CN101275456B

CN101275456B - Spring transmission and drag brake for drive for coverings for architectural openings

Info

Publication number: CN101275456B
Application number: CN2007101988899A
Authority: CN
Inventors: R·安德森; R·E·费希尔二世; D·E·弗拉塞尔
Original assignee: Hunter Douglas NV
Current assignee: Hunter Douglas NV
Priority date: 2007-03-30
Filing date: 2007-12-12
Publication date: 2013-03-13
Anticipated expiration: 2027-12-12
Also published as: TWI465636B; KR20150005890A; CN101275456A; KR101517334B1; KR101517228B1; KR20080089140A; TW200839081A

Abstract

A spring motor and drag brake for use in coverings for architectural openings. The combination of the spring motor and drag brake comprises: an output scroll, installed to rotate clockwise and anticlockwise; a transmission device spring, winding itself and limiting the first end and the second end, wherein the first end is fixed on the output scroll; and a brake. The brake comprises: a brake drum, connected to the output scroll functionally so as to make the rotation of the output scroll lead to the rotation of the brake drum; a helical spring component, installed on the brake drum; and a casing, wherein, through the installation manner that the helical spring component resists the brake drum rotating clockwise and anticlockwise relatively to the casing, so as to install the helical spring component and to overcome the torque needed by rotating resistance in one of clockwise direction and anticlockwise direction bigger than in the other direction.

Description

The spring motor of the drive unit of architectural opening overburden and drag brake

Technical field

The present invention relates to a kind of spring motor (spring motor) and drag brake (dragbrake), it can be used for opening and closes or tilt for the overburden (covering) of architectural opening, such as venetian blind, shutter curtain, vertical blinds, other expandable material and other mechanical device.

Background technology

Generally speaking, the blind transmission system will have upper rail, rail supporting overburden and hiding for improving and reducing or open and the mechanism that closes overburden on this.This blind system is described in United States Patent (USP) the 6th, 536, in No. 503, be used for the modularization transmission system (Modular Transport System for Coverings for ArchitecturalOpenings) of architectural opening overburden, aforementioned patent is integrally incorporated herein by reference.In typical case top-down (top/down) product, suspended and be attached to one on the lower rail (also be known as and move rail or bottom batten) or many stay cords improve and reduce overburden by certainly going up rail.Opening with closing usually of overburden reached by louver curtain heading tape (and/or suspension cable), ladder tape for venetian blind operation before and after the bar stack of plates.Stay cord moves or is passed in the hole in the batten usually along bar stack of plates front and back.In the overburden of these types, it is minimum to improve the required power of overburden when overburden is fallen (fully launch) fully, this be since the weight of batten by the supporting of louver curtain heading tape so that rail under when beginning, only improving.Along with overburden is further improved, the bar stack of plates is upward on the lower rail, and the weight of batten is transferred on the stay cord from the louver curtain heading tape, therefore mentions the position of (regaining fully) fully along with overburden approaches, and the lifting force that needs to increase gradually improves overburden.

Some window covers product and oppositely builds (bottom-up), wherein be in substituting of window covering Cong Shu bottom as moving rail, move rail and be in window covering Cong Shu top, between this Cong Shu and upper rail, so that when this overburden is retracted, this clump Shu Tongchang is deposited in bottom of window, and when this overburden launches, moves the upper rail place of top next-door neighbour that rail is in the window overburden.Also have joint product, it can operate in two ways, top-down operation and/or bottom-up operation.

In horizontal window covers product, have external force of gravity, the operator overcome this external force of gravity with the position movement of expandable material from its expanded position and retrieving position to another position.

Opposite with blind, in top-down window-blind, such as level of shear window shade (shear horizontal window shade), when improving window-blind, whole light screening material twines around rotation rail (rotator rail) usually.Therefore, when improving window-blind, the weight of window-blind is transferred on the rotation rail, and therefore along with window-blind (shading element) moves closer to fully the position of mentioning (opening fully), improves the required power of window-blind and reduce gradually.Certainly, also have bottom-up window-blind and compound window-blind, compound window-blind can operate in two ways, top-down and/or bottom-up operation.In the situation of bottom-up window-blind, along with window-blind is lowered, the weight of window-blind is transferred on the rotation rail, imitates the operator scheme of top-down louver curtain.

In the situation of vertical orientation window overburden, it moves by side to opposite side but not moves up and down from one, and the first rope is generally used for moving overburden to retrieving position and the second rope (or second end of the first rope) then is used for moving overburden to expanded position.In this case, the operator overcomes the gravity operation.Yet these window overburdens also may have by setting another external force or the load of non-gravity, such as spring, the operator will overcome spring with expandable material from a position movement to the another location.

The a variety of driving mechanisms that be used for to launch and regain overburden (horizontal or vertical mobile overburden or batten is tilted) are known.These many driving mechanisms may provide catalytic force (catalyst force) (and/or catalytic force of complement operation person supply) to come mobile overburden with spring motor.

Summary of the invention

The invention provides a kind of spring motor and drag brake, it can be used for opening and closes or tilt for the overburden of architectural opening.The combination of this spring motor and drag brake comprises: the output spool, and it is mounted for upward rotating in the clockwise direction with counterclockwise; The transmission device clockwork spring, it is certainly being reeled with it and is limiting first end and the second end, and this first end is fixed on this output spool; And brake.This brake comprises: brake drum, and it is connected on this output spool in function, so that the rotation of this output spool causes the rotation of this brake drum; Coil spring assembly, it is installed on this brake drum; And shell.Wherein, at this clockwise direction and the mounting means of rotation counterclockwise this coil spring assembly is installed with respect to this shell by making this coil spring assembly resist this brake drum, and is overcome the required moment of torsion of this rotational resistance greater than on other direction in this clockwise direction and a direction counterclockwise.

