JP2000220368A - Blind device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a blind device in which an appropriate braking force is exserted on the downward movement resulting from its own weight of the blind member and it can be surely lowered to the lowermost position and it can be lifted up by a light force when lifting it up. SOLUTION: A rise and fall shaft 8 from which a blind member is hangingly supported can be rotated by an operational cord 7. A clutch means 21 is arranged between the shaft 8 and the cord 7, and the blind member can be lowered by the own weight when the clutch means 21 is released by the operation of the cord 7. meanwhile, a braking device controlling the rotation of the shaft 8 in the gravitational descent resulting from its own weight is connected to the shaft 8. The braking device is provided with a speed increasing ring rows having worm and worm wheel and a centrifugal governor. The braking force is varied so that the braking force is made large when the rotary load acting on the rise and fall shaft 8 is large, and it is made small when the rotary load acting on the shaft is small.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a blind device for lowering a plurality of horizontally supported blind members such as slats by its own weight.

[0002]

2. Description of the Related Art Conventionally, as one kind of blind, a common operation rod suspended from one end of a head box in order to easily and quickly perform a lifting operation and an angle adjustment operation of a plurality of horizontally supported slats. There is known a device for operating such operations (see JP-A-4-269293).

The horizontal blind disclosed in Japanese Patent Application Laid-Open No. 4-269293 is capable of adjusting the angle of a slat by rotating an operation rod suspended from one end of a head box. When the operation rod is further rotated, the slat can be moved up and down. When the operating rod is pulled downward, the clutch is released and the slat descends by its own weight.

As described above, the slat angle adjustment operation and the elevating operation can be performed by the operation using the common operation rod. In particular, the slat can be lowered by its own weight by pulling the operation rod downward. Thus, Japanese Patent Application Laid-Open No. 4-26
The horizontal blind device disclosed in Japanese Patent No. 9293 can lower the slats without rotating the operation rod.
In addition, in this horizontal blind, a speed reducer is connected to an elevating shaft (an axis that suspends the slat via an elevating cord) in order to prevent the slat from dropping abruptly. It is designed to descend.

Japanese Utility Model Laid-Open Publication No. Sho 61-43398 discloses a technique for braking the rotation of a winding pipe when a roll screen is wound up.
Japanese Patent Application Laid-Open Publication No. HEI 10-125566 discloses a governing device for adjusting a descending speed of a slat of a shutter curtain. By using these speed control devices, a brake is applied when the blind member is raised or lowered.

Furthermore, the horizontal blind slat elevating device described in Japanese Patent Application Laid-Open No. 7-324572 is provided with a governor device connected to an elevating shaft. Since the governor apparatus exerts a stronger braking force as the rotation of the elevating shaft increases, the rotational speed of the elevating shaft is always suppressed to a certain value or less. In addition, the governor device idles when the elevating shaft rotates in the direction of hoisting the slat, and does not exert its braking force, so that the hoisting operation can be performed with a light force. .

[0007]

However, in the blind apparatus disclosed in Japanese Patent Application Laid-Open No. 4-269293, when a slat composed of multiple stages descends by using its own weight, it is suspended and supported by the lower end of a lifting cord. As the bottom rail serving as the lower plate approaches a predetermined position (lowest position), the rotational load applied to the lifting shaft via the lifting cord gradually decreases, while the above-described braking force remains constant. I have.

Therefore, immediately before the end of the lowering operation (when the bottom rail approaches the lowermost position), the brake is applied too much and the slats and the bottom rail do not operate smoothly or the slats and the bottom rail do not move smoothly. There is a problem that the vehicle stops halfway without descending. In order to avoid such danger, if you reduce the braking force,
The descending speed in the upper direction becomes too high, so that stop control at a desired position cannot be performed properly, and the commercial value decreases.

The braking technique disclosed in Japanese Utility Model Laid-Open Publication No. Sho 61-43398 is for the time of winding, and since the winding force at a predetermined position and the weight of the curtain to be wound at that time generally have a proportional relationship, the braking technique is If the hoisting force stored by lowering the hoisting force is configured to always surpass the weight and braking force of the curtain, the problem of stopping halfway even when braking the hoisting operation does not occur. This is because this technique is intended for winding a roll screen, and does not require a delicate adjustment of the braking force as when the curtain is lowered by its own weight.

In the shutter curtain disclosed in Japanese Utility Model Laid-Open Publication No. Hei 7-26600, a braking force acts even when the curtain is raised. This is because a motor is used when raising the curtain, so that there is no problem even if a slight braking force is applied when raising the curtain. In addition, since the shutter curtain governor has a structure in which the weight portion is supported by the supporting pieces on both sides, the frictional force becomes constant when the centrifugal force exceeds a predetermined value, and the frictional force increases as the centrifugal force increases. There is no such configuration.

The slat lifting / lowering device disclosed in Japanese Patent Application Laid-Open No. 7-324572 transmits the rotation of the lifting / lowering shaft to a rotary plate member which is the final stage of the wheel train by increasing the speed via a wheel train of spur gears. In addition, there is provided a braking device utilizing a frictional force generated when the rotary plate member rotates at a high speed while sliding on the case body. The braking device has a configuration in which spur gears are arranged in multiple stages in order to obtain a high speed increase ratio necessary for obtaining a more reliable braking force. Therefore, there arises a problem that the number of components of the braking device is large and the entire braking device is large. In addition, the rotational resistance due to friction between the spur gears assembled in multiple stages increases, and there is a possibility that braking is excessively effective.

Further, the braking device used in each of the above-mentioned devices is constituted by a train of wheels, frictional members, and the like when the lifting shaft is excessively rotated due to, for example, pulling a blind member such as a slat with an excessive force. The rotation of the braking member or the like becomes too fast, and there is a risk that the internal mechanism is destroyed.

[0013] An object of the present invention is that when a blind member such as a slat descends by its own weight, an appropriate brake in accordance with the descending speed and the rotational load is applied, and the blind member can be surely lowered to the lowest position. Moreover, it is an object of the present invention to provide a blind device having a compact structure of a braking device. Another object of the present invention is to provide a blind device that facilitates the operation of raising and lowering the blind member and adjusting the angle of the blind member using a common operation unit. Another object of the present invention is to provide a blind device having a braking device that is not destroyed even when an excessive rotation load is applied to the elevating shaft.

[0014]

SUMMARY OF THE INVENTION In order to achieve the above object, the present invention provides a blind member suspended from an elevating shaft via an elevating cord, and rotating the elevating shaft to perform the elevating operation of the blind member. In a blind device comprising an operating means for operating and a clutch means for switching between rotation and stop of the elevating shaft, wherein the blind means is capable of releasing the clutch means based on the operation of the operating means and lowering the blind member by its own weight. An input shaft for inputting the rotation of the elevating shaft, a speed-up gear train for speeding up and transmitting the rotation input to the input shaft, and rotating as a part of the speed-up wheel train and according to the rotation speed A centrifugal governor comprising a rotating plate member that expands in the outer peripheral direction and a sliding contact case that is disposed around the rotating plate member and that can slidably contact the rotating plate member that expands; A braking device including a worm wheel and a worm wheel is connected to the lifting shaft, and when the blind member lowers its own weight, the braking force is increased when the rotating load applied to the lifting shaft is large, and when the rotating load is small, the braking force is reduced. The braking force is varied so as to be small.

According to another aspect of the present invention, in addition to the above-described blind device, the rotating plate member is integrally formed on a rotation center shaft that rotates as a part of the speed increasing gear train and radially outside the rotation center shaft. And an expanding plate integrally formed of an elastic member with a weight portion which expands in the outer peripheral direction by rotation.

According to another aspect of the present invention, in addition to the above-mentioned blind device, a one-way rotation transmitting means for transmitting only the rotation of the elevating shaft when the blind member descends to the input shaft or the speed increasing gear train to the rotary plate member. Is provided so as not to apply the braking force of the braking device when raising the blind member.

According to another aspect of the present invention, in addition to the above-described blind device, an elevating shaft is disposed in a head box installed above the blind member, and the blind member is constituted by multi-stage slats. The ladder cord for adjusting the hang from the headbox.

According to still another aspect of the present invention, in addition to the above-described blind device, an angle adjusting shaft for hanging a slat through a ladder cord is provided in a head box, and the turning operation of the angle adjusting shaft is performed by operating means. Also provided is a clutch means which is also used and releases the connection between the operating means and the angle adjusting shaft when the slat is moved up and down by the operating means.

