WO2016186064A1 - Transmission delay unit and shielding material raising/lowering device - Google Patents

Abstract

Provided is a means for reliably preventing a bottom rail from descending due to its own weight prior to the completion of a tilting operation. The present invention provides a transmission delay unit (25) equipped with a first input shaft (28), intermediate rotating bodies (31) configured so as to rotate at a slower rotational speed than that of the first input shaft in conjunction with rotation of the first input shaft, and a first output shaft (29, 30) to which the rotation of the first input shaft is transmitted via the intermediate rotating bodies. The intermediate rotating bodies are configured so as to be incapable of rotating relative to the first output shaft after rotating by a prescribed angle.

Description

Transmission delay unit, shielding material lifting device

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

In the horizontal blind, the lifting operation of the bottom rail is performed by rotating the lifting shaft by lowering the ascending operation side of the loop-shaped operation cord hung on the operation pulley rotatably supported by the head box, There is one configured to rotate the tilt shaft by lowering the lowering operation side of the operation cord to perform the tilt operation of the slats and to lower the bottom rail by releasing the clutch connected to the lifting shaft (patent) Reference 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 in the cam shaft 14, and the slide ball 20 is moved along the guide groove 67. Thus, the lifting shaft is separated.

The horizontal blind as described above has the advantage of not requiring an operating rod for tilting operation, while the clutch is activated before the tilting operation is completed and the lifting shaft is disconnected, and the bottom blind is moved at an unintended timing. The rail may fall by its own weight.

In Patent Document 2, the switching cylinder 42 connected to the idle cylinder 71 with a predetermined amount of play in the rotational direction, and the engagement connected to the switching cylinder 42 with a predetermined amount of play in the rotational direction. The cylinder 44 is used to delay and transmit the rotation of the operation pulley, thereby suppressing the bottom rail from falling by its own weight during the slat tilting operation.

Japanese Patent No. 3378813 Japanese Patent No. 4074420

In the configuration of Patent Document 2, it is possible to prevent the bottom rail from falling by its own weight to some extent during the slat tilting operation. However, since the rotation angle required until the completion of 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 be insufficient.

The present invention has been made in view of such circumstances, and provides means for reliably suppressing the bottom rail from falling by its own weight before the completion of the tilting operation.

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

If the transmission delay unit of the present invention is used, the rotation of the first input shaft can be delayed and transmitted to the output shaft, so that the bottom rail can be prevented from falling by its own weight before the tilt operation is completed. In addition, when the transmission delay is insufficient, the bottom rail may fall by its own weight before the completion of the tilting operation. In the present invention, however, 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 the intermediate rotator configured to rotate at a speed, it is easy to set the rotation transmission delay amount to 360 degrees or more. Since the tilt operation is normally completed before the first input shaft rotates 360 degrees, it is possible to more reliably suppress the bottom rail from falling by its own weight before the tilt operation is completed.

Hereinafter, various embodiments of the present invention will be exemplified. The following embodiments 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 rotators are provided, and the plurality of intermediate rotators are configured to rotate simultaneously with the rotation of the first input shaft.
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 to revolve around the first input shaft in a direction opposite to the direction of the rotation.
Preferably, the intermediate rotator includes a restriction protrusion, and the intermediate protrusion is locked to the first output shaft as the restriction protrusion is locked by the first output shaft as the intermediate rotator rotates. So that the relative rotation is impossible.

Preferably, the shielding member lifting / lowering device is configured to rotate the lifting shaft by operating the operation code to raise and lower the shielding material, and the rotation of the input shaft that rotates in accordance with the operation of the operation code is the transmission delay unit and the clutch described above The clutch unit includes a second input shaft that rotates as the first output shaft rotates, and a second output shaft that rotates integrally with the lift shaft. The clutch unit includes: a cam portion that moves the cam shaft in an axial direction thereof as the cam shaft rotates as the second input shaft rotates; and the cam shaft that moves as the cam shaft moves. A shielding material elevating device is provided that includes a clutch portion that switches between a connected state and a non-connected state between the first output shaft and the second output shaft.

According to another aspect of the present invention, there is provided a shielding material lifting / lowering device configured to rotate a lift shaft and a tilt shaft by operation of an operation code, and rotation of an input shaft that rotates in accordance with the operation of the operation code Is transmitted to the elevating shaft via a transmission delay unit, and the transmission delay unit is configured to delay the rotation of the first input shaft and the first input shaft rotating with the rotation of the input shaft. A transmission gear that rotates integrally with the first input shaft, and a tilt shaft gear that rotates integrally with the tilt shaft and meshes with the transmission gear. Is provided with a shield lifting / lowering device disposed on the input side of the transmission delay unit. In this aspect, the transmission delay unit may be any unit 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 aspect, wear between the transmission gear and the first input shaft can be suppressed.

