DESCRIPTION

This application is based on the Provisional specification filed in relation to New Zealand Patent Application Numbers 728734, 730610, 729277, 732973, 737988 and 733441, the entire contents of which are incorporated herein by reference.

TECHNICAL FIELD

The present invention generally relates to an alternative fan for use in an air conditioning system. The invention may also relate to other applications to move fluids, as well as for use as a turbine for capturing wind energy or other energies.

BACKGROUND ART

Ventilation systems can require elongated or more compact fans, or could usefully use ones that move a fluid in a different direction, especially ones that improve flow rate and pressure. A more compact and efficient turbine that can be tailored to small scale residential use is also very useful in the future. The following prior art discloses some similarities with the current invention.

PCT/IN2010/000761 describes a pump with a continuous conic helical blade within a taper housing. The inlet is from one side and the blade cooperates with the internal surface configuration of the housing to build up pressure.

DE202015100489 describes an axial tower fan whereby air is sucked in below the fan blades from all directions and blown circumferentially outward above the fan blades in all directions.

US patent No 1258986 describes a compressor with continuous spiral rib means on the casing substantially transverse to lobes that define a substantially helical fluid working space between the rotor and the inside wall surface of the casing. The cross sectional area of the fluid working space decreases gradually from one end portion of the casing towards the other end portion of the casing with the objective to build up pressure.

PCT/NZ2016/050088 by the inventor of the current invention, describes a helical blade of opposite chirality that draws in a fluid from a side of the axis and deflects this to an exhaust opening that is longitudinally offset from a centre of the intake opening. The current invention improves certain features in PCT ^' /NZ2016/050088 to increase the flow rate and pressure in various applications.

DISCLOSURE OF THE INVENTION

According to one aspect of the invention there is provided a fan/turbine/pump comprising a rotor rotatable: the rotor comprising an elongate first end portion having a longitudinal axis, at least one pair of blades, the first blade having a root which is substantially helically shaped to the longitudinal axis according to a logarithmic, exponential, power or other sequencing. Preferably the first blade has a flat or concave pressure face.

Preferably at least one blade extends from the first end portion, wherein a first opening is provided substantially and at least axially aligned with substantially helically shaped portions such that the tangent to the blade approaches perpendicular alignment to the axis at a first end of the first end portion and approaches parallel alignment to the axis at the second end of the first end portion.

Preferably the first portion comprises a second opening longitudinally offset from the first opening.

According to a second aspect of the invention there is provided a fan/turbine/pump comprising a rotor, the rotor comprising an elongate first and second substantially helically shaped portion having a longitudinal axis, the second helically shaped portion having an opposite chirality to the first substantially helically shaped portion.

Preferably it comprises a central portion and at least two pairs of blades, wherein at least one first and one second blade extend from the centre of the central portion.

Preferably a first and second blade have a root which is substantially helically shaped to the longitudinal axis with a flat and/or concave pressure face.

Preferably a first opening defining the fluid intake is substantially axially aligned with first end portions of first and second substantially helically shaped portions, such that the tangent to the blades approaches perpendicular alignment to the axis at a centre of the central portion and approaches parallel alignment to the axis near the outer limits of the central portion, and wherein the root is substantially helically shaped to the longitudinal axis according to a logarithmic, exponential, power or other sequencing

Preferably an elongate second end portion of first and second substantially helically shaped portions comprising second opening defining a fluid outlet longitudinally offset from the first opening.

According to a third aspect of the invention, there is provided a fan/turbine/pump comprising a rotor rotatable:

Preferably the radius from axis centre to blade tip and/or surface area of the first blade is proportionally the same or more than the radius from axis centre to blade tip and/or surface area of the second blade.

Preferably the axis diameter increases to accommodate a fan comprising a motor at the first or second end portions and/or to direct flow and/or increase pressure.

