Operating device and shielding device

Abstract

To provide a technique that can make the rotational speed of a drive shaft in the same rotational direction different from the rotation of an input shaft with the same rotational speed in a different rotational direction.SOLUTION: An operating device 8 that operates a lifting shaft 22 that drives a shielding material in a shielding device to open and close, includes an input shaft 811 to which rotational force around a first rotational direction or around a second rotational direction opposite to the first rotational direction is input; and a switching mechanism that transmits the rotational force to the lifting shaft 22 via a first transmission path when the rotational force around the first rotational direction is input to the input shaft 811 and that transmits the reversed rotational force around the first rotational direction to the lifting shaft 22 via a second transmission path when the rotational force around the second rotational direction is input to the input shaft 811. The switching mechanism shifts the rotation input to the input shaft 811 to different gear ratios in either the first transmission path or the second transmission path.SELECTED DRAWING: Figure 3

Description

TECHNICAL FIELD

[0001] The present embodiment relates to an operating device for performing opening and closing operations on a shielding member of a shielding apparatus, and a shielding apparatus provided with the operating device. BACKGROUND ART

[0002] Conventionally, as a shielding apparatus provided with an operating device for performing opening and closing operations on a shielding member, a solar radiation shielding apparatus disclosed in Patent Document 1 is known. This solar radiation shielding apparatus is provided with a transmission unit that transmits the rotation of an input shaft, which is rotated in forward and reverse directions based on the operation of an operating unit, in the lowering direction of the shielding member to a drive shaft at a higher speed than the rotation in the raising direction of the shielding member.

[0003] According to such a shielding apparatus, the drive shaft can be rotated at the same speed as the input shaft during the pulling-up operation of the shielding member, and the lowering speed of the shielding member can be made higher than the pulling-up speed of the shielding member during the lowering operation of the shielding member. PRIOR ART DOCUMENTS PATENT DOCUMENTS

[0004] PATENT DOCUMENT 1 Japanese Unexamined Patent Application Publication No. 2006-28871 SUMMARY OF THE INVENTION PROBLEMS TO BE SOLVED BY THE INVENTION

[0005] However, according to the above-described solar radiation shielding apparatus, while it is possible to make the rotational speed of the drive shaft during the pulling-up operation and during the lowering operation, that is, the forward rotational direction speed and the reverse rotational direction speed of the drive shaft, different from each other with respect to the rotation of the input shaft at the same rotational speed, there is a problem that the rotational speed in the same rotational direction of the drive shaft cannot be changed.

[0006] This invention was made to solve the above-mentioned problems, and aims to provide a technique for making the rotational speed of the drive shaft different for the same rotational speed of an input shaft with a different rotational direction. [Means for solving the problem]

[0007] To solve the above-mentioned problems, one aspect of the present invention is an operating device for operating a drive shaft that drives a shielding material to open and close in a shielding device, comprising: an input shaft to which a rotational force is input around a first rotational direction or around a second rotational direction opposite to the first rotational direction; and a switching mechanism that transmits the rotational force to the drive shaft via a first transmission path when a rotational force is input to the input shaft around the first rotational direction, and transmits the rotational force to the drive shaft via a second transmission path when a rotational force is input to the input shaft around the second rotational direction, wherein the switching mechanism changes the rotation input to the input shaft to different gear ratios in either the first transmission path or the second transmission path.

[0008] Furthermore, one aspect of the present invention is an operating device for opening and closing a shielding material in a shielding device, comprising a switching mechanism that switches between a first operating state in which a drive shaft for driving the opening and closing of the shielding material to which the rotation is transmitted is rotated in one direction at a first rotational speed, and a second operating state in which the drive shaft is rotated in one direction at a second rotational speed different from the first rotational speed, according to the direction of rotation of the rotation input by a rotational operation on the shielding device. [Effects of the Invention]

[0009] According to the present invention, it is possible to make the rotational speed of the drive shaft in the same direction of rotation different for input shafts that rotate at the same rotational speed but in different directions. [Brief explanation of the drawing]

[0010] [Figure 1] This is a front view showing the configuration of the shielding device according to the first embodiment. [Figure 2]This is a front view showing the configuration of the drive mechanism in the operating device according to the first embodiment. [Figure 3] This is a front view showing the configuration of the switching mechanism in the operating device according to the first embodiment. [Figure 4] This is a cross-sectional view along line AA in Figure 3. [Figure 5] Figure 3 is a cross-sectional view along line BB. [Figure 6] This is a front view showing the configuration of the clutch according to the first embodiment. [Figure 7] Figure 3 is a cross-sectional view along the CC line. [Figure 8] This is a perspective view showing the cylindrical member and the second transmission member. [Figure 9] This is a perspective view showing the clutch spring attached to the cylindrical member. [Figure 10] This is a perspective view showing a cylindrical member with a cam member attached. [Figure 11] This is a front view showing a clutch mechanism in a first engagement state according to the first embodiment. [Figure 12] This is a front view showing a clutch mechanism in a second engagement state according to the first embodiment. [Figure 13] This is a front view showing the switching mechanism in the first operating state according to the first embodiment. [Figure 14] This is a front view showing the switching mechanism in the second operating state according to the first embodiment. [Figure 15] This is a front view showing the configuration of the switching mechanism according to the second embodiment. [Figure 16] This is a front view showing the switching mechanism in the first operating state according to the second embodiment. [Figure 17] This is a front view showing the switching mechanism in the second operating state according to the second embodiment. [Modes for carrying out the invention]

