JP6584894B2 - Louver device - Google Patents

Description

  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 Patent Document 1, when the arm is moved to the forward position, the load of the arm and the wind direction plate is applied to the base end of the arm and the vicinity of the opening of the case (the first fixed body 31 and the second fixed body 32). It is necessary to support only in the department. In particular, one of the arms (first louver support member 21) is provided with a motor (second motor 81) for rotating the wind direction plate at the tip thereof, and further the wind pressure received by the wind direction plate. Also increase the load. In order to prevent breakage and deformation of the portion where the stress supporting the load is concentrated, it is necessary to provide the arm and case of Patent Document 1 with appropriate rigidity, and there is a problem that it is difficult to downsize the member.

  In view of the above problems, the problem to be solved by the present invention is to provide a louver device that can disperse and support the loads of the wind direction plate and the arm.

  In order to solve the above problems, a louver device according to the present invention includes a first drive source that is a drive source, a link mechanism that swings by a drive force of the first drive source, and a fixing portion that can accommodate the link mechanism. The link mechanism includes a plurality of link members, and an arm member that is supported by these link members and reciprocates in the extending direction and the storage direction, and the plurality of link members include the first link member. A drive link driven by a drive source; and a driven link that follows the operation of the drive link via the arm member. The drive link has a distal end on the arm member and a proximal end on the first link. Connected to the drive source directly or via another member, the driven link has a distal end side connected to the arm member, a proximal end side connected to the fixed portion, and an extension direction side end portion of the arm member, Wind that is a plate-like member Plates and gist to be 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 concentrating on only a part, and to reduce the size of the entire apparatus.

  Moreover, 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.

  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.

  Further, the link mechanism or the fixed portion is a swing that is a pair of locking portions that restricts the swingable range of the link mechanism by abutting each other when the link mechanism swings to a predetermined position. It is preferable that a restricting portion is provided.

  By providing the swing restricting portion of the link mechanism in the louver device, the swingable range of the link mechanism can be limited to a desired range.

  A first swing restricting portion that is the swing restricting portion including a protrusion formed on the drive link and a contact formed on the fixed portion; It protrudes from the drive link to the fixed portion side along the axial direction of the indirect portion, and the contact portion is disposed at a position where it comes into contact with the protrusion when the link mechanism swings to a predetermined position. preferable.

  When the link mechanism is swung to a predetermined position, the projecting portion formed on the drive link and the contact portion formed on the fixed portion are brought into contact with each other, so that the swingable range of the link mechanism is reduced. It can be limited to a desired range. Further, when the arm member is moved to the limit in the extending direction side (that is, when it is moved to a position where the projecting portion and the contact portion abut), the drive link is fixed to the fixed portion via the projecting portion and the contact portion. As a result, the load on the arm member and the wind direction plate can be further dispersed.

  And a second swing restricting portion that is the swing restricting portion including the arm member and the driven link bent in a substantially L shape toward the inner side of the link mechanism. It is good also as a structure bent at the angle which contact | abuts the opposing surface of the said arm member, when an arm member extends to the predetermined position in the said extension direction.

  When the arm member moves to a predetermined position in the extending direction, the arm member and the driven link are brought into contact with each other, whereby the swingable range of the link mechanism can be limited to a desired range. . Further, when the arm member is moved to the limit in the extending direction side (that is, when the arm member is moved to a position where the facing surfaces of the arm member and the driven link abut), the driven link is connected to the connecting portion ( By supporting not only the joint portion) but also the surface facing the arm member, the load of the arm member and the wind direction plate can be further dispersed.

  The first drive source is a motor that can rotate in both forward and reverse directions, and a gear portion is formed on the base end side of the drive link, and the gear portion is connected to the first drive via a reduction gear train. It is preferably connected to a source.

  By using a motor that can rotate in both forward and reverse directions, the moving direction of the arm member can be controlled by switching the rotation direction of the motor. Further, by reducing the rotation of the motor by the reduction gear train and transmitting it to the gear portion of the drive link, the arm member can be moved by a general output motor.

  The first drive source is preferably a stepping motor.

  The stepping motor can rotate in both forward and reverse directions, and the rotation angle can be calculated from the number of steps. Therefore, there is no need to separately perform feedback control using a rotary encoder or the like in order to detect the arrangement angle of the drive link at that time. Thereby, the number of parts in the whole apparatus can be reduced and the apparatus can be downsized.

