WO2016009881A1 - Shielding device - Google Patents

Abstract

[Problem] To provide a shielding device provided with a speed adjustment unit which is capable of automatically adjusting the movement speed of a shielding material using a simple configuration, and with which noise during operation is suppressed. [Solution] According to the present invention, provided is a shielding device in which a shielding material is opened and closed by rotating a winding shaft. The shielding device is provided with a speed adjustment unit for automatically adjusting the movement speed of the shielding material. The speed adjustment unit is provided with: a housing for accommodating a viscous fluid; and a moving member which is accommodated inside the housing, and which moves in accordance with the rotation of the winding shaft. Furthermore, the speed adjustment unit is configured such that the resistance force that the moving member receives from the viscous fluid changes in accordance with the movement of the moving member.

Description

Shielding device

This invention is semi-automatic operation due to the gravity and biasing force of the shielding material by rotating the winding shaft in the rolling screen, horizontal blind, scooping curtain, pleated screen, vertical blind, panel curtain, curtain rail and horizontal pulling shielding device The present invention relates to a shielding device that opens and closes a shielding material that performs the above.

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

On the other hand, in the roll screen described in Patent Document 2, when the screen is lifted by winding the screen around the winding shaft by the urging force of the torsion coil spring, the weight bar attached to the lower end of the screen collides with the mounting frame. Therefore, a damper device is used to suppress the generation of noise. The damper device includes a rotary damper, a planetary gear mechanism, and a rotor. The rotor device is engaged with the planetary gear mechanism only when the weight bar is pulled up to the vicinity of the upper limit. By raising the relative rotational speed between the input shafts and increasing the braking force by the rotary damper, the screen lifting speed is kept below a certain speed.

Japanese Patent No. 3140295 JP 2000-27570 A

The governor device of Patent Document 1 has a problem that noise is generated by friction between the governor weight and the governor drum. The damper device of Patent Document 2 has a problem that a complicated mechanism is required to change the braking force when the weight bar is pulled up to the vicinity of the upper limit.

The present invention has been made in view of such circumstances, and provides a shielding device having a speed adjustment unit capable of adjusting the automatic movement speed of the shielding material with a simple configuration and suppressing noise during operation. To do.

According to the present invention, there is provided a shielding device that opens and closes a shielding material by rotation of a winding shaft, and includes a speed adjusting unit that adjusts an automatic moving speed of the shielding material, and the speed adjusting unit contains a viscous fluid. A housing, and a moving member that is accommodated in the housing and moves as the winding shaft rotates, and the resistance force that the moving member receives from the viscous fluid changes as the moving member moves. A shielding device configured as described above is provided.

In the present invention, the moving member that moves in accordance with the rotation of the winding shaft is disposed in the housing that accommodates the viscous fluid, and the resistance force that the moving member receives from the viscous fluid changes as the moving member moves. Configured. According to such a configuration, the braking force by the speed adjusting unit can be easily changed by a method such as changing the flow resistance of the viscous fluid. Further, since the braking force is generated using the resistance received from the viscous fluid when the moving member moves, the generation of noise is suppressed.

Hereinafter, various embodiments of the present invention will be exemplified. The following embodiments can be combined with each other.
Preferably, the speed adjusting unit is configured such that the moving member is capable of reciprocating relative movement within a certain range in conjunction with the opening / closing range of the shielding material in the housing, and the moving member receives from the viscous fluid. The resistance force is configured to change depending on the position within the certain range.
Preferably, the speed adjusting unit is configured such that the lowest position of the driving torque in the opening / closing range of the shielding material is the lowest position of the resistance force within the certain range.
Preferably, the speed adjusting unit is configured such that the maximum position of the driving torque in the opening / closing range of the shielding material is the maximum position of the resistance force within the certain range.
Preferably, the speed adjusting unit may change a cross-sectional area of the flow path through which the viscous fluid can pass through the moving member as the moving member moves, bypass the larger flow path, or It is comprised so that the at least 1 elastic modulus of the member which comprises a flow path may change.
Preferably, the speed adjusting unit has a flow resistance of the viscous fluid in a second direction opposite to the first direction when the moving member moves in the first direction when the shielding member is automatically moved. It is comprised so that it may become larger than the distribution | circulation resistance of the said viscous fluid at the time of a movement.
Preferably, the speed adjusting unit is configured such that a moving distance of the moving member per unit rotation of the winding shaft changes with the movement of the moving member.
Preferably, the speed adjusting unit includes a linked state in which the rotation of the winding shaft and the movement of the moving member are linked, and an unlinked state in which the rotation of the winding shaft and the movement of the moving member are not linked. Are configured to be switchable.
Preferably, a brake force increasing means for increasing a brake force applied to the winding shaft in a brake force increasing range that is a part of a movable range of the moving member is provided in the housing.
Preferably, the brake force increasing means is configured to form a piston structure with the moving member when the moving member is in the brake force increasing range.
Preferably, the brake force increasing means is a rotation resistor that increases the brake force by rotating with the rotation of the winding shaft when the moving member is within the brake force increasing range.
Preferably, the moving member is configured to move while rotating with the rotation of the winding shaft, and the rotation resistor is configured to move the moving member when the moving member is within the brake force increasing range. And is configured to rotate together with the moving member.
Preferably, the movable member includes a first resistance portion and a second resistance portion that generate a resistance force that the moving member receives from the viscous fluid in conjunction with an opening / closing range of the shielding material, and the first resistance portion and the second resistance portion At least one of them is configured to change the resistance force received from the viscous fluid within the open / close range of the shielding material.
Preferably, the speed adjusting unit includes an internal pressure limiter that operates when a torque applied to the winding shaft exceeds a predetermined threshold value or an internal pressure of the housing exceeds a predetermined threshold value to reduce the internal pressure of the housing. .
Preferably, the speed adjustment unit includes a non-moving region where the moving member does not move even when the winding shaft rotates in the descending direction of the shielding material, and the moving member is in the non-moving region. When the winding shaft rotates in the upward direction of the shielding member, the moving member moves with the rotation of the winding shaft.
Preferably, the shielding device rewinds the lifting / lowering cord having one end attached to the shielding material from the winding shaft by rotating the winding shaft by its own weight. The material is configured to automatically descend, and the speed adjusting unit is configured to decrease the resistance as the shielding material descends.
Preferably, thrust imparting means for imparting thrust to the moving member by rotating and moving together with the moving member as the winding shaft rotates is provided in the housing.
Preferably, the shielding device is configured to automatically raise the shielding material by rotating the winding shaft by the urging force of the urging device and winding the shielding material on the winding shaft, and the speed The adjustment unit is configured to increase the resistance when the shielding material is raised to the vicinity of the upper limit position.

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 speed adjustment part 36 of 1st Embodiment of this invention is shown, (a) is the time of the descent | fall start of the bottom rail 5, (b) shows the state just before completion of the descent of the bottom rail 5. FIG. (C) to (e) show examples of the cross-sectional structure perpendicular to the axis of the speed adjusting unit 36. (A) is a graph which shows the relationship between the height position of the bottom rail 5 of a pleat screen, and the load added to the raising / lowering cord 7, (b) is the height position of the bottom rail 5 of a pleat screen, and speed adjustment. FIG. 7C is a graph showing the relationship between the braking force by the portion 36 and (c), the number of rotations of the central shaft 38 from the state in which the gap 41 between the housing 37 and the moving member 39 is minimum, and the braking force by the speed adjusting portion 36. It is a graph which shows the relationship. The speed adjustment part 36 of 2nd Embodiment of this invention is shown, (a) shows the state at the time of the raising operation of the bottom rail 5, (b) shows the time of the bottom rail 5's own weight fall. FIG. 4 shows a speed adjustment unit 36 according to a third embodiment of the present invention, in which (a) is a cross-sectional view, and (b) to (d) are development views of an inner surface 37a of a housing 37 of structural examples 1 to 3. It is a perspective view which shows the speed adjustment part 36 of 4th Embodiment of this invention. The speed adjustment part 36 of 5th Embodiment of this invention is shown, (a) is a front view (the housing 37 is sectional drawing), (b) is a development view of the inner surface 37a of the housing 37, (c) is the moving member 39. Front view, (d) is a left side view of moving member 39, (e) to (g) are cross-sectional views taken along line AA in (c), showing the state of movable plate 39b at positions R, Q, and P. It is. (H) is a graph showing the relationship between the rotational speed and the braking force. The speed adjustment part 36 of 6th Embodiment of this invention is shown, (a) is a front view (the housing 37 is sectional drawing), (b) is a front view of the moving member 39, (c) is the left side surface of the moving member 39. FIGS. 4D to 4E are cross-sectional views taken along line AA in FIG. 2B, showing the state of the movable projecting member 39k at positions Q and P. FIG. The speed adjustment part 36 of 7th Embodiment of this invention is shown, (a) is a front view (the housing 37 is sectional drawing), (b) is a left view of the moving member 39. FIG. The speed adjustment part 36 of 8th Embodiment of this invention is shown, (a) is a front view (the housing 37 is sectional drawing), (b)-(e) is AA sectional drawing, BB sectional drawing, respectively, CC sectional view, DD sectional view, (f) is a sectional view corresponding to (a), showing a state in which the moving member 39 has moved to positions S, T, U. It is a perspective view which shows the speed adjustment part 36 of 9th Embodiment of this invention. The moving member 39 and the center axis | shaft 38 of the speed adjustment part 36 of 10th Embodiment of this invention are shown, (a) is a perspective view, (b) is sectional drawing. The speed adjustment part 36 of 11th Embodiment of this invention is shown, (a) is an expanded view of the inner surface 37a of the housing 37, (b) is a graph which shows the relationship between rotation speed and brake force. The speed adjustment part 36 of 12th Embodiment of this invention is shown, (a) is a front view (housing 37 is sectional drawing), (b) is AA sectional drawing. The speed adjustment part 36 of 13th Embodiment of this invention is shown, (a) is a front view (the housing 37 is sectional drawing), (b)-(g) is AA sectional drawing, BB sectional drawing, respectively, They are CC sectional view, DD sectional view, EE sectional view, and FF sectional view. In the speed adjustment part 36 of 13th Embodiment of this invention, it is a front view (housing 37 is sectional drawing) which shows the state after the moving member 39 moved with the fall of the bottom rail 5. FIG. The speed adjusting part 36 of the fourteenth embodiment of the present invention is shown, (a) is a front view (housing 37 is a sectional view), (b) to (e) are AA sectional views, BB sectional views, FIG. 6 is a cross-sectional view taken along line EE and a cross-sectional view taken along line FF. The speed adjustment part 36 of 14th Embodiment of this invention is shown, (a) is a front view (housing 37 is sectional drawing) which shows the state after the moving member 39 moved, (b) is rotation speed and brake force. It is a graph which shows the relationship. The speed adjustment part 36 of the modification 1 of 14th Embodiment of this invention is shown. The speed adjustment part 36 of the modification 2 of 14th Embodiment of this invention is shown. The speed adjustment part 36 of the modification 3 of 14th Embodiment of this invention is shown. The speed adjustment part 36 of 15th Embodiment of this invention is shown, (a) is a front view (the housing 37 is sectional drawing), (b)-(d) is AA sectional drawing, BB sectional drawing, respectively, It is CC sectional drawing. In the speed adjustment part 36 of 15th Embodiment of this invention, it is a front view (housing 37 is sectional drawing) which shows the state after the moving member 39 moved. The speed adjustment part 36 of the modification 1 of 15th Embodiment of this invention is shown. The speed adjustment part 36 of 16th Embodiment of this invention is shown, (a) is a front view (the housing 37 is sectional drawing), (b)-(d) is AA sectional drawing, BB sectional drawing, respectively, It is CC sectional drawing. In the speed adjustment part 36 of 16th Embodiment of this invention, it is a front view (housing 37 is sectional drawing) which shows the state after the moving member 39 moved. The speed adjustment part 36 of the modification 1 of 16th Embodiment of this invention is shown. The speed adjustment part 36 of 17th Embodiment of this invention is shown, (a) is a front view (housing 37 is sectional drawing), (b) is AA sectional drawing, (c) is BB sectional drawing (housing) 37 is omitted) (d) is an exploded perspective view of the moving member 39. FIG. (A)-(b) is a front view (a housing 37 is a sectional view) of a speed adjusting unit 36 according to an eighteenth embodiment of the present invention, (a) is before the operation of the internal pressure limiter, and (b) is an internal pressure limiter. The state after the operation is shown. It is a front view (housing 37 is sectional drawing) which shows the speed adjustment part 36 of 19th Embodiment of this invention. It is a schematic front view which shows the method of incorporating the speed adjustment part 36 of 19th Embodiment of this invention in the head box 1, (a) is the state which has the bottom rail 5 in an upper limit position, (b) The state in the lower limit position is shown. It is a schematic front view which shows the method of incorporating the speed adjustment part 36 of 19th Embodiment of this invention in the head box 1, and shows the state which raised the bottom rail 5 to the middle. It is a front view of the roll screen of 20th Embodiment of this invention. It is sectional drawing which shows the urging | biasing apparatus 80 of the winding shaft 63 of the roll screen of FIG. It is sectional drawing which shows the speed adjustment part 36 and the clutch apparatus 70 of the roll screen of FIG. (A) is a graph which shows the relationship between the height position of the weight bar 64a of a roll screen, and the torque added to a winding shaft, (b) is the height position of the weight bar 64a of a roll screen, and speed adjustment. 4 is a graph showing a relationship of braking force by a part 36. The speed adjustment part 36 of 20th Embodiment of this invention is shown, (a) is a state at the time of the start of raising of the weight bar 64a, (b) shows the state immediately before completion of raising of the weight bar 64a. The inner surface 37a of the housing 37 of the speed adjustment part 36 of 21st Embodiment of this invention is shown. (A)-(b) is a graph which shows the relationship of the torque and brake force which are added to a winding shaft with respect to the winding shaft rotation speed in a horizontal blind, respectively. (A)-(b) is a graph which shows the relationship of the torque and braking force which are added to a winding shaft with respect to the winding shaft rotation speed in a roman shade, respectively. (A) to (b) are graphs showing the relationship between the torque applied to the winding shaft and the braking force with respect to the number of rotations of the winding shaft on the roll screen, and (c) is the braking force shown in (b). It is sectional drawing which shows the speed adjustment part 36 which has a characteristic. (A) to (b) are graphs showing the relationship between the torque applied to the take-up shaft and the braking force with respect to the take-up shaft rotation speed in the shield device having a structure that automatically raises the shield device with the reverse characteristics, (C) is sectional drawing which shows the speed adjustment part 36 which has the braking force characteristic shown to (b).

