WO2016009881A1 - Dispositif de blindage - Google Patents

Dispositif de blindage Download PDF

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Publication number
WO2016009881A1
WO2016009881A1 PCT/JP2015/069450 JP2015069450W WO2016009881A1 WO 2016009881 A1 WO2016009881 A1 WO 2016009881A1 JP 2015069450 W JP2015069450 W JP 2015069450W WO 2016009881 A1 WO2016009881 A1 WO 2016009881A1
Authority
WO
WIPO (PCT)
Prior art keywords
moving member
shielding
winding shaft
housing
speed
Prior art date
Application number
PCT/JP2015/069450
Other languages
English (en)
Japanese (ja)
Inventor
万人 山岸
将哉 山口
翼 阿坂
武信 江波戸
Original Assignee
立川ブラインド工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2015021647A external-priority patent/JP6403592B2/ja
Application filed by 立川ブラインド工業株式会社 filed Critical 立川ブラインド工業株式会社
Priority to CN201580048522.1A priority Critical patent/CN106687658B/zh
Priority to CA2987009A priority patent/CA2987009A1/fr
Priority to US15/326,064 priority patent/US10294719B2/en
Publication of WO2016009881A1 publication Critical patent/WO2016009881A1/fr

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05F—DEVICES FOR MOVING WINGS INTO OPEN OR CLOSED POSITION; CHECKS FOR WINGS; WING FITTINGS NOT OTHERWISE PROVIDED FOR, CONCERNED WITH THE FUNCTIONING OF THE WING
    • E05F5/00—Braking devices, e.g. checks; Stops; Buffers
    • E05F5/02—Braking devices, e.g. checks; Stops; Buffers specially for preventing the slamming of swinging wings during final closing movement, e.g. jamb stops
    • E—FIXED CONSTRUCTIONS
    • E06—DOORS, WINDOWS, SHUTTERS, OR ROLLER BLINDS IN GENERAL; LADDERS
    • E06B—FIXED OR MOVABLE CLOSURES FOR OPENINGS IN BUILDINGS, VEHICLES, FENCES OR LIKE ENCLOSURES IN GENERAL, e.g. DOORS, WINDOWS, BLINDS, GATES
    • E06B9/00—Screening or protective devices for wall or similar openings, with or without operating or securing mechanisms; Closures of similar construction
    • E06B9/24—Screens or other constructions affording protection against light, especially against sunshine; Similar screens for privacy or appearance; Slat blinds
    • E06B9/26—Lamellar or like blinds, e.g. venetian blinds
    • E06B9/28—Lamellar or like blinds, e.g. venetian blinds with horizontal lamellae, e.g. non-liftable
    • E06B9/30—Lamellar or like blinds, e.g. venetian blinds with horizontal lamellae, e.g. non-liftable liftable
    • E06B9/32—Operating, guiding, or securing devices therefor
    • E06B9/322—Details of operating devices, e.g. pulleys, brakes, spring drums, drives
    • E—FIXED CONSTRUCTIONS
    • E06—DOORS, WINDOWS, SHUTTERS, OR ROLLER BLINDS IN GENERAL; LADDERS
    • E06B—FIXED OR MOVABLE CLOSURES FOR OPENINGS IN BUILDINGS, VEHICLES, FENCES OR LIKE ENCLOSURES IN GENERAL, e.g. DOORS, WINDOWS, BLINDS, GATES
    • E06B9/00—Screening or protective devices for wall or similar openings, with or without operating or securing mechanisms; Closures of similar construction
    • E06B9/56—Operating, guiding or securing devices or arrangements for roll-type closures; Spring drums; Tape drums; Counterweighting arrangements therefor
    • E06B9/80—Safety measures against dropping or unauthorised opening; Braking or immobilising devices; Devices for limiting unrolling
    • E06B9/82—Safety measures against dropping or unauthorised opening; Braking or immobilising devices; Devices for limiting unrolling automatic