Description of drawings

Fig. 1 is window shade and the decomposed phantom drawing that is used for drive unit this window shade and that combine spring motor;

Fig. 2 is the decomposition diagram of the spring motor of Fig. 1;

Fig. 3 is the phantom drawing of transmission device of the assembling of Fig. 2;

Fig. 4 is the end-view of the spring motor of Fig. 3;

The sectional view that Fig. 5 intercepts for the line 5-5 along Fig. 4;

Fig. 6 A be in conjunction with the spring motor of Fig. 3 top-down/phantom drawing of bottom-up window-blind;

Fig. 6 B is the decomposed phantom drawing of the upper rail of Fig. 6 A, combines two groups of drive units on this in the rail;

Fig. 7 is the decomposition diagram of another embodiment of spring motor;

Fig. 8 is the phantom drawing of transmission device of the assembling of Fig. 7;

Fig. 9 is the end-view of the spring motor of Fig. 8;

The sectional view that Figure 10 intercepts for the line 10-10 along Fig. 9;

Figure 11 is the phantom drawing of transmission device output shaft, helical spring and the spring coupling of the assembling of Fig. 7;

Figure 12 is the decomposition diagram of another embodiment of spring motor;

Figure 12 A is the decomposition diagram of another embodiment that is similar to the spring motor of Figure 12;

Figure 13 is the assembly drawing of the spring motor of Figure 12;

Figure 14 is that the spring motor of Figure 13 is end-view;

The sectional view that Figure 15 A intercepts for the line 15-15 along Figure 14;

Figure 15 B be the assembling of Figure 12 the resistance brake drum, sleeve and helical spring phantom drawing bridge;

Figure 16 is the decomposition diagram of another embodiment of spring motor;

Figure 17 is the assembly drawing of the spring motor of Figure 16;

Figure 18 is similar to shown in Figure 15 but is the sectional view of the spring motor of Figure 17;

Figure 19 be the backward-coiled of leaf spring transmission device (flat spring motor) around in the schematic diagram of related three steps; And

Figure 20 is the curve map of the torque curve of display standard wind spring and reverse wind spring.

The specific embodiment

Fig. 1 to Figure 20 illustrates the various embodiment of spring motor.These spring motors can by improve and reducing the window overburden, move by side to it opposite side or make their batten inclination opening be used for cutting out launching and regaining the window overburden from one.Window overburden or the overburden that is used for architectural opening also can more specifically be called blind (blind) or window-blind in this article.

Fig. 1 is the decomposed phantom drawing of the first embodiment that utilizes lattice shape (cellular) window-blind 100 of spring motor and drag brake combination 102.

The window-blind 100 of Fig. 1 comprises rail 108, lower rail 110 and certainly goes up rail 108 suspended and be attached to lattice shape window-blind structure 112 on rail 108 and the lower rail 110.Cladding material 112 has the width substantially the same with the length of upper rail 108 and lifting arm 118, and it has the height substantially the same with the length of stay cord (in this figure and not shown but shown two groups of stay cords in Fig. 6 A) when launching fully, stay cord is attached on lower rail 110 and the lifting station 116 so that when lifting arm 118 rotation, lifting spool on lifting station 116 also rotates, and stay cord is wound on the lifting station 116 or untie to improve or reduce lower rail 110 and therefore improve or reduce window-blind 100 from lifting station 116.The United States Patent (USP) the 6th that these lifting stations 116 and their operating principle were promulgated on March 25th, 2003,536, No. 503, " the modularization transmission system (Modular Transport System forCoverings for Architectural Openings) that is used for the architectural opening overburden " is open, and aforementioned patent is integrally incorporated herein by reference.End cap 120 seals the end of upper rail 108 and can be used for trellis product 100 is installed on the architectural opening.

Between two lifting stations 116, be provided with spring motor and drag brake combination 102, it is interconnecting so that when spring motor rotates with lifting station 116 on the function via lifting arm 118, lifting arm 118 and the spool on lifting station 116 also rotate, and vice versa, as discussing in more detail hereinafter.In aforesaid U.S. Patent the 6th, 536, also disclose with spring motor in No. 503 and improved and reduced louvre curtain.

In order to improve window-blind, the user mentions at lower rail 110.The auxiliary user of spring motor improves window-blind.Simultaneously, the drag brake part of spring motor and drag brake combination 102 applies resistance to this moving upward of window-blind.Such as hereinafter explanation, depend on direction of rotation, drag brake applies two kinds of different moments of torsion and resists rotation.In this embodiment, the resistance to upwards motion that is applied by drag brake is smaller in two moments of torsion (is known as and discharges moment of torsion), as explaining in more detail hereinafter.This discharges in addition system friction and because the size of the moment of torsion that the weight of window-blind causes is enough to prevent that spring motor from causing window-blind 100 to swash after the user discharges window-blind of moment of torsion.

In order to reduce window-blind, the user is drop-down on lower rail 110, the auxiliary user of gravity in this task.When drop-down on lower rail 100, rotate this spring motor in order to increase the potential energy (being wound up on its output spool 122 by the leaf spring with transmission device, as explaining in more detail hereinafter) of leaf spring.The drag brake of this combination 102 part moves downward to window-blind this and applies resistance and this resistance for the greater in two moments of torsion that applied by drag brake (be known as and keep moment of torsion), as explaining in more detail hereinafter.The size of the moment of torsion that this maintenance moment of torsion and spring motor apply and system friction combination is enough to prevent that window-blind 100 from falling.Therefore, window-blind rests on the position that it is discharged by the user, no matter where window-blind is released in along its whole travel range; It neither swashes also not fall when discharging.

Now referring to Fig. 2, spring motor and drag brake combination 102 comprise transmission device output spool 122, leaf spring 124 (also being known as transmission device clockwork spring (motor spring) 124), classification (stepped) helical spring 126, drive housing part 128 and brake shell part 130.Two housing parts 128,130 are joined together to form complete shell.It should be noted that in this embodiment, brake shell part 130 extends beyond stopper mechanism in order to also enclose the part of transmission device.

Transmission device output spool 122 (also referring to Fig. 5) comprises that spring batches (take-up) part 132, it is chamfered respectively left shoulder 134 and surrounds and define directed vertically smooth recess 138 with right shoulder 136 in the side, this smooth recess 138 comprises that raised button 140 (referring to Fig. 5) is used for the first end 142 of leaf spring 124 is fixed to transmission device output spool 122.The first end 142 of leaf spring 124 is threaded in the smooth recess 138 of spring reel-up 132 until the raised button 140 of spring reel-up 132 is passed in the opening 144 of the first end 142 of leaf spring 124 fastens, and leaf spring 124 is fixed on the transmission device output spool 122 releasedly.

Transmission device output spool 122 also comprises the resistance brake drum part 146 that extends to vertically right shoulder 136 right sides.Minor axis 148,150 each end from transmission device output spool 122 extend vertically for swivel bearing transmission device output spool 122, and are as mentioned below.

Leaf spring 124 is for closely being wound up into the flat metal band from it, as Fig. 2 describes.As discussed above, the first end 142 of spring 124 limits port 144 releasedly leaf spring 124 is fixed on the transmission device output spool 122.Can find out that such as the starting point from Fig. 2 the path of leaf spring 124 (routing) is the operation and entering in the smooth recess (flat) 138 until button 140 snaps in the port 144 of leaf spring 124 below transmission device output spool 122 of the end 142 of leaf spring 124.

