GB2225061A - Vertical-axle wind turbine - Google Patents

Abstract

A vertical-axle wind turbine comprises tubal sliders 11 on a vertical axle 1, horizontal members 9 supported in tubular supports 17, 17' blades 2, 2', equipoises 3, 3' 4, 4' and a rope and reel system 8, 15, 27. Openings 19 near both ends of the tubes 17, 17' accommodate stop-pins 20 to control the turning range of the members 9 up to 90 degrees whereby pairs of blades can oscillate when rotating, to secure maximum wind force. The tubal sliders 11 are linked by chain links 14, 14', and the top and the bottom sliders are connected to the ropes 15, 27' under the control of the reel 8 to facilitate elevating and descending of the bladed rotors. Two alternative counterpoise arrangements are disclosed as well as spring arrangements with the members 17, 17' for absorbing shock and regulating speed under centrifugal force. <IMAGE>

Description

VERTICAL-AXLE WIND TURBINE This invention relates to a wind turbine, which has in view an important objective to secure maximum favorable wind force, but to produce least resistance against headwind current while blades are wheeling about the virtical axle.

Although the vertical-axle wind turbine in my previous invention (patent application Serial No. 8805608, filing date on 3 Sept 1988) can catch about 260 degrees of favorable wind range at optimum leeway and produce least resistance against head wind current within the rest range each rotation by rocking linkage members, and each blade thereon can oscillate sensitively by the help of equipoise devices each comprising a ball in a tube or comprising a counter-lever with a nut equipoise; which devices just suit to low rotational speed for long radius turbine, but not to high rotational speed for short radius turbine because both linkage members and equipoise devices cannot rock and oscillate instantly at high rotational speed when they are mounted on any short radius or small type wind turbine.Besides, the wind turbine in my previous invention provides no security elements against hurricane or typhoon, which then needs to be improved.

Accordingly, the wind turbine in this invention, has an objective to secure not only maximum favorable wind force with least resistance against headwind current, but also high efficiency even at high rotational speed for a small or light wind turbine with additional security device, which comprises elevateable and descendable tubal sliders along the vertical axle, horizontal axes, arc blades, counter-levers with horizontal bar-equipoises, and a reel system.

A specific embodiment of the invention will now be described by way of example with reference characters to the accompanying drawings in which: - Figure 1 shows in perspective, the overall apparatus.

Figure 2 illustrates the rotary motion of blades.

Figure 2A shows the pair blades oscillating within the lower quadrant.

Figure 2B shows the pair blades oscillating within the upper quadrant.

Figure 3 shows in perspective, the tubal slider on the vertical axle.

Figure 3A shows the top view of the alternative horizontal axis at a single tubal slider on the vertical axle.

1 -- vertical axle 2, 2' -- pair blades 3, 3' -- dual "I" counter-levers with horizontal bar-equipoise 4, 4' -- dual "Y" counter-levers 5 -- axial rail 6, 6' -- fixed pulleys 7 -- blade pillow 8 -- reel to connect with the lower end cf control rope 9 -- blade axis 10 -- tubal slider 11 -- axial tube 12 -- sliding groove inside axial tube 13, 13' -- chain pins 14, 14' -- chain links 15 -- control rope 16 -- connecting ear to the upper end 0 Control rope (15) 17, 17' -- horizontal tube to hold blacc ax;;s 18, 18' -- beam of blade 19 -- range control window 20 -- stop pin 21 -- female joint at both ends of blade c-xis 22 -- joint pin 23 -- male joint at the inner end of blade beam 24 -- reinforcing tube to embrace axis joint 25 -- positioning pin of reinforcing tube 26 -- connecting ear at the bottom tubal slider 27 -- tightening rope 28 -- horizontal bar-equipoise 29 -- spring 30 -- dowel pin for spring (29) Referring to Fig. 1, in which, vertical axle (1) is attached with axial rail (5) as a guide of tubal sliders (10 or Fig. 3).

Referring to Figs. 1 & 3, in which, each tubal slider (10) on vertical axle (1) consists of three side-crossing tubes, of which one (11) is vertical and two others (17, 17') are horizontal and side-crossing. On the inner side of each vertical tube (11), there is a vertical guide groove (12) to fit with axial rail (5) to let the crossing-tubal sliders (10) slide up and down along vertical axle (1), but unable to deviate to either tangential direction against axle (1) so that crossing-tubal sliders (10) and vertical axle (1) can keep rotating synchronously.

