WO2017057229A1

WO2017057229A1 - Louver device

Info

Publication number: WO2017057229A1
Application number: PCT/JP2016/078176
Authority: WO
Inventors: 林　勝彦; 岳彦矢澤; 顕一保科; 葉津嘉山
Original assignee: 日本電産サンキョー株式会社
Priority date: 2015-09-29
Filing date: 2016-09-26
Publication date: 2017-04-06

Abstract

Provided is a louver device with which it is possible to prevent excess stress from being transmitted to a motor and/or a power transmission member even when the louver device is subjected to an external force in the direction in which a wind-direction plate is either opened or closed. Specifically, the present invention overcomes the problem through a louver device (10) characterized in that a reducing gear train (30) for transmitting drive force from a first drive source (20) to an arm member (42) has a gear member (31) provided with an overload protection mechanism for minimizing transmission torque by consuming the excess torque of the reducing gear train (30) through turning at idle, the gear member (31) having a fixed gear (311) and a clutch gear (312) that are disposed on a shared shaft (314), the fixed gear (311) and the shaft body (314) rotate integrally in the circumferential direction, and the clutch gear (312) and the shaft body (314) rotate integrally in the circumferential direction when the torque is equal to or less than a prescribed threshold value.

Description

Louver device

The present invention relates to a louver device.

In Patent Document 1 below, an arm (first louver support member) that supports a wind direction plate (louver 5) along an arcuate cam surface (guide surface 322e) provided in a case (second cases 312 and 322). 21, a louver device (louver device 1) is disclosed in which an arm is reciprocated between a retracted position and an advanced position by sliding a cam follower portion (arc portions 213, 223) of a second louver support member 22). ing.

JP 2009-210207 A

In the louver device of the above-mentioned Patent Document 1, when an unexpected external force is applied to the power transmission member of the stepping motor, for example, the wind direction plate is manually opened and closed while the stepping motor is held, the stepping motor steps out, The power transmission member that transmits the driving force of the stepping motor to the wind direction plate may be damaged.

In view of the above problems, the problem to be solved by the present invention is that an excessive force is applied to the motor and the power transmission member even when an external force is applied to the louver device in either the opening direction or the closing direction of the wind direction plate. An object of the present invention is to provide a louver device that can prevent the transmission of various stresses.

In order to solve the above problems, a louver device according to the present invention includes a first drive source, an arm member that supports a wind direction plate that is a plate-like member, and a driving force of the first drive source directly or via another member. A reduction gear train that transmits to the arm member, and the reduction gear train includes an overload protection mechanism that suppresses transmission torque by idling when torque exceeding a predetermined threshold is applied. The gear member has a fixed gear and a clutch gear arranged on a common shaft body, and the fixed gear always rotates integrally with the shaft body in the circumferential direction, The clutch gear has the shaft body inserted through a shaft hole thereof, and the clutch gear and the shaft body are integrated in the circumferential direction when the torque applied to the gear member is equal to or less than a predetermined threshold value. In a connected state that rotates Wherein when the gear member to the torque exceeds a predetermined threshold value is applied, characterized by comprising the uncoupling state either idles.

A gear member having an overload protection mechanism is arranged in the reduction gear train, and the clutch gear and the shaft body are integrally rotated in the circumferential direction when the torque applied to the gear member is below a predetermined threshold value ( When a torque exceeding a predetermined threshold is applied, a configuration in which one of them is idled (to be in a disconnected state) can transmit excessive stress to the motor and the power transmission member. Can be blocked. Further, by incorporating a gear member having an overload protection mechanism as a part of the reduction gear train, the number of parts can be reduced as compared with the case where a separate overload protection mechanism is provided, and the apparatus can be downsized.

Further, it is preferable that the clutch gear and the shaft body in the connected state rotate integrally in the circumferential direction by a frictional force that acts directly or via another member rod between the clutch gear and the shaft body. .

When the clutch gear and the shaft body are connected by the frictional force, when a torque exceeding the frictional force is applied, the excess torque is consumed by sliding the clutch gear and the shaft body in the circumferential direction. By adjusting the frictional force according to a threshold value for switching between the connected state and the disconnected state of the clutch gear and the shaft body, the overload protection mechanism can be mounted with a simple structure. In addition, even when an external force is applied in any of the opening direction and the closing direction of the wind direction plate, it is possible to prevent excessive stress from being transmitted to the motor and the power transmission member.

The gear member further includes an elastic member, and the elastic member is disposed between the fixed gear and the clutch gear, and the fixed gear and the clutch gear are arranged along the axial direction of the shaft body. It is preferable that the clutch gears are biased in directions opposite to each other, and the clutch gear is connected to the shaft body by being biased in the axial direction by the elastic member.

An elastic member is disposed between the fixed gear and the clutch gear, and the elastic member is elastically moved by urging these gears in opposite directions with the elastic member so that the clutch gear and the shaft body are connected. By appropriately replacing with another elastic member having a different force, the torque for operating the overload protection mechanism (torque for switching the connected state to the disconnected state) can be flexibly adjusted.

In addition, a locking portion having an outer diameter larger than the diameter of the shaft hole of the clutch gear is provided at an end of the shaft body on the clutch gear side in the axial direction. The elastic member is biased toward the locking portion, and the movement in the direction is locked by the locking portion, whereby the axial position of the shaft body is determined. It is preferable that the opposing surface of a stop part and the said clutch gearwheel comprises the connection part which makes the said shaft body and the said clutch gearwheel the said connection state.

By inserting the shaft body into the clutch gear and urging the clutch gear toward the locking portion with the elastic member, the axial position of the clutch gear in the shaft body is determined, and the locking portion and the locking portion of the clutch gear The opposite surface on the side can be used as a connecting portion that connects the shaft body and the clutch gear.

Further, the locking portion may be constituted by an enlarged diameter portion in which the outer diameter of the shaft body itself is increased.

Further, a flange portion extending radially outward from the shaft body is formed at an end portion of the shaft body on the fixed gear side in the axial direction, and the fixed gear includes the shaft body and the flange portion. A shaft hole that can be inserted is formed, and a concave portion is formed on a surface of the end face of the fixed gear opposite to the surface on the elastic member side in which the flange portion is inserted into the shaft hole. The fixed gear is urged toward the flange portion by the elastic member, and the movement in the direction is locked by the flange portion, so that the axial arrangement position of the shaft body is increased. The shaft body and the fixed gear can rotate integrally in the circumferential direction when the flange portion and the concave portion in which the flange portion is fitted are engaged with each other in the circumferential direction. preferable.

The shaft of the fixed gear is positioned in the axial direction by fitting the flange of the shaft body into the recess provided on the end surface of the fixed gear, and urging the fixed gear toward the flange with an elastic member. And the shaft body can be integrally rotated in the circumferential direction.

Further, it is preferable that the fixed gear is integrally formed with the shaft body.

¡By integrally molding the fixed gear and the shaft body, it is possible to eliminate assembly errors when they are made of different members.

Further, the locking portion is constituted by a locking member separate from the shaft body, and the end of the shaft body on the clutch gear side in the axial direction is radially outward from the shaft body. An extended collar portion is formed, and the locking member has a shaft hole through which the shaft body and the collar portion can be inserted, and of the end surface of the locking member, the side opposite to the surface on the clutch gear side On the surface, a recess is formed in which the flange portion inserted through the shaft hole is fitted, and the locking member is urged toward the flange portion by the elastic member via the clutch gear. In addition, the axial position of the shaft body is determined by the movement in the direction being locked by the flange portion, and the flange portion and the flange portion are fitted. Positions in the circumferential direction of the shaft body by engaging the recesses with each other in the circumferential direction It is preferable that has been determined.

By configuring the locking portion with a locking member separate from the shaft body, the clutch gear can be disposed on the shaft body even if the fixed gear is a gear member formed integrally with the shaft body. .

Further, it is preferable that the elastic member is a cylindrical member, and the shaft body is inserted through a hollow portion of the elastic member.

It is not necessary to fix the end of the elastic member to the fixed gear or the clutch gear by making the elastic member cylindrical and inserting the shaft into the hollow portion and holding the elastic member on the gear member. Thereby, even when the clutch gear and the shaft are rotated in a disconnected state, the elastic member can be prevented from being twisted or dropped.

Moreover, when the surface of the end face of the clutch gear that is directed toward the axially central side of the gear member is the inner surface of the clutch gear, the inner surface of the clutch gear is opposed to the elastic member. It is preferable that a first annular plate having an outer diameter equal to or larger than the outer diameter of the elastic member is disposed between the elastic member and the elastic member.