Now referring to helical spring 126, it is similar to the conventional helical spring, except it limits two different spring ring diameters.(it should be noted that spring ring diameter is only for a feature of spring coil.Another is characterized as steel wire (wire) diameter or steel wire cross sectional dimensions.) the first spring coil part 152 has less spring ring diameter and only limit slightly internal diameter less than resistance brake drum 146 external diameters.The second spring coil part 154 has larger spring ring diameter and only limits slightly external diameter greater than the internal diameter of respective cavities 156, respective cavities 156 (also being known as shell aperture 156 or drag brake hole 156) is limited by brake shell 130, as hereinafter in more detail as described in.

Brake shell part 130 limits cylindrical cavities 156 (as shown previously, it also is known as drag brake shell aperture 156), and the diameter of this cylindrical cavity 156 is only slightly less than the external diameter of the second spring coil part 154 of classification helical spring 126.Brake shell part 130 comprises boring axle protuberance 158, it limits leaf spring storage volume axle 162 with boring axle protuberance 160 (referring to Fig. 5) similar in drive housing part 128 and that be complementary, and this leaf spring storage spool 162 limits and passes housing parts 128,130 ports 164 that extend.As explaining hereinafter, this port 164 can be used as the position of passing of bar (such as lifting arm or tilting bar), it allows two independently very closely close in parallel with each other placements of drive unit are obtained using the possibility of upper rail 108 that may be narrower than originally.

In Fig. 5, in fact the first spring coil part 152 that has shown classification helical spring 126 is embedded in the resistance brake drum part 146 and has shown that similarly in fact the second spring coil part 154 is embedded in the resistance brake hole 156.In fact, these spring coil parts 152,154 are not to be embedded into veritably in their parts 146,156 separately, but show by this way and be illustrated in spring coil part 152,154 and their drums 146 separately and the fact of the interference engagement between the shell aperture 156.The steel wire diameter of the amount of this interference engagement and classification helical spring 126 or steel wire cross sectional dimensions have determined that (dictate) is in order to make brake drum 146 rotate the release moment of torsion and maintenance moment of torsion that must overcome at first direction and second direction respectively with respect to shell 130.These two moments of torsion also can be known as component torque, this is because they are the moments of torsion that applied or applied at the drag brake parts by the drag brake parts, compare with system torque, system torque for also being comprised by the moment of torsion that applies on the overall system and system torque because the moment of torsion that the spring motor of this combination 102 part causes, friction torque, moment of torsion of causing owing to the weight of window-blind etc.

Helical spring 126 applies moment of torsion against the hole 156 of brake drum 146 and shell 130, and these moments of torsion opposing brake drums 146 with respect to shell 130 in the clockwise direction with counter clockwise direction on rotation.The amount of the moment of torsion that is applied against brake drum 146 and hole 156 by helical spring 126 is looked brake drum 146 with respect to the direction of rotation of shell 130 and different and the position apparent rotation direction of sliding occurs and become.For the ease of these descriptions, for the helical spring moment of torsion that must overcome with respect to shell rotation brake drum in one direction is known as the maintenance moment of torsion, and in order to be known as the release moment of torsion in another direction with respect to the bulging helical spring moment of torsion that must overcome of shell rotation brake.

Moment of torsion occurs to keep when output spool and brake drum rotates (can find out such as the starting point from Fig. 2) in the counterclockwise direction with respect to shell 130, and this maintenances moment of torsion tends to make helical spring 126 to divide 146 and towards 146 expansion of the hole of shell 130 or stretching, extension away from tympanic part.In this case, the first spring coil part 152 that resistance brake drum part 146 is slided and crossed helical spring 126, and the second spring coil part 154 of helical spring 126 locks onto on the shell aperture 146.This maintenance moment of torsion is the higher person and in this embodiment in two component torque of these drag brake parts, when leaf spring 124 is winding on the output spool 122 (and from 162 expansion of storage spool, the potential energy of increase device 102) time this maintenance moment of torsion occurs, when it also betides the user by means of the drop-down window-blind 100 of gravity.

Therefore, drop-down to overcome when keeping moment of torsion on lower rail 100 as the user, leaf spring 124 is wound up on the output spool, and drum 146 slides with respect to helical spring 126.Keep moment of torsion when any point along the stroke distances of window-blind 112 discharges window-blind, to be enough to prevent that window-blind 100 from falling the user by design.(certainly, but this set also is opposite, so that be rotated counterclockwise when lower rail promotes the user).

Equally, when the lower rail 110 of window-blind 100 was raised, output spool 122 and brake drum 146 rotated (as seen from Figure 2) in the clockwise direction with respect to the hole 156 of shell 130.Leaf spring 124 is wound up on the storage spool 162 and from output spool 132 and launches, and auxiliary user improves window-blind 100.And classification helical spring 126 causes helical spring 126 to shrink away from shell aperture 156 and towards drum 146 in identical clockwise direction rotation.This causes the first spring coil part 152 to be clamped on the resistance brake drum part 146 downwards and the second spring coil part 154 tightens away from hole 156.Moment of torsion (smaller in two moments of torsion of these drag brake parts) when sliding with respect to shell aperture 156, classification helical spring 126 occurs to discharge.

Therefore, when the operator when lower rail 110 is mentioned, leaf spring 124 is wound up on the storage spool 162 and along with window-blind rises, helical spring slides with respect to hole 156.

In a word, keeping moment of torsion is the greater in two moments of torsion of this resistance brake component, and when helical spring 126 increases or expands, this maintenance moment of torsion occurs so that the second spring coil part 154 stretches also " locking " to the hole 156 of shell 130 against the hole 156 of shell 130, and the first spring coil part 152 is slided from 146 stretching, extensions of resistance brake drum part and with respect to resistance brake drum part 146.Discharge moment of torsion and be smaller in two moments of torsion of resistance brake component and this releases moment of torsion occurs when resistance tripping spring 126 draws in so that the second spring coil part 154 is shunk away from the hole 156 of shell 130 and with respect to hole 156 slips of

shell

130 and 152 gatherings of the first spring coil part also " locking " on resistance brake drum part 146.Two moments of torsion of resistance brake component all provide drum 146 and the resistance of output spool 122 with respect to shell 130 rotations.The larger application-specific that depends on of which moment of torsion in the torque capacity of each direction of rotation of drag brake and these moments of torsion.