Another aspect of the present invention provides a blind member suspended from an elevating shaft via an elevating cord, operating means for rotating the elevating shaft for performing the elevating operation of the blind member, and rotation of the elevating shaft. And a clutch device for switching between a stop and a stop, wherein a lifting device is disposed on an upper portion of the blind member in a blind device capable of releasing the clutch device based on the operation of the operating device and lowering the blind member by its own weight. The ladder cord for adjusting the angle of the slat is suspended from the head box, and the slat is inserted into the head box through the ladder cord. A hanging angle adjusting shaft is provided, and when the slat is turned to the fully closed state, the operating means and the angle adjusting shaft A second clutch means for releasing the connection is provided such that when the blind member lowers its own weight, the braking force is increased when the rotation load applied to the lifting shaft is large, and the braking force is reduced when the rotation load is small. In addition, a braking device for varying the braking force is connected to the lifting shaft.

Another aspect of the present invention provides a blind member suspended from an elevating shaft via an elevating cord, operating means for rotating the elevating shaft for performing the elevating operation of the blind member, and rotation of the elevating shaft. And a clutch device for switching between a stop and a stop, wherein a lifting device is disposed on an upper portion of the blind member in a blind device capable of releasing the clutch device based on the operation of the operating device and lowering the blind member by its own weight. The ladder cord for adjusting the angle of the slat is suspended from the head box, and the slat is inserted into the head box through the ladder cord. A hanging angle adjusting shaft is provided, and when the slat is turned to the fully closed state, the operating means and the angle adjusting shaft An input shaft provided with second clutch means for releasing the connection, and inputting the rotation of the elevating shaft, a speed-up gear train for increasing and transmitting the rotation input to the input shaft, and the speed-up wheel train A centrifugal governor comprising a rotating plate member that rotates as a part of the rotating plate member and expands in the outer peripheral direction in accordance with the rotation speed thereof, and a sliding contact case disposed around the rotating plate member and capable of slidingly contacting the expanding rotating plate member. And a braking device including a worm and a worm wheel in the speed increasing gear train is connected to the lifting shaft, and when the blind member lowers its own weight, the braking force is increased when the rotational load applied to the lifting shaft is large. When the rotational load is small, the braking force is varied so that the braking force is small.

Another aspect of the present invention is directed to a blind member suspended from an elevating shaft via an elevating cord, operating means for rotating the elevating shaft for performing the elevating operation of the blind member, and rotation of the elevating shaft. An input shaft for inputting rotation of an elevating shaft in a blind device having a clutch device for switching between a stop and a stop, and capable of releasing the clutch device based on the operation of the operating device and lowering the blind member by its own weight. And a rotating member that rotates based on the rotation input to the input shaft, and applies a predetermined resistance to the rotation of the rotating member to apply braking to the rotation of the elevating shaft, and to apply excessive torque to the rotating member. Is connected to a lifting shaft provided with an overload prevention means for preventing the rotation member from being over-rotated.

In the blind device of the present invention, when the blind member lowers its own weight, a braking device that varies a braking force by a rotating load that changes according to the weight is connected to the lifting shaft. Therefore, in the initial stage of descent when the rotational load on the elevating shaft is large, a large braking force acts to lower the blind member at an appropriate speed, and at the end of the descent when the rotational load is small, the braking force becomes small, and the blind member becomes smooth. And descend to the end. The braking device includes a speed increasing gear train including a worm and a worm wheel, and a centrifugal governor. As a result, the braking device has a compact configuration and a very high speed increase ratio, and the braking force is extremely small when the rotation of the elevating shaft is low, and the braking force is extremely high at high speed. can do. In addition, when the elastic member having the weight portion expanding to the outer periphery is provided on the rotating plate member, it is possible to perform a more reliable and smooth braking operation.

Further, if the one-way rotation transmitting means is provided in the braking device so that the braking force of the braking device does not work when the blind member is raised, it can be raised lightly even by manual operation.

Further, the operating means is used for both the raising and lowering operation and the angle adjusting operation, and the connection of the angle adjusting shaft for performing the angle adjusting operation to the operating means is released by releasing the clutch means during the raising and lowering operation. Configuration
Both operations can be easily performed by one operating means, and at the time of raising operation of the blind member, no extra load is applied and the blind member can be raised with a light force.

Further, if an overload preventing means for preventing an excessive torque from being inputted to the rotating member of the braking device is provided,
During the descent of the blind member's own weight, the elevating shaft rotates strongly by operating the operating means in the descending direction, etc., and even if excessive torque is input to the input shaft of the braking device, the torque is applied to the rotating member. Not transmitted. Therefore, damage to the internal mechanism is avoided.

[0026]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of a blind device according to the present invention will be described below with reference to FIGS.
What is described below is a so-called horizontal blind device in which multiple slats are suspended from a head box.

As shown in FIG. 1, a horizontal blind device 1 according to the present embodiment includes a head box 2, a plurality (specifically, two) ladder codes 3 suspended from the head box 2, and a plurality of ladder codes 3. (Specifically, two) elevating cords 4, a plurality of slats 5 as blind members suspended from the head box 2 via each ladder cord 3 and each elevating cord 4, and each ladder cord 3, It has a bottom rail 6 connected to the lower end of each lifting cord 4, and an operation cord 7 as operating means for performing a lifting operation and an angle adjustment of each slat 5.

The head box 2 is adapted to be mounted on an upper end portion of a window frame or the like (not shown) and has a space for storing a mechanical portion of the apparatus. In the head box 2, an elevating shaft 8 for elevating the slat 5 and an angle adjusting shaft 9 for adjusting the angle of the slat are rotatably arranged. In the head box 2, a slat driving unit 10 for rotating the lifting shaft 8 and the angle adjusting shaft 9 to perform the raising and lowering operation and the angle adjusting operation of the slat 5, and the raising and lowering shaft when the slat 5 falls by its own weight. A braking device 11 for braking the rotation of the motor 8 is provided.

The elevating cord 4 has an upper end wound around a cord take-up portion 12 inserted and fixed to an elevating shaft 8 in the head box 2. On each slat 5 supported horizontally,
The lifting cords 4 are respectively penetrated. The lower end of the lifting cord 4 is connected to the bottom rail 6. Therefore, when the lifting shaft 8 is rotated in one direction, the winding unit 1 is rotated.
The lifting cord 4 is spirally wound around 2. Then, the bottom rail 6 is raised toward the head box 2, that is, upward, while collecting the slats 5. Conversely, when the elevating shaft 8 is rotated in the other direction, each slat 5 and the bottom rail 6 are lowered. Since the weight of each slat 5 and the bottom rail 6 is applied to the lifting shaft 8 via the lifting cord 4, the lifting shaft 8 always rotates in the other direction, that is, the direction in which the slat 5 and the bottom rail 6 are lowered. try to.

However, the horizontal blind device 1 according to the present embodiment has a mechanism for stopping the rotation of the elevating shaft 8 in the descending direction in the slat drive unit 10, as will be described later. Each slat 5 can be stopped at an arbitrary position. Further, in the horizontal blind device 1 according to the present embodiment, as will be described later, when the first clutch means 21 is released by operating the operation code 7, the lifting shaft 8 becomes free with respect to the slat drive unit 10. The slats 5 and the bottom rail 6 can be lowered by their own weight. At the time of the self-weight drop, the above-described braking device 11 is effective while varying the braking force according to the weight of the bottom rail 6 and the slats 5 arranged on the bottom rail 6, and the slats 5 are appropriately positioned. Make sure to descend at the speed and to the lowest position.

The ladder-shaped ladder cord 3 is inserted into and fixed to an angle adjusting shaft 9 in the head box 2.
3 has its upper end fixed. Each slat 5 is placed and fixed on each stage of the ladder cord 3. The lower end of the ladder cord 3 is connected to the bottom rail 6. Therefore, the slats 5 are arranged apart from each other by the stroke of the ladder of the ladder cord 3. With this configuration, when each slat 5 is lowered to a predetermined position, it is supported by each step of the ladder cord 3. Therefore, the weight of each slat 5 supported by the ladder cord 3 does not fall on the elevating shaft 8 via the elevating cord 4.

The slat drive unit 10 is driven by operating the operation code 7. The slat drive unit 10 rotates the elevating shaft 8 to lift the slat 5 upward,
Rotating the angle adjusting shaft 9 to adjust the angle of the slat 5 or stopping the rotation of the elevating shaft 8 and the angle adjusting shaft 9 at a predetermined position to adjust the hanging position and the angle of the slat 5. Mechanism. That is, in the horizontal blind device 1 of the present embodiment, the operation code 7
Is an operating means capable of both raising and lowering the slat 5 and adjusting the angle. Further, the slat drive unit 10
By releasing the first clutch means 21 to be described later, the connection with the lifting shaft 8 is released, and the slat 5 can be lowered by its own weight.

