JP3485164B2 - Blind equipment - Google Patents

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 large number of horizontally supported blind members such as slats by their own weight.

[0002]

2. Description of the Related Art Conventionally, as one type of blind, a common operating rod hung from one end of a head box is used in order to easily and swiftly perform vertical operation and angle adjustment operation of a large number of horizontally supported slats. It is known to operate such devices (see Japanese Patent Laid-Open No. 4-269293).

In the horizontal blind disclosed in Japanese Patent Application Laid-Open No. 4-269293, the slat angle can be adjusted by rotating the operating rod hung from one end of the head box. When the operating rod is further rotated, the slats 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 operation of the common operating rod allows the slat angle adjustment operation and the elevating operation, and in particular, by pulling the operating rod downward, the slat can be lowered by its own weight. As described above, Japanese Patent Laid-Open No. 4-26
The horizontal blind device disclosed in Japanese Patent No. 9293 can lower the slat without rotating the operating rod.
Also, in this horizontal blind, a speed reducer is connected to the lifting shaft (the shaft that suspends the slat via the lifting cord) to prevent the slats from dropping suddenly. It is designed to descend.

Incidentally, Japanese Utility Model Laid-Open No. 61-43398 discloses a technique for braking the rotation of a winding pipe when winding a roll screen.
The publication discloses a speed governing device for adjusting the descending speed of the slats of the shutter curtain. By using these speed governors, braking is applied when the blind member is rolled up or lowered.

Further, the horizontal blind slat elevating device described in Japanese Patent Laid-Open No. 7-324572 is equipped with a governor device connected to an elevating shaft. This governor device exerts a stronger braking force as the rotation of the lifting shaft increases, so that the rotation speed of the lifting shaft is always suppressed below a certain level. In addition, this governor device is designed so that when the lifting shaft rotates in the direction in which the slats are wound up, it spins idle and does not exert its braking force, so that the winding operation can be performed with a light force. .

[0007]

However, in the blind device disclosed in Japanese Unexamined Patent Publication No. 4-269293, when the slats configured in multiple stages descend using their own weight, they are suspended and supported at the lower end of the elevating cord. As the bottom rail, which is the lower plate, approaches the predetermined position (lowermost position), the rotational load applied to the lifting shaft via the lifting cord gradually decreases, while the above-mentioned braking force remains constant. There is.

Therefore, just before the end of the lowering operation (when the bottom rail approaches the lowermost position), the brake is too effective and the slats and the bottom rail do not operate smoothly, or the slats and the bottom rail reach the lowermost position. There is a problem that it does not descend and stops on the way. In order to avoid such danger, if the braking force is reduced,
The descending speed in the upper part becomes too high, and the stop control at the desired position cannot be performed properly, resulting in a decrease in commercial value.

Further, the braking technique disclosed in Japanese Utility Model Laid-Open No. 61-43398 is one for winding, and since the winding force at a predetermined position and the weight of the curtain to be wound at that time are usually in a proportional relation, the curtain If the hoisting force stored by lowering the hoisting force is always higher than the weight of the curtain and the braking force, the problem that the hoisting operation stops even if the hoisting operation is stopped does not occur. This is because this technique is intended for winding up a roll screen, and therefore does not require a delicate adjustment of the braking force as in the descent of the curtain by its own weight.

In the shutter curtain disclosed in Japanese Utility Model Laid-Open No. 7-26600, the braking force works even when the curtain is raised. This is because the motor is used to raise the curtain, and even if some braking force is applied when raising the curtain, there is no problem. Also, since the speed control device for this shutter curtain has a structure in which the weight portion is supported by the support pieces on both sides, when the centrifugal force exceeds a predetermined value, a constant frictional force is generated, and as the centrifugal force increases, the frictional force increases. It is not configured as.

Further, in the slat lifting device disclosed in Japanese Patent Laid-Open No. 7-324572, the rotation of the lifting shaft is accelerated through the train of spur gears and transmitted to the rotary plate member which is the final stage of the train. The rotating plate member has a braking device that utilizes frictional force generated by rotating at high speed while slidingly contacting the case body. The braking device has a structure in which a plurality of spur gears are arranged in order to obtain a high speed increasing ratio necessary for obtaining a more reliable braking force. Therefore, there is a problem that the number of parts of the braking device is large and the entire braking device is large. Further, the rotational resistance due to the mutual friction of the spur gears that are assembled in multiple stages increases, and there is a risk that braking will be too effective.

Further, the braking device used in each of the above-mentioned devices is constituted by a train wheel, a friction body or the like when the lifting shaft excessively rotates due to pulling a blind member such as a slat with an excessive force. The rotation of the braking member or the like becomes too high, and there is a risk that the internal mechanism will be destroyed.

An object of the present invention is that when a blind member such as a slat is lowered by its own weight, an appropriate brake is applied according to its descending speed and a rotational load, and the blind member can be reliably lowered to the lowest position. Moreover, it is to provide a blind device having a compact braking device. Another object of the present invention is to provide a blind device that facilitates the operation of raising and lowering and adjusting the angle of a blind member by a common operation means. Another object of the present invention is to provide a blind device having a braking device that is not destroyed even if an excessive rotational load is generated on the lifting shaft.

[0014]

Means for Solving the Problems To achieve the above object, the present invention relates to a blind member that is hung and supported by an elevating shaft via an elevating cord, and a rotating elevating shaft for performing an elevating operation of the blind member. Operating means for operating and clutch means for switching between rotation and stop of the lifting shaft,
A blind device capable of releasing the clutch means and lowering the blind member by its own weight based on the operation of the operating means, including a braking device connected to the elevating shaft for braking rotation of the elevating shaft. The device includes an input shaft for inputting rotation of a lifting shaft, a speed increasing train wheel for speeding up and transmitting the rotation input to the input shaft, and a rotation speed for rotating as a part of the speed increasing train wheel. A centrifugal governor comprising a rotary plate member that expands in the outer peripheral direction in response to the rotary plate member and a sliding contact case that is arranged around the rotary plate member and that can slide and contact the rotary plate member that expands. The wheel train includes a worm and a worm wheel, and the centrifugal governor has a large frictional force to the sliding contact case of the rotating plate member when the rotating load applied to the lifting shaft is large when the blind member is lowered by its own weight. When the rotational load is smaller constructed as frictional force to the sliding contact case of the rotating plate member becomes smaller, further
Blind along the inner surface of the worm wheel.
Only the rotation of the lifting shaft when the member descends is transmitted to the rotating plate member.
One-way rotation transmission means to reach the blind member
Do not use the braking force of the braking device when lifting
It is.