  The reduction gear train has an overload protection mechanism, and the overload protection mechanism suppresses the transmission torque by consuming the excess torque due to idling when a torque exceeding a predetermined threshold is applied. A gear member is preferred.

  Since the reduction gear train has an overload protection mechanism, even when an unexpected external force is applied to the power transmission member of the stepping motor, for example, when the wind direction plate is manually opened and closed while the stepping motor is held, the stepping motor Step-out and damage to the power transmission member can be prevented.

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

  The overload protection mechanism of the present invention consumes excess torque due to idling. 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. By engaging the gear member, which is an overload protection mechanism, with the pinion gear of the first drive source, an overload protection mechanism that makes it relatively easy to set the operating torque and that can operate quickly with an abnormality is realized. Can do.

  The urging member further includes a braking mechanism that brakes the arm member, and the urging member is connected to a part of the link mechanism and the fixing portion, or to the driven link and the drive link. The urging member urges a part of the link mechanism or the driven link toward the storage direction by its elastic force when the arm member moves in the extending direction. It is good also as a structure which brakes the movement to the said extension direction.

  When the arm member is moved in the extending direction, the arm member is biased toward the extending direction by the load of the arm member and the wind direction plate. In particular, when the wind direction plate receives 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, may damage the power transmission member of the first drive source, and may cause a step-out when the first drive source is a stepping motor, for example. By connecting the link mechanism and the fixing portion with the urging member and braking the movement of the arm member in the extending direction with its elastic force, the above-mentioned concern can be solved.

  The biasing member of the braking mechanism is preferably a coil spring.

  By using the coil spring, a braking mechanism for the arm member can be easily realized.

  Moreover, the said fixing | fixed part has the rib extended in the linear form which protruded in the said link mechanism side along the axial direction of the indirect part of each said link member, and each said link member contacts the said rib so that sliding is possible. Accordingly, it is preferable that the positioning in the axial direction is performed.

  By supporting each link member from the axial direction with a linearly formed rib formed in the fixed portion, it is possible to prevent the link mechanism from rattling. Moreover, sliding resistance with each link member can be reduced by forming such ribs in a linear shape.

  In addition, a second drive source as a drive source is disposed at a side end portion of the arm member in the extending direction, and the wind direction plate is rotated within a predetermined angle range by the drive force of the second drive source. Preferably it is possible.

  By rotating the wind direction plate by the second drive source provided at the side end portion in the extending direction of the arm member, more complicated operation of the wind direction plate is possible, and the degree of freedom of wind direction control can be increased.

  The second drive source is preferably a stepping motor.

  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 wind direction plate at that time. Thereby, the number of parts in the whole apparatus can be reduced and the apparatus can be downsized.

  According to the louver device of the present invention, it is possible to disperse and support the load of the wind direction plate and the arm.

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 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.

  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.

  On the surface of the wind direction plate 91 facing the louver device 10 and the like, arm connection pieces 911 and 912 that are connecting portions with the louver device 10 and the like are formed. 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 devices 10 and 10 ′ are driving devices that open and close and rotate the wind direction plate 91 by a driving force of a driving source provided in the louver devices 10 and 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 includes two link members 41 and an arm 42 (arm member) supported by these link members 41 and reciprocating in an extension direction A and a storage direction B (see FIG. 6) 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 (the 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.

  In addition, a gear portion 411 c extending 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 end portions of the drive link 411 and the driven link 412 are both supported by the case 50, but these base end portions are not necessarily 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.

  A second motor 25 (second drive source), which is a stepping motor, is accommodated in an end portion 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 that is formed in a corrugated shape. The rib 423 increases the rigidity of the arm 42. 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. 8 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 on the rear side (left side in FIG. 8) of the intermediate plate 53 and guided to the guide piece 532. It is pulled out of the louver device 10 from the outlet 54. As shown in FIG. 8B, 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.

(Torque limiter mechanism)
Among the gear members of the reduction gear train 30, the first reduction gear 31 is a torque limiter mechanism that suppresses transmission torque by consuming excess torque by idling when torque exceeding a predetermined threshold is applied. A gear member having an overload protection mechanism. As the predetermined threshold torque, an appropriate 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 the normal operation of the louver device 10, and a torque that can be determined to be highly likely to be abnormal. You only have to set it.

  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). . 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. 5A and 5B, and “plan view” refers to the first reduction gear. A line-of-sight direction in which the first reduction gear 31 is looked down from above 31.