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 and 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.

The bottom rail 5 is attached with 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. 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 the winding shaft 10. 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 rewinding the lifting / lowering cord around 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 speed adjustment unit 36 is disposed on the side of the stopper device 24. The speed adjustment unit 36 suppresses the rotation speed of the drive shaft 12 to be equal to or lower than a predetermined value without stopping the rotation of the drive shaft 12, and suppresses the lowering speed when the bottom rail 5 is lowered by its own weight.

Here, the speed adjustment unit 36 will be described in detail. As shown in FIG. 3, the speed adjustment unit 36 includes a housing 37, a central shaft 38 inserted into the housing 37, and a moving member 39 accommodated in the housing 37. The central shaft 38 is connected to the drive shaft 12 so as not to rotate. Note that the drive shaft 12 itself may be inserted into the housing 37 through the central shaft 38. If the cross section of the central shaft 38 is rectangular and the penetrating portion of the drive shaft 12 has the same rectangular cross section, the shafts 38 can be connected so as not to rotate. The housing 37 is fixed to the head box 1 so as not to rotate directly or indirectly.

A gap 41 is provided between the inner surface 37 a of the housing 37 and the moving member 39. The accommodation space 40 in the housing 37 is filled with oil. At least a part of the center shaft 38 in the housing 37 is a screw shaft, and the screw shaft is immersed in oil. The moving member 39 is screwed to the central shaft 38 and is engaged with the housing 37 so that relative sliding movement is possible and relative rotation is impossible. Specifically, as shown in FIG. 3C, an example in which the inner circumference of the inner surface 37 a is a circle and the outer circumference of the cross section of the moving member 39 is a circle with a gap 41 from the inner surface 37 a. Then, the convex portion 39v or the concave portion provided in the moving member 39 is engaged with the groove 37c or the convex strip provided on the inner surface of the housing 37 along the longitudinal direction of the central shaft 38. In this example, it is sufficient that the moving member 39 and the housing 37 are relatively movable in the axial direction and not relatively rotatable. As shown in FIGS. 3D to 3E, the moving member 39 and the housing 37 are square. -If it is an ellipse, a convex part or a recessed part is unnecessary, and in short, what is necessary is just to have a contact with a different distance from the center point. With such a configuration, the moving member 39 slides with the rotation of the central shaft 38. Specifically, the moving member 39 moves in the arrow X direction by the rotation in the arrow B direction in FIG. When the moving member 39 moves, the oil in the accommodation space 40 moves from the front (traveling direction) side of the moving member 39 to the rear side through the gap 41. The resistance received by the oil at this time is the oil flow resistance. The narrower the gap 41 and the higher the viscosity of the oil, the greater the oil flow resistance. As the oil flow resistance increases, the resistance force that the moving member 39 receives from the oil increases, and accordingly, the braking force applied to the central shaft 38 increases. Therefore, when the inner surface 37a is tapered, as shown in FIG. 4C, the braking force decreases with an increase in the rotational speed of the central shaft from the minimum gap portion. Further, the brake force applied to the central shaft 38 by the speed adjusting unit 36 can be easily adjusted by appropriately changing the size of the gap 41 and the viscosity of the oil.

By the way, when the screen 4 is folded, almost the entire weight of the screen 4 and the bottom rail 5 is supported by the lifting / lowering cord 7, so that the load applied to the lifting / lowering cord 7 is large. Since the screen 4 is suspended and supported by the head box 1, the load applied to the elevating cord 7 decreases as the bottom rail 5 descends and the screen 4 is expanded. From the upper limit, the height position of the bottom rail 5 decreases in proportion to the increase in the rotational speed of the shaft. That is, the relationship between the height position of the bottom rail 5 and the load applied to the lifting / lowering cord 7 is as shown in FIG. Since the bottom rail 5 tends to descend at a higher speed as the load applied to the lifting / lowering cord 7 is larger, a speed adjusting unit prevents the lowering speed of the bottom rail 5 from excessively increasing when the bottom rail 5 is lowered from a higher position. As shown in FIG. 4B, 36 is configured such that the braking force increases as the bottom rail 5 is at a higher position. That is, in the shielding device, the braking force changes so that the braking force is maximized when the bottom rail 5 is at the upper limit position and the braking force is minimized when the bottom rail 5 is at the lower limit position. In order to realize such characteristics, the inner surface 37a of the housing 37 of the speed adjusting portion 36 is tapered as shown in FIGS. 3A and 3B, and the moving member 39 moves in the direction of the arrow X. As the gap 41 gradually increases, the oil flow resistance gradually decreases. With such a configuration, the height position of the bottom rail 5 and the braking force by the speed adjusting unit 36 have the relationship shown in FIG. 4B, and the lowering speed of the bottom rail 5 can be prevented from becoming excessively large. Further, immediately before the bottom rail 5 is lowered, the braking force by the speed adjusting unit 36 can be made extremely small, so that the problem that the bottom rail 5 does not drop to the lower limit position can be prevented, and the bottom rail 5 The lifting / lowering cord can be rewound to the lowest limit without stopping just before completion of the descent. This is defined by the wide clearance 41 and the viscosity of the allowable minimum brake force that can rewind the lifting and lowering cord without stopping the bottom rail 5 to the lowest limit while receiving the sliding resistance of all rotating parts, Under such conditions, it can be realized by defining a narrow gap 41 at a high position near the upper limit of the blind height so that the descending speed of the blind is equal to or lower than a predetermined speed. By adopting such a blind configuration, the bottom rail 5 stops immediately before completion of the descent by properly defining the oil viscosity and the gap 41 even with shielding materials of any weight and specific gravity and shielding materials of any width / height ratio. It can be lowered to the lowest limit without any problem. The inclination direction of the graph of FIG. 4B needs to be the same as that of the graph of FIG. 4A, but the inclination angle of the graph of FIG. Even if the brake force is within an allowable range in which the lifting / lowering cord can be rewound without stopping the bottom rail from the lowering start position to the lowest limit while receiving the sliding resistance of all the rotating parts, FIG. It may be the same as or different from the graph of 4 (a). Further, the relationship between the height position of the bottom rail 5 and the braking force by the speed adjusting unit 36 may not be a linear relationship as shown in FIG. 4B, but may be a relationship represented by a curve or a broken line. . The relationship between the height position and the braking force can be easily changed by changing the inner surface shape of the housing 37.

Here, the operation of this pleated screen is explained. 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. As the drive shaft 12 rotates, the take-up shaft 10 rotatably supported by the support member 8 in the head box 1 rotates in the direction of arrow A in FIG. The bottom rail 5 attached to the tip of the cord 7 is raised.

When 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. In this embodiment, the weight drop corresponds to “automatic movement” in the claims.

When the bottom rail 5 starts to descend, the moving member 39 is located at the position shown in FIG. For this reason, the braking force by the speed adjustment part 36 is large, and the descent speed of the bottom rail 5 does not become excessively large.

As the bottom rail 5 descends, the moving member 39 moves in the direction of the arrow X in FIG. 3A, so that the gap 41 gradually increases. As a result, the oil flow resistance and the braking force by the speed adjusting unit 36 are increased. Gradually decreases. And immediately before completion of the lowering of the bottom rail 5, the speed adjustment part 36 will be in the state shown in FIG.3 (b).

From the state shown in FIG. 3B, by pulling the ball chain 13 again in the direction of arrow A in FIG. 2, the bottom rail 5 is raised and the moving member 39 is moved in the direction of arrow Y in FIG. Can be made. When the bottom rail 5 reaches the upper limit position, the moving member 39 moves to the position shown in FIG.

Here, an example has been described in which the moving member 39 moves from the substantially left end to the substantially right end of the housing space 40 of the housing 37, but the moving member 39 is substantially the left end or the substantially right end of the housing space 40. It is not necessary to reach. When the common speed adjustment unit 36 is used for a plurality of types of pleated screens having different lengths of the lifting / lowering cord 7, the position of the moving member 39 when the bottom rail 5 is at the lower limit position is aligned. It is preferable to do. This is because it is important to appropriately define the braking force immediately before the bottom rail 5 is lowered.

The present invention can also be implemented in the following embodiments.
-In addition to the pleated screen, the present invention can be applied to a solar shading device having a reverse characteristic that lowers the solar shading material by its own weight (eg, a horizontal blind, a raising curtain). The solar radiation shielding device having the reverse characteristic is window covering in which the torque applied to the winding shaft decreases as it is rewound. Further, the torque applied to the take-up shaft by the weight of the shielding material becomes the drive torque for driving the take-up shaft to rotate. In the case of a horizontal blind, the torque applied to the take-up shaft decreases each time the slats stacked on the bottom rail ride on the ladder cord one by one during the weight drop. Therefore, the relationship between the rotation speed of the winding shaft and the torque applied to the winding shaft by the weight of the shielding material is as shown in the graph of FIG. The lower clearance slats ride on the ladder cords and the bottom rails between the lowermost slats and the warp cords between the lowermost slats extend until the lifting cords can be rewound without stopping until the lifting cords are rewound. In this condition, a narrow gap 41 is defined at a high position near the upper limit of the blind height so that the blind descending speed is less than or equal to a predetermined speed, and as shown in FIG. The inner surface of the housing 37 may be tapered so that the graph of the number has a slope that approximates the slope of the torque-rotation speed of the winding shaft.

