindrical portion 92b is divided into a plurality of pieces. Here, the cylindrical portion 92 b is fitted so as to cover the cylindrical portion 218 formed on the cover member 216, so that the gear 92 can be rotated. At that time, a coil spring 92e is mounted around the cylindrical portion 92b.

  Therefore, when the gear 92 rotates while being supported by the cylindrical portion 218, a large frictional force is generated between the outer peripheral surface of the cylindrical portion 218 and the inner peripheral surface of the cylindrical portion 92b. It is in the state that it took. Therefore, when the wind is blown from the air conditioner, even if the louver 2 receives the wind pressure, the support shaft 41 and the gear 92 do not vibrate, so no abnormal noise is generated.

(Measures against damage to train wheel 73)
In this embodiment, the gear used for the train wheel 73 of the second drive device 70 shown in FIGS. 8A and 8B and FIGS. 10A and 10B is made of resin. Therefore, when an air conditioner user touches the louver 2 and an excessive force is applied to the train wheel 73 through the louver 2, the gears constituting the train wheel 73 may be damaged. Therefore, a torque limiter described with reference to FIG.

  That is, in FIGS. 10A and 10B, a torque limiter using the roller pin 93 a is configured in the gear 93 just before the last stage gear 92 of the train wheel 73. In constructing such a torque limiter, in the present embodiment, as shown in FIG. 11C, first, the gear 93 includes a first gear 93b and a second gear 93h. The first gear 93b is formed with a disk portion 93c having a tooth portion that meshes with the gear 92 of the final stage, and a cylindrical portion 93d extending downward from the disk portion 93c, and a roller pin 93a is formed on the cylindrical portion 93d. A plurality of grooves 93e to be held are formed at equiangular intervals. On the other hand, the second gear 93g includes a disk part 93h formed with a tooth part and a cylindrical part 93i protruding upward from the disk part 93h, and a roller pin is provided on the outer peripheral surface of the cylindrical part 93i. A plurality of grooves 93j into which 93a is partially fitted are formed at equiangular intervals.

  Here, the number of grooves 93e is equal to the number of roller pins 93a, whereas the number of grooves 93j is twice the number of grooves 93e and roller pins 93a. For example, the number of grooves 93e and roller pins 93a is 3, while the number of grooves 93j is 12. Therefore, the roller pin 93a is inserted into every third groove 93j, and the cylindrical portion 93d is fitted over the cylindrical portion 93i with the roller pin 93a mounted in each of the grooves 93e. At that time, a coil spring 93m is mounted around the cylindrical portion 93d. As a result, a portion of the roller pin 93a that protrudes outward from the groove 93e is pressed by the coil spring 93m, and the roller pin 93a is urged by the groove 93j while being held by the groove 93e.

  Therefore, in the gear 93, when a large torque is not applied to the first gear 93b, the rotation of the second gear 93g is transmitted via the roller pin 93b. On the other hand, when the flap 2 is held by the user and the force is applied to the first gear 93b via the support shaft 41 and the gear 92, a large torque is applied to the first gear 93b. Even if the second gear 93g rotates, the roller pin 93b moves from the groove 93j held so far to the adjacent groove 93j against the urging force of the coil spring 93m, and the first gear 93b has the first gear 93b. The rotation of the second gear 93g is not transmitted. Therefore, since the force applied to the flap 2 is absorbed by the gear 93, an excessive force is not applied to the gears constituting the train wheel 73, and even if a resin gear is used for the train wheel 73, the gears are damaged. There is nothing to do.

(Measures against dead weight of arm 21 and flap 2)
In this embodiment, as described with reference to FIGS. 4A and 4B, the link-cam mechanism 11 is configured by the arc-shaped cam groove 521, the large-diameter gear 65, and the shaft portion 211 of the arm 21. The movement of the arm 21 and the flap 2 is restricted by the cam groove 521. When such a configuration is adopted, when the shaft portion 211 rises along the cam groove 521, the arm 21 moves in the direction against the dead weight of the flap 2 and the arm 21. The arm 21 is displaced according to the rotation output of the first motor 60 when the shaft 211 is about to descend along the cam groove 521 due to the weight of the flap 2 and the arm 21. The flap 2 and the arm 21 may be displaced.

  Therefore, in this embodiment, a second brake mechanism is provided to the wheel train 63 of the first drive device 60 shown in FIGS. 9 (a) and 9 (b). Specifically, a brake mechanism 94 described with reference to FIG. 11D is configured between the gear 633 fixed to the support shaft 3 and the case member 58. In configuring such a brake mechanism 94, a portion of the case member 58 into which the cylindrical portion 633a of the gear 633 is inserted is a cylindrical portion 94a, and the cylindrical portion 94a includes a plurality of axially extending portions. Slits 94b are formed at equiangular intervals. A coil spring 94c is mounted around the cylindrical portion 94a.

