Fluid dynamic machine with one or more impellers with restrained control mobile blades

A turbomachine, comprising a housing, at least two blade wheels rotatably accommodated by the housing, at least two rotatably arranged blades, which are evenly distributed along a circle of the at least two blade wheels and mounted with an axle parallel to the axis of the corresponding blade wheel. According to the invention, each blade axle is connected to an adjusting element, which can be displaced relative to the shaft of the second blade wheel via a four bar link, which lies in a plane perpendicular to the blade axle and consists mainly of a square arm that is fixed to the axle of the blades, wherein a square arm is articulated to the bottom of the blade wheel, whereas the other end is connected to the end of the first square arm via a connecting axle.

BACKGROUND OF THE INVENTION

Field of the Invention

The present invention refers to a fluid dynamic machine with at least one blade impeller controlled according to the identifying section of claim1.

BRIEF SUMMARY OF THE INVENTION

A machine of this type was described in Italian patent application BZ 2008 A 000 030 of 30 Jul. 2008. In that application, each blade axis is connected through transmission means to a rotatable sleeve on the impeller shaft. These transmission means, still in the same application, comprise a conical wheel integral with the axis of each blade, a conical wheel engaging with the latter, a rod supporting the latter and rotatable supported by the impeller, a conical wheel integrally supported by the rod and a conical wheel integrally supported by the sleeve. In this way, the blades were orientable so as to be covered by the fluid with a high performance in the rotation of impeller about its shaft. It has now been found that the orientation of the individual blades within the fluid could be diversified with the aim of obtaining a variable thrust from or in the fluid regardless of the number of revolutions.

The aim of the present invention therefore to find other solutions for the coordinated orientation of the blades and at the same time to make the structure of the fluid dynamic machine as compact and simple as possible.

This aim is achieved by a fluid dynamic machine with desmodromically guided blade impellers with the characteristics as per claim1.

The orientation movement is obtained by individually connecting each blade axis to a movable organ with respect to the impeller shaft, through an articulated quadrilateral of levers and rods, lying on a perpendicular plane to the blade axis; one arm of the quadrilateral becomes integral with the blade axis, another arm of the quadrilateral is articulated to one end on a plane of the impeller while at the other end it is connected to the blade arm through a connection rod; the arm articulated to the plane of the impeller is desmodromically articulated and sliding through a block-guide pair integral with the shift organ assembly. It is clear that for each blade the same type of quadrilateral of rods and levers and block-guides is repeated individually up to the shift organ. The simultaneous rotational pull of the guides assembled on the respective collar being part of the shift organ, in coincident movement with respect to the movement of the respective impeller, is ensured through a geometry of levers and rods that ensures its free decentring in all directions. It is also clear that the same mechanisms and articulations are repeated in coordination for each impeller.

In a first embodiment, the shift organ comprises a sort of perforated bell which is supported and articulated to the body of the machine through a spherical housing, which enables the swinging in all directions of the bell body; actuator means (two or more) in turn articulated both to the machine body and the bell, are envisaged for shifting the bell itself with oscillating movement having a virtual centre of rotation lying in a central axis of the machine, and so as to be able to eccentrically orient it with a precise and decisive movement. A double collar is slidably arranged on the bell, which transforms the swinging movement into a radial direction lying on an orthogonal plane to the central shaft of the machine. The double collar itself mounts outwards a radial bearing for each impeller, onto which all the respective block-guides of each quadrilateral-blade are mounted.

In a second embodiment, on the other hand, the bell is missing, the collar is not double but single and, whilst keeping its axis parallel to the central axis of the machine, it can undergo a controlled decentring or eccentric shift on a plane orthogonal to the machine axis. The collar towards its inside is complete with a ring-shaped plate, which has four straight slots, orthogonal and equidistant from one another and with respect to the central axis of the collar; in these slots blocks move to support and move the collar itself; each block is in turn supported and moved at its centre by an articulated shaft with a parallel axis to the axis of the collar; said shaft is integral with a lever with an arch movement parallel to the shift plane of the collar and mounted and moved by a shaft having a parallel axis to the central machine axis; said shaft rotates and is supported by a housing integral with the machine structure; in the upper part of the axis a second lever is integral, which is moved in turn by an actuator articulated to the machine structure. Clearly this lever and shaft system is repeated for each slot. In order to optimise the shift of the collar, four actuators are provided with a coordinated movement. The collar in the external part mounts the radial bearings in the same shape and functionality as the first embodiment of the shift organ.

In a third possible embodiment of orientation control, it is possible to provide in the upper part of the shift organ, two large slots at right angles to one another which, slidably guided fixed with the organ, are moved by two actuators articulated to the machine body, along two parallel planes to the shift of the collar. The combined movement of the two slots forms the desired decentring. The shift organ is supported by the actual slot system itself. The machine, as a whole, can be likened to slow turbines with an orthogonal axis to the flow direction of the fluid, and operating with normally two (single or multiple) coaxial impellers (concentric or opposing). The machine is built to produce a thrust, or to intercept and capture the maximum amount of kinetic energy in the flow of fluid (normally water) in which it operates; the peculiarity lies in the possibility to dose the maximum exerted power from zero, regardless of the direction (which is however controllable) and the number of revolutions.