In order to assemble spring motor and drag brake combination 102, leaf spring 124 is fixed on the output spool 122, as already mentioned above.Classification helical spring 126 is placed on brake shell part 130 inside at 146 slips of resistance brake drum part and this assembly of output spool 122, and the central opening 166 of leaf spring 124 is placed in 156 inside, drag brake hole at 158 slips of hollow shaft protuberance and the classification helical spring 126 of brake shell part 130.Then drive housing part 128 matches with brake shell part 130.These two housing parts 128,130 pins that are illustrated 168 and bridge 170 are buckled together (such as the U.S. patent application case S/N 11/382 that files an application on May 8th, 2006, No. 089, " be used for the interlock design (Snap-Together Design for ComponentAssembly) of assembling parts " and describe comprehensively, aforementioned application is incorporated herein by using integral ground).The corresponding port 172,174 (referring to Fig. 5) that the minor axis 148,150 of output spool 122 is cross-placed on respectively in drive housing part 128 and the resistance brake drum part 146 is upper for rotatably mounted output spool 122.

As finding out in Fig. 5, the position that leaf spring 124 shown being in " are discharged " fully all is wound up on the storage spool 162.Classification helical spring 126 is shown to mediate, this position first helical spring part 152 closely winding dynamic braking tympanic part divide 146 to reel and the second spring coil part 154 also closely 156 is reeled against the drag brake hole.As explaining in front, when the lower rail 110 of the drop-down window-blind 100 of user, classification helical spring 126 stretches or launches so that the second spring coil part 154 closely is locked on the drag brake hole 156, and the first spring coil part 152 stretches away from resistance brake drum part 146, and this higher person (it is known as and keeps moment of torsion) that allows brake to sentence for two moments of torsion of drag brake parts in brake drum part 146 slides.The user must overcome this and keep moment of torsion and leaf spring 24 is wound up into required moment of torsion and any other system torque reduces window-blind 100 on the output spool 122, and these moments of torsion also are the moments of torsion that prevents that after the user discharges window-blind 100 window-blind from falling.

Fig. 1 has shown how spring motor and drag brake combination 102 may be installed in the window-blind 100.Since lifting arm 118 fully by spring motor and drag brake combination 102 (via in exporting spool 122 at axially aligned port 176), therefore spring motor and drag brake combination 102 may be installed in along any position of upper rail 108 length, between the lifting station 116 or on the either side of lifting station 116.The design flexibility that the Installation Flexibility that this designing institute provides provides far above the prior art designing institute.

It should be noted that in Fig. 4 this port 176 in output spool 122 has non-circular profile.In fact, in this specific embodiment, it has " V " recess profile 176, should " V " recess profile 176 and lifting arm 118 couplings with similar profile.Therefore, the rotation of output spool 122 causes the corresponding rotation of lifting arm 118 and vice versa.

Storage spool 162 also is hollow reel, and it limits port 164, and another bar can pass this port 164 such as another lifting arm 118 and extend.Yet this opening 164 does not match with the bar that be used for to drive engages but the passage that only provides this bar to pass through.This obtains the very compact setting of the drive unit of two independent parallel, as shown in Fig. 6 B.This especially conforms with the needs of bottom-up/top-down window-blind 1002 operations, as shown in Fig. 6 A.

Shown in Fig. 6 B, the wider envelop of function of ability permission realization of a kind of driving control element (such as spring motor or brake) can be installed in any position along a plurality of axostylus axostyles.Axostylus axostyle 1022 of setup and use shown in Fig. 6 B improves and reduces the part of overburden and improves and the another part that reduces overburden with another axostylus axostyle 1024 that is parallel to the first axostylus axostyle 1022, but uses two or more axostylus axostyles also to allow other function.For example in fact, axostylus axostyle can be used for improving and reduces this covering and another axostylus axostyle and can be used for making the batten on the overburden to tilt, as at United States Patent (USP) the 6th, 536, described in No. 503 like that.

Fig. 6 A and Fig. 6 B have described top-down/bottom-up window-blind 1002, two spring motors of its use and drag brake combination 102, one of each

lifting arm

1022,1024 use.Window-blind 1002 comprises the head track 1004 with end cap 1006, middle rail 1008 with end cap 1010, lower rail 1012 with end cap 1014, lattice shape window-blind structure 1016, spring motor and

drag brake combination

102M, 102B, two lower rail lifting stations 1018, two middle rail lifting stations 1020, lower rail lifting arm 1022 and middle rail lifting arms 1024.

Fig. 6 B top-down/situation of bottom-up window-blind 1002 under, spring motor and

drag brake combination

102M, 102B,

lifting station

1018,1020, and

lifting arm

1022,1024 all is contained in the head track 1004.Lifting arm or

axostylus axostyle

1022,1024 all pass completely through the combination of two spring motors and

drag brake

102M, 102B, but in lifting arm or the

axostylus axostyle

1022,1024 each in only engaging transmission device and drag brake making up one and with in the situation that another one engages do not passing another one.Front lifting arm 1024 interconnects with two lifting stations 1020, spring motor and drag brake combination 102M and middle rail 1008 in operation via stay cord 1030 (referring to Fig. 6 A) but just passes another spring motor and drag brake combination 102B.Rear lifting arm 1022 interconnects via stay cord 1032 (referring to Fig. 6 A) and two lifting stations 1018, spring motor and drag brake combination 102B and lower rail 1012 but just passes another spring motor and drag brake combination 102M.

In this case, middle rail 1008 may make progress operation all the time until it just is held on head track 1004 belows, perhaps it may move downwards all the time until it just is held on lower rail 1012 tops, and perhaps middle rail 1008 may rest on any position between these two extreme positions.Lower rail 1012 may make progress operation all the time until it just is held on the below (no matter where middle rail is positioned at for 1008 this moments) of middle rail 1008, perhaps it may move downwards all the time until it extends the total length of window-blind 1002, perhaps descends rail 1012 may rest on any position between these two extreme positions.

Each

lifting arm

1022,1024 uses its parts separately to operate independently of one another about the described same way as of single pole system as mentioned, and wherein front bar 1024 is connected on the middle rail 1008 in operation, and rear bar 1022 is connected on the lower rail in operation.

Briefly referring to Fig. 6 B, spring motor and

drag brake combination

102B, 102M may be identical or different between them be that classification helical spring 126 may have different steel wire diameter (perhaps different steel wire cross sectional dimensions) in case the maintenance moment of torsion that customization is used for each brake with discharge moment of torsion.The larger-diameter steel wire (or larger steel wire cross sectional dimensions) that is used for classification helical spring 126 produces higher maintenance moment of torsion and discharges moment of torsion.Whether no matter identical, spring motor and drag brake combination 102B are " upsets " with respect to spring motor and drag brake combination 102M when mounted.The lifting arm 1022 that is used for lower rail 1012 passes the port 176 (and export spool 122 with this engage) of spring motor and the output spool 122 of drag brake combination 102B.It also passes the port 164 of the storage spool 162 of spring motor and drag brake combination 102M.Equally, the lifting arm 1024 that is used for rail 1008 is passed in port 176 in the output spool 122 of spring motor and drag brake combination 102M (and export spool 122 with this engage).It also makes up the port 164 of the storage spool 162 of 102B by another spring motor and drag brake.

