JP6986411B2 - Vertical blind operation mechanism - Google Patents

Description

The present invention relates to a mechanism for operating a vertical blind suitable for tilted mounting on the upper edge of a window frame of a slanted window or on a wall surface or ceiling above the slanted window.

Conventionally, an inclined screw rod is rotatably supported in the head rail, and the louvers are suspended from a plurality of carriers that can move in the head rail by the rotation of the screw rod, and the carriers are moved by the operation of the operation unit. An operating device for an inclined vertical blind configured as described above is disclosed (see, for example, Patent Document 1). The tilting vertical blind operating device includes a one-way clutch means that converts the operation of the operating unit into the rotation of the screw rod while blocking the rotation from the screw rod. This one-way clutch means prevents the pulley to which the operation code constituting the operation unit is hung, the clutch drum that rotates integrally with the pulley and the screw rod, and the clutch drum in the direction in which the carrier descends. It has a clutch spring that allows the clutch drum to rotate in the direction in which the carrier rises, and a clutch spring releasing means that releases the function of the clutch spring that prevents the clutch drum from rotating in the direction in which the carrier descends. Further, the clutch spring releasing means can be operated by operating one side of the operation cord, and the operation of one side of the operation cord allows the clutch spring to rotate the clutch drum in the direction in which the carrier descends.

In the operating device of the vertical blind for tilting configured in this way, since the screw rod is tilted, the carrier moves downward along the screw of the screw rod due to the weight of the louver, and the screw corresponds accordingly. Although the rod tries to rotate, the one-way clutch means prevents the screw rod from rotating. Therefore, the carrier cannot move and maintains its stop position. At this time, even if the lead angle of the screw rod is large, the stop position of the carrier can be maintained, so that the moving distance of the carrier with respect to one rotation of the screw rod can be increased, that is, when the carrier is moved, The carrier can be moved with a small amount of operation by the operation unit, and the operability is good. Further, since the clutch spring prevents the carrier from rotating in the descending direction, the carrier tends to descend due to the weight of the louver, so that even if the screw rod and the clutch drum try to rotate in that direction, the clutch spring Prevents its rotation. Further, when moving the carrier in the upward direction, the clutch spring allows the clutch drum to rotate in that direction. Therefore, when the pulley is rotated to rotate the screw rod and the carrier is moved in the downward direction, the pulley is rotated. The screw rod can be rotated by operating the clutch spring releasing means by the operation code and allowing the clutch spring to rotate the clutch drum by the clutch spring releasing means.

Japanese Patent No. 3908200 (Claim 1, paragraph [0009], [0011], [0012], FIG. 1, FIG. 3, FIG. 4).

However, in the operation device for the vertical blind for inclination shown in the above-mentioned conventional patent document 1, when the size of the blind is increased or the inclination angle is increased, the operation force for moving the louver to the upper side of the inclined window is increased. There was a problem that the operability was deteriorated due to the extremely large size.

The first object of the present invention is that even if the blind becomes large or the tilt angle of the window frame or the like increases, the operating force for moving the louver is only slightly increased, and the deterioration of operability can be suppressed. , To provide an operating mechanism for vertical blinds. A second object of the present invention is to prevent a plurality of louvers from unintentionally moving downward due to their own weight, such as a window frame, and without using a one-way clutch means or a clutch spring releasing means. It is an object of the present invention to provide a vertical blind operation mechanism capable of stopping a plurality of louvers at any position on the head rail. A third object of the present invention is to provide a vertical blind operation mechanism capable of adjusting tension to a driven cord to prevent slipping of the driven cord with a relatively simple operation.

As shown in FIGS. 1 to 8, the first aspect of the present invention is a head rail 11 mounted on a window frame, a wall surface, or a ceiling, and the head rail 11 accommodated in the head rail 11 and movable in the longitudinal direction of the head rail 11. The plurality of carriers 12, 13 are interposed between the head rail 11 and the plurality of carriers 12, 13, the plurality of louvers 14 suspended from the plurality of carriers 12, 13, respectively, and the plurality of carriers 12, 13. A louver moving mechanism 16 that moves along the head rail 11 to deploy or superimpose a plurality of louvers 14, a drive pulley 18 rotatably attached to one end of the head rail 11 via a drive shaft 17, and the drive pulley. In the operation mechanism of the vertical blind 10 including the loop-shaped operation code 19 wound around the 18 and the transmission mechanism 21 for transmitting the operation force of the operation code 19 to the louver movement mechanism 16, the louver movement mechanism 16 is used. The louvered driven cord 33 circulated in the head rail 11 and the tension adjusting mechanism 36 for adjusting the tension of the driven cord 33 are provided, and the tension adjusting mechanism 36 includes the tension adjusting case 37. In order to rotate the take-up pin 38 from the take-up pin 38 rotatably housed in the tension adjusting case 37 and the end portion of the driven cord 33 attached so that the take-up pin 38 can be taken up, and the opening 11a on the lower surface of the head rail 11. The operation shaft 39 provided on the louver, the take-up pin 38, and the take-up pin 38 provided on the operation shaft 39, and the take-up pin 38 and the operation shaft 39 in the direction of winding the driven cord 33 are allowed to rotate and the take-up pin is allowed to rotate. It is characterized by having a take-up pin 38 in a direction of feeding out the driven cord 33 from 38 and a feeding prevention mechanism 41 for preventing the rotation of the operating shaft 39.