According to another aspect of the invention, in addition to the above-mentioned blind device, the rotary plate member is integrally formed on a rotation center shaft portion that rotates as a part of the speed increasing train wheel and on the outer side in the radial direction of the rotation center shaft portion. And a weight portion which is provided on the outer peripheral portion and expands in the outer peripheral direction by rotation, is integrally formed by an elastic member.

Another aspect of the present invention is the blind device described above.
In addition to the installation, the lifting shaft is installed above the blind member.
It is installed in the head box and the blind member is
Consists of a rat and for adjusting the angle of this slat
The ladder cord is hanging from the head box.

Still another invention is the blind described above.
In addition to the device, through the ladder cord in the head box
With an angle adjustment shaft for hanging the slats,
The operation means also serves to rotate the angle adjustment shaft, and
When operating the slat with the operating means,
A clutch means is provided to release the connection with the degree adjusting shaft.
It

Another aspect of the present invention is that the lifting cord is used.
The blind member suspended from the lifting shaft and the
Rotate the lifting shaft to move the lifting member up and down.
Switching between operating means and rotation / stop of the lifting shaft
The clutch means and the
Release the latching means and lower the blind member by its own weight.
A blind device that can be lowered
The input shaft to input the rotation of and the rotation input to the input shaft
With a rotating member that rotates based on
Braking the rotation of the lifting shaft by adding a predetermined resistance
Equipped with a braking device, which is excessive on the rotating member.
To prevent excessive rotation of the rotating member due to excessive torque input.
Therefore, if an excessive torque is input, rotate this torque.
Instead of transmitting it to the rolling member, it rotates its rotating force during normal rotation.
Equipped with overload protection means adapted to transmit to the rolling member
I am.

The blind device of the present invention is a blind
When the weight of a member is lowered
Therefore, a braking device that changes the braking force is connected to the lifting shaft.
There is.

Therefore, the load of rotation on the lifting shaft is large.
At the beginning of descent, a large braking force is applied to the blind member.
While lowering at a moderate speed, lowering of rotating load
The braking force becomes small at the end of the period, and the blind member is smooth
Moreover, it surely descends to the end.

The braking device also includes a worm and a wheel.
Equipped with a speed-up gear train including a home wheel and a centrifugal governor
It is obtained. Therefore, the braking device has a compact configuration.
In addition, a very high speed increasing ratio can be obtained, and
The braking force is very small when the
However, the braking force can be extremely high at high speeds.
it can.

[0022] The Contact, the rotating plate member and an elastic member having a weight portion for expanding to the outer periphery, it is possible to perform more reliable and and smooth braking operation.

If the braking device is provided with one-way rotation transmitting means so that the braking force of the braking device does not work when the blind member is raised, the lifting force can be raised lightly even by hand.

Further, the operating means is configured to be used for both the raising and lowering operation and the angle adjusting operation, and the clutch adjusting means is released during the raising and lowering operation so that the angle adjusting shaft for performing the angle adjusting operation is disconnected from the operating means. If the configuration is
Both operations can be easily performed by one operating means, and the blind member can be pulled up with a light force without applying an extra load during the operation of pulling up the blind member.

Further, if an overload preventing means for preventing an excessive rotational force from being input to the rotating member of the braking device is provided,
While the blind member is descending its own weight, the elevating shaft rotates strongly by operating the operating means in the descending direction, and even if an excessive rotational force is input to the input shaft of the braking device, that rotational force will be applied to the rotating member. Not transmitted. Therefore, damage to the internal mechanism is avoided.

[0026]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the blind device according to the present invention will be described below with reference to FIGS.
In addition, what is described below is a so-called horizontal blind device in which multi-stage slats are suspended from a head box.

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

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

The lifting cord 4 has an upper end wound around a cord winding portion 12 inserted and fixed to a lifting shaft 8 in the head box 2. Each horizontally supported slat 5 includes:
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
The elevating cord 4 is spirally wound around the cord 2. Then, the bottom rail 6 is pulled up to the head box 2 side, that is, the upper side while collecting the respective slats 5. Conversely, when the lifting shaft 8 is rotated in the other direction, each slat 5 and the bottom rail 6 descend. 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, in the direction of lowering the slat 5 and the bottom rail 6. try to.

However, as will be described later, the horizontal blind device 1 of the present embodiment is provided with a mechanism for stopping the rotation of the elevating shaft 8 in the descending direction in the slat drive portion 10, and the bottom rail 6 and It is possible to stop each slat 5 at any position. Further, in the horizontal blind device 1 of the present embodiment, as will be described later, when the first clutch means 21 is released by operating the operation cord 7, the elevating shaft 8 becomes free with respect to the slat drive unit 10. It is possible to descend by the weight of the slat 5 and the bottom rail 6. When the weight is lowered, the braking device 11 works 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 operated. Make sure to descend to the lowest position at speed.

The ladder-like ladder cord 3 is inserted into and fixed to the angle adjusting shaft 9 in the head box 2 and the cord tilting portion 1 is provided.
The upper end is fixed to 3. 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, each slat 5 is supported by each step of the ladder cord 3 when it descends to a predetermined position. Therefore, the weight of each slat 5 supported by the ladder cord 3 is not applied to the lifting shaft 8 via the lifting cord 4.

The slat drive unit 10 is driven by operating the operation code 7. The slat driving unit 10 rotates the lifting shaft 8 to pull up the slat 5 or
For rotating the angle adjusting shaft 9 to adjust the angle of the slat 5, or for 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. It is a mechanism. That is, in the horizontal blind device 1 according to the present embodiment, the operation code 7
Is the operating means capable of both the vertical movement of the slat 5 and the angle adjustment. Furthermore, the slat drive unit 10
Is disengaged from the elevating shaft 8 by releasing the first clutch means 21 to be described later, and the slat 5 can be lowered by its own weight.

In this embodiment, the slat drive unit 10 is arranged on one end side (right end in FIG. 1) of the head box 2. As shown in FIGS. 2 and 3, the slat drive unit 10 includes a case body 14 having a structure in which the internal space is divided into two spaces, and a tilt clutch case 15 attached above the case body 14. I have it.

