JP2000145329A - Slat drive equipment for lateral blind - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a slat drive equipment for a lateral blind capable of reducing an operating force during slat lifting/lowering operation in the lateral blind performing slat lifting/lowering operation and angle adjusting operation by common operation means. SOLUTION: In a slat drive device for the lateral blind, slats in a number of stages are suspended and support through a head box 1 to ladder cords and lift cords, an angle adjusting shaft 48 for adjusting the angle of slat and a lift/lower shaft 36 for lifting/lowering the slats are arranged in the head box 1, operation means 6 is suspended from the head box 1, and an angle adjusting shaft 48 and a lift/lower shaft 36 are driven based on the operation of the operation means 6 in the head box 1. And for the lateral blind equipped with a slat drive device 7, a clutch device 37 is provided which interrupts the connection between the slat drive device 7 and the angle adjusting shaft 48 when the slats are rotated to fully closed state between the slat drive device 7 and the angle adjusting shaft 48.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a slat drive device for performing a vertical slat elevating operation and an angle adjusting operation of a horizontal blind.

[0002]

2. Description of the Related Art Conventionally, as one type of a horizontal blind,
In order to easily and quickly perform the slat elevating operation and the angle adjusting operation, the slat elevating operation and the angle adjusting operation are performed by operating a common operation code or a common operation rod that is hung from one end of the head box. Some have made it possible.

In the horizontal blind disclosed in Japanese Patent Application Laid-Open No. 4-269293, the angle of the slat can be adjusted by rotating an operating rod suspended from one end of a head box. When the operation rod is further rotated, the slat can be moved up and down. Further, when the operation rod is pulled downward, the operation of the clutch device that operates as the self-weight drop prevention device is released, and the slat can be lowered by its own weight.

[0004] With such an operation, the slat angle adjustment operation and the elevation operation can be performed by operating the common operation rod. In particular, the slat can be lowered by its own weight by pulling the operation rod downward. The slat can be lowered without rotating the operation rod.

[0005] In the horizontal blind disclosed in Japanese Patent Application Laid-Open No. 5-302482, the angle of the slat can be adjusted by operating an operation code suspended from one end of the head box. When the operation code is further operated, the slat can be moved up and down. Further, when the pulley case is tilted by pulling the operation cord diagonally downward, the operation of the clutch device that operates as the self-weight drop prevention device is released, and the slat can be lowered by its own weight.

[0006] By such an operation, the slat angle adjustment operation and the elevating operation can be performed by operating the common operation code. In particular, the slat can be lowered by its own weight by tilting the pulley case. It is possible to lower the slat without repeatedly operating the operation code.

In the above-mentioned horizontal blind, the upper end of a ladder cord supporting each slat is supported by a ladder cord support device in a head box, and an angle adjusting shaft rotatably supported in the head box has a ladder cord. It is inserted into the support device.

When the operation rod or the operation cord is operated to rotate the angle adjusting shaft, the rotation of the angle adjusting shaft is transmitted to the ladder cord supporting device via a predetermined frictional force. The slat is rotated via the ladder code based on the above operation.

[0009]

However, in the above-mentioned horizontal blind, when the slat is pulled up,
After the angle adjusting shaft is continuously rotated and the slat is rotated in the vertical direction, the angle adjusting shaft is continuously rotated against the frictional force between the angle adjusting shaft and the ladder cord supporting device.

Therefore, an unnecessary operation force for rotating the angle adjusting shaft at the time of raising the slat is required,
There is a problem that the operating force required for the slat lifting operation increases.

Further, when the slat is lowered by its own weight, the weight of the slat acting on the lifting cord decreases as the slat is lowered to the vicinity of the lowermost limit, so that the friction between the angle adjusting shaft and the ladder cord supporting device is reduced. When the weight of the slat is balanced with the weight of the slat, the lowering operation of the slat stops. Therefore, there is a problem that the slat cannot be reliably lowered to the lowermost limit.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a slat drive device for a horizontal blind which can reduce the operation force at the time of slat elevating operation in a horizontal blind in which slat elevating operation and angle adjusting operation are performed by a common operating means. is there.

Further, in a horizontal blind in which a slat is lifted and lowered and an angle is adjusted based on the operation of a common slat drive, a slat drive of a horizontal blind which can surely lower the slat to its lower limit by its own weight is provided. Is to do.

[0014]

According to the present invention, a multi-stage slat is suspended from a head box via a ladder cord and a lifting cord, and an angle for adjusting the angle of the slat is provided in the head box. An adjusting shaft and an elevating shaft for raising and lowering the slats are provided, and operating means is hung from the head box, and the angle adjusting shaft and the elevating In a horizontal blind having a slat drive for driving a shaft, between the slat drive and the angle adjustment axis, when the slat is turned to the fully closed state, the slat drive and the angle adjustment axis A clutch device for interrupting connection is provided.

According to a second aspect of the present invention, the slat driving device includes a slat lowering device for lowering the slat by its own weight based on an operation of the operating means. Claim 3
In the clutch device, the friction force between the first clutch shaft that is rotated based on the operation of the slat drive device, the second clutch shaft that is connected to the angle adjustment shaft, and both clutch shafts is provided. And frictional force selection means to be selected,
The frictional force selecting means secures a frictional force for integrally rotating the two clutch shafts until the slat is fully closed, and when the slat is rotated to the fully closed state, the frictional force between the two clutch shafts is reduced. The first clutch shaft is allowed to idle with respect to the second clutch shaft by reducing the rotation.

According to a fourth aspect, the first clutch shaft is
Formed in the shape of a truncated cone whose diameter is reduced toward the tip, a recess is formed on the outer peripheral surface of the first clutch shaft, and a needle roller is rotatably housed in the recess, and the second clutch shaft is When formed into a cylindrical shape whose diameter is enlarged toward the tip corresponding to the first clutch shaft, when the first clutch shaft is inserted into the second clutch shaft until the needle roller cannot rotate. A case that rotatably supports both clutch shafts, and the frictional force selecting means includes a case that rotatably supports the second clutch shaft, a slide ball supported on an inner peripheral surface of the case, and the slide ball. And a guide groove formed on the outer peripheral surface of the second clutch shaft so as to engage with the second clutch shaft.The guide groove is formed so that both clutch shafts rotate integrally until the slat is fully closed. Position the second clutch shaft So, the slats when rotated to the fully closed state, the needle rollers to guide the second clutch shaft in a position that enables the rotation.