In the operation mechanism of the vertical blind according to the first aspect of the present invention, the tension of the driven cord is adjusted by the tension adjusting mechanism. It is possible to prevent slipping and prevent the operation code from spinning when operating the operation code. As a result, the louver can be reliably stopped at a desired position, and the operating force of the operating cord is reliably transmitted to the driven cord.

Further, in the operation mechanism of the vertical blind according to the first aspect of the present invention, when the tension of the driven cord is adjusted at the time of manufacturing the blind, or when the driven cord is extended due to long-term use of the blind, the take-up pin is used. When an attempt is made to rotate the operation shaft in the direction in which the driven cord is wound, the take-up prevention mechanism allows the operation shaft and the take-up pin to rotate in the take-up direction, so that the take-up pin is taken up together with the operation shaft. Rotating in the direction, the driven cord of the take-up pin is taken up. Then, when the rotational force of the operation shaft in the winding direction is loosened, tension is applied to the driven cord, so that a force for rotating the winding pin in the direction of feeding the driven cord from the winding pin is applied. Acts on the take-up pin. However, since the feeding prevention mechanism prevents the winding pin and the operating shaft from rotating in the feeding direction, the winding pin and the operating shaft do not rotate in the feeding direction, and tension is applied to the driven cord. Is done. With such a relatively simple operation, the tension of the driven cord can be adjusted. As a result, similarly to the above, it is possible to prevent the driven cord from slipping due to the weight of a plurality of louvers located on the upper side of, for example, an inclined window frame, and it is possible to prevent the operation code from spinning when the operation code is operated. Therefore, the louver can be reliably stopped at a desired position, and the operating force of the operating cord is reliably transmitted to the driven cord.

It is an exploded perspective view which shows the main member of the operation mechanism of the vertical blind of this invention embodiment. It is an exploded perspective view which shows each member of a tension adjustment mechanism. It is a front view of the main part which shows the state which the tension adjustment mechanism and the leading carrier are engaged, and both ends of these driven cords are attached. FIG. 3 is a cross-sectional view showing a state in which the tension adjusting mechanism is cut along the line AA of FIG. 5A. It is sectional drawing which shows the operation of the tension adjustment mechanism when the tension adjustment mechanism is cut by the line BB of FIG. 4 and the operation shaft is turned counterclockwise. It is sectional drawing which shows the operation of the tension adjustment mechanism when the tension adjustment mechanism is cut by the line BB of FIG. 4 and the operation shaft is turned clockwise. It is sectional drawing of the main part which shows the state which the tension is always applied by the tension applying mechanism to the driven cord hung on the 1st and 2nd driven pulleys. It is a front view of the vertical blind which omitted a part of a head rail and a louver.

Next, a mode for carrying out the present invention will be described with reference to the drawings. As shown in FIGS. 1 and 8, the operation mechanism of the vertical blind 10 includes a head rail 11 attached to a window frame, a plurality of carriers 12 and 13 housed in the head rail 11, and a plurality of carriers 12. A plurality of louvers 14 suspended from each of 13, a louver moving mechanism 16 interposed between the head rail 11 and the plurality of carriers 12, 13 and rotation at one end of the head rail 11 via a drive shaft 17. It includes a drive pulley 18 that can be attached, a loop-shaped operation code 19 wound around the drive pulley 18, and a transmission mechanism 21 that transmits the operation force of the operation code 19 to the louver movement mechanism 16. Although not shown, in the attic of a detached house having a sloping roof, a substantially trapezoidal sloping window whose upper edge is sloping along the sloping roof is provided. In this embodiment, the head rail 11 is attached to the lower surface of the upper edge of the inclined window frame of the inclined window. Further, the head rail 11 includes a rail main body 22 extending along the lower surface of the upper edge of the inclined window frame of the inclined window, a housing 23 attached to the end of the inclined upper side of the rail main body 22, and the inclined rail main body 22. It has an end cap 24 attached to the lower end. Further, the housing 23 is formed into a bowl-shaped upper housing portion 23a that is inserted into the inclined upper end portion of the rail main body 22 and has an open lower surface, and a bowl-shaped upper housing portion 23a that has an open upper surface. It is composed of a lower housing portion 23b attached to the lower housing portion 23b.

On the other hand, the plurality of carriers 12 and 13 are housed in the rail main body 22 and are configured to be movable in the longitudinal direction of the rail main body 22 (FIG. 1). Further, the plurality of carriers 12 and 13 are classified into a single leading carrier 12 and the remaining plurality of subsequent carriers 13 based on the difference in shape. The leading carrier 12 is provided at the position closest to the end cap 24 among the plurality of carriers 12, 13 arranged in a row in the head rail 11. Further, in this embodiment, the leading carrier 12 is configured such that a tension adjusting mechanism 36 described later is attached and moves together with the tension adjusting mechanism 36 (FIGS. 1 and 3). The leading carrier 12 has a carrier case 12a and a pair of substantially L-shaped receiving portions 12b, 12b projecting from both outer surfaces of the carrier case 12a. The lower surfaces of the pair of receiving portions 12b, 12b are configured to slide on a pair of ridges (not shown) projecting from the inner surface of the pair of side walls 22a, 22a (FIG. 7) of the head rail 11. Further, in the carrier case 12a, a carrier-side rotating worm gear 26 including a worm 26a and a worm wheel 26b that mesh with each other to rotate the louver 14 is rotatably housed (FIG. 1). The upper part of the wheel shaft 27 is inserted into the worm wheel 26b, and the lower part of the wheel shaft 27 is projected downward from the opening 11a (FIG. 7) of the head rail 11 (FIGS. 1, 3 and 8). .. Further, the lower end of the wheel shaft 27 is connected to the upper end of the louver holding member 28 via a pin 29, and the upper end of the louver 14 is attached to the lower end of the louver holding member 28 (FIG. 8). As a result, the louver 14 is suspended from the leading carrier 12 via the worm wheel 26b, the wheel shaft 27, the pin 29, and the louver holding member 28.