[0011] Hereinafter, embodiments according to the present invention will be described with reference to the drawings. In the present embodiment, description will be given taking as an example a shading device in which the present invention is applied to a horizontal blind provided with a plurality of slats as a shading member. In the present embodiment, when the shading device is installed, the indoor side surface is referred to as the front face, the outdoor side surface as the back face, the direction consisting of the front face and the back face as the front-rear direction, and the longitudinal direction of the shading device as the left-right direction for the subsequent description. In addition, in the present specification and the drawings, components having substantially the same function are denoted by the same reference numerals, and redundant description thereof will be omitted.

[0012] <First Embodiment> (Overall Configuration) The overall configuration of the shading device according to the first embodiment will be described. Figure 1 is a front view showing the configuration of the shading device according to the present embodiment. Note that Figure 1 shows the shading device in a state where the bottom rail is lowered to the lowest lowered position, and components incorporated in the headbox are shown by making a part of the headbox transparent.

[0013] As shown in Figure 1, the shading device 1 according to the present embodiment includes a headbox 2, a plurality of slats 4, a plurality of lift cords 5, a plurality of ladder cords 6, a bottom rail 7, an operating device 8, a lift shaft 22, a rotation shaft 23, a plurality of drum devices 24, and a stopper (not shown).

[0014] The headbox 2 is formed in a substantially rectangular parallelepiped shape that defines a storage space inside, and is fixed to a window frame or the like (not shown) via a plurality of brackets 21. The headbox 2 accommodates the lift shaft 22, the rotation shaft 23, the drum device 24 having a take-up drum and a rotation drum, and the stopper. In addition, the operating device 8 is provided at one end of the headbox 2.

[0015] Each of the multiple slats 4 is supported in a vertical direction by ladder cords 6 that hang down from the headbox 2 between the headbox 2 and the bottom rail 7. One end of each ladder cord 6 is connected to a rotating drum in a corresponding drum device 24 so as to be able to be wound up and unwound, and hangs down from the headbox 2. The other end is connected to the bottom rail 7 and is positioned in front of and behind the slats 4, sandwiching them and supporting the slats 4 individually.

[0016] The bottom rail 7 is suspended and supported by lifting cords 5 that hang down from the headbox 2, so as to be located at the lowest end of the shielding device 1. Multiple lifting cords 5 are connected at one end to a winding drum in the corresponding drum device 24 so as to be able to be wound and unwound, and at the other end to the bottom rail 7, thereby suspending and supporting the bottom rail 7.

[0017] The lifting shaft 22 is rotatably supported within the headbox 2 such that its axial direction is aligned with the longitudinal direction of the headbox 2, i.e., left-right. The winding drum in each of the multiple drum devices 24 is rotated by the lifting shaft 22, raising and lowering the bottom rail 7, which in turn raises and lowers the slats 4. The rotation of the lifting shaft 22 is restricted by a stopper when a predetermined operation is performed on the shielding device 1, as will be described in detail later.

[0018] The rotating shaft 23 is positioned above the lifting shaft 22 and is rotatably supported within the headbox 2 such that its axial direction faces the longitudinal direction of the headbox 2, i.e., the left-right direction. The rotating drum in each of the multiple drum devices 24 is rotated by the rotating shaft 23 by a predetermined angular range, thereby causing the front and rear ladder cords 6 to move relative to each other in the vertical direction and the slats 4 to rotate.

[0019] (Configuration of the operating device) The configuration of the operating device according to the first embodiment will now be described. Figures 2 and 3 are front views showing the configuration of the drive mechanism and the switching mechanism in the operating device according to this embodiment, respectively.

[0020] As shown in Figures 2 and 3, the shielding device 1 according to this embodiment includes a pulley 800, an operating member 801, a first housing portion 802, a plurality of planetary gears 803, a drive gear 804, an output shaft 805, a driven gear 806, a second housing portion 810, an input shaft 811, a first clutch receiver 812, a second clutch receiver 813, a first gear 815, a second gear 816, an intermediate gear 817, and a clutch 82.