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

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 portion 1 whose tip is formed in the case body 14.
An operation pulley 16a around which the loop-shaped operation cord 7 is wound is fixed to the protruding portion 4h from the outside of the case body 14. As a result, the operation of the operation cord 7 causes the input shaft 16 to rotate 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 14e of the case body 14, the fitting shaft 17, the cam shaft 18 also serving as the first clutch plate supported on the other end side of the fitting shaft 17, and the cam shaft 18 are provided. 18, a first clutch means 21 composed of a second clutch plate 20 which can be engaged and disengaged, a coil spring 19 for sliding the cam shaft 18 on the fitting shaft 17 and urging it toward the second clutch plate 20 side, Are arranged.

The fitting shaft 17 is a wall portion 14f of the case body 14.
It is rotatably supported in the fitting hole portion 14g formed in the. Then, one end side of the fitting shaft 17 has the fitting hole portion 14
It projects through the inside of g to the 1st space 14d side. An end portion 17a, which is a protruding portion of the fitting shaft 17 into the first space 14d, has a hole portion 16c formed at the other end of the input shaft 16.
It is fitted in the inside so that relative rotation is possible. On the other hand, a further end portion of the end portion 17b on the opposite side of the end portion 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 together with the fitting shaft 17 and the fitting shaft 17
Therefore, it is supported so as to be movable 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 reduced at a predetermined reduction ratio and transmitted to the fitting shaft 17. It is like this. Then, when the fitting shaft 17 rotates, the cam shaft 18 rotates to rotate the lifting shaft 8 in the slat pull-up direction via the first clutch means 21 in the connected state. The fitting shaft 17 is the input shaft 1
After the carrier 22 of the planetary gear mechanism rotates a predetermined angle based on the rotation of 6, the carrier 22 is engaged with the carrier 22 and integrally rotates. That is, at the timing of starting the rotation of the fitting shaft 17, the drive gear 35 and the rotation shaft 36, which will be described later, in the tilt clutch case 15 are rotated by a predetermined angle (=
This is the time when each slat 5 is rotated until it becomes substantially vertical (by rotating the angle adjusting shaft 9 by a predetermined angle).

The cam shaft 18 rotates about the fitting shaft 17 as a center of rotation and has a cam groove 24 on its outer peripheral surface. Teeth 26 that mesh with the teeth 25 formed on the second clutch plate 20 are formed at the tip end portion of the cam shaft 18.
On the other hand, the second clutch plate 20 has teeth 25 that can be engaged with and disengaged from the cam shaft 18, and the center shaft 20a that is the center of rotation of the second clutch plate 20 from the fitting hole portion 14j formed in the case body 14 to the case body 1.
4 is projected outside.

One end of the elevating shaft 8 is fixed to the tip portion of the central shaft 20a. Therefore, the first
Camshaft 18 also serving as the clutch plate of the second clutch plate 2
When the cam shaft 18 rotates in a state of meshing with 0, the rotation is transmitted to the elevating shaft 8. The coil spring 19 described above is disposed between the end surface of the cam shaft 18 and the wall portion 14f of the case body 14, and the cam shaft 18 is attached to the side that engages with the second clutch plate 20. I am energetic.

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

Therefore, the slide ball 28 itself has the recess 2
Although it slightly moves within 7, the slide ball 28 relatively moves along the shape of the cam groove 24 when the cam shaft 18 rotates. As a result, 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 a first continuous groove on the circumferential surface of the cam shaft 18.
From the groove 24a and the bent portion 24c of the first groove 24a to the tip side of the cam shaft 18 (the first clutch means 21 side), and passes through a predetermined rotation angle (rotation angle of approximately 270 °) to the converging portion. The second groove 24b gradually converges toward the first groove 24a by 24d. The bent portion 24c is formed at a branch portion between the first groove 24a and the second groove 24b, and is bent so as to bend toward the second groove 24b.

When the cam shaft 18 having the cam groove 24 as described above is rotated in the direction of pulling up the slat 5 by the fitting shaft 17, the slide ball 28 moves relative to the cam groove 24 in FIG. Move in the direction of arrow A. In this state, that is, in the state where the operation code 7 is operated to pull up the slat 5 and the bottom rail 6, the cam shaft 18 is urged in the arrow C direction 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, so that the slide ball 28 moves in the recess 27 in the axial direction. The cam shaft 18 does not move in the axial direction. Therefore, the cam shaft 18 is always in the state of meshing with the second clutch plate 20, and the winding operation can be performed by the operation cord 7.

On the contrary, when the cam shaft 18 is rotated in the direction in which the slat 5 is lowered by the fitting shaft 17, the slide ball 28 moves in the arrow B direction relative to the cam groove 24 in FIG. Moving. Then, the slide ball 28 is guided from the first groove 24a through the bent portion 24c into the second groove 24b. As a result, the cam shaft 18 moves in the arrow D direction in FIG. 4 against the urging force in the arrow C direction, and separates from the second clutch plate 20, so that the second clutch plate 20 moves. Will be free (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 direction while the slats 5 and the like are descending,
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 pulling-up operation is performed by the operation code 7, the winding-up operation of the slat 5 can be started again.

When the operation code 7 is operated in the pulling-up direction of the slat 5 and the bottom rail 6 to rotate the input shaft 16, the rotational force of the input shaft 16 is reduced by the action delay means 29 which also functions as a one-way clutch, which will be described later. The signal is transmitted to the cam shaft 18 after a predetermined time delay. Then, when the cam shaft 18 rotates, the teeth 26 of the cam shaft 18 and the teeth 25 of the second clutch plate 20 mesh with each other due to the action of the cam groove 24 as described above, and the lifting and lowering connected to the second clutch plate 20. The shaft 8 is adapted to rotate.

That is, the first space 14 of the case body 14
In the inner circumference of the case body 14 near the wall portion 14f of d,
When the angle adjustment 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 lifting shaft 8 side, and the rotation of the input shaft 16 is lifted after the angle adjustment is completed. An operation delay means 29 which also serves as a one-way clutch for transmitting power to the shaft 8 side and transmitting power only in a predetermined direction.
Are arranged.

The operation delay means 29 includes a projection-shaped 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 projection-shaped first engagement portion 30 formed on the fitting shaft 17. The second engaging portion 31 and the stop ring 32 and the stop ring case 33 arranged outside these.