The surface position of the contact surface of the first annular plate with the elastic member is equal to the surface position of the inner surface of the clutch gear in the vicinity of the first annular plate, or the surface of the inner surface. It is preferable that it is located in the axial direction center side of the said gear member rather than a position.

By making the assembled state of the first annular plate easily visible from the outside, for example, the first annular plate is mistakenly assembled twice, and the threshold torque in the connected state and the disconnected state deviates from the original value. Can be prevented.

Further, when the surface facing the axially outer side of the gear member among the end surfaces of the clutch gear is used as the outer surface of the clutch gear, the portion of the outer surface of the clutch gear that faces the locking portion It is preferable that a second annular plate having an outer diameter equal to or larger than the outer diameter of the elastic member is disposed between the engaging portion and the engaging portion.

In addition, the surface position of the contact surface of the second annular plate with the engaging portion is equal to the surface position of the outer surface of the clutch gear in the vicinity of the second annular plate, or It is preferable that the gear member is located outside the surface position in the axial direction.

By making the assembled state of the second annular plate easily visible from the outside, for example, the second annular plate is mistakenly assembled twice, and the threshold torque in the connected state and the disconnected state deviates from the original value. Can be prevented.

Further, it is preferable that the first annular plate and the second annular plate are made of a metal material when the clutch gear is made of a resin material, and made of a resin material when the clutch gear is made of a metal material.

When the elastic member is in direct contact with the end face of the clutch gear made of a resin material, the end face of the clutch gear may be scraped by the elastic member, or the rotation of the clutch gear may be hindered by the elastic member. These disadvantages can be eliminated by arranging the first annular plate between the clutch gear and the elastic member. Furthermore, the surface contact between the resins does not stabilize the friction coefficient, and tends to generate a squeak noise when sliding. Since the state of the surface of the metal plate is stable, these disadvantages can be eliminated by arranging the second annular plate between the clutch gear and the enlarged diameter portion. On the contrary, when the clutch gear (and the shaft body) is made of a metal material, each annular plate is preferably made of a resin material.

Further, a concentric ridge having an outer diameter equal to or smaller than the outer diameter of the first annular plate is formed at the contact portion of the clutch gear with the first annular plate side. Preferably it is.

場合 When contacting flat surfaces, the contact area becomes unstable. By providing concentric protrusions (that is, irregularities) on the end face of the clutch gear and intentionally limiting the contact portion between the clutch gear and the first annular plate, the contact area between the clutch gear and the first annular plate Can be made constant, and the operation of the overload protection mechanism can be stabilized.

The contact portion of the clutch gear with the second annular plate side is formed with a concentric protrusion having an outer diameter equal to or smaller than the outer diameter of the second annular plate. Preferably it is.

場合 When contacting flat surfaces, the contact area becomes unstable. By providing concentric ridges (that is, irregularities) on the end face of the clutch gear and intentionally limiting the contact portion between the clutch gear and the second annular plate, the contact area between the clutch gear and the second annular plate Can be made constant, and the operation of the overload protection mechanism can be stabilized.

Further, a cylindrical guide portion extending from the end surface to the elastic member side is formed on an end surface of the fixed gear on the elastic member side, and the end portion of the elastic member on the fixed gear side is formed on the guide gear. Preferably, a gap is provided between the inner peripheral surface of the elastic member and the outer peripheral surface of the shaft body.

A cylindrical guide part is provided on the end surface of the fixed gear on the elastic member side, and the end of the elastic member is arranged on the guide part, thereby preventing the elastic member from falling off the end surface of the fixed gear when the gear member is assembled. Is done. Thereby, the radial positioning of the fixed gear and the gear member is facilitated, and the assembly efficiency of the gear member can be increased. Further, by providing a gap between the inner peripheral surface of the elastic member and the outer peripheral surface of the shaft body, it is possible to prevent the elastic member and the shaft body from contacting each other even when the elastic member is drawn and squeezed. Can do.

The elastic member is preferably a coil spring.

A wide variety of coil springs are widely available in the market, and by using such coil springs as elastic members, the overload protection mechanism of the present invention adjusted to a desired operating torque can be realized more easily. Can do.

Further, it is preferable that a shaft hole which is a through hole extending in the axial direction is formed at the rotation center of the shaft body.

By providing the through hole in the shaft body, the occurrence of sink marks is suppressed even when the shaft body is made of resin, and the dimensional accuracy of the shaft body is increased. In addition, the louver device can be easily assembled by inserting the fixed shaft into the through hole of the shaft body to support the shaft body.

Further, it is preferable that the support shaft inserted through the shaft hole of the shaft body is fixed to the first drive source.

By supporting the gear member with the support shaft fixed to the first drive source, the gear member can be positioned with high accuracy, and the inclination and rattling of the gear member can be suppressed. Thereby, the meshing accuracy of the gear member is increased, the operation of the overload protection mechanism of the gear member becomes more accurate, and the noise and the deterioration of the component life due to the rattling of the gear member can be suppressed.

Further, it is preferable that the gear member is configured to mesh with the pinion gear of the first drive source.

The overload protection mechanism for a gear member of the present invention consumes excess torque due to idling. Therefore, even if the torque for operating the overload protection mechanism is too large or too small, the overload protection mechanism cannot achieve its purpose. Naturally, the overload protection mechanism operates when a torque larger than the transmission torque during normal operation is applied. Therefore, if the gear member having a large transmission torque during normal operation is provided with an overload protection mechanism, a protective effect can be obtained only when a higher external force (torque) is applied. On the other hand, if a gear member having a small transmission torque during normal operation is provided with an overload protection mechanism, the torque at which the overload protection mechanism operates needs to be smaller than the torque at which the gear member itself slips and rotates, Restrictions on the setting of the operating torque become severe. A gear member having an overload protection mechanism is meshed with the pinion gear of the first drive source, thereby realizing an overload protection mechanism in which the operation torque can be set relatively easily and can be operated quickly with respect to an abnormality. Can do.

Further, it is preferable that the fixed gear meshes with the pinion gear of the first drive source.

In order to allow the clutch gear and the shaft body to rotate asynchronously (operation in a state where the gear member is disengaged) is possible, a clearance needs to be provided between the clutch gear and the shaft body. Even if the clearance is provided with high accuracy, it is impossible to completely eliminate the deviation of the rotation center of the clutch gear and the shaft body. Further, the gear meshed with the pinion gear of the first drive source has a small meshing length and is particularly susceptible to eccentricity. By engaging the fixed gear integrally formed with the shaft body with the pinion gear of the first drive source, it is possible to suppress variations in noise and torque due to such eccentricity.

And a link mechanism that swings by the driving force of the first drive source, and a fixing portion that can accommodate the link mechanism, and the first drive source is a motor that can rotate in both forward and reverse directions. The link mechanism includes a plurality of link members and the arm member supported by these link members and reciprocatingly moved in the extending direction and the storing direction, and the plurality of link members are driven by the first drive source. A drive link that is driven, and a driven link that follows the operation of the drive link via the arm member, and a gear portion is formed on a proximal end side of the drive link, The distal end side is connected to the arm member, the proximal end gear portion is connected to the first drive source via the reduction gear train, and the driven link has the distal end side connected to the arm member and the proximal end side fixed to the fixed portion. Linked to the previous The said side edge portion of the extending direction of the arm member, it is preferable to adopt a configuration in which the wind direction plate is pivotally connected.

The load of the wind direction plate and the arm member can be distributed to each link member by reciprocating the arm member that opens and closes the wind direction plate by the link mechanism. As a result, it is possible to prevent the stress supporting the load from being concentrated on only a part, and to reduce the size of the entire apparatus.

Further, it is preferable that the link mechanism is a four-bar link mechanism having the arm member as an intermediate link, and the driven link is disposed on the extension direction side with respect to the drive link.

とする By making the link mechanism a four-bar link, the reciprocating movement of the arm member by the link mechanism can be realized with a minimum number of parts. Further, since the driven link does not need to be connected to the first drive source, there are fewer restrictions on the arrangement location than the drive link. Therefore, by disposing the driven link closer to the extending direction of the arm member than the driving link, the driven link can be disposed at the end of the extending direction side of the device, and the arm member is supported farther. Is possible.

According to the louver device of the present invention, even when an external force is applied to the louver device in either the opening direction or the closing direction of the wind direction plate, transmission of excessive stress to the motor and the power transmission member is prevented. Is possible.