[0021] As shown in Figure 2, the pulley 800, operating member 801, first housing 802, multiple planetary gears 803, drive gear 804, output shaft 805, and driven gear 806 constitute the drive mechanism. As shown in Figure 3, the second housing 810, input shaft 811, first clutch receiver 812, second clutch receiver 813, first gear 815, second gear 816, intermediate gear 817, and clutch 82 constitute the switching mechanism.

[0022] (Configuration of the drive mechanism) The configuration of the drive mechanism according to the first embodiment will be described with reference to Figure 2.

[0023] The operating member 801 is a member formed in the shape of an endless string. The pulley 800 is rotatably mounted so as to be substantially concentric with the lifting shaft 22 and is formed so that the operating member 801 is wound around it. When the operating member 801 is wound around the pulley 800, it hangs down from two different locations in the front-rear direction of the operating device 8 so that it can be pulled by an operator. When the indoor side of the hanging operating member 801 is pulled by the operator, the pulley 800 rotates in the first rotational direction. Also, when the outdoor side of the hanging operating member 801 is pulled by the operator, the pulley 800 rotates in the second rotational direction, which is opposite to the first rotational direction.

[0024] The first housing portion 802 is a member on which an internal gear is formed and is fixedly mounted to the headbox 2. Multiple planetary gears 803 cooperate with the internal gear formed on the first housing portion 802, a sun gear (not shown), etc., to form a planetary gear mechanism. The rotation of the pulley 800 is input to the planetary gear mechanism, and the planetary gear mechanism reduces the input rotation and transmits it to the output shaft 805.

[0025] The output shaft 805 is rotatably mounted so as to be substantially concentric with the lifting shaft 22 and the pulley 800, and its axial direction is oriented left to right. The output shaft 805 is connected to the input shaft 811 so as to be rotatable together, thereby outputting rotational force to the switching mechanism. The drive gear 804 is rotatably mounted together with the output shaft 805 and meshes with the driven gear 806. The driven gear 806 is rotatably mounted together with the rotating shaft 23 and meshes with the drive gear 804.

[0026] With this drive mechanism, the rotational force of the pulley 800 is reduced and transmitted to the switching mechanism and the rotating shaft 23. Furthermore, when the indoor side of the operating member 801 is pulled, the pulley 800 rotates counterclockwise (first rotation direction) when viewed from the left-right outward side, and when the outdoor side of the operating member 801 is pulled, the pulley 800 rotates clockwise (second rotation direction) when viewed from the left-right outward side.

[0027] (Configuration of the switching mechanism) The configuration of the switching mechanism according to the first embodiment will be described with reference to Figures 3 to 5. Figures 4 and 5 are cross-sectional views taken along lines AA and BB of Figure 3, respectively.

[0028] The second housing section 810 is a component that defines the housing space and is fixedly mounted to the headbox 2. The housing space of the second housing section 810 houses the input shaft 811, the first clutch receiver 812, the second clutch receiver 813, the first gear 815, the second gear 816, the intermediate gear 817, and the clutch 82. The input shaft 811, the first gear 815, the second gear 816, and the intermediate gear 817 are rotatably supported by the second housing section 810.

[0029] The input shaft 811 is approximately concentric with the lifting shaft 22, the pulley 800, and the output shaft 805, and is rotatably mounted so that its axial direction faces left to right. The left-right outer side of the input shaft 811 (right side in Figure 3) is connected to the output shaft 805 so as to be integrally rotatable, thereby inputting rotational force from the output shaft 805 to the input shaft 811. The input shaft 811 is supported by the insertion of the first clutch receiver 812, the second clutch receiver 813, and the clutch 82. The input shaft 811, the first clutch receiver 812, the second clutch receiver 813, and the clutch 82 constitute a clutch mechanism.

[0030] The first and second clutch receivers 812 and 813 are both formed in a disc shape with a through hole in the center, and the input shaft 811 is inserted through this through hole, thereby supporting them so as to be rotatable relative to the input shaft 811. When supported by the input shaft 811, the first clutch receiver 812 is located on the inward side in the left-right direction relative to the clutch 82 (left side in Figure 3), and the second clutch receiver 813 is located on the outward side in the left-right direction relative to the clutch 82 (right side in Figure 3).

[0031] Multiple projections spaced apart in the circumferential direction are formed on the opposing surface of the first clutch receiver 812 that faces the second clutch receiver 813. Similarly, multiple projections spaced apart in the circumferential direction are formed on the opposing surface of the second clutch receiver 813 that faces the first clutch receiver 812. Each of the multiple projections in the first and second clutch receivers 812 and 813 has an inclined surface that is inclined with respect to the circumferential direction and a vertical surface that is perpendicular to the opposing surface. In this embodiment, the inclined surfaces of the multiple projections formed on the first clutch receiver 812 are formed on the counterclockwise direction side of the projection when viewed from the outward side in the left-right direction. Similarly, the inclined surfaces of the multiple projections formed on the second clutch receiver 813 are formed on the counterclockwise direction side of the projection when viewed from the inward side in the left-right direction.