In this embodiment, the slat drive unit 10 is disposed at one end of the head box 2 (the right end in FIG. 1). As shown in FIGS. 2 and 3, the slat drive unit 10 includes a case body 14 having an internal space divided into two spaces, and a tilt clutch case 15 mounted above the case body 14. Have.

The case body 14 is formed by fitting an upper case 14a disposed on the upper side in FIG. 2 and a lower case 14b disposed on the lower side in FIG.
c is fitted. Inside the case body 14, the inner space is divided into two spaces 14d, 1d.
There is provided a wall 14f for partitioning into 4e. The wall portion 14f is formed with a bearing hole portion 14g that rotatably supports a fitting shaft 17 described later. Also, coaxially with the bearing hole 14g of the case body 14, a bearing hole 14h for rotatably supporting the input shaft 16 described later and a bearing hole for rotatably supporting the central shaft 20a of the clutch plate 20 described later. The portions 14j are respectively formed.

An input shaft 16 is rotatably arranged in the first space 14d of the case body 14. This input shaft 16
Is a bearing hole 1 having a tip portion formed in the case body 14.
An operation pulley 16a around which a loop-shaped operation cord 7 is wound is fixed to the projected portion from the outside of the case body 14 from 4h. Thus, the input shaft 16 is rotated by the operation of the operation code 7 via the operation pulley 16a. The input shaft 16
An input gear (not shown) is formed on the outer periphery of the.

On the other hand, in the second space 14 e of the case body 14, a fitting shaft 17, a cam shaft 18 serving also as a first clutch plate supported on the other end of the fitting shaft 17, and this cam shaft A first clutch means 21 comprising a second clutch plate 20 which can be disengaged from the first clutch plate 18; a coil spring 19 which slides the cam shaft 18 on the fitting shaft 17 to bias the cam shaft 18 toward the second clutch plate 20; Is arranged.

The fitting shaft 17 is connected to the wall 14f of the case body 14.
Is rotatably supported by a fitting hole 14g formed in the hole. One end of the fitting shaft 17 is fitted to the fitting hole 14.
g, and protrudes toward the first space 14d. An end portion 17a of the fitting shaft 17 serving as a protruding portion into the first space 14d is provided with a hole 16c formed at the other end of the input shaft 16.
Are fitted so as to be relatively rotatable. On the other hand, a further end of the end 17b opposite to the end 17a of the fitting shaft 17 is formed in a square shaft shape, and is inserted into a square hole formed in the cam shaft 18. With this configuration, the camshaft 1
8 rotates integrally with the fitting shaft 17 and
Is supported movably in the axial direction.

A planetary gear mechanism (not shown) is interposed between the fitting shaft 17 and the input shaft 16, and the rotation of the input shaft 16 is transmitted to the fitting shaft 17 at a reduced speed at a predetermined reduction ratio. It has become. When the fitting shaft 17 rotates, the cam shaft 18 rotates to rotate the elevating shaft 8 in the slat lifting direction via the first clutch 21 in the connected state. This fitting shaft 17 is used for the input shaft 1.
After the carrier 22 of the planetary gear mechanism rotates by a predetermined angle based on the rotation of 6, the carrier 22 engages with the carrier 22 and integrally rotates. That is, the rotation start timing of the fitting shaft 17 is determined by rotating the drive gear 35 and the rotating shaft 36 described later in the tilt clutch case 15 by a predetermined angle (=
This is the time when each slat 5 is rotated until the angle adjusting shaft 9 is rotated by a predetermined angle until it is substantially vertical.

The cam shaft 18 rotates around the fitting shaft 17 and has a cam groove 24 on the outer peripheral surface. At the tip of the camshaft 18, teeth 26 that mesh with teeth 25 formed on the second clutch plate 20 are formed.
On the other hand, the second clutch plate 20 has teeth 25 which can be engaged with and disengaged from the camshaft 18, and a center shaft 20 a serving as a rotation center thereof is inserted into the case
4 so as to protrude outside.

One end of the elevating shaft 8 is fixed to the end of the central shaft 20a. Therefore, the first
Cam shaft 18 also serving as second clutch plate and second clutch plate 2
When the camshaft 18 rotates in a state where the gears are engaged with each other, the rotation is transmitted to the elevating shaft 8. The above-described coil spring 19 is disposed between the end face of the camshaft 18 and the wall 14f of the case body 14, and the camshaft 18 is attached to the side that engages with the second clutch plate 20. I'm going.

The outer peripheral surface of the cam shaft 18 is
A cam groove 24 having a semicircular cross section is formed continuously in the circumferential direction on the outer peripheral surface thereof. In addition, a concave portion 27 formed in a long groove shape in the axial direction of the cam shaft 18 is provided on the inner wall of the case body 14 facing the cam groove 24. A slide ball 28 is provided between the concave portion 27 and the cam groove 24 so as to fit therein.

Therefore, the slide ball 28 itself is
7 only slightly moves, but when the camshaft 18 rotates, the slide ball 28 relatively moves along the shape of the cam groove 24. Thereby, the cam shaft 18 relatively moves in the axial direction according to the shape of the cam groove 24.

The shape of the cam groove 24 will be described with reference to FIG. FIG. 4 is a development view of the outer peripheral surface of the cam shaft 18. The cam groove 24 is formed on a first surface continuous on the peripheral surface of the cam shaft 18.
From the bent portion 24c of the first groove 24a to the tip end side of the camshaft 18 (toward the first clutch means 21), and after a predetermined rotation angle (a rotation angle of approximately 270 °), the converging portion 24d and a second groove 24b that gradually converges toward the first groove 24a. The bent portion 24c is formed at a branch portion between the first groove 24a and the second groove 24b, and is formed to bend toward the second groove 24b.

When the cam shaft 18 having the cam groove 24 as described above is rotated by the fitting shaft 17 in a direction in which the slat 5 is pulled up, the slide ball 28 is relatively moved with respect to the cam groove 24 in FIG. Move in the direction of arrow A. In this state, that is, in a state in which the operation cord 7 is operated to raise the slats 5 and the bottom rail 6, the cam shaft 18 is urged in the direction of arrow C by the urging force of the coil spring 19. As a result, the slide ball 28
Moves only in the first groove 24a which is continuous in the circumferential direction.

When the slide ball 28 passes through the bent portion 24c, the recess 27 allows the slide ball 28 to move in the axial direction. The camshaft 18 does not move in the axial direction. Therefore, the camshaft 18 is always engaged with the second clutch plate 20, and the operation cord 7 can perform a hoisting operation.

Conversely, when the cam shaft 18 is rotated in the direction of lowering the slat 5 by the fitting shaft 17, the slide ball 28 moves in the direction of arrow B relative to the cam groove 24 in FIG. Moving. Then, the slide ball 28 is guided from the first groove 24a to the second groove 24b via the bent portion 24c. Thereby, the camshaft 18 moves in the direction indicated by the arrow D in FIG. 4 against the biasing force in the direction indicated by the arrow C, and moves away from the second clutch plate 20. (See FIG. 3). As a result, the lifting shaft 8 can be lowered by the weight of the slats 5 and the bottom rail 6.

If the operation cord 7 is rotated in the pulling-up direction while the slats 5 and the like are in a lowered state,
Since the slide ball 28 returns to the first groove 24a side, the second clutch plate 20 and the cam shaft 18 are connected again.
Therefore, if the lifting operation is performed with the operation code 7, the winding operation of the slat 5 can be started again.

When the input shaft 16 is rotated by operating the operation cord 7 in the direction in which the slats 5 and the bottom rail 6 are lifted, the rotational force of the input shaft 16 is reduced by the action of an operation delaying means 29 which also functions as a one-way clutch described later. Are transmitted to the camshaft 18 with a delay of a predetermined time. When the camshaft 18 rotates, the teeth 26 of the camshaft 18 and the teeth 25 of the second clutch plate 20 mesh with each other by the action of the cam groove 24 as described above. The shaft 8 rotates.

That is, the first space 14 of the case body 14
d on the inner periphery of the case body 14 near the wall 14f,
When the angle adjusting shaft 9 is rotated by the operation of the operation code 7, the rotation of the input shaft 16 is not immediately transmitted to the elevating shaft 8 side, and the rotation of the input shaft 16 is raised and lowered after the angle adjustment is completed. The operation delay means 29 which also serves as a one-way clutch for transmitting the power only in a predetermined direction while transmitting the power to the shaft 8 side.
Is arranged.