The stop ring case 33 has a substantially cylindrical shape and is non-rotatably fitted to 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 has a coil spring shape 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. Further, by reducing the frictional force, the power from the input shaft 16 is transmitted to the fitting shaft 17 and the cam shaft 18 is rotated. further,
The fitting shaft 17 has a function of preventing the input shaft 16 from rotating due to the rotation of the input shaft 16 for a predetermined period.

As shown in FIG. 5, both ends 32a and 32b of the stop ring 32 are bent toward the center at approximately 90 °. Stop ring 3
In the space of about 270 ° sandwiched between the two end portions 32a, 32b of the first engagement portion 30, the first engagement portion 30 projected from the carrier 22 (see FIG. 2) of the planetary gear mechanism that engages with the input shaft 16 described above. Are projected in the range of approximately 130 °. Also,
In the space of approximately 90 ° sandwiched between the both ends 32a and 32b of the stop ring 32, the second protrusion projecting from the fitting shaft 17 is provided.
The engaging portion 31 of is projected.

With such a configuration, initially, even if the carrier 22 rotates due to the rotation of the input shaft 16, the first engaging portion 30 of the carrier 22 is placed between the end portions 32a and 32b of the stop ring 32. Carrier 2 just by moving
2 idles with respect to the fitting shaft 17.

However, when the first engaging portion 30 of the carrier 22 comes into contact with either of the both end portions 32a and 32b, the end portion of the stop ring 32 on the side brought into contact with the first engaging portion 30. Will be pulled in the direction of reducing the diameter of the stop ring 32. This reduces the frictional force between the stop ring 32 and the stop ring case 33. Therefore, when the input shaft 16 rotates and the carrier 22 rotates in this state, in the stop ring case 33,
The 1st engaging part 30, the stop ring 32, and the 2nd engaging part 31 will be 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
The engaging portion 31 of the end portion 32a, 32 of the stop ring 32
Contact either of b. That is, when the winding operation in the predetermined direction by the operation cord 7 is stopped midway or the like and the hand is released, the rotational force is transmitted from the cam shaft 18 side to the fitting shaft 17 side by the weight of the slat 5 or the like.

When the camshaft 18 rotates while the first clutch means 21 is connected and the end 32a or 32b of the stop ring 32 is pushed in this way, the stop ring 32 expands and stops. The frictional force with the stop ring case 33 increases. Therefore, the fitting shaft 17
Is prevented from rotating, 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 any position. That is, it is possible to set the number of slats 5 arranged above the bottom rail 6 and hanging at a constant interval to an arbitrary number.

Further, the second clutch means 34 including the tilt clutch case 15 described above is provided above the case body 14 configured as described above. The second clutch means 34 includes an operation cord 7 and an angle adjusting shaft 9.
It is for connecting / disconnecting with, and can be engaged and disengaged with the input shaft 16 side and the angle adjusting shaft 9 side, respectively. The specific configuration of the second clutch means 34 will be described below.

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. It should be noted that the input gear (not shown) and the drive gear 35 can transmit rotation through a transmission gear (not shown), and the rotation of the input gear is reduced at a predetermined reduction ratio and transmitted to the rotary shaft 36. It is supposed to be done.
With such a configuration, when the rotating shaft 36 rotates with the second clutch means 34 connected, the rotation of the rotating shaft 36 becomes the second
Is transmitted to the angle adjusting shaft 9 through the clutch means 34 of
The angle adjusting shaft 9 is rotated to adjust the angle of the slat 5.

A rotary shaft 36 which is the center of rotation of the drive gear 35.
A clutch spring 37 is wound around the tip of the
Further, a clutch member 38 is supported at the tip of the rotary 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 project outward in the radial direction at a predetermined interval.

Both ends 37a of the clutch spring 37,
An engaging portion 38a projects from the clutch member 38 between the portions 37b. Then, when the rotary shaft 36 is rotated and either one of the both end portions 37a, 37b abuts on the engaging portion 38a, the abutted end portion is engaged by the clutch spring 37.
Is pressed in the direction to reduce the diameter of. Therefore, in this state, the frictional force between the clutch spring 37 and the rotary 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.

Further, the upper case 14a is formed with a rotation blocking portion 39 projecting on the rotation loci of both ends 37a, 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 either one of a and 37b comes into contact with the rotation preventing portion 39, the contacted end portion is pushed in the direction of expanding the clutch spring 37, and the clutch spring 3
The frictional force between the rotary shaft 36 and the rotary shaft 7 decreases. As a result, the rotating shaft 36 rotates idly with respect to the clutch spring 37.

On the tip end side of the clutch member 38, that is, on the angle adjusting shaft 9 side of the clutch member 38, a substantially cylindrical coil frame 40 is fitted and fixed between the tilt clutch case 15 and the upper case 14a. , Its coil frame 4
Stop ring 41 in the shape of a spring coil on the inner peripheral surface of 0
Is fitted. As shown in FIG. 7, both ends 41a and 41b of the stop ring 41 are projected inward in the radial direction at predetermined intervals, and an engagement portion 38b is projected from the clutch member 38 between the both ends 41a and 41b. ing.

Then, the clutch member 38 is rotated,
The engaging portion 38b has both ends 41a, 41 of the stop ring 41.
When it abuts against any of b, the abutting end is pushed in the direction of reducing the diameter of the stop ring 41, and the frictional force between the stop ring 41 and the coil frame 40 decreases. As a result, the stop ring 41 rotates integrally with the clutch member 38 as the clutch member 38 rotates.

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

Further, the engaging portion 42a is moved to the both ends 41a, 4 of the stop ring 41 based on the rotation of the tilt output shaft 42.
When it abuts against any one of 1b, the abutted end is pushed in the direction of expanding the stop ring 41. Therefore, the frictional force between the stop ring 41 and the coil frame 40 increases, and the tilt output shaft 42 is prevented from rotating. One end of the angle adjusting shaft 9 is fitted to the tip end portion of the tilt output shaft 42 thus configured, and based on the rotation of the angle adjusting shaft 9, the slat is slid through the cord tilting portion 13 and the ladder cord 3. An angle adjustment of 5 is made.

As described above, the lifting shaft 8 which can be connected / disengaged with the operation cord 6 side via the first clutch means 21 has a rotating force based on the weight of the slat 5 and the bottom rail 6 which causes the lifting cord. 4 and the take-up part 12 are working. At this time, the weights of the slats 5 and the bottom rail 6 applied to the elevating shaft 8 change according to the weight of the slats 5 that have not descended to a predetermined position.