Definitions

  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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. .
  • 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.
  • 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.
  • 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.
  • 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.
  • FIG. 1st Embodiment of this invention 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
  • 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.
  • FIG. 37 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.
  • 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.
  • 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.
  • 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.
  • FIG. 37 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.
  • 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.
  • 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.
  • 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.
  • FIG. 37 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.
  • (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).
  • a pitch holding cord 33 for holding the pitch of the folds of the screen 4 is provided between the head box 1 and the bottom rail 5.
  • 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.
  • 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.
  • the stopper device 24 stops the rotation of the drive shaft 12 and prevents the bottom rail 5 from dropping its own weight.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the moving member 39 and the housing 37 are relatively movable in the axial direction and not relatively rotatable.
  • 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.
  • the moving member 39 moves in the arrow X direction by the rotation in the arrow B direction in FIG.
  • 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.
  • 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.
  • 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.
  • 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.
  • the inner surface 37a of the housing 37 of the speed adjusting portion 36 is tapered as shown in FIGS.
  • the moving member 39 moves in the direction of the arrow X.
  • the gap 41 gradually increases, the oil flow resistance gradually decreases.
  • 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.
  • 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.
  • 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.
  • the stopper device 24 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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).
  • the lifting cord 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.
  • 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.
  • 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.
  • a structure that generates power by a spring motor of a torsion coil spring is generally used. Is.
  • 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.
  • 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).
  • 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.
  • 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.
  • 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.
  • 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.
  • 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).
  • the taper shape may be set so as to be a brake force gradient that approximates the gradient of the torque gap.
  • 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.
  • the moving member 39 is screwed to the central shaft 38 and is slidably engaged with the housing 37.
  • 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.
  • 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).
  • the main difference is that the moving member 39 includes an internal flow passage 43 and a valve member 44.
  • the difference will be mainly described.
  • 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.
  • the moving member 39 moves in the direction of the arrow X.
  • 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.
  • 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.
  • the valve is opened by rotation to the side (down direction) where speed control is not performed.
  • 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).
  • the valve is opened by rotation to the side where the speed is not controlled (closing direction).
  • 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.
  • the difference will be mainly described.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the number of concave portions 46 arranged around the moving member 39 increases.
  • the cross-sectional area of the oil flow passage increases, and the oil flow resistance is reduced.
  • 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.
  • the elastic coefficient of the inner surface 37a of the housing 37 is changed along the moving direction of the moving member 39.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the oil flow passage is provided between the housing 37 and the moving member 39.
  • the gap 51 between the moving member 39 and the fixed shaft 49 is the main oil. It becomes a flow passage.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the protrusion 39c moves along the groove 53, whereby the movable plate 39b rotates.
  • the through hole 39d is gradually opened, the oil flow resistance is reduced, and the braking force is shown in FIG.
  • 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.
  • FIG. 6 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.
  • 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.
  • 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.
  • 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.
  • the tip 39g moves along the groove 54 as the moving member 39 moves in the arrow X direction.
  • 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.
  • 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.
  • 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.
  • 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.
  • the magnet of the housing 37 is disposed on the outer periphery of the housing 37.
  • 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.
  • 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.
  • 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.
  • the moving member 39 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.
  • 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.
  • 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.
  • FIG. 9 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.
  • 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.
  • 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.
  • 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.
  • the gap becomes narrower toward the right end of FIG.
  • 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.
  • the central shaft 38 does not penetrate the housing 37, but may be configured to penetrate the housing 37.
  • 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).
  • a damper torque is not generated or significantly reduced for rotation to a side where speed control is not performed.
  • 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.
  • 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.
  • 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.
  • the valve is opened by rotation to the side where the speed control is not performed (in the raising direction).
  • 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).
  • opening 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).
  • closing 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).
  • 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
  • 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.
  • 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.
  • 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.
  • the braking force is decreased from the lower limit by a predetermined multiple number of revolutions.
  • 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.
  • the bottom rail 5 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.
  • 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.
  • the spiral groove 38b 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.
  • 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.
  • 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.
  • 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.
  • the difference will be mainly described.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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
  • 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.
  • 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.
  • the difference will be mainly described.
  • the center shaft 38 is provided with a flange 72
  • 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.
  • the “braking force increasing means” recited in the claims is configured by the flange 72 and the recess 39w.
  • 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.
  • 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.
  • This embodiment is also an embodiment in the following aspects.
  • (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.
  • the braking force can be gradually reduced or increased over the entire length from the braking force increase range.
  • a cylindrical member 77 is disposed in the housing 37, and the cylindrical structure 77 and the recess 39w constitute a piston structure. Good.
  • 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.
  • 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.
  • the speed adjusting unit 36 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.
  • 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 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 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.
  • FIGS. 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.
  • the thrust applying means is a screw 39aa provided on the moving member 39.
  • the difference will be mainly described.
  • 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.
  • the driving torque decreases as the shielding material approaches 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.
  • 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.
  • 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.
  • 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.
  • the thrust generated by the rotation of the screw 39aa is increased, so that the braking force is further reduced.
  • 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.
  • 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 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.
  • 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.
  • 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.
  • the internal pressure of the accommodation space 40a is reduced and the generation of excessive pressure is prevented.
  • 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.
  • 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.
  • the internal pressure of the housing 37 is reduced and excessive pressure is prevented from being generated. .
  • 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.
  • 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.
  • the user may forcibly lower the shielding material or the user may be caught by the shielding material.
  • excessive torque in the descending direction of the shielding material is applied to the winding shaft 10.
  • 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.
  • 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. .
  • 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.
  • the difference will be mainly described.
  • the valve 37o moves in the arrow X direction until the valve is opened within the allowable torque. It does not lead to.
  • 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.
  • 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.
  • 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.
  • the moving member 39 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 urging member e.g., coil spring
  • the speed adjusting unit 36 of the present embodiment is characterized in that it can be easily incorporated into the head box 1.
  • a method of incorporating the speed adjusting unit 36 into the head box 1 will be described with reference to FIGS.
  • the speed adjustment unit 36 is attached in the head box 1 with the bottom rail 5 raised to the upper limit position.
  • the moving member 39 is disposed in the screwless portion 38e.
  • the bottom rail 5 is lowered to the lowest limit.
  • the drive shaft 12 and the central shaft 38 rotate in the descending direction along with the rotation of the winding shaft 10.
  • the moving member 39 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.
  • 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.
  • the moving member 39 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.
  • 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.
  • 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.
  • the moving member 39 moves with the rotation of the winding shaft 10.
  • ⁇ 20th Embodiment> A twentieth embodiment of the present invention will be described with reference to FIGS.
  • the speed adjusting unit 36 is used to adjust the rising speed when the roll screen is automatically raised. Details will be described below.
  • 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.
  • 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.
  • 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.
  • 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.
  • the torsion coil spring 66 is de-energized.
  • 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.
  • 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.
  • 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.
  • 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.
  • the braking force is increased from the upper limit by a predetermined number of rotations.
  • 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.
  • the winding shaft 63 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.
  • the moving member 39 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.
  • 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.
  • the through hole 39d of the main body 39a is gradually closed as the moving member 39 moves, so that the oil
  • 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.
  • 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.
  • 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Operating, Guiding And Securing Of Roll- Type Closing Members (AREA)
  • Blinds (AREA)