The operation delay means 29 includes a first engaging portion 30 formed on the carrier 22 of the planetary gear mechanism that operates by the rotation of the input shaft 16, and a first engaging portion 30 formed on the fitting shaft 17. , And a stop ring 32 and a stop ring case 33 disposed outside these.

The stop ring case 33 has a substantially cylindrical shape, and is fitted non-rotatably on the inner peripheral surface of the case body 14. The stop ring 32 is fitted on the inner peripheral surface of the stop ring case 33. The stop ring 32 is in the form of a coil spring, and prevents the force transmitted from the cam shaft 18 to the fitting shaft 17 from being transmitted to the input shaft 16 due to the frictional force between the stop ring 32 and the stop ring case 33. In addition, by reducing the frictional force, the power from the input shaft 16 is transmitted to the fitting shaft 17 to rotate the camshaft 18. further,
The fitting shaft 17 has a function of preventing the input shaft 16 from rotating due to rotation of the input shaft 16 for a predetermined period.

As shown in FIG. 5, both ends 32a and 32b of this stop ring 32 are bent toward the center at an angle of about 90 °. Stop ring 3
The first engaging portion 30 protruding from the carrier 22 (see FIG. 2) of the planetary gear mechanism that engages with the input shaft 16 in a space of approximately 270 ° sandwiched between the two end portions 32 a and 32 b of the second gear 2. Are projected in a range of approximately 130 °. Also,
In the space of approximately 90 ° sandwiched between both ends 32a and 32b of the stop ring 32, the second
Are projected.

With this configuration, even if the carrier 22 rotates at first due to the rotation of the input shaft 16, the first engagement portion 30 of the carrier 22 is moved between the both ends 32 a and 32 b of the stop ring 32. Just move the carrier 2
2 rotates idly with respect to the fitting shaft 17.

However, when the first engaging portion 30 of the carrier 22 comes into contact with one of the both ends 32a, 32b, the end portion of the stop ring 32 on the side contacted by the first engaging portion 30. Is pulled in a direction to reduce the diameter of the stop ring 32. Thereby, the frictional force between the stop ring 32 and the stop ring case 33 is reduced. Therefore, when the input shaft 16 rotates and the carrier 22 rotates in this state, in the stop ring case 33,
The first engagement portion 30, the stop ring 32, and the second engagement portion 31 are integrally rotated. As a result, the rotation of the input shaft 16 is transmitted to the fitting shaft 17 via the carrier 22 to rotate the cam shaft 18. This operation is an operation when the operation code 7 is operated.

On the other hand, when the fitting shaft 17 tries to rotate due to the rotational force acting on the fitting shaft 17 from the cam shaft 18, the second
Are engaged with the ends 32a, 32 of the stop ring 32.
b. That is, when the winding operation in the predetermined direction by the operation cord 7 is stopped in the middle or the like and the hand is released, the rotational force is transmitted from the camshaft 18 side to the fitting shaft 17 side by the weight of the slats 5 and the like.

When the camshaft 18 rotates and the end 32a or 32b of the stop ring 32 is pushed in a state where the first clutch means 21 is connected as described above, the stop ring 32 expands, and the stop ring 32 and the stop ring 32 are opened. The frictional force with the stop ring case 33 increases. For this reason, the fitting shaft 17
Is prevented, and the lifting shaft 8 is held so as not to rotate. As a result, the bottom rail 6 located at the lowermost end of the slat 5 can be held at an arbitrary position. That is, the number of the slats 5 arranged above the bottom rail 6 and suspended at regular intervals can be set to an arbitrary number.

A second clutch means 34 including the above-described tilt clutch case 15 is provided above the case body 14 configured as described above. The second clutch means 34 includes an operation code 7 and an angle adjusting shaft 9.
For engaging and disengaging with the input shaft 16 side and the angle adjustment shaft 9 side, respectively. Hereinafter, a specific configuration of the second clutch means 34 will be described.

A tilt clutch case 15 is mounted on the upper case 14a and the case cover 14c, and a drive gear 35 is rotatably supported in the tilt clutch case 15. The input gear (not shown) and the drive gear 35 can transmit rotation via a transmission gear (not shown). The rotation of the input gear is reduced at a predetermined reduction ratio and transmitted to the rotating shaft 36. It is supposed to be.
Due to such a configuration, when the rotation shaft 36 rotates in a state where the second clutch means 34 is connected, the rotation is changed to the second rotation.
Is transmitted to the angle adjusting shaft 9 through the clutch means 34 of
The angle adjusting shaft 9 rotates to adjust the angle of the slat 5.

A rotating shaft 36 serving as a center of rotation of the driving gear 35
A clutch spring 37 is wound near the tip of
Further, a clutch member 38 is supported at the tip of the rotating shaft 36 so as to be relatively rotatable. The clutch spring 3
As shown in FIG. 6, both end portions 37a and 37b of 7 are bent so as to protrude radially outward at a predetermined interval.

Both ends 37a of the clutch spring 37,
An engagement portion 38a protrudes from the clutch member 38 between the portions 37b. Then, when the rotating shaft 36 is rotated and one of the both ends 37a and 37b abuts on the engaging portion 38a, the abutted end is provided by the clutch spring 37.
It is pushed in the direction to reduce the diameter of. Therefore, in this state, the frictional force between the clutch spring 37 and the rotating shaft 36 increases. At this time, when the rotating shaft 36 is rotated, the clutch member 38 is rotated in the same direction via the clutch spring 37.

The upper case 14a is provided with a rotation preventing portion 39 which protrudes on the rotation trajectory of both ends 37a and 37b of the clutch spring 37. Then, the rotating shaft 36 is rotated, and both ends 37 of the clutch spring 37 are rotated.
When one of the a and 37b abuts against the rotation preventing portion 39, the abutted end is pushed in a direction to expand the clutch spring 37, and the clutch spring 3
The frictional force between the shaft 7 and the rotating shaft 36 decreases. As a result, the rotating shaft 36 idles with respect to the clutch spring 37.

A substantially cylindrical coil frame 40 is fitted and fixed between the tilt clutch case 15 and the upper case 14a on the tip side of the clutch member 38, that is, on the angle adjusting shaft 9 side of the clutch member 38. , Its coil frame 4
0 on the inner peripheral surface of the spring coil-shaped stop ring 41
Is fitted. As shown in FIG. 7, both ends 41a and 41b of the stop ring 41 protrude radially inward at a predetermined interval, and an engagement portion 38b protrudes from the clutch member 38 between the both ends 41a and 41b. ing.

Then, when the clutch member 38 is rotated,
The engagement portion 38b is connected to both ends 41a, 41 of the stop ring 41.
When it comes into contact with any one of b, the contacted end is pushed in a direction to reduce the diameter of the stop ring 41, and the frictional force between the stop ring 41 and the coil frame 40 is reduced. As a result, the stop ring 41 rotates integrally with the clutch member 38 as the clutch member 38 rotates.

Further, an engaging portion 42 a at one end of the tilt output shaft 42 protrudes into the coil frame 40. The other end of the tilt output shaft 42 is rotatably supported between the upper case 14a and the tilt clutch case 15. The stop ring 4 is formed by the engagement portion 42a on one end of the tilt output shaft 42 and the engagement portion 38b of the clutch member 38.
1 are sandwiched between both ends 41a and 41b. Therefore, when the clutch member 38 rotates, the tilt output shaft 42 integrally rotates via the stop ring 41.

Further, based on the rotation of the tilt output shaft 42, the engaging portions 42 a are connected to both ends 41 a, 4 a of the stop ring 41.
1b, the contacted end is pushed in a direction to expand the stop ring 41. Therefore, the frictional force between the stop ring 41 and the coil frame 40 increases, and the rotation of the tilt output shaft 42 is prevented. One end of the angle adjusting shaft 9 is fitted to the tip of the tilt output shaft 42 thus configured, and the slat is inserted through the cord tilting portion 13 and the ladder cord 3 based on the rotation of the angle adjusting shaft 9. An angle adjustment of 5 is performed.

As described above, the lifting / lowering shaft 8, which can be connected to / disengaged from the operation cord 6 via the first clutch means 21, is provided with a rotational force based on the weight of the slats 5 and the bottom rail 6. 4 and the winding section 12. At this time, the weight of the slat 5 and the bottom rail 6 on the elevating shaft 8 changes according to the weight of the slat 5 that has not been lowered to a predetermined position.

That is, when the lifting cord 4 is almost completely wound around the winding section 12 and all the slats 5 are gathered on the head box 2 side, all the slats 5 are placed on the bottom rail 6. ing. Therefore, the weight of all the slats 5 and the bottom rail 6 is applied to the lifting shaft 8 via the lifting cord 4 in which the bottom rail 6 is fixed to the lower end. As a result, the total weight of the slats 5 and the bottom rail 6 on the lifting shaft 8 becomes large.

