JP6925266B2 - Transmission delay unit, shielding material lifting device - Google Patents

Description

The present invention relates to a transmission delay unit that delays the rotation of the input shaft and transmits it to the output shaft, and a shielding material elevating device that uses the transmission delay unit.

In the horizontal blind, the lifting shaft is rotated by pulling down the lifting operation side of the loop-shaped operation cord mounted on the operation pulley rotatably supported by the head box to raise the bottom rail. By pulling down the lowering operation side of the operation code, the tilt shaft is rotated to tilt the slats, and by disengaging the clutch connected to the elevating shaft, the bottom rail is lowered by its own weight (patented). Document 1). For example, in the second embodiment of Patent Document 1, a guide groove 67 having a shape as shown in FIG. 13 of Patent Document 1 is formed on the cam shaft 14, and the slide ball 20 is moved along the guide groove 67. The elevating shaft is separated by.

The horizontal blind as described above has the advantage that it does not require an operating rod for tilt operation, but the clutch is activated and the elevating shaft is disconnected before the tilt operation is completed, and the bottom is at an unintended timing. The rail may drop by its own weight.

In Patent Document 2, an engagement between a switching cylinder 42 which is connected to the idling cylinder 71 with a predetermined amount of play in the rotational direction and an engagement which is connected to the switching cylinder 42 with a predetermined amount of play in the rotational direction. By using the cylinder 44 to delay and transmit the rotation of the operation pulley, it is possible to prevent the bottom rail from descending by its own weight during the tilt operation of the slats.

Patent No. 3378813 Patent No. 4074420

In the configuration of Patent Document 2, it is possible to prevent the bottom rail from lowering its own weight to some extent during the tilt operation of the slats. However, since the rotation angle required to complete the tilt operation changes depending on the rotation transmission mechanism, the slat width, and the like, the delay angle obtained by the configuration of Patent Document 2 may not be sufficient.

The present invention has been made in view of such circumstances, and provides a means capable of reliably suppressing the bottom rail from lowering its own weight before the completion of the tilt operation.

According to the present invention, the first input shaft, an intermediate rotating body configured to rotate at a rotation speed slower than that of the first input shaft as the first input shaft rotates, and the intermediate rotating body are used. A transmission delay unit comprising a first output shaft to which the rotation of the first input shaft is transmitted, and the intermediate rotating body is configured so as to be unable to rotate relative to the first output shaft after rotating by a predetermined angle. Provided.

By using the transmission delay unit of the present invention, the rotation of the first input shaft can be delayed and transmitted to the output shaft, so that it is possible to suppress the bottom rail from lowering its own weight before the completion of the tilt operation. Further, if the transmission delay is insufficient, the bottom rail may lower its own weight before the tilt operation is completed. However, in the present invention, the rotation of the first input shaft is slower than that of the first input shaft. Since the rotation of the first input shaft is transmitted to the first output shaft via an intermediate rotating body configured to rotate at a speed, it is easy to set the delay amount of rotation transmission to 360 degrees or more. Since the tilt operation is usually completed before the first input shaft rotates 360 degrees, it is possible to more reliably suppress the bottom rail from descending by its own weight before the completion of the tilt operation.

Hereinafter, various embodiments of the present invention will be illustrated. The embodiments shown below can be combined with each other.
Preferably, the outer peripheral surface of the intermediate rotating body is configured to mesh with the outer peripheral surface of the first input shaft.
Preferably, the intermediate rotating body is configured to rotate intermittently with the rotation of the first input shaft.
Preferably, a plurality of the intermediate rotating bodies are provided, and the plurality of intermediate rotating bodies are configured to rotate at the same time as the first input shaft rotates.
Preferably, the inner peripheral surface of the intermediate rotating body is configured to mesh with the outer peripheral surface of the first input shaft.
Preferably, the intermediate rotating body is configured to rotate with the rotation of the first input shaft and revolve around the first input shaft in a direction opposite to the direction of the rotation.
Preferably, the intermediate rotating body is provided with a regulating protrusion, and the regulating protrusion is locked by the first output shaft as the intermediate rotating body rotates, so that the intermediate rotating body is locked with respect to the first output shaft. It is configured so that it cannot rotate relative to each other.

Preferably, it is a shielding material elevating device that rotates the elevating shaft by operating the operation code to elevate the shielding material, and the rotation of the input shaft that rotates with the operation of the operation code is the transmission delay unit and the clutch described above. The clutch unit is configured to be transmitted to the elevating shaft via the unit, and the clutch unit has a second input shaft that rotates with the rotation of the first output shaft and a second output shaft that rotates integrally with the elevating shaft. The clutch unit includes a cam portion that moves the cam shaft in the axial direction with the rotation of the cam shaft that rotates with the rotation of the second input shaft, and the cam shaft with the movement of the cam shaft. Provided is a shielding material elevating device including a clutch portion for switching between a connected state and a second output shaft.

According to another aspect of the present invention, it is a shielding material elevating device configured to rotate the elevating shaft and the tilt shaft by operating the operation code, and the rotation of the input shaft that rotates with the operation of the operation code. Is transmitted to the elevating shaft via the transmission delay unit, and the transmission delay unit delays the rotation of the first input shaft that rotates with the rotation of the input shaft and the rotation of the first input shaft. The transmission gear is provided with a first output shaft that is integrally rotated with the first input shaft, and a tilt shaft gear that is integrally rotated with the tilt shaft and is provided so as to mesh with the transmission gear. Provides a shielding material elevating device that is located on the input side of the transmission delay unit. From this point of view, the transmission delay unit may be any as long as the rotation of the first input shaft is delayed and transmitted to the first output shaft, and it is not essential to include an intermediate rotating body. According to this viewpoint, wear between the transmission gear and the first input shaft can be suppressed.

According to still another aspect of the present invention, the shielding material elevating device that elevates and elevates the shielding material by rotating the elevating shaft by operating the operation code, and the rotation of the input shaft that rotates with the operation of the operation code is The transmission delay unit is configured to be transmitted to the elevating shaft via the transmission delay unit and the clutch unit, and the transmission delay unit has a first input shaft that rotates with the rotation of the input shaft and a rotation of the first input shaft. The clutch unit includes a first output shaft that is delayed and transmitted, and the clutch unit includes a second input shaft that rotates with the rotation of the first output shaft and a second output shaft that rotates integrally with the elevating shaft. The clutch unit includes a cam portion that moves the cam shaft in the axial direction with the rotation of the cam shaft that rotates with the rotation of the second input shaft, and the cam shaft and the second with the cam shaft moving with the movement of the cam shaft. A clutch unit for switching between connected and disconnected states between output shafts is provided, a brake unit is provided between the transmission delay unit and the clutch unit, and the brake unit uses the rotation of the first output shaft as the second input shaft. Provided is a shielding material elevating device configured to transmit and prevent rotation of the second input shaft due to torque generated by the weight of the shielding material. From this point of view, the transmission delay unit may be any as long as the rotation of the first input shaft is delayed and transmitted to the first output shaft, and it is not essential to include an intermediate rotating body. According to this viewpoint, it is possible to prevent the first output shaft of the transmission delay unit from being rotated by the torque generated by the weight of the shielding material.