  For this reason, when the gear 633 rotates while being inserted into the cylindrical portion 94 a, a large frictional force is generated between the outer peripheral surface of the cylindrical portion 633 a of the gear 633 and the cylindrical portion 94 a of the case member 58. Therefore, when the movement trajectory of the arm 21 and the flap 2 is defined by the link-cam mechanism 11 using the arc-shaped cam groove 521 as in the present embodiment, the shaft portion 211 tends to descend along the cam groove 521. In this case, the arm 21 does not move prior to the rotation of the first motor 60 due to the weight of the flap 2 and the arm 21, and the flap 2 and the arm 21 are moved by the rotation of the first motor 60. Can be controlled.

[Other embodiments]
In the first embodiment, the single cam groove 521 is used in configuring the link-cam mechanism 11. However, as in the second embodiment, the two cam grooves are arranged in parallel to the support 5. The shaft portion that is formed and protrudes from the arm 21 may be engaged with each of the two cam grooves. If comprised in this way, the arm 21 can be supported reliably.

  Moreover, in the said form, although the train wheel 73 was comprised in the 2nd drive device 70 for transmission of motive power, you may employ | adopt a timing belt mechanism. In such a case, the second driving device 70 includes a roller (first power transmission) coaxially with the shaft portion used for the rotatable portion 81 that rotatably connects the arm 21 and the large-diameter gear 65. And a roller (second power transmission rotating member) may be provided coaxially with respect to the rotation center shaft 650 of the large-diameter gear 65.

(A), (b) is the perspective view and top view of a louver apparatus which concern on Embodiment 1 of this invention. It is a top view which extracts and shows the arm periphery located in the one side edge part of the louver apparatus shown in FIG. (A), (b) is explanatory drawing when the motor actuator comprised with respect to the arm located in the one side edge part of the louver apparatus shown in FIG. 1 is seen from the direction shown by arrow A1 of FIG.1 (b). FIG. 2 is an explanatory diagram when viewed from the direction indicated by the arrow A2 in FIG. It is explanatory drawing which shows the structure of the link-cam mechanism of the 1st drive device in the motor actuator used for the louver apparatus shown in FIG. It is explanatory drawing when the arm arrange | positioned at the other side edge part of the louver apparatus shown in FIG. 1 is seen from the direction shown by the arrow D2 of FIG.1 (b). (A), (b) is the side view which looked at the louver apparatus which concerns on Embodiment 2 of this invention from the one side edge part, and the front view which looked at the one side edge part of the louver apparatus from the louver side. (A), (b) is DD sectional drawing and dd sectional drawing, respectively. (A), (b) is respectively EE sectional drawing and UVWXZ-ab sectional drawing. (A), (b) is respectively a BB sectional view and a NPQRST sectional view. (A), (b) is respectively AA sectional drawing and FGHHJKL sectional drawing. It is explanatory drawing of the one-way clutch mechanism, torque limiter, and brake mechanism which were added to the louver apparatus which concerns on Embodiment 2 of this invention.

Explanation of symbols

1 Louver device 2 Louver (second driven member)
10 motor actuator 11 link-cam mechanism 21 arm (first driven member)
60 first driving device 70 second driving device 71 second motor 81 rotatable part 82 second rotation center shaft 650 first rotation center shaft 731 gear (first power transmission rotating member)
732 Gear (second rotating member for power transmission)

Claims (8)

A support;
A first driving device including a first motor mounted on the support, and a driving rotary member that is driven to rotate about a first rotation center axis by the first motor;
A first driven member connected to the driving rotary member via a rotatable portion spaced from the first rotation center axis;
A second driven member disposed on the first driven member so as to be rotatable about a second rotation center axis separated from the rotatable portion;
A second motor for causing the second driven member to rotate around the second rotation center axis includes a second driving device mounted on the support or the driving rotating member; ,
In the second driving device, the rotation output of the second motor is composed of a gear or a roller supported coaxially with the rotatable portion with respect to the driving rotating member or the first driven member. A motor actuator, wherein the motor actuator is transmitted to the second driven member via a first power transmission rotating member. In claim 1,
The second motor is mounted on the support;
The rotational output of the second motor is obtained by using a second power transmission rotating member comprising a gear or a roller supported coaxially with the first rotation center axis with respect to the support or the driving rotating member. After passing through, the motor actuator is transmitted to the first power transmission rotating member. In claim 1 or 2,
The motor actuator, wherein the second motor is located on the opposite side of the driving rotating member from the first driven member. In any of claims 1 to 3,
A motor comprising a link-cam mechanism for defining a movement locus of the first driven member when the driving rotating member rotates with respect to the first driven member. Actuator. In claim 4,
The support is formed with a cam groove that defines a movement locus of the first driven member when the driving rotary member rotates by engaging with the convex portion of the first driven member,
The motor actuator, wherein the rotating member for driving, the rotatable portion, the convex portion of the first driven member, and the cam groove constitute the link-cam mechanism. In claim 5,
The cam groove is formed in two parallel to the support body,
2. The motor actuator according to claim 2, wherein the two cam grooves are engaged with each of two protrusions protruding from different positions of the first driven member. In any one of Claims 1 thru | or 6.
In the motor actuator, the second drive device includes a one-way clutch in a power transmission mechanism from the second motor to the second driven member. In any one of Claims 1 thru | or 7,
In the motor actuator, the second drive device includes a torque limiter in a power transmission mechanism from the second motor to the second driven member.

Images