However, when each slat 5 descends to a predetermined position and is supported on each step of the ladder cord 3 suspended on the angle adjusting shaft 9, the weight of the slat 5 supported by the slat 5 is reduced. It will depend on the ladder code 3. Therefore, the weight applied to the elevating shaft 8 is that of the bottom rail 6 and the slats 5 mounted on the bottom rail 6, and the total weight is reduced. And each slat 5
Is completely lowered to the predetermined position, the weight applied to the lifting shaft 8 via the lifting cord 4 is only that of the bottom rail 6, and the weight applied to the lifting shaft 8 is further reduced.

As described above, the rotation speed of the elevating shaft 8 that supports the weight that varies depending on the degree of lowering of the bottom rail 6 is controlled by the braking device that varies the braking force to cope with the rotational load (= weight) applied to the elevating shaft 8. 11 is moderately controlled. That is, the braking device 11 changes the braking force so that the braking force is large when the rotational load applied to the lifting shaft 8 is large and small when the rotational load is small.

The camshaft 18 and the second clutch plate 20
When the rotational force based on the weight of the slats 5 and the like is transmitted to the camshaft 18 in a state in which
8 and try to rotate together. However, at that time, the second
Because the engaging portion 31 of the opening expands the stop ring 32,
The friction force between the stop ring 32 and the stop ring case 33 increases. As a result, the rotation of the fitting shaft 17 is prevented. Therefore, the self-weight drop of the slat 5 and the like is prevented. As a result, the bottom rail 6 and the slat 5 can be pulled up and down by the operation cord 7, or stopped at an arbitrary position.

When the camshaft 18 moves in the direction indicated by the arrow D shown in FIG. 2 to disengage the teeth 26 of the camshaft 18 from the teeth 25 of the second clutch plate 20, the second clutch The plate 20 is free with respect to the camshaft 18 and the slat 5
And the bottom rail 6 rotates based on its own weight drop.

The braking device 11 is connected to the other end of the elevating shaft 8 (near the end opposite to the side where the slat drive unit 10 is installed = left end in FIG. 1). As shown in FIGS. 8 and 9, the braking device 11 includes an input shaft 51 for inputting the rotation of the elevating shaft 8, and a speed increasing train that speeds up and transmits the rotation input to the input shaft 51. 52, a centrifugal governor 50, and a resin case 54 for incorporating these members.

The centrifugal governor 50 includes a speed increasing wheel train 52.
A rotating plate member 53 that rotates as the final stage and expands in the outer peripheral direction in accordance with the rotation speed, and a rotating plate member 53 that is fitted inside the case 54 and that is arranged with a predetermined clearance around the rotating plate member 53 and expanded. And a sliding contact case 55 capable of slidingly contacting the rotating plate member 53 to be opened. Also,
The case 54 includes a box-shaped case body 54 a and a case lid 5.
4b.

The input shaft 51 has a hollow hollow shaft portion 5 having a square insertion port 56 for inserting the tip of the elevating shaft 8.
1a, and an input gear 51b formed integrally with the hollow shaft portion 51a. The input shaft 51 includes a bearing portion 57 formed on a case body 54a and a case lid 54.
The both ends are rotatably supported by a bearing portion 54c formed at b.

The bearing portion 57 has a hole 57a for inserting the elevating shaft 8 into the case 54 through the inside and outside of the case 54, and a hole 57a from the edge of the hole 57a to the inside of the case body 54a. And an extended cylindrical portion 57b. Then, the input shaft 51 is inserted into the cylindrical portion 57b such that one surface of the input gear 51b is placed on the distal end portion of the cylindrical portion 57b. Note that a portion of the cylindrical portion 57b has a cutout shape, and the rotation locus of the worm wheel 58 that becomes a part of the speed increasing train 52 enters into the cutout portion 57c. I have.

The speed increasing gear train 52 includes an input gear 51b, a pinion 60 engaged with the input gear 51b, a worm wheel 58 disposed coaxially with the pinion 60, and a worm 59 engaged with the worm wheel 58. , Warm 59
And a rotary plate member 53 arranged coaxially. When the input gear 51b of the input shaft 51 rotates, the pinion 60 is rotated by the rotation of the input gear 51b, and the rotation of the pinion 60 is transmitted to the worm wheel 58 and the worm 59. The rotating plate member 53 is rotated.

The worm 59 includes a worm gear 59 a made of metal and meshing with the worm wheel 58, a spring winding part 59 b around which a coil spring 66 described later is wound, and a shaft part supported by the sliding contact case 55 of the centrifugal governor 50. 59c,
A shaft portion 59d which is an opposite end portion of the shaft portion 59c and an engaging portion 59e with which the rotating plate member 53 of the centrifugal governor 50 is engaged.
(See FIG. 10).

The pinion 60 and the worm wheel 58
Is rotatably supported on a metal fixed shaft 61 erected in a case 54. The worm wheel 58 is formed in a hollow shape in which one end in the axial direction is closed, and an insertion hole 58a for inserting the fixed shaft 61 is formed in the center of the closed end surface. In addition, this insertion hole 58a
, A cylindrical portion 58b extending from the edge portion toward the other end is formed. This cylindrical portion 58b is
It is a shaft portion for preventing the run-out of the worm wheel 58.

The pinion 60 has a cylindrical portion 60 a inserted into the internal space of the worm wheel 58, a flange portion 60 b extending in the radial direction, a gear portion 60 c, and a contact portion that contacts the cylindrical portion 58 b of the worm wheel 58. And a cylindrical shaft portion 60e having a contact portion 60d. At the center of rotation of the pinion 60, an insertion hole 60f for inserting the fixed shaft 61 is formed. And, the pinion 60 is
a is rotatably supported by the fixed shaft 61 with the a inserted into the worm wheel 58.

In the gap between the cylindrical portion 60a of the pinion 60 and the inner wall of the worm wheel 58, only the rotation of the elevating shaft 8 when the slat 5 descends is transmitted to the rotating plate member 53 of the centrifugal governor 50. A coil spring 62 is disposed as one-way rotation transmitting means for performing the rotation.

The coil spring 62 is arranged along the inner peripheral surface of the worm wheel 58. The coil spring 62 has a bent portion (not shown) directed toward the center at the upper end portion, and this bent portion is inserted into a slit (not shown) formed in the cylindrical portion 60 a of the pinion 60. You. As a result, the coil spring 62 is engaged with the pinion 60 and is integrally rotatable.

The coil spring 62 has a pinion 6
When the rotating shaft 8 receives the rotation of the elevating shaft 8 when the 0 descends the slat 5, it expands and makes strong contact with the inner wall of the worm wheel 58 to integrate the pinion 60 and the worm wheel 58. Therefore, when the slat 5 descends, the pinion 60 and the worm wheel 58 rotate integrally,
The rotational force input from the input shaft 51 is increased in speed and transmitted to the rotary plate member 53 of the centrifugal governor 50. Accordingly, when the slats 5 and the bottom rail 6 are lowered, the rotating plate member 53 rotates at a high speed and expands, and slides on the inner wall of the sliding contact case 55 to brake the rotation of the lifting shaft 8. Is to be applied.

On the other hand, when the pinion 60 rotates by receiving the rotation of the elevating shaft 8 when the pinion 60 winds the slat 5, the coil spring 62 contracts the diameter and causes the worm wheel 58 to rotate.
Idling against. Therefore, when the slat 5 is wound up, the rotation of the pinion 60 is not transmitted to the worm wheel 58, and the rotating plate member 53 of the centrifugal governor 50 is not rotated. Thereby, this braking device 11
Does not operate when the slats 5 are wound up, and can be smoothly wound up.

The shaft 59d of the worm 59 is supported by a worm support groove 63 formed in the case body 54a. The worm 59 is held in position by the worm support groove 63 by the holding projection 54d formed on the case lid 54b. A shaft portion 59c serving as the other end of the worm 59 is supported by a circular worm support hole 64 formed in a sliding contact case 55 mounted inside the case 54. The worm 59 supported at both ends in this manner
Are orthogonally engaged with the worm wheel 58, and are rotated by the worm gear 59a receiving the rotation of the worm wheel 58.

