JP6345517B2 - Braking device, shielding device - Google Patents

Description

  The present invention relates to a shielding device that lowers a shielding material by its own weight, such as a horizontal blind, a raised curtain, and a pleated screen, and a braking device that can be used to maintain a descending speed of the shielding material below a certain level in this shielding device. .

  In the horizontal blind described in Patent Document 1, when the slat and the bottom rail are lowered by their own weight, a centrifugal governor is used to maintain the descent speed below a certain level. In this centrifugal governor, the governor weight is pressed against the governor drum by the centrifugal force generated by the rotation of the central shaft, thereby generating a frictional resistance between the governor weight and the governor drum so as to suppress the rotation of the central shaft to a certain speed or less. It is configured.

  In Patent Document 2, the rotational speed of the drive shaft is suppressed to a predetermined value or less using an oil damper.

Japanese Patent No. 3140295 JP 2001-112616 A

  In the centrifugal governor of Patent Document 1, since frictional resistance is always generated, generation of wear, operating noise, vibration, and the like is a problem. On the other hand, although the oil damper of patent document 2 is excellent in quietness and durability compared with the centrifugal governor, there is a problem that the shielding material may not be lowered because the minimum torque at the time of low rotation is large. There is.

  This invention is made | formed in view of such a situation, and provides the braking device excellent in durability, silence, and the descending property of a shielding material.

  According to the present invention, there is provided a braking device that applies a braking torque to the drive shaft, comprising a centrifugal governor and an oil damper, and the braking torque according to a decrease in the rotational speed of the drive shaft or an increase in the descending rotational speed. A braking device is provided that is configured to increase the contribution of the centrifugal governor to the.

  In the present invention, when the rotational speed of the drive shaft is high, the braking torque by the oil damper is mainly used, and the contribution ratio of the centrifugal governor to the braking torque increases as the rotational speed decreases. Since problems such as wear, operating noise, and vibration that occur when using a centrifugal governor are significant when the rotational speed of the drive shaft is high, the present invention suppresses problems such as wear, operating noise, and vibration. Durability and quietness can be improved. The oil damper has a problem that the minimum torque at low rotation is large. However, in the present invention, the contribution of the centrifugal governor to the braking torque is increased as the rotation speed decreases, so the centrifugal governor is mainly used at low rotation. Therefore, the descending property of the shielding material can be improved.

  Further, in the shielding device that lowers the shielding material by its own weight, the driving torque applied to the driving shaft decreases as the rotational speed of the driving shaft descends as the shielding material descends, so the rotational speed of the driving shaft also decreases. Therefore, in the case where the contribution ratio of the centrifugal governor is increased in accordance with the increase in the rotational speed of the drive shaft instead of increasing the contribution ratio of the centrifugal governor in accordance with the decrease in the rotational speed of the drive shaft, the durability, The quietness and the descending property of the shielding material can be improved. In this specification, “the descent speed of the drive shaft” means the number of rotations of the drive shaft that accompanies the drop in the weight of the shielding material.

Hereinafter, various embodiments of the present invention will be exemplified. The following embodiments can be combined with each other.
Preferably, the rotation of the drive shaft is transmitted to the input shaft of the centrifugal governor, and the output shaft of the centrifugal governor and the input shaft of the oil damper are configured to rotate integrally. Preferably, the centrifugal governor and the oil damper have an intersection of a graph of rotational speed of the input shaft-braking torque and an inclination of the graph of the centrifugal governor at the intersection is larger than an inclination of the graph of the oil damper. It is comprised so that it may become. Preferably, a rotation restricting portion is provided that stops the rotation of the output shaft of the centrifugal governor when the descent speed of the drive shaft reaches a predetermined value. According to another aspect of the present invention, there is provided a shielding device configured to lower the shielding material by its own weight by rotating the winding shaft by the weight of the shielding material, comprising the braking device described above. A shielding device is provided in which the drive shaft is rotated in accordance with the rotation of the winding shaft.