[0032] The first clutch receiver 812 is provided with a gear section 812G and an output shaft 812A that rotate integrally with the first clutch receiver 812. The gear section 812G is positioned to the left-right inward side relative to the first clutch receiver 812 when the first clutch receiver 812 is pivotally supported on the input shaft 811, and as shown in Figure 4, it is a spur gear that meshes with the spur gear 815G of the first gear 815, which will be described later. In this embodiment, the gear ratio between the gear section 812G and the spur gear 815G is 19:23. The output shaft 812A is positioned to the left-right inward side relative to the gear section 812G when the first clutch receiver 812 is pivotally supported on the input shaft 811, and one end of the lifting shaft 22 is rotatably connected to it. The rotational force input to the switching mechanism is output to the lifting shaft 22 via the output shaft 812A.

[0033] The second clutch receiver 813 is provided with a gear portion 813G that rotates integrally with the second clutch receiver 813. The gear portion 813G is positioned outward in the left-right direction relative to the second clutch receiver 813 when the second clutch receiver 813 is pivotally supported on the input shaft 811, and as shown in Figure 5, it is a spur gear that meshes with the spur gear 816G of the second gear 816, which will be described later. In this embodiment, the gear ratio between the gear portion 813G and the spur gear 816G is 23:19.

[0034] As will be described in detail later, the clutch 82 is pivotally supported on the input shaft 811 so as to be unable to rotate relative to it and movable in the axial direction. The clutch mechanism transitions to a first engagement state in which the clutch 82 and the first clutch receiver 812 are engaged so as to be able to rotate together when the clutch 82 is moved inward in the left-right direction, and to a second engagement state in which the clutch 82 and the second clutch receiver 813 are engaged so as to be able to rotate together when the clutch 82 is moved outward in the left-right direction. The configuration of the clutch 82 and the operation of the clutch mechanism will be described later.

[0035] The first gear 815 has a spur gear 815G and a helical gear 815H that are mounted to rotate integrally with each other, and is rotatably supported around an axis that faces left to right. When the first gear 815 is mounted, the helical gear 815H is located outward in the left to right direction relative to the spur gear 815G. The second gear 816 has a spur gear 816G and a helical gear 816H that are mounted to rotate integrally with each other, and is rotatably supported around an axis that faces left to right. When the second gear 816 is mounted, the helical gear 816H is located inward in the left to right direction relative to the spur gear 816G.

[0036] The intermediate gear 817 is a helical gear provided between the helical gears 815H and 816H in the left-right direction and rotatably supported around an axis facing up and down. As described above, the spur gears 815G and 816G mesh with the gear portion 812G of the first clutch receiver 812 and the gear portion 813G of the second clutch receiver 813, respectively. The helical gears 815H and 816H mesh with the intermediate gear 817.

[0037] The gear sections 812G, 813G, the first and second gears 815, 816, and the intermediate gear 817 constitute a reverse gear shifting mechanism that reverses and shifts the rotation of the second clutch receiver 813 and transmits it to the first clutch receiver 812. In this embodiment, the reverse gear shifting mechanism transmits the rotation of the input shaft 811 (19 / 23) 2 The speed is increased by the gear ratio and transmitted to the output shaft 812A.

[0038] (Clutch configuration) The configuration of the clutch according to the first embodiment will now be described. Figure 6 is a front view showing the configuration of the clutch according to this embodiment. Figure 7 is a cross-sectional view taken along line CC in Figure 3. Figure 8 is a perspective view showing the cylindrical member and the second transmission member. Figure 9 is a perspective view showing the cylindrical member with the clutch spring attached. Figure 10 is a perspective view showing the cylindrical member with the cam member attached.

[0039] As shown in Figures 6 to 10, the clutch 82 comprises a cylindrical member 823, a cam member 824, a clutch spring 825, first and second transmission members 826A, 826B, and first and second fitting portions 826A1, 826B1.

[0040] As shown in Figure 6, the first and second transmission members 826A and 826B are both formed in a disc shape with a through hole in the center through which the input shaft 811 can be inserted. When the input shaft 811 is inserted, the first transmission member 826A is located on the left-right side (left side in Figure 6) relative to the second transmission member 826B, and the second transmission member 826B is located on the right-right side (right side in Figure 6) relative to the first transmission member 826A.

[0041] Multiple projections spaced apart in the circumferential direction are formed on the opposing surface of the first transmission member 826A that faces the first clutch receiver 812. Similarly, multiple projections spaced apart in the circumferential direction are formed on the opposing surface of the second transmission member 826B that faces the second clutch receiver 813. Each of the multiple projections on the first and second transmission members 826A and 826B has an inclined surface that is inclined with respect to the circumferential direction and a vertical surface that is perpendicular to the opposing surface. In this embodiment, the inclined surfaces of the multiple projections formed on the first transmission member 826A are formed on the counterclockwise side of the projection when viewed from the inward side in the left-right direction. Similarly, the inclined surfaces of the multiple projections formed on the second transmission member 826B are formed on the counterclockwise side of the projection when viewed from the outward side in the left-right direction.