It is a front view which shows the whole structure of the horizontal blind of 1st Embodiment of this invention. It is a left side view of FIG. It is a perspective view which shows the state which the take-up shaft 9 and the tilter unit 19 are supported by the support member 11. It is an exploded perspective view of FIG. The tilter unit 19 is shown, (a) is a perspective view, and (b) is an exploded perspective view. (A) to (b) are perspective views which show the assembly process of the tilter unit 19. (A) is a cross-sectional view of the central surface in the front-rear direction of FIG. 3, and (b) is a cross-sectional view taken along the line AA in (a). It is sectional drawing corresponding to FIG. 7A which shows another structure of the tilter drum 32. The operation unit 6 is shown, (a) is a perspective view, and (b) is a cross-sectional view of a central surface in the front-rear direction of (a). (A) to (c) show the transmission delay unit 25, (a) is a perspective view, (b) is an exploded perspective view, and (c) is a left side view. (D) is a perspective view of the input shaft 28 of the transmission delay unit 25. The transmission delay unit 25 is shown, (a) is a perspective view, (b) is an exploded perspective view, (c) is a right side view, and (d) is an enlarged view of a region A. (A) is a cross-sectional view showing a fitted state of the input shaft 28 of the transmission delay unit 25 and the transmission gear 24b, and (b) is a cross-sectional view of the input shaft 28 of the transmission delay unit 25 and the planetary carrier 23d of the planetary gear 23b. It is sectional drawing which shows the mating state. It is sectional drawing which shows the fitting state of the 2nd case 30 of the transmission delay unit 25, and the engagement projection 26a1 of the input part 26a of a brake part 26. The transmission delay unit 25 is arranged in the operation unit case 45, (a) is a right side view, and (b) is a perspective view. In each of the figures (a) to (g), the middle stage is a cross-sectional view showing the engagement between the input shaft 28 of the transmission delay unit 25 and the intermediate rotating body 31, and the upper and lower stages are in the rotating grooves 29a and 30a. It is a figure seen from the operation pulley 23a side which shows the position of the regulation protrusion 31b, 31c of. The regulation protrusions 31b and 31c are not originally shown in the cross-sectional view of the middle stage, but are shown for convenience for the sake of understanding. It is a perspective view which shows the operation part case 45 and the clutch unit 27. (A) is a perspective view of the clutch unit 27, (b) is a perspective view of the output shaft 43, (c) is a perspective view of the cam shaft 42, and (d) is a perspective view of the input shaft 41. Yes, (e) is a perspective view of the separate part 46. It is a cross-sectional view corresponding to FIG. 9B which shows the operation part case 45 and the clutch unit 27, (a) is the state which the cam shaft 42 and the output shaft 43 are connected, and (b) is the cam shaft 42 and output. The state in which the shaft 43 is disconnected is shown. (A) to (c) are development views of the outer peripheral surfaces of the cam shaft 42 and the output shaft 43, and are diagrams for explaining the action of the cam shaft 42 and the output shaft 43 being disconnected by the lowering operation. .. (A) to (c) are development views of the outer peripheral surfaces of the cam shaft 42 and the output shaft 43, and are views for explaining the action of connecting the cam shaft 42 and the output shaft 43 by the ascending operation. It is a perspective view which showed only a part of the members in the operation part unit 6. It is a perspective view which showed only a part of the members in the operation part unit 6. It is a perspective view which showed only a part of the members in the operation part unit 6. (A) to (b) are perspective views showing only a part of the members in the operation unit unit 6. It is a perspective view which showed only a part of the members in the operation part unit 6. The transmission delay unit 25 of the second embodiment of the present invention is shown, (a) to (b) are perspective views, and (c) is a perspective view of an intermediate rotating body 55 and an input shaft 56. The transmission delay unit 25 of the third embodiment of the present invention is shown, (a) to (b) are perspective views, (c) is a perspective view in a state where the cover portion 51a of the case 51 is removed, and (d) is an exploded perspective view. It is a figure. It is sectional drawing of the cross section passing through each gear part of the transmission delay unit 25 of FIG. 27. (A) to (d) are cross-sectional views showing the operation of the intermediate rotating body 52 when the input shaft 53 is rotated from the state of FIG. 28. (A) to (c) are cross-sectional views showing the operation of the intermediate rotating body 52 when the input shaft 53 is further rotated from the state of FIG. 29 (d). A fourth embodiment of the present invention in which the transmission delay unit 25 is applied to a roll screen is shown, (a) is a front view, (b) is a right side view, and (c) is a front view of the screen. In (a), the screens 64a and 65a are omitted, and in (b), the operation pulley 23a and the operation code 7 are not shown.

Hereinafter, embodiments of the present invention will be described. The various features shown in the embodiments shown below can be combined with each other. In addition, the invention is independently established for each feature.

1. 1. In the horizontal blind as a shielding device shown in FIGS. 1 and 2, a multi-stage slat 3 as a shielding material is suspended and supported via a plurality of ladder cords 2 hanging from the head box 1. A bottom rail 4 is suspended and supported at the lower end of the ladder cord 2. The ladder cord 2 includes a plurality of weft threads between the pair of warp threads. A slat 3 is supported on each weft. As shown in FIG. 5B, a loop portion 2a is provided on the upper end side of the ladder cord 2, and the loop portion 2a is rotated by the support member 10 or the support member 11 arranged in the head box 1. It is hung on a V-shaped groove 32a provided in a tilter drum 32 that is possibly supported. The V-shaped groove 32a is formed so as to widen outward in the radial direction so as to orbit the outer peripheral surface of the tilter drum 32. The slat 3 is configured to rotate by displacement of the loop portion 2a following the rotation of the tilter drum 32 due to friction between the loop portion 2a and the inner surface 32e of the V-shaped groove 32a. Further, after the slat 3 is rotated until it is in a fully closed state or a reverse fully closed state (a state in which the slat 3 faces the opposite side to the fully closed state and is substantially vertical), the tilter drum 32 is a ladder cord. It is designed to run idle with respect to 2. The ladder code 2 corresponds to the "slat support code" in the claims. The configuration of the "slat support cord" is not limited as long as it can support and rotate the slats 3. For example, the "slat support cord" includes two warp threads separated from each other, and one warp thread is attached to one edge of the slats. It may be configured such that it is attached and the other warp is attached to the other edge of the slats.

An elevating cord 5 also hangs down from the head box 1, and the lower end of the elevating cord 5 is attached to the bottom rail 4. The bottom rail 4 is lifted and lowered by winding and rewinding the lifting cord 5 on the winding shaft 9 rotatably supported by the support member 11 arranged in the head box 1.

A tilter unit 19 having the same configuration is supported on the support members 10 and 11. The support member 10 is configured to support only the tilter unit 19. On the other hand, the support member 11 is configured to support the tilter unit 19 and the take-up shaft 9. Regarding the portion that supports the tilter unit 19, the support member 10 has substantially the same configuration as the support member 11. Hereinafter, the support member 11, the take-up shaft 9, and the tilter unit 19 will be described in detail.

As shown in FIGS. 3 to 4, the support member 11 includes a support member main body 11a and an adapter plate 11b. The support member main body 11a includes a take-up shaft accommodating portion 11e that supports the take-up shaft 9 and a tilter unit accommodating portion 11f that supports the tilter unit 19. The adapter plate 11b includes an elevating cord insertion portion 11c through which the elevating cord 5 is inserted and a ladder cord insertion portion 11d through which the ladder cord 2 is inserted, and is attached to the adapter mounting portion 11g of the support member main body 11a.

As shown in FIGS. 3 to 4, the take-up shaft 9 includes a take-up cone 9a and a cam unit 9b. As disclosed in Japanese Patent Application Laid-Open No. 2014-231696, the cam unit 9b has a take-up cone 9a when the bottom rail 4 collides with an obstacle while its own weight is lowered or the bottom rail 4 reaches the lower limit position. Has a function to stop the rotation of. The cam unit 9b is configured to rotate integrally with the elevating shaft 8 that rotates with the operation of the operation code 7. When the bottom rail 4 is raised, the cam unit 9b is configured with the rotation of the elevating shaft 8. And the take-up cone 9a rotate integrally. On the other hand, when the bottom rail 4 is lowered by its own weight, a tensile force is applied to the elevating cord 5 as the bottom rail 4 is lowered, and the take-up cone 9a is configured to rotate by the torque generated by this pulling force. There is. A speed adjuster 22 is provided on the elevating shaft 8 so that the rotation speed of the elevating shaft 8 when the bottom rail 4 is lowered by its own weight is adjusted so as not to be excessively high.

As shown in FIGS. 5 to 7, the tilter unit 19 includes a tilter drum 32, a support cap 33, a tilter gear 34, and a bearing plate 35. As described above, the loop portion 2a of the ladder cord 2 is hooked on the V-shaped groove 32a of the tilter drum 32. The tilter drum 32 does not rotate with the rotation of the elevating shaft 8. On the other hand, the tilt shaft 17 that rotates with the operation of the operation code 7 is engaged with the insertion hole 34c of the tilter gear 34, so that the tilter gear 34 rotates with the rotation of the tilt shaft 17. .. Then, since the gear portion 32c of the tilter drum 32 meshes with the gear portion 34b of the tilter gear 34, the tilter drum 32 rotates as the tilter gear 34 rotates with the rotation of the tilt shaft 17.