Subsequent carriers 13 include a carrier case 13a formed to be narrower than the carrier case 12a of the leading carrier 12, and a pair of rolling rollers 13b rotatably attached to both outer surfaces of the carrier case 13a. , 13b and. The pair of rolling rollers 13b, 13b is configured to roll on a pair of ridges (not shown) projecting from the inner surfaces of the pair of side walls 22a, 22a of the rail body 22 (FIG. 1). Other than the above, it is configured in the same manner as the leading carrier 12. Specifically, the carrier case 13a of the subsequent carrier 13 rotatably accommodates a carrier-side rotating worm gear 26 composed of a worm 26a and a worm wheel 26b that mesh with each other to rotate the louver 14. The upper portion of the wheel shaft 27 is inserted into the worm wheel 26b, and the lower portion of the wheel shaft 27 projects downward from the opening 11a (FIG. 7) of the head rail 11 (FIGS. 1 and 8). Further, the lower end of the wheel shaft 27 is connected to the upper end of the louver holding member 28 via a pin 29, and the upper end of the louver 14 is attached to the lower end of the louver holding member 28 (FIG. 8). As a result, the louver 14 is suspended from the subsequent carrier 13 via the worm wheel 26b, the wheel shaft 27, the pin 29, and the louver holding member 28.

On the other hand, the louver moving mechanism 16 connects the loop-shaped driven cord 33, which is circulated in the head rail 11, and the adjacent carriers 12, 13 among the plurality of carriers 12, 13, which are adjacent to each other. It has a plurality of spacing control bars 34 that regulate the maximum distance between the carriers 12 and 13 (FIGS. 1 and 7). In this embodiment, the first and second driven pulleys 31 and 32 are rotatably housed at both ends of the head rail 11, and the loop-shaped driven cord 33 is hooked on the first and second driven pulleys 31 and 32, respectively. Passed. The first driven pulley 31 is formed to have a larger diameter than the second driven pulley 32, and in this embodiment, the first driven pulley 31 is attached to the housing 23 to which the single first driven pulley 31 is attached to the inclined upper end of the rail body 22. The pair of second driven pulleys 32, 32 are rotatably accommodated via the one driven shaft 31a, and the pair of second driven shafts 32a, 32a are attached to the end cap 24 attached to the lower end portion of the rail body 22. Each is rotatably housed via. Further, one end 33a of the driven cord 33 is attached to the leading carrier 12, and the other end is attached to the tension adjusting mechanism 36 that moves together with the leading carrier 12 (FIGS. 1 and 3). Further, the driven cord 33 has a cord play insertion portion 12c projecting in a substantially C shape on both side surfaces of the leading carrier 12, and a cord play projecting in a substantially C shape on both side surfaces of the subsequent carrier 13. It is loosely inserted into the insertion portion 13c.

The spacing control bar 34 is made of plastic and is formed in the shape of an elongated plate (FIG. 1). Further, although not shown, the interval limiting bar 34 has a bar main body, a locking claw formed at the base end of the bar main body, and a hook formed at the tip of the bar main body. The locking claws of the spacing limiting bar 34 are respectively fixed to the subsequent carriers 13 so that the tip of the spacing limiting bar 34 extends toward the end cap 24. Then, when the leading carrier 12 moves to the end cap 24 side and the distance from the succeeding carrier 13 adjacent to the leading carrier 12 reaches the maximum separation distance, the hook at the tip of the spacing limiting bar 34 is the leading. It is configured to be locked to the carrier 12 so that the distance between the leading carrier 12 and the adjacent subsequent carrier 13 is maintained at the maximum separation distance. Further, when the succeeding carrier 13 adjacent to the leading carrier 12 moves to the end cap 24 side and the distance from the next succeeding carrier 13 adjacent to the succeeding carrier 13 reaches the maximum separation distance, the distance is regulated. The hook at the tip of the bar 34 is configured to be engaged with the succeeding carrier 13 so that the distance between the succeeding carrier 13 and the adjacent next succeeding carrier 13 is maintained at the maximum separation distance. In this way, the maximum separation distance between the adjacent carriers 12 and 13 is regulated by the spacing regulation bar 34. Further, when the plurality of carriers 12 and 13 are in close contact with the housing 23 side, the plurality of spacing regulation bars 34 are overlapped with each other in a state of being displaced in the longitudinal direction of the head rail 11 by the thickness of the carriers 12 and 13. ing.