It is an external appearance perspective view which shows an example of the arrangement configuration of a louver apparatus. It is a disassembled perspective view which shows the internal structure of a louver apparatus. It is a disassembled perspective view which shows the internal structure of an arm. It is a permeation | transmission figure which shows the meshing structure of a reduction gear train. It is the external appearance perspective view and sectional drawing of a 1st reduction gear. It is a disassembled perspective view of a 1st reduction gear. It is a perspective sectional view of the small diameter gear part of the 1st reduction gear. It is explanatory drawing which shows the reciprocating motion of the arm by a link mechanism. It is explanatory drawing which shows the structure of a 1st rocking | fluctuation control part. It is a figure explaining the handling structure of the lead wire of the 2nd motor. It is a disassembled perspective view which shows the internal structure of a support unit. It is explanatory drawing which shows the reciprocating motion of the arm by a support unit. It is explanatory drawing which shows the reciprocating motion of the arm in a louver apparatus. It is the external appearance perspective view and sectional drawing of the 1st reduction gear gear concerning other embodiment. It is a disassembled perspective view of the 1st reduction gear concerning other embodiment. It is a perspective sectional view of the small diameter gear part of the 1st reduction gear concerning other embodiments. It is a disassembled perspective view which shows the support structure of a 1st reduction gear. It is sectional drawing seen from the side which shows the support structure of a 1st reduction gear.

Hereinafter, embodiments of a louver device according to the present invention will be described with reference to the drawings. The louver device according to the present embodiment is a device that is installed at a blower opening of an air conditioner (not shown) and controls the air direction. In the following description, “width direction” means the X direction shown in the coordinate axis display of FIG. 1, “front-back direction” means the Y direction shown in the coordinate axis display, and “vertical direction” means the same coordinate axis table. Z direction shown in FIG.

(overall structure)
FIG. 1 is an external perspective view showing an example of an arrangement configuration of a louver device. In the arrangement example of FIG. 1, one common wind direction plate 91 is also referred to as two

louver devices

10, 10 ′ and one support unit 70 (hereinafter collectively referred to as “louver device 10 etc.”). ). The two louver devices 10 and 10 'are the same device, and the configuration of the louver device 10 described below is also the configuration of the louver device 10'. These louver devices 10 and the like are all arranged behind the wind direction plate 91 (on the side of the air conditioner casing not shown). The

louver devices

10 and 10 ′ are arranged in the vicinity of both ends in the longitudinal direction of the wind direction plate 91, and the support unit 70 is arranged at substantially the center in the longitudinal direction.

Arm connection pieces

911 and 912 which are connecting portions with the louver device 10 and the like are formed on the surface of the wind direction plate 91 facing the louver device 10 and the like. The wind direction plate 91 is supported by the

arms

42 and 72 by coupling the

arm connection pieces

911 and 912 to the wind direction

plate connection portions

252 and 721 provided on the

arms

42 and 72 of the louver device 10 and the like. The

arms

42 and 72 operate integrally.

The louver device 10, 10 'is a drive device that opens and closes and rotates the wind direction plate 91 by the driving force of the drive source provided in the louver device 10, 10'. On the other hand, the support unit 70 is an auxiliary unit that supports the wind direction plate 91 following the operation of the

louver devices

10, 10 ′. Even when the length of the wind direction plate 91 in the longitudinal direction is short, or when only the both ends of the wind direction plate 91 are supported by the

louver devices

10 and 10 ′, the wind direction plate 91 has a rigidity that does not cause deflection due to its own weight. In some cases, the support unit 70 may be omitted.

(Internal structure of louver device)
FIG. 2 is an exploded perspective view showing the internal structure of the louver device 10 (and the louver device 10 ′). The louver device 10 includes a first motor 20 (first drive source) that is a stepping motor, a link mechanism 40 that swings by the driving force of the first motor 20, and a link mechanism 40 that decelerates the rotation of the first motor 20. And a case 50 (fixed portion) that accommodates the link mechanism 40 and the reduction gear train 30.

The link mechanism 40 has two link members 41 and an arm 42 (arm member) supported by these link members 41 and reciprocating in an extending direction A and a storage direction B (see FIG. 8) described later. ing. The link member 41 includes a drive link 411 driven by the first motor 20 and a driven link 412 that follows the operation of the drive link 411 via the arm 42. In addition to the drive link 411 and the driven link 412, the link mechanism 40 constitutes a four-bar linkage mechanism in which the case 50 is a fixed link and the arm 42 is an intermediate link.

The case 50 includes a first case half 51 that can be disassembled in the width direction X, a second case half 52, and an intermediate plate 53. The first case half 51, the second case half 52, and the intermediate plate 53 are integrated by being connected by a set screw 59. The link mechanism 40 is disposed in a space defined by the first case half 51 and the middle plate 53, and the reduction gear train 30 is disposed in a space defined by the second case half 52 and the middle plate 53.

The first motor 20 is disposed outside the bottom surface (surface orthogonal to the width direction X) of the second case half 52 and is fixed to the second case half 52 by a set screw 29. On the bottom surface of the second case half 52, a portion corresponding to the position of the pinion gear 21 of the first motor 20 has a covered cylindrical shape protruding toward the opening side (inside the case 50) of the second case half 52. The pinion cover part 521 is provided. The pinion cover portion 521 is open on the pinion gear 21 side, and the pinion gear 21 is accommodated inside the pinion cover portion 521. The pinion cover part 521 is provided with a window part 521a which is an opening partly cut off in the circumferential direction, and the pinion gear 21 housed in the pinion cover part 521 has a part of its tooth part. Is exposed to the inside of the second case half 52 through the window 521a.

The reduction gear train 30 is a composite gear train that includes a large-diameter gear portion and a small-diameter gear portion, respectively. Each gear member of the reduction gear train 30 is rotatably supported by a support shaft 36 erected between the second case half 52 and the intermediate plate 53. The reduction gear train 30 sequentially transmits the rotation of the pinion gear 21 of the first motor 20 from the large diameter gear portion to the small diameter gear portion, thereby reducing the rotation of the pinion gear 21 and transmitting it to the gear portion 411c of the drive link 411. To do. By decelerating the rotation of the first motor 20 and transmitting it to the drive link 411, the arm 42 can be reciprocated using a general output motor.

A through hole 411b penetrating in the width direction X is formed in the base end portion (base end side) of the drive link 411 constituting the link mechanism 40, and the support shaft erected in the second case half 52 By inserting 522 into the through hole 411b, the base end portion of the drive link 411 is rotatably supported by the case 50.

Further, a gear portion 411c extending from the surface on the reduction gear train 30 side toward the reduction gear train 30 side is provided at the base end portion of the drive link 411. A cutout portion 533 through which the gear portion 411c is inserted is formed at a portion corresponding to the position of the gear portion 411c in the intermediate plate 53. The gear portion 411 c is inserted through the notch portion 533, thereby penetrating the intermediate plate 53 and meshing with the final gear of the reduction gear train 30. As the gear portion 411c meshes with the final gear of the reduction gear train 30, the driving force of the first motor 20 is transmitted to the drive link 411 via the reduction gear train 30 and the gear portion 411c.

The driven link 412 of the link mechanism 40 is provided with a substantially cylindrical shaft body 412b whose axis is parallel to the width direction X at the base end portion (base end side).

Bearings

513 and 523 which are circular through holes penetrating in the width direction X are formed at portions corresponding to the positions of the shaft bodies 412 b in the first case half 51 and the second case half 52. The driven link 412 is rotatably supported by the case 50 by fitting the shaft body 412b to the

bearings

513 and 523.

The “base end” of the link member 41 (drive link 411, driven link 412) in the present invention is a fixed joint, that is, fixed to a predetermined position and allowed to rotate, but in the vertical direction Z and the front-rear direction Y. The “tip” refers to a free joint, that is, an end that is allowed to rotate and swing.

In the present embodiment, the base ends of the drive link 411 and the driven link 412 are both supported by the case 50, but these base ends need not necessarily be supported by the case 50. For example, a member (fixed part) whose position is fixed, such as a housing of an air conditioner (not shown), can support the base end part rotatably, and is deformed by the load of the arm 42 and the wind direction plate 91 The case 50 can be substituted if it is a member having such a degree of rigidity that it does not.

(Inner structure of arm)
FIG. 3 is an exploded perspective view showing the internal structure of the arm 42. The arm 42 has a first arm half 421 and a second arm half 422 that are case bodies that can be disassembled in the width direction X. The first arm half 421 and the second arm half 422 are set screws. By being combined at 429, they are integrated.

The second motor 25, which is a stepping motor, is accommodated in the end of the arm 42 in the extending direction A side. The second motor 25 is a drive source that rotates the wind direction plate 91 within a predetermined angle range. A pinion gear 251 is mounted on the output shaft of the second motor 25 subjected to the D cut, and the rotation of the pinion gear 251 is decelerated and transmitted to the wind direction plate connecting portion 252 via the gear portion 252a of the wind direction plate connecting portion 252. . A circular opening portion 421a penetrating in the width direction X is formed at the end of the first arm half 421 on the extending direction A side, and the wind direction plate connecting portion 252 extends from the opening portion 421a to the outside of the arm 42. Exposed to. Thereby, the wind direction plate connection part 252 of the arm 42 and the arm connection piece 911 of the wind direction plate 91 can be coupled. By adopting a configuration in which the wind direction plate 91 is rotated by the second motor 25, a more complicated operation of the wind direction plate 91 is possible, and the degree of freedom of wind direction control is enhanced.

