BRIEF DESCRIPTION OF THE DRAWINGS
In order to understand the invention and to see how it may be carried out in practice, an embodiment will now be described, by way of a non-limiting example only, with reference to the accompanying drawings, in which:
FIG. 1 is an isometric view of a Venetian blind assembly comprising a control mechanism according to the present invention;
FIG. 2 is an enlarged isometric view of an actuator of the control mechanism of FIG. 1;
FIG. 3A is a longitudinal cross section view of the actuator and rod of the control mechanism according to the invention;
FIG. 3B is an enlargement of a detail ‘H’ of FIG. 3A;
FIG. 3C is an enlarged isometric view of the portion marked III in FIG. 3A;
FIG. 4A is an isometric view of the control mechanism of FIG. 2 with the actuator and hollow rod removed for visualization;
FIG. 4B is an isometric view of the lead bar and friction ring of the control mechanism;
FIG. 5 is a cross section view of the control mechanism during raising of the slats;
FIGS. 6A to 6D are cross section views of the control mechanism of FIG. 1 showing gradual angular displacement of the shift pin during lowering of the slats, with the actuator removed; and
FIGS. 7A to 7D are enlargements of details A to D in FIGS. 6A to 6D, respectively, with the actuator removed.
DETAILED DESCRIPTION OF EXEMPLARY EMBODIMENTS
FIG. 1 shows a Venetian blind generally designated 100 fitted with a control mechanism generally designated 1. The Venetian blinds assembly comprises a headrail 101 and a plurality of slats/blinds 102 extending from the headrail 101 by two or more main lift cord 103, adapted for raising and lowering the slats 102. The slack of said lift cords, depending on the elevation of the slats 102, is collectable by spools (not seen) received within the headrail 101, as known per se. There are further provided ladders comprising auxiliary cords 104A, 104B for supporting and tilting of the slats 102. The headrail 101 is fitted with a combined raising/lowering and tilting mechanism 110 (received and concealed within the headrail 101 and is thus schematically illustrated), adapted for raising/lowering and tilting the blinds respectively, as known per se.
Referring now to FIG. 2, the control mechanism 1 comprises a rod (actuating wand) 10 in the form of main hollow rod articulated to the combined mechanism 110 of the blinds as will be explained in detail later. The rod 10 has a body 12 formed with an axial hollow 14 therein. A longitudinal slot 16 extends along the majority of the hollow rod 10. In fact, the length of the slot 16 defines the extent to which the raising/lowering mechanism can travel and respectively the raising/lowering extent of the slats 102, as will become apparent hereinafter. In the present example, the length of the slot is 50% the height of the blind, however, this length may be greater or shorter, by providing a length ratio manipulator.
An actuator 20, in the form of a grip handle, comprises a body 22 and a knob 24 and is slidingly mounted onto the rod 10. An actuating mechanism 30 is received within the hollow rod 10, and articulated to the actuator 20 and to the combined mechanism 110 as will be explained in detail herein below. Also received within the rod 10 are raising/lowering cords 103, to be further discussed hereinafter.
The arrangement is such that the rod 10 is free to rotate about its longitudinal axis X-X thus allowing tilting of the blinds 102 as with a conventional Venetian blind. The actuator 20 is free to slide up and down along the rod 10, for lowering or raising the blinds 102 respectively, as will be explained hereinafter.
With further reference also to FIGS. 3, 4A and 4B, the actuating mechanism 30 is received within the hollow rod 10 and is articulated to a lift cord coupling unit 50 (FIG. 3B) using a ball link 40, acting as an axial coupler however not transferring rotary motion between the lead rod 31 and the cord 103, as will be appreciated later. The lift cord coupling unit 50 is connected, in turn, to the main lift cord 103 (FIG. 2). The actuating mechanism 30 comprises a lead bar 31 formed at a top distal end thereof with a connector portion 32, adapted for coupling to the ball chain 40. The lead bar 31 is further formed with a tapering portion 33 (best seen in FIG. 4B) extending between a portion of the of the lead bar 31 having a large diameter ‘D’, and a portion of the lead bar 31 having a smaller diameter ‘d’, with a rubber O-ring 34 mounted over said tapering portion 33 and positioned between a first sleeve 35A and a second sleeve 36, both coaxially received between the lead bar 31 and the hollow rod 10 in a fairly tight manner. A coiled spring 37 is mounted onto the lead bar 31, between the connector portion 32 and the second sleeve 36 thereby giving rise to a biasing force between the lead bar 31 and the second sleeve 36.