The bearing plate 35 includes a pair of arms 35a having an engaging convex portion 35b, a tilter gear bearing portion 35c, and a tilter drum bearing portion 35d. As shown in FIG. 6A, with the gear portion 32c and the gear portion 34b meshed with each other, the shaft portion 34a of the tilter gear 34 is inserted into the tilter gear bearing portion 35c, and the shaft portion 32b of the tilter drum 32 is inserted into the tilter drum bearing. It is inserted into the portion 35d. At this time, while the pair of arms 35a are elastically deformed so that the distance between the pair of arms 35a is widened, the engaging convex portion 35b gets over the gear base 32d of the tilter drum 32, and the engaging convex portion 35b is engaged with the gear base 32d. , The state shown in FIG. 6 (b) is obtained. In this state, the axial movement of the tilter drum 32 is blocked by the engaging convex portion 35b, and the axial movement of the tilter gear 34 is blocked by the gear base 32d. Therefore, the bearing plate 35, the tilter drum 32, and the tilter gear 34 are integrated. .. Before or after integrating these, and before attaching the support cap 33, the loop portion 2a of the ladder cord 2 is hooked on the V-shaped groove 32a.

The support cap 33 includes a V-shaped protrusion 33a whose width narrows toward the tip, and a pair of side walls 33d having an engaging groove 33b. As shown in FIG. 6B, when the support cap 33 is attached so that the base plate 35e of the bearing plate 35 enters the engaging groove 33b from above the bearing plate 35, the V-shaped protrusion 33a becomes the V-shaped groove 32a. It is arranged so as to extend inward.

By the way, when the bottom rail 4 is located at a position other than the upper limit position, the weight of the slats 3 is applied to the ladder cord 2, so that the ladder cord 2 and the V-shaped groove 32a are frictionally engaged with each other, and the ladder cord 2 rotates the tilter drum 32. On the other hand, when the bottom rail 4 is in the upper limit position, the weight of the slat 3 is not added to the ladder cord 2 because the entire weight of the slat 3 is added to the elevating cord 5. In such a state, if there is no V-shaped protrusion 33a, the loop portion 2a of the ladder cord 2 is lifted from the V-shaped groove 32a, and the tilter drum 32 is not fully closed even though the slats 3 are not fully closed. May run idle with respect to the ladder code 2. However, in the present embodiment, since the V-shaped protrusion 33a functions as a lift suppressing portion that suppresses the lift of the ladder cord 2, the slats 3 are fully closed even when the weight of the slats 3 is not applied to the ladder cord 2. If this is not the case, the tilter drum 32 is prevented from idling with respect to the ladder cord 2. In the present embodiment, the V-shaped protrusion 33a is provided at an angle of about 104 degrees in the circumferential direction. The central angle α (shown in FIG. 7B) in the range in which the V-shaped protrusion 33a is provided is preferably 30 degrees or more, and more preferably 60 or 90 degrees or more. The upper limit of the central angle α is not particularly specified, but is, for example, 180 degrees. By increasing the central angle α, a frictional force sufficient to make the ladder cord 2 follow the rotation of the tilter drum 32 is generated without excessively narrowing the gap S between the V-shaped protrusion 33a and the V-shaped groove 32a. It is possible. The structure of the floating suppressing portion is not limited as long as it can suppress the loop portion 2a of the ladder cord 2 from floating from the V-shaped groove 32a. For example, as shown in FIG. 8, the floating suppressing portion of the V-shaped groove 32a. A locking projection 32f protruding from the inner surface 32e may be provided to hold the loop portion 2a of the ladder cord 2 in the space S1 below the locking projection 32f in the V-shaped groove 32a. Even in this case, the lifting of the loop portion 2a can be suppressed by the same action as when the V-shaped protrusion 33a is provided on the support cap 33.

The bearing plate 35 is provided with positioning projections 35f protruding from the base plate 35e on both sides in the front-rear direction, and the lower surface 33c of the side wall 33d of the support cap 33 comes into contact with the upper surface 35g of the positioning projection 35f, whereby the support cap 33 Is positioned vertically with respect to the bearing plate 35.

With the above configuration, the tilter unit 19 in which the tilter drum 32, the support cap 33, the tilter gear 34, and the bearing plate 35 are integrated can be obtained.

As shown in FIG. 4, the tilter unit 19 can be attached to the support member main body 11a from above the support member main body 11a in a state where the take-up shaft 9 is supported by the support member main body 11a. In this way, after assembling the tilter unit 19 in advance, the tilter unit 19 can be attached to the support member 11 main body a, so that the assemblability is excellent.

An operation unit 6 is provided at a substantially right end of the head box 1. As shown in FIGS. 9 to 25, the operation unit 6 includes a planetary gear / operation pulley unit 23, a tilt transmission unit 24, a transmission delay unit 25, a brake unit 26, and a clutch unit 27. The planetary gear / operation pulley portion 23 includes an operation pulley 23a and a planetary gear 23b. The operation code 7 is mounted on the operation pulley 23a. The operation code 7 is led out of the head box 1 through the code gate 15. The operation pulley 23a includes a support shaft 23a1, and the support shaft 23a1 is rotatably supported by a case cap 23c. When the operation code 7 is operated to rotate the operation pulley 23a, the rotation is transmitted to the input shaft 23e of the planetary gear 23b. In the planetary gear 23b, the rotation of the input shaft 23e is decelerated and transmitted to the planet carrier 23d. The rotation of the planetary carrier 23d is transmitted to the input shaft 28 of the transmission delay unit 25.

The tilt transmission unit 24 includes a gear plate 24a, a transmission gear 24b rotatably supported by the gear plate 24a, and a tilt shaft gear 24c. The transmission gear 24b is configured to rotate integrally with the input shaft 28. The transmission gear 24b is provided on the input side of the transmission delay unit 25. When the transmission gear 24b moves relative to the input shaft 28 in the axial direction, wear is likely to occur between the transmission gear 24b and the input shaft 28, but in the present embodiment, the transmission gear 24b is relative to the input shaft 28. Since it does not move relative to the axial direction, there is no problem of wear due to the relative movement. The tilt shaft gear 24c meshes with the transmission gear 24b and rotates with the rotation of the transmission gear 24b. The rotation of the tilt shaft gear 24c is transmitted to the tilter gear 34 of the tilter unit 19 through the tilt shaft 17, and the slats 3 are rotated.

As shown in FIGS. 10 to 15, the transmission delay unit 25 includes an input shaft 28 and a pair of intermediate rotating bodies 31 rotatably supported by the first and second cases 29 and 30.

The input shaft 28 includes a first shaft portion 28f, a second shaft portion 28g, a third shaft portion 28e, a fourth shaft portion 28i, and a fifth shaft portion 28d in order from the input side. The first shaft portion 28f has a smaller diameter than the second shaft portion 28g. The second shaft portion 28g has a smaller diameter than the third shaft portion 28e. The fourth shaft portion 28i has a smaller diameter than the third shaft portion 28e. The fifth shaft portion 28d has a smaller diameter than the fourth shaft portion 28i. The first shaft portion 28f is bearing by a bearing portion 23e1 provided on the input shaft 23e of the planetary gear 23b. The second shaft portion 28g is provided with an engaging groove 28b. Three engaging grooves 28b are provided at equal intervals in the circumferential direction. As shown in FIG. 12B, an insertion hole 23d1 is provided at the center of rotation of the planet carrier 23d, and an engagement projection 23d2 protruding inward in the radial direction is provided in the insertion hole 23d1. Three engaging projections 23d2 are provided at equal intervals in the circumferential direction, and the input shaft 28 and the planetary carrier 23d rotate integrally when each engaging projection 23d2 is engaged with each engaging groove 28b. Will be done. The third shaft portion 28e is provided with an engaging groove 28c. Three engaging grooves 28c are provided at equal intervals in the circumferential direction. As shown in FIG. 12A, an insertion hole 24b1 is provided at the center of rotation of the transmission gear 24b, and an engagement protrusion 24b2 protruding inward in the radial direction is provided in the insertion hole 24b1. Three engaging projections 24b2 are provided at equal intervals in the circumferential direction, and the input shaft 28 and the transmission gear 24b rotate integrally when each engaging projection 24b2 is engaged with each engaging groove 28c. Will be done. The first case 29 is provided with a bearing portion 29g, and the third shaft portion 28e is bearing by the bearing portion 29g. Two dental protrusions 28a protruding in the radial direction are provided on the outer peripheral surface of the fourth shaft portion 28i at a pitch of 180 degrees. As shown in FIG. 13, the fifth shaft portion 28d is bearing by the bearing surface 30h of the engaging projection 30g protruding inward in the radial direction from the tubular portion 30k of the second case 30.