According to still another aspect of the present invention, there is provided a shielding material lifting / lowering device that lifts and lowers a shielding material by rotating a lifting shaft by operation of an operation code, wherein an input shaft that rotates in accordance with the operation of the operation code rotates. The transmission delay unit is configured to be transmitted to the elevating shaft via a transmission delay unit and a clutch unit, and the transmission delay unit includes a first input shaft that rotates as the input shaft rotates, and a rotation of the first input shaft. A first output shaft that is transmitted with a delay; and the clutch unit includes a second input shaft that rotates as the first output shaft rotates, 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 as the cam shaft rotates as the second input shaft rotates, and the cam shaft and the second shaft that move as the cam shaft moves. Connection between output shafts A clutch unit that switches a coupling state, and a brake unit that is provided between the transmission delay unit and the clutch unit, wherein the brake unit transmits rotation of the first output shaft to the second input shaft; A shielding material lifting / lowering device configured to prevent rotation of the second input shaft due to torque generated by its own weight is provided. In this aspect, the transmission delay unit may be any unit 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 aspect, 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 view of FIG. FIG. 3 is a perspective view showing a state in which a winding shaft 9 and a tilter unit 19 are supported by a support member 11. FIG. 4 is an exploded perspective view of FIG. 3. The tilter unit 19 is shown, (a) is a perspective view, (b) is an exploded perspective view. (A)-(b) is a perspective view which shows the assembly process of the tilter unit 19. FIG. (A) is a cross-sectional view of the central plane in the front-rear direction of FIG. FIG. 8 is a cross-sectional view corresponding to FIG. 7A, showing another configuration of the tilter drum 32. The operation part unit 6 is shown, (a) is a perspective view, (b) is sectional drawing of the center surface of the front-back direction of (a). (A)-(c) shows the transmission delay unit 25, (a) is a perspective view, (b) is an exploded perspective view, and (c) is a left side view. FIG. 4D 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. FIG. (A) is sectional drawing which shows the fitting state of the input shaft 28 of the transmission delay unit 25, and the transmission gear 24b, (b) is the input shaft 28 of the transmission delay unit 25, and the planet carrier 23d of the planetary gear 23b. It is sectional drawing which shows a fitting state. 4 is a cross-sectional view showing a fitting state between the second case 30 of the transmission delay unit 25 and the engagement protrusion 26a1 of the input portion 26a of the brake portion 26. FIG. The state in which the transmission delay unit 25 is arrange | positioned in the operation part case 45 is shown, (a) is a right view, (b) is a perspective view. In each of the drawings (a) to (g), the middle stage is a cross-sectional view showing the meshing between the input shaft 28 of the transmission delay unit 25 and the intermediate rotating body 31, and the upper stage and the lower stage are within the rotation grooves 29a and 30a. It is the figure seen from the operation pulley 23a side which shows the position of the control protrusions 31b and 31c. Although the regulation protrusions 31b and 31c are not originally shown in the middle sectional view, they are shown for convenience in order to help understanding. FIG. 4 is a perspective view showing an operation unit case 45 and a 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. FIG. 6E is a perspective view of the separate part 46. It is sectional drawing corresponding to FIG.9 (b) which shows the operation part case 45 and the clutch unit 27, (a) is the state with which the cam shaft 42 and the output shaft 43 were connected, (b) is the cam shaft 42 and output. A state in which the shaft 43 is disconnected is shown. (A)-(c) is an expanded view of the outer peripheral surface of the camshaft 42 and the output shaft 43, and is a figure for demonstrating the effect | action which the camshaft 42 and the output shaft 43 will be in a non-connection state by lowering operation. . (A)-(c) is an expanded view of the outer peripheral surface of the cam shaft 42 and the output shaft 43, and is a figure for demonstrating the effect | action which the cam shaft 42 and the output shaft 43 will be in a connection state by raising operation. FIG. 5 is a perspective view showing only some members in the operation unit 6. FIG. 5 is a perspective view showing only some members in the operation unit 6. FIG. 5 is a perspective view showing only some members in the operation unit 6. (A)-(b) is the perspective view which showed only the one part member in the operation part unit 6. FIG. FIG. 5 is a perspective view showing only some members in the operation unit 6. The transmission delay unit 25 of 2nd Embodiment of this invention is shown, (a)-(b) is a perspective view, (c) is a perspective view of the intermediate | middle rotary body 55 and the input shaft 56. FIG. The transmission delay unit 25 of 3rd Embodiment of this invention is shown, (a)-(b) is a perspective view, (c) is a perspective view of the state which removed the cover part 51a of the case 51, (d) is a disassembled perspective view. FIG. It is sectional drawing of the cross section which passes each gear part of the transmission delay unit 25 of FIG. (A)-(d) is sectional drawing which shows operation | movement of the intermediate | middle rotary body 52 when the input shaft 53 rotates from the state of FIG. (A)-(c) is sectional drawing which shows operation | movement of the intermediate | middle rotary body 52 when the input shaft 53 rotates further from the state of FIG.29 (d). The 4th Embodiment of this invention which applied the transmission delay unit 25 to the roll screen is shown, (a) is a front view, (b) is a right view, (c) is a front view of a screen. In (a), illustration of the screens 64a and 65a is omitted, and in (b), illustration of the operation pulley 23a and the operation cord 7 is omitted.

Hereinafter, embodiments of the present invention will be described. Various characteristic items shown in the following embodiments can be combined with each other. The invention is established independently for each feature.

1. First Embodiment A horizontal blind as a shielding device shown in FIGS. 1 and 2 is supported by hanging a plurality of slats 3 as a shielding material through a plurality of ladder cords 2 suspended from a 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 wefts between a pair of warp yarns. A slat 3 is supported on each weft. As shown in FIG. 5 (b), a loop portion 2 a is provided on the upper end side of the ladder cord 2, and the loop portion 2 a is rotated by the support member 10 or the support member 11 disposed in the head box 1. It is hung on a V-shaped groove 32a provided on a tilter drum 32 supported in a possible manner. The V-shaped groove 32a is formed so that its width increases outward in the radial direction so as to go around the outer peripheral surface of the tilter drum 32. By the friction between the loop portion 2a and the inner surface 32e of the V-shaped groove 32a, the slat 3 is rotated by the displacement of the loop portion 2a following the rotation of the tilter drum 32. Further, after the slat 3 is rotated until the slat 3 is in a fully closed state or a reverse fully closed state (a state in which the slat 3 faces substantially opposite to the fully closed state), the tilter drum 32 is a ladder code. 2 is idle. The ladder cord 2 corresponds to the “slat support cord” in the claims. The structure of the “slat support cord” is not limited as long as it can support and rotate the slat 3. For example, the slat support cord includes two warps separated from each other, and one warp is provided on one edge of the slat. A configuration may be employed in which the other warp is attached to the other edge of the slat.

The lifting / lowering cord 5 is also suspended from the head box 1, and the lower end of the lifting / lowering cord 5 is attached to the bottom rail 4. The bottom rail 4 is raised and lowered by winding and unwinding the lifting cord 5 on the winding shaft 9 rotatably supported by the support member 11 disposed in the head box 1.

The support members 10 and 11 support a tilter unit 19 having the same configuration. 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 winding shaft 9. The support member 10 has substantially the same configuration as that of the support member 11 for the part that supports the tilter unit 19. Hereinafter, the support member 11, the winding 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 11 a includes a winding shaft housing portion 11 e that supports the winding shaft 9 and a tilter unit housing portion 11 f that supports the tilter unit 19. The adapter plate 11b includes a lifting / lowering cord insertion portion 11c through which the lifting / lowering cord 5 is inserted, and a ladder cord insertion portion 11d through which the ladder cord 2 is inserted, and is mounted on the adapter mounting portion 11g of the support member main body 11a.