That is, in a state in which almost all the lifting cords 4 are wound around the winding portion 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 having the bottom rail 6 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 by each step of the ladder cord 3 suspended by the angle adjusting shaft 9, the weight of the supported slat 5 is increased. It will depend on the ladder code 3. Therefore, the weight applied to the lifting shaft 8 becomes that of the bottom rail 6 and the slats 5 mounted on the bottom rail 6, and the total weight thereof decreases. And each slat 5
When is completely lowered to a predetermined position, the weight applied to the elevating shaft 8 via the elevating cord 4 is only that of the bottom rail 6, and the weight applied to the elevating shaft 8 is even smaller.

As described above, the rotating speed of the lifting shaft 8 that supports the weight, which varies depending on the degree of lowering of the bottom rail 6, changes the braking force so as to cope with the rotational load (= weight) applied to the lifting shaft 8. It is moderately controlled by 11. That is, the braking device 11 changes its braking force so that the braking force is large when the rotational load applied to the lifting shaft 8 is large and is 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 cam shaft 18 in a state where the fitting shaft 17 is engaged with the cam shaft 1,
Trying to rotate together with 8. But then, the second
Since the engaging portion 31 of expands the stop ring 32,
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 blocked. Therefore, the weight of the slats 5 and the like is prevented from falling. As a result, the bottom rail 6 and the slat 5 can be pulled up or pulled down by the operation cord 7 or stopped at any position.

When the camshaft 18 moves in the direction of the arrow D shown in FIG. 2 and the teeth 26 of the camshaft 18 and the teeth 25 of the second clutch plate 20 disengage from each other, the second clutch is released. The plate 20 becomes free with respect to the cam shaft 18, and the slats 5
Also, the bottom rail 6 is rotated based on its own weight drop.

The braking device 11 is connected to the other end side of the elevating shaft 8 described above (in the vicinity of the end opposite to the side where the slat driving unit 10 is installed = the 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 lifting shaft 8 and a speed increasing train wheel for increasing and transmitting 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 has a speed increasing train wheel 52.
The rotating plate member 53 that rotates as the final stage of the rotating plate and expands in the outer peripheral direction in accordance with the rotating speed, and the rotating plate member 53 that is fitted inside the case 54 and is arranged around the rotating plate member 53 with a predetermined clearance. The sliding contact case 55 is slidably contactable with the rotating plate member 53 to be opened. Also,
The case 54 includes a box-shaped case body 54a and a case lid 5.
4b and.

The input shaft 51 has a hollow hollow shaft portion 5 having a rectangular 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 57 and a case lid 54 formed on the case body 54a.
Both ends are rotatably supported by a bearing portion 54c formed in b.

The bearing part 57 has a hole 57a for inserting the elevating shaft 8 into the case 54 through the inside and the outside of the case 54, and the edge part of the hole 57a extends from the inside of the case body 54a. It is composed of an extended tubular portion 57b. Then, the input shaft 51 is inserted into the tubular portion 57b such that the one surface of the input gear 51b is placed on the tip portion of the tubular portion 57b. In addition, a part of the tubular portion 57b has a notched shape, and the rotation locus of the worm wheel 58, which is a part of the speed increasing gear train 52, enters the notched portion 57c. There is.

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

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

Pinion 60 and worm wheel 58
Is rotatably supported by a metal fixed shaft 61 provided upright in the case 54. The worm wheel 58 is formed in a hollow shape whose 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. Incidentally, this insertion hole 58a
A cylindrical portion 58b extending from the edge portion toward the other end is formed so as to surround the. This tubular portion 58b is
It is a shaft portion that prevents rotational runout of the worm wheel 58.

The pinion 60 is in contact with the tubular portion 60a fitted into the inner space of the worm wheel 58, the radially extending flange portion 60b, the gear portion 60c, and the tubular portion 58b of the worm wheel 58. And a cylindrical shaft portion 60e having a contact portion 60d. An insertion hole 60f for inserting the fixed shaft 61 is formed at the rotation center of the pinion 60. Then, the pinion 60 has the tubular portion 60.
The a is inserted into the worm wheel 58, and is rotatably supported by the fixed shaft 61.

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 lifting shaft 8 when the slat 5 descends is transmitted to the rotary plate member 53 side of the centrifugal governor 50. A coil spring 62 is arranged as a one-way rotation transmission means for performing the operation.

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) toward the center at the upper end portion, and this bent portion is inserted into a slit (not shown) formed in the tubular portion 60a of the pinion 60. It As a result, the coil spring 62 engages with the pinion 60 and is rotatable integrally.

This coil spring 62 is used for the pinion 6
When 0 rotates due to the rotation of the elevating shaft 8 when descending the slat 5, it spreads and strongly slides against 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 accelerated and transmitted to the rotary plate member 53 side of the centrifugal governor 50. As a result, in the braking device 11, when the slat 5 and the bottom rail 6 descend, the rotary plate member 53 rotates at a high speed and spreads out, slidingly contacts the inner wall of the sliding contact case 55 to brake the rotation of the lifting shaft 8. It is supposed to be applied.

On the contrary, when the pinion 60 is rotated by the rotation of the lifting shaft 8 when the pinion 60 winds up the slat 5, the coil spring 62 contracts its diameter to cause the worm wheel 58 to rotate.
Idle 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 rotary plate member 53 of the centrifugal governor 50 is not rotated. As a result, this braking device 11
Does not operate when the slat 5 is wound up, and can be wound up smoothly.

The worm 59 has a shaft portion 59d supported by a worm bearing groove 63 formed in the case body 54a. Then, the worm 59 is held in position in the worm bearing groove 63 by the pressing protrusion 54d formed on the case lid 54b. The shaft 59c, which is the other end of the worm 59, is supported by a circular worm bearing hole 64 formed in a sliding contact case 55 mounted inside the case 54. A worm 59 supported at both ends in this way
Engages the worm wheel 58 at right angles, and the worm gear 59a receives the rotation of the worm wheel 58 and rotates.

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 put into the worm bearing groove 63, and at the same time, the sliding contact case 55
The square-shaped portion 55a is inserted into the two vertical grooves 54e, 54e provided in the case body 54a. At this time, the rectangular portion 55a of the sliding contact case 55 is placed on the two placing portions 54f of the case body 54a. After that, the case lid 54b is integrated with the case main body 54a. At this time, the vertical groove 54 formed in the case lid 54b.
The square-shaped part 55a enters the g and the two holding parts 5
4h and 54h press down the rectangular portion 55a.