It is a front view of the pleat screen of a 1st embodiment of the present invention. It is a right view of the pleat screen of FIG. The braking device 36 of 1st Embodiment of this invention is shown, (a) is a perspective view from upper direction, (b) is a schematic sectional drawing. In (b), detailed internal structures of the centrifugal governor 25 and the oil damper 31 are omitted. The braking device 36 of 1st Embodiment of this invention is shown, (a) is a perspective view from right front, (b) is a disassembled perspective view of (a). The braking device 36 of 1st Embodiment of this invention is shown, (a) is a perspective view from the left front, (b) is a disassembled perspective view of (a). It is sectional drawing which shows the braking part 25c of the centrifugal governor 25 of the braking device 36 of 1st Embodiment of this invention. The oil damper 31 of the braking device 36 of 1st Embodiment of this invention is shown, (a) is a front view (main body case 31b is sectional drawing), (b) is AA sectional drawing in (a). It is a graph which shows the relationship between the rotational speed of an input shaft, and braking torque about the centrifugal governor 25 and the oil damper 31 of the braking device 36 of 1st Embodiment of this invention. 5 is a flow chart showing the relationship between the descent rotation speed of the drive shaft 12 and the drive torque applied to the drive shaft 12 of the pleated screen of the first embodiment of the present invention. It is sectional drawing which shows the structure of the braking device 36 of 2nd Embodiment of this invention. It is sectional drawing which shows the state after the moving member 35 moved to the arrow Y direction from the state of FIG.

  Hereinafter, embodiments of the present invention will be described. Various characteristic items shown in the following embodiments can be combined with each other. The invention is established independently for each feature.

<First Embodiment>
In the pleated screen according to the first embodiment of the present invention shown in FIGS. 1 to 2, the screen 4 is suspended and supported from the head box 1, and the bottom rail 5 is attached to the lower end of the screen 4. The screen 4 enables the fabric to be folded in a zigzag shape.

  Between the head box 1 and the bottom rail 5, a pitch holding cord 33 for holding the pitch of the folds of the screen 4 is provided. The pitch holding cord 33 is provided with a large number of annular holding portions 57 at equal intervals. After the holding portions 57 are inserted into the screen 4, the lifting cord 7 for raising and lowering the bottom rail 5 is held by the holding portion 57. The holding portion 57 is prevented from coming off from the screen 4 by being inserted into the screen 4, thereby enabling the pitch of the screen 4 to be held. The pitch holding cord 33 and the lifting / lowering cord 7 are arranged on opposite sides of the screen 4.

  A pitch holding cord holding member 56 that holds the pitch holding cord 33 and a lifting cord holding member 55 that holds the lifting cord 7 are attached to the bottom rail 5. The pitch holding cord 33 and the lifting / lowering cord 7 are attached to the bottom rail 5 by these holding members.

  The upper end of the lifting / lowering cord 7 is attached to a winding shaft 10 that is supported by the support member 8 so as to be relatively rotatable. The winding shaft 10 rotates together with the drive shaft 12. The screen 4 can be folded or stretched by raising or lowering the bottom rail 5 by winding or unwinding the lifting / lowering cord 7 on the winding shaft 10. At one end of the head box 1, an operation unit unit 23 including a ball chain 13, an operation pulley 11, and a transmission clutch 21 is provided. The ball chain 13 is hooked on the operation pulley 11, and the rotational force in the pulling direction of the bottom rail 5 (direction of arrow A in FIG. 1) applied to the operation pulley 11 by the ball chain 13 is transmitted via the transmission clutch 21. It is transmitted to the drive shaft 12. The transmission clutch 21 is configured to transmit the rotational force in the direction of arrow A in FIG. 1, but not to transmit the rotational force in the direction of arrow B in FIG.

  The drive shaft 12 is inserted through the stopper device 24 at the intermediate portion of the head box 1. When the ball chain 13 is released after the bottom rail 5 is lifted, the stopper device 24 stops the rotation of the drive shaft 12 and prevents the bottom rail 5 from dropping its own weight.

  As shown in FIG. 1, a braking device 36 is disposed at one end of the drive shaft 12. The braking device 36 suppresses the rotational speed of the drive shaft 12 to a predetermined value or less without stopping the rotation of the drive shaft 12, and suppresses the descending speed when the bottom rail 5 is lowered by its own weight.