As shown in FIGS. 3 to 4, the winding shaft 9 includes a winding cone 9a and a cam unit 9b. As disclosed in Japanese Patent Application Laid-Open No. 2014-231696, the cam unit 9b is provided with a winding cone 9a when the bottom rail 4 collides with an obstacle while the weight of the bottom rail 4 is lowered, or when the bottom rail 4 reaches the lower limit position. Has the function of stopping the rotation of the. The cam unit 9 b is configured to rotate integrally with the lifting shaft 8 that rotates in accordance with the operation of the operation cord 7. When the bottom rail 4 is lifted, the cam unit 9 b is rotated with the rotation of the lifting shaft 8. And the winding cone 9a rotate integrally. On the other hand, when the bottom rail 4 is lowered by its own weight, a pulling force is applied to the lifting cord 5 as the bottom rail 4 is lowered, and the winding cone 9a is rotated by the torque generated by the pulling force. Yes. In addition, the lifting / lowering shaft 8 is provided with a speed adjuster 22 so that the rotational speed of the lifting / lowering shaft 8 when the weight of the bottom rail 4 is lowered is not excessively increased.

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 2 a of the ladder cord 2 is hooked on the V-shaped groove 32 a of the tilter drum 32. The tilter drum 32 does not rotate with the rotation of the lifting shaft 8. On the other hand, the tilt shaft 17 that rotates in accordance with the operation of the operation cord 7 is engaged with the insertion hole 34 c of the tilter gear 34, so that the tilter gear 34 rotates with the rotation of the tilt shaft 17. . Since the gear portion 32 c of the tilter drum 32 is engaged with the gear portion 34 b of the tilter gear 34, the tilter gear 32 rotates as the tilter gear 34 rotates as the tilt shaft 17 rotates.

The bearing plate 35 includes a pair of arms 35a having engaging convex portions 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 engaged, 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 part 35d. At this time, while the pair of arms 35a is 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. Then, the state shown in FIG. In this state, the axial movement of the tilter drum 32 is blocked by the engaging projection 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 these are integrated and before the support cap 33 is attached, the loop portion 2a of the ladder cord 2 is hung on the V-shaped groove 32a.

The support cap 33 includes a pair of side walls 33d each having a V-shaped protrusion 33a that becomes narrower toward the tip and an engagement groove 33b. As shown in FIG. 6B, when the support cap 33 is mounted from above the bearing plate 35 so that the base plate 35e of the bearing plate 35 enters the engagement groove 33b, the V-shaped protrusion 33a becomes the V-shaped groove 32a. It is arrange | positioned so that it may extend in.

By the way, when the bottom rail 4 is located at a position other than the upper limit position, the ladder cord 2 and the V-shaped groove 32a are frictionally engaged with each other because the weight of the slat 3 is added to the ladder cord 2, so that 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 entire weight of the slat 3 is added to the lifting / lowering cord 5 so that the weight of the slat 3 is not added to the ladder cord 2. In such a state, when 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 slat 3 is not fully closed, but the tilter drum 32 is not fully closed. May be idle with respect to the ladder code 2 in some cases. However, in the present embodiment, since the V-shaped protrusion 33a functions as a lift suppression unit that suppresses the lift of the ladder cord 2, even when the weight of the slat 3 is not applied to the ladder cord 2, the slat 3 is fully closed. When it is not, the tilter drum 32 is prevented from spinning around the ladder cord 2. In this embodiment, the V-shaped protrusion 33a is provided over 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 defined, but is 180 degrees, for example. Increasing the central angle α generates a frictional force sufficient to cause the ladder cord 2 to follow the rotation of the tilter drum 32 without excessively narrowing the gap S between the V-shaped protrusion 33a and the V-shaped groove 32a. It is possible. The configuration of the lifting suppression portion is not limited as long as the loop portion 2a of the ladder cord 2 can be prevented from lifting from the V-shaped groove 32a. For example, as illustrated in FIG. A locking projection 32f protruding from the inner surface 32e may be provided so that the loop portion 2a of the ladder cord 2 is held 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 protrusions 35f that protrude from the base plate 35e in the front-rear direction. The lower surface 33c of the side wall 33d of the support cap 33 abuts the upper surface 35g of the positioning protrusion 35f, thereby supporting the support cap 33. Is positioned in the vertical direction 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 is obtained.

As shown in FIG. 4, the tilter unit 19 can be attached to the support member body 11a from above the support member body 11a in a state where the winding shaft 9 is supported by the support member body 11a. Thus, 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 the 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 unit 23 includes an operation pulley 23a and a planetary gear 23b. An operation cord 7 is hung 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 cord 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 planet 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 and a tilt shaft gear 24c that are rotatably supported by the gear plate 24a. The transmission gear 24b is configured to rotate integrally with the input shaft 28. The transmission gear 24 b 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 tends to occur between the transmission gear 24b and the input shaft 28. However, in this embodiment, the transmission gear 24b is relative to the input shaft 28. Since there is no relative movement in the axial direction, there is no problem of wear associated with 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 slat 3 is 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 that are rotatably supported by the first and second cases 29 and 30.

The input shaft 28 includes, in order from the input side, 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. 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 supported by a bearing portion 23e1 provided on the input shaft 23e of the planetary gear 23b. An engagement groove 28b is provided in the second shaft portion 28g. Three engagement grooves 28b are provided at regular intervals in the circumferential direction. As shown in FIG. 12B, an insertion hole 23d1 is provided at the rotation center of the planet carrier 23d, and an engagement protrusion 23d2 protruding radially inward is provided in the insertion hole 23d1. Three engagement projections 23d2 are provided at equal intervals in the circumferential direction, and the input shaft 28 and the planet carrier 23d rotate integrally by engaging each engagement projection 23d2 with each engagement groove 28b. Is done. An engagement groove 28c is provided in the third shaft portion 28e. Three engagement grooves 28c are provided at equal intervals in the circumferential direction. As shown in FIG. 12A, an insertion hole 24b1 is provided at the rotation center of the transmission gear 24b, and an engagement protrusion 24b2 protruding radially inward is provided in the insertion hole 24b1. Three engagement protrusions 24b2 are provided at equal intervals in the circumferential direction, and the input shaft 28 and the transmission gear 24b rotate integrally as each engagement protrusion 24b2 is engaged with each engagement groove 28c. Is done. The first case 29 is provided with a bearing portion 29g, and the third shaft portion 28e is supported by the bearing portion 29g. Two tooth 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 28 d is supported by a bearing surface 30 h of an engagement protrusion 30 g that protrudes radially inward from the cylindrical portion 30 k of the second case 30.