According to a fifth aspect of the present invention, a torsion coil spring is disposed between the first clutch shaft and the second clutch shaft, and rotation of the first clutch shaft is controlled by friction of the torsion coil spring. Can be transmitted to the second clutch shaft via force,
The frictional force selecting unit is a rotation preventing unit provided in a case that rotatably supports the first and second clutch shafts,
When the slat is rotated to the fully closed state, the rotation preventing portion abuts on the torsion coil spring in a direction to reduce the frictional force.

According to a sixth aspect of the present invention, a rotational torque is transmitted between the second clutch shaft and the angle adjusting shaft from the second clutch shaft to the angle adjusting shaft. A torque transmitting device that does not transmit rotational torque to the shaft is interposed.

[0019]

DESCRIPTION OF THE PREFERRED EMBODIMENTS (First Embodiment) A first embodiment of the present invention will be described below with reference to the drawings. The horizontal blind shown in FIG.
A plurality of slats 3 are suspended from and supported via a plurality of ladder cords 2, and a bottom rail 4 is connected to a lower end of the ladder cord 2.

A plurality of elevating cords 5 hanging from the head box 1 penetrate through the slats 3, and the bottom rail 4 is connected to a lower end of the elevating cord 5. The upper end of the lifting cord 5 is wound around a lifting cord winding device in the head box 1.

An endless operation code 6 is hung from one end of the head box 1, and the operation of the operation code 6 causes a slat drive device disposed in the head box 1 to operate. Then, based on the operation of the slat drive device, a lifting operation of the slat 3 or an angle adjusting operation of the slat 3 is performed.

The specific configuration of the slat driving device 7 disposed in the head box 1 will be described. As shown in FIG. 2, one side of the head box 1 has an upper case 8a of the slat driving device 7 as shown in FIG. , The lower case 8b and the case cover 8c are arranged in a state where they are fitted to each other.

The input shaft 9 is rotatably supported by the bearing 17a of the case cover 8c, and a pulley 10 is fitted to the base end of the input shaft 9 outside the case cover 8c. The operation code 6 is mounted on the pulley 10, and the input shaft 9 is rotated via the pulley 10 by operating the operation code 6.

A gear is engraved on the base end of the input shaft 9, and a drive gear 11 is provided on the base end of the case cover 8c.
Are rotatably supported. When the input shaft 9 is rotated, the drive gear 11 is rotated via the transmission gear supported on the case cover 8c.

A transmission shaft 1 is provided at the center of the drive gear 11.
The two base ends are fitted. Therefore, the rotation of the input shaft 9 is reduced at a predetermined reduction ratio and transmitted to the transmission shaft 12.

The bearing 17b of the upper case 8a includes
The fitting shaft 13 is rotatably supported, and the base end of the fitting shaft 13 is relatively rotatably fitted to the distal end of the input shaft 9, and the distal end of the fitting shaft 13 has a square shaft shape. Formed
The camshaft 14 is fitted into a square hole 15 formed at the center of the base end side. Accordingly, the cam shaft 14 rotates integrally with the fitting shaft 13 and is supported so as to be movable in the axial direction with respect to the fitting shaft 13.

A planetary gear mechanism is interposed between the input shaft 9 and the fitting shaft 13, and the rotation of the input shaft 9 is reduced at a predetermined reduction ratio and transmitted to the fitting shaft 13. In addition, fitting shaft 1
3 engages with the carrier of the planetary gear mechanism, and after the carrier is rotated by a predetermined angle based on the rotation of the input shaft, that is, after the transmission shaft 12 is rotated by the predetermined angle and the slat 3 is rotated substantially vertically, It is designed to rotate with the carrier.

A coil spring 16 is disposed between the bearing 17b of the upper case 8a and the base end surface of the cam shaft 14. The camshaft 14 is urged away from the bearing 17b by the urging force of the coil spring 16 with the bearing 17b as a fulcrum.

An outer peripheral surface of a base end portion of the cam shaft 14 is located near an inner surface of the lower case 8b, and a guide groove 18 having a semicircular cross section is formed on the outer peripheral surface so as to be continuous in the circumferential direction. I have.

A concave portion 19 is formed on the inner surface of the lower case 8b facing the cam shaft 14, and a slide ball 20 is provided between the concave portion 19 and the guide groove 18. The recess 19 is formed in a long groove shape in the axial direction of the camshaft 14. Accordingly, when the camshaft 14 is rotated, the slide ball 20 moves in the guide groove 18 and also moves in the recess 19.

FIG. 4 is a development view of the guide groove 18.
That is, the guide groove 18 branches from the first groove 18a that is continuous on the peripheral surface of the cam shaft 14 to the distal end side of the cam shaft 14 from the bent portion 18c of the first groove 18a, and passes through a predetermined angle to the converging portion 18d. And a second groove 18b converging in a direction perpendicular to the first groove 18a. The first and second grooves 18a and 18b are formed on the peripheral surface of the cam shaft 14 for two periods.

The bent portion 18c is formed at a branch portion between the first groove 18a and the second groove 18b so as to be bent toward the second groove 18b. When the camshaft 14 configured as described above is rotated in the slat pulling direction by the fitting shaft 13, the slide ball 20 moves in the direction of arrow A relative to the guide groove 18 in FIG. Then, the slide ball 2 is driven by the urging force of the coil spring 16.
0 moves in the first groove 18a.

When the slide ball 20 passes through the bent portion 18c, the cam shaft 14 is not moved in the axial direction because the concave portion 19 allows the slide ball 20 to move.

When the cam shaft 14 is rotated by the fitting shaft 13 in the slat pull-down direction, the slide ball 20 moves in the arrow B direction relative to the guide groove 18. Then, the slide ball 20 moves from the first groove 18a to the bent portion 18c.
Through the second groove 18b.
To return to the first groove 18a via

At this time, the slide ball 20 is
b, the camshaft 14 is driven by the coil spring 1
6 moves in the direction of arrow C shown in FIG. In addition, the slide ball 20 is moved to the converging portion 1 of the second groove 18b.
When the rotation reaches 8d, further rotation of the cam shaft 14 in the same direction is prevented. In this state, when the operation cord 6 is released, the slide ball 20 is moved from the converging portion 18d by the urging force of the coil spring 16 to the first position. It returns into the groove 18a.