  Here, the braking device 36 will be described in detail with reference to FIGS. The braking device 36 includes a centrifugal governor 25 and an oil damper 31. The centrifugal governor 25 includes an input shaft 25a into which the drive shaft 12 is inserted and rotated integrally with the drive shaft 12, and a main body case 25b. A braking portion 25c shown in FIG. 6 is provided in the main body case 25b. The braking portion 25c includes a drum 25d having a circular inner surface, a central shaft 25e supported so as to be rotatable relative to the drum 25d, and a sliding body 25f that rotates integrally with the central shaft 25e. The drum 25d is supported so as not to rotate relative to the main body case 25b. The rotation of the input shaft 25a is accelerated by a gear mechanism (not shown) and transmitted to the central shaft 25e. Since a gap 25g is provided between the sliding body 25f and the drum 25d, when the rotation of the center shaft 25e is slow, the braking torque applied to the center shaft 25e is very small. On the other hand, as the rotational speed of the central shaft 25e increases, the centrifugal force applied to the sliding body 25f increases, and the braking torque generated by rubbing the sliding body 25f against the inner surface of the drum 25d increases. Therefore, the magnitude of the braking torque generated by the centrifugal governor 25 increases as the rotational speed of the input shaft 25a increases as shown in FIG. In general, the magnitude of the braking torque when the rotational speed of the input shaft 25a is very small can be adjusted by changing the size of the gap 25g, and the inclination of the graph can be changed by changing the shape and material of the sliding body 25f. Can be adjusted by. In FIG. 8, the relationship between the rotation speed of the input shaft 25a and the braking torque is shown by a straight line. However, depending on the design of the centrifugal governor 25, this relationship may be expressed by a broken line or a curve.

  The centrifugal governor 25 only needs to generate a braking torque by a centrifugal force generated by the rotation of the input shaft, and its specific configuration is not limited. In the present embodiment, the sliding body 25f is configured to be pressed against the drum 25d by elastic deformation of the sliding body 25f when a centrifugal force is applied to the sliding body 25f. The sliding body 25f may be configured to be pressed against the drum 25d by the relative movement of the sliding body 25f radially outward when a centrifugal force is applied to 25f. In the present embodiment, the sliding body 25f is preferably made of rubber so that the sliding body 25f is easily elastically deformed. However, when the sliding body 25f does not need to be elastically deformed, the sliding body 25f is a resin. It can also be formed of metal.

  The main body case 25 b is an output shaft of the centrifugal governor 25. When the rotational speed of the input shaft 25a is small, the input shaft 25a rotates relative to the main body case 25b. When the rotational speed of the input shaft 25a is large, the main body case 25b rotates integrally with the input shaft 25a. Switching between relative rotation and integral rotation will be described in detail later.

  The main body case 25 b is connected to the input shaft 31 a of the oil damper 31 through the joints 27 and 29 so as not to be relatively rotatable. The specific configuration is as follows. The joint 27 includes a centrifugal governor body case housing portion 27a and a connecting recess 27b. The joint 29 includes a connecting convex portion 29a and an oil damper input shaft accommodating portion 29b. The main body case 25b is accommodated in the centrifugal governor main body case accommodating portion 27a so as not to be relatively rotatable, the connecting convex portion 29a is accommodated in the connecting recess 27b so as not to be relatively rotatable, and the input shaft 31a of the oil damper 31 is accommodated in the oil damper input shaft. The main body case 25 b is configured to rotate integrally with the input shaft 31 a of the oil damper 31 by being housed in the portion 29 b so as not to be relatively rotatable. In addition, you may comprise the joints 27 and 29 by one member.

  As shown in FIG. 7, the oil damper 31 includes a main body case 31b and a central shaft 31d inserted therein. The center shaft 31d is configured to rotate integrally with the input shaft 31a. The accommodation space 31f in the main body case 31b is filled with oil. A fin 31e is provided on the central shaft 31d. When the central shaft 31d rotates relative to the main body case 31b, the fin 31e receives a viscous resistance from the oil, thereby generating a braking torque that attenuates the relative rotational speed between the main body case 31b and the input shaft 31a. As shown in FIG. 8, the magnitude of the braking torque generated by the oil damper 31 increases as the rotational speed of the input shaft 31a increases. The intercept and inclination of the graph of FIG. 8 can be adjusted by changing the viscosity of the oil and the shape of the fin 31e. In FIG. 8, the relationship between the rotational speed of the input shaft 31 a and the braking torque is shown by a straight line. However, depending on the design of the oil damper 31, this relationship may be expressed by a broken line or a curve.