Preferably the rate of change of the axis diameter follows a logarithmic or other series such that it approaches perpendicular alignment with the axis at the first end of the first portion or second end of the second portion and approaches parallel alignment with the axis at the second end of the first portion and the first end of the second portion.

Preferably the second end portion is substantially continuous with first end portion.

According to a fourth aspect of the invention, there is provided a fan/turbine/pump comprising a rotor rotatable:

Preferably the blade surface and/or axis include penetrations.

Preferably the first blade conforms to Betz's law of capturing no more than about 60% of the kinetic energy in wind.

According to a fifth aspect of the invention, there is provided a fan/turbine/pump comprising a rotor rotatable: Preferably the second blade consists of serrations and/or is scalloped along the edge of the blade.

According to a sixth aspect of the invention, there is provided a fan/turbine/pump comprising a rotor rotatable:

Preferably the second portion consists of an additional fan at the second end of the second end portion.

According to a seventh aspect of the invention, there is provided a fan, turbine or pump that directs a fluid from one or more ducts connected to the housing of the first end portion towards one or more ducts in the housing of the second end portion.

According to an eighth aspect of the invention, there is provided a fan/turbine or pump comprising a housing which funnels outwards in the first end of the first end portion to increase fluid intake, or funnels inwards or outwards in the second end portion to either increase or release pressure.

According to a ninth aspect of the invention, there is provided at least one fan/turbine/pump housing for heat recovery.

Preferably the heat recovery housing comprises two fans/ turbines/pumps servicing two heat transfer units.

According to a tenth aspect of the invention, there is provided at least one fan/turbine/pump housing.

Preferably the housing consists of a water-proofing manifold to protect the fans/ turbines/pumps within or outside the building envelope.

BRIEF DESCRIPTION OF THE DRAWINGS

Figure 1 is a perspective view of one embodiment of a housing for fan/turbine of the present invention.

Figure 2 is a diagrammatic view of another embodiment of a housing for a heat exchange unit using a fan of the current invention

Figure 3 is a diagram of one embodiment locating the root of the fan/turbine/pump blade of the current invention according to distance and angle along the axis

Figure 4 is a perspective view of another embodiment of a fan/turbine/pump and housing of opposite chirality of the present invention

Figure 5 is a perspective view of another embodiment of a fan/turbine/pump and housing of the present invention

Figure 6 is a perspective view of another embodiment of a fan/turbine/pump of the present invention that defines two distinct areas and functions

Figure 7 is a perspective view of another embodiment of a fan/turbine/pump of opposite chirality of the present invention that defines two distinct areas and functions

Figure 8 is a perspective view of another embodiment of a fan/turbine/pump and housing of the present invention with relatively different radius within these two distinct areas

Figure 9 is a perspective view of another embodiment of a fan/turbine/pump and housing of the present

invention with relatively different radius within these two distinct areas and with additional openings

Figure 10 is a perspective view of another embodiment of a fan/turbine/pump of the present invention with increased free area

Figure 11 is a perspective view of an embodiment of an alternative fan housing feeding multiple smaller ducts from one main duct

Figure 12 is a cross sectional view of a fan/turbine/pump within the first area along the axis

Figure 13 is a perspective view of an embodiment of further alternative fan housing DESCRIPTION OF THE INVENTION

The current invention describes a fan/turbine/pump 1 with substantially helically shaped blade with a fluid intake that is axially aligned to a longitudinal axis. The blade within the fluid intake portion has a flat and/or concave pressure face. The root of one or more blades in fluid intake portion is substantially helically shaped to the longitudinal axis according to a logarithmic, exponential, power or other sequencing such that the tangent to the blade approaches perpendicular alignment to the axis at a first end of fluid intake portion and approaches parallel alignment to the axis at a second end of fluid intake portion. The fluid outlet is longitudinally offset from fluid intake.

In another embodiment of the invention, a second substantially helically shaped portion has an opposite chirality to the first substantially helically shaped portion wherein the tangent to the blade approaches perpendicular alignment to the axis at a centre of fluid intake portion, and approaches parallel alignment to the axis at both ends of fluid intake portion.