  The first reduction gear 31 is composed of an upper small-diameter gear portion 311 and a lower large-diameter gear portion 312 that are made of different members. The small-diameter gear portion 311 and the large-diameter gear portion 312 are supported by a common shaft portion 314 and can rotate independently of each other. A coil spring 313 is disposed between the small-diameter gear portion 311 and the large-diameter gear portion 312 in a state of being compressed in the vertical direction. The small-diameter gear portion 311 is moved upward by the coil spring 313, and the large-diameter gear portion 312. Is biased downward.

  The small-diameter gear portion 311 is urged upward by the coil spring 313 coming into contact with the lower surface thereof, and is moved upward by a flange portion 314a extending radially outward from the vicinity of the upper end of the shaft portion 314. It has been stopped. Moreover, as shown to Fig.5 (a), the opening part 311a of the small diameter gear part 311 upper end in which the collar part 314a is arrange | positioned is formed in planar view cross shape. Thereby, the collar part 314a and the opening part 311a are mutually engaged in the circumferential direction, and the small diameter gear part 311 and the shaft part 314 are always rotated integrally in the circumferential direction.

  The large-diameter gear portion 312 is press-fitted into the shaft portion 314, and a metal plate 315, which is an annular flat plate member, is coaxially disposed on the upper and lower surfaces thereof. The large-diameter gear portion 312 is urged downward through the metal plate 315 when the coil spring 313 contacts the metal plate 315 disposed on the upper surface side of the large-diameter gear portion 312. Further, the metal plate 315 disposed on the lower surface side of the large diameter gear portion 312 is placed on the upper surface of the enlarged diameter portion 314b formed in the vicinity of the lower end of the shaft portion 314. The downward movement of the large-diameter gear portion 312 is locked by the portion 314b. Therefore, the large-diameter gear portion 312 is pressed against the enlarged-diameter portion 314b by the urging force of the coil spring 313. As a result, the large-diameter gear portion 312 rotates around the shaft portion 314 in the circumferential direction due to the frictional resistance caused by press-fitting into the shaft portion 314 and the frictional resistance caused by being pressed against the enlarged-diameter portion 314b by the coil spring 313. To do.

  Since the first reduction gear 31 has the above-described configuration, the first reduction gear 31 and the smaller diameter gear portion 311 (and the shaft portion 314) are larger than the smaller diameter gear portion 311 within the torque range in which the shaft portion 314 and the large diameter gear portion 312 can be rotated by the frictional resistance. The diameter gear portion 312 rotates integrally in the circumferential direction, and when a torque exceeding the frictional resistance is applied, either the small diameter gear portion 311 (and the shaft portion 314) or the large diameter gear portion 312 idles.

  Since the reduction gear train 30 includes the first reduction gear 31 provided with the torque limiter mechanism, for example, during the hold of the first motor 20, the wind direction plate 91 is manually opened and closed by the user, and the reduction gear train 30 and the link mechanism. Even when an unexpected external force such as 40 is applied to the power transmission member of the first motor 20, it is possible to prevent the step-out of the first motor 20 and damage to the power transmission member. 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 torque limiter mechanism is provided on a gear member (for example, the fifth reduction gear 35) having a large transmission torque during normal operation, a protective effect can be obtained only when a greater external force (torque) is applied. By providing the first speed reduction gear 31 having the smallest transmission torque in the speed reduction gear train 30 with the torque limiter mechanism, the torque limiter mechanism can be operated quickly with respect to an abnormality.

(Arm reciprocation)
FIG. 6 is an explanatory view showing the reciprocating motion of the arm 42 by the link mechanism 40. 6A shows a state where the arm 42 has moved to the limit in the storage direction B, and FIG. 6B shows a state where the arm 42 has moved to the limit in the extending direction A.

  As shown in FIGS. 2 and 6, 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 has 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 by 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. The first drive source of the present invention is not necessarily a stepping motor, and other motors can be used as long as the motor can rotate in both forward and reverse directions. However, in that case, as described above, a position detecting means such as feedback control may be required separately.

  Also, ribs 511 (see FIG. 7) 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. 6) 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.

  By supporting each link member 41 with a linear rib, rattling of the link mechanism 40 in the width direction X is prevented, and sliding resistance with each link member 41 is reduced.

(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. 7 is an explanatory view showing the structure of the first swing restricting portion 60. 7A shows a state where the arm 42 has moved to the limit in the storage direction B, and FIG. 7B shows a state where the arm 42 has moved to the limit in the extending direction A. In addition, the 1st case half 51 of FIG. 7 is transparently displayed by the broken line.