  The oil damper 31 only needs to generate a braking torque when a moving body that moves by rotation of the input shaft receives viscous resistance from the oil, and its specific configuration is not limited. In the present embodiment, the fin 31e is a moving body, and the fin 31e receives a viscous resistance from the oil due to the rotational movement of the fin 31e due to the rotation of the input shaft. In another embodiment, however, the rotation of the input shaft causes the rotation of the input shaft. The moving member that moves uniaxially by the screw feeding method may be a moving body, and the moving member may receive viscous resistance from oil when the moving member moves uniaxially by the screw feeding method.

  The oil damper 31 is accommodated in an oil damper accommodating portion 32 a of an oil damper support 32 that is supported by the head box 1 so as not to be relatively rotatable. By engaging the engaging convex portion 31c of the oil damper 31 with the engaging concave portion 32b provided in the oil damper accommodating portion 32a, the oil damper 31 is not rotatable relative to the oil damper support 32. .

  By the way, in this embodiment, the centrifugal governor 25 and the oil damper 31 intersect at a crossing point P, as shown in FIG. Since the gradient of the graph of the centrifugal governor 25 at the intersection P is larger than the gradient of the graph of the oil damper 31, the braking torque of the centrifugal governor 25 is in a region where the rotational speed of the input shaft is larger than the rotational speed Vp at the intersection P. Is larger than the braking torque of the oil damper 31 and the rotational speed of the input shaft is smaller than the rotational speed Vp at the intersection P, the braking torque of the centrifugal governor 25 is smaller than the braking torque of the oil damper 31.

  If the main body case 25b, which is the output shaft of the centrifugal governor 25, is supported so as not to rotate relative to the head box 1, the braking torque Tgh is generated by the centrifugal governor 25 when the drive shaft 12 rotates at the rotational speed Vh. Arise. However, in this embodiment, the main body case 25b of the centrifugal governor 25 is connected to the input shaft 31a of the oil damper 31 so as not to be relatively rotatable, and the braking torque Toh of the oil damper 31 at the rotational speed Vh is greater than the braking torque Tgh. Therefore, when the drive shaft 12 rotates at the rotational speed Vh, the main body case 25b is rotated integrally with the drive shaft 12, whereby the rotation of the drive shaft 12 is transmitted to the input shaft 31a of the oil damper 31. Thus, at the rotational speed Vh, the rotational speed of the drive shaft 12 is controlled mainly by the braking torque generated by the oil damper 31. At this time, since the relative rotational speed between the sliding body 25f and the drum 25d is 0 or a very small value, generation of wear, operating noise, vibration, and the like due to the relative rotation of the sliding body 25f with respect to the drum 25d is suppressed. Is done.

  On the other hand, at a rotational speed Vl smaller than the rotational speed Vp, the braking torque Tol of the oil damper 31 is larger than the braking torque Tgl of the centrifugal governor 25 as shown in FIG. For this reason, when the drive shaft 12 rotates at the rotation speed Vl, the main body case 25b of the centrifugal governor 25 does not substantially rotate, and the drive shaft 12 rotates mainly by the braking torque generated by the centrifugal governor 25. Is controlled. At this time, since the braking torque applied to the drive shaft 12 is very small, the descending property of the shielding material is improved.

  As described above, in the present embodiment, by adopting a configuration in which the output shaft of the centrifugal governor 25 and the input shaft of the oil damper 31 are integrally rotated, the rotational speed of the drive shaft 12 is reduced, and the rotational speed Vp or the vicinity thereof. The mechanism that mainly generates the braking torque switches from the oil damper 31 to the centrifugal governor 25 naturally and smoothly. That is, as the rotational speed of the drive shaft 12 decreases, the contribution ratio of the centrifugal governor 25 to the braking torque increases. With such a configuration, it is possible to obtain the braking device 36 that is excellent in durability, quietness, and descendability of the shielding material.