・ In the case of a roman shade, the torque applied to the take-up shaft decreases each time the rings (folds) stacked on the cord catch are separated one by one during the weight drop. Therefore, the relationship between the rotational speed of the winding shaft and the torque applied to the winding shaft by the weight of the shielding material is as shown in the graph in FIG. Then, as shown in FIG. 41 (b), the inner surface of the housing 37 is tapered so that the brake force-winding shaft rotational speed graph has an inclination that approximates the inclination of torque-winding shaft rotational speed. What is necessary is the same as that of the horizontal blind.

-For the horizontal blind, the lowest limit means that the lifting / lowering cord is unwound and descends, the tension of the lifting / lowering cord decreases rapidly, and the warp thread of the ladder cord supports the bottom rail (the ladder between the bottom rail and the lowermost slat). In the state where the warp of the cord is stretched), in the case of a roman shade, the lifting cord is rewound and lowered and the head box supports the entire load of the screen. In the case of a pleated screen, the lifting cord is rewound and lowered and lowered. A state in which the entire load is supported directly by the headbox or directly supported by the pitch cord or supported by the headbox, or before reaching each of the above states, the lifting / lowering cord is unwound by a lower limit device etc. It is the limit that cannot be lowered any further. If the lower limit device is a device that locks by detecting the mechanical slack of the lifting / lowering cord that also functions as an obstacle stop device, it will be the lowest limit at almost the same timing as above, but with a lower limit device such as a screw feed mechanism In this blind, the user can freely determine the lower limit position. Therefore, in the case of a blind with a lower limit device such as a screw feed mechanism, the minimum brake force may be determined by setting the lower limit freely determined by the user as the lowest limit.

-It can also be applied to the case where control is performed so that the winding speed does not become excessive with respect to the blind using an automatic winding mechanism by a stored energy such as a spring. In this case, the position is adjusted so as to generate a braking force suitable for each position (torque gap) between the biasing force of a spring or the like and the blind load. The torque gap becomes a driving torque for rotationally driving the winding shaft. In the case of a solar radiation shielding device with positive characteristics (such as a roll screen, the torque to the winding shaft increases due to the weight of the shielding material as it unwinds), a structure that generates power by a spring motor of a torsion coil spring is generally used. Is. When the twist rotational speed of the spring motor accompanying the rewinding rotation of the winding shaft increases, the torque generated by the spring motor increases as indicated by Ts in FIG. On the other hand, as the shielding material moves toward the lower limit, the torque applied to the winding shaft due to the weight of the shielding material increases as indicated by Tw in FIG. Therefore, the torque applied to the winding shaft by the generated torque of the spring motor and the weight of the shielding material approximates the inclination direction. A structure in which the torque generated by the spring motor is made larger than the screen load acting on the take-up shaft to generate a torque gap and automatically take up is provided, and a damper is provided to prevent an excessive speed. When the present invention is applied to a shielding device using an automatic winding mechanism such as a spring and the like, the braking force may be set according to the inclination of the torque gap. That is, the increase / decrease tendency of the braking force may be matched with the increase / decrease tendency of the torque gap that changes for each open / close position during automatic operation in the shielding device. In the case of a roll screen, the torque gap TG changes from large to small and from small to large as the screen descends as shown in FIG. 42 (a), and accordingly, as shown in FIG. 42 (c). Furthermore, by changing the cross-sectional area of the inner surface 37a of the housing 37 from small 1 to large 2, and from large 2 to small 3, as shown in FIG. 42 (b), the braking force can be approximated to the torque gap TG. Good. That is, the braking force may be increased or decreased in proportion to the increasing or decreasing tendency of the torque gap that changes for each open / close position during automatic operation in the shielding device. Of course, the cross-sectional area of the inner surface of the housing may be approximated by changing nonlinearly.

A structure that automatically lifts with a shielding device having a reverse characteristic such as a horizontal blind, a pleated screen, or a roman shade is disclosed in, for example, Japanese Patent Laid-Open No. 2000-130052, but such a device does not have an excessive winding speed. Thus, the present invention can be applied. For example, when adjusting to the torque gap TG (the difference between the torque Ts generated by the spring motor and the torque Tw applied to the winding shaft by the dead weight of the shielding material) in FIG. 43 (a), as shown in FIG. 43 (c) Even if the lift starts at a position where the gap is the smallest TG, the minimum brake force within an allowable range in which the lifting / lowering cord can be wound up by the urging means without being stopped is determined by the wide gap 41-1 and the viscosity. The gap 41-2 is set to be medium at a high position near the upper limit (the torque gap is at a medium position), and the gap 41-3 is set at a position where the torque gap is the maximum (near the lower limit in this load converter). As shown in FIG. 43 (b), the taper shape may be set so as to be a brake force gradient that approximates the gradient of the torque gap.

・ Automating either the opening or closing direction by the stored energy of springs, weights, etc. for partitions such as solar shading devices such as horizontal type vertical brides, curtain rails, panel screens, pleated screen doors and accordion curtains. Even when applied to a shielding device that is self-opening, the inclination of the damper torque may be approximated in accordance with the inclination of the torque gap.

In the above embodiment, the central shaft 38 is rotated integrally with the drive shaft 12, but the central shaft 38 may be fixed to the head box 1 and the housing 37 may be rotated integrally with the drive shaft 12. Further, the rotation of the drive shaft 12 may be transmitted so that the central shaft 38 and the housing 37 rotate in opposite directions.

In the above embodiment, the moving member 39 is screwed to the central shaft 38 and is slidably engaged with the housing 37. However, the moving member 39 is screwed to the housing 37 and slid to the central shaft 38. You may engage so that movement is possible. In this case, for example, by changing the thickness of the central shaft 38 along the moving direction of the moving member 39, the size of the gap between the moving member 39 and the central shaft 38 is changed to change the oil flow resistance. be able to.
In the above embodiment, oil is used as the viscous fluid, but a viscous fluid other than oil can also be used.

Second Embodiment
A second embodiment of the present invention will be described with reference to FIG. This embodiment is similar to the first embodiment, and differs in that it has a one-way function (a damper torque is not generated or significantly reduced for rotation to a side where speed control is not performed). As a specific member, the main difference is that the moving member 39 includes an internal flow passage 43 and a valve member 44. Hereinafter, the difference will be mainly described.

As shown in FIG. 5, the moving member 39 is provided with an internal flow passage 43 that penetrates the moving member 39 and a valve member 44 that can open and close the internal flow passage 43. When the bottom rail 5 is lowered by its own weight, the moving member 39 moves in the direction of the arrow X. At that time, the valve member 44 is pushed by the oil and moves to a position where the internal flow passage 43 is closed as shown in FIG. In this state, the oil can move from the front to the rear of the moving member 39 only through the gap 41, and the oil flow resistance is large, and therefore the braking force of the speed adjusting unit 36 is large.

On the other hand, when the bottom rail 5 is raised, the moving member 39 moves in the direction of the arrow Y. At that time, the valve member 44 is pushed by oil and moves to a position where the internal flow passage 43 is opened as shown in FIG. To do. In this state, the oil can move from the front to the rear of the moving member 39 through both the gap 41 and the internal flow passage 43, and the oil flow resistance is small, so that the braking force of the speed adjusting unit 36 is large.

As described above, in this embodiment, the speed adjustment unit 36 is obtained by using the valve member 44 to substantially change the cross-sectional area of the flow path through which the oil can pass through the moving member 39 according to the moving direction of the moving member 39. It is possible to change the braking force. Further, with such a configuration, when the bottom rail 5 is lowered by its own weight with a simple configuration, it is possible to suppress an excessive increase in the descending speed of the bottom rail 5 by appropriately applying a braking force, and the side where the speed is not controlled (bottom) When the rail 5 is lifted, the braking force is reduced to suppress an increase in operating force when the bottom rail 5 is lifted. In order to apply the present invention to a blind using an automatic winding mechanism using a stored energy such as a spring, the valve is opened by rotation to the side (down direction) where speed control is not performed. When it is applied to a self-closing device using a horizontal pulling window covering or a stored energy in a partition, the valve is opened by rotation to the side where the speed is not controlled (opening direction). When applied to a self-opening device, the valve is opened by rotation to the side where the speed is not controlled (closing direction).

<Third Embodiment>
A third embodiment of the present invention will be described with reference to FIG. This embodiment is similar to the first embodiment, and the inner surface 37a of the housing 37 is not tapered, and the flow resistance of the oil can be changed by the movement of the moving member 39 by another means. This is the main difference. Hereinafter, the difference will be mainly described.

In the configuration example 1 of the present embodiment, as illustrated in FIG. 6B, a large number of grooves 45 extending along the moving direction of the moving member 39 are provided on the inner surface 37 a of the housing 37. The oil in the accommodation space 40 moves from the front to the rear of the moving member 39 through the groove 45. As shown in FIG. 6B, the number of grooves 45 arranged around the moving member 39 increases as the moving member 39 moves in the arrow X direction. For this reason, the cross-sectional area of the oil flow passage increases stepwise, and the oil flow resistance is reduced. Although the braking force decreases stepwise by the movement of the moving member 39 in the direction of the arrow X, the amount of movement of the moving member—the inclination of the braking force may be matched to the height of the blind—the inclination of the load. If the increased pitch of each step is matched with the stepwise decrease of the shielding material, it is possible to further approximate the torque change accompanying the lowering of the shielding material. Although the number of grooves 45 is changed here, the width or depth of the grooves may change as the moving member 39 moves. That is, the cross-sectional area of the groove around the moving member 39 may be increased as the moving member 39 moves.

In the configuration example 2 of the present embodiment, as shown in FIG. 6C, a large number of recesses 46 are provided on the inner surface 37 a of the housing 37. The oil in the accommodation space 40 moves from the front of the moving member 39 to the rear through the recess 46. As shown in FIG. 6C, as the moving member 39 moves in the arrow X direction, the number of concave portions 46 arranged around the moving member 39 increases. For this reason, the cross-sectional area of the oil flow passage increases, and the oil flow resistance is reduced. Although the number of recesses 46 is changed here, the size or depth of the recesses may change as the moving member 39 moves. In other words, the cross-sectional area of the recess around the moving member 39 may be increased as the moving member 39 moves.

In the configuration example 3 of the present embodiment, as shown in FIG. 6D, the elastic coefficient of the inner surface 37a of the housing 37 is changed along the moving direction of the moving member 39. When the moving member 39 is not moving, there is substantially no gap between the housing 37 and the moving member 39 or the size of the gap between the housing 37 and the moving member 39 is in the moving direction of the moving member 39. However, when the moving member 39 moves in the direction of the arrow X, the oil elastically deforms the inner surface 37a of the housing 37 to form a flow passage, and moves from the front to the rear of the moving member. In this configuration example, as the moving member 39 moves, the elastic coefficient of the inner surface 37a becomes smaller, so that an oil flow passage is easily formed, and the oil flow resistance becomes smaller.

As described above, even if the inner surface 37a of the housing 37 is not tapered, the inner surface 37a of the housing 37 is configured with a simple configuration as shown in the first to third configuration examples, whereby the moving member 39 is moved. By changing the oil flow resistance, the oil can be reliably opened and closed at a position where the weight is minimum or a position where the torque gap is minimum without stopping.

<Fourth embodiment>
A fourth embodiment of the present invention will be described with reference to FIG. This embodiment is similar to the first embodiment, and the main difference is that the flow resistance of oil is changed using a tapered fixed shaft 49. Hereinafter, the difference will be mainly described.

In the present embodiment, the difference between the inner periphery of the moving member 39 and the housing 37 is constant in the axial direction, and the gap is zero or very small. The through hole 50 is provided in the moving member 39, and the through hole 50 is provided. A taper-shaped fixed shaft 49 is inserted through the shaft. Since the cross-sectional area of the through hole 50 is larger than the cross-sectional area of the fixed shaft 49, a gap 51 is provided between the moving member 39 and the fixed shaft 49. When the moving member 39 moves, the oil moves from the front to the rear of the moving member 39 through the gap 51. As the moving member 39 moves in the direction of the arrow X, the gap 51 increases and the oil flow resistance decreases.