The first and second cases 29 and 30 function as an output shaft of the transmission delay unit 25. The base portion 29b of the first case 29 is provided with a bearing portion 29g and a turning groove 29a. As shown in FIG. 11D, an engagement protrusion 29h is provided at the center of the rotation groove 29a in the circumferential direction so as to protrude toward the rotation groove 29a. A pair of projecting walls 29e and projecting cylinders 29c projecting 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. The snap holes 29f are provided at two positions spaced apart in the vertical direction on each protruding wall 29e.

A rotation groove 30a is provided in the base 30b of the second case 30. A pair of projecting walls 30d and projecting rods 30c projecting from the base 30b are provided on the input side surface of the base 30b. A snap projection 30e is provided on the outer surface of each protruding wall 30d. The snap projections 30e are provided at two locations apart in the vertical direction. A support shaft 30f protruding from the base portion 30b is provided between the pair of protruding walls 30d. The support shaft 30f is provided at two locations apart 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 at two locations in the respective rotating grooves 30a so as to be separated in the direction along the respective rotating grooves 30a. Each protruding piece 30i is provided with an engaging protrusion 30j protruding in the direction of the rotation groove 30a. Moreover, the cylinder part 30k is provided in the surface of the output side of the base part 30b, and the engagement protrusion 30g which protrudes radially inward from the cylinder part 30k is provided in the cylinder part 30k. Three engagement protrusions 30g are provided at equal intervals in the circumferential direction. A bearing surface 30h is provided at the tip of each engagement protrusion 30g. As described above, the fifth shaft portion 28d of the input shaft 28 is supported by the bearing surface 30h.

The intermediate rotating body 31 is provided with a bearing portion 31d, and the intermediate rotating body 31 is rotatably supported by the second case 30 when the support shaft 30f of the second case 30 is supported by the bearing portion 31d. . Three tooth protrusions 31 a protruding in the radial direction are provided on the outer peripheral surface of the intermediate rotating body 31 at a 45-degree pitch. As shown in FIG. 15, the tooth protrusions 28a and the tooth protrusions 31a are arranged so as to mesh with each other. As the input shaft 28 rotates, the tooth protrusions 28a abut against the tooth protrusions 31a and the intermediate rotating body 31 rotates. It has come to be. Moreover, the intermediate | middle rotary body 31 is provided with the control protrusions 31b and 31c which protrude in the axial direction front and back both sides. When the restricting protrusions 31b and 31c are inserted into the turning grooves 29a and 30a of the first and second cases 29 and 30, the intermediate rotating body 31 has the restricting protrusions 31b and 31c within the turning grooves 29a and 30a. Within a rotatable angle range (about 140 degrees in the present embodiment), relative rotation with respect to the first and second cases 29 and 30 is possible. An engaging groove 31e is provided in the restricting protrusion 31b. An engagement protrusion 31f is provided on the restriction protrusion 31c.

The transmission delay unit 25 inserts the support shaft 30f into the bearing portion 31d, and the first shaft portion 28f, the second shaft portion 28g, the second shaft portion 28g, and the fifth shaft portion 28d of the input shaft 28 are supported by the bearing surface 30h. The triaxial portion 28e can be assembled by inserting the bearing portion 29g in this order, inserting the protruding rod 30c through the insertion hole 29d, and engaging the snap projection 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 direction of the arrow X shown in FIGS. 10B and 11B (the direction in which the bottom rail 4 is raised), the tooth protrusion 28a is moved to the arrow as shown in FIG. Rotate in the X direction. When the input shaft 28 rotates about half a half, as shown in FIG. 15 (b), the tooth protrusion 28a meshes with the tooth protrusion 31a. When the input shaft 28 is further rotated in the arrow X direction in this state, the intermediate rotator 31 rotates in the arrow Y direction as the input shaft 28 rotates as shown in FIGS. 15 (c) to 15 (d). The intermediate rotator 31 also rotates about 60 degrees before the input shaft 28 rotates about 60 degrees to reach the state shown in FIG. At this time, the restricting protrusions 31b and 31c rotate about 60 degrees in the arrow Y direction in the rotation grooves 29a and 30a. While the restricting protrusions 31b and 31c are rotatable 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 And it rotates relative to the second cases 29 and 30. In the state of FIG. 15D, the meshing of the tooth 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 half, the tooth protrusions 28a and 31a are engaged again as shown in FIGS. 15E to 15F, and the intermediate rotating body 31 is rotated as the input shaft 28 rotates. become. Then, after the input shaft 28 and the intermediate rotator 31 are rotated about 60 degrees, the meshing of the tooth protrusions 28a and 31a is released, and the rotation of the intermediate rotator 31 accompanying the rotation of the input shaft 28 is stopped. When the input shaft 28 is further rotated about a half turn, the input shaft 28 is engaged again, and the intermediate rotating body 31 rotates as the input shaft 28 rotates. When the input shaft 28 and the intermediate rotator 31 rotate about 20 degrees, the restricting protrusions 31b and 31c reach the ends of the rotating grooves 29a and 30a, and the state shown in FIG. Thus, the intermediate rotating body 31 is intermittently rotated with the rotation of the input shaft 28.

In the state shown in FIG. 15G, the regulation protrusions 31 b and 31 c are not rotatable in the rotation grooves 29 a and 30 a, so that when the input shaft 28 is rotated, the rotation is via the intermediate rotator 31. The first and second cases 29, 30 are transmitted to the first and second cases 29, 30, and the first and second cases 29, 30 rotate integrally with the input shaft 28.

Thus, the first and second cases 29 and 30 start to rotate in the arrow X direction as the input shaft 28 rotates after the input shaft 28 rotates about 1.5 in the arrow X direction. When the input shaft 28 is rotated in the arrow Y direction, the restricting protrusions 31b and 31c move in the rotation grooves 29a and 30a in the arrow X direction from the state shown in FIG. When about 1.5 rotations in the direction of the arrow Y, the restricting 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 the arrow Y as the input shaft 28 rotates. Start rotating in the direction.

In the state shown in FIGS. 15 (a) to 15 (b), the rotation of the intermediate rotating body 31 is loosely restricted by locking the side surface of the restricting protrusion 31b with the engaging protrusion 30j. In the state of FIG. 15C, the rotation of the intermediate rotating body 31 is loosely restricted by the engagement protrusion 30j being engaged with the engagement groove 31e. In the state shown in FIGS. 15D to 15E, the engaging protrusion 31f is locked by the engaging protrusion 29h, and the side surface of the restricting protrusion 31b is locked by the engaging protrusion 30j. Rotation is controlled loosely. In the state of FIG. 15F, the rotation of the intermediate rotating body 31 is loosely restricted by the engagement protrusion 30j being engaged with the engagement groove 31e. In the state of FIG. 15G, the rotation of the intermediate rotating body 31 is loosely restricted by locking the side surface of the restricting protrusion 31b with the engaging protrusion 30j. As described above, in each state of FIGS. 15A to 15G, the rotation of the intermediate rotator 31 is loosely regulated, and the intermediate rotator 31 is rotated by vibration or the like when the input shaft 28 is not rotated. The movement is suppressed. For this reason, it is suppressed that the rotation angle of the two intermediate | middle rotary bodies 31 shifts | deviates.