In the arm 42, a portion of the arm 42 on the side of the housing direction B with respect to the housing portion of the second motor 25 is provided with a rib 423 formed in a corrugated shape therein, and the rigidity of the arm 42 is enhanced by the rib 423. Yes. A part of the rib 423 also serves as an arm-side contact portion 67 of the second swing restricting portion 65 described later.

FIG. 10 is a diagram for explaining a structure for handling the lead wire 93 of the second motor 25. The lead wire 93 connected to the connector 253 of the second motor 25 is drawn into the case 50 through a gap provided above the rib 423 inside the arm 42. The lead wire 93 drawn into the case 50 passes through the upper side of the drive link 411 and is drawn into the guide piece 532 formed behind the middle plate 53 (left side as viewed in FIG. 10) and guided to the guide piece 532. It is pulled out of the louver device 10 from the outlet 54. As shown in FIG. 10B, the outlet 54 is an opening defined by the first case half 51 and the second case half 52.

(Reduction gear train)
FIG. 4 is a transparent view showing the meshing structure of the reduction gear train 30. The tooth part shown by the dotted line in FIG. 4 represents the gear part on the rear side of the figure of each gear member.

The tooth part of the pinion gear 21 exposed from the window part 521a of the pinion cover part 521 meshes with the large-diameter gear part of the first reduction gear 31 constituting the reduction gear train 30. Thereafter, the small-diameter gear portion of the first reduction gear 31 is the large-diameter gear portion of the second reduction gear 32, the small-diameter gear portion of the second reduction gear 32 is the large-diameter gear portion of the third reduction gear 33, and the third reduction gear. The small-diameter gear portion 33 is in mesh with the large-diameter gear portion of the fourth reduction gear 34, and the small-diameter gear portion of the fourth reduction gear 34 is in mesh with the large-diameter gear portion of the fifth reduction gear 35. The small-diameter gear portion of the fifth reduction gear 35 meshes with the gear portion 411c of the drive link 411. Thereby, the rotation of the first motor 20 is decelerated and transmitted to the drive link 411.

FIG. 17 is an exploded perspective view showing a support structure for the first reduction gear 31. 18 is a cross-sectional side view showing the support structure of the first reduction gear 31 (a cross-sectional view in the direction DD in FIG. 17 after the louver device 10 is assembled). The first motor 20 is provided with an attachment plate 201, which is a plate-like metal member, for fixing the first motor 20 to the second case half 52 on the output shaft side end surface of the case body 202. . The attachment plate 201 is formed with a support shaft fixing portion 201a whose upper surface is partially cut and raised. The support shaft 361 of the first reduction gear 31 is fixed to the support shaft fixing portion 201a so as not to move. Yes. The support shaft 361 passes through the support shaft fixing portion 201a in the thickness direction, and is adjusted to an axial position such that the base end portion does not contact the case body 202 of the first motor 20. The support shaft 361 passes through the boss portion 524 formed in the second case half 52 and is inserted into the shaft hole of the first reduction gear 31, and the tip portion is supported by the intermediate plate 53.

The first reduction gear 31 is supported by the support shaft 361 that is immovably fixed to the first motor 20, so that the inclination and rattling of the first reduction gear 31 are suppressed and the first relative to the position of the pinion gear 21 is suppressed. Since the relative positional relationship of the reduction gear 31 is kept constant, the meshing accuracy between the pinion gear 21 and the first reduction gear 31 is enhanced. As a result, a torque limiter mechanism (described later) of the first reduction gear 31 can be operated more accurately, and noise and a decrease in the component life due to the rattling of the first reduction gear 31 are suppressed.

(Torque limiter mechanism)
The first reduction gear 31 constituting the reduction gear train 30 is a torque limiter mechanism (overload protection mechanism) that suppresses transmission torque by consuming excess torque by idling when a torque exceeding a predetermined threshold is applied. ). As the predetermined threshold torque, a margin value is appropriately added to the upper limit value of the torque that can actually be transmitted to the first reduction gear 31 during normal operation of the louver device 10, and it can be determined that the probability of abnormality is high. What is necessary is just to set a torque.

FIG. 5 is an external perspective view of the first reduction gear 31 (FIG. 5A), and a cross-sectional view in the AA direction of the first reduction gear 31 shown in FIG. 5A (FIG. 5B). It is. FIG. 6 is an exploded perspective view of the first reduction gear 31. FIG. 7 is a perspective sectional view of the small-diameter gear portion 311. Hereinafter, in the description of the first reduction gear 31 and the torque limiter mechanism, “upper” and “lower” refer to the upper and lower sides in FIGS. 5 and 6, and “plan view” means from above the first reduction gear 31. This refers to the line-of-sight direction in which the first reduction gear 31 is looked down.

As shown in FIGS. 5 and 6, the first reduction gear 31 has a small-diameter gear portion 311 (fixed gear) and a large-diameter gear portion 312 (clutch gear) which are two gear portions. The small-diameter gear portion 311 and the large-diameter gear portion 312 are supported by a shaft portion 314 that is a common shaft body. The small-diameter gear portion 311 is above the shaft portion 314 and the large-diameter portion is below the shaft portion 314. A gear portion 312 is arranged.

Between the small-diameter gear portion 311 and the large-diameter gear portion 312, a coil spring 313, which is an elastic member, is arranged in a state compressed in the vertical direction, and the small-diameter gear portion 311 is moved upward by the coil spring 313. The radial gear portion 312 is biased downward.

Near the upper end portion of the shaft portion 314, a flange portion 314a extending outward in the radial direction from the shaft portion 314 is formed. As shown in FIG. 7, the small-diameter gear portion 311 has a shaft hole 311a into which the shaft portion 314 and the flange portion 314a can be inserted, and the upper surface of the small-diameter gear portion 311 has a flange after being inserted into the shaft hole 311a. A recess 311b into which the portion 314a is fitted is formed.

As shown in FIG. 5B, the small-diameter gear portion 311 is urged upward by the coil spring 313, and the upward movement is locked by the flange portion 314a fitted in the recess 311b. The arrangement position in the axial direction of the shaft portion 314 is determined. Further, as shown in FIG. 5A, the shaft portion 314 and the small-diameter gear portion 311 are circumferentially engaged with each other in the circumferential direction by the flange portion 314a and the concave portion 311b fitted with the flange portion 314a. Rotate in unison.

In the present embodiment, the small-diameter gear portion 311 (the gear that rotates integrally with the shaft portion 314) and the shaft portion 314 are separable due to the structure of assembling the large-diameter gear portion 312 to the shaft portion 314 described later. In the case of a structure in which the large diameter gear portion 312 can be assembled to the shaft portion 314 without removing the small diameter gear portion 311 from the shaft portion 314, the small diameter gear portion 311 and the shaft portion 314 are formed as one member. It may be integrally formed.

Further, on the lower surface of the small-diameter gear portion 311 (in the small-diameter gear portion 311 of this embodiment, the bottom surface of the gear portion 311c with which the upper end of the coil spring 313 contacts) is a cylindrical guide that extends downward from the peripheral portion of the lower surface. A portion 311d is formed, and the upper end of the coil spring 313 is disposed inside the guide portion 311d. Since the small-diameter gear portion 311 includes the guide portion 311d, the coil spring 313 is prevented from slipping and dropping off the lower surface of the small-diameter gear portion 311 when the first reduction gear 31 is assembled. Thereby, the radial positioning of the small-diameter gear portion 311 and the coil spring 313 is facilitated, and the assembly efficiency of the first reduction gear 31 is increased. The guide portion 311d is thinner than the gear portion 311c, and the guide portion 311d is not provided with a tooth portion.