In the first to third embodiments, the oil flow passage is provided between the housing 37 and the moving member 39. However, in this embodiment, the gap 51 between the moving member 39 and the fixed shaft 49 is the main oil. It becomes a flow passage. By changing the size of the gap 51 in accordance with the movement of the moving member 39, the oil flow resistance is changed, so that the braking force that does not stop at the position where the own weight is the minimum or the torque gap is the minimum can be opened and closed reliably. it can.

<Fifth Embodiment>
A fifth embodiment of the present invention will be described with reference to FIG. This embodiment is similar to the first embodiment, and the main difference is that the flow resistance of oil is changed using the movable plate 39b. Hereinafter, the difference will be mainly described.

In this embodiment, as shown in FIG. 8, the moving member 39 includes a main body 39a having a through hole 39d and a movable plate 39b capable of opening and closing the through hole 39d. The movable plate 39 b has a protrusion 39 c, and the protrusion 39 c engages with a groove 53 provided on the inner surface 37 a of the housing 37. In this example, as shown in the development view of FIG. 8B, the groove 53 is provided on the inner surface 37a of the housing 37 with an oblique angle with respect to the axial direction. The main body portion 39a is provided with a female screw portion 39f and a groove 39e. The female screw portion 39f is screwed into a male screw portion 38a provided on the central shaft 38. Further, the ridge 52 provided on the inner surface 37 a of the housing 37 is engaged in the groove 39 e so that the moving member 39 is accommodated in a relatively non-rotatable manner with respect to the housing 37. With such a configuration, the moving member 39 slides along the axial direction of the central shaft 38 with relative rotation between the housing 37 and the central shaft 38.

In this embodiment, when the moving member moves, the oil in the accommodation space 40 moves from the moving direction of the moving member to the separating direction through the through hole 39d of the main body 39a. When the moving member is at the position P, the through hole 39d is completely closed as shown in FIG. 8G, so that the oil flow resistance is large, and therefore the braking force by the speed adjusting unit 36 is also large. On the other hand, as the moving member 39 moves in the arrow X direction, the protrusion 39c moves along the groove 53, whereby the movable plate 39b rotates. As the movable plate 39b rotates, as shown in FIGS. 8 (e) to 8 (f), the through hole 39d is gradually opened, the oil flow resistance is reduced, and the braking force is shown in FIG. 8 (h). To change. The shielding member can be reliably opened and closed by setting the moving member so that its own weight is minimized at a position slightly ahead of the maximum R of the through hole 39d and the opening and closing body does not stop halfway. Further, by setting the descent speed associated with the weight drop near P to a predetermined value or less, it is possible to achieve both reliable opening and closing of the shielding material and speed control for starting the weight drop.

<Sixth Embodiment>
A sixth embodiment of the present invention will be described with reference to FIG. This embodiment is similar to the fifth embodiment, and the main difference is that the flow resistance of oil is changed using the movable projecting member 39k. Hereinafter, the difference will be mainly described.

In the present embodiment, as shown in FIG. 9, the moving member 39 includes a main body portion 39a having a through hole 39h and a movable projecting member 39k capable of opening and closing the through hole 39h. The movable projecting member 39k has a through hole 39j, and is biased by a biasing member (for example, a coil spring) 39i so that the tip 39g thereof is a main body portion 39a as shown in FIG. 9 (d). Protruding from. A groove 54 whose depth varies along the moving direction of the moving member 39 is provided on the inner surface 37a of the housing 37, and when the moving member 39 is housed in the housing space 40, the tip of the movable projecting member 39k. 39 g contacts the upper end in the groove 54.

In the present embodiment, the oil in the accommodation space 40 moves from the accommodation space in the traveling direction to the accommodation space in the separation direction as the moving member moves through the through hole 39h of the main body 39a. When the moving member is at the position P, the end 39g of the movable projecting member 39k is pushed by the inner surface 37a of the housing 37, and the state shown in FIG. In this state, the position of the through hole 39h of the main body 39a and the position of the through hole 39j of the movable projecting member 39k do not match, so the through hole 39h is completely closed. For this reason, the flow resistance of oil is large, and therefore the braking force by the speed adjusting unit 36 is also large. On the other hand, the tip 39g moves along the groove 54 as the moving member 39 moves in the arrow X direction. As the groove 54 becomes deeper, the tip 39g protrudes as shown at the position Q, and at the position R, as shown in FIG. 9 (d), the protruding amount of the tip 39g increases. The overlap of the through holes 39j is increased, the oil flow resistance is reduced, and the braking force is reduced. With such a configuration, it is possible to both weaken the braking force near the position R and securely open and close the shielding material, and to reduce the descent speed associated with the weight drop near the position P to a predetermined value or less.

<Seventh embodiment>
A seventh embodiment of the present invention will be described with reference to FIG. This embodiment is similar to the fifth embodiment, and the main difference is that the flow resistance of oil is changed using magnetic force. Hereinafter, the difference will be mainly described.

In the present embodiment, as shown in FIG. 10, a magnet 57 is provided on the outer periphery of the moving member 39. Further, on the outer periphery of the housing 37, a magnetic body 55 such as an iron plate is provided in a part of the longitudinal direction in the brake force increasing region P. According to such a configuration, when the moving member 39 moves to the region P, the housing 37 is contracted by the attractive force between the magnet 57 and the magnetic body 55, so that the gap 41 between the moving member 39 and the housing 37 is formed. It is narrowed. Further, when the magnet 57 moves in the conductor 55, an eddy current is generated in the conductor 55 so as to prevent a change in the magnetic field, and a braking force in a direction that prevents the movement is applied to the magnet. In the present embodiment, the oil moves from the front to the rear of the moving member 39 through the gap 41. Therefore, the oil circulation is achieved by changing the size of the gap 41 with a simple configuration by the magnetic force as the moving member 39 moves. Resistance can be changed. Further, when the moving speed of the magnet is increased, the braking force is increased by the eddy current in the conductor 55.
The moving member 39 may be provided with a magnetic body, and the housing 37 may be provided with a magnet. Further, a magnet may be provided on both the moving member 39 and the housing 37. An attractive force or a repulsive force may be applied between the magnet of the moving member 39 and the magnet of the housing 37. When an attractive force is applied between them, the magnet of the housing 37 is disposed on the outer periphery of the housing 37. Further, when a repulsive force is applied between the magnet of the moving member 39 and the magnet of the housing 37, the magnet of the housing 37 is disposed on the inner surface of the housing 37. In this case, the housing 37 is expanded by the repulsive force, the gap 41 between the moving member 39 and the housing 37 is widened, and the oil flow resistance is reduced.

<Eighth Embodiment>
The eighth embodiment of the present invention will be described with reference to FIG. This embodiment is similar to the fifth embodiment, and is mainly different in that the resistance force that the moving member 39 receives from the oil is changed using the oil flow passage 37d provided in the housing 37. Hereinafter, the difference will be mainly described.

In this embodiment, the moving member 39 is accommodated in the housing 37 so as to be relatively movable in the axial direction and not to be relatively rotatable. The center shaft 38 is screwed into the center of the moving member 39, and the moving member 39 moves in the axial direction as the center shaft 38 rotates. In the case of application to window covering with reverse characteristics such as a horizontal blind, when the central shaft 38 rotates based on the rotation of the drive shaft 12 in the descending direction, the moving member 39 moves toward the direction of arrow X in FIG. Configured to move. An oil flow passage 37 d is provided at the right end of the housing 37. The oil flow passage 37d includes a first opening 37e and a second opening 37f that are separated from each other in the moving direction of the moving member 39.

When the bottom rail 5 is at a position away from the lower limit position, as shown in FIG. 11A, the oil flow passage 37d does not function because the moving member 39 is on the left side of the second opening 37f. The resistance force that the moving member 39 receives from the oil is large.

When the bottom rail 5 falls by its own weight and reaches near the lower limit position, the moving member 39 reaches the position T past the position S in FIG. In this state, the moving member 39 is located between the first opening 37e and the second opening 37f. When the moving member 39 moves from the position T toward the position U, oil on the moving direction side of the moving member 39 enters the oil flow passage 37d through the first opening 37e and moves through the second opening 37f. Therefore, the resistance force that the moving member 39 receives from the oil is small. Also, when turning upward, the oil flows back from the traveling direction to the separating direction through 37f, 37d, and 37e due to the movement of the moving member.

Based on the above principle, according to the present embodiment, the resistance force that the moving member 39 receives from the oil while the moving member 39 moves from the position S to the position T is drastically reduced. Continue until position U is reached. Therefore, by setting the moving member 39 to reach the position S when the bottom rail 5 reaches the vicinity of the lower limit position, the braking force in the vicinity of the lower limit position of the bottom rail 5 is reduced, It is possible to reliably reach the lower limit position.

<Ninth Embodiment>
A ninth embodiment of the present invention will be described with reference to FIG. This embodiment is similar to the first embodiment, and is mainly different in that the moving member 39 is fixed to the central shaft 38. Hereinafter, the difference will be mainly described.

In this embodiment, the moving member 39 is fixed to the central shaft 38 as shown in FIG. The central shaft 38 rotates in conjunction with the drive shaft 12 of the shielding device and applies a braking force to the drive shaft 12 as a reaction force of the rotational resistance. For example, a square shaft having a square cross section is inserted into a square hole provided on the central axis and having substantially the same shape as the outer shape of the rectangular shaft, so that the angular shaft and the central axis are not relatively rotatable and relatively movable. Engaged. The housing is fixed so that it cannot move relative to the head box in the axial direction and cannot rotate relative to the head box. The central shaft 38 is screwed to a pedestal 59 fixed to the head box 1, and the central shaft 38 moves in the axial direction while rotating with respect to the pedestal 59 as the central shaft 38 rotates. At that time, the drive shaft 12 and the central shaft 38 move relative to each other. Further, as the central shaft 38 rotates and moves in the axial direction, the moving member 39 moves in the axial direction while rotating in the accommodation space 40 of the housing 37. There is a slight gap between the inner surface 37a and the outer peripheral surface of the moving member 39. As the moving member moves in the axial direction, the moving member moves from the receiving space in the moving direction toward the receiving space in the separating direction. Oil moves. Since the inner surface 37a of the housing 37 is tapered as shown in FIG. 12, the gap becomes narrower toward the right end of FIG. As the moving member 39 moves, the oil flow resistance changes. The blinds are assembled so that the right end is at the top and the left end is at the bottom. Accordingly, as the rewinding rotational speed increases so as to approximate the load characteristic of the blind, the braking force decreases, and the blind is rewound without stopping near the lower limit of the blind.

In the present embodiment, the central shaft 38 does not penetrate the housing 37, but may be configured to penetrate the housing 37.

<Tenth Embodiment>
A tenth embodiment of the present invention will be described with reference to FIG. This embodiment is similar to the ninth embodiment, and differs in that it has a one-way function (a damper torque is not generated or significantly reduced for rotation to a side where speed control is not performed). Hereinafter, the difference will be mainly described.

In this embodiment, as shown in FIG. 13, the moving member 39 includes a main body 39a and a movable ring 39l. The main body 39a is fixed to the central shaft 38 by a fixing pin 39t. The tip of the central shaft 38 is inserted into the shaft hole 39r of the movable ring 39l. The main body 39a is disposed so that the engaging protrusion 39n provided in the main body 39a and protruding in the axial direction is accommodated between the engaging protrusions 39o and 39p provided in the movable ring 39l and protruding in the radial direction. In a state where the movable ring 39l is overlapped, the fixed ring 39s is attached to the front and back of the movable ring 39l so that the movable ring 39l is rotatably supported with respect to the main body 39a. When the bottom rail 5 is raised, the central shaft 38 rotates in the direction of arrow A, and the main body 39a and the movable ring 39l are in contact with the engaging convex 39n of the main body 39a abutting on the engaging convex 39o of the movable ring 39l. Rotate together. In this state, the through-hole 39m of the main body 39a and the through-hole 39q of the movable ring 39l are overlapped, and oil can flow through these through-holes, so the oil flow resistance is small. For this reason, the operation force required for the raising operation of the bottom rail 5 is small. On the other hand, when the weight of the bottom rail 5 is lowered, the central shaft 38 rotates in the direction of arrow B, and the main body 39a and the main body 39a are in contact with the engaging convex 39p of the movable ring 39l. The movable ring 39l rotates integrally. In this state, since the through hole 39m of the main body 39a and the through hole 39q of the movable ring 39l do not overlap, the oil flow resistance is large. For this reason, an appropriate braking force is generated when the bottom rail 5 is lowered by its own weight. In short, the valve is opened by rotation to the side where the speed control is not performed (in the raising direction). In window covering that automatically raises by the urging force, the valve is opened by rotation to the side where the speed is not controlled (down direction). When it is applied to a self-closing device using a horizontal pulling window covering or a stored energy in a partition, the valve is opened by rotation to the side where the speed is not controlled (opening direction). When applied to a self-opening device, the valve is opened by rotation to the side where the speed is not controlled (closing direction).