It should be noted, may add as required the combination of a plurality of spring motors or a plurality of spring motor and drag brake, and, they pass completely through their shell because provide these parts to be used for axostylus axostyle or

bar

1022,1024, so may be positioned at along bar 1022, any position of 1024.Should also be noted that wider assembly combination range in the ability permission system of the driver part that makes two or more axostylus axostyles pass completely through spring-operated (wherein at least one axostylus axostyle engages this spring and at least one another axostylus axostyle does not engage this spring in operation in operation).The driver part of spring-operated may be independent spring motor, the combination of independent spring-loaded brake, spring motor as shown here and spring-loaded brake or other parts.

Other embodiment of spring motor and drag brake combination

Fig. 7 to Figure 11 described spring motor and drag brake combination 102 ' another embodiment.And Fig. 2 has relatively given prominence to difference between this embodiment 102 ' and previous the disclosed embodiments 102.As substituting of single classification helical spring 126, this embodiment comprises two " routine "

helical spring

126S, 126L, and these two " routine "

helical spring

126S, 126L are by spring coupling 127 ' link together in function.The first helical spring 126S has less spring ring diameter, and the second helical spring 126L has larger spring ring diameter.

Spring coupling 127 ' be the washer-shaped device, its limit pod 178 ', the elongated end 180 of pod 178 ' admit respectively

helical spring

126S, 126L ', 182 '.Because helical spring 126S has less spring ring diameter, its be assemblied in larger diameter helical spring 126L inside and elongated end 180 ', 182 ' adjacent one another are be positioned at groove 178 ', as shown in figure 10.

Spring coupling 127 ' restriction central opening 184 ', this central opening 184 ' permission spring coupling 127 ' output spool 122 ' minor axis 150 ' slip.Spring coupling 127 ' permission two

spring

126S, 126L by have different-diameter (or different steel wire cross sectional dimensions because the cross section of steel wire may not be as these springs for circular) steel wire makes and still serve as single spring when exporting spool 122 ' rotation.Figure 11 has shown two

helical spring

126S, 126L, these two helical spring 126S, 16L on the function by spring coupling 127 ' connect and be installed on output spool 122 ' on.

This spring motor and drag brake combination 102 ' work to make up 102 identical modes with spring motor mentioned above and drag brake is selected separately the steel wire cross sectional dimensions of each

helical spring

126S, 126L neatly except using two

helical spring

126S, 126L permissions.In this way, can select more accurately correct (perhaps desirable) braking torque for every kind of application.

For example, Fig. 7 described to be used for winding dynamic braking tympanic part divide 146 ' clamping than the steel wire cross sectional dimensions of small coil springs 126S greater than the steel wire cross sectional dimensions than king bolt spring 126L that is used in drag brake hole 156 ' inner clamping.Because sliding torque (helical spring slides and crosses its institute against the moment of torsion on the surface of clamping) along with for the vary in diameter of helical spring steel wire cross section (in the same situation of other condition, the steel wire cross sectional dimensions is larger, sliding torque is higher), therefore maintenance moment of torsion embodiment illustrated in fig. 7 (two the greater in moment of torsion) is greater than the maintenance moment of torsion of the similar spring motor with the less spring coil 126S that is made by the smaller cross-sectional area steel wire and drag brake.

Figure 12 and Figure 13 to Figure 15 B have described spring motor and drag brake combination 102 " another embodiment." and the difference between previous the disclosed embodiments 102 that and the ratio of Fig. 2 has been given prominence to this embodiment 102 more quickly.This embodiment 102 " comprise a plurality of identical or very similar parts, such as transmission device output spool 122 ", leaf spring 124 " (or transmission device clockwork spring 124 "), drive housing part 128 ", brake shell part 130 ", resistance brake drum part 146 " and helical spring 126 ".Such as hereinafter discussion, some clauses and subclauses in these clauses and subclauses slightly are different from above and " also have the sleeve of bridging 127 " about the described clauses and subclauses of previous embodiment and this embodiment 102, the needs of the operation of the sleeve 127 that bridges " being to conform with this spring motor and drag brake combination 102 " but be not strict necessity.(at the another embodiment 102 shown in Figure 16 ^*Do not use sleeve.)

Very significantly difference is resistance brake drum part 146, and " be single-piece, it is rotatably supported on the transmission device output spool 122 " axle extension 148 ".As can recognizing from Figure 15 A, on transmission device output spool 122 " is rotatably supported in housing parts 128 ", 130 " upper and resistance brake drum parts 146 " are rotatably supported in transmission device output spool 122 " axostylus axostyle extension 148 ".Transmission device output spool 122 " with resistance brake drum part 146 " has the hollow shaft 176 ", 186 " of band non-circular profile (also referring to Figure 12 and Figure 14), in order to engage lifting arm 118.

Brake shell part 130 " comprises two " ears " 188 ", and it is limited to axially aligned groove shape opening so that fixing helical spring 126 " crimp end 190 " releasedly, as discussed below.

Sleeve 127 bridges " be discontinuous cylinder ring, it has longitudinal cut 192 ", and this longitudinal cut 192 " allows the diameter of ring " gathering " Cheng Gengxiao.Two sleeves 127 that bridge " being identical, two helical springs 126 " also are identical (still, if need, helical springs 126 " may have different steel wire diameter to realize desirable moment of torsion).Explaining this transmission device and drag brake combination 102 " operation after this will become clearer, if need and enough, may use only one group of sleeve 127 that bridges " and helical spring 126 ".The embodiment 102 of Figure 12 " has shown two groups of sleeves 127 that bridge that are used for obtaining larger maintenance moment of torsion (larger brake power) " and helical spring 126 ".Certainly, if need (and if can be contained in resistance brake drum part 146 " on), also can use additional group.And sleeve 127 bridges " use be optional, such as the embodiment 102 by Figure 16 ^*Can find out that it is described hereinafter in more detail.

On the external diameter that helical spring 126 " can directly be cross-placed on resistance brake drum part 146 ", but use the sleeve 127 that bridges " selecting to be used for resistance brake drum part 146 " and be used for bridging sleeve 127 " suitable material aspect the permission greater flexibility.For example in fact, the external diameter of the sleeve 127 that bridges " may be best some is flexible by having (so that it can be in resistance brake drum part 146 " draws in) and the material with some self-lubricating character make.In addition, if use the sleeve 127 that bridges ", in the situation of high wear between the helical spring 126 " and the sleeve 127 that bridges ", may simply replace the sleeve 127 that bridges so ", and nonessential replacement resistance brake drum part 146 ".The remainder of this description has been introduced only one group of sleeve 127 that bridges " with helical spring 126 " (unless otherwise noted), should be appreciated that also and can use two or more groups, may have preferably result but its operating principle is substantially the same, as discussed above.