Figure 1 is an example of a housing for a fan/turbine/pump 1 of opposite chirality that drives a fluid from all sides of housing portion 2 towards openings 10a and 10b at the ends of housing 7. Air is deflected along helical blades 6a and 6b within housing portion 2 towards outer housing portions 3a and 3b where the fluid is dispersed simultaneously out openings 10a and 10b. Opening(s) 4 in housing portion 2 may be of any size or shape along any side. The longitudinal limits 8a and 8b define a portion 5 for air intake. A diffuser 14 may sometimes be desirable in the application of a fan. Examples of applications may be a vertical fan driven by a motor 9, or a turbine whereby helical blade 6a and 6b are rotated by wind.

Providing openings 10a and 10b at the ends of housing 7 can be useful in many other applications such as in a T intersection of pipes to move a fluid from one main pipe branching off to two pipes or as a hydro or wind generator. In some cases where a cross flow is desirable, openings in housing portions 3a and 3b may be on the sides or it may also be totally open under certain circumstances that are discussed later. The applications can vary widely and not be limited to any one fluid.

Figure 2 is a top view of an example of a heat recovery unit housing. Heat recovery systems generally transfer heating and cooling from the interior air flow to fresh air flow through a heat transfer unit. They require at least two fans, one to pump fresh air and the other stale air. This example shows how two helical fans/turbine/pump 1 of opposite chirality, can increase output and efficiency by simultaneously supplying either fresh or stale air to two heat transfer boxes 12a and 12b, rather than just one.

The fan with opening along the side of housing 7a can draw in air from the exterior for example and the opening along the side of 7b can draw in air from the interior. In some cases all sides of first portion may be open. Fresh air within housing 7a and stale air within 7b can then be driven towards heat transfer units 12a and 12b. Fresh air that is heated or cooled by stale air is then introduced into the interior via openings 13a and 13b while stale air is exhausted from openings 11a and lib. The heat transfer units may be arranged differently or elongated to allow for a counter current flow arrangement which can be more efficient than a cross flow arrangement. Thus the fan/turbine/pump 1 of opposite chirality allows for a spatially compact system supplying larger volumes of a fluid using only two fans to service two heat transfer units. In some cases a simpler half fan/turbine/pump 1 may be beneficial too as described later.

In order to increase the efficiency of the volume of a fluid at the intake, the root of helical blade 6 is plotted along the axis according to an approximation of a logarithmic sequence of numbers, such as the Fibonacci series. In fact, the location of the root of blade 6 can approximate any logarithmic, exponential, power or other sequences, or linear extrapolation of these, in order to achieve the objectives described here. Visually this results initially in an almost perpendicular alignment of the blade to the axis followed by a progressive stretching of helical blade 6 along the axis until it tangentially approaches parallel alignment with the axis. The following is an example of such a series whereby each number in the Fibonacci series is the sum of the previous two numbers as shown below. The right column is an example of a proportionally adjusted Fibonacci series for a 125mm long axis. This marks the distances from the origin along the axis.

Figure 3 is a diagrammatic example how this can be applied with one opening for the fan/pump/turbine 1 on a side of an axis to another opening longitudinally offset from the first opening. Cross sectional axis 15 can be divided into equal sectors of, for example 25.7 degrees. The series of numbers 16 can be the distances from the origin 23 at each angle turn of 25.7 degrees. The spacing of the points along the axis continues to widen until by seven turns of 25.7 degrees around axis 15, the root of the helical blade is facing the opposite direction from its initial location at origin 23, and is spaced along the axis about 50mm from the origin. However, the location at which the blade approaches parallel alignment with the axis is not necessarily required to be facing the opposite direction from its initial location. In this example, this point approximates the transition from intake of a fluid to its expulsion since the tangent to the helical blade is now substantially parallel with the axis and its ability to take in a fluid is much diminished. In fact extending the opening beyond this may create negative resistance to fluid flow and be counter-productive. It can be beneficial for a portion of the fan (for example here between 50mm and 75mm) to be fully enclosed in order to avoid this negative resistance and so as to build pressure.