The first and second cases 29 and 30 function as output shafts of the transmission delay unit 25. The base portion 29b of the first case 29 is provided with a bearing portion 29g and a rotation groove 29a. As shown in FIG. 11D, an engaging protrusion 29h projecting into the rotating groove 29a is provided at the center of the rotating groove 29a in the circumferential direction. Further, a pair of protruding walls 29e and a protruding cylinder 29c protruding from the base 29b are provided on the output side surface of the base 29b. The protruding wall 29e is provided with a snap hole 29f, and the protruding cylinder 29c is provided with an insertion hole 29d. Snap holes 29f are provided at two positions on each protruding wall 29e so as to be separated in the vertical direction.

A rotating groove 30a is provided in the base portion 30b of the second case 30. A pair of protruding walls 30d and protruding rods 30c protruding from the base 30b are provided on the input side surface of the base 30b. A snap protrusion 30e is provided on the outer surface of each protrusion wall 30d. The snap protrusions 30e are provided at two positions separated in the vertical direction. Further, a support shaft 30f protruding from the base portion 30b is provided between the pair of protruding walls 30d. The support shafts 30f are provided at two locations separated in the vertical direction. On the output side surface of the base portion 30b, a protruding piece 30i is provided adjacent to the rotation groove 30a. The protruding pieces 30i are provided in each of the rotating grooves 30a at two positions separated in the direction along the respective rotating grooves 30a. Each protruding piece 30i is provided with an engaging protrusion 30j that protrudes in the direction of the rotating groove 30a. Further, a tubular portion 30k is provided on the output side surface of the base portion 30b, and the tubular portion 30k is provided with an engaging projection 30g protruding inward in the radial direction from the tubular portion 30k. Three engaging protrusions 30g are provided at equal intervals in the circumferential direction. A bearing surface 30h is provided at the tip of each engaging projection 30g. As described above, the fifth shaft portion 28d of the input shaft 28 is bearing by the bearing surface 30h.

The intermediate rotating body 31 is provided with a bearing portion 31d, and the supporting shaft 30f of the second case 30 is supported by the bearing portion 31d so that the intermediate rotating body 31 is rotatably supported by the second case 30. .. On the outer peripheral surface of the intermediate rotating body 31, three dental protrusions 31a protruding in the radial direction are provided at a pitch of 45 degrees. As shown in FIG. 15, the tooth protrusion 28a and the tooth protrusion 31a are arranged so as to mesh with each other, and as the input shaft 28 rotates, the tooth protrusion 28a abuts on the tooth protrusion 31a and the intermediate rotating body 31 rotates. It is supposed to be done. Further, the intermediate rotating body 31 includes regulation protrusions 31b and 31c protruding on both front and rear sides in the axial direction. By inserting the regulating protrusions 31b and 31c into the rotating grooves 29a and 30a of the first and second cases 29 and 30, the intermediate rotating body 31 has the regulating protrusions 31b and 31c in the rotating grooves 29a and 30a. Within a rotatable angle range (about 140 degrees in this embodiment), it is rotatable relative to the first and second cases 29 and 30. The regulating projection 31b is provided with an engaging groove 31e. The regulation protrusion 31c is provided with an engagement protrusion 31f.

In the transmission delay unit 25, the support shaft 30f is inserted through the bearing portion 31d, and the fifth shaft portion 28d of the input shaft 28 is bearing by the bearing surface 30h, and the first shaft portion 28f, the second shaft portion 28g, and the second shaft portion 28g are supported. It can be assembled by inserting the three shaft portions 28e into the bearing portion 29g in this order, inserting the protruding rod 30c into the insertion hole 29d, and engaging the snap protrusion 30e with the snap hole 29f.

Here, the operation of the transmission delay unit 25 will be described with reference to FIG.
First, when the input shaft 28 is rotated in the arrow X direction (direction for raising the bottom rail 4) shown in FIGS. 10 (b) and 11 (b), the tooth protrusion 28a becomes an arrow as shown in FIG. 15 (a). Rotate in the X direction. When the input shaft 28 rotates about half a turn, the dental protrusion 28a meshes with the dental protrusion 31a as shown in FIG. 15B. When the input shaft 28 is further rotated in the arrow X direction in this state, the intermediate rotating body 31 rotates in the arrow Y direction as the input shaft 28 rotates, as shown in FIGS. 15 (c) to 15 (d). The intermediate rotating body 31 also rotates about 60 degrees before the input shaft 28 rotates about 60 degrees to reach the state shown in FIG. 15 (d). At this time, the regulation protrusions 31b and 31c rotate about 60 degrees in the arrow Y direction in the rotation grooves 29a and 30a. While the regulating projections 31b and 31c can rotate in the rotation grooves 29a and 30a, the rotation of the input shaft 28 is not transmitted to the first and second cases 29 and 30, and the input shaft 28 is the first. And it rotates relative to the second cases 29 and 30. In the state shown in FIG. 15D, the meshing of the dental protrusions 28a and 31a is released, so that the rotation of the intermediate rotating body 31 accompanying the rotation of the input shaft 28 is stopped. When the input shaft 28 is further rotated about half a turn, the tooth protrusions 28a and 31a are re-engaged as shown in FIGS. 15 (e) to 15 (f), and the intermediate rotating body 31 rotates as the input shaft 28 rotates. become. Then, after the input shaft 28 and the intermediate rotating body 31 rotate by about 60 degrees, the meshing of the tooth protrusions 28a and 31a is released, and the rotation of the intermediate rotating body 31 accompanying the rotation of the input shaft 28 is stopped. When the input shaft 28 is further rotated about half a turn, it meshes again and the intermediate rotating body 31 rotates as the input shaft 28 rotates. Then, when the input shaft 28 and the intermediate rotating body 31 each rotate about 20 degrees, the regulating projections 31b and 31c reach the ends of the rotating grooves 29a and 30a, and the state shown in FIG. 15 (g) is reached. In this way, the intermediate rotating body 31 is intermittently rotated with the rotation of the input shaft 28.

In the state shown in FIG. 15 (g), the regulation protrusions 31b and 31c cannot rotate in the rotation grooves 29a and 30a. Therefore, when the input shaft 28 is rotated, the rotation is via the intermediate rotating body 31. It is transmitted to the first and second cases 29 and 30, and the first and second cases 29 and 30 rotate integrally with the input shaft 28.

In this way, the first and second cases 29 and 30 start rotating in the arrow X direction with the rotation of the input shaft 28 after the input shaft 28 has rotated about 1.5 times in the arrow X direction. When the input shaft 28 is rotated in the arrow Y direction, the regulating protrusions 31b and 31c move in the rotation grooves 29a and 30a in the arrow X direction from the state shown in FIG. 15 (g), and the input shaft 28 moves in the arrow X direction. When about 1.5 rotations in the direction of the arrow Y, the regulating protrusions 31b and 31c reach the ends of the rotation grooves 29a and 30a, and the first and second cases 29 and 30 move along with the rotation of the input shaft 28 and the arrow Y. Start rotating in the direction.

In the states of FIGS. 15A to 15B, the side surface of the regulation protrusion 31b is locked by the engagement protrusion 30j, so that the rotation of the intermediate rotating body 31 is loosely restricted. In the state of FIG. 15C, the rotation of the intermediate rotating body 31 is loosely restricted by engaging the engaging projection 30j with the engaging groove 31e. In the state of FIGS. 15D to 15E, the intermediate rotating body 31 is locked by the engaging protrusion 31f by the engaging protrusion 29h and the side surface of the regulating protrusion 31b by the engaging protrusion 30j. The rotation of is loosely regulated. In the state of FIG. 15 (f), the rotation of the intermediate rotating body 31 is loosely restricted by engaging the engaging projection 30j with the engaging groove 31e. In the state of FIG. 15 (g), the side surface of the regulating projection 31b is locked by the engaging projection 30j, so that the rotation of the intermediate rotating body 31 is loosely restricted. As described above, in each of the states of FIGS. 15A to 15G, the rotation of the intermediate rotating body 31 is loosely regulated, and the intermediate rotating body 31 rotates due to vibration or the like when the input shaft 28 does not rotate. Movement is suppressed. Therefore, it is possible to prevent the rotation angles of the two intermediate rotating bodies 31 from shifting.

The transmission delay unit 25 is housed in the operation unit case 45 as shown in FIG. The transmission delay unit 25 is rotated in the operation unit case 45 in a state where the outer peripheral surfaces of the base portions 29b and 30b are bearing by the bearing portion 45d of the operation unit case 45. The bearing portions 45d are provided at four locations at equal intervals in the circumferential direction.