[0042] As shown in Figure 7, the second fitting portion 826B1 is provided on the opposing surface of the second transmission member 826B that faces the first transmission member 826A, and is formed in a substantially cylindrical shape. Three protrusions are formed on the circumferential surface of the input shaft 811, projecting radially outward and extending axially, and three guide grooves are formed between the three protrusions along the axial direction. The second fitting portion 826B1 is formed in an uneven shape to match the shape of the circumferential wall of the input shaft 811, and fits to the input shaft 811 so as to be integrally rotatable. The axial length of the second fitting portion 826B1 is formed to be shorter than the three guide grooves, thereby allowing the second transmission member 826B, to which the second fitting portion 826B1 is provided, to slide axially along the three guide grooves. In addition, three guide grooves are formed on the outer circumferential surface of the second fitting portion 826B1 at circumferential positions corresponding to the three guide grooves of the input shaft 811.

[0043] As shown in Figure 7, the first fitting portion 826A1 is provided on the opposing surface of the first transmission member 826A facing the second transmission member 826B, and has three plate-like members. The three plate-like members are each provided on the opposing surface so as to be spaced apart from each other in the circumferential direction, and extend in the axial direction of the input shaft 811. The first transmission member 826A is assembled to the second fitting portion 826B1 so as to be integrally rotatable when the three plate-like members are fitted into the three guide grooves of the second fitting portion 826B1.

[0044] As shown in Figure 7, the cylindrical member 823 is formed in a hollow cylindrical shape, and the first and second fitting portions 826A1 and 826B1 are inserted through its hollow portion and pivotally supported by the first and second fitting portions 826A1 and 826B1. As shown in Figure 8, a fitting groove 823G is formed on a part of the outer peripheral wall of the cylindrical member 823, into which a projection 826B2 formed on the inner peripheral wall of the hollow portion of the second transmission member 826B fits. By fitting the projection 826B2 into this fitting groove 823G, the cylindrical member 823 is fixed so as to be able to rotate integrally with the second transmission member 826B. Therefore, in accordance with the rotation of the input shaft 811, the cylindrical member 823 can rotate integrally with the first and second transmission members 826A and 826B.

[0045] As shown in Figures 7, 9, and 10, the clutch spring 825 is a linear elastic member that is spirally wound around the outer circumference of the cylindrical member 823, with both ends 825E bent radially outward. When the clutch is engaged, the clutch spring 825 is tightened to the cylindrical member 823 by elastic force and rotates integrally with the cylindrical member 823. When the clutch is released, it expands in diameter as will be described in detail later, releasing the clutch engagement state, and becomes rotatable relative to the cylindrical member 823.

[0046] As shown in Figures 6, 7, and 10, the cam member 824 is formed in a hollow cylindrical shape, and is pivotally supported by inserting a cylindrical member 823, through which a clutch spring 825 is wound, into its hollow portion. As shown in Figure 10, two through holes 824H are formed in the outer circumferential wall of the cam member 824, through which each of the two ends 825E of the clutch spring 825 is individually inserted. When the clutch spring 825 is in the clutch-engaged state, the clutch spring 825 rotates together with the cylindrical member 823 in accordance with the rotation of the input shaft 811. As a result, either one of the two ends 825E comes into contact with the wall surface of the through hole 824H through which it is inserted, and the cam member 824 rotates integrally with the cylindrical member 823 via the clutch spring 825. On the other hand, when the clutch spring 825 is in the clutch release state, the cam member 824 and the clutch spring 825 become rotatable relative to the cylindrical member 823, and the components of the clutch 82 other than the cam member 824 and the clutch spring 825 rotate together with the input shaft 811.

[0047] As shown in Figure 6, the cam member 824 has a cam groove 824G formed on its outer circumferential wall that is inclined in the left-right direction with respect to the circumferential direction. A steel ball 829 is slidably fitted into the cam groove 824G, and the steel ball 829 is fixed immovably to the front inner wall of the second housing portion 810. In this embodiment, the cam groove 824G is inclined such that, with the steel ball 829 approximately in the center of the cam groove 824G, the upper end is located outward in the left-right direction and the lower end is located inward in the left-right direction. When it rotates in accordance with the rotation of the input shaft 811, the steel ball 829 slides along the cam groove 824G. At this time, since the steel ball 829 is fixed immovably and the clutch 82 is movable in the axial direction relative to the input shaft 811, the rotational motion is converted into linear motion in the left-right direction, and the clutch 82 rotates in accordance with the direction of rotation and moves inward and outward in the left-right direction.