With with above about the transmission device of Fig. 2 output spool 122 described same way as leaf spring 124 " is assembled into transmission device output spool 122 " on.Then the leaf spring 124 assembled " with transmission device output spool 122 " is assembled in the drive housing part 128 " with brake shell part 130 ", wherein leaf spring 124 " opening 166 " is respectively in hollow shaft protuberance 158 " with 160 " slip of drive housing part 128 " with brake shell part 130 ".

Then on the external diameter that, the sleeve 127 that will bridge " with helical spring 126 " is assembled into resistance brake drum part 146 " on, shown in Figure 15 B, the sleeve 127 that wherein bridges " with helical spring 126 " is installed to resistance brake drum part 146 continuously ".That " to be installed to its corresponding sleeve 127 that bridges " upper so that helical spring 126 " crimp end 190 " is outstanding by the sleeve 127 that bridges " groove shape opening 192 " with helical spring 126.Each sleeve 127 that bridges " comprises peripheral flange 194 at each end " to help to prevent operating period " upper landing from its corresponding sleeve 127 that bridges of helical spring 126 " in spring motor and drag brake combination 102 ".

Then, the outrigger shaft 148 that the resistance brake drum part 146 that assembles ", helical spring 126 " and the sleeve 127 that bridges " are installed to transmission device output spool 122 " " on, guarantee that each helical spring 126 " crimp end 190 " is stuck in the one in the brake shell part 130 " groove shape opening 188 ".Resistance brake drum part 146 " rotation until transmission device output spool 122 " and resistance brake drum part 146 " non-circular profile 176 ", 186 " are aimed at respectively so that lifting arm 118 can pass whole assembly insertion, as shown in figure 13.

During operation, as from shown in the starting point of Figure 12, along with transmission device output spool 122 " be rotated counterclockwise (corresponding to reduction and the leaf spring 124 of window-blind 100 " " is transferred to transmission device output spool 122 " from storage spool 162), transmission device output spool 122 " with resistance brake drum part 146 " all counterclockwise rotates at this.Also impelled the sleeve 127 that bridges " the rotation of this equidirectional (sleeve 127 owing to bridge " with resistance brake drum part 146 " between friction), and also impelled helical spring 126 " this equidirectional rotation (owing to bridging sleeve 127 " and helical spring 126 " between friction).Yet, helical spring 126 " crimp end 190 " is fixed to brake shell part 130 " upper and prevent this crimp end 190 " rotation, therefore, at helical spring 126 " remainder when beginning to rotate in the counterclockwise direction, tighten on the helical spring 126 " to the sleeve 127 that bridges ".Therefore draw on the external diameter of sleeve 127 " slightly to the drag brake part 146 " that bridge, to the rotation of the lifting arm of resistance brake drum part 146 " rotation (and to engaging resistance brake drum part 146 ") resistance that increases is provided.

When promoting window-blind 100, auxiliary user when spring motor and drag brake combination 102 " at leaf springs 124 " " launch (therefore it turn clockwise) and are wound up into storage spool 162 " from transmission device output spool 122." also turn clockwise, it has impelled the sleeve 127 that bridges " with helical spring 126 " to turn clockwise to resistance brake drum part 146.Equally, the groove shape opening 188 of " crimp end 190 be fixed to brake shell part 130 " because helical spring 126 " on; so helical spring 126 " " growths " or stretch, increased their internal diameter and the sleeve 127 that reduces to a great extent to bridge " go up and tympanic part divides 146 " on braking torque.Therefore, resistance brake drum part 146 " can from helical spring 126 " rotates than under the slight drag.Therefore, the user can be in spring motor and drag brake combination 102 " help under easily improve window-blind 100.

Figure 12 A has described spring motor and the drag brake combination 102 with Figure 12

Identical embodiment, except helical spring 126 " in a helical spring 126 " with respect to helical spring 126 " 180 degree that overturn, and it is to be made by the wire material with thinner cross section.Now, " when turning clockwise, the sleeve 127 that bridges " with helical spring 126 " also turns clockwise when resistance brake drum part 146.Yet in this case, turning clockwise to cause on the second helical spring 126 " downwards to its sleeve 127 that bridges " tightens, on the sleeve 127 that reduced to bridge " internal diameter and therefore be clamped in resistance brake drum part 146 downwards ".The cross-sectional diameter of " cross-sectional diameter less than the first helical spring 126 " because this second helical spring 126, therefore, the moment of resistance that " is applied to resistance brake drum part 146 when rotating in the clockwise direction " when resistance brake drum part 146 is applied to resistance brake drum part 146 when rotating in the counterclockwise direction " the moment of resistance.If the cross sectional dimensions of the second helical spring steel wire is greater than the first helical spring 126 " the cross sectional dimensions of steel wire, the braking torque in so in the clockwise direction will be larger.If two helical springs 126 " identical but still opposite each other, so in both direction braking torque with identical.

Figure 16 and Figure 17 have described spring motor and drag brake combination 102 ^*Another embodiment.Compare with Figure 12 and to have shown this embodiment 102 ^*" substantially the same, " and it only has single helical spring 126 except this embodiment does not have the sleeve 127 that bridges with previous the disclosed embodiments 102 ^*Yet, if need, can use two or more this helical springs 126 ^*, such as described embodiment 102 formerly " situation under.Helical spring 126 ^*Directly ride up to resistance brake drum part 146 ^*External diameter on but not use the sleeve 127 that bridges ".Except these differences, this spring motor and drag brake combination 102 ^*So that " substantially the same mode operates with previous described embodiment 102.

It should be noted, in this spring motor and drag brake combination 102 ^*In, as in the situation of all spring motors as herein described and drag brake combination, helical spring 126 ^*Or leaf spring 124 ^*Can from assembly, omit.If omitted helical spring 126 ^*, the combination of spring motor and drag brake 102 so ^*Only operate as spring motor, and do not have the ability of drag brake.Equally, if omitted leaf spring 124 ^*, the combination of spring motor and drag brake 102 so ^*Only do not have the transmission device ability as the drag brake operation.

Figure 18 has described spring motor and drag brake combination 102 ^*Another embodiment.With Fig. 5 relatively shown this embodiment 102 ^*Substantially the same with embodiment 102, except making up 102 at this spring motor and drag brake ^*In, storage spool 162 ^*Be not as with the situation of previous described embodiment 102 under hollow reel.Therefore, in this case, lifting arm can not pass storage spool 162 ^*Except this difference, this spring motor and drag brake combination 102 ^*Operate in basically substantially the same with embodiment 102 mode.