Referring to Figs. 1, 3 & 3A, in which, horizontal axes (9, 9') each is inserted through each horizontal tube (17, 17') with both ends extending toward both sides of the vertical axle. At each end of horizontal axes (9, 9'), there is a female joint (21) to connect with male joint (23) at the inner end of beam (18, 18') of each blade (2, 2') by inserting joint pins (22) through respective eyes in both joints, which will facilitate loading and removal of individual blades (2, 2') for replacement or security against hurricane or typhoon. Each joint is embraced by reinforcing tube (24) with positioning pin (25) through both the enforcing tube and the joint to reinforce the joint.

Pair blades (2, 2') at both ends of the same axis are displayed to a contained angle of 90 degrees from each other along their axis as shown in Fig. 2A & 2B.

Referring to Figs. 3, in which, near each end of the horizontal tube (17,'17'), there is an open window (19) wider than 90 of radian, and within which stop-pin (20) is inserted into horizontal axis (9) to define the oscillating range of each blade up to 90 degrees within its set quadrant and to stop the horizontal axis from sliding toward either end; thus stop-pins (20) together with the horizontal axis will be stopped by windows (19) when one blade turns to the horizontal position with least resistance against headwind streams, when the opposite blade turns to the vertical position of the same quadrant with optimum leeway to intercept favorable wind force and when either blade tends to slide toward either axial direction.

Referring to Fig. 3A, in which, provided for each horizontal tube (17) is an alternative horizontal axis, which is partitioned into two equal halves and reconnected by -spring (29) and spring (29) is further partitioned and positioned by dowel pin (30) through the central point of both horizontal tube (17) and spring (29) to let spring (29) turn free to either tangential direction, but unable to slide toward either end. When so rang control window (19) is lengthened to provide additional area for the extension of spring (29). Accordingly partitioned spring (29) toward both ends can absorb shocks from gusts and serve as a rotational speed regulator by its tensible length as pulled by variable centrifugal force of both the wind force and the rotary effect.In addition, partitioned spring (29) can also serve as a twisting buffer regardless the blades at both ends of the same axis oscillate synchronously or unsynchronously; namely when both blades oscillate synchronously they can drive each other to promote their oscillating sensitivity, while they oscillate unsynchronously, the spring will provide appropriate buffer for their phase inconsistency to avoid interruption against each other.

Referring to Figs. 1, 2, 2A & 2B, in which, pair horizontal blades (2, 2') on the same axis are slightly arching toward their contained angle. Thus when the up-wind blade stops at the horizontal position of the lower quadrant, it will arch slightly downward to intercept favorable wind force from its outer side by its convex surface and will be depressed downward till the vertical position to continue intercepting favorable wind force for converting it to torque toward its concave direction, and at the same time it will twist the down-wind blade from the vertical position to the horizontal position for releasing resistence from the relative wind; whereas the down-wind blade when stoping at the vertical position of the lower quadrant is arching slightly toward headwind range to intercept headwind force from its inner side by its concave surface and will be elevated to the horizontal position by both the headwind force and the tiwst of the up-wind blade. As both blades together with their beams are slightly arching, their beams will also produce crank effect to heighten the oscillating sensitivity of blades.

Referring to Figs. 1, 2, 2A & 2B, in which, dual "I" counter-levers with horizontal bar-equipoise (3) or dual; Y counter-levers (4) with horizontal bar-equipoises (28) between side forks are fixed to the horizontal beam opposite each blade or opposite the contained angle of both blades for getting appropriate movement of force to produce wide range of neutral equilibrium for each blade within its oscillating quadrant. The merit of dual "I" type counterpoise is taking the advantage of the heavier counter-weight of the horizontal bar to produce greater movement of force than a single counter-lever with nut equipoise may do.Besides, the horizontal bar not only serves as a handle of the blade, but also shortens the oscillating radius of the counter-lever, that will certainly promote the sensitivity of oscillating blade, which is especially essential to the blade oscillating at high rotational speed on a small or light wind tubine.

The merit of dual Y type counterpoise is that the horizontal bars between side-forks of the dual "Y" counterlevers will produce greater effect of movement of force than dual "I" type counterpoise because the dual horizontal bars opposite the contained angle of both blades parallel with the horizontal axis. When the dual horizontal bars oscillate above or under their axis, one bar is strenthening its movement of force, the other will reduce its movement of force before passing across the axis and will alter to strenthen its movement of force right after passing across the axis, which will double the effect of counter-weight to secure greater sensitivity for the oscillating blade than dual I type counterpoise may do.

Referring to Fig. 1, in which, the reel system consists of chain links (14, 14') between the lower and the upper tubal sliders (10), a rope (27) to connect between the lowest tubal slider and blade pillow (7) to adjust and define the height of the lowest tubal slider, and another rope (15) to connect between the top tubal slider and reel (8) under blade pillow (7) through fixed pulley (6) at the top of the vertical axle, along inside or outside of the vertical axle, and another fixed pulley (6) under blade pillow (7) for elevating and descending resspective tubal sliders, which will facilitate loading and removal of respective blades for replacement or security purpose.