<Eleventh embodiment>
The eleventh embodiment of the present invention will be described with reference to FIG. This embodiment is similar to the fifth embodiment, and the main difference is that the shape of the groove 53 is different. Hereinafter, the difference will be mainly described.

In the fifth embodiment, since the groove 53 is linear in the developed view shown in FIG. 8B, the through hole 39d of the main body 39a is gradually closed as the moving member 39 moves, so that the oil In the present embodiment, the groove 53 is formed in the moving direction of the moving member 39 in the range from the position S to the position T as shown in FIG. Since it is parallel, until the moving member 39 moves from the position S to the position T, the through hole 39d is kept closed as shown in FIG. The braking force by the speed adjustment unit 36 is large as shown in FIG. Then, since the inclination angle of the groove 53 is large in the range from the position T to the position U, the through hole 39d is opened while the moving member 39 moves in this range, and the state shown in FIG. The braking force by the part 36 is reduced. A weak braking force is maintained while the moving member 39 moves from the position U to the position V. Therefore, the weak brake region R is between the position T and the position V. With such a configuration, by setting the moving member 39 to reach the region R when the bottom rail 5 reaches the vicinity of the lower limit position, the braking force in the vicinity of the lower limit position of the bottom rail 5 is reduced, The bottom rail 5 can be reliably reached to the lower limit position. Thus, in this embodiment, in the dead weight solar radiation shielding device, the braking force is decreased from the lower limit by a predetermined multiple number of revolutions.

<Twelfth embodiment>
A twelfth embodiment of the present invention will be described with reference to FIG. The present embodiment is similar to the eighth embodiment, and the main point is that the resistance that the moving member 39 receives from the oil is changed by changing the moving speed of the moving member 39 as the moving member 39 moves. This is a major difference. Hereinafter, the difference will be mainly described.

In the present embodiment, a moving member 39 that is movable as the bottom rail 5 is moved up and down is provided in a housing 37 filled with oil, and the oil moves through a gap between the outer periphery of the moving member 39 and the inner surface 37 a of the housing 37. Get braking force with resistance. The moving speed of the moving member 39 when the weight of the bottom rail 5 is lowered is changed by changing the feed angle of the central shaft 38 having the groove 38b within the moving range of the moving member 39 and changing the moving distance of the moving member 39 per unit rotation. And the braking force is changed according to the position of the bottom rail 5. When the bottom rail 5 is near the upper limit, the braking force is increased, and when the bottom rail 5 is near the lower limit, the braking force is decreased. Even in the region where the bottom rail 5 is lowered to near the lower limit and the difference between the downward force due to the weight of the bottom rail 5 and the screen 4 and the upward force due to the spring property of the screen 4 itself is small, the bottom rail 5 The braking force in this region is sufficiently reduced so that reaches the lower limit position.

Hereinafter, the configuration of the present embodiment will be described more specifically. The moving member 39 is accommodated in the housing 37 so as to be relatively movable in the axial direction and not to be relatively rotatable. The central shaft 38 includes a spiral groove 38b, and the pitch of the spiral of the groove 38b becomes narrower as it goes to the right in FIG. The moving member 39 includes an engaging convex portion 39u that is engaged with the groove 39b.

When the central shaft 38 rotates based on the rotation of the drive shaft 12 in the descending direction, the spiral groove 38b also rotates together, and the engaging convex portion 39u moves along the groove 39u, whereby the moving member 39 is moved to the arrow. Move in the X direction. The moving distance of the moving member 39 per unit rotation of the drive shaft 12 depends on the pitch of the spiral of the groove 39u, and the moving member 39 moves fast in the high-speed moving region where the pitch is relatively large. The resistance force received from is great. On the other hand, as the moving member 39 moves, the pitch of the spiral of the groove 39u becomes narrower, and accordingly, the moving distance of the moving member 39 per unit rotation of the drive shaft 12 (or the winding shaft 10) becomes smaller. The resistance force that the moving member 39 receives from oil is reduced. For this reason, when the moving member 39 moves from the high-speed moving region to the medium-speed moving region to the low-speed moving region as the descending rotation speed increases, the resistance force received by the moving member 39 changes from large to medium to small, and the bottom rail 5 The braking force in the vicinity of the lower limit position becomes sufficiently small, and the bottom rail 5 reliably reaches the lower limit position. In the present embodiment, the pitch of the spiral of the groove 39u changes in three stages, but it may be changed in more stages, or may be changed continuously in a stepless manner.

<13th Embodiment>
A thirteenth embodiment of the present invention will be described with reference to FIG. The present embodiment is similar to the eighth embodiment, and the main difference is that the rotation of the drive shaft 12 is transmitted to the central shaft 38 via the switching member 62. Hereinafter, the difference will be mainly described.

In the present embodiment, as shown in FIG. 16B, the central shaft 38 has an opening 38d having a circular cross section, and the drive shaft 12 can idle in the opening 38d. A switching member 62 is provided adjacent to one end of the central shaft 38. The switching member 62 is configured so as not to rotate relative to the drive shaft 12 and to be relatively movable in the axial direction of the drive shaft 12. Engaging portions 38c and 62a that can be engaged with each other are provided at the respective ends of the central shaft 38 and the switching member 62 so as to face each other. As shown in FIGS. 16A and 16F, the engaging portion 62a is configured by alternately forming concave portions and convex portions in the circumferential direction. The engaging portion 38 c has a shape complementary to the engaging portion 62. As shown in FIG. 17, when the switching member 62 is slid in the direction approaching the central shaft 38 and the engaging portions 38 c and 62 a are engaged, the drive shaft 12 and the central shaft 38 are connected to each other so as to be integrally rotatable. . On the other hand, when the switching member 62 is slid in the direction away from the central shaft 38 to disengage the engaging portions 38c and 62a, the central shaft 38 is idled with respect to the drive shaft 12.

According to such a configuration, even after the drive shaft 12 is inserted into the central shaft 38, the moving member can be rotated without rotating the drive shaft 12 by rotating the central shaft 38 in an unconnected state. 39 can be moved to a desired position. That is, the stroke end position of the moving member 39 can be adjusted in the assembled state. According to such a configuration, it is possible to adjust the position of the moving member 39 after the speed adjusting unit 36 is incorporated into the head box 1, and the assemblability is improved.

Further, an upward force is exerted on the bottom rail 5 due to the spring property of the screen 4 itself. This upward force may become weaker as time elapses, and as a result, the bottom rail 5 descends. The speed may be higher than at the start of use. In the present embodiment, by rotating the central shaft 38 in the disconnected state, the position of the moving member 39 at the lower limit position and the upper limit position of the bottom rail 5 is changed from L1 and U1 to L2 and U2, as shown in FIG. It is possible to change. By changing in this way, the timing at which the moving member 39 reaches the second opening 37 when the bottom rail 5 is lowered is delayed, and accordingly, the timing at which the braking force applied to the drive shaft 12 is reduced is delayed. The descending speed of the bottom rail 5 can be reduced.

In another expression, in the present embodiment, the speed adjustment unit 36 includes a link state in which the rotation of the winding shaft 10 and the movement of the moving member 39 are linked, and the rotation of the winding shaft 10 and the moving member 39. It is configured to be switchable between an unlinked state in which movement is not linked. In the unlinked state, the moving member 39 can be moved independently of the rotation of the winding shaft 10. In other embodiments as well, the same effect can be obtained by enabling switching between a link state and a non-link state as in the present embodiment. If it demonstrates in 8th Embodiment, it will be illustrated that the drive shaft 12 is removable with respect to the center axis | shaft 38. FIG.

<Fourteenth embodiment>
A fourteenth embodiment of the present invention will be described with reference to FIGS. The basic configuration of the present embodiment is similar to that of the thirteenth embodiment, and the brake force increasing means for increasing the brake force applied to the winding shaft 10 in the brake force increasing range that is a part of the movable range of the moving member 39. Is the main difference. In the present embodiment, the brake force increasing means is configured to form a piston structure with the moving member 39 when the moving member 39 is within the brake force increasing range.
Hereinafter, the difference will be mainly described.

In this embodiment, the center shaft 38 is provided with a flange 72, and the moving member 39 is provided with a recess 39w that accommodates the flange 72 on the side facing the flange 72 and forms a piston structure. The moving member 39 can move in the axial direction with respect to the housing 37 along with the rotation of the central shaft 38, but the flange 72 is fixedly provided on the central shaft 38, and the flange 72 and the moving member 39 can move relative to each other. It has become. According to such a configuration, while the left end of the moving member 39 is within the braking force increase range shown in FIG. 18A, the moving member 39 moves when the moving member 39 moves with the rotation of the winding shaft 10. In addition to the resistance force due to oil flow between the outer peripheral surface of 39 and the inner surface 37a of the housing 37, resistance force due to oil flow between the outer peripheral surface of the flange 72 and the inner surface of the recess 39w of the moving member 39 is generated. The braking force applied to the take-up shaft 10 is increased. Thus, in the present embodiment, the “braking force increasing means” recited in the claims is configured by the flange 72 and the recess 39w. On the other hand, as shown in FIG. 19 (a), when the moving member 39 is separated from the braking force increasing range, the piston structure between the flange 72 and the recess 39w is eliminated, and is added to the winding shaft 10 by that amount. Brake force is reduced. Therefore, as shown in FIG. 18A, the relationship between the rotational speed of the winding shaft 10 with the origin when the moving member 39 is located on the left end side of the movable range in the housing 37 and the braking force applied thereto. Is as shown in FIG.

In the shielding device for dropping the shielding material by its own weight, the driving torque applied to the winding shaft 10 is large when the shielding material is near the upper limit, and the descending speed of the shielding material tends to increase excessively. On the other hand, in a shielding device such as a roll screen that is automatically raised by a spring, when the shielding material is wound up to the vicinity of the upper limit, the ascending speed tends to increase excessively. Therefore, for such a shielding device, when the shielding member is in the vicinity of the upper limit, the moving member 39 is configured to be positioned in the braking force increasing range, so that the shielding material descending speed is likely to increase. The braking torque (braking force) can be increased.

By the way, the speed adjustment unit 36 of the present embodiment is provided with an adjustment dial 71, and the drive shaft 12 is operated by operating the adjustment dial 71 when the switching member 62 and the central shaft 38 are not connected. The moving member 39 can be moved to an arbitrary position by rotating the central shaft 38 without rotating. According to such a configuration, the initial position of the moving member 39 can be easily adjusted. For example, in the self-weight drop type shielding device, when the descent time of the shielding material (time to reach the lower limit from the upper limit of the shielding material) is long, the initial position of the moving member 39 is set to the right in FIG. By moving the moving member 39 in the direction, it is possible to advance the timing at which the moving member 39 leaves the range of increase in the braking force, thereby shortening the descent time of the shielding material. On the other hand, when the descending speed of the shielding material is fast, the initial position of the moving member 39 is moved to the left in FIG. Thus, the descending speed of the shielding material can be reduced. According to such a configuration, speed (descent time) can be easily adjusted. In addition, when applying the speed adjustment part 36 of this embodiment to a roll screen, a raise time can be adjusted easily.