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

Rotation of the first and second cases 29 and 30 is 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 protrusion 26a1. The engagement protrusions 26a1 are provided at three locations that are spaced apart at equal intervals in the circumferential direction. Each engagement protrusion 26a1 is engaged between two adjacent engagement protrusions 30g. With such a configuration, the input portion 26 a of the brake portion 26 rotates integrally with the first and second cases 29 and 30.

In the brake unit 26, the rotation transmitted to the input unit 26a from the first and second cases 29, 30 side is input 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. Communicate to
The input shaft 41 is prevented from rotating due to the torque generated by the weight of the shielding material (slat 3 and bottom rail 4). For this reason, by providing the brake part 26, the bottom-rail 4's own weight fall is prevented. By disposing 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.

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 accommodated in the operation portion 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 41 a is provided at the rotation center of the input shaft 41. The fitting hole 41a and the transmission shaft 26c are non-circular in cross section (square), 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. . On the outer peripheral surface of the input shaft 41, an engagement protrusion 41b is provided that protrudes radially outward. The engagement protrusions 41b are provided at three locations that are spaced apart at equal intervals in the circumferential direction.

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

A bearing 41e is provided on the output side of the input shaft 41. A bearing portion 42 j 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 respectively supported by the bearing portion 41e and the bearing portion 42j.

The cam shaft 42 and the output shaft 43 are formed with engaging portions 42k and 43k having a corrugated shape having a cross-sectional wave shape. When the cam shaft 42 is located away from the output shaft 43 as shown in FIG. 18B, the engaging portions 42k and 43k do not mesh with each other, and the cam shaft 42 and the output shaft 43 are not connected to each other and rotate relative to each other. To do. On the other hand, when the cam shaft 42 is at a position close to the output shaft 43 as shown in FIG. 18A, the engaging portions 42k and 43k are engaged with each other so that the cam shaft 42 and the output shaft 43 are connected to rotate integrally. To do. Therefore, the cam shaft 42 and the output shaft 43 constitute a clutch portion.

The outer periphery of the cam shaft 42 is provided with a guide groove 42g having a substantially semicircular cross section extending in the circumferential direction of the cam shaft 42. A 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 within the slide groove 46a. Further, the ball 44 relatively moves in the circumferential direction of the cam shaft 42 along the guide groove 42g as the cam shaft 42 rotates. In the following description, the relative movement in the circumferential direction may be simply referred to as “movement” for convenience.

As shown in FIG. 16, the operation part case (case body) 45 includes a cylindrical part 45a in which the cam shaft 42 and the output shaft 43 are accommodated, and a pocket part 45b provided so as to protrude in the radial direction from the cylindrical part 45a. Is provided. 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 connected to the cylindrical portion 45a and the pocket portion 45b. These members can be disposed in the operation unit case 45 by being housed in the operation unit case 45. Further, when the locking projection 46b of the separate part 46 is engaged with the end face 45c of the pocket portion 45b, the axial movement of the separate part 46 is restricted. In another assembling method, the output shaft 43 is accommodated in the cylindrical portion 45a, and then the separate part 46 is disposed in the pocket portion 45b and the ball 44 is disposed in the slide groove 46a. The cam shaft 42 can be accommodated 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, 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 so that the position of the introduction groove 42a matches 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 accommodated in the cylindrical portion 45a before the ball 44 is accommodated in the slide groove 46a. By reducing the outer diameter of the shaft or by providing an introduction groove in 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 accommodated in the cylindrical portion 45a while the ball 44 is accommodated in the slide groove 46a.

As shown in FIGS. 19 to 20, the guide groove 42g is composed of the rows A to C, and the movable range of the balls 44 in the slide groove 46a is the width of the two rows of the guide grooves 42g. It has become. The axial movement of the cam shaft 42 is realized by moving the ball 44 along the guide groove 42g as the cam shaft 42 rotates in a state where the movable range of the ball 44 in the axial direction is limited. Accordingly, the cam portion is constituted by the guide groove 42g, the slide groove 46a, and the ball 44.

Here, the operation of the horizontal blind according to this 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. 15G, and the balls 44 of the clutch unit 27 are placed in the rows A or B of the guide grooves 42g as shown in FIG. Has been placed. In this state, the cam shaft 42 and the output shaft 43 are connected as shown in FIG.

When the operation pulley 23a is rotated in the upward direction of the bottom rail 4 by pulling down the ascending operation side of the operation cord 7, the rotation is transmitted to the input shaft 28 of the transmission delay unit 25 through the planetary gear 23b. When the input shaft 28 is rotated in the upward direction of the bottom rail 4, the transmission gear 24b and the tilt shaft gear 24c meshing with the transmission gear 24b are rotated. The rotation of the tilt shaft gear 24 c 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. With the rotation of the tilter drum 32, the ladder cord 2 hung on the V-shaped groove 32a of the tilter drum 32 is displaced, and the slat 3 is rotated until the slat 3 is in the reverse fully closed state. After the slat 3 is in the reverse fully closed state, the tilter drum 32 rotates idly with respect to the ladder cord 2.

With the rotation of the input shaft 28 of the transmission delay unit 25, the restricting protrusions 31b and 31c move in the rotation grooves 29a and 30a in the arrow X direction from the state of FIG. 15G, and the input shaft 28 moves in the arrow Y direction. When about 1.5 rotations (in the upward direction of the bottom rail 4), the restricting 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 arrow Y direction. Accordingly, the rotation of the input shaft 28 is delayed by 1.5 rotations and transmitted to the first and second cases 29 and 30.