  Here, the operation of the pleated screen will be described. When the interior portion of the ball chain 13 is pulled in the direction of arrow A in FIG. 2, the rotational force generated by the force is transmitted to the transmission clutch 21 via the operation pulley 11. Since the transmission clutch 21 is configured to transmit only the rotational force in the direction of arrow A in FIG. 1 to the drive shaft 12, the rotational force generated by pulling the ball chain 13 in the direction of arrow A in FIG. Is transmitted to the drive shaft 12, and the drive shaft 12 is rotated. By the rotation of the drive shaft 12, the winding shaft 10 supported in the head box 1 so as to be relatively rotatable with respect to the support member 8 rotates in the direction of arrow A in FIG. The bottom rail 5 attached to the tip of the lifting / lowering cord 7 rises.

  If the hand is released from the ball chain 13 in this state, the stopper device 24 is activated to prevent the bottom rail 5 from dropping its own weight. In this state, when the ball chain 13 is pulled again in the direction of arrow A in FIG. 2 and then released, the operation for preventing the weight of the stopper device 24 from dropping is released, and the lifting / lowering cord 7 is rewound from the winding shaft 10. The bottom rail 5 falls by its own weight. At this time, the drive shaft 12 rotates integrally with the winding shaft 10.

  By the way, the relationship between the descent speed of the drive shaft 12 and the drive torque applied to the drive shaft 12 due to the weight of the screen 4 and the bottom rail 5 is as shown in the graph of FIG. The driving torque applied to the driving shaft 12 gradually decreases as the descending rotational speed of the driving shaft 12 increases. For this reason, the rotational speed of the drive shaft 12 exceeds the rotational speed Vp immediately after the start of lowering the dead weight of the bottom rail 5, the drive shaft 12 and the body case 25 b rotate integrally, and the drive shaft 12 is mainly composed of the oil damper 31. The rotational speed is controlled by the braking torque generated by.

  As the bottom rail 5 descends and the descent speed of the drive shaft 12 increases, the drive torque applied to the drive shaft 12 decreases, and as a result, the rotational speed of the drive shaft 12 gradually decreases. When the rotational speed of the drive shaft 12 falls below the rotational speed Vp, the rotation of the main body case 25b is substantially stopped, and the rotational speed of the drive shaft 12 is controlled mainly by the braking torque generated by the centrifugal governor 25. Will come to be. Since the centrifugal governor 25 has a small braking torque at the time of low speed rotation, the occurrence of the problem that the bottom rail 5 does not drop by itself to the lower limit position is suppressed.

The present invention can also be implemented in the following modes.
In the centrifugal governor 25 and the oil damper 31, the input shaft and the output shaft can be configured differently from the above embodiment. For example, the main body case 25b of the centrifugal governor 25 is supported so as not to rotate relative to the head box 1, the drum 25d is supported so as to be rotatable relative to the main body case 25b, and rotation of the drum 25d is provided on an output shaft provided separately. Can be transmitted. Further, in the oil damper 31, for example, the rotation of the output shaft of the centrifugal governor 25 is transmitted to the main body case 31b, the fin 31e is fixed to the main body case 31b, and the central shaft 31d is supported by the head box 1 so as not to be relatively rotatable. Can do. In this case, the main body case 31 b serves as the input shaft of the oil damper 31.
In addition to the pleated screen, the braking device 36 of the above embodiment can be applied to a shielding device having a reverse characteristic that lowers the weight of the shielding material (for example, a horizontal blind or a lifting curtain).

Second Embodiment
A second embodiment of the present invention will be described with reference to FIGS. This embodiment is similar to the first embodiment, and the configuration of the braking device 36 is different. In the first embodiment, the contribution ratio of the centrifugal governor 25 to the braking torque increases as the rotational speed of the drive shaft 12 decreases. However, in this embodiment, the rotational speed of the drive shaft 12 decreases. It is comprised so that the contribution ratio of the centrifugal governor 25 with respect to braking torque may increase with an increase. Hereinafter, the difference will be mainly described.