Further, an enlarged diameter portion 314b (locking portion) in which the outer diameter of the shaft portion 314 is increased is formed in the vicinity of the lower end of the shaft portion 314. The enlarged diameter portion 314b is larger than the diameter of the shaft hole of the large diameter gear portion 312, and the large diameter gear portion 312 is urged downward by a coil spring 313 (via a first metal plate 315 described later), The downward movement (via a second metal plate 316 described later) is locked by the enlarged diameter portion 314b, whereby the axial position of the shaft portion 314 is determined. Further, the large-diameter gear portion 312 and the shaft portion 314 are applied with a torque equal to or less than a predetermined threshold value to the first reduction gear 31 by a frictional force generated when the large-diameter gear portion 312 is pressed against the enlarged-diameter portion 314b. Rotate in the circumferential direction when connected (connected state)

More specifically, in the axial direction of the shaft portion 314, a facing portion between the enlarged diameter portion 314 b of the shaft portion 314 and the large diameter gear portion 312 is a connecting portion 317 that connects the shaft portion 314 and the large diameter gear portion 312. The large-diameter gear portion 312 is pressed toward the diameter-expanded portion 314b by the coil spring 313, so that a circumferential direction is formed between these opposing portions (via a second metal plate 316 described later). A frictional force is generated against the rotation of the. The frictional force is adjusted to be equal to the above threshold torque, so that when a torque equal to or less than a predetermined threshold is applied to the first reduction gear 31, the large diameter gear portion 312 and the shaft portion 314 are Rotates integrally in the circumferential direction.

The coil spring 313 of this embodiment is a cylindrical member, and the coil spring 313 is held by the first reduction gear 31 by inserting the shaft portion 314 into the hollow portion. Both ends of the coil spring 313 are not fixed to the small-diameter gear portion 311, the large-diameter gear portion 312, and the like, so that even when the large-diameter gear portion 312 and the shaft portion 314 rotate asynchronously, the coil spring 313 The twisting and the coil spring 313 are prevented from falling off the first reduction gear 31. Further, a gap is provided between the inner peripheral surface of the coil spring 313 and the outer peripheral surface of the shaft portion 314, and the coil spring 313 does not contact the shaft portion 314 even if the coil spring 313 is slightly squeezed. .

Note that the elastic member of the present invention is not limited to the coil spring 313 of the present embodiment. The elastic member of the present invention can bias the small-diameter gear portion 311 and the large-diameter gear portion 312 in the vertical direction in addition to a coil spring having a different winding number and winding direction from the coil spring 313, a so-called closed-end coil spring, and the like. As long as it is a member that can slide at least the upper surface of the first metal plate 315, rubber or the like may be used. Further, the torque for operating the torque limiter mechanism can be flexibly adjusted by appropriately replacing the coil spring 313 with another elastic member having a different elastic force.

Further, of the end face of the large-diameter gear portion 312, a portion facing the coil spring 313 on the inner side surface 312 i, which is a surface directed upward (in the axial direction of the first reduction gear 31), and below (first first gear). A first metal plate 315, which is an annular thin plate member made of a metal material, is provided on a portion facing the enlarged diameter portion 314b of the outer surface 312e, which is a surface facing the reduction gear 31 in the axial direction. A first annular plate) and a second metal plate 316 (second annular plate) are disposed. The outer diameters of the first metal plate 315 and the second metal plate 316 are formed to be slightly larger than the outer diameter of the coil spring 313.

As shown in FIG. 6, D-cuts are made in the center holes of the first metal plate 315 and the second metal plate 316, and the D-cut

surfaces

315 a and 316 a are provided in the D-cut provided on the shaft portion 314. By being fitted to the surface 314d, the shaft portion 314, the first metal plate 315, and the second metal plate 316 rotate integrally in the circumferential direction.

For example, when the coil spring 313 is in direct contact with the inner side surface 312 i of the large-diameter gear portion 312, the inner surface 312 i of the large-diameter gear portion 312 may be scraped by the coil spring 313, and the rotation of the large-diameter gear portion 312 may cause the coil spring 313 to rotate. May be hindered. Since the first metal plate 315 is disposed between the large-diameter gear portion 312 and the coil spring 313, these problems are avoided.

In addition, the surface contact between the resins has a problem that the friction coefficient is difficult to stabilize and a squeak noise is liable to occur during sliding. Since the surface state of the metal plate is stable, such a problem is avoided by arranging the second metal plate 316 between the large-diameter gear portion 312 and the enlarged diameter portion 314b. .

The form of the first metal plate and the second metal plate of the present invention is not limited to the first metal plate 315 and the second metal plate 316 in the present embodiment. Other annular members may be used as long as they are members that are not deformed even when urged by the coil spring 313 and do not inhibit the rotation of the coil spring 313. Furthermore, the first metal plate and the second metal plate of the present invention are not essential components. If the above inconvenience does not occur even if the inner side surface 312i and the outer side surface 312e of the large-diameter gear portion 312 are brought into contact with the coil spring 313 or the enlarged diameter portion 314b, or if the inconvenience does not matter, the first metal plate The second metal plate may be omitted. The large-diameter gear portion 312 in this embodiment is a resin gear, but when the large-diameter gear portion 312 is made of a metal material, the first annular plate and the second annular plate are made of resin. Is preferred.

As shown in FIGS. 5B and 6, the contact portion of the inner surface 312 i of the large-diameter gear portion 312 with the first metal plate 315 and the second metal plate 316 on the outer surface 312 e of the large-diameter gear portion 312. Two concentric protrusions 312a are formed at the contact portion with each other. When the flat surfaces are brought into contact with each other, there is a problem that the contact area becomes unstable. By providing concentric ridges (that is, irregularities) on the end face of the large-diameter gear portion 312 and intentionally limiting the contact portion between the first metal plate 315 and the second metal plate 316 and the large-diameter gear portion 312. These contact areas can be made constant. Thereby, the stability of the operation of the torque limiter mechanism is enhanced.

Further, a shaft hole 314c, which is a through hole extending in the axial direction, is formed at the rotation center of the shaft portion 314. By providing the through hole in the shaft portion 314, sink marks during molding of the shaft portion 314 made of resin are suppressed, and the dimensional accuracy of the shaft portion 314 is improved. In addition, the louver device 10 can be easily assembled by adopting a configuration in which the support shaft 361 is inserted into the shaft hole 314c of the shaft portion 314 and the shaft portion 314 is supported.

Since the first reduction gear 31 has the above-described configuration, the small-diameter gear portion 311 (and the shaft portion 314) is within a torque range in which the shaft portion 314 and the large-diameter gear portion 312 can rotate integrally with the frictional force thereof. When the large-diameter gear portion 312 rotates integrally in the circumferential direction and a torque exceeding the frictional force is applied, either the small-diameter gear portion 311 (and the shaft portion 314) or the large-diameter gear portion 312 is idled. Yes (unconnected state).

The first reduction gear 31 in the present embodiment is configured such that the large-diameter gear portion 312 and the shaft portion 314 can slip each other, but naturally, the small-diameter gear portion 311 and the shaft portion 314 can slip. A configuration is also possible.

Since the reduction gear train 30 includes the first reduction gear 31 provided with the torque limiter mechanism, the wind direction plate 91 is manually opened and closed by the user during the hold of the first motor 20, for example. Even when an unexpected external force is applied to the power transmission member of the first motor 20 such as the link mechanism 40, the step-out of the first motor 20 and the breakage of the power transmission member are prevented. Further, for example, in the initialization operation of the first motor 20, the first motor 20 is intentionally moved toward the initial position of the drive link 411 in order to synchronize the recognition angle of the first motor 20 and the actual arrangement angle of the drive link 411. Even in the case of a step out of several steps, it is possible to reduce damage and abnormal noise of the power transmission member.

Further, as shown in FIG. 4, the first reduction gear 31 meshes with the pinion gear 21 of the first motor 20. Naturally, the torque limiter mechanism of the present invention operates when a torque larger than the transmission torque during normal operation is applied. Therefore, if a gear member having a large transmission torque during normal operation is provided with a torque limiter mechanism, a protective effect can be obtained only when a greater external force (torque) is applied. On the other hand, if a gear member having a small transmission torque during normal operation is provided with a torque limiter mechanism, the torque at which the torque limiter mechanism operates needs to be smaller than the torque at which the gear member itself slips and rotates. Restrictions on the setting of stricter. Since the first reduction gear 31 that is a torque limiter mechanism is engaged with the pinion gear 21 of the first motor 20, the setting of the operating torque is facilitated, and a torque limiter mechanism that can operate quickly with respect to an abnormality is provided. It has been realized.

Further, by incorporating the torque limiter mechanism as a part of the reduction gear train 30, the number of parts can be reduced as compared with the case where a separate torque limiter mechanism is provided, and the louver device 10 can be downsized.

(Another embodiment of the first reduction gear)
Below, the structure of the 1st reduction gear 81 which is other embodiment of a 1st reduction gear is demonstrated. Similar to the first reduction gear 31, the first reduction gear 81 is a gear member provided with a torque limiter mechanism (overload protection mechanism).