This embodiment is also an embodiment in the following aspects.
As shown in Modification 1 in FIG. 20, (1) the inner peripheral diameter of the housing 37 is increased toward the distal end side, and the braking force can be gradually reduced or increased over the entire length. (2) The inner peripheral diameter of the recess 39w of the moving member 39 is formed so as to increase toward the base end side, and the braking force can be gradually reduced or increased in the braking force increasing range. By combining (1) and (2), the braking force can be gradually reduced or increased over the entire length from the braking force increase range.
As shown in Modification 2 of FIG. 21, instead of providing the flange 72 on the center shaft 38, a cylindrical member 77 is disposed in the housing 37, and the cylindrical structure 77 and the recess 39w constitute a piston structure. Good. Even in this case, the same effect as the above-described embodiment can be obtained. The cylindrical member 77 may be fixed to the central shaft 38, may be fixed to the housing 37, and may be provided on any member as long as it can be moved relative to the moving member 39. Further, as shown in Modification 3 of FIG. 22, instead of providing the moving member 39 with the concave portion 39w, a convex portion 39ab is provided, and the convex portion 39ab is inserted into the small-diameter portion 37j of the housing 37 in the brake force increasing range. A structure may be formed. Even in this case, the same effect as the above-described embodiment can be obtained. Instead of forming the piston structure between the convex portion 39ab and the housing 37, another member may be disposed in the housing 37, and the piston structure may be formed between the member and the convex portion 39ab.
A member that forms a piston structure with the moving member 39 is a member that moves relative to the moving member 39 when the moving member 39 moves with the rotation of the winding shaft 10 (a member that does not move, the moving member 39). The member is not limited as long as the member moves at a different speed or in a different direction.

<Fifteenth embodiment>
A fifteenth embodiment of the present invention will be described with reference to FIGS. Similar to the fourteenth embodiment, the speed adjusting unit 36 according to the present embodiment includes a brake force increasing unit that increases the braking force applied to the winding shaft 10 in the brake force increasing range. The increasing means is composed of a rotation resistor 74 that increases the braking force applied to the winding shaft 10 by rotating with the rotation of the winding shaft 10 when the moving member 39 is within the braking force increasing range. . Details will be described below.

In this embodiment, a drive shaft 12 that rotates integrally with the winding shaft 10 is inserted through a central shaft 38 that is rotatably supported by the housing 37. The center shaft 38 rotates integrally with the drive shaft 12. The housing space 40 in the housing 37 is divided into first and second housing spaces 40a and 40b by a partition wall 37h. A hole 37i is provided in the partition wall 37h so that oil can move between the first and second storage spaces 40a and 40b. The hole 37i is provided with a female screw portion 37g.

The moving member 39 includes a flange 39y and a screw shaft 39x. The screw shaft 39x is screwed into the female screw portion 37g. The moving member 39 is configured to rotate with the rotation of the central shaft 38. According to such a configuration, the moving member 39 moves in the axial direction of the central shaft 38 while rotating as the central shaft 38 rotates.

In the housing 37, a rotation resistor 74 supported so as to be rotatable about the drive shaft 12 is provided. The rotation of the drive shaft 12 and the central shaft 38 is not directly transmitted to the rotation resistor 74. The rotation resistor 74 includes a base portion 74a, a screw 74b provided so as to spread in the radial direction from the base portion 74a, and a protrusion 74c that protrudes in the direction of the moving member 39 from the base portion 74a. The moving member 39 includes a protrusion 39 z that protrudes in the direction of the rotation resistor 74. The protrusions 74 c and 39 z are engaged only when the right end of the protrusion 39 z is within the braking force increase range shown in FIG. 23A, and the rotation of the moving member 39 is transmitted to the rotation resistor 74. The tips of the projections 74c and 39z are provided with a taper surface 39z1 (the taper surface of the tip of the projection 74c is not shown) for allowing the rotation resistor to escape in the rotation direction when the tips are brought into contact with each other.

The operation of the speed adjustment unit 36 of this embodiment will be described below.
First, in the state shown in FIG. 23, since the protrusions 74c and 39z are engaged, the moving member 39 and the rotation resistor 74 rotate integrally with the rotation of the central shaft 38, and only the moving member 39 is in FIG. (A) Move in the arrow X direction. In this state, in addition to the resistance force caused by the oil flow between the outer peripheral surface of the flange 39y and the inner surface 37a of the housing 37, the resistance force generated by the rotation of the screw 74b is generated, so the braking force applied to the winding shaft 10 is reduced. Will be increased.

When the right end of the projection 39z moves away from the braking force increasing range shown in FIG. 23A with the movement of the moving member 39, the resistance force accompanying the rotation of the rotation resistor 74 is not applied to the winding shaft 10. The braking force applied to the shaft 10 is reduced.

Since the inner peripheral diameter of the housing 37 increases from the position indicated by the position Y in FIG. 24 toward the arrow X direction, the moving member 39 advances in the arrow X direction after the moving member 39 reaches the position Y. As a result, the braking force applied to the winding shaft 10 gradually decreases.

This embodiment is also an embodiment in the following aspects.
As shown in the first modification of FIG. 25, as the rotation resistor 74, instead of the screw 74b, one having wings 74d (example: two) that rotate in oil and receive resistance in the rotation direction is used. Also good.

<Sixteenth Embodiment>
A sixteenth embodiment of the present invention will be described with reference to FIGS. The basic configuration of the present embodiment is similar to that of the fifteenth embodiment, and thrust applying means that rotates and moves with the moving member 39 as the winding shaft 10 rotates and applies thrust to the moving member 39. The main difference is that it is provided in the housing 37. In the present embodiment, the thrust applying means is a screw 39aa provided on the moving member 39.
Hereinafter, the difference will be mainly described.

26, the screw 39aa is provided on the moving member 39 as shown in FIG. 26, and the screw 39aa rotates and moves when the moving member 39 rotates and moves with the rotation of the central shaft 38. Then, the movement of the moving member 39 is smoothed by the thrust generated by the rotation of the screw 39aa, and the braking force applied to the winding shaft 10 is reduced.

In the shielding device that lowers the weight of the shielding material, the driving torque decreases as the shielding material approaches the lower limit position. For this reason, when the shielding material is in the vicinity of the lower limit position, the braking force by the speed adjusting unit 36 is larger than the driving torque, and as a result, the shielding material is not lowered to the lower limit position and stops halfway. May occur. In order to eliminate such a problem, the braking force by the speed adjusting unit 36 may be reduced as the shielding material approaches the lower limit position, but the moving member 39 is moved in oil as in the present embodiment. In the speed adjusting unit 36, a certain amount of braking force is inevitably generated due to the viscosity of the oil, and there is a limit to reducing the braking force. In order to reduce the braking force, the gap 41 between the moving member 39 and the housing 37 may be increased. However, if the gap 41 is increased to some extent, the effect of reducing the braking force even if the gap 41 is further increased. Is small. According to this embodiment, the movement of the moving member 39 is smoothed by the thrust generated by the rotation of the screw 39aa, so that the braking force by the speed adjusting unit 36 is reduced as compared with the case where there is no screw 39aa.

The operation of the speed adjustment unit 36 of this embodiment will be described below.
First, in the state shown in FIG. 26, the moving member 39 and the screw 39aa rotate together as the central shaft 38 rotates, and move in the direction of arrow X in FIG. In this state, a resistance force is generated by the oil flow between the outer peripheral surface of the flange 39y and the inner surface 37a of the housing 37. However, the moving member 39 moves relatively smoothly by the thrust generated by the rotation of the screw 39aa, and thus is reduced. Brake force is applied to the winding shaft 10.

Since the inner peripheral diameter of the housing 37 increases from the position indicated by the position Y in FIG. 27 in the direction of the arrow X, after the moving member 39 reaches the position Y, the moving member 39 advances in the direction of the arrow X. As a result, the braking force applied to the winding shaft 10 gradually decreases further.

This embodiment is also an embodiment in the following aspects.
As shown in Modification 1 of FIG. 28, a small diameter portion 37 may be provided in the housing 37 as a thrust increasing means for increasing the thrust in a thrust increasing range that is a part of the movable range of the moving member 39. In this case, when the screw 39aa reaches the thrust increase range, the thrust generated by the rotation of the screw 39aa is increased, so that the braking force is further reduced.

<Seventeenth Embodiment>
The seventeenth embodiment of the present invention will be described with reference to FIG. The basic configuration of the present embodiment is similar to the first and eighth embodiments, and includes an internal pressure limiter that operates when the torque applied to the winding shaft 10 exceeds a predetermined threshold and reduces the internal pressure of the housing 37. This is the main difference. Hereinafter, the difference will be mainly described.

As shown in FIG. 29A, when the drive shaft 12 rotates in the arrow B direction as the winding shaft 10 rotates, the moving member 39 moves in the arrow X direction. As the moving member 39 moves, the internal pressure (pressure due to oil) in the accommodating space 40a on the moving direction side of the moving member 39 becomes higher than the internal pressure in the accommodating space 40b on the rear side of the moving member 39. Oil flows through the gap 41 from the storage space 40a toward the storage space 40b. Since the internal pressure in the accommodation space 40a increases as the torque applied to the winding shaft 10 increases, if excessive torque is applied to the winding shaft 10, the internal pressure in the accommodation space 40a increases excessively and the housing 37 is damaged. It leads to. Therefore, in this embodiment, an internal pressure limiter that operates when the torque applied to the winding shaft 10 exceeds a predetermined threshold and reduces the internal pressure of the housing 37 is provided.

Hereinafter, the configuration of the moving member 39 incorporating the internal pressure limiter will be described. As shown in FIG. 29, in this embodiment, the moving member 39 includes first and second moving members 39ba, 39ca, a one-way spring 39da, and a fixing ring 39ea. The first moving member 39ba has a base portion 39bj and a cylindrical portion 39bc extending from the base portion 39bj in the axial direction of the central shaft 38. At least a part of the base portion 39bj and the cylindrical portion 39bc is provided with a female screw portion 39bi that is screwed into the male screw portion 38a of the central shaft 38. The base portion 39bj is provided with a notch portion 39bb, through holes 39bd1 and 39bd2, and a protrusion accommodating portion 39be for accommodating the restricting protrusion 39ce of the second moving member 39ca. A pair of leaf springs (biasing members) 39bf1 and 39bf2 are provided in the protrusion accommodating portion 39be so as to sandwich the restricting protrusion 39ce. The cylindrical portion 39bc is provided with an engaging groove 39bg that is engaged with the fixing ring 39ea. Accordingly, the first moving member 39ba and the second moving member 39ca are in a relationship of being relatively rotatable and not movable in the axial direction. The notch 39bb is wider than the protrusion 52 of the housing 37, and the first moving member 39ba can rotate relative to the housing 37 in a state where the protrusion 52 is accommodated in the notch 39bb. It has become.

The second moving member 39ca has a base portion 39cj and a regulation protrusion 39ce protruding from the base portion 39cj in the direction of the first moving member 39ba. The base 39cj is provided with a groove 39cb, a central opening 39cc, and a through hole 39cd. The base 39dj of the one-way spring 39da is provided with a groove 39db, a central opening 39dc, and a through hole 39dd. Since the widths of the grooves 39cb and 39db of the second moving member 39ca and the one-way spring 39da are substantially the same as the width of the convex stripes 52 of the housing 37, the convex stripes 52 are engaged with the grooves 39cb and 39db. The second moving member 39ca and the one-way spring 39da are not rotatable relative to the housing 37, and can only move in the axial direction along the central axis 38.

The fixing ring 39ea is engaged with the engaging groove 39bg in a state where the cylindrical portion 39bc is inserted into the central opening portions 39cc and 39dc of the second moving member 39ca and the one-way spring 39da, whereby the second moving member ca and the one-way The spring 39da is held so as to be rotatable relative to the first moving member 39ba. However, in this state, the relative rotation between the first and second moving members 39ba and 39ca is restricted by sandwiching the restricting protrusion 39ce by the pair of leaf springs 39bf1 and 39bf2. In this state, the through hole 39cd and the through hole 39dd overlap each other, but the through holes 39bd1 and 39bd2 are arranged so as not to overlap the through holes 39cd and 39dd (the base portion 39bj of the first moving member 39ba so as to face the through hole 39dd). The closed surface of the oil is closed so that the oil does not move in the axial direction through the through hole.