[0048] (Operation of the clutch mechanism) The operation of the clutch mechanism according to the first embodiment will now be described. Figures 11 and 12 are front views showing the clutch mechanism in the first and second engagement states according to this embodiment, respectively.

[0049] As shown in Figure 11, when the input shaft 811 is rotated counterclockwise when viewed from the outward side in the left-right direction, the clutch 82 rotates counterclockwise, causing the steel ball 829 to slide upward towards the cam groove 824G, thereby moving the clutch 82 inward in the left-right direction (left side in Figure 11), and the clutch mechanism enters the first engaged state. At this time, the vertical surface of the projection of the first clutch receiver 812 and the vertical surface of the projection of the first transmission member 826A come into contact with each other and engage in the circumferential direction, making it possible to transmit the rotational force of the clutch 82 to the first clutch receiver 812.

[0050] When the clutch mechanism is in the first engaged state, the steel ball 829 is positioned at the upper end of the cam groove 824G, thereby restricting the counterclockwise rotation of the cam member 824. When the input shaft 811 is further rotated counterclockwise, the clutch spring 825 disengages, and the cam member 824 becomes rotatable relative to the input shaft 811. Therefore, the clutch 82 can transmit the rotational force of the input shaft 811 to the first clutch receiver 812 via the first transmission member 826A without the counterclockwise rotation being hindered by the steel ball 829.

[0051] As shown in Figure 12, when the input shaft 811 is rotated clockwise when viewed from the left-right outward side, the clutch 82 rotates clockwise, causing the steel ball 829 to slide downward in the cam groove 824G, thereby moving the clutch 82 outward in the left-right direction (right side in Figure 12), and the clutch mechanism enters the second engagement state. At this time, the vertical surface of the projection of the second clutch receiver 813 and the vertical surface of the projection of the second transmission member 826B come into contact with each other and engage in the circumferential direction, allowing the rotational force of the clutch 82 to be transmitted to the second clutch receiver 813.

[0052] When the clutch mechanism is in the second engagement state, the steel ball 829 is positioned at the lower end of the cam groove 824G, thereby restricting the clockwise rotation of the cam member 824. In this case, if the input shaft 811 is rotated further clockwise, the clutch spring 825 disengages, and the cam member 824 becomes rotatable relative to the input shaft 811. Therefore, the clutch 82 can transmit the rotational force of the input shaft 811 to the second clutch receiver 813 via the second transmission member 826B without its clockwise rotation being hindered by the steel ball 829.

[0053] Furthermore, if the steel ball 829 is not located at either the upper or lower end of the cam groove 824G, the clutch mechanism will be in a disengaged state (see Figure 6) in which the first transmission member 826A does not engage with the first clutch receiver 812 and the second transmission member 826B does not engage with the second clutch receiver 813.

[0054] (Operation of the switching mechanism) The operation of the switching mechanism according to the first embodiment will now be described. Figures 13 and 14 are front views showing the switching mechanism in the first and second operating states according to this embodiment, respectively.

[0055] As shown in Figure 13, when the clutch mechanism transitions to the first engaged state, the switching mechanism transitions to the first operating state in which the rotational force of the input shaft 811 is output to the output shaft 812A via the first transmission path. When the input shaft 811 is rotated counterclockwise when viewed from the left-right outward side while the switching mechanism is in the first operating state, the lifting shaft 22, which is connected to the output shaft 812A and is integrally rotatable with the first clutch receiver 812, is rotated counterclockwise via the clutch 82. In the first engaged state, the rotational force input to the input shaft 811 is output from the output shaft 812A without changing speed.

[0056] In the first operating state, the rotational force of the gear section 812G, which is integrally rotatable with the first clutch receiver 812, is transmitted to the second clutch receiver 813, which is equipped with a gear section 813G, via the first gear 815, the intermediate gear 817, and the second gear 816. Since the second clutch receiver 813 is pivotally supported so as to be rotatable relative to the input shaft 811, the rotation of the second clutch receiver 813 in the first operating state does not affect the rotation of the lifting shaft 22.

[0057] As shown in Figure 14, when the clutch mechanism transitions to the second engagement state, the switching mechanism transitions to the second operating state, which outputs the rotational force of the input shaft 811 to the output shaft 812A via the second transmission path. When the input shaft 811 is rotated clockwise when viewed from the left-right outward side while the switching mechanism is in the second operating state, the gear portion 813G, which is integrally rotatable with the second clutch receiver 813, is rotated clockwise via the clutch 82.

[0058] The rotational force of gear section 813G is reversed when transmitted to the second gear 816, causing the second gear 816 to rotate counterclockwise. The rotational force of the second gear 816 is reversed when transmitted to the first gear 815 via the intermediate gear 817, causing the first gear 815 to rotate clockwise. The rotational force of the first gear 815 is reversed when transmitted to the gear section 812G of the first clutch receiver 812, causing the lifting shaft 22, which is connected to the output shaft 812A that rotates integrally with the gear section 812G, to rotate counterclockwise.