The rotations of the first and second cases 29 and 30 are transmitted to the input unit 26a of the brake unit 26. As shown in FIG. 13, the input portion 26a is provided with an engaging projection 26a1. The engaging protrusions 26a1 are provided at three positions at equal intervals in the circumferential direction. Each engaging projection 26a1 is engaged between two adjacent engaging projections 30g. With such a configuration, the input portion 26a of the brake portion 26 rotates integrally with the first and second cases 29 and 30.

In the brake unit 26, the rotation transmitted from the first and second cases 29 and 30 to the input unit 26a is transmitted to the input shaft 41 of the clutch unit 27 via the transmission shaft 26c fitted in the fitting hole of the output unit 26b. To convey to
It is configured to prevent the rotation of the input shaft 41 due to the torque generated by the weight of the shielding material (slat 3 and bottom rail 4). Therefore, by providing the brake portion 26, the bottom rail 4 is prevented from lowering its own weight. By arranging the brake unit 26 between the clutch unit 27 and the transmission delay unit 25, it is possible to prevent the output shaft of the transmission delay unit 25 from being rotated by the torque generated by the weight of the bottom rail 4.

As shown in FIGS. 16 to 20, the clutch unit 27 includes an input shaft 41, a cam shaft 42, and an output shaft 43. The cam shaft 42 and the output shaft 43 are housed in the operation unit case 45 so as to be relatively rotatable. The cam shaft 42 is configured to rotate integrally with the input shaft 41.

A fitting hole 41a is provided at the center of rotation of the input shaft 41. The fitting hole 41a and the transmission shaft 26c have a non-circular cross section (quadrangle), and the input shaft 41 is configured to rotate integrally with the transmission shaft 26c when the transmission shaft 26c is inserted into the fitting hole 41a. .. An engaging projection 41b that protrudes outward in the radial direction is provided on the outer peripheral surface of the input shaft 41. The engaging protrusions 41b are provided at three positions at equal intervals in the circumferential direction.

A fitting hole 42h is provided at the center of rotation of the cam shaft 42. The fitting hole 42h is provided with an engaging groove 42i. Engagement grooves 42i are provided at six locations at equal intervals in the circumferential direction. The cam shaft 42 is configured to rotate integrally with the input shaft 41 by engaging the engaging protrusions 41b with the three engaging grooves 42i. Further, the cam shaft 42 is movable in the axial direction of the input shaft 41.

A bearing portion 41e is provided on the output side of the input shaft 41. A bearing portion 42j is provided on the output side of the cam shaft 42. On the input side of the output shaft 43, a first shaft portion 43e and a second shaft portion 43d are provided in order from the input side. The first shaft portion 43e has a smaller diameter than the second shaft portion 43d. The first shaft portion 43e and the second shaft portion 43d are bearing by the bearing portion 41e and the bearing portion 42j, respectively.

The cam shaft 42 and the output shaft 43 are formed with engaging portions 42k and 43k having a corrugated cross-section. When the cam shaft 42 is located away from the output shaft 43 as shown in FIG. 18 (b), the engaging portions 42k and 43k do not mesh with each other, and the cam shaft 42 and the output shaft 43 are disconnected and rotate relative to each other. do. On the other hand, when the cam shaft 42 is in a position close to the output shaft 43 as shown in FIG. 18A, the engaging portions 42k and 43k are engaged with each other, and the cam shaft 42 and the output shaft 43 are connected and integrally rotate. do. Therefore, the cam shaft 42 and the output shaft 43 form a clutch portion.

A guide groove 42g having a substantially semicircular cross section extending in the circumferential direction of the cam shaft 42 is provided on the outer circumference of the cam shaft 42. The separate part 46 supported by the operation unit case 45 is provided with a slide groove 46a having a substantially semicircular cross section extending in the axial direction, and the ball 44 is sandwiched between the guide groove 42g and the slide groove 46a. .. The ball 44 is movable in the axial direction in the slide groove 46a. Further, the ball 44 moves relative to the cam shaft 42 in the circumferential direction along the guide groove 42 g as the cam shaft 42 rotates. In the following description, for convenience, the relative movement in the circumferential direction may be simply referred to as "movement".

As shown in FIG. 16, the operation unit case (case body) 45 has a cylindrical portion 45a in which the cam shaft 42 and the output shaft 43 are housed, and a pocket portion 45b provided so as to project radially from the cylindrical portion 45a. To be equipped. With the ball 44 sandwiched between the guide groove 42g of the cam shaft 42 and the slide groove 46a of the separate part 46, the output shaft 43, the cam shaft 42, the ball 44 and the separate part 46 are placed in the cylindrical portion 45a and the pocket portion 45b. By accommodating them inside, these members can be arranged in the operation unit case 45. Further, the axial movement of the separate part 46 is restricted by engaging the locking projection 46b of the separate part 46 with the end surface 45c of the pocket portion 45b. In another assembly method, the output shaft 43 is housed in the cylindrical portion 45a, then the separate part 46 is arranged in the pocket portion 45b, and the ball 44 is arranged in the slide groove 46a. The cam shaft 42 can be housed in the cylindrical portion 45a. As shown in FIG. 17, since the cam shaft 42 is provided with an introduction groove 42a extending from the output side of the cam shaft 42 to the guide groove 42g, the cam is inserted into the cylindrical portion 45a when the cam shaft 42 is inserted into the cylindrical portion 45a. The ball 44 can be easily introduced into the guide groove 42g by appropriately rotating the shaft 42 to match the position of the introduction groove 42a with the position of the ball 44. Here, in order to avoid interference between the output shaft 43 and the ball 44, the output shaft 43 is housed in the cylindrical portion 45a before the ball 44 is housed in the slide groove 46a. By reducing the outer diameter of the ball or providing an introduction groove on the output shaft 43, interference between the output shaft 43 and the ball 44 can be avoided. In this case, the output shaft 43 can be housed in the cylindrical portion 45a while the ball 44 is housed in the slide groove 46a.

As shown in FIGS. 19 to 20, the guide groove 42g is composed of the grooves of rows A to C, and the movable range of the ball 44 in the slide groove 46a is the width of two rows of the guide groove 42g. It has become. With the axially movable range of the ball 44 limited, the ball 44 moves along the guide groove 42g as the cam shaft 42 rotates, so that the cam shaft 42 moves in the axial direction. Therefore, the cam portion is composed of the guide groove 42g, the slide groove 46a, and the ball 44.

Here, the operation of the horizontal blind of the present embodiment will be described.

For convenience of explanation, it is assumed that the bottom rail 4 is in the lower limit position as an initial state. In this state, the transmission delay unit 25 is in the state shown in FIG. 15 (g), and the balls 44 of the clutch unit 27 are in rows A or B of the guide grooves 42 g as shown in FIG. 19 (a). Have been placed. In this state, the cam shaft 42 and the output shaft 43 are in a connected state as shown in FIG. 18A, so that both rotate integrally.

When the operation pulley 23a is rotated in the ascending direction of the bottom rail 4 by pulling down the ascending operation side of the operation code 7, the rotation is transmitted to the input shaft 28 of the transmission delay unit 25 via the planetary gear 23b. When the input shaft 28 is rotated in the ascending direction of the bottom rail 4, the transmission gear 24b and the tilt shaft gear 24c that mesh with the transmission gear 24b are rotated. The rotation of the tilt shaft gear 24c is transmitted to the tilter gear 34 via the tilt shaft 17. The rotation of the tilter gear 34 is transmitted to the tilter drum 32. As the tilter drum 32 rotates, the ladder cord 2 mounted on the V-shaped groove 32a of the tilter drum 32 is displaced, and the slats 3 are rotated until the slats 3 are in the reverse fully closed state. After the slat 3 is in the reverse fully closed state, the tilter drum 32 idles with respect to the rudder cord 2.

As the input shaft 28 of the transmission delay unit 25 rotates, the regulating protrusions 31b and 31c move in the rotation grooves 29a and 30a in the direction of arrow X from the state shown in FIG. 15 (g), and the input shaft 28 moves in the direction of arrow Y. When about 1.5 rotations (upward direction of the bottom rail 4), the regulation protrusions 31b and 31c reach the ends of the rotation grooves 29a and 30a, and the first and second cases 29 and 30 rotate the input shaft 28. Along with this, it starts to rotate in the Y direction of the arrow. Therefore, the rotation of the input shaft 28 is delayed by 1.5 rotations and transmitted to the first and second cases 29 and 30.