On the other hand, the drive pulley 18 is housed in the pulley cover 35 attached to the side surface of the housing 23 (FIG. 1). The pulley cover 35 includes a cover body 35a in which the drive pulley 18 is housed and one surface of which is open, and a lid body 35b that closes the opening surface of the cover body 35a. Further, the base portion of the drive shaft 17 is rotatably mounted in the housing 23, and the tip of the drive shaft 17 is projected into the pulley cover 35. A drive pulley 18 around which an operation code 19 is wound is fitted to the tip of the drive shaft 17. Further, the transmission mechanism 21 is composed of a moving worm gear 21 having a worm 21a connected to the drive shaft 17 and a worm wheel 21b that meshes with the worm 21a and is attached to the louver moving mechanism 16. A pair of worm shafts 21c and 21c are projected integrally with the worm 21a at both ends of the worm 21a. The center lines of these worm axes 21c and 21c are configured to coincide with the center lines of the worm 21a. Further, one worm shaft 21c is rotatably attached to the housing 23, the other worm shaft 21c is non-rotatably connected to the drive shaft 17 inserted into the housing 23, and the worm 21a rotates together with the drive shaft 17. It is configured as follows.

Further, a square columnar upper wheel shaft 21d is integrally projected from the worm wheel 21b on the upper surface of the worm wheel 21b (FIG. 1), and a columnar lower wheel shaft 21d is projected on the lower surface of the worm wheel 21b (FIG. 1). Is projected integrally with the worm wheel 21b. The center lines of the upper wheel shaft 21d and the lower wheel shaft are configured to coincide with the center line of the worm wheel 21b. On the other hand, the first driven shaft 31a is integrally projected on the upper surface of the first driven pulley 31 together with the first driven pulley 31 (FIG. 1), and a square columnar square hole 31b is centered on the lower surface of the first driven pulley 31. Is formed (Fig. 7). The upper wheel shaft 21d is inserted into the square hole 31b of the first driven pulley 31 so as not to rotate relative to the first driven pulley 31 and rotates together with the first driven pulley 31, and the lower wheel shaft is rotatably attached to the lower housing portion 23b of the housing 23. As a result, the rotational force can be transmitted from the worm 21a to the worm wheel 21b, and the rotational force cannot be transmitted from the worm wheel 21b to the worm 21a. The reason why the rotational force is not transmitted from the worm wheel 21b to the worm 21a is that the specifications of the moving worm gear 21, for example, the advance angle of the worm 21a is set to be equal to or less than the friction angle, or the tooth surface of the moving worm gear 21 is roughened. This is because the self-locking function is exhibited by setting the roughness coarsely.

On the other hand, the tension adjusting mechanism 36 is configured to adjust the tension of the driven cord 33. Then, in this embodiment, the tension adjusting mechanism 36 is configured to engage with the leading carrier 12 and move together with the leading carrier 12. The tension adjusting mechanism 36 rotates the tension adjusting case 37, the take-up pin 38 rotatably housed in the tension adjusting case 37, and the take-up pin 38 from the opening 11a on the lower surface of the head rail 11. It has an operation shaft 39 provided in the above, a take-up pin 38, and a feeding prevention mechanism 41 provided in the operation shaft 39 (FIGS. 2 to 6). The tension adjusting case 37 is formed in a substantially rectangular parallelepiped box shape with an open upper surface, and a pair of locking pieces 37a and 37a are provided on the carrier case 12a of the leading carrier 12 on both upper sides of the tension adjusting case 37. It is projected toward the pair of receiving portions 12b, 12b (FIGS. 2 to 4). These locking pieces 37a, 37a are inserted into a pair of receiving portions 12b, 12b of the leading carrier 12, and are configured to be lockable (FIG. 3). As a result, the tension adjusting case 37 is held in close contact with the end cap 24 side of both sides of the leading carrier 12, and is configured to be movable together with the leading carrier 12.

The take-up pin 38 is rotatably housed in a bottomed cylindrical portion 37b projecting from the lower surface of the tension adjusting case 37 (FIGS. 2 and 4). Further, the take-up pin 38 includes a columnar take-up main body 38a capable of taking up the driven cord 33, and an upper flange portion 38b integrally formed with the take-up main body 38a on the upper surface and the lower surface of the take-up main body 38a. The lower flange portion 38c, the lower shaft portion 38d projecting from the lower surface of the lower flange portion 38c and integrally formed with the lower flange portion 38c, and the lower shaft portion 38d projecting from a part of the outer peripheral surface of the lower shaft portion 38d. It is composed of a fan-shaped portion 38e integrally formed in a substantially fan shape and a through hole 38f formed in the winding body 38a through which the other end 33b of the driven cord 33 is inserted (FIGS. 2 and 4 to 6). By tying a knot (not shown) at the other end 33b of the driven cord 33 inserted through the through hole 38f, the other end 33b of the driven cord 33 cannot be pulled out from the winding body 38a, and the winding body 38a is tension-adjusted. By rotating the case 37 in the bottomed cylindrical portion 37b, the other end 33b of the driven cord 33 of the winding body 38a can be wound.