As shown in FIG. 3, a one-way cam 21 is fitted to an intermediate portion of the cam shaft 14 so as to be relatively non-rotatable and movable in the axial direction. A coil spring 22 is provided between the cam shaft 14 and the side surface on the base end side of the one-way cam 21, and the one-way cam 21 is moved by the urging force of the coil spring 22 with the cam shaft 14 as a fulcrum. It is urged toward the distal end. Further, ratchet teeth 23 constituting a one-way clutch are formed on the side surface on the tip side of the one-way cam 21.

A first clutch plate 24 is rotatably supported at the tip of the camshaft 14, and the camshaft 1
The camshaft 14 is formed by the E-ring 25 fitted to the tip of the camshaft 14.
Are supported so as to be relatively immovable in the axial direction. Therefore, when the camshaft 14 moves in the axial direction, the first clutch plate 24 moves integrally with the camshaft 14.

A ratchet tooth 26 meshing with the ratchet teeth 23 of the one-way cam 21 is formed on the side surface on the base end side of the first clutch plate 24. Then, the ratchet teeth 23 are generated by the urging force of the coil spring 22.
Are urged toward the ratchet teeth 26 so that the two ratchet teeth 23 and 26 are in mesh with each other.

When the one-way cam 21 is rotated in the slat pull-up direction, the ratchet teeth 23 and 26 mesh with each other to rotate the first clutch plate 24 integrally with the one-way cam 21 and rotate in the slat pull-down direction. In this case, the one-way cam 21 idles with respect to the first clutch plate 24. During this idling operation, the ratchet teeth 23 rotate while riding over the ratchet teeth 26, so that the one-way cam 21 reciprocates in the axial direction against the urging force of the coil spring 22.

A clutch ring 28 is provided around the first clutch plate 24. As shown in FIG. 5, a plurality of recesses 27 extending in the axial direction are formed on the outer peripheral surface of the first clutch plate 24 at equal intervals in the circumferential direction. A ridge 29 is formed which engages the ridge 27. Therefore, the clutch ring 28 is supported so as not to rotate relative to the first clutch plate 24 and to be movable in the axial direction. On the outer peripheral surface of the clutch ring 28, irregularities having a corrugated cross section are continuously formed as cams 30.

The upper case 8a and the lower case 8b located around the clutch ring 28 are located close to the outer peripheral edge of the clutch ring 28, and one side of the lower case 8b is connected to the outer peripheral edge of the clutch ring 28. The locking portion 31 is formed by increasing the interval upward.

A clutch ball 32 is accommodated in the locking portion 31. When the clutch ring 28 is rotated in the slat-pulling direction, that is, in the direction of arrow D in FIG. To be repeatedly lifted. Therefore, the clutch ring 28 is freely rotated in the direction of arrow D with respect to the lower case 8b.

When the clutch ring 28 is rotated in the slat pull-down direction, that is, in the direction of arrow E in FIG. 5, the clutch ball 32 is sandwiched between the cam 30 and the engaging portion 31, and the clutch ring 28 is moved in the same direction. Prevent further rotation to Therefore, after the clutch ball 32 is sandwiched between the cam 30 and the locking portion 31, the clutch ring 28 cannot rotate in the direction of arrow E.

On the side surface on the tip side of the first clutch plate 24, teeth 33 extending in the tip direction are formed at equal intervals in the circumferential direction. The second clutch plate 3 is provided in the lower case 8b.
4 is rotatably supported. The second clutch plate 34 has teeth 35 meshing with the teeth 33 formed on the side surface on the base end side, and an elevating shaft 36 for driving the elevating cord winding device is fitted to the distal end. ing.

Therefore, the first and second clutch plates 24,
When the first clutch plate 24 is rotated in a state where the teeth 33 and 35 of 34 are engaged, the elevating shaft 36 is rotated via the second clutch plate 34.

The lifting cord winding device is driven based on the rotation of the lifting shaft 36. Then, based on the rotation of the elevating shaft 36 in the slat lifting direction, the elevating cord 5 is spirally wound around the elevating cord winding device, and based on the rotation of the elevating shaft 36 in the slat descending direction, the elevating cord 5 is raised and lowered. It is rewound from the cord winder.

A rotating force based on the weight of the slat 3 acts on the elevating shaft 36 via an elevating cord winding device. When the first and second clutch plates 24 and 34 are engaged with each other and a rotational force based on the weight of the slat 3 is transmitted to the first clutch plate 24, the clutch ring 28 is moved in the direction of arrow E shown in FIG. However, the rotation of the clutch ring 28 in the same direction is prevented by the operation of the clutch ball 32, so that the slat 3 is prevented from descending under its own weight.

The camshaft 14 moves in the direction of arrow C shown in FIG. 2, and the first clutch plate 24 moves in the same direction together with the camshaft 14 so that the teeth 33 of the first clutch plate 24 When the clutch plate 34 is disengaged from the teeth 35, the second clutch plate 34 can freely rotate, so that the slat 3 descends by its own weight.

Above the second clutch plate 34, a case 38 of a tilt clutch 37 is supported on the upper edge of the lower case 8b, and the case 38 has a first and a second clutch shaft 39, The base end of the forty is rotatably supported. The transmission shaft 12 is fitted to the base end of the first clutch shaft 39.

As shown in FIG. 6, the case 38 is formed in a substantially cylindrical shape, and has a hemispherical concave portion 41 on its inner peripheral surface.
Are formed. The second clutch shaft 40 is rotatably supported in a state in which its outer peripheral surface is close to the inner peripheral surface of the case 38, and has a semicircular guide groove 4
2 are formed in the circumferential direction.

In the development view shown in FIG. 7, the guide groove 42 has an intermediate portion extending linearly in the circumferential direction, and
2a is symmetrically bent toward the first clutch shaft 39 side. The recess 41 and the guide groove 42
And a slide ball 43 is disposed between them.

A coil spring 44 is provided between the second clutch shaft 40 and the case 38,
The second clutch shaft 40 is urged toward the first clutch shaft 39 by the urging force of the coil spring 44 having the fulcrum as a fulcrum.