The rotations of the first and second cases 29 and 30 are transmitted to the input shaft 41 of the clutch unit 27 via the brake unit 26. This rotation is also transmitted to the cam shaft 42. When the cam shaft 42 is rotated in the ascending direction of the bottom rail 4, the ball 44 moves along a reciprocating route between the rows A and B of the guide grooves 42 g, as shown in FIG. 19 (a). .. Specifically, when the ball 44 reaches the cam protrusion a1 while moving in the row A, the cam protrusion a1 guides the ball 44 in the row B direction. When the ball 44 reaches the cam island a2 while moving in the row B, the cam island a2 guides the ball 44 in the row A direction. In this way, the ball 44 is guided and moved by the cam protrusion a1 and the cam island a2 so as to reciprocate between the row A and the row B. On the outer peripheral surface of the cam shaft 42, cam protrusions a1 and cam islands a2 are provided at four locations at equal intervals in the circumferential direction. The cam island a2 is provided so that a row B is formed between the cam protrusion a1 and the cam island a2. When the ball 44 is in the A row, the ball 44 is located on the right side in the slide groove 46a, and when the ball 44 moves to the B row, the ball 44 moves to the left side in the slide groove 46a. Therefore, the camshaft 42 does not move axially while the ball 44 is moving along the reciprocating route between rows A and B.

In this state, since the cam shaft 42 and the output shaft 43 are connected to each other, the rotation of the cam shaft 42 is transmitted in the order of the output shaft 43, the elevating shaft 8, and the take-up shaft 9. Therefore, the bottom rail 4 is raised by pulling down the ascending operation side of the operation code 7.

As described above, in the present embodiment, the rotation of the input shaft 28 is immediately transmitted to the tilt shaft 17, but is transmitted to the elevating shaft 8 after being delayed by the transmission delay unit 25. Therefore, it is suppressed that the bottom rail 4 starts to rise during the rotation of the slats 3.

When the bottom rail 4 rises to the upper limit position, when the operation code 7 is released, the torque generated by the weight of the bottom rail 4 is the take-up shaft 9, the elevating shaft 8, the output shaft 43, the cam shaft 42, and the input shaft 41. The input shaft 41 tries to rotate in the downward direction, but the rotation is stopped by the brake unit 26, so that the input shaft 41 does not rotate and the cam shaft 42 does not rotate either. At this time, the ball 44 is arranged somewhere in the row A or B. Here, the description will proceed on the assumption that the rotation of the cam shaft 42 is stopped with the ball 44 arranged at the position shown in FIG. 19B.

From this state, when the lowering operation side of the operation code 7 is pulled down and the operation pulley 23a is rotated in the lowering direction of the bottom rail 4, the rotation causes the input shaft 28, the transmission gear 24b, the tilt shaft gear 24c, the tilt shaft 17, and the like. It is transmitted to the tilter drum 32 via the tilter gear 34. When the bottom rail 4 is in the upper limit position, the weight of all the slats 3 is added to the elevating cord 5, so that the weight of the slats 3 is not added to the ladder cord 2. Therefore, in the prior art, the loop portion 2a of the ladder cord 2 in the tilter drum 32 is lifted, and the tilter drum 32 idles with respect to the ladder cord 2 even though the slats 3 are not fully closed. Therefore, the slat 3 is not rotated. Therefore, in the prior art, when the bottom rail 4 is in the upper limit position, the bottom rail 4 may be lowered by its own weight without the slat 3 being fully closed. On the other hand, when the bottom rail 4 is at a position lower than the upper limit position, the bottom rail 4 is lowered by its own weight with the slats 3 fully closed. The fact that the bottom rail 4 is lowered by its own weight with the slats 3 open only when the bottom rail 4 is in the upper limit position is a problem in that the usability is deteriorated. In the present embodiment, the ladder cord 2 is prevented from rising by arranging the V-shaped protrusion 33a provided on the support cap 33 so as to extend into the V-shaped groove 32a. Therefore, in the present embodiment, the tilter drum 32 does not idle when the slat 3 is not fully closed, and when the operation pulley 23a is rotated in the downward direction of the bottom rail 4, the slat 3 is fully closed. It is rotated until it becomes. On the other hand, after the slats 3 are fully closed, the tilter drum 32 idles with respect to the ladder cord 2.

As the input shaft 28 of the transmission delay unit 25 rotates, the regulating protrusions 31b and 31c move in the rotation grooves 29a and 30a in the arrow Y direction from the state shown in FIG. 15A, and the input shaft 28 moves in the arrow X direction. When about 1.5 rotations (downward direction of the bottom rail 4), the regulation protrusions 31b and 31c reach the ends of the rotation grooves 29a and 30a, and the first and second cases 29 and 30 rotate the input shaft 28. Along with this, it starts to rotate in the direction of arrow X. Therefore, the rotation of the input shaft 28 is delayed by 1.5 rotations and transmitted to the first and second cases 29 and 30.

The rotations of the first and second cases 29 and 30 are transmitted to the input shaft 41 of the clutch unit 27 via the brake unit 26. This rotation is also transmitted to the cam shaft 42. When the cam shaft 42 is rotated in the downward direction of the bottom rail 4, the balls 44 move in the order of row A → row B → row C of the guide grooves 42 g, as shown in FIGS. 19 (b) to 19 (c). .. Specifically, when the ball 44 reaches the cam protrusion a1 while moving in the row A, the cam protrusion a1 guides the ball 44 in the row B direction. When the ball 44 reaches the cam island a2 while moving in the row B, the cam island a2 guides the ball 44 in the row C direction. In this way, the ball 44 is guided and moved in the order of row A → row B → row C by the cam protrusion a1 and the cam island a2. When the ball 44 moves from row B to row C, a leftward force is applied to the ball 44 and a rightward force is applied to the camshaft 42. Since the ball 44 cannot move further to the left in the slide groove 46a, the cam shaft 42 moves to the right (that is, the direction of separation from the output shaft 43) when the ball 44 moves from row B to row C. ). As a result, the cam shaft 42 and the output shaft 43 are not connected to each other, the elevating shaft 8 freely rotates, and the bottom rail 4 descends by its own weight. As shown in FIG. 19B, a tapered surface 42k1 is provided at the tip of the convex portion of the engaging portion 42k. The tapered surface 42k1 is such that when the cam shaft 42 is rotated in the downward direction, the tapered surface 42k1 comes into contact with the convex portion of the engaging portion 43k of the output shaft 43 and the output shaft is brought into contact with the cam shaft 42. It is provided so that a force in the separation direction from 43 is applied. By providing such a tapered surface 42k1, the cam shaft 42 can be easily separated from the output shaft 43.

In the present embodiment, since the distance between the two adjacent cam protrusions a1 and the distance between the two adjacent cam islands a2 are short, the position of the ball 44 in the row A or the row B at the start of the lowering operation is short. Even if there is, the idling angle is relatively small from the start of the descent operation to the start of the self-weight descent of the bottom rail 4. Specifically, in the present embodiment, since the cam protrusions a1 and the cam islands a2 are each provided at a pitch of 90 degrees, the maximum idling angle is less than 180 degrees. The maximum value of this idling angle can be further reduced by increasing the number of cam protrusions a1 and cam islands a2 (that is, providing five or more).

As described above, in the present embodiment, the rotation of the input shaft 28 is immediately transmitted to the tilt shaft 17, but is transmitted to the elevating shaft 8 after being delayed by the transmission delay unit 25. Therefore, it is suppressed that the bottom rail 4 starts lowering by its own weight during the rotation of the slats 3.

When the lowering operation side of the operation code 7 is further pulled down and the camshaft 42 is further rotated in the lowering direction of the bottom rail 4 during the lowering of the own weight of the bottom rail 4 or after the lowering of the own weight is completed, as shown in FIG. , The ball 44 moves along a reciprocating route between rows B and C of the guide groove 42 g. Specifically, when the ball 44 reaches the cam protrusion a3 while moving in the row C, the cam protrusion a3 guides the ball 44 in the row B direction. When the ball 44 reaches the cam island a2 while moving in the row B, the cam island a2 guides the ball 44 in the row C direction. In this way, the ball 44 is guided and moved by the cam protrusion a3 and the cam island a2 so as to reciprocate between the row C and the row B. Cam protrusions a3 are provided on the outer peripheral surface of the cam shaft 42 at four locations at equal intervals in the circumferential direction. The cam island a2 is provided so that a row B is formed between the cam protrusion a3 and the cam island a2. When the ball 44 is in the B row, the ball 44 is located on the right side in the slide groove 46a, and when the ball 44 moves to the C row, the ball 44 moves to the left side in the slide groove 46a. Therefore, the camshaft 42 does not move axially while the ball 44 is moving along the reciprocating route between rows B and C.