FIG. 14 is an external perspective view of the first reduction gear 81 (FIG. 14A), and a cross-sectional view in the AA direction of the first reduction gear 81 shown in FIG. 14A (FIG. 14B). It is. FIG. 15 is an exploded perspective view of the first reduction gear 81. FIG. 16 is a perspective sectional view of the locking member 819 (locking portion). Hereinafter, in the description of the first reduction gear 81 and the torque limiter mechanism, “upper” and “lower” refer to the upper and lower sides in FIGS. 14 and 15, and “plan view” means from above the first reduction gear 81. A line-of-sight direction in which the first reduction gear 81 is looked down.

As shown in FIGS. 14 and 15, the first reduction gear 81 has a small-diameter gear portion 812 (clutch gear) and a large-diameter gear portion 811 (fixed gear) which are two gear portions. The small-diameter gear portion 812 and the large-diameter gear portion 811 are supported by a shaft portion 814 that is a common shaft body. The small-diameter gear portion 812 is above the shaft portion 814 and the large-diameter portion is below the shaft portion 814. A gear portion 811 is arranged.

The large-diameter gear portion 811 of the first reduction gear 81 is integrally formed with the shaft portion 814. In the present embodiment, since the integrally formed large-diameter gear portion 811 meshes with the pinion gear 21 of the first motor 20, the large-diameter gear portion 312 and the first reduction gear 31 according to the previous embodiment are connected. Compared with a configuration in which the shaft portion 314 is formed of a separate member, the meshing accuracy between the large-diameter gear portion and the pinion gear 21 is improved. Thereby, noise and torque variations during rotation of the first reduction gear 81 are suppressed.

Between the small-diameter gear portion 812 and the large-diameter gear portion 811, a coil spring 813, which is an elastic member, is arranged in a state compressed in the vertical direction, and the small-diameter gear portion 812 is moved upward by the coil spring 813. The radial gear portion 811 is urged downward.

At the upper end of the shaft portion 814, a flange portion 814a extending outward in the radial direction from the shaft portion 814 is formed. As shown in FIG. 16, the locking member 819 has a shaft hole 819a into which the shaft portion 814 and the flange portion 814a can be inserted, and the flange portion 814a after being inserted into the shaft hole 819a is formed on the upper surface of the locking member 819. A recess 819b is formed in which is fitted.

As shown in FIG. 14B, the locking member 819 is urged upward by the coil spring 813 via the small-diameter gear portion 812 and moved upward by the flange portion 814a fitted in the concave portion 819b. Is locked, the axial position of the shaft portion 814 is determined. Further, as shown in FIG. 14A, the locking member 819 has a circumferential portion in the shaft portion 814 by engaging a flange portion 814a and a recess portion 819b fitted with the flange portion 814a with each other in the circumferential direction. The position of the direction is determined.

The locking member 819 attached to the upper end of the shaft portion 814 has an outer diameter larger than the diameter of the shaft hole of the small diameter gear portion 812. The small-diameter gear portion 812 is biased upward (via a first metal plate 815 described later) by a coil spring 813 and is moved upward by a locking member 819 (via a second metal plate 816 described later). As the movement is locked, the axial position of the shaft portion 814 is determined. Further, the small-diameter gear portion 812 and the shaft portion 814 are configured such that when a torque equal to or smaller than a predetermined threshold is applied to the first reduction gear 81 due to frictional force generated when the small-diameter gear portion 812 is pressed against the locking member 819. Rotate integrally in the circumferential direction (connected state).

More specifically, the facing portion of the locking member 819 and the small diameter gear portion 812 in the axial direction of the shaft portion 814 constitutes a connecting portion 817 that connects the shaft portion 814 and the small diameter gear portion 812. When the small-diameter gear portion 812 is pressed toward the locking member 819 by the coil spring 813, a frictional force against rotation in the circumferential direction is generated between these facing portions (via a second metal plate 816 described later). . The frictional force is adjusted to be equal to the above threshold torque, so that when a torque equal to or less than a predetermined threshold is applied to the first reduction gear 81, the small-diameter gear portion 812 and the shaft portion 814 rotate around. Rotate integrally in the direction.

In addition, since the locking member 819 is a separate member that can be attached and detached, the small-diameter gear portion 812 is assembled to the shaft portion 814 even if the large-diameter gear portion 811 and the shaft portion 814 are integrally formed. It is possible.

The coil spring 813 of this embodiment is a cylindrical member, and the coil spring 813 is held by the first reduction gear 81 by inserting a shaft portion 814 through the hollow portion. Both ends of the coil spring 813 are not fixed to the small-diameter gear portion 812, the large-diameter gear portion 811 or the like, and even when the small-diameter gear portion 812 and the shaft portion 814 rotate asynchronously, the coil spring 813 is twisted or coiled. The spring 813 is prevented from falling off the first reduction gear 81. Further, a gap is provided between the inner peripheral surface of the coil spring 813 and the outer peripheral surface of the shaft portion 814, and the coil spring 813 does not contact the shaft portion 814 even if the coil spring 813 is slightly wound. . The coil spring 813 is a closed-end coil spring whose both ends are polished, whereby the inclination of the arrangement position of the coil spring 813 and the bias of the biasing force are suppressed, and a stable threshold torque can be maintained. Has been.

Further, of the end surface of the small-diameter gear portion 812, the inner surface 812i, which is a surface directed downward (in the axial direction center side of the first reduction gear 81), is opposed to the coil spring 813, and upward (first reduction gear). The first metal plate 815 (first metal plate 815), which is a ring-shaped thin plate member made of a metal material, is disposed on the outer surface 812e facing the locking member 819, which is a surface facing the outer side of the gear 81 in the axial direction. 1 annular plate) and a second metal plate 816 (second annular plate) are disposed. The outer diameters of the first metal plate 815 and the second metal plate 816 are formed to be slightly larger than the outer diameter of the coil spring 813.

The surface position of the contact surface 815a with the coil spring 813 in the first metal plate 815 is located on the same plane as the surface position of the inner surface 812i in the vicinity of the first metal plate 815. In addition, the surface position of the contact surface 816a with the locking member 819 in the second metal plate 816 is located higher than the surface position of the outer surface 812e in the vicinity of the second metal plate 816. The first reduction gear 81 of the present embodiment has a configuration in which the assembled state of the first metal plate 815 and the second metal plate 816 is easily visible from the outside. Such work mistakes are unlikely to occur, and the threshold torque in the connected state and the disconnected state is prevented from deviating from the original value. In the present embodiment, the surface position of the inner surface 812i of the small-diameter gear portion 812 and the surface position of the first metal plate 815 are on the same plane, but these surface positions are not necessarily on the same plane. There is no need to be. For example, even when the surface position of the first metal plate 815 is lower than the surface position of the inner side surface 812i, the assembled state of the first metal plate 815 can be easily visually recognized from the outside, so the same effect is expected. be able to.

As shown in FIG. 15, D-cuts are made in the center holes of the first metal plate 815 and the second metal plate 816, and the D-cut

surfaces

815 a and 816 a are provided on the shaft portion 814. By being fitted to 814d and 814e, the shaft portion 814, the first metal plate 815 and the second metal plate 816 rotate integrally in the circumferential direction.

Also, a shaft hole 814c, which is a through hole extending in the axial direction, is formed at the rotation center of the shaft portion 814. By providing the through hole in the shaft portion 814, sink marks during the formation of the shaft portion 814 made of resin are suppressed, and the dimensional accuracy of the shaft portion 814 is improved.

Since the first reduction gear 81 has the above-described configuration, the small-diameter gear portion 812 and the large-diameter gear portion 811 (within the torque range in which the shaft portion 814 and the small-diameter gear portion 812 can rotate integrally with the frictional force thereof ( And the shaft portion 814) integrally rotate in the circumferential direction, and when a torque exceeding the frictional force is applied, either the small diameter gear portion 812 or the large diameter gear portion 811 (and the shaft portion 814) idles. (Unconnected state).

(Arm reciprocation)
FIG. 8 is an explanatory view showing the reciprocating motion of the arm 42 by the link mechanism 40. 8A shows a state where the arm 42 has moved to the limit in the storage direction B, and FIG. 8B shows a state where the arm 42 has moved to the limit in the extending direction A.

As shown in FIGS. 2 and 8, the link mechanism 40 includes two link members 41 (a drive link 411 and a driven link 412), and is reciprocated in the extending direction A and the storage direction B supported by the link members 41. And an arm 42. A second motor 25, which is a drive source for rotating the wind direction plate 91, is disposed at the end of the arm 42 on the extending direction A side.

The drive link 411 is formed with a circular through hole 411a penetrating in the width direction X at the tip. By inserting the support shaft 422a of the arm 42 into the through hole 411a, the distal end portion of the drive link 411 and the arm 42 are rotatably connected to each other. Further, as described above, the base end portion of the drive link 411 can rotate to the case 50 by inserting the support shaft 522 of the second case half 52 into the through hole 411b formed in the base end portion. It is supported by. The gear portion 411 c formed at the base end portion of the drive link 411 meshes with the fifth reduction gear 35 of the reduction gear train 30.