Abstract

La présente invention a pour but de fournir un dispositif de blindage ayant une unité d'ajustement de vitesse qui peut ajuster automatiquement la vitesse de mouvement d'un matériau de blindage à l'aide d'une configuration simple, et avec lequel un bruit pendant le fonctionnement est supprimé. Pour atteindre ce but, la présente invention concerne un dispositif de blindage dans lequel un matériau de blindage est ouvert et fermé par rotation d'un arbre d'enroulement. Le dispositif de blindage est pourvu d'une unité d'ajustement de vitesse pour ajuster automatiquement la vitesse de mouvement du matériau de blindage. L'unité d'ajustement de vitesse est pourvu : d'un boîtier pour recevoir un fluide visqueux ; d'un élément mobile qui est logé à l'intérieur du boîtier et qui se déplace en fonction de la rotation de l'arbre d'enroulement. En outre, l'unité d'ajustement de vitesse est configurée de telle sorte que la force de résistance que l'élément mobile reçoit du fluide visqueux se modifie en fonction du mouvement de l'élément mobile.
PCT/JP2015/069450 2014-07-14 2015-07-06 Dispositif de blindage WO2016009881A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN201580048522.1A CN106687658B (zh) 2014-07-14 2015-07-06 遮蔽装置
CA2987009A CA2987009A1 (fr) 2014-07-14 2015-07-06 Dispositif de blindage
US15/326,064 US10294719B2 (en) 2014-07-14 2015-07-06 Shielding apparatus

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
JP2014-144524 2014-07-14
JP2014144524 2014-07-14
JP2014246823 2014-12-05
JP2014-246823 2014-12-05
JP2015021647A JP6403592B2 (ja) 2014-05-02 2015-02-05 遮蔽装置
JP2015-021647 2015-02-05

Publications (1)

Publication Number Publication Date
WO2016009881A1 true WO2016009881A1 (fr) 2016-01-21