Figure 19 and Figure 20 have described the embodiment of leaf spring (or transmission device clockwork spring), if need, it is used in these embodiment described in this manual.Himself make by the flat metal band closely is wound at the leaf spring 124 shown in the step #1, afterwards, spring coil is disengaged stress.This leaf spring defines internal diameter 196, and internal diameter 196 is 0.25 inch in this embodiment.Spring 124 shown in when step #1 finishes can be used for embodiment mentioned above, and perhaps this spring can experience extra step, as shown in figure 19.

In step #1, at first reel this helical spring 124 so that the first end 200 of spring 124 in the inside of spring coil and the second end 202 of spring 124 outside at spring coil.Then, then helical spring 124 is disengaged stress, therefore it is rendered as spring coil group (springset) shown in Figure 1, and its medi-spring has less radius of curvature and to its second (outer) end little by little and constantly increase at its first (interior) end.Afterwards, in step #2, backward-coiled around this helical spring 124 until it arrives the position shown in step #3, in this position, the end 202 (having larger spring coil suite rate radius) that the end 200 of spring 124 (having less spring coil suite rate radius) now is in spring coil outside and spring 12 now is in spring coil inside, and wherein spring coil suite rate radius little by little and constantly reduces outward from the inner.This backward-coiled around spring coil 124R again do not separated de-stress.And, this backward-coiled around spring coil 124R define internal diameter 198, this internal diameter 198 preferably is slightly larger than the internal diameter 196 of original leaf spring 124.In this embodiment 124R, this internal diameter is 0.29 inch.

Figure 20 with chart drawing standard coiling leaf spring 124 (leaf spring when it is illustrated in step #1 and finishes) power-assisted moment of torsion (power assist torque) curve and with its with backward-coiled when the step #3 of Figure 19 end around the torque curve of leaf spring 124R compare.When it has described to begin to launch (left side far away of curve) from spring until its be fully expanded (its for towards the curve middle part, curve shows the point of rapid drawdown) and then return until spring by the torsional forces of fully again reel (right-hand member far away of curve).Will be appreciated that the power-assisted torque curve of backward-coiled winding board spring 124R is curve more smooth than standard coiling leaf spring 124 on the whole opereating specification of spring.This more smooth torque curve normally is used for improving and reducing the employed desirable feature of spring motor type of window overburden.

Now briefly referring to Fig. 2, if the reverse wind spring 124R with Figure 19 replaces leaf spring 124, so oppositely the end 200 (it has less spring coil suite rate radius) of wind spring 124 is with holes 144 end 142, and this hole 144 allows it to be attached on the output spool 122.The lever arm that acts on output spool 122 is defined as the distance on surface 132 from the rotation of output spool 122 to output spool 122.When reverse wind spring 124R launched and basically be wound up into himself when upper from output spool 122 basically, this lever arm is minimum.Therefore, utilize this setting, the part with reverse wind spring 124R of the highest spring rate (minimum spring coil suite rate radius) works at minimum lever arm.

When backward-coiled around spring 124R when basically being wound up on the output spool 122, acting on the lever arm of output on the spool 122 will increase by the thickness that now is wound up into the spring coil on the output spool 122.Therefore, when backward-coiled around the minimum spring rate (part of maximum spring coil suite rate radius) of spring 124R when acting on the output spool, this lever arm is with maximum.Final result is that the power-assisted torque curve is become smoothly, as shown in figure 20.

Oppositely the program of wind spring 124 only is to keep simultaneously the uniform thickness of the metal tape that forms spring and a kind of method of width along the length change spring rate of spring depicted in figure 19.Use other program may obtain similar result, and the spring coil suite rate that may design spring 124 is to obtain to have the torque curve of negative slope or any other desirable slope.

For example, the metal tape that forms spring 124 may stretch with the spring coil suite rate (with spring rate therefore) of the various parts that change spring 124 at anvil with various angles, and does not change other physical parameter of spring.The angle that stretches at anvil by changing metal, can make spring rate continue to increase or reduce to the other end from an end of spring, it is increased to mid point from an end, keep constant and then reduce for the length-specific of spring coil, perhaps increase and then reduce, perhaps progressively change, perhaps depend on the application that it will be used for, with any other desirable pattern.The spring coil suite rate radius that can handle as required spring forms desirable spring force with each point along spring in order to obtain desirable power-assisted torque curve for any application-specific.

Spring coil suite rate radius in the prior art 202 continues to increase outward along the whole consistent length of leaf spring or from inner 200, and wherein outer end 202 is connected to the output spool of spring motor.Yet, as explained above, leaf spring may be designed so that may have radius of curvature greater than the spring coil group of the part of the leaf spring of the more close end that is connected to the output spool, such as situation and the many situations in other design leaf spring mentioned above arranges at the reverse wind spring as shown in the step #3 of Figure 19 apart from the part of the end leaf spring far away that is connected to the output spool.Spring coil suite rate radius may have apart from the farther third part in end that is connected to the output spool, and this third part is less than the relatively large radius part, and perhaps it can keep from this relatively large radius part to the other end constant etc.

It will be apparent to those skilled in the art that in the situation that does not deviate from the category of the present invention that limits such as claim and can embodiment mentioned above be made amendment.For example, the resistance arrestment mechanism can be attached on the spring motor storage spool, this spring motor storage spool is installed to rotate with respect to shell, this still makes the resistance arrestment mechanism be attached to spring motor output spool and still realize same result in function.Also can carry out multiple other modification.

Claims

1. a transmission device clockwork spring and drag brake combination, it comprises:

Output spool, described output spool are mounted for upward rotating in the clockwise direction with counterclockwise;

Transmission device clockwork spring, described transmission device clockwork spring are reeled on himself and are limited first end and the second end, and described first end is fixed on the described output spool; And

Brake, described brake comprises:

Brake drum, described brake drum is connected on the described output spool in function, so that the rotation of described output spool causes the rotation of described brake drum;

Coil spring assembly, described coil spring assembly are installed on the described brake drum; And

Fixing shell, it defines fixing endoporus;

Wherein, at described clockwise direction and the mounting means of rotation counterclockwise described coil spring assembly is installed with respect to described shell by making described coil spring assembly resist described brake drum, and is overcome the required moment of torsion of described rotational resistance greater than on other direction in described clockwise direction and a direction counterclockwise;

Described coil spring assembly comprises small diameter spring section and larger diameter spring section;

When described brake drum described clockwise direction with counterclockwise in a direction on during with respect to described shell rotation, described small diameter spring section draws on the described brake drum and described larger diameter spring section shrinks away from described endoporus; And

When described brake drum described clockwise direction with counterclockwise in another direction on during with respect to described shell rotation, described small diameter spring section stretches away from described brake drum and described larger diameter spring section stretches against described endoporus.