The driven link 412 is arranged on the extending direction A side with respect to the drive link 411. A circular through hole 412a penetrating in the width direction X is formed at the distal end portion of the driven link 412, and the distal end portion of the driven link 412 is inserted by inserting the support shaft 422b of the arm 42 into the through hole 412a. And the arm 42 are rotatably connected to each other. Further, as described above, the base end portion of the driven link 412 is attached to the case 50 by fitting the shaft body 412b to the

bearings

513 and 523 of the first case half 51 and the second case half 52. It is rotatably supported.

In the present embodiment, when the first motor 20 is rotated in the CW direction, the drive link 411 is also rotated in the CW direction, and the arm 42 is moved in the extending direction A. When the first motor 20 is rotated in the CCW direction, the arm 42 is also CCW. The arm 42 moves in the storage direction B.

By reciprocating the arm 42 that opens and closes the wind direction plate 91 with the link mechanism 40, the load of the wind direction plate 91 and the arm 42 can be distributed to each link member 41 (the drive link 411 and the driven link 412). As a result, it is possible to prevent the stress supporting the load from being concentrated on only a part, and the entire apparatus is downsized. Further, since the sliding portion of the link mechanism 40 is almost only the joint portion, the sliding resistance accompanying the reciprocating motion of the arm 42 is relatively small.

Further, a stepping motor is used as the first motor 20 of the present embodiment. The stepping motor can rotate in both forward and reverse directions, and the rotation angle can be calculated from the number of steps. Therefore, it is not necessary to separately perform feedback control using a rotary encoder or the like in order to detect the arrangement angle of the drive link 411 at that time. Thereby, reduction of the number of parts in the whole apparatus and size reduction of the apparatus are achieved. This also applies to the second motor 25.

Also, ribs 511 (see FIG. 9) that support the link member 41 from the width direction X (the axial direction of the indirect portion of each link member) on the surface of the first case half 51 and the intermediate plate 53 on the link mechanism 40 side. And ribs 531 (see FIG. 8) are formed. The rib 511 and the rib 531 are linearly extending ribs protruding toward the link mechanism 40 along the rotation trajectory of each link member 41, and each link member 41 is slidably in contact with the rib 511 and the rib 531. Yes.

Supporting each link member 41 with a linear rib prevents rattling of the link mechanism 40 and reduces sliding resistance with each link member 41.

(Swing restriction part)
The louver device 10 is provided with a swing restricting portion that is a pair of locking portions that restrict the swingable range of the link mechanism 40 by abutting each other when the link mechanism 40 swings to a predetermined position. Yes. In the present embodiment, two types of swing restricting portions, the first swing restricting portion 60 and the second swing restricting portion 65, are provided.

FIG. 9 is an explanatory view showing the structure of the first swing restricting portion 60. 9A shows a state where the arm 42 has moved to the limit in the storage direction B, and FIG. 9B shows a state where the arm 42 has moved to the limit in the extending direction A. The first case half 51 in FIG. 9 is transparently displayed by a broken line.

The first swing restricting portion 60 includes a protruding portion 61 formed on the drive link 411 and a contact portion 62 formed on the first case half 51. The protrusion 61 is a substantially rectangular tube-like engagement piece that protrudes from the drive link 411 along the width direction X (the axial direction of the indirect portion of the drive link) toward the first case half 51. The contact portion 62 is a rib-like engagement piece formed at a position where the link mechanism 40 abuts on the protrusion 61 when the link mechanism 40 swings to a predetermined position. The formation position of the contact portion 62 can be determined as appropriate according to the desired swing range of the link mechanism 40.

When the link mechanism 40 is swung to a predetermined position, the projection 61 formed on the drive link 411 and the contact portion 62 formed on the first case half 51 are brought into contact with each other, whereby the link The swingable range of the mechanism 40 can be limited to a desired range. Further, when the arm 42 is moved to the limit in the extending direction A side (that is, when the arm 42 is moved to a position where the projecting portion 61 and the contact portion 62 contact each other), the projecting portion 61 and the contact portion 62 are interposed. By supporting the drive link 411 on the first case half 51, the load on the arm 42 and the wind direction plate 91 can be further dispersed.

The second swing restricting portion 65 is formed from

opposed surfaces

66a and 67a of the bent portion 66 of the driven link 412 bent in a substantially L shape toward the inside of the link mechanism 40 and the arm side contact portion 67 of the arm 42. (See FIG. 8). The bent portion 66 is bent at an angle with which the facing

surfaces

66a and 67a abut when the arm 42 extends to a predetermined position in the extending direction A. The bending angle of the bent portion 66 can be appropriately determined according to the desired extension range of the arm 42.

FIG. 8B shows the arm 42 moved in the extending direction A. The extension range of the arm 42 in FIG. 8B is limited by the first swing restricting portion 60, and the second swing restricting portion 65 is not acting. However, when an even greater load is applied to the arm 42 and the arm 42 bends downward, the movement of the arm 42 is limited by the contact of the facing

surfaces

66a and 67a. As described above, the driven link 412 supports the arm 42 not only at its connecting portion but also at these facing

surfaces

66a and 67a, so that the load of the arm 42 and the wind direction plate 91 can be further dispersed.

In the present embodiment, the two types of swing restricting portions are provided, but only one of these swing restricting portions may be provided.

(Support unit)
FIG. 11 is an exploded perspective view showing the internal structure of the support unit 70. FIG. 12 is an explanatory view showing the reciprocating motion of the arm 72 by the support unit 70. The support unit 70 does not include a drive source, and is an auxiliary unit that supports the wind direction plate 91 following the operation of the

louver devices

10, 10 ′.

The support unit 70 has a case 71 composed of a first case half 711 and a second case half 712 that can be disassembled in the width direction X. An arm 72 and a follower link 73 are swingably supported on the case 71.

The configuration and support structure of the driven link 73 are the same as the driven link 412 of the louver device 10. The arm 72 is not provided with a driving source corresponding to the second motor 25 of the louver device 10, and the wind direction plate 91 is rotated by the wind direction plate connecting portion 721 provided at the end portion in the extending direction A side. They are only combined as possible.

A pin 751 that protrudes along the width direction X toward the second case half 712 is formed at the base end of the arm 72. The pin 751 is a cam follower that slides along an arcuate cam groove 752 provided in the second case half 712. The arc shape of the cam groove 752 is the same as the swing locus of the link mechanism 40 of the louver device 10. Thereby, the arm 72 of the support unit 70 can reciprocate on the same locus as the arm 42 of the

louver device

10, 10 ′.

The width of the support unit 70 in the width direction X is smaller than that of the louver devices 10 and 10 ', and the air path of the air conditioner is not obstructed. In the present embodiment, the use of the support unit 70 prevents the wind direction plate 91 from being bent by its own weight or wind pressure.

(Other embodiment of louver device)
Hereinafter, a louver device 11 according to another embodiment of the present invention will be described with reference to the drawings. In the following description, components having the same or the same functions as those of the previous embodiment are denoted by the same reference numerals as those of the previous embodiment, and detailed description thereof is omitted.

FIG. 13 is an explanatory view showing the reciprocating motion of the arm 42 in the louver device 11. 11A shows a state where the arm 42 has moved to the limit in the storage direction B, and FIG. 13B shows a state where the arm 42 has moved to the limit in the extending direction A.

The louver device 11 is provided with a braking mechanism that brakes the arm 42 by a braking spring 95 that is a coil spring. The brake spring 95 in this embodiment is connected to the drive link 411 and the driven link 412, and when the arm 42 moves in the extending direction A, the driven link 412 is urged toward the storage direction B by its elastic force. Thus, the movement of the arm 42 in the extending direction A is braked.

When moving the arm 42 in the extending direction A, the arm 42 is urged toward the extending direction A by the load of the arm 42 and the wind direction plate 91. In particular, when the wind direction plate 91 is receiving a large amount of wind pressure, the urging force is further increased. This may impair the stability of the opening / closing operation of the wind direction plate 91, may damage the power transmission member of the first motor 20, and may cause the first motor 20 to step out. By connecting each link member 41 with a brake spring 95 and braking the movement of the arm 42 in the extending direction A with its elastic force, it is possible to prevent such a problem in advance.

Note that the connection target of the brake spring 95 is not limited to the drive link 411 and the driven link 412, and the same effect can be obtained by connecting the case 50 and a part of the link mechanism 40.

The embodiments of the present invention have been described above. However, the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the scope of the present invention.