In summary, helical blade 6 (or 6a or 6b in the case of the fan/pump/turbine 1 of opposite. chirality), is initially tangentially substantially perpendicular to the axis at the intake, the location of the root derived from a sequence such as described above in order to slice into a fluid with the least resistance and maximise fluid intake. In addition to further fluid intake along the axis, the second objective is that the tangential rate of change progressively slows in order to smoothly divert this fluid along the axis. As the tangent to the blade approaches parallel alignment with the axis, its function is then to continue to divert fluid along the axis and sometimes to build up pressure along the blade before expelling this fluid.

Fluid flow can additionally be directed smoothly along the axis at the first end portion by increasing the diameter of the axis in the direction of the first end of the first end portion, anywhere up to and including the blade tip. Likewise, if it is desirable to direct flow outwards at the other end of the axis, for example, the diameter of the axis can increase again towards the second end of the second end portion anywhere up to and including the blade tip. The rate of change of the axis diameter can also follow a logarithmic or other series such that it too approaches perpendicular alignment with the axis at the first end of the first portion or second end of the second portion and approaches parallel alignment with the axis at the second end of the first portion and the first end of the second portion.

A reverse adaptation of a logarithmic series at the blade root can speed up the expulsion of a fluid during the course of rotation of blades 16, or 16a and 16b, at the outer housing portion(s) 3. But other methods to aid the expulsion of a fluid can be utilized that include, for example, transitioning to a substantially conic helical blade 16, or 16a and 16b, one or more serrations 17 along the edge, increasing the number of blades, changing to convex blade, another fan/turbine 26 at the ends of the axis as described in Figure 4 and any other method whereby the objective is to effectively deflect and exhaust a fluid to an outlet longitudinally offset from the inlet. The location of opening 4 in Figure 4 and 5 depends on the angle of the tangent to blade 6 in Figure 5, or 6a and 6b in Figure 4. These blades approach perpendicular alignment to axis 21 at origin 23 in the middle of opening 4 in the case of Figure 4, and at the outer limit 8a in the case of Figure 5. Air is deflected along helical blades 6a and 6b in Figure 4 towards limits 8a and 8b, or along blade 6 in Figure 5 towards limit 8b where its tangent approaches parallel alignment with the axis and where the ability to take in air is greatly reduced. These limits 8a and 8b define portion 5.

In addition to the root of the blade at the intake being defined by a logarithmic or exponential sequence, a flat or concave blade that scoops in the fluid and retains it along helical blades 6 or 6a and 6b is another important factor to increase and retain the volume of fluid drawn in.

In these examples, housings 3, or 3a and 3b, funnel outwards. This can be useful to prevent a choking effect when axis 22 within housings 3 or 3a and/or 3b bulges outwards, for example when motor 9 is located at the end of axis 22. This funnelling can also be useful in certain circumstances to direct exhausted air outwards. Air flow can be maximized further with the aid of secondary fan blades 26 at the ends of housing 7 or other means such as one of more serrations 17 along the edges of blades 16, or 16a and 16b in Figures 4 and 5 within housing portions 3 or 3a and 3b. In other applications, it may be desirable for the fluid to build up more pressure along the axis in which case the housing may funnel inwards. Additionally, the radius and/or surface area of blades 6, or 6a and 6b, can be greater than that of blades 16, or 16a and 16b, which would further increase the volume of fluid intake and increase pressure along blades 16, or 16a and 16b.