The operation shaft 39 is rotatably housed in the bottomed cylindrical portion 37b of the tension adjusting case 37 so as to be located below the take-up pin 38, and the lower end is configured to protrude from the bottomed cylindrical portion 37b ( 2 and 4). Specifically, the operation shaft 39 has a cylindrical operation body 39a whose lower end is inserted into a small-diameter through hole 37d formed in the bottom wall 37c of the bottomed cylindrical portion 37b and whose lower end protrudes from the bottomed cylindrical portion 37b. From the flange portion 39b integrally formed with the operation main body 39a on the upper surface of the operation main body 39a, and the arcuate portion 39c integrally formed with the flange portion 39b on the upper surface of the flange portion 39b. (Fig. 2 and FIGS. 4 to 6). In this embodiment, a locking groove 39d to which a tool (minus driver) for rotating the take-up pin 38 via the operating shaft 39 can be locked is formed on the lower surface of the operating body 39a (FIG. 2). ~ Fig. 4). Further, the outer diameter of the flange portion 39b is larger than the through hole 37d formed in the bottom wall 37c of the bottomed cylindrical portion 37b, and is formed to be smaller than the inner diameter of the bottomed cylindrical portion 37b (FIG. 4). .. Further, the lower shaft portion 38d of the take-up pin 38 is loosely inserted into the arc-shaped portion 39c, and the fan-shaped portion 38e of the take-up pin 38 is loosely inserted into the notched portion of the arc-shaped portion 39c (FIG. 5 and FIG. FIG. 6). As a result, the take-up pin 38 is configured to be rotatable relative to the operating shaft 39 by a predetermined angle and to be rotatable together with the operating shaft 39.

In this embodiment, the feeding prevention mechanism 41 is a brake spring wound around a take-up pin 38 and an operating shaft 39. The brake spring 41 is a torsion coil spring in which a pair of bent pieces 41a and 41b are formed by bending both ends inward (FIGS. 2 and 4 to 6). The coil outer diameter of the brake spring 41 is formed to be larger than the inner diameter of the bottomed cylindrical portion 37b of the tension adjusting case 37. Therefore, in order to accommodate the brake spring 41 in the bottomed cylindrical portion 37b, the brake spring 41 is operated in a state of being reduced in diameter against the elastic force thereof, and the brake spring 41 is accommodated in the bottomed cylindrical portion 37b. The brake spring 41 is expanded in diameter by its elastic force and is pressed against the inner peripheral surface of the bottomed cylindrical portion 37b so as to be non-rotatable relative to the bottomed cylindrical portion 37b (FIGS. 4 to 6). Further, the brake spring 41 has the arcuate portion 39c of the operation shaft 39 and the fan-shaped portion of the take-up shaft 38 in a state where the lower shaft portion 38d of the take-up pin 38 is loosely inserted into the arcuate portion 39c of the operation shaft 39. It is loosely fitted to 38e. At this time, one bent piece 41a of the brake spring 41 is projected into one of the pair of spaces provided between the arc-shaped portion 39c and the fan-shaped portion 38e, and the other bent piece 41b is the pair. It is projected into the other space of the space. Then, when the operation shaft 39 is to be rotated in the direction of the solid arrow in FIG. 5A or the direction of the broken arrow in FIG. 6A, the brake spring 41 is reduced in diameter and this rotation is allowed. That is, the reduced diameter of the brake spring 41 allows the winding pin 38 and the operating shaft 39 to rotate in the direction in which the driven cord 33 is wound. When the force for rotating the operating shaft 39 is released, the brake spring 41 expands in diameter due to its elastic force and is pressed against the inner surface of the bottomed cylindrical portion 37b, so that the brake spring 41 cannot rotate relative to the bottomed cylindrical portion 37b. That is, the elastic force of the brake spring 41 prevents the winding pin 38 and the operating shaft 39 from rotating in the direction in which the driven cord 33 is drawn out from the winding pin 38. Reference numeral 42 in FIGS. 2 and 4 is a presser that locks the take-up pin 38, the operation shaft 39, and the brake spring 41 into the tension adjusting case 37 in order to prevent the bottomed cylindrical portion 37b from coming off. It is a board.

Reference numeral 43 in FIGS. 1 and 7 is a constant tension applying mechanism that constantly applies tension to the driven code 33. The constant tension applying mechanism 43 is rotatably held by a pair of substantially U-shaped holders 43a and 43a housed in the upper housing portion 23a in close proximity to the first driven pulley 31 and these holders 43a and 43a. It has a pair of pressure contact rollers 43b and 43b, and a pair of compression coil springs 43c and 43c that urge the pair of holders 43a and 43a to be pressed toward the driven cord 33. The pair of holders 43a, 43a are slidably provided so as to face each other and approach each other with the driven cord 33 interposed therebetween. Further, the pair of pressure contact rollers 43b, 43b are rotatably attached to the pair of holders 43a, 43a via the pair of roller pins 43d, 43d (FIG. 7). Further, the pair of compression coil springs 43c, 43c are interposed between the pair of side walls 23c, 23c of the upper housing portion 23a and the back surfaces of the pair of holders 43a, 43a. As a result, the pressure contact roller 43b constantly applies tension to the driven cord 33 by the elastic force of the compression coil spring 43c, and the contact area of the driven cord 33 with the first driven pulley 31 becomes large, so that the amount of drawing of the driven cord 33 is large. Therefore, the louver 14 can be stopped at a desired position, and the first driven pulley 31 can be prevented from idling when the operation code 19 is operated.