[0059] In the second operating state, the rotational force of the input shaft 811 is transmitted to the lifting shaft 22 via the reverse speed change mechanism, so that the lifting shaft 22 can be rotated in the same rotational direction as in the first engagement state by the increased rotational force.

[0060] In both the first and second operating states, when the lifting shaft 22 is rotated, the multiple lifting cords 5 are wound up by the winding drums in each of the multiple drum devices 24, causing the bottom rail 7 to rise. Furthermore, when the operator releases the operating member 801, the rotation of the lifting shaft 22 is restricted by the stopper, and the bottom rail 7 is maintained in the raised position.

[0061] Furthermore, in the first operating state, when the indoor side of the operating member 801 is pulled by a predetermined distance, or in the second operating state, when the outdoor side of the operating member 801 is pulled by a predetermined distance, the stopper restriction is released and the bottom rail 7 descends by its own weight. At this time, the clutch mechanism becomes disengaged, so that the rotational force of the lifting shaft 22 generated by the lowering of the bottom rail 7 and the winding of the multiple lifting cords 5 from the corresponding winding drums is not transmitted to the pulley 800.

[0062] Thus, according to the operating device 8 of this embodiment, the rotational speed of the lifting shaft 22, which acts as a drive shaft for opening and closing the shielding material, can be varied in the same rotational direction depending on the input rotational direction.

[0063] <Second Embodiment> The operating device according to the second embodiment will now be described. Figure 15 is a front view showing the configuration of the switching mechanism according to this embodiment. Figures 16 and 17 are front views showing the switching mechanism in the first operating state and the second operating state according to this embodiment.

[0064] As shown in Figure 15, the operating device 8a according to this embodiment differs from the operating device 8 according to the first embodiment in the configuration of the clutch mechanism. Specifically, the operating device 8a differs from the operating device 8 in that it has a first clutch receiver 812a and a clutch 82a instead of the first clutch receiver 812 and clutch 82, and further includes a spring 818.

[0065] The first clutch receiver 812a differs from the first clutch receiver 812 in that its disc-shaped portion is separated from the gear portion 812G and the output shaft 812A in the left-right direction and is pivotally supported on the output shaft 812A so as to be integrally rotatable. The first clutch receiver 812a also differs from the first clutch receiver 812 in that a flange portion 812F is provided between its disc-shaped portion and the gear portion 812G, extending radially outward from the output shaft 812A over its entire circumferential area. The spring 818 is a compression coil spring pivotally supported between the flange portion 812F and the disc-shaped portion of the first clutch receiver 812a, biasing the disc-shaped portion of the first clutch receiver 812 outward in the left-right direction relative to the flange portion 812F.

[0066] The clutch 82a is a component in which members corresponding to the first and second transmission members 826A and 826B of the clutch 82 are integrally formed. Similar to the clutch 82, the clutch 82a is pivotally supported on the input shaft 811 so as to be movable in the left-right direction between the first clutch receiver 812a and the second clutch receiver 813, and so as to be rotatable integrally with the input shaft 811.

[0067] As shown in Figure 16, when the input shaft 811 is rotated counterclockwise when viewed from the left-right outward side, the inclined surface formed on the projection on the left-right outward side of the clutch 82a and the inclined surface of the projection on the second clutch receiver 813 come into sliding contact, causing the clutch 82a to move inward in the left-right direction and the clutch mechanism to transition to the first engaged state.

[0068] As shown in Figure 17, when the input shaft 811 is rotated clockwise when viewed from the left-right outward side, the inclined surface formed on the projection on the left-right inward side of the clutch 82a and the inclined surface of the projection on the first clutch receiver 812a come into sliding contact, causing the clutch 82a to move outward in the left-right direction and the clutch mechanism to transition to the second engagement state.

[0069] The spring 818 prevents the tip of the projection of the first clutch receiver 812 from engaging with the tip of the projection on the left-right inward side of the clutch 82a, thereby ensuring reliable rotation and left-right movement of the clutch 82a. For further details of the clutch mechanism according to this embodiment, please refer to Japanese Patent Application Publication No. 2020-94360.

[0070] Thus, the switching mechanism of the operating device 8a uses a clutch mechanism different from that of the first embodiment, allowing it to vary the rotational speed in the same direction according to the rotational direction of the input shaft 811.

[0071] In the embodiment described above, the rotational force is increased in the second operating state, but operating devices 8, 8a may be configured with a gear ratio that is changed so that the rotational force is reduced in the second operating state. Furthermore, operating devices 8, 8a may be configured such that the rotational force is changed such that the gear ratios are different in at least one of the first or second operating states.

[0072] Furthermore, although the reverse gear shifting mechanism is configured with multiple gears in the above-described embodiment, it may also be configured with other components that can reverse rotation and change speed, such as multiple sprockets or multiple pulleys that are provided to transmit rotational force to each other.