For example, in the link mechanism 40 according to the present embodiment, a four-bar linkage mechanism is employed in order to realize the reciprocating movement of the arm member by the link mechanism with a minimum number of parts. More complex operations may be possible.

10, 10 'louver device, 11 louver device according to another embodiment, 20 first motor (first drive source), 25 second motor, 251 pinion gear, 30 reduction gear train, 31, 81 first reduction gear (gear) Member (overload protection mechanism), 311 small gear part (fixed gear), 311a shaft hole, 311b recess, 311d guide part, 312 large gear part (clutch gear), 312a protrusion, 312i, 812i inner surface, 312e, 812e outer surface, 313, 813 coil spring (elastic member), 314, 814 shaft (common shaft body), 314a, 814a collar, 314b expanded diameter portion (locking portion), 314c, 814c shaft hole, 315, 815 First metal plate (first annular plate), 316, 816 Second metal plate (second annular plate), 317, 817 , 361, first reduction gear support shaft, 811 large diameter gear portion (fixed gear), 812 small diameter gear portion (clutch gear), 819 locking member (locking portion), 819a shaft hole, 819b recess, 40 link mechanism , 41 link member, 411 drive link, 412 driven link, 42 arm (intermediate link), 50 case (fixed part), 70 support unit, 91 wind direction plate, A extension direction, B storage direction

Claims

A first drive source;
An arm member that supports a wind direction plate that is a plate-shaped member;
A reduction gear train that transmits the driving force of the first drive source to the arm member directly or via another member,
The reduction gear train has a gear member having an overload protection mechanism that suppresses transmission torque by idling when a torque exceeding a predetermined threshold is applied;
The gear member has a fixed gear and a clutch gear arranged on a common shaft body,
The fixed gear always rotates integrally with the shaft body in the circumferential direction,
The clutch gear has the shaft body inserted through a shaft hole, and the clutch gear and the shaft body are integrated in the circumferential direction when the torque applied to the gear member is equal to or less than a predetermined threshold value. The louver device is in a connected release state in which one of the gear members is idled when a torque exceeding a predetermined threshold is applied to the gear member.
The clutch gear and the shaft body in the connected state are integrally rotated in the circumferential direction by a frictional force acting directly or via another member between the clutch gear and the shaft body. The louver device according to claim 1.
The gear member further includes an elastic member,
The elastic member is disposed between the fixed gear and the clutch gear, and urges the fixed gear and the clutch gear in opposite directions along the axial direction of the shaft body,
2. The louver device according to claim 1, wherein the clutch gear is connected to the shaft body by being urged by the elastic member in the axial direction.
A locking portion having an outer diameter larger than the diameter of the shaft hole of the clutch gear is provided at the end of the shaft body on the clutch gear side in the axial direction thereof.
The clutch gear is urged toward the locking portion by the elastic member, and movement in that direction is locked by the locking portion, thereby determining an axial position of the shaft body. And
The louver device according to claim 3, wherein a facing surface between the locking portion and the clutch gear constitutes a connecting portion that brings the shaft body and the clutch gear into the connected state.
The louver device according to claim 4, wherein the locking portion is constituted by an enlarged diameter portion in which the outer diameter of the shaft body itself is increased.
A flange portion extending radially outward from the shaft body is formed at an end of the shaft body on the fixed gear side in the axial direction,
The fixed gear has a shaft hole into which the shaft body and the flange can be inserted,
Of the end surface of the fixed gear, a surface opposite to the surface on the elastic member side is formed with a recess into which the flange portion is inserted into the shaft hole.
The fixed gear is urged toward the flange by the elastic member, and the movement in that direction is locked by the flange, whereby the axial position of the shaft body is determined. And
The shaft body and the fixed gear rotate integrally in the circumferential direction when the collar portion and the concave portion in which the collar portion is fitted are engaged with each other in the circumferential direction. 4. The louver device according to 3.
The louver device according to claim 1, wherein the fixed gear is integrally formed with the shaft body.
The fixed gear is integrally formed with the shaft body,
The locking portion is constituted by a locking member separate from the shaft body,
An end portion of the shaft body on the side of the clutch gear in the axial direction is formed with a flange extending radially outward from the shaft body,
The locking member has a shaft hole into which the shaft body and the flange portion can be inserted,
On the opposite surface of the end surface of the locking member to the clutch gear side, a recess is formed in which the flange portion is inserted into the shaft hole.
The locking member is urged toward the flange portion by the elastic member via the clutch gear, and the movement in the direction is locked by the flange portion, whereby the axial direction of the shaft body The arrangement position in the circumferential direction of the shaft body is determined by engaging the flange part and the concave part fitted with the flange part in the circumferential direction. The louver device according to claim 4.
4. The louver device according to claim 3, wherein the elastic member is a cylindrical member, and the shaft is inserted into a hollow portion of the elastic member.
Of the end faces of the clutch gear, when the face directed toward the axial center of the gear member is the inner face of the clutch gear,
A first annular plate having an outer diameter equal to or larger than the outer diameter of the elastic member is provided between the elastic member and the facing portion of the clutch gear facing the elastic member. The louver device according to claim 9, wherein the louver device is arranged.
The surface position of the contact surface of the first annular plate with the elastic member is equal to the surface position of the inner surface of the clutch gear in the vicinity of the first annular plate, or from the surface position of the inner surface. The louver device according to claim 10, wherein the louver device is also located on the axial center side of the gear member.
The elastic member is a cylindrical member, and the shaft body is inserted through a hollow portion of the elastic member,
Of the end faces of the clutch gear, when the face directed outward in the axial direction of the gear member is the outer face of the clutch gear,
A second annular member having an outer diameter equal to or larger than the outer diameter of the elastic member between the engaging portion on the outer side surface of the clutch gear and the engaging portion. The louver device according to claim 4, wherein a plate is arranged.
The surface position of the contact surface of the second annular plate with the locking portion is equal to the surface position of the outer surface of the clutch gear in the vicinity of the second annular plate, or the surface position of the outer surface. The louver device according to claim 12, wherein the louver device is located on the outer side in the axial direction of the gear member.
The elastic member is a cylindrical member, and the shaft body is inserted through a hollow portion of the elastic member,
Of the end faces of the clutch gear, when the face directed outward in the axial direction of the gear member is the outer face of the clutch gear,
A second annular member having an outer diameter equal to or larger than the outer diameter of the elastic member between the engaging portion on the outer side surface of the clutch gear and the engaging portion. The board is placed,
11. The first annular plate and the second annular plate are made of a metal material when the clutch gear is made of a resin material, and made of a resin material when the clutch gear is made of a metal material. The louver device described in 1.
The contact portion of the clutch gear with the first annular plate is formed with a concentric ridge having an outer diameter equal to or smaller than the outer diameter of the first annular plate. The louver device according to claim 10.
A concentric ridge having an outer diameter equal to or smaller than the outer diameter of the second annular plate is formed at the contact portion of the clutch gear with the second annular plate side. The louver device according to claim 12.
A cylindrical guide portion extending from the end surface to the elastic member side is formed on the end surface of the fixed gear on the elastic member side,
An end portion of the elastic member on the fixed gear side is disposed inside the guide portion,
The louver device according to claim 9, wherein a gap is provided between an inner peripheral surface of the elastic member and an outer peripheral surface of the shaft body.
The louver device according to claim 9, wherein the elastic member is a coil spring.
2. A louver device according to claim 1, wherein a shaft hole, which is a through hole extending in the axial direction, is formed at the rotation center of the shaft body.
The louver device according to claim 19, wherein a support shaft inserted through the shaft hole of the shaft body is fixed to the first drive source.
2. The louver device according to claim 1, wherein the gear member meshes with a pinion gear of the first drive source.
The louver device according to claim 7, wherein the fixed gear of the gear member meshes with a pinion gear of the first drive source.
A link mechanism that swings by the driving force of the first driving source;
A fixing portion capable of accommodating the link mechanism;
The first drive source is a motor that can rotate in both forward and reverse directions,
The link mechanism includes a plurality of link members and the arm member supported by these link members and reciprocating in the extending direction and the storing direction.
The plurality of link members include a drive link driven by the first drive source, and a driven link that follows the operation of the drive link via the arm member,
A gear portion is formed on the base end side of the drive link,
The drive link has a distal end side connected to the arm member, and a base end side gear portion connected to the first drive source via the reduction gear train,
The driven link has a distal end side connected to the arm member and a proximal end side connected to the fixed portion.
The louver device according to claim 1, wherein the wind direction plate is rotatably connected to a side end portion of the arm member in the extending direction.
The link mechanism is a four-bar link mechanism having the arm member as an intermediate link,
The louver device according to claim 23, wherein the driven link is disposed on the extension direction side of the drive link.