  The first swing restricting portion 60 includes a protrusion 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. 6). 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. 6B shows the arm 42 moved in the extending direction A. The extension range of the arm 42 in FIG. 6B 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 above two types of swing restricting portions are provided, but only one of these swing restricting portions may be provided.

(Support unit)
FIG. 9 is an exploded perspective view showing the internal structure of the support unit 70. FIG. 10 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 and 10 '.

  The support unit 70 includes a case 71 including 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 protruding toward the second case half 712 along the width direction X is formed at the base end portion of the arm 72. The pin 751 is a cam follower that slides along a curved cam groove 752 provided in the second case half 712. The curved 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 embodiments)
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. 11 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. 11B 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 (biasing member) 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 the arm 42 is moved 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.

  Although the embodiments of the present invention have been described above, 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 20 according to another embodiment First motor (first drive source)
25 Second motor (second drive source)
251 Pinion gear 30 Reduction gear train 31 First reduction gear (gear member (overload protection mechanism))
40 link mechanism 41 link member 411 drive link 411c gear portion 412 driven link 42 arm (intermediate link)
50 Case (fixed part)
51 First case half 511 Rib 52 Second case half 522 Support shaft 53 Middle plate 531 Rib 60 First swing restricting portion 61 Projection portion 62 Contact portion 65 Second swing restricting portion 66 Bending portion 66a Opposing surface 67 Arm Side contact portion 67a Opposing surface 70 Support unit 91 Wind direction plate 95 Brake spring A Extension direction B Storage direction

Claims (14)

A first drive source which is a 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 link mechanism includes a plurality of link members and arm members that are supported by these link members and reciprocate 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,
The drive link has a distal end connected to the arm member and a proximal end connected to the first drive source directly or via another member,
The driven link has a distal end side connected to the arm member and a proximal end side connected to the fixed portion.
A louver device, wherein a wind direction plate, which is a plate-like member, 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 1, wherein the driven link is disposed closer to the extending direction than the drive link.   When the link mechanism swings to a predetermined position, the link mechanism or the fixed portion has a swing restricting portion that is a pair of locking portions that restrict the swingable range of the link mechanism by contacting each other. The louver device according to claim 1, wherein a louver device is provided. A first swing restricting portion that is the swing restricting portion including a protrusion formed on the drive link and a contact portion formed on the fixed portion;
The protrusion protrudes from the drive link toward the fixed portion along the axial direction of the indirect portion of the drive link,
The louver device according to claim 3, wherein the contact portion is disposed at a position where it comes into contact with the protrusion when the link mechanism swings to a predetermined position. A second swing restricting portion that is the swing restricting portion including the arm member and the driven link bent in a substantially L shape toward the inside of the link mechanism;
5. The follower link is bent at an angle that abuts against the opposing surface of the arm member when the arm member extends to a predetermined position in the extending direction. The louver device described in 1. The first drive source is a motor that can rotate in both forward and reverse directions,
A gear portion is formed on the base end side of the drive link,
The louver device according to any one of claims 1 to 5, wherein the gear portion is connected to the first drive source via a reduction gear train.   The louver device according to claim 6, wherein the first drive source is a stepping motor. The reduction gear train has an overload protection mechanism;
7. The gear member according to claim 6, wherein the overload protection mechanism is a gear member that suppresses the transmission torque by consuming the excess torque by idling when a torque exceeding a predetermined threshold is applied. 8. The louver device according to 7.   The louver device according to claim 8, wherein the gear member meshes with a pinion gear of the first drive source. A brake mechanism that brakes the arm member by an urging member;
The biasing member is connected to a part of the link mechanism and the fixed part, or to the driven link and the drive link,
When the arm member moves in the extending direction, the biasing member biases a part of the link mechanism or the driven link toward the storage direction by its elastic force. The louver device according to any one of claims 1 to 9, wherein the movement in the extending direction is braked.   The louver device according to claim 10, wherein the biasing member of the braking mechanism is a coil spring. The fixing portion has a linearly extending rib protruding toward the link mechanism along the axial direction of the indirect portion of each link member;
The louver device according to any one of claims 1 to 11, wherein each link member is positioned in the axial direction by slidably contacting the rib. A second drive source that is a drive source is disposed at a side end portion of the arm member in the extending direction,
The louver device according to any one of claims 1 to 12, wherein the wind direction plate is rotatable within a predetermined angle range by a driving force of the second driving source.   The louver device according to claim 13, wherein the second drive source is a stepping motor.

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