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ID=55078378

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2015/069450 WO2016009881A1 (fr) 2014-07-14 2015-07-06 Dispositif de blindage

Country Status (1)

Country Link
WO (1) WO2016009881A1 (fr)

Cited By (6)

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Publication number Priority date Publication date Assignee Title
EP3199744A1 (fr) * 2016-01-29 2017-08-02 Nien Made Enterprise Co., Ltd. Système de couverture de fenêtre et son dispositif de commande de déplacement associé
US10302172B2 (en) 2016-01-22 2019-05-28 Nien Made Enterprise Co., Ltd. Window covering system and window covering control assembly thereof
US10501985B2 (en) 2016-04-06 2019-12-10 Nien Made Enterprise Co., Ltd. System and device for window covering
US10612299B2 (en) 2016-01-22 2020-04-07 Nien Made Enterprise Co., Ltd. Control device of window covering system
US10900280B2 (en) 2017-09-20 2021-01-26 Hunter Douglas Inc. Architectural structure covering having a speed regulating assembly
TWI790546B (zh) * 2021-02-09 2023-01-21 慶豐富實業股份有限公司 電動窗簾下降防堵的控制方法

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JPH09256729A (ja) * 1996-03-19 1997-09-30 Kuriki Seisakusho:Kk 引戸の閉鎖装置
JPH11270257A (ja) * 1997-12-12 1999-10-05 Hunter Douglas Internatl Nv 建築物遮蔽体用ワインディング機構
JP2004518923A (ja) * 2001-03-13 2004-06-24 ジュリウス ブルム ゲゼルシャフト エム．ビー．エイチ． 流体ダンパー、とくに家具の可動部分のための流体ダンパー
JP2005232841A (ja) * 2004-02-20 2005-09-02 Shin Nippon Air Technol Co Ltd 扉の開閉補助装置
JP2007063884A (ja) * 2005-09-01 2007-03-15 Toyota Auto Body Co Ltd 車両用ドア開閉装置

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Publication number Priority date Publication date Assignee Title
JPH09256729A (ja) * 1996-03-19 1997-09-30 Kuriki Seisakusho:Kk 引戸の閉鎖装置
JPH11270257A (ja) * 1997-12-12 1999-10-05 Hunter Douglas Internatl Nv 建築物遮蔽体用ワインディング機構
JP2004518923A (ja) * 2001-03-13 2004-06-24 ジュリウス ブルム ゲゼルシャフト エム．ビー．エイチ． 流体ダンパー、とくに家具の可動部分のための流体ダンパー
JP2005232841A (ja) * 2004-02-20 2005-09-02 Shin Nippon Air Technol Co Ltd 扉の開閉補助装置
JP2007063884A (ja) * 2005-09-01 2007-03-15 Toyota Auto Body Co Ltd 車両用ドア開閉装置

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10302172B2 (en) 2016-01-22 2019-05-28 Nien Made Enterprise Co., Ltd. Window covering system and window covering control assembly thereof
US10428899B2 (en) 2016-01-22 2019-10-01 Nien Made Enterprise Co., Ltd. Window covering system and window covering control apparatus thereof
US10451145B2 (en) 2016-01-22 2019-10-22 Nien Made Enterprise Co., Ltd. System and device for window covering system
US10612299B2 (en) 2016-01-22 2020-04-07 Nien Made Enterprise Co., Ltd. Control device of window covering system
EP3199744A1 (fr) * 2016-01-29 2017-08-02 Nien Made Enterprise Co., Ltd. Système de couverture de fenêtre et son dispositif de commande de déplacement associé
AU2017200374B2 (en) * 2016-01-29 2018-02-15 Nien Made Enterprise Co., Ltd. Window covering system and displacement controlling device thereof
US10731408B2 (en) 2016-01-29 2020-08-04 Nien Made Enterprise Co., Ltd. Window covering system and displacement controlling device thereof
US10501985B2 (en) 2016-04-06 2019-12-10 Nien Made Enterprise Co., Ltd. System and device for window covering
US10533371B2 (en) 2016-04-06 2020-01-14 Nien Made Enterprise Co., Ltd. System and device for window covering
US10900280B2 (en) 2017-09-20 2021-01-26 Hunter Douglas Inc. Architectural structure covering having a speed regulating assembly
TWI790546B (zh) * 2021-02-09 2023-01-21 慶豐富實業股份有限公司 電動窗簾下降防堵的控制方法

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