  In the present embodiment, the braking device 36 includes a centrifugal governor 25 and an oil damper 31, as shown in FIG. The configurations of the centrifugal governor 25 and the oil damper 31 are the same as those in the first embodiment. The braking device 36 includes a joint 28 and a moving member 35 instead of the joints 27 and 29. The joint 28 includes a centrifugal governor body case housing portion 28a for housing the body case 25b, a locking portion 28b, a screw shaft 28c, and an oil damper input shaft housing portion 28d. The main body case 25b is accommodated in the centrifugal governor main body case accommodating portion 28a so as not to be relatively rotatable, and the input shaft 31a of the oil damper 31 is accommodated in the oil damper input shaft accommodating portion 28d so as not to be relatively rotatable. The oil damper 31 is configured to rotate integrally with the input shaft 31 a of the oil damper 31.

  The moving member 35 has a female screw hole 35a, and the female screw hole 35a is screwed to the screw shaft 28c. The moving member 35 is configured to be relatively unrotatable with respect to the head box 1, and is configured to be capable of uniaxial movement along the screw shaft 28c without rotating as the screw shaft 28c rotates. The moving member 35 includes a locking portion 35b on a surface facing the locking portion 28b, at a position overlapping the rotation locus of the locking portion 28b when viewed from the direction in which the screw shaft 28c extends (arrow X direction).

Here, the operation of the braking device 36 of the present embodiment will be described.
When the weight of the bottom rail 5 is lowered from the upper limit position, the rotational speed of the drive shaft 12 exceeds the rotational speed Vp immediately after the start of the weight drop, and the drive shaft 12 and the main body case 25b rotate integrally. Further, the rotation speed is controlled by the braking torque generated by the oil damper 31. Further, the joint member 28 and the screw shaft 28c rotate with the rotation of the main body case 25b, whereby the moving member 35 moves in the arrow Y direction.

  As the bottom rail 5 descends and the descent speed of the drive shaft 12 increases, the moving member 35 further moves in the direction of arrow Y, and when the descent speed of the drive shaft 12 reaches a predetermined value, FIG. As shown, the locking portion 35b contacts the locking portion 28b and stops the rotation of the joint 28. As a result, the rotation of the main body case 25 b stops, and thereafter, the rotational speed of the drive shaft 12 is controlled by the braking torque generated by the centrifugal governor 25. A mechanism for stopping the rotation of the output shaft of the centrifugal governor 25 when the descending rotational speed of the drive shaft 12 reaches a predetermined value is the “rotation restricting portion” in the claims, and the configuration thereof is shown here. It is not limited to.

  As described above, in the present embodiment, the rotation of the main body case 25b is surely stopped when the descent rotational speed of the drive shaft 12 reaches a predetermined value, so that the drive is performed when the bottom rail 5 is lowered to a predetermined position. The mechanism that mainly generates the braking torque for the shaft 12 can be reliably switched from the oil damper 31 to the centrifugal governor 25.

1: head box 4: screen 5: bottom rail 7: lifting cord 8: support member 10: winding shaft 11: operation pulley 12: drive shaft 13: ball chain 21: transmission clutch 24: stopper device 25: centrifugal governor 27, 28, 29: Joint 31: Oil damper 32: Oil damper support 33: Pitch holding cord 36: Braking device

Claims (5)

A braking device for applying a braking torque to a drive shaft, comprising a centrifugal governor and an oil damper, wherein the centrifugal governor contributes to the braking torque as the rotational speed of the drive shaft decreases or the rotational speed decreases. A braking device configured to increase in proportion. The braking device according to claim 1, wherein rotation of the drive shaft is transmitted to an input shaft of the centrifugal governor, and an output shaft of the centrifugal governor and an input shaft of the oil damper are integrally rotated. The centrifugal governor and the oil damper have an intersection of a graph of rotational speed of the input shaft-braking torque and an inclination of the graph of the centrifugal governor at the intersection is larger than an inclination of the graph of the oil damper. The braking device according to claim 2 configured. 4. The braking device according to claim 2, further comprising a rotation restricting portion that stops rotation of the output shaft of the centrifugal governor when the descent rotational speed of the drive shaft reaches a predetermined value. 5. A shielding apparatus configured to lower the weight of the shielding material by rotating the winding shaft by the weight of the shielding material;
A braking device according to any one of claims 1 to 4, comprising:
The said drive shaft is a shielding apparatus rotated with rotation of the said winding shaft.