Further, reference numeral 44 in FIG. 8 is a tilt operation rod for rotating a plurality of louvers 14 around the axis of the louver holding member 28. The tilt operation rod 44 is connected to the louver holding member 28 via the tilt mechanism 46 (FIGS. 1 and 8). The tilt mechanism 46 includes a gear case (not shown) housed on the inclined upper side of the rail body 22, a worm gear for rotating the gear case side (not shown) rotatably housed in the gear case, and the rail on the rail body 22. The worm of the tilt shaft 47 extending in the longitudinal direction of the main body 22 and rotatably housed in the leading carrier 12 and the succeeding carrier 13, and the worm gear 26 for rotating the carrier side at the upper part. It has a wheel shaft 27 which is inserted into the wheel 26b and whose lower end is connected to the louver holding member 28 via a pin 29 (FIG. 1). The tilt operating rod 44 is connected to the worm (not shown) of the gear case side rotating worm gear via the universal joint 48 (FIG. 8), and this worm meshes with the worm wheel (not shown) of the gear case side rotating worm gear. .. Further, the tilt shaft 47 is a spline shaft (FIG. 1), one end of the tilt shaft 47 is inserted into the worm wheel of the worm gear for rotation on the gear case side, and the other end is rotatably attached to the end cap 24. Further, the tilt shaft 47 is inserted into the worm 26a of the carrier-side rotating worm gear 26 housed in the carrier case 12a of the leading carrier 12 so as not to rotate relative to each other, and is housed in the carrier case 13a of the subsequent carrier 13. It is inserted into the worm 26a of the carrier-side rotating worm gear 26 so as to be relatively non-rotatable. As a result, when the tilt operation rod 44 is operated, the plurality of louvers 14 can be rotated at the same time via the tilt mechanism 46.

The operation of the operation mechanism of the vertical blind 10 configured in this way will be described. When adjusting the tension of the driven cord 33 at the time of manufacturing the blind 10, a tool (minus driver) is locked in the locking groove 39f of the operating shaft 39 of the tension adjusting mechanism 36, and the operating shaft 39 is set in FIG. 5A. When rotated in the direction of the solid line arrow (rotation to the left), the arcuate portion 39c of the operation shaft 39 comes into contact with one of the bent pieces 41a of the brake spring 41 (FIG. 5 (b)), and this one is bent. Since the piece 41a is pushed in the same direction as the rotation direction to rotate counterclockwise, the diameter of the brake spring 41 is reduced, the operation shaft 39 and the brake spring 41 rotate in the same direction as the rotation direction (left rotation), and one of them is further rotated. The bent piece 41a comes into contact with the fan-shaped portion 38e of the take-up pin 38 and rotates in the same direction as the above-mentioned rotation direction (left rotation). As a result, the driven cord 33 is wound up by the winding pin 38. On the other hand, when the operation shaft 39 is rotated in the direction of the broken arrow in FIG. 6A (rotation to the right), the arcuate portion 39c of the operation shaft 39 comes into contact with the other bent piece 41b of the brake spring 41 (FIG. 6). 6 (b)), since the other bent piece 41b is pushed in the same direction as the rotation direction to rotate to the right, the diameter of the brake spring 41 is reduced, and the operation shaft 39 and the brake spring 41 are in the same direction as the rotation direction. (Rotating to the right), and the other bent piece 41b comes into contact with the fan-shaped portion 38e of the take-up pin 38 and rotates in the same direction as the above-mentioned rotation direction (rotating to the right). As a result, the driven cord 33 is unwound from the take-up pin 38. Then, when the rotational force on the operation shaft 39 is released, the other locking portion 41b of the brake spring 41 expands in diameter due to the elastic force of the brake spring 41, so that the brake spring 41 is a bottomed cylinder of the tension adjusting case 37. It is pressed against the inner surface of the portion 37b. At this time, since tension is applied to the driven cord 33, a force for rotating the winding pin 38 in the direction of feeding the driven cord 33 from the winding pin 38 acts on the winding pin 38. However, the brake spring 41 is pressed against the inner surface of the bottomed cylindrical portion 37b of the tension adjusting case 37, and the brake spring 41 prevents the winding pin 38 and the operating shaft 39 from rotating in the feeding direction. The pin 38 and the operation shaft 39 do not rotate in the feeding direction, and the driven cord 33 is kept in a state where tension is applied. With such a relatively simple operation, the tension of the driven cord 33 can be adjusted.

After mounting the head rail 11 of the blind 10 along the upper edge of the inclined window where the blind 10 is installed, the operation code 19 is operated to deploy the plurality of louvers 14 overlapping on the inclined upper side of the head rail 11. This operating force is applied to the driven cord 33 via the drive pulley 18, the drive shaft 17, the worm shaft 21c of the transmission mechanism 21, the worm 21a of the transmission mechanism 21, the worm wheel 21b of the transmission mechanism 21, and the upper wheel shaft 21d of the transmission mechanism 21. Be transmitted. When the driven code 33 moves, the leading carrier 12 first moves toward the end cap 24, and when the leading carrier 12 is separated from the succeeding carrier 13 adjacent to the leading carrier 12 by the maximum distance, the above-mentioned adjacent carriers 12 are adjacent to each other. Subsequent carriers 13 move towards the end cap 24. Then, when the succeeding carriers 13 sequentially move toward the end cap 24 and the leading carrier 12 reaches the end cap 24, the plurality of louvers 14 are in the deployed state, and the louvers 14 cannot be further deployed. When the plurality of louvers 14 are deployed in this way, the louvers 14 move diagonally downward, so that the operation code 19 can be operated with an extremely small force supported by the weight of the louvers 14.