Figure 6 is a perspective view of a further embodiment of fan/pump/turbine 1 showing cross sectional planes 18 and 19 that define portion 5. The limits of portion 5 along the axis is defined by 1) the tangential angle of blade 6 at origin plane 18 and cross sectional blade 23 as it approaches perpendicular alignment to the axis, and 2) the tangent to blade 6 at cross-sectional blade 24 and plane 19 as it approaches parallel alignment with axis 21. Within this portion 5 the rate at which the angle of the tangent changes slows down as fluid is deflected along axis 21 and blade 6. By plane 19, the function of blade 16 is now to efficiently exhaust the fluid and/or build pressure before exhausting the fluid. This outlet opening can be anywhere within outer portion 24 defined between planes 19 and 20 and/or at the end of axis 22, depending on the application.

Figure 7 is a perspective view showing how planes 19a and 19b define intake portion 5 when the fan/pump/turbine 1 of Figure 2 continues in opposite chirality at origin plane 18. In this case intake blades 6a and 6b divert the fluid to both ends of the axis where it is expelled along blades 16a and 16b from outer portions 24a and 24b. In this example the substantially perpendicular angle of the tangent at blade 6a or 6b is centred in the middle of intake portion 5. This allows for a streamline entry in the direction of rotation when mechanically driven. In the case of a turbine, the flow rate would increase along concave blades 6a and 6b which would then function like sails causing the axis to rotate.

Figure 8 is a perspective view showing housing 7 with intake portion 5 defined by planes 18 and 19 and outlet portion 24 defined within planes 19 and 20. Fluid intake can be from one side of the axis along intake portion 5, or any proportion of it around intake portion 5. The opening for fluid outlet housing 7 is not shown here but it can also be on the side or the end of the axis depending on whether blade 16 is exhausting a fluid as in a cross-flow, or in an L or T intersection direction of flow.

In this example the radius of cross-sectional helical blade 6 at plane 18 can be greater than the radius of cross- sectional blade 6 at plane 19. Even a small extension of the radius of blade 6 near the origin plane 23 can significantly increase the intake of a fluid. In contrast, extending the radius of axis 21 by the equivalent amount insignificantly influences the free cross-sectional area. In this example, axis 21 bulges at the intake where a motor 9 is located. This can help funnel a fluid along blades 6 and 16 towards the outlet.

The proportions of portions 5 and 24 along the axis can vary according to, for example 1) pressure build up required, 2) relative radius difference of blade portions 6 versus 16, or axis, 3) funnelling of housing, 4) position and proportion of openings in housing, or in some cases no housing, 5) whether blades 6 is continuous or not with blade 16.

Figure 9 is a similar perspective view to Figure 8. In addition to intake portion 5, some intake of fluid can also be obtained through opening(s) 27 in plane 18. In other embodiments plane 18 can be domed to form a cover 29 with blade 6 at plane 18 conforming to cover 29 for example. Opening 27 is not limited to any shape or size. The length of the radius of helical blade 6 is not limited either to the dimensions of housing 8. The objective is to increase the volume of fluid intake and sometimes pressure.

Figure 10 is a perspective view of another embodiment of the fan/turbine. According to Betz's law, no turbine can capture more than about 60% of the kinetic energy in wind. The objective is then to both reduce weight and a proportion of resistance, while preserving sufficient strength. In this example, axis 21 and 22 are understood but not necessarily there. It may be necessary to retain parts of the axis 31 to ensure that the blades do not tend to expand outwards when turning. The blades can also include penetrations 30 to further prevent resistance to air flow and allow some air to flow through. Penetrations 30 are shown here to be vertical slits but they could also, for example, be parallel with the blades, or be any shape.

In order to maximize rotation of a turbine from an outside force, the amount of resistance (created by less 'free area' in the blades) could be more concentrated within intake portion 5 relative to outlet portion 24, although still limited according to Betz's law. Methods to reduce resistance within outlet portion 24 could include a housing or partial housing, and/or reducing the size of helical blade 16 such as conically helically shaped, and/or more free area along blade 16, and/or scalloping the edges of blade 16, and/or removing parts or all of axis 22.