Rotation of the first and second cases 29 and 30 is 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 upward direction of the bottom rail 4, the ball 44 moves along a route that reciprocates between the rows A and B of the guide grooves 42g as shown in FIG. . Specifically, when the ball 44 reaches the cam projection a1 while moving in the row A, the ball 44 is guided in the row B direction by the cam projection a1. When the ball 44 reaches the cam island a2 while moving in the row B, the ball 44 is guided in the row A direction by the cam island a2. In this manner, the ball 44 is guided and moved so as to reciprocate between the rows A and B by the cam protrusion a1 and the cam island a2. On the outer peripheral surface of the cam shaft 42, cam protrusions a1 and cam islands a2 are provided at four locations spaced apart 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 positioned on the right side in the slide groove 46a. When the ball 44 moves to the B row, the ball 44 moves to the left side in the slide groove 46a. Therefore, the cam shaft 42 does not move in the axial direction while the ball 44 is moving along a route that reciprocates between the rows A and B.

In this state, since the cam shaft 42 and the output shaft 43 are in a connected state, the rotation of the cam shaft 42 is transmitted in the order of the output shaft 43, the lifting shaft 8 and the winding shaft 9. Accordingly, the bottom rail 4 is raised by lowering the raising operation side of the operation cord 7.

As described above, in this embodiment, the rotation of the input shaft 28 is immediately transmitted to the tilt shaft 17, but is transmitted to the lift shaft 8 after being delayed by the transmission delay unit 25. For this reason, the bottom rail 4 is prevented from starting to rise during the rotation of the slat 3.

When the bottom rail 4 is raised to the upper limit position, the torque generated by the weight of the bottom rail 4 when the hand is released from the operation cord 7 causes the winding shaft 9, the lifting shaft 8, the output shaft 43, the cam shaft 42, and the input shaft 41. In this order, the input shaft 41 tries to rotate in the downward direction, but the rotation is stopped by the brake unit 26, so 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 be made assuming that the rotation of the cam shaft 42 is stopped in a state where the ball 44 is disposed at the position shown in FIG.

From this state, when the operation cord 7 is lowered on the lowering operation side and the operation pulley 23a is rotated in the lowering direction of the bottom rail 4, the rotation is caused by the input shaft 28, the transmission gear 24b, the tilt shaft gear 24c, the tilt shaft 17, It is transmitted to the tilter drum 32 via the tilter gear 34. In the state where the bottom rail 4 is in the upper limit position, the weight of all the slats 3 is added to the lifting / lowering cord 5, and therefore the weight of the slats 3 is not added to the ladder cord 2. For this reason, in the prior art, the loop portion 2a of the ladder cord 2 in the tilter drum 32 is lifted and the slat 3 is not fully closed, but the tilter drum 32 is idle with respect to the ladder cord 2. Then, the slat 3 is not rotated. For this reason, in the prior art, when the bottom rail 4 is at 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 being fully closed. Only when the bottom rail 4 is in the upper limit position, the bottom rail 4 being lowered by its own weight with the slats 3 open is a problem in that the feeling of use is deteriorated. In the present embodiment, the ladder cord 2 is prevented from being lifted by arranging the V-shaped protrusion 33a provided on the support cap 33 so as to extend into the V-shaped groove 32a. For this reason, in this embodiment, when the slat 3 is not fully closed, the idler of the tilter drum 32 does not occur, 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 slat 3 is fully closed, the tilter drum 32 is idle with respect to the ladder cord 2.

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

Rotation of the first and second cases 29 and 30 is 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 camshaft 42 is rotated in the lowering direction of the bottom rail 4, the balls 44 move in the order of row A → row B → row C of the guide grooves 42g as shown in FIGS. 19 (b) to 19 (c). . Specifically, when the ball 44 reaches the cam projection a1 while moving in the row A, the ball 44 is guided in the row B direction by the cam projection a1. When the ball 44 reaches the cam island a2 while moving in the row B, the ball 44 is guided in the row C direction by the cam island a2. Thus, the balls 44 are 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 the row B to the row C, a leftward force is applied to the ball 44 and a rightward force is applied to the cam shaft 42. Since the ball 44 cannot move further to the left in the slide groove 46a, when the ball 44 moves from the row B to the row C, the cam shaft 42 moves in the right direction (that is, the separation direction from the output shaft 43). ) As a result, the cam shaft 42 and the output shaft 43 are disconnected, the lifting shaft 8 freely rotates, and the bottom rail 4 is lowered by its own weight. In addition, as shown in FIG.19 (b), the taper surface 42k1 is provided in the front-end | tip of the convex part of the engaging part 42k. The tapered surface 42k1 is configured so that the tapered surface 42k1 comes into contact with the convex portion of the engaging portion 43k of the output shaft 43 when the cam shaft 42 is rotated in the downward direction, and the cam shaft 42 is connected to the output shaft 43. 43 so that a force in the separation direction from 43 is applied. By providing such a tapered surface 42k1, the cam shaft 42 is easily separated from the output shaft 43.

In this 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 In this case, the idling angle is relatively small from the start of the lowering operation to the start of the weight drop of the bottom rail 4. Specifically, in the present embodiment, since the cam protrusions a1 and the cam islands a2 are provided at a pitch of 90 degrees, the idling angle has a maximum value of less than 180 degrees. The maximum value of the 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 this embodiment, the rotation of the input shaft 28 is immediately transmitted to the tilt shaft 17, but is transmitted to the lift shaft 8 after being delayed by the transmission delay unit 25. For this reason, the bottom rail 4 is restrained from starting its own weight descent while the slat 3 is rotating.

As shown in FIG. 20A, when the bottom rail 4 is lowered or its completion is lowered, the lowering side of the operation cord 7 is further lowered to further rotate the cam shaft 42 in the lowering direction of the bottom rail 4. The balls 44 move along a route that reciprocates between the rows B and C of the guide grooves 42g. Specifically, when the ball 44 reaches the cam projection a3 while moving in the row C, the ball 44 is guided in the row B direction by the cam projection a3. When the ball 44 reaches the cam island a2 while moving in the row B, the ball 44 is guided in the row C direction by the cam island a2. Thus, the ball 44 is guided and moved so as to reciprocate between the row C and the row B by the cam protrusion a3 and the cam island a2. On the outer peripheral surface of the cam shaft 42, cam protrusions a3 are provided at four locations that are spaced apart at equal intervals in the circumferential direction. The cam island a2 is provided such 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 positioned on the right side in the slide groove 46a. When the ball 44 moves to the C row, the ball 44 moves to the left side in the slide groove 46a. Therefore, the cam shaft 42 does not move in the axial direction while the ball 44 is moving along a route that reciprocates between the rows B and C.