When the ascending operation side of the operation code 7 is pulled down to rotate the operation pulley 23a in the ascending direction of the bottom rail 4, the rotation is delayed by the transmission delay unit 25. It is transmitted to the input shaft 41 and the cam shaft 42 of the clutch unit 27. When the cam shaft 42 is rotated in the ascending direction of the bottom rail 4, the balls 44 move in the order of row C → row B → row A of the guide grooves 42 g, as shown in FIGS. .. Specifically, when the ball 44 reaches the cam protrusion a3 while moving in the row C, the cam protrusion a3 guides the ball 44 in the row B direction. When the ball 44 reaches the cam island a2 while moving in the row B, the cam island a2 guides the ball 44 in the direction of the row A. In this way, the ball 44 is guided and moved in the order of row C → row B → row A by the cam protrusion a3 and the cam island a2. When the ball 44 moves from row B to row A, a rightward force is applied to the ball 44 and a leftward force is applied to the camshaft 42. Since the ball 44 cannot move further to the right in the slide groove 46a, the cam shaft 42 moves to the left (that is, the connecting direction to the output shaft 43) when the ball 44 moves from row B to row A. ). As a result, the cam shaft 42 and the output shaft 43 are connected to each other, the rotation of the cam shaft 42 is transmitted to the elevating shaft 8, and the bottom rail 4 is raised.

The present invention can also be implemented in the following aspects.
-In the above embodiment, a lift suppressing portion for suppressing the lift of the ladder code 2 is provided, but the lift suppressing portion is not essential.
In the above embodiment, the slat 3 is tilted by using the tilter drum 32 having the V-shaped groove 32a, but the mechanism for tilting the slat 3 is not particularly limited, and for example, it is disclosed in FIG. 2 of Japanese Patent Application Laid-Open No. 2014-231696. A mechanism using a tilt spring as described above may be used.
In the above embodiment, the rotation of the input shaft 28 is transmitted to the first and second cases 29 and 30 by using the two intermediate rotating bodies 31 in order to disperse the load applied to the intermediate rotating body 31, but the intermediate rotating body 31 is used. The number of rotating bodies 31 may be one or three or more.
In the above embodiment, in order to disperse the load applied to the intermediate rotating body 31, regulating protrusions 31b and 31c are provided on both sides of each intermediate rotating body 31 in the axial direction, and the regulating protrusions 31b and 31c are first and second. Although engaged with the cases 29 and 30, the regulating protrusion may be provided on only one of the axial directions of each intermediate rotating body 31.
The direction in which the regulation protrusions 31b and 31c protrude is not particularly limited, and the regulation protrusions 31b and 31c may be provided so as to protrude in the radial direction.
The delay amount can be adjusted by appropriately changing the number and pitch of the tooth protrusions 28a and 31a and the angle range in which the regulation protrusions 31b and 31c can rotate in the rotation grooves 29a and 30a. The delay amount is preferably 360 degrees or more, more preferably 400, 450, or 500 degrees or more.
-Instead of the tooth protrusions 28a and 31a, gears that mesh with each other may be provided on the input shaft 28 and the intermediate rotating body 31. In this case, the rotation speed of the intermediate rotating body 31 can be made smaller than that of the input shaft 28 by increasing the number of teeth of the gear of the intermediate rotating body 31 to be larger than the number of teeth of the gear of the input shaft 28. However, in this case, in order to slow down the rotation speed of the intermediate rotating body 31 to the same degree as in the above embodiment, it is necessary to make the number of gear teeth of the intermediate rotating body 31 three times the number of gear teeth of the input shaft 28. Therefore, the diameter of the gear of the intermediate rotating body 31 is also three times the diameter of the gear of the input shaft 28. On the other hand, in the above embodiment, the intermediate rotating body 31 is intermittently rotated by making the pitch of the tooth protrusion 31a of the intermediate rotating body 31 smaller than the pitch of the tooth protrusion 28a of the input shaft 28. Since the rotation speed is reduced, the diameter of the intermediate rotating body 31 can be made relatively small. In the specification of the present application, the rotation speed of the intermediate rotating body 31 is defined by (the rotation angle of the intermediate rotating body 31 for each rotation of the input shaft 28) / (the time required for the input shaft 28 to make one rotation). Will be done. Therefore, when the intermediate rotating body 31 is rotated intermittently, the time while the intermediate rotating body 31 is stopped is also included in the time for calculating the rotation speed.
-The transmission delay unit 25 can be used for any application that requires a delay in transmission of rotation, in addition to the applications other than those in the above embodiment.
In the above embodiment, the clutch unit 27 is connected / separated by engaging / disengaging the two members (cam shaft 42 and output shaft 43) by moving relative to each other in the axial direction. Although the form is used, if the input rotation to the clutch unit is within a predetermined rotation angle and the input shaft can be connected / separated to the output shaft, the two members may be engaged / disengaged in the radial direction. ..

2. Second Embodiment The second embodiment of the present invention will be described with reference to FIG. 26. This embodiment is similar to the first embodiment, and the main difference is the difference in the configuration of the transmission delay unit 25. Hereinafter, the differences will be mainly described.

In the present embodiment, the transmission delay unit 25 includes a case 54, an intermediate rotating body 55, and an input shaft 56. The case 54 functions as an output shaft. The intermediate rotating body 55 includes a shaft portion 55c rotatably supported by the case 54, an annular portion 55d, an inner peripheral gear portion 55a provided on the inner peripheral surface of the annular portion 55d, and an annular portion 55d in the axial direction. It is provided with a regulating protrusion 55b provided so as to protrude. The shaft portion 55c and the annular portion 55d are connected via the base portion 55e. The input shaft 56 includes a shaft portion 56a rotatably supported by the case 54 and a gear portion 56b provided so as to mesh with the inner peripheral gear portion 55a. The regulation protrusion 55b is inserted into the rotation groove 54a provided in the case 54. With such a configuration, the intermediate rotating body 55 can rotate relative to the case 54 within an angle range (about 270 degrees in the present embodiment) in which the regulation protrusion 55b can rotate in the rotating groove 54a. ing. Since the gear ratio of the inner peripheral gear portion 55a / gear portion 56b is 3, the regulation protrusion 55b rotates 120 degrees each time the gear portion 56b makes one revolution with the rotation of the input shaft 56, and the gear portion 56b When it rotates a little twice, the regulation protrusion 55b reaches the end of the rotation groove 54a. While the regulating protrusion 55b can rotate in the rotating groove 54a, the input shaft 56 rotates relative to the case 54, and when the regulating protrusion 55b reaches the end of the rotating groove 54a, the input shaft 56 rotates. It is transmitted to the case 54 via the intermediate rotating body 55, and the input shaft 56 rotates integrally with the case 54. As described above, also in this embodiment, the rotation of the input shaft 56 is delayed and transmitted to the output shaft (case 54).

3. 3. Third Embodiment The third embodiment of the present invention will be described with reference to FIGS. 27 to 30. This embodiment is similar to the first embodiment, and the main difference is the difference in the configuration of the transmission delay unit 25. Hereinafter, the differences will be mainly described.

In the present embodiment, the transmission delay unit 25 includes a case 51, an intermediate rotating body 52, and an input shaft 53. The case 51 functions as an output shaft. The case 51 includes a base portion 51c, a cover portion 51a, an annular portion 51h, and a locking portion 51d. The base portion 51c is provided with a rotation groove 51f and an insertion hole 51g. An inner peripheral gear portion 51e is provided on the inner peripheral surface of the annular portion 51h. The intermediate rotating body 52 includes a shaft portion 52a rotatably supported by the rotation groove 51f, an annular portion 52e, an inner peripheral gear portion 52d provided on the inner peripheral surface of the annular portion 52e, and an outer circumference of the annular portion 52e. It includes an outer peripheral gear portion 52b provided on the surface and a regulation protrusion 52c provided so as to project radially from the annular portion 55d. The shaft portion 52a and the annular portion 52e are connected via the base portion 52f. The input shaft 53 includes a shaft portion 53a that is inserted through the insertion hole 51g and is rotatably supported, and a gear portion 53b that is provided so as to mesh with the inner peripheral gear portion 52d.

28 to 30 show a cross-sectional view of the cross section passing through each gear portion as viewed from the cover portion 51a side. Originally, the regulation protrusion 52c does not appear in each cross-sectional view, but the regulation protrusion 52c is displayed in each drawing for convenience in order to show the positional relationship between the regulation protrusion 52c and the locking portion 51d.