Figure 11 is another embodiment of a fan and housing wherein air is pulled in the sides through multiple smaller ducts and exhausted to one main duct at the end of the axis. In this case ducts 32 around inlet portion 5 are sized and shaped according to intake blade 6 and to the number required to feed one large duct opening at 17. In other embodiments, the bulge in the housing can be instead located at intake portion 5. Also, a second fan 17 at the end of the axis can further increase pressure. Additionally, it may have an opposite chirality to the first fan and housing as in Figure 4. This application can lend itself to efficient power use and the likely reduction of bends and dampers. For example, in an HVAC context, it can efficiently exhaust (or pull in) air from, or to, a number of locations in the building. In some circumstances it may be beneficial for one or more ducts connected to intake portion 5 to supply to one or more ducts in in outlet portion 24.

Figure 12 is a cross-sectional example of three blades with intake portion 5, but this number is not limited to three. Preferably the one or each blade is flat to concave to maximise intake of fluid.

A series of cross flow fans of opposite chirality similar to that in Figure 7 can form an elongated shape that can be usefully used to draw in or exhaust air within the narrow confines of a wall cavity. Naturally the challenge is protecting a fan from moisture and water egress. Figure 13 is an example of an alternative vent extending outside the building envelope to allow for adequate water-proofing to protect such a fan. The vent can stand alone or be connected to the exterior window extrusions between window frame 38 and transom 35. Air is drawn in across the entire vent and supplied to the interior via collector 39, or vice versa.

Good water-proofing in this case is due to vent 37 of manifold 34 being positioned on the outside of the building envelope so that any water that enters vent 37 or splashes against the back inner face of manifold 34 drips back out. It also forces air to flow up an adequate distance before it enters the interior, which again helps to avoid water egress. Additionally a drip seal 33 located above the vent can shed most of the water. Figure 13 shows the use of this type of manifold vent and fan used in combination with a wall-mounted solar collector 39. Alternatively, they can be used for a wall-integrated heat-exchanger as described in Figure 2, or simply used as a passive vent. Its shape is not limited to the example shown here, nor is the location of the vent limited to the one shown. In general, it is a manifold/vent that removes water to the outside of the building envelope in order to water-proof a fan and the interior.

The embodiments of the fan/turbine/pump 1 as described in Figures 1 to 11 vary according to specific applications. For example, the embodiment in Figure 10 may be best suited to a turbine, Figure 4 to a fan, and Figure 9 to a propeller. Variations include 1) the relative width of radius of blade 6 and 16 or axis 21 and 22, 2) the location of openings within intake portion 5 that includes plane 20, or outlet area 24 that includes plane 18, 3) the housing shape if there is a housing, 4) whether or not blades 6 or 16 conform to the inside periphery of the housing, 5) whether the fan/turbine/pump is additionally at opposite chirality, 6) the shape of blade 16 whether concave or convex, 7) the amount of resistance created by free area along the blades and axis and 8) bulges in the axis anywhere up to and including the tip of the blade and/or bulges in the housing. Applications may combine any of these features.

Despite the variations, all multiple applications share certain features which significantly contribute to the efficiency of intake volume and pressure:

• Intake opening 4 is substantially axially aligned to the axis

• Outlet opening within outlet portion 24 is longitudinally offset from intake opening 4

• The outer limits of intake opening 4 are determined by the angle of the tangent to blade 6, as it approaches either tangentially substantially perpendicular or parallel alignment to the axis. In the case of a fan/turbine/pump of opposite chirality, the centre of the opening aligns with the blades of opposite chirality as they approach perpendicular alignment.

• A logarithmic, exponential, power or other sequencing locates the root of blade 6 along the axis of intake portion 5. This visually results in a gradual stretching of the helical blade caused by a decreasing rate of change of the tangential angle to the blade along the axis of intake portion 5.

• Blade 6 is preferably flat or concave along intake area 5.