Worm 5 incorporated in sliding contact case 55
9 is assembled to the case 54 together with the sliding contact case 55. In this assembly, the shaft portion 59d of the worm 59 is inserted into the worm support groove 63, and at the same time, the sliding contact case 55
Is inserted into two vertical grooves 54e, 54e provided in the case main body 54a. At this time, the square portion 55a of the sliding contact case 55 is mounted on the two mounting portions 54f of the case body 54a. Thereafter, the case lid 54b is integrated with the case body 54a. At this time, the vertical grooves 54 provided in the case lid 54b are provided.
g into the square portion 55a and the two pressing portions 5
4h and 54h hold down the square portion 55a.

In the braking device 11 of the horizontal blind device 1 according to the present embodiment, since the combination of the worm wheel 58 and the worm 59 is used for the speed increasing wheel train 52, the speed increasing ratio is about 1:70. And has become very high. For this reason, it has high braking performance in a small space.

The sliding contact case 55 near the other end of the worm 59
The rotary plate member 53 is fitted inside. The rotating plate member 53 includes an expanding plate 53a formed of an elastic member such as rubber and expanding in the outer peripheral direction by rotating, and a loading member 65 for loading the expanding plate 53a. The expansion plate 53a and the loading member 65 rotate integrally.

As shown in FIG. 10, the expanding plate 53a is a substantially inverted S-shaped member having a hole 53b.
3b, and two arms 53d, 53 extending to the outer periphery of the rotation center shaft 53c.
d, and weights 53e, 53e formed continuously at the respective tips of the arms 53d, 53d.
Then, by rotating, the weight parts 53e, 53
e expands together with the arms 53d, 53d in the outer peripheral direction by centrifugal force, and when rotation stops, returns to the original state by elastic force. In addition, this expansion plate 53a
Is placed on one side of the disk portion 65a while being guided by the guide protrusions 65b of the loading member 65.

The loading member 65 is fitted to the worm 59 to such an extent that the worm 59 rotates integrally with the worm 59 when the worm 59 rotates with a normal rotational force. The loading member 65 includes a disk portion 6 for loading the expanding plate 53a.
5a, a guide protrusion 65b provided on one surface of the disk portion 65a, and a cylindrical portion 65c formed integrally with the disk portion 65a. An insertion hole 65d is formed for letting through the hole.

The insertion hole 65d and the cylindrical hole of the cylindrical portion 65c form a series of passages. The cylindrical portion 65c
Is provided with a slit 65e for mounting the bent portion 66a of the coil spring 66 for preventing overload. A coil spring 66 for preventing overload, in which the bent portion 66a is fitted into the slit 65e, is provided inside the cylindrical portion 65c.

That is, the coil spring 66 is
a is fitted into the slit 65e of the loading member 65, and the loading member 65 and the spring winding portion 59 of the worm 59 are fitted.
b. The coil spring 66 is normally wound so as to be in sliding contact with the outer periphery of the spring winding portion 59b. For this reason, in the case of a normal rotational force, the rotational force of the worm 59 is transmitted to the loading member 65 and both of the worm 59 and the worm 59 are transmitted.
5 rotates integrally.

On the other hand, when the loading member 65 rotates while an excessive rotational load is applied to the worm 59, the coil spring 66 expands and idles with respect to the worm 59. As a result, the connection between the worm 59 and the loading member 65 is cut off, and an excessive rotational force is not transmitted to the loading member 65. Therefore, the rotating plate member 53 does not rotate.

The rotating plate member 53 thus formed is
When the lifting shaft 8 rotates in the lowering direction of the slat 5, FIG.
Rotate integrally with the worm 59 in the direction of arrow E. At this time, the weight portions 53e, 53e of the expanding plate 53a of the rotating plate member 53 are turned into arm portions 53d, 53d in accordance with the rotational force.
At the same time, it expands in the outer circumferential direction and slides on the inner wall of the sliding contact case 55 disposed outside with a clearance. The weight portions 53e, 53e of the expanding plate 53a and the sliding contact case 5
The sliding of the lifting shaft 8 is braked by the sliding contact with the lifting shaft 5.

The weight portions 53e, 53e of the expanding plate 53a
The 53e expansion is variable depending on the rotation speed. That is,
When the rotation speed is high, the spread increases, and the frictional force due to the sliding contact with the sliding contact case 55 increases. On the other hand, when the rotation speed is low, the expansion of the weight portions 53e, 53e of the expansion plate 53a decreases, and the frictional force due to sliding contact with the sliding contact case 55 decreases.

From this, during the initial descent operation in which the weight of the slat 5 on the elevating shaft 8 is large, the elevating shaft 8
Is high, the braking force generated in the braking device 11 is large, and conversely, at the end of descent where the weight of the slat 5 applied to the lifting shaft 8 is small, the rotation of the lifting shaft 8 is slow, and thus the braking device 11 generates the braking force. The braking force is reduced. Therefore,
In the horizontal blind device 1 of the present embodiment, the slats 5
When the vehicle descends its own weight, the braking force is varied from the initial descent to the end of the descent, so that the descent is always performed at an appropriate speed and the descent to the lowest position is ensured.

Next, the operation of the above-described horizontal blind device 1 will be described. First, an operation for adjusting the angle of the slat 5 will be described.

In order to perform the angle adjustment operation of the slat 5,
When the operation code 7 is operated in an arbitrary direction, the input shaft 16 is rotated via the operation pulley 16a, and this rotational force is input to the drive gear 35 via a transmission gear (not shown).
Thereby, the drive gear 35 and the rotating shaft 36 rotate integrally. Then, the clutch member 38 rotates together with the clutch spring 37 based on the rotation of the rotating shaft 36, and the tilt clutch shaft 42 rotates together with the stop ring 41 based on the rotation of the clutch member 38. As a result, the angle adjusting shaft 9 rotates, and the angle of the slat 5 is adjusted by this rotation.

Then, with the rotation of the input shaft 16, the rotation shaft 36, the clutch spring 37, the clutch member 38 and the tilt clutch shaft 42 until the slat 5 stands upright.
Is rotated, first, one of both ends 37a, 37b of the clutch spring 37 comes into contact with the rotation preventing portion 39 of the upper case 14a. In this state, when the rotation shaft 36 further rotates in the same direction, the clutch spring 37 expands, and the rotation shaft 36 idles with respect to the clutch spring 37.

Therefore, the connection between the rotating shaft 36 and the clutch spring 37 is cut off, and the second clutch means 34 is released. As a result, the torque of the input shaft 16 is not transmitted to the angle adjustment shaft 9 side. For this reason, even if the rotation of the slat 5 is stopped and the operation cord 7 is continuously operated, the slat 5 is rotated to the vertical position and does not further rotate in the same direction.

In such an operation of adjusting the angle of the slat 5, the carrier 22 of the planetary gear mechanism is rotated based on the rotation of the input shaft 16. Since the slats 5 are rotated until the slats 5 become vertical before engaging with the second engaging portions 31, the lifting shaft 8 is not rotated during the angle adjustment operation of the slats 5.
As a result, when the angle of the slat 5 is adjusted, the bottom rail 6 is not moved up and down. The raising operation or the lowering operation of the slat 5 is started by further operating the operation cord 7 in the same direction after the above-described angle adjusting operation.

Next, the operation at the time of raising the slat 5 and the bottom rail 6 will be described.

In order to perform the lifting operation of the slat 5,
First, the slats 5 are set to a position where the slats 5 are overlapped in parallel (= a state in which light is blocked) by the above-described angle adjustment operation. afterwards,
When the operation code 7 is further operated in the lifting direction, the input shaft 16 is rotated in the slat lifting direction via the operation pulley 16a. Then, the carrier 2 of the planetary gear mechanism
As the 2 rotates, the stop ring 32 is tightly wound and idles with respect to the stop ring case 33. On the other hand, the rotation of the carrier 22 causes the first engagement portion 30 of the carrier 22 to engage with the second engagement portion 31 of the fitting shaft 17. For this reason, the fitting shaft 17 receives the rotation of the input shaft 16 and rotates together with the cam shaft 18.

At this time, the cam shaft 18 rotates in the direction indicated by the arrow B in FIG. For this reason, the slide ball 28 arranged on the outer periphery of the camshaft 18 relatively moves in the first groove 24a of the camshaft 18 in the direction of arrow A in FIG. As a result, the cam shaft 18 does not move in the axial direction. For this reason,
The teeth 26 of the camshaft 18 and the teeth 25 of the second clutch plate 20
Is to maintain the meshed state. Therefore, the camshaft 1
8 is transmitted to the second clutch plate 20, and the second clutch plate 20 rotates integrally with the camshaft 18. Thus, the lifting shaft 8 connected to the second clutch plate 20
Rotates, and the lifting cord 4 is wound up. As a result,
The bottom rail 6 is lifted, and is sequentially pulled up to the head box 2 side together with the bottom rail 6 from the slats 5 arranged on the bottom rail 6 side.