2. transmission device clockwork spring according to claim 1 and drag brake combination is characterized in that described coil spring assembly comprises: the first helical spring that described small diameter spring section is provided; Second helical spring that separates of described larger diameter spring section is provided; And the spring coupling, described spring coupling makes described the first helical spring link to each other in function with the second helical spring, so that described two helical springs rotate together as single component.

3. transmission device clockwork spring according to claim 1 and drag brake combination, it is characterized in that, described coil spring assembly applies moment of torsion against the described endoporus of described brake drum and described shell, and described moment of torsion is resisted described brake drum with respect to the rotation of described shell on described clockwise direction and described anticlockwise both direction; And described coil spring assembly slides to allow described brake drum to rotate in described clockwise direction and a direction counterclockwise with respect to described shell with respect to described brake drum, and described coil spring assembly slides to allow described brake drum to rotate with respect to described shell another direction in described both direction with respect to the described hole of described shell.

4. transmission device clockwork spring according to claim 3 and drag brake combination is characterized in that, when described small diameter spring section stretched away from described brake drum, described transmission device clockwork spring was wound up on the described output spool.

5. transmission device clockwork spring according to claim 2 and drag brake combination, it is characterized in that, described small diameter spring section is made by the steel wire with first cross sectional dimensions, and described larger diameter spring section is to be made by the steel wire with second cross sectional dimensions that is different from described the first cross sectional dimensions.

6. transmission device clockwork spring according to claim 1 and drag brake combination, it is characterized in that, described transmission device clockwork spring and drag brake combination also comprise the overburden for architectural opening, described overburden is connected on the described brake drum in function, so that when described overburden launches described brake drum described clockwise with counterclockwise in a direction rotate, and when described overburden is regained described brake drum described clockwise with counterclockwise in another direction operate.

7. transmission device clockwork spring according to claim 6 and drag brake combination, it is characterized in that, described shell define the two pairs of openings of aiming at vertically parallel with two open path, each path of opening passes completely through described shell and passes the described a pair of extension of opening in corresponding that axially align, every pair of opening of aiming at is vertically admitted and is passed the axostylus axostyle that described shell extends, one in the described path of opening extends through described output spool vertically, and in the described axostylus axostyle each is connected to described overburden in operation.

8. transmission device clockwork spring according to claim 1 and drag brake combination is characterized in that the part that described small diameter spring section and described larger diameter spring section are single spring.

9. transmission device clockwork spring according to claim 6 and drag brake combination, it is characterized in that, described transmission device clockwork spring is leaf spring, wherein at least one part apart from described first end described leaf spring far away has the larger groups of springs of radius of curvature, and the second portion of the described leaf spring of more close described first end has the less groups of springs of radius of curvature.

Transmission device clockwork spring according to claim 9 and drag brake the combination, it is characterized in that, the described radius of curvature of described leaf spring from described first end than small curvature radius continue to increase to described the second end than larger radius of curvature.

11. transmission device clockwork spring according to claim 10 and drag brake combination, it is characterized in that, exist apart from the third part of the described first end described leaf spring more farther than a described part, described third part has radius of curvature less than the spring coil group of a described part.

12. a transmission device clockwork spring and drag brake combination, it comprises:

Brake, described brake comprises:

Shell;

Coil spring assembly, at described clockwise direction and the mounting means of rotation counterclockwise described coil spring assembly is installed on the described brake drum with respect to described shell by making described coil spring assembly resist described brake drum, and overcomes the required moment of torsion of described rotational resistance greater than on other direction in described clockwise direction and a direction counterclockwise; Described coil spring assembly comprises the first helical spring and the second helical spring that is installed on the described brake drum; In described the first helical spring and the second helical spring each comprises the first end that is fixed on the described shell, when described output spool described clockwise with counterclockwise in a direction rotation time described the first helical spring draw in to described brake drum, and when described output spool described clockwise with counterclockwise in another direction when rotating described the second helical spring draw in to described brake drum.

13. transmission device clockwork spring according to claim 12 and drag brake combination is characterized in that described coil spring assembly is included in drawn in the sleeve in the middle of described brake drum and described the first helical spring.

14. transmission device clockwork spring according to claim 12 and drag brake combination, it is characterized in that, described shell defines two pairs of opening paths of opening parallel with two of aiming at vertically, each path of opening pass completely through described shell and pass the described opening of aiming at vertically in corresponding a pair of extension and be suitable for admitting and pass the axostylus axostyle that described shell extends, one in the described path of opening extends through described output spool vertically.

15. a covering system that is used for covering architectural opening, it comprises:

Overburden movably; And

Spring motor, described spring motor is connected on the described removable overburden in operation, described spring motor comprises output spool and leaf spring, described leaf spring has first end and the second end, described leaf spring is connected on the described output spool at described first end, wherein at least one part apart from described first end described leaf spring far away has the larger groups of springs of radius of curvature, the second portion of the described leaf spring of more close described first end has the less groups of springs of radius of curvature, and described output spool is mounted for rotating clockwise and counterclockwise;

Brake drum, described brake drum is connected on the described output spool in function, so that the rotation of described output spool causes described brake drum rotation;

Shell; And

Coil spring assembly, by make described coil spring assembly resist described brake drum with respect to described shell described clockwise with counterclockwise on the mounting means of rotation described coil spring assembly is installed on the described brake drum, and overcome the required moment of torsion of described rotational resistance greater than on other direction in described clockwise direction and a direction counterclockwise;

Wherein, described shell be fix and define endoporus; Described coil spring assembly comprises small diameter spring section and larger diameter spring section, when the direction of described brake drum in described clockwise direction and described counter clockwise direction rotated, described small diameter spring section draws on the described brake drum and described larger diameter spring section draws in away from described endoporus, and described small diameter spring section stretches against described endoporus away from described brake drum stretching, extension and described larger diameter spring section when described brake drum another direction in described clockwise direction and described counter clockwise direction is rotated.

16. the covering system for covering architectural opening according to claim 15 characterized by further comprising:

The first axostylus axostyle and the second axostylus axostyle, described the first axostylus axostyle and the second axostylus axostyle are connected on the described overburden in operation, described the first axostylus axostyle and described the second axostylus axostyle pass completely through described shell and extend, described the first axostylus axostyle engages described leaf spring in operation, and described the second axostylus axostyle does not engage described leaf spring in operation.

17. the covering system for covering architectural opening according to claim 16 is characterized in that described the first axostylus axostyle engages described leaf spring by engaging described output spool in operation.