At the tip of the second clutch shaft 40,
A cylindrical portion 45 that opens toward the distal end is formed, and the cylindrical portion 45 is formed so that the diameter gradually increases toward the distal end.

The first clutch shaft 39 has a tip portion corresponding to the cylindrical portion 45 of the second clutch shaft 40,
It is formed in the shape of a truncated cone whose diameter is gradually reduced toward the tip,
A plurality of recesses 46 extending in the axial direction are formed on the outer peripheral surface at equal intervals in the circumferential direction.

As shown in FIG. 8, the recess 46 is formed so as to gradually become deeper toward the center in the circumferential direction, and needle rollers 47 are provided in the recess 46, respectively.

The first clutch shaft 39 is rotatably supported by the case 38 with its tip end inserted into the cylindrical portion 45 of the second clutch shaft 40. Then, in a state where the slide ball 43 is located at the intermediate portion of the guide groove 42, as shown in FIG. 6, the inner peripheral surface of the cylindrical portion 45 of the second clutch shaft 40 and the concave portion 46 of the first clutch shaft 39 are formed. The needle roller 47 is pinched between the first and second clutch shafts 39 and 40 based on the rotation of the transmission shaft 12.

When the slide ball 43 moves to one of the two ends 42a of the guide groove 42 based on the rotation of the second clutch shaft 40, as shown in FIG. It moves in a direction away from one clutch shaft 39.

Then, the needle roller 47 is
And the first clutch shaft 39 idles with respect to the second clutch shaft 40. Therefore, in this state, the rotation of the transmission shaft 13 is not transmitted to the second clutch shaft 40.

At the base end of the second clutch shaft 40,
One end of the angle adjusting shaft 48 is fitted, and the angle adjusting shaft 48
The angle of the slat 3 is adjusted via the ladder cord support device and the ladder cord 2 based on the rotation of the slat 3. And
In the rotation range of the angle adjusting shaft 48 until the second clutch shaft 40 rotates integrally with the first clutch shaft 39 and the slide ball 43 moves from one end of the intermediate portion of the guide groove 42 to the other end, the slat is 3 is set so as to rotate substantially 180 degrees from the fully closed state and return to the fully closed state.

Next, the operation of the horizontal blind configured as described above will be described. When the operation cord 6 is operated in the slat pulling direction to perform the pulling operation of the slat 3, the input shaft 9 is rotated in the slat pulling direction via the pulley 10, and the slat 3 is rotated to almost the vertical direction. The carrier of the gear mechanism is engaged with the fitting shaft 13,
The carrier and the camshaft 14 are rotated integrally.

Then, since the slide ball 20 moves in the first groove 18a of the cam shaft 14, the cam shaft 14 hardly moves in the axial direction. When the camshaft 14 is rotated in this state, the one-way cam 21 is rotated in the same direction, and the first clutch plate 24 is rotated in the same direction via the ratchet teeth 23 and 26. Then, the clutch ring 28 is rotated together with the first clutch plate 24 in the direction of arrow D in FIG. 5, and idles with respect to the lower case 8b.

Further, the second clutch plate 34 meshing with the first clutch plate 24 is rotated in the same direction, and the elevating shaft 36 is rotated. Accordingly, the lifting cord 5 is wound up by operating the operation cord 6, and the slat 3 is raised.

At this time, the transmission shaft 12 is rotated based on the rotation of the input shaft 9, and the first and second clutch shafts 39, 4 are rotated.
0 is rotated integrally, the angle adjusting shaft 48 is rotated based on the rotation of the second clutch shaft 40, and the slat 3 is rotated.

When the slat 3 is rotated to the fully closed state and the slide ball 43 reaches the end 42 a of the guide groove 42, the second clutch shaft 40 is moved to the first clutch shaft 39.
, And the first clutch shaft 39 idles with respect to the second clutch shaft 40.

Therefore, when the slat 3 is rotated to the fully closed state, the connection between the transmission shaft 12 and the angle adjusting shaft 48 is cut off. When the operation cord 6 is released after the slat 3 is pulled up to a desired position, a rotating force in the downward direction of the slat 3 acts on the elevating shaft 36 due to the weight of the slat 3. Then, a rotational force acts on the second clutch plate 34 in the same direction, and the first clutch plate 24 attempts to rotate in the same direction.

Then, as shown in FIG. 5, the clutch ring 28 is rotated in the direction of arrow E, and the cam 30 and the engaging portion 3 are rotated.
1 and the clutch ball 32 is engaged, and the clutch ring 2
8 is prevented from rotating in the same direction.

Accordingly, the first and second clutch plates 24,
34, the rotation of the lifting shaft 36 in the same direction is prevented, and the slat 3 is prevented from falling under its own weight. As a result, the slat is suspended and supported at a desired position.

When the operation cord 6 is operated in the slat descent direction to lower the slat 3, the input shaft 9 is rotated in the slat descent direction via the pulley 10, and the cam is transmitted via the planetary gear mechanism and the fitting shaft 13. The shaft 14 is rotated in the same direction.

Then, the ratchet teeth 23 of the one-way cam 21 rotating integrally with the camshaft 14 idle around the ratchet teeth 26 of the second clutch plate 34, and the camshaft 14
Are allowed to rotate in the same direction. Then, with the rotation of the cam shaft 14, the slide ball 20 moves from the first groove 18a of the cam shaft 14 into the second groove 18b, so that the cam shaft 14 moves in the direction of arrow C shown in FIG. Thus, the state shown in FIG. 3 is obtained.

Then, the one-way cam 21 and the first clutch plate 24 move together with the camshaft 14 in the same direction.
The first clutch plate 24 is disengaged from the second clutch plate 34, and the second clutch plate 34 and the elevating shaft 36 are freely rotatable. As a result, the slat 3 descends by its own weight, and this descending operation can be performed by an operation within half a rotation of the camshaft 14.

When the slide ball 20 reaches the converging portion 18d of the second groove 18b, further rotation of the cam shaft 14 in the same direction is prevented, and further rotation of the pulley 10 by the operation cord 6 cannot be performed. Becomes When the operation cord 6 is released in this state, the slide ball 20 returns to the first groove 18a by the urging force of the coil spring 16.