A shift pin 26 interconnects the actuator assembly 20 (FIGS. 3A and 3B), and the actuating mechanism 30, extending through the longitudinal slot 16 of the hollow rod 10 and an aperture 39 formed in the sleeve 35B. The pin 26 is engaged at one end thereof with the handle knob 24, and at its respective other end with a shaped cavity 38 formed within the lead bar 31 of the actuating mechanism 30.
As noted also in FIGS. 5 to 7, however best in FIG. 3B, the shaped cavity 38 is formed with a first inclined surface 38I, a second inclined surface 38II, with a pivot point 38P there between, a third inclined surface 38III and a substantially vertically extending surface 38IV. Knob 24 is formed with a receptacle 25 with a main, substantially vertical channel 26I and an inclined wall surface 26II.
The shift pin 26 is so positioned that it is able to perform an angular/pivotal displacement within the cavity 38 of the lead bar 31 and within the knob 24, as will be explained in detail later.
The arrangement is such that when the pin 26 is at its normal, standby position it extends substantially upright (as seen in FIGS. 3, 5, 6A and 7A) whereby the pin aligned within the opening 38 and receptacle 25, i.e. substantially parallel to the surfaces 26I and 38IV.
In operation, when the blinds assembly 100 is at rest (regardless of the position of the blinds, namely raised/lowered or tilted), the weight of the slats 102 applies tension via cords 103 on the lift cord coupling unit 50, and consequently on the lead bar 31. Since the fit between the sleeve portions 35A and 36 and the inside surface of the hollow rod 10 is tighter than that between the hollow rod 10 and the sleeves 35A and 36, the weight of the slats 102 causes the lead bar 31 to move upwards (i.e. in direction of arrow 107 in FIG. 3A), while the sleeves 35A and 36 are temporarily held in place by friction. During such displacement of the lead bar 31, the sleeve 36 partially arrests the friction ring 34, whereby progress of the lead bar 31 causes the ring 34 to extend now over a larger diameter of the tapering surface 33, adjacent a rear end thereof end, subsequently entailing an expansion in the diameter of the friction ring 34. Once the friction ring 34 is expanded, the friction between the friction ring 34 and the inner surface of the hollow rod 10 facilitates jamming of the actuating mechanism 30, arresting it further axial displacement upwards within the hollow rod 10 under the self weight of the slats 102, thus keeping the blinds at a fixed elevation position, namely “fixed mode”.
During raising of the slats 102 as seen in FIG. 5, namely switching to a “raising mode”, downward displacement (i.e. in a direction opposed to that of arrow 107) of the actuator 20 is required. This downward displacement of the actuator 20 entails a corresponding downward displacement of the lead bar 31, due to the engagement by the shift pin 26, extending substantially upright and linking between the actuator 22 and the lead rod 31. During such displacement the pin 26 does not pivot within the receptacle 25 and opening 38. Since the first sleeve 35A and the second sleeve 36 are tightly fit within the hollow rod 10, they stay temporarily in place, whereby downward displacement of only the lead bar 31, entails displacing the friction ring 34 (formerly trapped between the sleeves 35A and 36) to become positioned over the small diameter ‘d’ of the tapering portion 33. Consequentially, the coiled spring 37 becomes compressed between a shoulder of the connector portion 32 of lead rod 31 and an end face of the second sleeve 36. It is appreciated that when positioned on the small diameter ‘d’, the friction ring 34 shrinks, acquiring a smaller diameter, whereby the friction between the friction ring 34 and the hollow rod 10 is reduced, allowing the inner mechanism to freely slide down the rod 10.
Gripping the body 22 of the actuator 20 and sliding it downwards over the rod 10 entails corresponding downwards displacement of the lead rod 31 and the articulated coupling unit 50, thereby pulling on the lift cord 103, resulting in raising the slats 102. Here it is important to note that although the sleeves 35 and 36 are tightly fit into the hollow rod 10, the fit is such that they are still able to displace the length of the rod 10 along with the actuator 20 when raising and lowering the blinds, however as long as the O-ring 34 is at its shrunken position.