Since the combination of the worm wheel 58 and the worm 59 is used in the speed increasing train wheel 52 in the braking device 11 of the horizontal blind device 1 according to the present embodiment, the speed increasing ratio is about 1:70. And is 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.
A rotary plate member 53 is fitted inside. The rotating plate member 53 is composed of an expanding plate 53a which is formed of an elastic member such as rubber and expands 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 are integrally rotated.

As shown in FIG. 10, the expanding plate 53a is a substantially inverted S-shaped member having a hole 53b.
A rotation center shaft portion 53c having 3b as a center and two arm portions 53d, 53 extending to the outer periphery of the rotation center shaft portion 53c.
d, and weight portions 53e and 53e that are continuously formed at the respective tip portions of the arm portions 53d and 53d.
Then, by rotating, the weight portions 53e, 53
The e is expanded with the arms 53d and 53d in the outer peripheral direction by the centrifugal force, and when the rotation is stopped, the elastic force returns to the original state. In addition, this expansion plate 53a
Is mounted on one side of the disk portion 65a while being guided by the guide protrusion 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 is a disk portion 6 for loading the expansion plate 53a.
5a, a guide protrusion 65b provided on one surface of the disc portion 65a, and a tubular portion 65c integrally formed with the disc portion 65a. The worm 59 is provided at the center of rotation of the disc portion 65a. An insertion hole 65d for inserting the is formed.

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

That is, the coil spring 66 has a bent portion 66.
In the state in which a is fitted in the slit 65e of the loading member 65, the loading member 65 and the spring winding portion 59 of the worm 59.
It is sandwiched between b and. The coil spring 66 is normally wound so as to be in sliding contact with the outer circumference 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 59, 6
5 rotates integrally.

On the other hand, when the loading member 65 rotates with an excessive rotational load 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 prevented from being transmitted to the loading member 65. Therefore, the rotary plate member 53 does not rotate.

The rotary plate member 53 thus formed is
When the elevating shaft 8 rotates in the descending direction of the slats 5, as shown in FIG.
The worm 59 rotates integrally with the worm 59 in the E direction. At this time, in the expanding plate 53a of the rotating plate member 53, the weight portions 53e, 53e are moved to the arm portions 53d, 53d according to the rotating force thereof.
At the same time, it spreads in the outer peripheral direction and comes into sliding contact with the inner wall of the sliding contact case 55 arranged outside with a clearance. The weight portions 53e, 53e of the expanding plate 53a and the sliding contact case 5
By the sliding contact with 5, the rotation of the lifting shaft 8 is braked.

The weight portion 53e of the expanding plate 53a,
The expansion of 53e varies depending on the rotation speed. That is,
If the rotation speed is high, the expansion becomes large 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 slow, the expansion of the weight portions 53e, 53e of the expansion plate 53a becomes small, and the frictional force due to the sliding contact with the sliding contact case 55 becomes small.

Therefore, during the initial descent operation in which the weight of the slats 5 applied to the lifting shaft 8 is large, the lifting shaft 8
, The braking force generated in the braking device 11 is large, and conversely, at the end of the descent when the weight of the slat 5 applied to the lifting shaft 8 is small, the braking force is generated in the braking device 11 because the rotation of the lifting shaft 8 is slow. The braking force becomes smaller. Therefore,
In the horizontal blind device 1 according to the present embodiment, the slats 5
During the descent of its own weight, the braking force is varied from the initial descent to the final descent, and the descent is always performed at an appropriate speed, and the descent is surely performed to the lowest position.

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

In order to adjust the angle 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).
As a result, the drive gear 35 and the rotary shaft 36 rotate integrally. Then, the clutch member 38 is rotated together with the clutch spring 37 based on the rotation of the rotating shaft 36, and the tilt clutch shaft 42 is rotated 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, as the input shaft 16 rotates, the rotation shaft 36, the clutch spring 37, the clutch member 38, and the tilt clutch shaft 42 are rotated until the slat 5 stands vertically.
When is rotated, first, one of the both ends 37a and 37b of the clutch spring 37 comes into contact with the rotation blocking portion 39 of the upper case 14a. In this state, when the rotary shaft 36 further rotates in the same direction, the clutch spring 37 opens and the rotary shaft 36 idles with respect to the clutch spring 37.

Therefore, the connection between the rotary shaft 36 and the clutch spring 37 is cut off, and the second clutch means 34 is released. As a result, the rotational force of the input shaft 16 is not transmitted to the angle adjusting shaft 9 side. For this reason, even if the rotation of the slat 5 is stopped and the operation code 7 is continuously operated, the slat 5 does not rotate any more in the same direction after being rotated to the vertical position.

When the angle of the slat 5 is adjusted as described above, the carrier 22 of the planetary gear mechanism is rotated based on the rotation of the input shaft 16, but the first engaging portion 30 of the carrier 22 is engaged with the fitting shaft 17. Since the slat 5 is rotated until it becomes vertical before engaging with the second engaging portion 31, the elevating shaft 8 is not rotated during the angle adjustment operation of the slat 5.
As a result, when adjusting the angle of the slat 5, the bottom rail 6 is not moved up and down. The operation of raising or lowering the slat 5 is started by further operating the operation cord 7 in the same direction after the above-mentioned angle adjusting operation.

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

In order to pull up the slat 5,
First, the slat 5 is set in a parallel overlapping position (= light blocking state) by the angle adjusting operation described above. afterwards,
When the operation cord 7 is further operated in the pull-up direction, the input shaft 16 is rotated in the slat pull-up 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, as the carrier 22 rotates, the first engaging portion 30 of the carrier 22 engages with the second engaging portion 31 of the fitting shaft 17. Therefore, 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 of arrow B in FIG. Therefore, the slide ball 28 arranged on the outer periphery of the cam shaft 18 relatively moves in the first groove 24a of the cam shaft 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 cam shaft 18 and the teeth 25 of the second clutch plate 20.
And keep in mesh. Therefore, the camshaft 1
The rotation of 8 is transmitted to the second clutch plate 20, and the second clutch plate 20 rotates integrally with the cam shaft 18. By this, 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 pulled up, and from the slat 5 arranged on the bottom rail 6 side, the bottom rail 6 is pulled up to the head box 2 side together with the bottom rail 6.