Next, the operation of the speed adjustment unit 36 of this embodiment will be described.
When torque in the direction of arrow B in FIG. 29A (the descending direction of the shielding material) is applied to the take-up shaft 10, the torque is transmitted to the first moving member 39ba through the drive shaft 12 and the central shaft 38, and the first Torque in the direction of arrow B in FIG. 29D is applied to the moving member 39ba. The first moving member 39ba moves in the direction of arrow X in FIG. 29A with the leaf spring 39bf1 elastically deformed in accordance with the magnitude of the applied torque. The first moving member 39ba rotates relative to the second moving member 39ca by the amount of deformation of the leaf spring 39bf1, and the through hole 39bd1 approaches the through hole 39cd by that amount. Within the allowable torque to the speed adjusting portion 36, the through hole 39dd is closed by the closing surface of the base portion 39bj of the first moving member 39ba, so that there is no movement of oil in the axial direction. As described above, the braking force gradually decreases due to the tapered inner surface 37a gradually expanding.

As the torque applied to the winding shaft 10 increases, the deformation amount of the leaf spring 39bf1 increases, and the relative rotation amount of the first moving member 39ba relative to the second moving member 39ca also increases. When the torque applied to the take-up shaft 10 due to an excessive external force exceeds a predetermined threshold, the through hole 39bd1 is overlapped with the through hole 39cd to be opened, and oil can be moved through the through holes 39bd1, 39cd, and 39dd. Thus, the internal pressure of the accommodation space 40a is reduced and the generation of excessive pressure is prevented.

Thereafter, when the torque applied to the winding shaft 10 is reduced, the amount of deformation of the leaf spring 39bf1 is reduced by elastically restoring the shape of the leaf spring 39bf1, and the first moving member 39ba with respect to the second moving member 39ca is reduced. The amount of relative rotation is also reduced, and the through hole 39bd1 does not automatically overlap the through hole 39cd (becomes a closed state), and the movement of oil through the through hole is blocked.

On the other hand, when torque in the direction opposite to the arrow B direction in FIG. 29A (the ascending direction of the shielding material) is applied to the winding shaft 10, the torque is transmitted to the first moving member 39 ba through the drive shaft 12 and the central shaft 38. Thus, torque in the direction opposite to the arrow B direction in FIG. 29D is applied to the first moving member 39ba. The first moving member 39ba moves in the direction opposite to the arrow X direction in FIG. 29A in a state where the leaf spring 39bf2 is elastically deformed according to the magnitude of the applied torque. The first moving member 39ba rotates relative to the second moving member 39ca by the amount of deformation of the leaf spring 39bf2, and the through hole 39bd2 approaches the through hole 39cd by that amount. When the torque applied to the winding shaft 10 exceeds a predetermined threshold value, the through hole 39bd2 overlaps the through hole 39cd, and the oil can be moved through the through holes 39bd2, 39cd, 39dd, and the internal pressure in the accommodation space 40b. Is reduced. Thus, in this embodiment, regardless of the rotational direction of the torque applied to the winding shaft 10, when the torque exceeds a predetermined threshold value, the internal pressure of the housing 37 is reduced and excessive pressure is prevented from being generated. .

By the way, the outer diameter of the one-way spring 39da is slightly larger than the outer diameter of the second moving member 39ca, and when the moving member 39 moves in the direction of the arrow X in FIG. The size is defined by the difference between the outer diameter of the one-way spring 39da and the inner diameter of the housing 37. On the other hand, when the moving member 39 moves in the direction opposite to the arrow X, the one-way spring 39da bends to widen the gap 41, and the resistance force that the moving member 39 receives from the oil is reduced.

This embodiment can also be implemented in the following forms.
-As an event in which excessive torque is applied to the winding shaft 10, the user may forcibly lower the shielding material or the user may be caught by the shielding material. When these events occur, excessive torque in the descending direction of the shielding material is applied to the winding shaft 10. On the other hand, an event in which excessive torque is applied to the winding shaft 10 in the upward direction of the shielding material is unlikely to occur. For this reason, the leaf spring 39bf2 and the through hole 39bd2 may be omitted, and the internal pressure limiter may be configured to operate when torque in the descending direction of the shielding material that exceeds a predetermined threshold is applied to the winding shaft 10. . In this case, the restricting protrusion 39ce is sandwiched between the leaf spring 39bf1 and the side wall of the protrusion accommodating portion 39be.
-Even if it is except the form mentioned above, if it is set as the structure which can open | release a moving member during the movement to a brake torque generation direction, and it will be in an open state with excess torque, it can replace with another aspect.

<Eighteenth embodiment>
The eighteenth embodiment of the present invention will be described with reference to FIG. The present embodiment is similar to the seventeenth embodiment in that an internal pressure limiter is provided, but the internal pressure limiter of the seventeenth embodiment operates when the torque applied to the winding shaft 10 exceeds a predetermined threshold. The internal pressure limiter of this embodiment is mainly different in that it operates when the internal pressure of the housing 37 exceeds a predetermined threshold. Hereinafter, the difference will be mainly described.

In the present embodiment, the housing 37 is provided with the first opening 37 l and the second opening 37 n that are separated in the moving direction of the moving member 39 in the housing 37 (preferably at both ends of the movable range of the moving member 39). The first and second openings 37l and 37n are connected by an oil flow passage 37m. A valve 37o is disposed in the first opening 37l, and the valve 37o is biased toward the first opening 37l by a coil spring (biasing member) 37p housed in the biasing member housing 39q. ing. The biasing member accommodating portion 39q is closed with a screw 37r, and one end of the coil spring 37p is supported by the screw 37r.

Next, the operation of the speed adjustment unit 36 of this embodiment will be described.
When an allowable torque in the direction of arrow B in FIG. 30A (the descending direction of the shielding material) is applied to the winding shaft 10, the torque is transmitted to the moving member 39 through the drive shaft 12 and the central shaft 38, and the moving member 39 Moves in the direction of the arrow X, and a braking force is generated by the flow resistance of oil in the gap between the outer periphery of the moving member and the inner peripheral surface of the housing to operate the shielding device at a suppressed speed. At that time, the internal pressure in the accommodation space 40a on the traveling direction side of the moving member 39 increases. When the force in the arrow X direction applied to the valve 37o by the increased internal pressure exceeds the urging force applied to the valve 37o by the coil spring 37p, the valve 37o moves in the arrow X direction until the valve is opened within the allowable torque. It does not lead to. When a torque greater than the allowable torque is applied to the central shaft 38 of the speed adjusting unit 36 by the external force or the like during the lowering of the shielding material, the valve 37o reaches a position where the internal pressure of the accommodation space 40a exceeds a predetermined threshold and the first opening 37l opens. The oil moves through the first opening 37l, the oil flow passage 37m, and the second opening 37n, the internal pressure in the accommodation space 40a is reduced, and excessive pressure is prevented from being generated. When the excessive pressure is removed, the valve 37o is automatically closed by the biasing force of the coil spring 37p, and the brake force is restored within the allowable torque range.

An internal pressure limiter that operates based on an increase in internal pressure in the accommodation space 40 a may be provided in the moving member 39. Furthermore, an internal pressure limiter that operates based on an increase in the internal pressure of the accommodation space 40b when the moving member 39 moves in the direction opposite to the arrow X may be provided.
-Even if it is other than the above-described form, if an opening / closing structure capable of inflowing oil from the pressure side accommodating part to the pressure reducing side accommodating part when excessive torque to the brake is generated, it will be in another aspect. It can be replaced.

<Nineteenth embodiment>
A nineteenth embodiment of the present invention will be described with reference to FIGS. This embodiment is similar to the fifth embodiment, and is mainly different in that a portion (non-threaded portion) 38e having no male screw portion 38a is provided on the central shaft 38. Hereinafter, the difference will be mainly described.

In the present embodiment, as shown in FIG. 31, the central shaft 38 is provided with a male screw portion 38 a over almost the entire portion except for a portion close to the left end of the accommodation space 40, and is not provided at the left end of the accommodation space 40. A screw portion 38e is provided. When the bottom rail 5 is at a high position, the moving member 39 is screwed into the male screw portion 38a, and the central shaft 38 rotates as the bottom rail 5 is lowered by its own weight, so that the moving member 39 is moved in the arrow X direction. Moving. The inner surface 37a of the housing 37 is tapered as in the first embodiment, and the resistance force that the moving member 38 receives from the oil as the bottom rail 5 is lowered is reduced.

When the moving member 39 reaches the non-threaded portion 38e, the screwing between the moving member 39 and the male screw portion 38a is released. In this state, even if the central shaft 38 is further rotated in the descending direction of the bottom rail 5, the moving member 39 does not move.

Since the moving member 39 is urged toward the male screw portion 38a by the urging member (e.g., coil spring) 58, when the central shaft 38 is rotated in the upward direction of the bottom rail 5, the moving member 39 is again turned on. It is screwed into the male screw portion 38a and moves toward the right end of the accommodation space 40 as the bottom rail 5 is raised.

The speed adjusting unit 36 of the present embodiment is characterized in that it can be easily incorporated into the head box 1. Hereinafter, a method of incorporating the speed adjusting unit 36 into the head box 1 will be described with reference to FIGS.

First, as shown in FIG. 32A, the speed adjustment unit 36 is attached in the head box 1 with the bottom rail 5 raised to the upper limit position. At this time, the moving member 39 is disposed in the screwless portion 38e.
Next, as shown in FIG. 32B, the bottom rail 5 is lowered to the lowest limit. At this time, the drive shaft 12 and the central shaft 38 rotate in the descending direction along with the rotation of the winding shaft 10. However, since the moving member 39 is already arranged in the screwless portion 38e, the central shaft 38 is rotated. However, the moving member 39 does not move.

32. When the drive shaft 12 is rotated in the upward direction of the bottom rail 5 from the state shown in FIG. 32 (b), the central shaft 38 is also rotated in the same direction. Since the moving member 39 is urged by the urging member 58, when the central shaft 38 is rotated in the upward direction of the bottom rail 5, the moving member 39 is immediately screwed into the male screw portion 38a, and the bottom rail As 5 rises, it moves in the direction of arrow Y in FIG. When the bottom rail 5 is lowered again, the moving member 39 moves in the direction of the arrow X in FIG. 31, and when the bottom rail 5 reaches the lowest limit, the moving member 39 reaches the screwless portion 38e.

As described above, by providing the screwless portion 38e, the position of the moving member 39 when the bottom rail 5 is at the lowest limit even when the speed adjusting portion 36 is mounted in the head box 1 at the upper limit position of the bottom rail 5. Can be set accurately. The speed adjusting unit 36 may be attached to the head box 1 at a position other than the upper limit position of the bottom rail 5. Further, the moving member 39 only needs to reach the unthreaded portion 38e until the bottom rail 5 reaches the lowest limit. Therefore, when the speed adjusting portion 36 is mounted in the head box 1, the moving member 39 is not necessarily placed on the unthreaded portion 38e. It may not be arranged. That is, when the speed adjusting unit 36 is attached to the head box 1, the moving member 39 is disposed on the male screw portion 38a, and the moving member 39 moves toward the non-threaded portion 38e as the bottom rail 5 is lowered. Thus, the moving member 39 may reach the non-threaded portion 38e until the bottom rail 5 reaches the lowest limit. Even in this case, the position of the moving member 39 when the bottom rail 5 is at the lowest limit can be accurately set.

In another expression, in the present embodiment, the speed adjustment unit 36 includes a non-moving region (no screw portion) in which the moving member 39 does not move even when the winding shaft 10 rotates in the descending direction of the bottom rail 5. When the winding shaft 10 rotates in the ascending direction of the bottom rail 5 while the moving member 39 is in the non-moving region, the moving member 39 moves with the rotation of the winding shaft 10. By configuring the speed adjusting unit 36 in this way, an effect is obtained that the position of the moving member 39 when the bottom rail 5 is at the lowest limit can be accurately set.