On the other hand, when the plurality of developed louvers 14 are superposed on the inclined upper side of the head rail 11, the operation code 19 is operated in the direction opposite to the operation direction. This operating force is applied to the driven cord 33 via the drive pulley 18, the drive shaft 17, the worm shaft 21c of the transmission mechanism 21, the worm 21a of the transmission mechanism 21, the worm wheel 21b of the transmission mechanism 21, and the upper wheel shaft 21d of the transmission mechanism 21. Is transmitted to. Since the driven code 33 moves in the direction opposite to the moving direction, the leading carrier 12 first moves toward the housing 34, and the leading carrier 12 comes into close contact with the succeeding carrier 13 adjacent to the leading carrier 12. Then, the adjacent carrier 13 moves toward the housing 23. Then, the succeeding carriers 13 move toward the housing 23 while being in close contact with each other, and when the second carrier 13 from the rear end is in close contact with the carrier 13 at the rear end, the plurality of louvers 14 are in a superposed state and the louvers are in a superposed state. 14 cannot be polymerized any more. When the plurality of louvers 14 are polymerized in this way, the louvers 14 move diagonally upward, so that the operation code 19 must be operated against the weight of the louvers 14. However, since the transmission mechanism 21 is composed of the moving worm gear 21 having the worm 21a and the worm wheel 21b, even if the blind 10 becomes large or the inclination angle increases, the compact size moving worm gear 21 is compared. A large gear ratio can be secured, and a relatively large reduction ratio can be obtained. As a result, a plurality of louvers 14 can be polymerized with a relatively small operating force.

In addition, when the tilt angle of the upper edge of the tilted window frame increases, the operating force for moving the louver to the upper side of the tilted window frame becomes extremely large, and the operation of the conventional vertical blind for tilting deteriorates in operability. In the present embodiment, as compared with the device, by ensuring a large gear ratio of the worm gear of the transmission mechanism 21, the operating force for moving the louver 14 to the upper side of the inclined window frame can be slightly increased. Therefore, the deterioration of the operability of the operation code 19 can be suppressed. Further, the self-locking function is exhibited by setting the specifications of the moving worm gear 21, for example, the advancing angle of the worm 21a to be equal to or less than the friction angle, or by setting the tooth surface roughness of the moving worm gear 21 to be rough. Therefore, although the rotational force of the transmission mechanism 21 can be transmitted from the worm 21a to the worm wheel 21b, the rotational force cannot be transmitted from the worm wheel 21b to the worm 21a. As a result, even if the plurality of louvers 14 unintentionally try to move to the lower side of the window frame tilted by their own weight, the rotational force from the worm wheel 21b to the worm 21a is not transmitted, and the drive shaft from the louver moving mechanism 16 Power is not transmitted to 17. As a result, the plurality of louvers 14 can be stopped at any position on the head rail 11 without using the one-way clutch means or the clutch spring releasing means such as the conventional operation device for the vertical blind for tilting.

On the other hand, the driven cord 33 extends due to the long-term use of the blind 10, and the louver 14 cannot be stopped at a desired position, or even if the operation code 19 is operated, the first driven pulley 31 spins idle. When the driven cord 33 cannot be moved, the tool ( The minus driver) is locked, and the operation shaft 39 is rotated in the direction of the solid line arrow in FIG. 5 (a) or the direction of the broken line arrow in FIG. 6 (a). Thereby, the tension of the driven cord 33 can be adjusted. As a result, the driven cord 33 can be prevented from slipping with respect to the first driven pulley 31 due to the weight of the plurality of louvers 14, and the first driven pulley 31 can be prevented from idling when the operation code 19 is operated. 14 can be reliably stopped at a desired position, and the operating force of the operation code 19 is reliably transmitted to the driven code 33 via the first driven pulley 31.

In the above embodiment, the head rail is attached to the lower surface of the inclined upper edge of the window frame of the inclined window, but the head rail is attached to the front surface of the inclined upper edge of the window frame of the inclined window, or the head rail is attached. Mounted on a slanted wall above the sloping window, mounted on a sloping ceiling above the sloping window of the headrail, or mounted on the lower surface of the horizontal upper edge or front of the upper edge of the window frame of a rectangular window. , The headrail may be mounted horizontally on the wall surface above the rectangular window of the headrail, or may be mounted horizontally on the horizontal ceiling above the rectangular window of the headrail. Here, even if the louver is a blind that moves in the horizontal direction, if the size of the blind is increased, the louver is heavy and its operating force increases. However, in the present invention, a large gear ratio of the worm gear of the transmission mechanism is secured. By doing so, the operating force for moving the heavy louver in the horizontal direction is only slightly increased, so that the deterioration of the operability of the operation code can be suppressed. Further, when the tilt angle of the window frame or the like is increased and the blind is enlarged, the operating force for moving the heavy louver to the upper side of the tilted window frame or the like is further increased. By ensuring a large gear ratio of the worm gear, the operating force for moving the heavy louver to the upper side of the inclined window frame or the like can be slightly increased, so that the deterioration of the operability of the operation code can be suppressed.