When the elevating shaft 8 is rotating in the slat winding-up direction as described above, the braking device 11 described above is used.
Does not work. That is, when the lifting shaft 8 rotates, the rotational force of the lifting shaft 8 causes an input shaft 5
1 rotates. Then, the rotation of the input shaft 51 is transmitted to the pinion 60 of the speed increasing train wheel 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 arranged on the inner circumference of the worm wheel 58, is wound tightly. .
Therefore, the coil spring 62 causes the worm wheel 5 to
8, 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 the slat is wound up, the lifting shaft 8 can be rotated without being affected by the braking force of the braking device 11, and the operator's burden at the time of winding up can be lightened.

When the slat 5 and the bottom rail 6 are pulled up to desired positions and the operation cord 7 is released,
Due to the weight of the slat 5 and the bottom rail 6, a rotational force in a direction of lowering the slat 5 and the like acts on the elevating shaft 8. As a result, the rotational force in the same direction acts on the second clutch plate 20, and the cam shaft 18 and the fitting shaft 17 tend to rotate in the same direction. However, at this time, the fitting shaft 1
Since the second engaging portion 31 of 7 pushes the end portion 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 blocked, and the rotation of the lifting shaft 8 integrated with the fitting shaft 17 via the cam shaft 18 and the second clutch plate 20 is blocked. As a result, the weight of the slats 5 and the like is prevented from falling, and the slats 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 slat 5 and the bottom rail 6, the operation cord 7 is operated in the lowering direction (the direction opposite to the slat rising direction described above). Then, the input shaft 16 is rotated in the slat descending direction via the operation pulley 16a. As a result, the carrier 22 of the planetary gear mechanism is
Rotates, and this rotation is transmitted to the cam shaft 18 via the fitting shaft 17, and the cam shaft 18 rotates in the descending direction. That is, the cam shaft 18 rotates in the direction of arrow A in FIG. 4, and the slide ball 28 relatively moves in the direction of arrow B in FIG.

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

When the lifting shaft 8 rotates in the descending direction, this 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 train wheel 52, and the pinion 60 rotates integrally with the coil spring 62. At this time, the coil spring 62 expands so as to be in sliding contact with the inner peripheral surface (= the inner wall of the tubular portion) of the worm wheel 58 arranged on the outer side. As a result, the worm wheel 58 rotates integrally with the pinion 60 via the coil spring 62.

When the worm wheel 58 rotates, this rotation causes the worm 59 to rotate, and the rotary plate member 53 of the centrifugal governor 50 rotates integrally with the worm 59. As a result, the weight portions 53e, 53e of the expansion plate 53a of the rotary plate member 53 expand in the outer peripheral direction while elastically deforming due to the rotational centrifugal force, and make sliding contact with the inner wall of the sliding contact case 55 arranged around the weight.

The expansion of the expansion plate 53a at this time is as follows.
It changes depending on the rotation speed of the worm 59. That is,
When all the slats 5 are wound up to the vicinity of the head box 2 and descend by their own weight, the total weight of the slats 5 and the bottom rail 6 applied to the elevating shaft 8 is large, so that the rotating speed of the elevating shaft 8 is high. Conversely, bottom rail 6
At the time of descending from the state where it has almost descended to the predetermined lowest position, the rotation speed of the lifting shaft 8 is slow because the total weight of the slats 5 and the bottom rail 6 applied to the lifting shaft 8 is small. In accordance with such a situation, the rotation speed of the worm 59 and the situation of the expansion of the weight portions 53e, 53e of the expansion plate 53a of the centrifugal governor 50 accompanying it 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 and 53e and the sliding contact case 55. Therefore, in the braking device 11, since the rotational load applied to the elevating shaft 8 is large in the initial descent of the slat 5, the braking force is large. Therefore, although the total weight is large, the descending speed becomes considerably slow.

On the other hand, the braking device 11 has a small braking force at the end of the descent of the slat 5 because the rotational load applied to the elevating shaft 8 is small, and has no braking force at the end of the final stage. . For this reason, when the descending weight becomes small, the braking force becomes small and the descending weight is surely lowered at a slow speed. In this way, 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 is lowered by its own weight, and can surely lower the slat 5 to the lowest position.

The above-described embodiments are examples of preferred embodiments of the present invention, but the present invention is not limited to these, 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 the multi-stage slats 5 are hung from the head box 2, but if the blind member for the purpose of light blocking can be lowered by its own weight, It may be applied to a blind device having another configuration. That is, it may be applied to a tuck-up curtain of a type in which a cloth hanging from a head box is wound up by winding a cord, a pleated curtain in which a blind member made of a cloth bent in a zigzag shape is hung.

Further, in the above-described embodiment, the braking device 1
By providing the coil spring 62 as the one-way transmission means in the inside of 1, the braking force is not applied when the slat is raised, but such a structure is not necessarily required. However, when the slat pulling up operation is manually performed, if the rotation of the lifting shaft 8 is braked, the braking force becomes a load, which is not preferable. Therefore, in the above-described embodiment, the braking is applied only to the rotation when the weight is lowered. It was configured.
However, if the braking force at the time of pulling up is weak, the braking force may be applied even at the time of pulling up.

Further, although the coil spring 66 is provided in the braking device 11 as an overload preventing means, the overload preventing means may have another structure. For example, when one of the train wheels is configured by two gears that integrally rotate due to a friction force of a predetermined value or less, when the input rotational force is a force of a predetermined value or more, slippage occurs between the two gears. It is also possible that it occurs and idles, and the rotation is not transmitted to the rotary plate member. Further, it is also possible to adopt a configuration without an overload prevention means.

In the above embodiment, the angle adjusting shaft 9 is provided, but the present invention can be applied to a device having no angle adjusting shaft 9. Furthermore, although the slat 5 and the like are raised and lowered by operating the operation cord 7 by hand, the slat 5 and the like may be raised and lowered by using a motor and an operation switch (or remote controller). Also,
As the braking device, the worm 59 and the worm wheel 58 are included in the speed increasing train wheel 52 and the centrifugal governor 50 is provided, but the centrifugal governor portion may be a wind turbine type governor. Alternatively, a centrifugal governor or a windmill-type governor that does not use a worm or the like may be used. Even in the case of the wind turbine type governor, the governor portion may be protected by providing an overload preventing means such as a coil spring type or a sliding gear type.

Further, in the above-described embodiment, the centrifugal governor 50 has a clearance between the rotating plate member 53 and the sliding contact case 55, but this clearance is not in a normal state and the rotation is prevented. Even in the state where it is not, the expanding plate 53a of the rotating plate member 53 and the sliding contact case may be in contact with each other.