The horizontal blind slat drive device configured as described above has the following effects. (1) By operating the operation cord 6 in the slat lifting direction, the lifting cord 5 can be wound by the lifting cord winding device, and the slat 3 can be pulled up. (2) After lifting the slat 3 to a desired position, releasing the operation cord 6 prevents the slat 3 from lowering its own weight.
The slat 3 can be suspended and supported at a desired position. (3) By operating the pulley 10 in the slat descent direction based on the operation code 6, the slat 3 can be lowered by its own weight by an operation within half a rotation of the cam shaft 14. (4) The weight of the slat 3 is prevented from lowering without using the frictional force of the torsion coil spring. The lowering operation of the slat 3 may be performed by operating the operation cord 6 in the slat lowering direction and rotating the cam shaft 14 within a range of half a rotation. At this time, since there is no urging force in the direction that hinders the rotation of the cam shaft 14, the lowering operation of the slat 3 can be performed with a small operation force. Further, the operation force at the time of raising the slat 3 can be reduced. (5) Since the lowering operation of the slat 3 can be performed by pulling the operation code 6 directly downward in the slat lowering direction, the lowering operation of the slat 3 can be performed easily. (6) A state in which the operation cord 6 is operated in the slat descending direction to move the slide ball 20 into the second groove 18b, and the engagement between the first clutch plate 24 and the second clutch plate 34 is released. Then, even if the slat 3 descends due to its own weight and releases the operation cord 6 in this state, the slide ball 20 is held in the second groove 18b. Therefore, even when the slat 3 is lowered to the lowermost limit, it is not necessary to continue pulling the operation code 6 downward, so that the lowering operation of the slat 3 can be performed easily. (7) When the slat 3 is rotated to the fully closed state during the pulling operation of the slat 3, the connection between the transmission shaft 12 and the angle adjustment shaft 48 is disconnected by the tilt clutch 37, and the transmission shaft 12 is adjusted in angle. It becomes freely rotatable with respect to the shaft 48.
Therefore, after the slat 3 is rotated to the fully closed state, the load acting on the transmission shaft 12 from the angle adjusting shaft 48 can be cut off, so that the operation force required for pulling up the slat 3 can be reduced. . (8) When the slide ball 20 passes through the bent portion 18c of the first groove 18a during the pulling operation of the slat 3, the slide ball 20 moves in the rotation axis direction of the cam shaft 14 due to the long groove-shaped concave portion 19. The cam shaft 14 is not moved in the axial direction. Therefore, the movement of the camshaft 14 in the rotation axis direction can be prevented when the slat 3 is pulled up, so that the operation force required for the pulling up operation can be reduced. (9) After the slat 3 has been rotated to the fully closed state, the load acting on the transmission shaft 12 from the angle adjusting shaft 48 can be cut off. Therefore, if the tilt clutch 37 is used for a horizontal blind in which the lowering operation of the slat 3 is performed by operating the operation code 6 without depending on its own weight, the operating force required for the lowering operation of the slat 3 can be reduced. (10) After the slat 3 has been rotated to the fully closed state, the load acting on the transmission shaft 12 from the angle adjusting shaft 48 can be cut off. Therefore, when the tilt clutch 37 is used in a horizontal blind having a configuration in which the connection between the lifting shaft 36 and the first clutch shaft 39 is not interrupted at the time of the lowering operation of the slat 3 by its own weight, the slat 3 is lowered to near the lowermost limit. Even if the weight acting on the lifting cord 5 becomes smaller,
The slats 3 can be reliably lowered to the lowermost limit. (11) During the angle adjusting operation of the slat 3, the carrier of the planetary gear mechanism and the fitting shaft 13 are not engaged, and the lifting shaft 36 is not rotated, so that the bottom rail 4 does not move up and down. (Second Embodiment) In this embodiment, the structure of the self-weight drop prevention device including the clutch ring 28 and the like and the tilt clutch 37 of the slat drive device of the first embodiment is changed. The same components as those in the first embodiment are denoted by the same reference numerals, and detailed description thereof will be omitted.

As shown in FIG. 10, a substantially cylindrical stop ring case 61 is non-rotatably fitted to the inner peripheral surface of the upper case 8a in the vicinity of the bearing portion 17b of the upper case 8a. A stop ring 62 is fitted on the inner peripheral surface of 61.

As shown in FIG. 12, both ends 63a and 63b of the stop ring 62 are bent toward the center at substantially 90 degrees. Inside the stop ring 62, in a space of approximately 270 degrees sandwiched between the both ends 63a and 63b, the first engagement portion 6 protruding from the carrier 64 of the planetary gear mechanism shown in FIG.
5 is projected in a range of approximately 130 degrees. A second engaging portion 66 protruding from the fitting shaft 13 protrudes from a space of approximately 90 degrees between the both ends 63a and 63b.

Then, the input shaft 9 is rotated and the carrier 6 is rotated.
4 is rotated, and the first engagement portion 65 is moved to the end portions 63a, 63b.
In this case, the end of the stop ring 62 is pulled in the radial direction by the first engagement portion 65, and the frictional force between the stop ring 62 and the stop ring case 61 is reduced.

Therefore, when the carrier 64 is rotated, the stop ring 62 and the second engagement portion 66 are rotated together with the first engagement portion 65 in the stop ring case 61, so that the stop ring case 61 is engaged with the carrier 64. The joint shaft 13 is integrally rotated. At this time, the first engaging portion 65 is connected to the end portions 63a, 63
The carrier 64 idles with respect to the fitting shaft 13 until it comes into contact with any one of 3b.

On the other hand, when the fitting shaft 13 is to be rotated by the rotational force acting on the fitting shaft 13 from the cam shaft 14, the second engaging portion 66 comes into contact with one of the ends 63a and 63b. Then, the end of the stop ring 62 is pulled in the radially expanding direction, and the stop ring 62 and the stop ring case 61 are pulled out.
, The rotation of the fitting shaft 13 is prevented.