When the bottom rail 4 is lowered or after completion of the weight reduction, the operation pulley 7 is pulled down to rotate the operation pulley 23a in the upward direction of the bottom rail 4, and the rotation is delayed by the transmission delay unit 25. This 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 upward direction of the bottom rail 4, as shown in FIGS. 20B to 20C, the balls 44 move in the order of row C → row B → row A of the guide groove 42g. . Specifically, when the ball 44 reaches the cam projection a3 while moving in the row C, the ball 44 is guided in the row B direction by the cam projection a3. When the ball 44 reaches the cam island a2 while moving in the row B, the ball 44 is guided in the row A direction by the cam island a2. In this way, the balls 44 are 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 the row B to the row A, a rightward force is applied to the ball 44 and a leftward force is applied to the cam shaft 42. Since the ball 44 cannot move any further to the right in the slide groove 46a, when the ball 44 moves from the row B to the row A, the cam shaft 42 moves to the left (that is, the connecting direction to the output shaft 43). ) As a result, the cam shaft 42 and the output shaft 43 are connected, and the rotation of the cam shaft 42 is transmitted to the elevating shaft 8 so that the bottom rail 4 is raised.

The present invention can also be implemented in the following modes.
In the above-described embodiment, the floating suppression unit that suppresses the floating of the ladder cord 2 is provided, but the floating suppression unit is not essential.
In the above embodiment, the slat 3 is tilted using the tilter drum 32 having the V-shaped groove 32a. However, the mechanism for tilting the slat 3 is not particularly limited, and is disclosed in, for example, FIG. 2 of JP-A-2014-231696. Such a mechanism using a tilt spring 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 using the two intermediate rotating bodies 31 in order to disperse the load applied to the intermediate rotating body 31. The number of the rotators 31 may be one or three or more.
In the above embodiment, in order to disperse the load applied to the intermediate rotator 31, the restricting protrusions 31b and 31c are provided on both sides in the axial direction of each intermediate rotator 31, and the restricting protrusions 31b and 31c are first and second. Although engaged with the cases 29 and 30, the restricting protrusions may be provided only on one side in the axial direction of each intermediate rotating body 31.
The direction in which the restriction protrusions 31b and 31c protrude is not particularly limited, and 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 restricting 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.
A gear that meshes with the input shaft 28 and the intermediate rotating body 31 may be provided instead of the tooth protrusions 28a and 31a. In this case, the rotational speed of the intermediate rotating body 31 can be made smaller than that of the input shaft 28 by making the number of gear teeth of the intermediate rotating body 31 larger than the number of gear teeth of the input shaft 28. However, in this case, in order to slow down the rotation speed of the intermediate rotator 31 to the same extent as in the above embodiment, the number of gear teeth of the intermediate rotator 31 needs to be 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 protrusions 31a of the intermediate rotating body 31 smaller than the pitch of the tooth protrusions 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 present specification, the rotation speed of the intermediate rotator 31 is defined by (rotation angle of the intermediate rotator 31 every time the input shaft 28 makes one revolution) / (time taken for the input shaft 28 to make one revolution). Is done. Therefore, when the intermediate rotator 31 is intermittently rotated, the time during which the intermediate rotator 31 is stopped is also included in the time for calculating the rotation speed.
The transmission delay unit 25 can be used for applications other than those in the above-described embodiment and for any application that requires a delay in transmission of rotation.
In the above embodiment, the clutch unit 27 is connected and disconnected by engaging and disengaging the two members (the cam shaft 42 and the output shaft 43) relative to each other in the axial direction. However, as long as the input rotation to the clutch unit is within a predetermined rotation angle and the input shaft can be connected to and disconnected from the output shaft, the two members may be engaged / disengaged in the radial direction. .

2. Second Embodiment A second embodiment of the present invention will be described with reference to FIG. This embodiment is similar to the first embodiment, and the difference in the configuration of the transmission delay unit 25 is the main difference. Hereinafter, the difference 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. 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 axial direction from the annular portion 55d. The control protrusion 55b provided so that it may protrude is provided. The shaft portion 55c and the annular portion 55d are connected via a base portion 55e. The input shaft 56 includes a shaft portion 56a that is rotatably supported by the case 54, and a gear portion 56b that is provided so as to mesh with the inner peripheral gear portion 55a. The restricting protrusion 55 b is inserted into a rotation groove 54 a provided in the case 54. With such a configuration, the intermediate rotator 55 can be rotated relative to the case 54 within an angular range (about 270 degrees in the present embodiment) in which the restricting protrusion 55b can rotate within the rotation groove 54a. ing. And since the gear ratio of the inner peripheral gear part 55a / gear part 56b is 3, every time the gear part 56b makes one rotation with the rotation of the input shaft 56, the restricting projection 55b rotates 120 degrees, and the gear part 56b Is slightly rotated twice, the restricting projection 55b reaches the end of the rotating groove 54a. While the restricting protrusion 55b can turn in the turning groove 54a, the input shaft 56 rotates relative to the case 54, and when the restricting protrusion 55b reaches the end of the turning groove 54a, the input shaft 56 rotates. The signal is transmitted to the case 54 via the intermediate rotating body 55, and the input shaft 56 rotates integrally with the case 54. Thus, also in this embodiment, the rotation of the input shaft 56 is delayed and transmitted to the output shaft (case 54).

3. Third Embodiment A third embodiment of the present invention will be described with reference to FIGS. This embodiment is similar to the first embodiment, and the difference in the configuration of the transmission delay unit 25 is the main difference. Hereinafter, the difference 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. 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 51c is provided with a turning 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 that is 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 periphery of the annular portion 52e. The outer peripheral gear part 52b provided in the surface and the regulation protrusion 52c provided so that it might protrude from the annular part 55d to radial direction are provided. The shaft portion 52a and the annular portion 52e are connected via a base portion 52f. The input shaft 53 includes a shaft portion 53a that is inserted into 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 are cross-sectional views of a cross section passing through each gear part as viewed from the cover part 51a side. Although the restriction projection 52c does not originally appear in each cross-sectional view, the restriction projection 52c is displayed in each drawing for the sake of convenience in order to represent the positional relationship between the restriction projection 52c and the locking portion 51d.

As shown in FIG. 28, when the input shaft 53 is rotated counterclockwise, the intermediate rotating body 52 is also rotated counterclockwise due to the engagement of 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 around the input shaft 53 in the clockwise direction along the rotation groove 51f by the meshing of 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 rotator 52 follows the trajectories shown in FIGS. 29 (a) to 29 (d) and FIGS. 30 (a) to (b), as shown in FIG. 30 (c). Then, the restricting projection 52c is rotated to a position where it is locked by the locking portion 51d.