When the elevating shaft 8 is rotating in the slat hoisting direction, the braking device 11
Does not work. That is, when the lifting shaft 8 rotates, the input shaft 5 of the braking device 11 is
1 rotates. Then, the rotation of the input shaft 51 is transmitted to the pinion 60 of the speed increasing gear train 52, and the pinion 60 rotates.

When the pinion 60 rotates in this way, one end fits into a slit (not shown) of the pinion 60, and the coil spring 62, which is a one-way rotation transmitting means disposed on the inner periphery of the worm wheel 58, is tightly wound. .
For this reason, the coil spring 62 is
8, and the rotational force from the input shaft 51 is not transmitted to the rotary plate member 53 side of the centrifugal governor 50. As a result, when hoisting the slat, the elevating shaft 8 can rotate without being affected by the braking force of the braking device 11, and the burden on the operator during hoisting can be reduced.

After the slats 5 and the bottom rail 6 have been pulled up to desired positions, the operation cord 7 is released.
Due to the weight of the slats 5 and the bottom rail 6, a rotational force acts on the elevating shaft 8 in a direction of lowering the slats 5 and the like. As a result, a rotational force acts on the second clutch plate 20 in the same direction, and the camshaft 18 and the fitting shaft 17 try to rotate in the same direction. However, at this time, the fitting shaft 1
7, since the second engaging portion 31 pushes the end of the stop ring 32 in the expanding direction, the frictional force between the stop ring 32 and the stop ring case 33 increases. As a result, the rotation of the fitting shaft 17 is prevented, and the rotation of the elevating shaft 8 integrated with the fitting shaft 17 via the cam shaft 18 and the second clutch plate 20 is prevented. As a result, the weight of the slat 5 or the like is prevented from falling, and the slat 5 and the bottom rail 6 are suspended and supported at desired positions.

Next, the operation of lowering the slat 5 and the bottom rail 6 will be described.

When lowering the slats 5 and the bottom rail 6, the operation cord 7 is operated in a lowering direction (a direction opposite to the above-described slat raising direction). Then, the input shaft 16 is rotated in the slat descending direction via the operation pulley 16a. Thereby, the carrier 22 of the planetary gear mechanism
Rotates, and this rotation is transmitted to the camshaft 18 via the fitting shaft 17, and the camshaft 18 rotates in the downward direction. That is, the cam shaft 18 rotates in the direction indicated by the arrow A in FIG. 4, and the slide ball 28 relatively moves in the direction indicated by the arrow B in FIG.

With the rotation of the camshaft 18 in the downward direction, the slide ball 28 arranged on the outer periphery of the camshaft 18 moves from the first groove 24a to the second groove 24b. This is because the second groove 24b is formed such that the relative movement of the slide ball 28 in the direction indicated by the arrow B in FIG. Recess 2
This is because 7 has a long groove shape. With this operation,
The camshaft 18 moves in the direction indicated by the arrow D in FIGS. 2 and 4 against the urging force of the coil spring 19, and enters the state shown in FIG. As a result, the engagement between the camshaft 18 and the second clutch plate 20 is released. That is, the first clutch means 21 is released, and the elevating shaft 8 is free with respect to the operation cord 7 side. Therefore, the slats 5 and the bottom rail 6 descend by their own weight, and the elevating shaft 8 rotates with this descending operation.

When the elevating shaft 8 rotates in the downward direction, the rotation is input to the input shaft 51 of the braking device 11. Then, the rotation of the input shaft 51 is transmitted to the pinion 60 of the speed increasing gear train 52, and the pinion 60 rotates integrally with the coil spring 62. At this time, the coil spring 62 expands so as to slidably contact the inner peripheral surface (= the inner wall of the cylindrical portion) of the worm wheel 58 disposed outside. As a result, the worm wheel 58 rotates integrally with the pinion 60 via the coil spring 62.

When the worm wheel 58 rotates, the rotation rotates the worm 59, and the rotating plate member 53 of the centrifugal governor 50 rotates integrally with the worm 59. As a result, the weight portions 53e, 53e of the expanding plate 53a of the rotating plate member 53 expand in the outer peripheral direction while being elastically deformed by the rotational centrifugal force, and slidingly contact the inner wall of the sliding contact case 55 disposed therearound.

At this time, the expansion of the expansion plate 53a is performed as follows.
It changes according to the rotation speed of the worm 59. That is,
When all the slats 5 are lowered by their own weight from a state in which they are wound up to the vicinity of the head box 2, the rotation speed of the elevating shaft 8 is high because the total weight of the slats 5 and the bottom rail 6 on the elevating shaft 8 is large. Conversely, bottom rail 6
When descending from a state in which the slats 5 and the bottom rail 6 on the elevating shaft 8 are almost down to a predetermined lowermost position, the rotation speed of the elevating shaft 8 is low because the total weight of the slats 5 and the bottom rail 6 on the elevating shaft 8 is small. In accordance with such a situation, the rotation speed of the worm 59 and the accompanying situation of the spreading of the weight portions 53e, 53e of the spreading plate 53a of the centrifugal governor 50 change.

That is, the weight portion 53 of the expanding plate 53a
When the rotation speed of the elevating shaft 8 is high, e and 53e greatly expand, so that a large frictional force is generated between the weight portions 53e, 53e and the sliding contact case 55. For this reason, in the initial stage of the descent of the slats 5, the braking device 11 exerts a large rotational load on the elevating shaft 8, so that its braking force acts greatly. Therefore, the lowering speed becomes considerably slow despite the large total weight.

On the other hand, the braking device 11 has a small braking force at the end of the downward movement of the slat 5 due to a small rotational load on the elevating shaft 8, and has no braking force immediately before the end. . For this reason, when the descending weight becomes smaller, the braking force becomes smaller, and the vehicle descends slowly and surely. As described above, the horizontal blind device 1 according to the present embodiment can lower the slat 5 while applying appropriate braking when the slat 5 or the like lowers its own weight, and can surely lower the slat 5 to the lowest position.

Although the above-described embodiment is an example of a preferred embodiment of the present invention, the present invention is not limited thereto, and various modifications can be made without departing from the gist of the present invention. is there. For example, the present embodiment is a so-called horizontal blind device in which multi-stage slats 5 are suspended from the head box 2, but if the blind member for light shielding can be lowered by its own weight, You may apply to the blind apparatus of another structure. That is, the present invention may be applied to a tuck-up curtain of a type in which a cloth hanging down from a head box is wound up by winding a cord, or a pleated curtain in which a blind member formed of a cloth folded in a zigzag shape is hung down.

In the above embodiment, the braking device 1
By providing a coil spring 62 as a one-way transmission means in 1, a braking force is not applied when the slat is raised, but such a configuration is not particularly required. However, in the case where the slat lifting operation is performed manually, if the braking of the rotation of the elevating shaft 8 is braked, the braking force becomes a load, which is not preferable. The configuration was adopted.
However, if the braking force at the time of the lifting operation is weak, the braking force may be applied at the time of the lifting.

Further, although the coil spring 66 is provided in the braking device 11 as overload preventing means, the overload preventing means may have another configuration. For example, if one of the trains is constituted by two gears that rotate integrally with a predetermined frictional force or less, when the input rotational force is a predetermined force or more, slippage occurs between the two gears. The rotation may be generated and the rotation may not be transmitted to the rotating plate member. Further, a configuration without the overload prevention means may be adopted.

Further, in the above-described embodiment, the angle adjusting shaft 9 is provided. However, the present invention can be applied to a case where the angle adjusting shaft 9 is not provided. Further, although the slats 5 and the like are raised and lowered by operating the operation code 7 by hand, the slats 5 and the like may be raised and lowered using a motor and an operation switch (or a remote controller). Also,
Although the worm 59 and the worm wheel 58 are included in the speed increasing train 52 and the centrifugal governor 50 is provided as the braking device, the centrifugal governor portion may be a windmill type governor. Further, a centrifugal governor or a windmill governor that does not use a worm or the like may be used. When a governor of a windmill type is used, the governor portion may be protected by providing an overload prevention means composed of a coil spring type or a sliding gear type.

Furthermore, in the above-described embodiment, the centrifugal governor 50 has a clearance between the rotating plate member 53 and the sliding contact case 55. Even when not performed, the configuration may be such that the expanding plate 53a of the rotating plate member 53 and the sliding contact case are in contact with each other.