Therefore, the rotation of the fitting shaft 13 due to the rotational force acting on the fitting shaft 13 from the cam shaft 14 is prevented. FIG. 13 is a development view of a guide groove 67 formed on the outer peripheral surface of the cam shaft 14. The guide groove 67 is
A first groove 67a that is continuous on the peripheral surface of the cam shaft 14, and a first groove 67a that branches off from the bent portion 67c of the first groove 67a to the distal end side of the cam shaft 14 through a rotation angle of approximately 270 degrees. And a second groove 67b that gradually converges toward the center. The first and second grooves 67a and 67b are formed on the peripheral surface of the cam shaft 14 for one period.

The bent portion 67c is formed at a branch between the first groove 67a and the second groove 67b so as to be bent toward the second groove 67b. When the camshaft 14 configured as described above is rotated in the slat pull-up direction by the fitting shaft 13, the slide ball 20 moves in the direction of arrow A relative to the guide groove 67 in FIG. Then, the slide ball 20 moves in the first groove 67a by the urging force of the coil spring 16.

When the slide ball 20 passes through the bent portion 68c, the cam shaft 14 is not moved in the axial direction because the recess 19 allows the slide ball 20 to move.

When the cam shaft 14 is rotated by the fitting shaft 13 in the slat pulling-down direction, the slide ball 20 moves in the arrow B direction relative to the guide groove 67. Then, the slide ball 20 moves from the first groove 67a to the bent portion 67c.
Is guided into the second groove 67b through the second groove 67b.
To return to the first groove 67a through the first groove 67a.

At this time, the slide ball 20 is
b, the camshaft 14 is driven by the coil spring 1
6 against the urging force of No. 6 in the direction of arrow F shown in FIG. When the slide ball 20 returns from the second groove 67b into the first groove 18a, the state returns to the state shown in FIG.

Therefore, while the camshaft 14 makes one rotation in the slat pull-down direction, the slide ball 20 moves in the second groove 67b within a range of approximately 270 degrees, and moves in the first range within the remaining range of approximately 90 degrees. It moves in the groove 67a.

A tooth 68 is formed at the tip of the camshaft 14 so that it can mesh with the second clutch plate 34. Therefore, the camshaft 14 of this embodiment corresponds to the one in which the first clutch plate 24 of the first embodiment is integrally formed.

The upper case 8a and the case cover 8c
A tilt clutch 69 is mounted on the upper side. Describing a specific configuration of the tilt clutch 69, a tilt clutch case 70 is mounted on the upper case 8a and the case cover 8c, and a tilt gear 71 is rotatably supported in the tilt clutch case 70. When the input shaft 9 is rotated, the tilt gear 71 is rotated via a transmission gear supported by the case cover 8c.

A clutch spring 72 is wound around the tip of the gear shaft of the tilt gear 71,
The proximal end of the clutch member 73 is supported at the distal end of “a” so as to be relatively rotatable. As shown in FIG. 14, the clutch spring 72 is bent so that both ends 72a and 72b protrude in a radial direction of the gear shaft 71a at a predetermined interval.

Both ends 72 of the clutch spring 72
a, 72b between the clutch member 73 and the engaging portion 7
3a is projected. Then, the gear shaft 71a is rotated, and either one of both ends 72a, 72b is
When it comes into contact with 3a, one of its ends 72a, 72b is pushed in the radial direction of the clutch spring 72, so that the frictional force between the clutch spring 72 and the gear shaft 71a increases.

Therefore, when the gear shaft 71a is rotated, the clutch member 73 is rotated in the same direction via the clutch spring 72, so that the gear shaft 71a is connected to the first clutch shaft 39 of the first embodiment. And the clutch member 7
Reference numeral 3 corresponds to the second clutch shaft 40 of the first embodiment.

The upper case 8a is formed with a rotation preventing portion 74 projecting on the rotation locus of both ends 72a and 72b of the clutch spring 72. And the gear shaft 7
1a is rotated, and both ends 72 of the clutch spring 72 are rotated.
a, 72b comes into contact with the rotation preventing portion 74,
Either of the two ends 72a, 72b is pushed in the radial direction of the clutch spring 72, so that the frictional force between the clutch spring 72 and the gear shaft 71a is reduced.

Accordingly, when one of the two ends 72 a, 72 b abuts against the rotation preventing portion 74, the gear shaft 71 a runs idle with respect to the clutch spring 72. As a result, the clutch member 73 is moved from a state in which one end of the clutch spring 72 is in contact with one side of the rotation preventing section 74 to a state in which the other end is in contact with the other side of the rotation preventing section 74. And almost 18
It rotates integrally with the gear shaft 71a only at 0 degrees.

On the tip side of the clutch member 73,
A substantially cylindrical coil frame 75 is fitted and fixed between the tilt clutch case 70 and the upper case 8a, and a stop ring 76 is fitted on the inner peripheral surface of the coil frame 75.

As shown in FIG. 15, both ends 76a and 76b of the stop ring 76 are projected radially inward at a predetermined interval, and the stop ring 76 is engaged with the clutch member 73 between the both ends 76a and 76b. The part 73b is projected.

Then, when the clutch member 73 is rotated,
The engaging portions 73b are provided at both ends 76a, 7 of the stop ring 76.
6b, the ends 76a, 76
Since any one of b is pushed in the diameter reducing direction of the stop ring 76, the frictional force between the stop ring 76 and the coil frame 75 is reduced.

Therefore, the engaging portion 73b is connected to the stop ring 7
6, the clutch member 73 and the stop ring 76 rotate integrally, so that the stop ring 76 rotates integrally with the clutch member 73 as the clutch member 73 rotates. I do.

The tilt output shaft 7 is provided in the coil frame 75.
The tip end of the tilt output shaft 77 is rotatably supported between the upper case 8 a and the tilt clutch case 70.

An engagement portion 77a is formed at the base end of the tilt output shaft 77 so as to sandwich both ends 76a, 76b of the stop ring 76 with the engagement portion 73b of the clutch member 73. I have. Therefore, when the clutch member 73 is rotated, the tilt output shaft 77 is integrally rotated via the stop ring 76.

Further, based on the rotation of the tilt output shaft 77, the engaging portion 77a is moved to both ends 76a, 7a of the stop ring 76.
6b, one of the two ends 76a, 76b is pushed in the radial direction of the stop ring 76, so that the frictional force between the stop ring 76 and the coil frame 75 increases.