For better understanding of the merits and advantages of this invention, detailed description of Fig. 2 & 2A are given below: When pair blades (2, 2') are set substaintially neutral equilibrium at 45 degrees within the lower quadrant, horizontal bar-equipoises t28) between both forks of dual Y counter-levers (4) are standing vertically above horizontal axis (9). When pair blades (2, 2') are mutually oscillating within relative lower quadrants, horizontal bars (28) on both sides of horizontal axis (9) will ride across horizontal axis (9). As a result, when one horizontal bar (28) is strengthen its movement of force, the opposite bar (28) is reducing its movement of force and will alter to strengthen its movement of force as soon as it passes across horizontal axis (9).

The cumulative effect of movement of force provided by dual "Y" type counterpoise will achieve greater oscillating sensitivity of pair blades (2, 2') as single "I" and dual "I" type counterpoises do.

For better understanding of the merits and advantages of this invention, detailed description of Figs. 2 & 2B are given below: When pair blades (2, 2') are set substaintially neutral equilibrium at 45 degrees within the upper quadrant, horizontal bar-equipoises (28) between both forks of dual Y counter-levers (4) are hung vertically under horizontal axis (9). When pair blades (2, 2') are mutually oscillating within relative upper quadrants, horizontal bars (28) under both sides of horizontal axis (9) will pass under horizontal axis (9). As a result, when one horizontal bar (28) is strengthening its movement of force, the opposite bar (28) is reducing its movement of force and will alter to strengthen its movement of force as soon as it passes across horizontal axis (9). The cumulative effect of movement of force provided by dual "Y" type counterpoise will achieve greater oscillating sensitivity of pair blades (2, 2') than single -I counter-lever with nut equipoise and dual "I" with a horizontal bar-counterpoise do.

Above description is only an example, an omission of the tubal sliders and the reel system simply by inserting and fixing horizontal tubes of blade axes through the vertical axle is still applicable to minor wind turbines.

Claims (10)

1. A wind tubine comprising a vertical-axle, tubal sliders along the vertical axle, horizontal axes through horizontal tubes aside tubal sliders, arc blades attaching to both ends of horizontal axes, horizontal bar-equipoises between dual "I" or dual Y counter-levers opposite arc blades or opposite the contained angle of arc blades, and a reel system.

2. A wind tubine as claimed in Claim 1, wherein an axial rail is attached to the vertical axle.

3. A wind tubine as claimed in Claim 1 and Claim 2, wherein the tubal sliders each consists of a vertical tube with an axial guide groove inside to fit with the axial rail along the vertical axle, two horizontal crossing tubes, and chain links between upper and lower tubal sliders.

4. A wind tubine as claimed in Claim 1 and Claim 3, wherein the horizontal crossing tubes each has an open window wider than 90 of radian near both ends to hold the horizontal axis and to control the turning range of the axis within 90 degrees by the stop pin at the horizontal axis inside the window area.

5. A wind tubine as claimed in Claim 1 and Claim 4, wherein each horizontal axis has a joint head at both ends to link with the inner end of the beam of the arc blade and the blades at both ends of the horizontal axis are displayed to a contained angle of 90 degrees and their oscillating range are controlled within set quadrant by the stop pin at its axis inside the window area.

6. A wind tubine as claimed in Claim 1 and Claim 4, wherein an alternative horizontal axis is partitioned in two equal halves and reconnected by a spring and the spring is further partitioned and positioned by a dowel pin through the central point of both the horizontal tube and the spring to serve as a buffer and rotational speed regulator as defined by the stop pins inside the lengthened open window areas near both ends of the horizontal tube.

7. A wind tubine as claimed in Claim 1 and Claim 5, wherein each horizontal axis is provided with dual "I" or counter-levers and horizontal bar-equipoises at appropriate weight opposite either respective blades or the contained angle of both blades for achieving appropriate movement of force.

8. A wind tubine as claimed in Claim 1 and any preceding claim, wherein the reel system consists of tubal sliders, chain links, tightening rope between the bottom tubal slider and the blade pillow, control rope between the top tubal slider and the reel through fixed pulleys.

9. A wind tubine as claimed in Claims 3, 4 and 8, wherein the tubal sliders and the reel system is omittable simply by inserting and fixing horizontal tubes of the axes through the vertical axle.

10. A wind tubine as described herein with reference to Figures 1-3 of the accompanying drawings.