Further, in the above embodiment, a loop-shaped driven cord is hung on the first and second driven pulleys in the head rail, and the driven cord is rotated by a moving worm gear to move a plurality of carriers along the head rail. Although it was moved, even if a screw rod extending in the longitudinal direction is rotatably attached to the head rail in the head rail and the screw rod is rotated by a moving worm gear, a plurality of carriers can be moved along the head rail. good. Further, in the above embodiment, the housing in which the operation cord is attached via the drive pulley or the like and the first driven pulley is rotatably accommodated is attached to the inclined upper end of the rail body of the head rail, and the second driven pulley is driven. The end cap in which the pulley was rotatably housed was attached to the lower end of the tilt of the rail body, but the end cap was attached to the upper end of the tilt of the rail body of the head rail, and the housing was attached to the tilted upper end of the rail body. It may be attached to the lower end.

Further, in the above embodiment, a locking groove in which a tool (minus driver) can be locked is formed on the lower surface of the operating shaft of the tension adjusting mechanism, but the tool (plus driver) is placed on the lower surface of the operating shaft of the tension adjusting mechanism. Even if a substantially cross-shaped locking hole that can be locked is formed, or a substantially hexagonal columnar locking hole that can be locked by a tool (hexagonal L-shaped wrench) is formed on the lower surface of the operation shaft of the tension adjusting mechanism. good. Further, in the above embodiment, the brake spring, which is a feeding prevention mechanism, is wound around the take-up pin and the operation shaft, and the brake spring rotates the take-up pin and the operation shaft in the direction in which the driven cord is taken up by the brake spring. Although it is configured to allow rotation of the take-up pin and the operation shaft in the direction of feeding the driven cord from the take-up pin, a worm gear which is a take-out prevention mechanism may be provided on the take-up pin and the operation shaft. In this case, the worm wheel of the worm gear is provided integrally with the take-up pin, and the worm of the worm gear is provided integrally with the operation shaft so that the worm wheel and the worm mesh with each other to obtain a self-locking function. The worm gear allows the winding pin and the operating shaft to rotate in the direction in which the driven cord is wound by the worm gear, and prevents the winding pin and the operating shaft from rotating in the direction in which the driven cord is drawn out from the winding pin. Further, in the above embodiment, the pair of pressure contact rollers are rotatably attached to the pair of holders of the constant tension applying mechanism via the pair of roller pins, so that the pair of pressure contact rollers are relatively relative to the pair of holders. Although it was configured to be immovable, a pair of roller pins were rotatably attached to a pair of holders via a pair of bearings, a pair of feed screw mechanisms were placed on the pair of bearings, and the screws of these feed screw mechanisms were attached. By turning the pair of pressure-welding rollers, the pair of pressure-welding rollers may be configured to be relatively movable in a direction toward or away from each other with respect to the pair of holders. Thereby, after assembling the blind, the contact area of the driven cord with respect to the first driven pulley, that is, the throttle amount of the driven cord can be adjusted.

10 Vertical blind 11 Head rail 11a Opening 12 Leading carrier 13 Subsequent carrier 14 Louver 16 Louver moving mechanism 17 Drive shaft 18 Drive pulley 19 Operation code 21 Transmission mechanism (moving worm gear)
21a Warm 21b Warm wheel 31 1st driven pulley 32 2nd driven pulley 33 driven cord 33a One end of the driven cord 33b The other end of the driven cord 34 Interval regulation bar 36 Tension adjustment mechanism 37 Tension adjustment case 38 Winding pin 39 Operation shaft 39d Locking groove 41 Feeding prevention mechanism (brake spring)

Claims (1)

A head rail mounted on a window frame, a wall surface, or a ceiling, a plurality of carriers housed in the head rail and movable in the longitudinal direction of the head rail, a plurality of louvers suspended from the plurality of carriers, and the above. A louver moving mechanism interposed between the head rail and the plurality of carriers to move the plurality of carriers along the head rail to deploy or superimpose the plurality of louvers, and a drive shaft at one end of the head rail. A vertical type equipped with a drive pulley rotatably attached via the louver, a loop-shaped operation cord wound around the drive pulley, and a transmission mechanism for transmitting the operation force of the operation code to the louver movement mechanism. In the operation mechanism of the blind
The louver moving mechanism has a loop-shaped driven cord circulated in the head rail and a tension adjusting mechanism for adjusting the tension of the driven cord.
The tension adjusting mechanism is rotatably housed in the tension adjusting case, the winding pin to which the end of the driven cord is rotatably attached, and the opening of the lower surface of the head rail. The operation shaft provided for rotating the take-up pin, and the take-up pin and the operation shaft provided on the take-up pin and the operation shaft in the direction of winding the driven cord around the take-up pin. An operation mechanism for a vertical blind, characterized by having a take-up pin in a direction in which the driven cord is taken out from the take-up pin and a take-out prevention mechanism for preventing rotation of the operation shaft.

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