Accordingly, the engaging portion 77a is
6, the rotation of the tilt output shaft 77 is prevented. One end of an angle adjusting shaft 48 is fitted to the tip of the tilt output shaft 77,
Based on the rotation of the angle adjusting shaft 48, the angle of the slat 3 is adjusted via the ladder cord support device and the ladder cord 2.

Next, the operation of the horizontal blind configured as described above will be described. When the operation cord 6 is operated in an arbitrary direction to perform the angle adjusting operation of the slat 3, the input shaft 9 is rotated via the pulley 10, and the tilt gear 71 is rotated via the transmission gear.

Then, the clutch member 73 is rotated together with the clutch spring 72 based on the rotation of the gear shaft 71a, and the tilt output shaft 77 is rotated together with the stop ring 76 based on the rotation of the clutch member 73. Then, the angle adjusting shaft 48 is rotated to adjust the angle of the slat 3 in a direction corresponding to the operation direction of the operation cord 6.

When the slat 3 is rotated to the vertical direction,
Either of the two ends 72a, 72b of the clutch spring 72 abuts against the rotation preventing portion 74 of the upper case 8a, and the gear shaft 71a idles with respect to the clutch spring 72,
The connection between the gear shaft 71a and the tilt output shaft 77 is cut off.

Therefore, the rotation of the gear shaft 71a is not transmitted to the tilt output shaft 77, and the rotation of the slat 3 is stopped. Therefore, even if the operation cord 6 is continuously operated, the slat 3 is rotated to the vertical direction. After that, it is not rotated further in the same direction.

In such an operation for adjusting the angle of the slat 3, the carrier 64 of the planetary gear mechanism is rotated based on the rotation of the input shaft 9. Before engaging with the second engaging portion 66 of
Since the slat 3 is rotated vertically, the slat 3
The lifting shaft 36 is not rotated during the angle adjustment operation. As a result, during the operation of adjusting the angle of the slat 3, the bottom rail 4
Is not raised or lowered.

When the operation cord 6 is operated in the slat pulling direction to perform the pulling operation of the slat 3, the input shaft 9 is rotated in the slat pulling direction via the pulley 10. Then, the carrier 64 of the planetary gear mechanism is rotated, and the stop spring 62 is moved to the stop ring case 61.
, And the fitting shaft 13 is rotated based on the rotation of the carrier 64.

Then, since the slide ball 20 moves in the first groove 67a of the cam shaft 14, the cam shaft 14 hardly moves in the axial direction. When the camshaft 14 is rotated in this state, the second clutch plate 34 meshing with the teeth 68 of the camshaft 14 is rotated in the same direction, and the elevating shaft 36 is rotated.
Accordingly, the lifting cord 5 is wound up by operating the operation cord 6, and the slat 3 is raised.

After lifting the slat 3 to the desired position,
When the operation cord 6 is released, a rotating force in the downward direction of the slat 3 acts on the lifting shaft 36 due to the weight of the slat 3. Then, a rotational force acts on the second clutch plate 34 in the same direction, and the camshaft 14 and the fitting shaft 13 try to rotate in the same direction.

Then, since the second engaging portion 66 of the fitting shaft 13 pushes the end of the stop ring 62 in the diameter increasing direction, the frictional force between the stop ring 62 and the stop ring case 61 increases, and the stop ring The rotation of 62 is prevented.

Therefore, the rotation of the fitting shaft 13 is prevented, and the lifting shaft 36 is moved via the cam shaft 14 and the second clutch plate 34.
Is prevented from rotating. As a result, the slat 3 is prevented from falling under its own weight, and the slat 3 is suspended and supported at a desired position.

When the operation cord 6 is operated in the slat descent direction to lower the slat 3, the input shaft 9 is rotated in the slat descent direction via the pulley 10, and the carrier 64 and the fitting shaft 13 of the planetary gear mechanism are moved. Via camshaft 1
4 is rotated in the same direction.

Then, as the camshaft 14 rotates,
Since the slide ball 20 moves from the first groove 67a of the camshaft 14 into the second groove 67b, the camshaft 14 moves in the direction of the arrow F shown in FIG. 10 to the state shown in FIG.

Then, the camshaft 14 and the second clutch plate 3
4 and the second clutch plate 34 and the lifting shaft 3
Numeral 6 is freely rotatable. As a result, the slat 3 is lowered by its own weight, and this lowering operation is performed by the camshaft 14.
It is possible by the operation within one rotation of.

When the slat 3 is lowered, the first groove 67
If the slide ball 20 is positioned in the second groove 67b of the portion extending in parallel with the position a, the slide ball 20 is held at that position even if the operation code 6 is released, and the camshaft 14 and the second clutch plate The slats 3 are lowered to the lowermost limit since the engagement with the slats 34 is maintained.

When the operation cord 6 is continuously operated in the downward direction of the slat 3, the slide ball 20 returns to the first groove 67a, and the cam shaft 14 moves toward the second clutch plate 34 and meshes with each other. Returns to the state.

Then, the rotation of the elevating shaft 36 based on the weight of the slat 3 is prevented, and the rotation of the fitting shaft 13 is
Is transmitted to the second clutch plate 34 through the
Is rotated in the slat descent direction.

Next, when the operation code 6 is further operated in the slat descending direction, the slide ball 20 is moved to the second groove 67b.
And the elevating shaft 36 becomes rotatable again.
When the operation cord 6 is continuously operated in the slat descending direction by such an operation, the slide ball 20 is returned to the first groove 67a during the rotation of the camshaft 14 by about 9 degrees.
In the range of 0 degrees, the elevating shaft 36 is forcibly rotated in the slat descending direction.