<20th Embodiment>
A twentieth embodiment of the present invention will be described with reference to FIGS. In the present embodiment, the speed adjusting unit 36 is used to adjust the rising speed when the roll screen is automatically raised. Details will be described below.

In the roll screen shown in FIG. 34, support brackets 62a and 62b are attached to both ends of a mounting frame 61 that is attached to the upper frame of a window or the like via a mounting bracket, and a winding shaft is provided between the support brackets 62a and 62b. 63 is rotatably supported.

A screen 64 is suspended from the winding shaft 63, a weight bar 64a is attached to the lower end of the screen 64, and an operation string 64b is suspended from the weight bar 64a. Then, the screen 64 is raised and lowered based on the rotation of the winding shaft 63.

In the winding shaft 63, an urging device 80 for applying a rotational force in the pulling direction of the screen 64 to the winding shaft 63, and a speed adjusting unit for controlling the rotational speed of the winding shaft based on the rotational force to a predetermined speed. 36 and a clutch device 70 that maintains the screen 64 in a desired lowered position against the rotational force applied by the biasing device 80 are incorporated.

A specific configuration of the urging device 80 will be described. As shown in FIG. 35, a wind plug 65 supported non-rotatably with respect to the support bracket 62a is disposed on one side of the winding shaft 63. One end of a torsion coil spring 66 is fixed to the wind plug 65.

One end of a guide pipe 67 is fixed to the center of the wind plug 65, and the guide pipe 67 is inserted into the torsion coil spring 66. A pipe stopper 68 is fitted and fixed to the other end of the guide pipe 67, and a drive plug 69 fitted to the inner peripheral surface of the take-up shaft 63 is rotatably supported by the pipe stopper 68. The other end of the torsion coil spring 66 is fixed to 69.

When the winding shaft 63 is rotated in the descending direction of the screen 64, the drive plug 69 is rotated integrally with the winding shaft 63, and the torsion coil spring 66 is stored, and the torsion coil spring 66 is stored. When the winding shaft 63 is rotated in the screen pulling direction by the urging force, the torsion coil spring 66 is de-energized.

As shown in FIG. 36, a clutch device 70 is disposed at the other end of the winding shaft 63. The clutch device 70 moves the screen 64 to a desired position against the biasing force of the torsion coil spring 66 by releasing the operation cord 64b while operating the operation cord 64b to lower the screen 64 to a desired position. To maintain. Further, if the operating string 64b is operated to slightly lower the screen 64 from that state, the operation of the clutch device 70 is released and the screen 64 is pulled up based on the urging force of the torsion coil spring 66. ing.

A speed adjusting unit 36 is disposed in the winding shaft 63 adjacent to the clutch device 70. The speed adjustment unit 36 includes a housing 37 and a central shaft 38 that is inserted into the housing 37. The housing 37 is fixed to the take-up pipe. The housing 37 is rotated integrally with the winding shaft 63. The end of the central shaft 38 is fixed to a fixed shaft. For example, it may be fitted to the drum 76 of the clutch device 70 as shown in FIG. The drum 76 is a fixed shaft because it is supported so as not to rotate with respect to the support bracket 62b, and the center shaft 38 is supported so as not to rotate with respect to the support bracket 62b.

Incidentally, when the torsional rotational speed of the spring motor accompanying the rewinding rotation of the winding shaft 63 increases, the torque generated by the urging device 80 increases as indicated by Ts in FIG. On the other hand, as the screen 64 moves toward the lower limit, the torque applied to the take-up shaft 63 by the dead weight of the screen 64 increases as indicated by Tw in FIG. When the screen 64 approaches the upper limit position, the torque gap TG, which is the difference between Ts and Tw, increases, and the weight bar 64a provided at the lower end of the screen 64 vigorously collides with the mounting frame 61 to generate noise. Cheap. Therefore, in the roll screen according to the present embodiment, the speed adjustment unit 36, when the weight bar 64a is pulled up to the vicinity of the upper limit and reaches the braking force further increasing region P as shown in FIG. It is configured to increase power. As described above, in the present embodiment, the braking force is increased or decreased in multiple stages in accordance with the increasing or decreasing tendency of the torque gap that changes for each opening / closing position during automatic operation in the shielding device. In the roll screen, the braking force is increased from the upper limit by a predetermined number of rotations.

Here, the configuration of the speed adjustment unit 36 of the present embodiment will be described with reference to FIG. The configuration of the speed adjustment unit 36 of the present embodiment is similar to the speed adjustment unit 36 of the first embodiment, and the shape of the inner surface 37a of the housing 37 is different. Specifically, in the speed adjusting unit 36 of the present embodiment, the inner surface 37a is not tapered, and the gap 41 between the moving member 39 and the housing 37 is narrowed when the weight bar 64a reaches the vicinity of the upper limit. It is configured as follows. More specifically, when the weight bar 64a is at the lower limit position, the moving member 39 is located in the vicinity of the left end in the accommodation space 40 as shown in FIG. When the winding shaft 63 is rotated by the biasing force of the biasing device 80, the screen 64 is wound around the winding shaft 63, the weight bar 64a starts to rise, the housing 37 is rotated, and the moving member 39 is moved to the arrow. Move in the X direction. In this state, since the gap 41 between the moving member 39 and the housing 37 is large, the oil flow resistance is small, and therefore the braking force by the speed adjusting unit 36 is small. When the winding shaft 63 further rotates to further wind up the screen 64 and the weight bar 64a is in a state immediately before the lifting of the weight bar 64a, the moving member 39 is a brake comprising a small diameter portion 37b in the vicinity of the right end of the accommodation space 40. It reaches the force increasing region P. When reaching the region P, the gap 41 between the moving member 39 and the housing 37 becomes narrow, so that the oil flow resistance increases and the braking force by the speed adjusting unit 36 increases.

<Twenty-first embodiment>
A twenty-first embodiment of the present invention will be described with reference to FIG. In the present embodiment, another configuration for increasing the braking force of the speed adjusting unit 36 when the weight bar 64a is pulled up to the vicinity of the upper limit in the same roll screen as in the twentieth embodiment is disclosed. Details will be described below.

The speed adjustment unit 36 of the present embodiment has the same configuration as that of the fifth embodiment except that the shape of the groove 53 is different. In the fifth embodiment, since the groove 53 is linear in the developed view shown in FIG. 8B, the through hole 39d of the main body 39a is gradually closed as the moving member 39 moves, so that the oil In this embodiment, the groove 53 is parallel to the moving direction of the moving member 39 in the range from the position S to the position T as shown in FIG. Therefore, until the moving member 39 moves from the position S to the position T, the through hole 39d is maintained open as shown in FIG. Is small. Since the inclination angle of the groove 53 is large in the range from the position T to the position U, the through hole 39d is closed while the moving member 39 moves in this range, and the state shown in FIG. The braking force by the part 36 increases. For this reason, the region between the position T and the position V is the braking force further increasing region P. Accordingly, by configuring the moving member 39 to reach the position U when the state just before the completion of the lifting of the weight bar 64a is reached, the braking force by the speed adjusting unit 36 is rapidly increased immediately before the lifting of the weight bar 64a. Can be made.

<Other embodiments>
The configurations disclosed in the first to nineteenth embodiments can be applied to a roll screen as long as it is not contrary to the gist.

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 33: Pitch holding cord 36 : Speed adjustment part 37: housing 38: central axis 39: moving member 40: accommodating space 41: gap

Claims (18)

1. A shielding device that opens and closes a shielding material by rotation of a winding shaft,
   A speed adjusting unit for adjusting an automatic moving speed of the shielding material;
   The speed adjusting unit includes a housing that contains the viscous fluid, and a moving member that is accommodated in the housing and moves as the winding shaft rotates, and the moving member moves as the moving member moves. A shielding device configured to change a resistance force received from the viscous fluid.
2. The speed adjustment unit is configured such that the moving member is capable of reciprocating relative movement within a certain range in conjunction with the opening / closing range of the shielding material within the housing, and the resistance force that the moving member receives from the viscous fluid is The shielding apparatus according to claim 1, wherein the shielding apparatus is configured to change depending on a position within the certain range.
3. The shielding apparatus according to claim 2, wherein the speed adjustment unit is configured such that a minimum position of driving torque in an opening / closing range of the shielding material is a minimum position of the resistance force within the certain range.
4. The shielding according to claim 2 or 3, wherein the speed adjustment unit is configured such that a maximum position of a driving torque in an opening / closing range of the shielding material is a maximum position of the resistance force within the certain range. apparatus.
5. The speed adjusting unit may change a cross-sectional area of the flow path through which the viscous fluid can pass through the moving member, detour from a larger flow path, or move the flow path through the movement member. The shielding apparatus according to any one of claims 1 to 4, wherein at least one elastic coefficient of a constituent member is changed.
6. When the moving member moves in the first direction when automatically moving the shielding material, the speed adjusting unit causes the viscous fluid flow resistance to move in a second direction opposite to the first direction. 6. The shielding device according to claim 1, wherein the shielding device is configured to be larger than a flow resistance of the viscous fluid.
7. The speed adjusting unit is configured to change a moving distance of the moving member per unit rotation of the take-up shaft as the moving member moves. The shielding apparatus as described in.
8. The speed adjustment unit switches between a linked state in which the rotation of the winding shaft and the movement of the moving member are linked and an unlinked state in which the rotation of the winding shaft and the movement of the moving member are not linked. The shielding apparatus according to any one of claims 1 to 7, wherein the shielding apparatus is configured to be possible.
9. 9. A brake force increasing means for increasing a brake force applied to the winding shaft in a brake force increasing range which is a part of a movable range of the moving member is provided in the housing. The shielding apparatus as described in one.
10. The shielding device according to claim 9, wherein the brake force increasing means is configured to form a piston structure with the moving member when the moving member is within the brake force increasing range.
11. The said braking force increase means is a rotation resistor which increases the said braking force by rotating with the rotation of the said winding shaft, when the said moving member exists in the said braking force increase range, The shielding apparatus according to claim 10.
12. The moving member is configured to move while rotating as the winding shaft rotates,
    The shielding device according to claim 11, wherein the rotation resistor is configured to rotate together with the moving member by being engaged with the moving member when the moving member is within the braking force increase range. .
13. In conjunction with the opening / closing range of the shielding material, the moving member has a first resistance portion and a second resistance portion that generate a resistance force received from the viscous fluid, and at least one of the first resistance portion and the second resistance portion The shielding device according to any one of claims 1 to 12, wherein the shielding device is configured to change a resistance force received from the viscous fluid within an opening / closing range of the shielding material.
14. The speed adjusting unit includes an internal pressure limiter that operates when a torque applied to the winding shaft exceeds a predetermined threshold value or an internal pressure of the housing exceeds a predetermined threshold value, and reduces the internal pressure of the housing. The shielding apparatus according to any one of claims 1 to 13.
15. The speed adjusting unit includes a non-moving region where the moving member does not move even when the winding shaft rotates in the descending direction of the shielding material, and the winding shaft is in a state where the moving member is in the non-moving region. The shielding device according to any one of claims 1 to 14, wherein when the shielding member rotates in the upward direction of the shielding member, the moving member moves with the rotation of the winding shaft.
16. The shielding device rotates the winding shaft by its own weight, thereby rewinding the lifting / lowering cord having one end attached to the shielding material from the winding shaft, thereby automatically removing the shielding material. Configured to descend,
    The shielding device according to any one of claims 1 to 15, wherein the speed adjustment unit is configured such that the resistance force decreases as the shielding material descends.
17. The shielding apparatus according to claim 16, wherein a thrust applying unit that applies a thrust to the moving member by rotating and moving together with the moving member as the winding shaft rotates is provided in the housing.
18. The shielding device is configured to automatically raise the shielding material by rotating the winding shaft by an urging force of an urging device and winding the shielding material on the winding shaft,
    The shielding according to any one of claims 1 to 14, wherein the speed adjusting unit is configured to increase the resistance when the shielding material is raised to a position near an upper limit position thereof. apparatus.

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