[0120]

In the blind device of the present invention, when the blind member is lowered by its own weight, its braking force is varied so as to cope with the rotational load applied to the elevating shaft which changes according to the weight of the portion that has not descended to the predetermined position. Since the braking device is connected to the lifting shaft, a large braking force works to lower the blind member at an appropriate speed at the beginning of descending when the rotating load on the lifting shaft is large, and at the end of descending when the rotating load is small. Reduces the braking force, and the blind member moves down smoothly and surely to the end.

In addition, the braking device of this blind device is provided with a speed increasing train wheel including a worm and a worm wheel, and a centrifugal governor. Therefore, the braking device has a compact structure, a very high speed increasing ratio can be obtained, the braking force is very small when the rotation of the lifting shaft is low, and the braking force is very high at high speed. can do. Further, since the number of parts of the speed increasing mechanism is small, friction between the respective parts is also reduced and the operation can be performed more smoothly. Furthermore, the rotary plate member,
If the elastic member integrally provided on the outer peripheral portion of the weight portion is provided, the number of parts is reduced as compared to the case where the shaft portion and the expanded portion are provided as separate members. In addition to being possible, it is possible to spread smoothly and exert a reliable braking force.

Further, if the braking device is provided with the one-way rotation transmission means so that the braking force of the braking device does not work when the blind member is raised, the lifting force can be raised lightly even by hand.

Further, if an angle adjusting shaft for suspending the slats via a ladder cord is provided in the head box, and the operating means also serves to rotate the angle adjusting shaft, a single operating means is used for raising and lowering operations. The angle adjustment operation can be performed, and the blind device is highly convenient.

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

[Brief description of drawings]

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

FIG. 2 is a cross-sectional view mainly showing a slat driving portion of the blind device shown in FIG.

3 is a cross-sectional view showing a state where the first clutch means is released in the slat drive section shown in FIG.

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

5 is a cross-sectional view of an operation delay unit that doubles as a one-way clutch of the slat drive unit illustrated in FIG.

6 is a cross-sectional view of a clutch spring portion of the second clutch means of the slat drive unit shown in FIG.

7 is a cross-sectional view of a coil frame portion of the second clutch means of the slat drive unit shown in FIG.

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

9 is a vertical cross-sectional view of the braking device shown in FIG.

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

[Explanation of symbols]

1 Blind device 2 head box 3 ladder code 4 lifting code 5 slats (blind members) 7 Operation code (operation means) 8 lifting axis 9 Angle adjustment axis 11 Braking device 21 First Clutch Means 34 Second Clutch Means 50 Centrifugal Governor 51 Input axis 52 gear train 53 Rotating plate member 53a Expansion plate 53c Rotation center shaft 53d weight part 55 Sliding contact case 58 worm wheel 59 Warm 62 Coil spring (unidirectional rotation transmission means) 66 Coil spring (overload prevention means)

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Katsuhiko Hayashi               14222 Hara-mura, Suwa-gun, Nagano Prefecture Co., Ltd.               Sankyo Seiki Seisakusho Suwa Factory                (56) References Japanese Patent Laid-Open No. 10-140949 (JP, A)                 JP-A-7-324572 (JP, A)                 Actual Kaihei 2-143498 (JP, U)                 59-94397 (JP, U)                 Actual Development Sho 61-73357 (JP, U)                 63-8053 (JP, U)                 Actual Kohei 6-16134 (JP, Y2)                 Utility model registration 3002331 (JP, Y2)

Claims (5)

(57) [Claims] 1. A blind member hung and supported by 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 rotating and stopping operation of the elevating shaft. And a clutch means for switching, 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. A braking device for braking the rotation of the lifting shaft, the braking device including an input shaft for inputting the rotation of the lifting shaft, a speed increasing train wheel for increasing and transmitting the rotation input to the input shaft, and the speed increasing device. A rotating plate member that rotates as a part of the train wheel and expands in the outer peripheral direction according to the rotation speed thereof, and a slide that is slidably contactable with the rotating plate member that is arranged around the rotating plate member and expands. Centrifugal governor consisting of contact case,
The speed-up gear train includes a worm and a worm wheel, and the centrifugal governor is configured to rotate when the rotational load applied to the lifting shaft is large when the blind member is lowered by its own weight. frictional force becomes large to the sliding contact case of the plate member, when the rotational load is smaller constructed as frictional force to the sliding contact case of the rotating plate member becomes small, further of the worm wheel On the circumference
As the blind member descends,
Unidirectional rotation that transmits only the rotation of the descending shaft to the rotating plate member
A transmission means is provided for raising the blind member.
The blind device is characterized in that the braking force of the braking device is not exerted . 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 expands in an outer peripheral direction by rotation. The blind device according to claim 1, further comprising a spreading plate integrally formed with a weight portion formed of an elastic member. 3. The elevating shaft is provided above the blind member.
Installed in the head box installed in the
The slats of the slats consist of multi-stage slats.
Adjust the ladder cord to adjust the
The blind device according to claim 1 or 2, wherein the blind device is suspended from the blind device. 4. The ladder box is provided in the head box.
An angle adjusting shaft is provided to suspend the slats through the cord.
Rutotomoni, in the operation means a rotational operation of the angle adjustment shaft
This operation means is also used as a dual purpose and the slat is moved up and down by this operating means.
When performing the operation, disconnect the connection between the operating means and the angle adjusting shaft.
Claim 3, characterized in that a clutch means for dividing
The blind device described. 5. An elevating shaft is hung and supported by an elevating cord.
Blind member and lifting operation of the blind member
To operate the lifting shaft to rotate
The clutch hand that switches between rotating and stopping the lifting shaft.
A step, and based on the operation of the operation means, the class
The blind means to release the blind member by its own weight.
In a blind device that can be lowered,
The input shaft for inputting the rotation of the lifting shaft and the input to the input shaft
And a rotating member that rotates based on rotation,
Rotation of the lifting shaft by adding a predetermined resistance to the rotation
Equipped with a braking device for braking the
Excessive rotational force is input to the rotating member, causing the above rotating member to over rotate.
In order to prevent the excessive rotation force from being input,
When this rotational force is not transmitted to the rotating member,
At the time of rolling, it is designed so that the rotational force is transmitted to the rotating member.
A grinding device comprising an overload prevention means formed .