In the slat drive device provided with the tilt clutch configured as described above, (1), (2), (5), (6), (7), (8), and (8) obtained in the first embodiment. 9)
In addition to the function and effect of (10), the following function and effect can be obtained. (1) By operating the pulley 10 in the slat descent direction based on the operation of the operation code 6, the slat 3 can be lowered by its own weight within one rotation of the camshaft 14. (2) When the angle of the slat 3 is adjusted by operating the operation code 6, the first engaging portion 65 of the carrier 64 is moved to the second position of the fitting shaft 13 in the rotation range of the input shaft 9 for the angle adjustment. Does not come into contact with the engaging portion 66. Therefore, when the angle of the slat 3 is adjusted, the lifting shaft 36 is not rotated, so that the bottom rail 4 does not move up and down. (3) When the operation code 6 is continuously pulled in the slat descent direction, the slide ball 20 is returned from the second groove 67b to the first groove 67a based on the rotation of the cam shaft 14,
The rotation of the input shaft 9 is transmitted to the lifting shaft 36. Therefore, even when the slat 3 cannot be lowered due to its own weight, the slat 3 can be lowered by operating the operation code 6. (4) The rotation of the tilt output shaft 77 based on the rotational force acting on the tilt output shaft 77 from the angle adjusting shaft 48 is stopped by the action of the stop ring 76. Therefore, slat 3
After the angle is adjusted to a desired angle, rotation of the angle adjusting shaft 48 due to the weight or the like of the slat 3 is prevented, so that the slat 3 can be reliably held at the desired angle.

Note that the above embodiment can also be configured as follows. -In addition to the operation code 6, the input shaft 9 may be configured to be rotated by an operation rod hanging down from the head box 1. As shown by the chain line in FIG. 4, the holding portion 18e may be provided by extending the converging portion 18d in the direction of arrow B. With such a configuration, the slide ball 20 is
When the cam shaft 14 is rotated from the position b to the inside of the holding portion 18e, the return of the slide ball 20 to the first groove 18a by the urging force of the coil spring 16 is prevented. 3 can be lowered to its lower limit by its own weight. -The input shaft 9 may be configured to be rotationally driven by the driving force of a motor.

[0118]

As described above in detail, the present invention relates to a horizontal blind in which the slats are raised and lowered and the angle is adjusted by a common operating means. An apparatus can be provided.

[Brief description of the drawings]

FIG. 1 is a front view showing a horizontal blind.

FIG. 2 is a cross-sectional view illustrating the slat drive device according to the first embodiment.

FIG. 3 is a cross-sectional view illustrating the slat drive device according to the first embodiment.

FIG. 4 is a development view showing a guide groove of the camshaft according to the first embodiment.

FIG. 5 is a cross-sectional view illustrating the slat drive device according to the first embodiment.

FIG. 6 is a sectional view showing a tilt clutch according to the first embodiment.

FIG. 7 is a developed view showing a guide groove of the tilt clutch.

FIG. 8 is a sectional view showing a tilt clutch according to the first embodiment.

FIG. 9 is a cross-sectional view illustrating an operation of the tilt clutch according to the first embodiment.

FIG. 10 is a cross-sectional view illustrating a slat drive device according to a second embodiment.

FIG. 11 is a cross-sectional view illustrating a slat drive device according to a second embodiment.

FIG. 12 is a cross-sectional view illustrating a self-weight drop prevention device according to a second embodiment.

FIG. 13 is a development view showing a guide groove of a cam shaft according to the second embodiment.

FIG. 14 is a cross-sectional view illustrating a tilt clutch according to a second embodiment.

FIG. 15 is a cross-sectional view illustrating a tilt clutch according to a second embodiment.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Head box 2 Ladder code 3 Slat 5 Elevating code 6 Operating means (operation code) 7 Slat drive device 36 Elevating shaft 37 Clutch device (tilt clutch) 48 Angle adjusting shaft

Claims (6)

[Claims] 1. A multi-stage slat is suspended from a head box via a ladder cord and an elevating cord, and an angle adjusting shaft for adjusting the angle of the slat in the head box; And a slat drive device for driving the angle adjusting shaft and the raising / lowering axis based on the operation of the operating means in the head box. In the horizontal blind, a clutch device is provided between the slat drive device and the angle adjustment shaft to disconnect the slat drive device and the angle adjustment shaft when the slat is rotated to a fully closed state. A slat drive device for a horizontal blind, characterized in that: 2. The slat drive device according to claim 1, further comprising a slat lowering device for lowering the slat by its own weight based on an operation of the operating means.
A slat drive for a horizontal blind as described. A first clutch shaft that is rotated based on an operation of the slat drive device;
A second clutch shaft connected to the angle adjusting shaft; and a friction force selection unit for selecting a friction force between the two clutch shafts, wherein the friction force selection unit brings the slat into a fully closed state. When the slat is rotated to the fully closed state, the friction force between the two clutch shafts is reduced to make the first clutch shaft a second clutch shaft. 3. The slat drive device for a horizontal blind according to claim 1, wherein the slat drive device is capable of idling. 4. The first clutch shaft is formed in a truncated cone shape whose diameter is reduced toward the tip, a concave portion is formed on an outer peripheral surface of the first clutch shaft, and a needle roller is rotated in the concave portion. The second clutch shaft is accommodated as possible, and the second clutch shaft is formed in a cylindrical shape whose diameter is enlarged toward the tip corresponding to the first clutch shaft, and the first clutch shaft is used as a second clutch shaft. On the other hand, when the needle roller is inserted until the needle roller becomes unrotatable, both clutch shafts are allowed to rotate together, and the frictional force selecting means includes a case that rotatably supports the second clutch shaft, A slide ball supported on the peripheral surface, and a guide groove formed on the outer peripheral surface of the second clutch shaft so as to engage with the slide ball, wherein the guide groove is provided when the slat is in a fully closed state. Until both clutch shafts are integrated Positioning the second clutch shaft so as to rotate, and guiding the second clutch shaft to a position where the needle roller can rotate when the slat is rotated to the fully closed state. Claim 3
A slat drive for a horizontal blind as described. 5. A clutch spring is disposed between the first clutch shaft and the second clutch shaft, and the rotation of the first clutch shaft is controlled by the friction force of the clutch spring. And the frictional force selecting means is a rotation preventing portion provided in a case that rotatably supports the first and second clutch shafts, and the rotation preventing portion is
4. The slat drive device for a horizontal blind according to claim 3, wherein when the slat is rotated to a fully closed state, the slat comes into contact with the clutch spring in a direction to reduce the frictional force. 6. A rotating torque is transmitted between the second clutch shaft and the angle adjusting shaft from the second clutch shaft to the angle adjusting shaft, and the rotation torque is transmitted from the angle adjusting shaft to the second clutch shaft. The slat drive device for a horizontal blind according to claim 5, wherein a torque transmission device that does not transmit a rotational torque is interposed.