[0073] Furthermore, in the above-described embodiment, the object of operation by the operating devices 8,8a was the lifting shaft 22 that raises and lowers the bottom rail 7, but the operating devices 8,8a may operate any drive shaft that drives the opening and closing of the shielding material. Also, in the above-described embodiment, the shielding device 1 to which the operating devices 8,8a are provided was a horizontal blind, but the operating devices 8,8a may be applied to other types of shielding devices such as vertical blinds or roller screens.

[0074] The present invention can be implemented in various other forms without departing from its essence or main features. Therefore, the embodiments described above are merely illustrative in all respects and should not be construed restrictively. The scope of the invention is defined by the claims and is not restricted in any way by the text of the specification. Furthermore, all variations, improvements, substitutions, and modifications falling within the equivalent scope of the claims are all within the scope of the invention. [Explanation of Symbols]

[0075] 1 Shielding device 22 Lifting shaft (drive shaft) 8,8a Operating device 811 input axis 812 First clutch receiver 813 Second clutch receiver 82,82a Clutch 815 First Gear 816 Second Gear 817 Relay Gear

Claims

1. A shielding device comprising an operating device for operating a drive shaft that drives a shielding material up and down, and a stopper for restricting the rotation of the drive shaft, The aforementioned operating device is An input shaft to which a rotational force is input around a first rotational direction or around a second rotational direction opposite to the first rotational direction, The system includes a switching mechanism that transmits a rotational force to the drive shaft via a first transmission path when a rotational force is input to the input shaft around the first rotational direction, and transmits a rotational force to the drive shaft via a second transmission path when a rotational force is input to the input shaft around the second rotational direction, with the rotation reversed around the first rotational direction. The switching mechanism changes the rotation input to the input shaft to different gear ratios in either the first or second transmission path. The shielding device is characterized in that the stopper restricts the rotation of the drive shaft around the second rotation direction which lowers the shielding material by the weight of the shielding material, and releases the restriction on the rotation of the drive shaft around the second rotation direction when the drive shaft has been rotated by a predetermined amount around the first rotation direction.

2. The aforementioned switching mechanism is A clutch is pivotally supported on the input shaft so as to be rotatable integrally with the input shaft and movable in the axial direction of the input shaft, and moves in a first direction in the axial direction when the input shaft is rotated around the first rotation direction, and moves in a second direction opposite to the first direction when the input shaft is rotated around the second rotation direction, A first clutch receiver is pivotally supported on the input shaft so as to be rotatable relative to it, engages with a clutch moved in the first direction, rotates integrally with the clutch, and transmits rotational force to the drive shaft via the first transmission path. The shielding device according to claim 1, further comprising a second clutch receiver that is pivotally supported on the input shaft so as to be rotatable relative to the input shaft, engages with a clutch moved in the second direction, rotates integrally with the clutch, and transmits rotational force to the drive shaft via the second transmission path.

3. The first transmission path transmits the rotation transmitted to the first clutch receiver to the drive shaft without changing speed. The shielding device according to claim 2, characterized in that the second transmission path changes the speed of the rotation transmitted to the second clutch receiver and transmits it to the drive shaft.

4. The shielding device according to claim 3, characterized in that the second transmission path reverses and changes the speed of the rotation transmitted to the second clutch receiver via a plurality of gears and transmits it to the drive shaft.

5. The first clutch receiver has a gear portion that rotates integrally with the first clutch receiver, and an output shaft that rotates integrally with the first clutch receiver and transmits rotational force to the drive shaft. The second clutch receiver has a gear portion that rotates integrally with the second clutch receiver. The second transmission path is The first gear meshes with the gear portion of the first clutch receiver, The second gear meshes with the gear portion of the second clutch receiver, The shielding device according to claim 4, further comprising a relay gear that transmits the rotation of the second gear to the first gear in reverse.

6. The shielding device according to claim 5, characterized in that the rotation transmitted to the second clutch receiver is changed in speed and transmitted to the drive shaft by at least one of the gear ratio between the gear portion of the first clutch receiver and the first gear, or the gear ratio between the gear portion of the second clutch receiver and the second gear.

7. A shielding device for raising and lowering a shielding material, A switching mechanism that switches between a first operating state in which a drive shaft for opening and closing the shielding material to which the rotation is transmitted rotates in one direction at a first rotational speed, and a second operating state in which the drive shaft rotates in the same direction at a second rotational speed different from the first rotational speed, depending on the direction of rotation of the rotation input by a rotational operation on the shielding device, A stopper restricts the rotation of the drive shaft in the reverse direction, which lowers the shielding material due to its own weight, and releases the restriction on the rotation of the drive shaft in the reverse direction when the drive shaft is rotated by a predetermined amount in the one direction that raises the shielding material. A shielding device equipped with the following features.

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