As shown in FIG. 28, when the input shaft 53 is rotated counterclockwise, the intermediate rotating body 52 also rotates counterclockwise due to the engagement between the gear portion 53b and the inner peripheral gear portion 52d. At the same time, the shaft portion 52a of the intermediate rotating body 52 revolves clockwise around the input shaft 53 along the rotation groove 51f due to the engagement between the outer peripheral gear portion 52b and the inner peripheral gear portion 51e. That is, the intermediate rotating body 52 is configured to revolve clockwise while rotating counterclockwise.

As the input shaft 53 rotates, the intermediate rotating body 52 follows the trajectories shown in FIGS. 29 (a) to 29 (d) and 30 (a) to 30 (b), as shown in FIG. 30 (c). , The regulation protrusion 52c is rotated to a position where it is locked by the locking portion 51d.

While the regulating protrusion 52c is not locked by the locking portion 51d, the input shaft 53 rotates relative to the case 51, and when the regulating protrusion 52c reaches the locking portion 51d, the rotation of the input shaft 53 rotates in the middle. It is transmitted to the case 51 via the body 52, and the input shaft 53 rotates integrally with the case 51. As described above, also in this embodiment, the rotation of the input shaft 53 is delayed and transmitted to the output shaft (case 51).

The number of rotations of the input shaft 53 from the state of FIG. 28 to the state of FIG. 30 (c) is about 4.5 times in this embodiment, but the number of teeth of the gear and the shape of the regulation protrusion 52c or the locking portion 51d. The number of rotations can be changed as appropriate by changing the position and the position.

4. Fourth Embodiment In the fourth embodiment of the present invention, an example in which the transmission delay unit 25 is applied to a roll screen is shown with reference to FIG. 31. In this roll screen, the drive gear 61 and the transmission gear 62 are meshed with each other, and the transmission gear 62 and the driven gear 63 are meshed with each other. The transmission gear 62 and the driven gear 63 have support shafts 62a and 63a, respectively, and the support shafts 62a and 63a are rotatably supported by support frames (not shown), respectively. The drive gear 61 has an engaging shaft 61a, and the engaging shaft 61a is engaged with the operating pulley 23a. According to such a configuration, the drive gear 61, the transmission gear 62, and the driven gear 63 rotate with the rotation of the operation pulley 23a. A transmission delay unit 25 is provided between the drive gear 61 and the take-up shaft 64. Therefore, the rotation of the drive gear 61 is delayed and transmitted to the take-up shaft 64. The upper end of the screen 64a is attached to the take-up shaft 64. A weight bar 64b is attached to the lower end of the screen 64a. Since the transmission delay unit is not provided between the driven gear 63 and the take-up shaft 65, the rotation of the driven gear 63 is transmitted to the take-up shaft 65 without delay. The upper end of the screen 65a is attached to the take-up shaft 65. A weight bar 65b is attached to the lower end of the screen 65a.

When the operation cord 7 mounted on the operation pulley 23a is operated to rotate the operation pulley 23a in the winding direction of the screens 64a and 65a, the rotation of the operation pulley 23a is transmitted to the winding shaft 65 without delay. NS. On the other hand, the rotation of the operation pulley 23a is delayed by the transmission delay unit 25 and transmitted to the take-up shaft 64. Therefore, the screens 64a and 65a are wound around the take-up shafts 64 and 65 with the screen 65a displaced upward from the screen 64a.

After winding the screens 64a and 65a until the lower ends of the screens 64a and 65a reach a desired position, the operation cord 7 is operated to rotate the operation pulley 23a in the rewinding direction of the screens 64a and 65a. The rotation of 23a is transmitted to the take-up shaft 65 without delay. On the other hand, the rotation of the operation pulley 23a is delayed by the transmission delay unit 25 and transmitted to the take-up shaft 64. Therefore, while the transmission of rotation is delayed, only the screen 65a is rewound, and the vertical deviation of the screens 64a and 65a becomes small. In this way, by using the transmission delay unit 25, the relative positions of the two screens 64a and 65a in the vertical direction can be changed. For example, when screens 64a and 65a are provided with alternating light-shielding portions 66 and light-transmitting portions 67 as shown in FIG. 31 (c), the relative positions of the screens 64a and 65a in the vertical direction are set. By changing the screen, the amount of light transmitted through the two screens 64a and 65a can be easily changed.

1: Head box, 2: Ladder cord, 3: Slat, 4: Bottom rail, 5: Lifting cord, 6: Operation unit, 7: Operation cord, 8: Lifting shaft, 9: Winding shaft, 10, 11: Support member, 15: cord gate, 17: tilt shaft, 19: tilter unit, 22: speed adjuster, 23: planetary gear / operation pulley, 24: tilt transmission, 25: transmission delay unit, 26: brake , 27: Clutch unit, 28: Input shaft, 29, 30: 1st and 2nd cases, 31: Intermediate rotating body, 32: Chiller drum, 32a: V-shaped groove, 33: Support cap, 33a: V-shaped protrusion, 34 : Clutch gear, 35: Bearing plate, 41: Input shaft, 42: Cam shaft, 43: Output shaft, 44: Ball, 45: Operation part case, 46: Separate parts, 51: Case, 52: Intermediate rotating body, 53 : Input shaft, 54: Case, 55: Intermediate rotating body, 56: Input shaft

Claims (5)

Comprising a first input shaft, and between the middle rotary member, the first output shaft to which the rotation of the first input shaft through said intermediate rotary member is transmitted,
The intermediate rotating body is provided with a first protrusion protruding in the radial direction on the outer peripheral surface thereof and a regulating protrusion protruding in the axial direction, and the first input shaft is provided with a second protrusion protruding in the radial direction on the outer peripheral surface thereof. It has a protrusion and
The intermediate rotating body is configured so as to be unable to rotate relative to the first output shaft by locking the regulation protrusion with the first output shaft after rotating by a predetermined angle.
The intermediate rotating body intermittently rotates at a rotation speed slower than that of the first input shaft as the first input shaft rotates by repeating a state in which the first protrusion meshes with the second protrusion and a state in which the first protrusion does not mesh with the second protrusion. configured Ru, transmission delay unit so as to rotate. A plurality of the intermediate rotating bodies are provided,
The transmission delay unit according to claim 1, wherein a plurality of the intermediate rotating bodies are configured to rotate at the same time as the first input shaft rotates. It is a shielding material lifting device that raises and lowers the shielding material by rotating the lifting shaft by operating the operation code.
The rotation of the input shaft that rotates with the operation of the operation code is transmitted to the elevating shaft via the transmission delay unit and the clutch unit according to claim 1 or 2.
The clutch unit includes a second input shaft that rotates with the rotation of the first output shaft, and a second output shaft that rotates integrally with the elevating shaft.
The clutch unit includes a cam portion that moves the cam shaft in the axial direction with the rotation of the cam shaft that rotates with the rotation of the second input shaft, and the cam shaft and the second one with the movement of the cam shaft. A shield material elevating device equipped with a clutch unit that switches between connected and disconnected states between two output shafts. A shielding material elevating device configured to rotate an elevating shaft and a tilt shaft by operating an operation code, comprising the transmission delay unit according to claim 1 or 2.
Is configured so that the rotation of the input shaft which rotates with the operation of the operation code is transferred to the elevator shaft through the transmission delay unit,
A transmission gear that rotates integrally with the first input shaft and a tilt shaft gear that rotates integrally with the tilt shaft and is provided so as to mesh with the transmission gear are further provided, and the transmission gear is located on the input side of the transmission delay unit. Shielding material lifting device to be placed. A shielding material elevating device for raising and lowering a shielding material by rotating an elevating shaft by operating an operation code, comprising the transmission delay unit according to claim 1 or 2.
Is configured so that the rotation of the input shaft which rotates with the operation of the operation code is transferred to the elevator shaft through the transmission delay unit and the clutch unit,
Before SL clutch unit comprises a second input shaft which rotates with the rotation of the first output shaft, a second output shaft that rotates integrally with the elevating shaft,
The clutch unit includes a cam portion that moves the cam shaft in the axial direction with the rotation of the cam shaft that rotates with the rotation of the second input shaft, and the cam shaft and the second one with the movement of the cam shaft. Equipped with a clutch that switches between connected and disconnected states between the two output shafts
A brake unit is provided between the transmission delay unit and the clutch unit.
The brake unit is configured to transmit the rotation of the first output shaft to the second input shaft and prevent the rotation of the second input shaft due to the torque generated by the weight of the shielding material. ..

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