When the actuator 20 is released by the user, the spring 37 decompresses (expands) and biases the lead bar 31 in an upwards direction (direction of arrow 107 in FIG. 3A). This upwards displacement causes the lead bar 31 to reposition itself with reference to the sleeves 35 and 36, such that the friction ring 34 is now again positioned on the large diameter ‘D’ of the tapering portion 33 and the control mechanism 1 returns to a “fixed mode” wherein any further displacement is temporarily arrested.
Referring now also to FIGS. 6A to 6D and FIGS. 7A to 7D, in order to lower the slats 102, namely switching to a “lowering mode”, upward displacement of the actuator 20 is required. This upward displacement entails pivoting of the shift pin 26 about pivot point 38P (FIGS. 6B, 6C, 7B and 7C) from its normally upright position (FIGS. 3A, 3B, 6A and 7A) substantially perpendicular to the lead bar 31 and parallel to surfaces 26I and 38IV, gradually into a position where it rests in the inclined channel of the shaped cavity 38, such that the pin 26 extends substantially parallel to the inclined surfaces 38II and 38III.
With the rod 10 being axially fixed to headrail 101, pivotal displacement of the shift pin 26 entails axial displacement of the first sleeve 35A and the second sleeve 36 in an upward direction, against the biasing effect of the spring 37. Following this displacement of the sleeves 35A and 36, the friction ring 34 displaces upwards as well, so that it becomes positioned on the small diameter ‘d’ of the tapering portion (FIGS. 6C and 7C). When positioned over the small diameter ‘d’, the friction ring 34 shrinks, acquiring a smaller diameter, whereby the friction between the friction ring 34 and the hollow rod 10 is reduced, allowing the inner mechanism 30 to freely slide up the rod 10 (FIGS. 6D and 7D). Sliding the actuator 20 up the rod 10 pulls on the lift cord 103, and thereby raises the blinds 102. In the particular example, since the cords 103 are looped about a roller 52 of the cord coupling unit 50, there is a pulley effect i.e. displacement of the lead rod 31 with the articulated cord coupling unit 50 at distance X entails raising/lowering of the slats at a distance corresponding with 2X.
When the actuator 20 is released, the spring 37 expands and thus causes the lead bar 31 to displace in an upwards direction. This upwards displacement causes the lead bar 31 to reposition itself with reference to the sleeves 35 and 36, such that the ring 34 is now again positioned over the large diameter ‘D’ of the conical surface 33 and the control mechanism 1 returns to its respective “fixed mode” such that when the user leaves the actuator body 22 the system is at an arrested position.
It should be noted, that raising/lowering ratio of the salts may be pre-determined to be in the range of about 1:1 to 1:3 due to a pulley mechanism (not shown) fitted with the combined mechanism 110 located in the headrail (FIG. 1), i.e. displacement of the actuator 20 at distance X along the rod 10 may entail a 2X or 3X raise/lowering of the blinds 102, depending on the transmission ratio of the pulley mechanism (i.e. using a different pulley arrangement other ratios may be achieved).
The first sleeve 35A and the back sleeve 35B may be integrated into one sleeve 35 formed with the aperture 39, adapted to receiver the shift pin 26. Alternatively, they may be separate elements.
The rod 10 is articulated to the combined mechanism 110, whereby revolving the hollow rod 10 about its longitudinal axis X-X either clock-wise or counter clock-wise entails corresponding tilt of the blinds 102 in one direction or the other, as known per se. However, such rotation of the hollow rod 10 does not twist the lift cord 103 around itself due to the connection of the inner mechanism 30 to the lift cord coupling unit 50 by the ball link 40.
It should also be noted, that according to other possible embodiments of the present invention, the raising/lowering and tilting operations performed by the control mechanism 1 may work individually, i.e. the control mechanism 1 may be used only for raising/lowering the blinds 102 whereas a separate tilting mechanism may be fitted to the blinds at another location along the headrail.
Those skilled in the art to which this invention pertains will readily appreciate that numerous changes, variations and modifications can be made without departing from the scope of the invention mutatis mutandis.
Patent Application
20080066876