[0120]

The blind device according to the present invention has a variable braking force to cope with a rotational load applied to a lifting shaft that changes according to the weight of a portion that has not been lowered to a predetermined position when the blind member lowers its own weight. Since the braking device is connected to the elevating shaft, a large braking force acts to lower the blind member at an appropriate speed in the early descent when the rotational load on the elevating shaft is large, and at the end of descent when the rotational load is small. In this case, the braking force is reduced, and the blind member descends smoothly and completely.

Further, the braking device of this blind device is provided with a speed increasing gear train including a worm and a worm wheel, and a centrifugal governor. As a result, the braking device has a compact configuration and a very high speed increase ratio, and the braking force is extremely small when the rotation of the elevating shaft is low, and the braking force is extremely high at high speed. can do. In addition, since the number of parts in the speed increasing mechanism is small, friction between the parts is reduced and the operation can be performed more smoothly. Furthermore, the rotating plate member is
If the weight portion has an elastic member integrally provided on the outer peripheral portion, the number of parts is reduced as compared with the case where the shaft portion and the expanding portion are provided as separate members, thereby reducing costs and improving the performance. In addition to being able to make it possible, the expansion is smooth and it is possible to exert a certain braking force.

Further, if the one-way rotation transmitting means is provided in the braking device so that the braking force of the braking device does not work when the blind member is raised, it can be raised lightly even by manual operation.

Further, an angle adjusting shaft for hanging down the slat via a ladder cord is provided in the head box, and the rotating operation of the angle adjusting shaft is also used as operating means. An angle adjustment operation can be performed, and a highly convenient blind device can be obtained.

According to another aspect of the present invention, since the braking member is provided with an overload preventing means for preventing an excessive torque from being input to the rotating member, the operating means can be moved in the descending direction while the weight of the blind member is lowered. The elevating shaft rotates strongly by operating, etc.
Even if an excessive torque is input to the input shaft of the braking device, the torque is not transmitted to the rotating plate member. Therefore, even in such a case, damage to a braking member such as a centrifugal governor and other rotating mechanisms can be avoided.

[Brief description of the drawings]

FIG. 1 is a front view showing an entire blind device according to an embodiment of the present invention.

FIG. 2 is a sectional view mainly showing a slat driving portion of the blind device of FIG. 1;

FIG. 3 is a cross-sectional view illustrating a state in which a first clutch unit is disengaged in the slat driving unit illustrated in FIG. 2;

FIG. 4 is a development view showing a guide groove of a cam shaft of the slat drive unit shown in FIG. 2;

FIG. 5 is a cross-sectional view of an operation delay unit serving also as a one-way clutch of the slat drive unit shown in FIG.

FIG. 6 is a sectional view of a clutch spring portion of a second clutch means of the slat drive shown in FIG. 2;

FIG. 7 is a sectional view of a coil frame portion of a second clutch means of the slat drive shown in FIG. 2;

FIG. 8 is a plan view of the braking device of the blind device shown in FIG. 1 when a case lid is removed.

9 is a longitudinal sectional view of the braking device shown in FIG.

FIG. 10 is a plan view showing a rotating plate member of a centrifugal governor of the braking device of FIG. 8;

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Blind device 2 Head box 3 Ladder code 4 Elevating code 5 Slat (blind member) 7 Operation code (Operating means) 8 Elevating shaft 9 Angle adjusting shaft 11 Braking device 21 First clutch means 34 Second clutch means 50 Centrifugal governor Reference Signs List 51 input shaft 52 speed-up gear train 53 rotating plate member 53a expanding plate 53c rotation center shaft portion 53d weight portion 55 sliding contact case 58 worm wheel 59 worm 62 coil spring (unidirectional rotation transmission means) 66 coil spring (overload prevention means) )

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Katsuhiko Hayashi 14222 Haramura, Suwa-gun, Nagano Pref.

Claims (8)

[Claims] 1. A blind member suspended from an elevating shaft via an elevating cord, an operating means for rotating the elevating shaft to perform an elevating operation of the blind member, and a rotation and stop of the elevating shaft. A clutch means for switching, wherein the input means inputs the rotation of the elevating shaft in a blind device capable of releasing the clutch means based on the operation of the operating means and lowering the blind member by its own weight. A shaft, a speed increasing gear train transmitting the rotation input to the input shaft at an increased speed, and a rotating plate member rotating as a part of the speed increasing gear train and expanding in an outer circumferential direction according to the rotation speed. And a centrifugal governor comprising a sliding contact case slidable around the rotating plate member and disposed around the rotating plate member, the worm and the worm wheel being provided on the speed increasing wheel train. And a braking device including a shaft and a lower shaft.When the blind member lowers its own weight, the braking force is increased when the rotating load applied to the lifting shaft is large, and when the rotating load is small, the braking force is reduced. A blind device characterized in that its braking force is varied so as to be small. 2. The rotating plate member is provided integrally with a rotation center shaft portion that rotates as a part of the speed-up gear train and radially outside the rotation center shaft portion, and is expanded in an outer circumferential direction by rotation. The blind device according to claim 1, further comprising an expanding plate in which a weight portion to be formed is integrally formed with an elastic member. 3. A one-way rotation transmitting means for transmitting only rotation of the elevating shaft when the blind member descends to the rotating plate member, wherein the input shaft or the speed increasing wheel train is provided. The blind device according to claim 1 or 2, wherein the braking force of the braking device is not applied when the vehicle is raised. 4. The apparatus according to claim 1, wherein the elevating shaft is disposed in a head box installed above the blind member, and the blind member is composed of multiple slats, and a ladder cord for adjusting the angle of the slat is provided. 4. The blind device according to claim 1, wherein the blind device is suspended from a head box. 5. An angle adjusting shaft for hanging said slats through said ladder cord is provided in said head box, and a rotating operation of said angle adjusting shaft is also used by said operating means. 5. The apparatus according to claim 4, further comprising a clutch for releasing the connection between the operating means and the angle adjusting shaft when the slat is moved up and down.
A blind device as described. 6. A blind member suspended from an elevating shaft via an elevating cord, an operating means for rotating the elevating shaft to perform an elevating operation of the blind member, and a rotation and stop of the elevating shaft. A clutch device for performing switching, wherein the clutch device is released based on the operation of the operating device, and the blind member can be lowered by its own weight. The blind member is composed of multi-stage slats, and a ladder cord for adjusting the angle of the slat is suspended from the head box, and the ladder is placed in the head box. Provide an angle adjustment axis for hanging the slat through a cord, and rotate the slat until it is fully closed The second clutch means for releasing the connection between the operating means and the angle adjusting shaft is provided, and when the blind member lowers its own weight, a braking force is applied when the rotational load applied to the lifting shaft is large. A blind device characterized in that a braking device that varies the braking force so that the braking force is small when the rotation load is small is connected to the lifting shaft. 7. A blind member suspended from an elevating shaft via an elevating cord, operating means for rotating the elevating shaft for performing the elevating operation of the blind member, and rotation and stop of the elevating shaft. A clutch device for performing switching, wherein the clutch device is released based on the operation of the operating device, and the blind member can be lowered by its own weight. The blind member is composed of multi-stage slats, and a ladder cord for adjusting the angle of the slat is suspended from the head box, and the ladder is placed in the head box. Provide an angle adjustment axis for hanging the slat through a cord, and rotate the slat until it is fully closed A second clutch means for releasing the connection between the operating means and the angle adjusting shaft, and an input shaft for inputting the rotation of the elevating shaft, and increasing the rotation input to the input shaft. And a rotating plate member that rotates as a part of the gear train and that expands in the outer peripheral direction in accordance with the rotation speed, and that is arranged around the rotating plate member and expands. A centrifugal governor comprising a sliding contact case capable of slidingly contacting the rotating plate member, wherein a braking device including a worm and a worm wheel is connected to the speed increasing wheel train to the elevating shaft, and the weight of the blind member is reduced. At the time of descending, the braking force is increased when the rotational load applied to the elevating shaft is large, and the braking force is varied so that the braking force is small when the rotational load is small. Blind equipment. 8. A blind member suspended from an elevating shaft via an elevating cord, operating means for rotating the elevating shaft for performing the elevating operation of the blind member, and rotation and stop of the elevating shaft. A clutch means for switching, wherein the input means inputs the rotation of the elevating shaft in a blind device capable of releasing the clutch means based on the operation of the operating means and lowering the blind member by its own weight. A shaft, and a rotating member that rotates based on the rotation input to the input shaft, and applies a predetermined resistance to the rotation of the rotating member to apply braking to the rotation of the elevating shaft, and to apply excessive force to the rotating member. A braking device provided with an overload preventing means for preventing an excessive rotation of the rotating member due to an input of a large rotational force is connected to the lifting shaft. Device.