While the restricting projection 52c is not locked by the locking portion 51d, the input shaft 53 rotates relative to the case 51. When the restricting projection 52c reaches the locking portion 51d, the input shaft 53 rotates to an intermediate rotation. It is transmitted to the case 51 via the body 52 and the input shaft 53 rotates integrally with the case 51. Thus, 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 FIG. 30C is about 4.5 in this embodiment, but the number of gear teeth, the shape of the restricting protrusion 52c or the locking portion 51d The number of rotations can be appropriately changed by changing 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 will be described with reference to FIG. In this roll screen, the drive gear 61 and the transmission gear 62 are engaged, and the transmission gear 62 and the driven gear 63 are engaged. 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 a support frame (not shown). The drive gear 61 has an engagement shaft 61a, and the engagement shaft 61a is engaged with the operation 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 winding shaft 64. For this reason, the rotation of the drive gear 61 is delayed and transmitted to the winding shaft 64. The upper end of the screen 64a is attached to the winding shaft 64. A weight bar 64b is attached to the lower end of the screen 64a. Since no transmission delay unit is provided between the driven gear 63 and the winding shaft 65, the rotation of the driven gear 63 is transmitted to the winding shaft 65 without being delayed. The upper end of the screen 65a is attached to the winding shaft 65. A weight bar 65b is attached to the lower end of the screen 65a.

When the operation cord 7 hung 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 being delayed. The On the other hand, the rotation of the operation pulley 23 a is delayed by the transmission delay unit 25 and transmitted to the winding shaft 64. For this reason, the screens 64a and 65a are wound around the winding shafts 64 and 65 in a state in which the screen 65a is shifted 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 pulley 7a 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 winding shaft 65 without being delayed. On the other hand, the rotation of the operation pulley 23 a is delayed by the transmission delay unit 25 and transmitted to the winding shaft 64. For this reason, while the transmission of rotation is delayed, only the screen 65a is rewound, and the vertical displacement of the screens 64a and 65a is reduced. Thus, by using the transmission delay unit 25, the relative position in the vertical direction of the two screens 64a and 65a can be changed. For example, as shown in FIG. 31C, when the screens 64a and 65a are provided with the light shielding portions 66 and the light transmitting portions 67 alternately, the relative positions of the screens 64a and 65a in the vertical direction are set. By changing it, 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 section, 24: tilt transmission section, 25: transmission delay unit, 26: brake section 27: clutch unit, 28: input shaft, 29, 30: first and second cases, 31: intermediate rotating body, 32: tilter drum, 32a: V-shaped groove, 33: support cap, 33a: V-shaped protrusion, 34 : Tilter gear, 35: bearing plate, 41: input shaft, 42: cam shaft, 43: output shaft, 44: ball, 45: operation part case, 46: separate part, 51: case, 52: During rotary member, 53: input shaft, 54: Case, 55: intermediate rotor, 56: input shaft

Claims (10)

1. A first input shaft, an intermediate rotator configured to rotate at a lower rotational speed than the first input shaft as the first input shaft rotates, and the rotation of the first input shaft via the intermediate rotator Is provided with a first output shaft,
   The transmission delay unit, wherein the intermediate rotating body is configured to be unable to rotate relative to the first output shaft after rotating by a predetermined angle.
2. The transmission delay unit according to claim 1, wherein an outer peripheral surface of the intermediate rotating body is configured to mesh with an outer peripheral surface of the first input shaft.
3. The transmission delay unit according to claim 2, wherein the intermediate rotating body is configured to rotate intermittently as the first input shaft rotates.
4. A plurality of the intermediate rotating bodies are provided,
   The transmission delay unit according to claim 2 or 3, wherein the plurality of intermediate rotating bodies are configured to rotate simultaneously with the rotation of the first input shaft.
5. The transmission delay unit according to claim 1, wherein an inner peripheral surface of the intermediate rotating body is configured to mesh with an outer peripheral surface of the first input shaft.
6. The transmission delay according to claim 1, wherein the intermediate rotating body is configured to rotate with the rotation of the first input shaft and to revolve around the first input shaft in a direction opposite to the direction of the rotation. unit.
7. The intermediate rotator includes a regulation protrusion, and the intermediate rotator rotates relative to the first output shaft by being locked by the first output shaft as the intermediate rotator rotates. The propagation delay unit according to any one of claims 1 to 6, which is configured to be disabled.
8. A shielding material lifting device that rotates the lifting shaft by operating the operation code to raise and lower the shielding material,
   The rotation of the input shaft that rotates in accordance with the operation of the operation code is transmitted to the lift shaft via the transmission delay unit and the clutch unit according to any one of claims 1 to 7. ,
   The clutch unit includes a second input shaft that rotates as the first output shaft rotates, and a second output shaft that rotates integrally with the lifting 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 cam shaft that move with the movement of the cam shaft. A shielding material elevating device including a clutch unit that switches between a connected state and a non-connected state between two output shafts.
9. A shielding material elevating device configured to rotate an elevating axis and a tilt axis by operating an operation code,
   The rotation of the input shaft that rotates in accordance with the operation of the operation code is configured to be transmitted to the lifting shaft via a transmission delay unit,
   The transmission delay unit includes a first input shaft that rotates with the rotation of the input shaft, and a first output shaft that is transmitted with the rotation of the first input shaft delayed.
   A transmission gear that rotates integrally with the first input shaft; and a tilt shaft gear that rotates integrally with the tilt shaft and meshes with the transmission gear, the transmission gear being disposed on the input side of the transmission delay unit Shielding material lifting device.
10. A shielding material lifting device that rotates the lifting shaft by operating the operation code to raise and lower the shielding material,
    The rotation of the input shaft that rotates in accordance with the operation of the operation code is configured to be transmitted to the lifting shaft via a transmission delay unit and a clutch unit,
    The transmission delay unit includes a first input shaft that rotates with the rotation of the input shaft, and a first output shaft that is transmitted with the rotation of the first input shaft delayed.
    The clutch unit includes a second input shaft that rotates as the first output shaft rotates, and a second output shaft that rotates integrally with the lifting 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 cam shaft that move with the movement of the cam shaft. It has a clutch part that switches the connection / disconnection state between the two output shafts,
    A brake part 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 to block the rotation of the second input shaft due to the torque generated by the weight of the shielding material. .

Images