Each impeller consists of a rotating circular body and has a number of blades (two or more) arranged and equidistant on a virtual circumference, whose diameter is taken as primitive diameter of the impeller. On each impeller the blades have an optimal hydrodynamic section and each one can be oriented on its own axis of rotation parallel to the central machine axis, with a fluid and alternate movement in both directions and controlled via a geometry of mechanisms (among the most diverse and common ones technically known) envisaged and built to simultaneously determine the precise angulation position of each blade with respect to the others, to the impeller supporting them, and according to the flow direction of the fluid. All the mechanisms pertain to a single central collar which, appropriately oriented, allows its simultaneous and respective angulation alignment, regardless of the individual rotary movements of the impellers.

The mechanical connections of the movements can be freely chosen according to the appropriate design requirements, as long as the orientation angulations thereof are respected, according to the thrust given or the kinetic energy captured in the fluid, and the position assumed moment by moment with respect to the rotation of its own impeller. The movement of each blade is harmonic with angulated fluid oscillations and without sudden realignments, since they are actuated following a virtual path (parasinusoidal) which can be likened to that of a cam having a variable shape, according to the size and control adjustment, and for the purpose of proportioning the energy given or received in the fluid. The appended drawings are schematic and exemplificative of the mechanisms.

The orientation of each blade is organised so as to make it rotate through a certain angle on its own axis in the two directions and in coordination with the rotation of its own impeller. This is valid simultaneously for all the affected blades on the primitive circumference of the respective impeller.

The two impellers rotate in opposite directions to one another. This introduces various advantages: it contributes to cancelling out the torsional reaction result in the fluid which could tend to make the machine assembly rotate, also with respect to the base supporting it; it centres the result of the various thrust forces of the blades at the axis of rotation enabling the adoption of a single machine instead of two alongside one another rotating in opposite directions; it does not cause shifting effects due to the set direction; it enables shorter blades to be used and therefore more contained structural strain.

The angular rotation speed of the impeller with the greater diameter is normally slower with respect to that with a smaller diameter, in order to maintain more or less the same peripheral speed between the impellers, which is proportional to the affected fluid dynamics. The angular speed of each individual impeller may be independent or coordinated with a precise ratio between the two impellers. According to requirements, it is possible to perform a mechanical choice of a free coupling with two force inputs-outputs, with a differential or proportionally restricted.

The counter rotation of the two impellers implies an angulated dynamic force on the blades which, according to their position and inclination and deviating the affected flow portion, direct the fluid onto the adjacent and subsequent blades between one impeller and another with improved synergy, until the system is crossed completely. The shape of the blades is a hydrodynamic profile, with dimensions that can vary between the two groups of blades per impeller. The dimensions of the machine and the impellers, as well as the dimension, shape and number of blades, are proportional to the envisaged power and the physical characteristics of the fluid and environment in which the work is performed. The construction materials of the machine are therefore chosen following a suitable targeted design.

The machine is usually envisaged for operating with a vertical axis, however, it can be operated with any arrangement and angulation, as long as the axis remains orthogonal to the fluid flow. The advantage with respect to other machines is that in this way it is possible to easily orient the blades only, even when the machine is at full power and operation, without having to orient the entire assembly, with remarkable dimensional and structural advantages on the response speed dynamics during manoeuvres.

By acting on the adjustment and orientation of the blades the fluid dynamic force of any size can be directed, indifferently towards any direction within 360 degrees. The action is always central to the axis, continuous and adjustable from zero to maximum even with the motor with constant revolutions, and free from vibrations thanks to the always constant and harmonic oscillations of the blades (without violent angular realignment returns) during the rotation of the impeller. Harmonic and fluid movements can enable a potential increase in the number of revolutions with respect to other systems.

DETAILED DESCRIPTION OF THE INVENTION

As shown in the figures, reference number1indicates as a whole a fluid dynamic machine according to the invention. The impellers3and4are supported therein during operation. The machine itself can in turn be applied to a stationary or mobile structure according to the allocation of the work.

The machine1has a hollow body2whose extended part contains force input mechanics, the rotation of the impellers and the central alignment organisation of the blades.

In the hollow body2the external impeller3and the internal impeller4are housed concentric to one another. They could also be arranged opposite one another. Each impeller is equipped along a circumference with shafts5supporting blades6. Appropriately the external impeller3is supported rotatably by a bearing arranged in the hollow body2. The internal impeller4, on the other hand, is supported rotatably by a bearing8arranged in the larger impeller so that the smaller impeller4can be rotated in the larger impeller3. Through a bevel gear9the external impeller3is connected with the outside. The ratio is studied according to the angular speed envisaged and in relation to the internal impeller4. The internal impeller4is moved by a shaft14and is connected rotatably through a bevel gear10with the outside. The ratio is studied according to the angular speed envisaged and in relation to the external impeller3.

The bevel gear9is connected with a pinion gear11with force and rotation input of the external impeller3, while the bevel gear10is connected with a pinion gear12with force and rotation input of the internal impeller4. With pinion gears11and12it engages with the gears13of a motor shaft. The ratio with the input pinion gears is designed according to the angular speed envisaged. The combination is important for the rotation direction of the respective impellers. Individual motor inputs can be provided for each impeller, or a differential combination.

The internal impeller4is integral with a central connection shaft14which integrally supports the conical crown of the bevel gear10.

A spherical articulation collar15is arranged on an orientation and movement bell17. It is supported by the body2and allows the oscillation of the bell17in all directions. It does not allow the rotation of the bell on itself, but its oscillation about a central orientation fulcrum16of the control bell17.

The movement bell, articulated in15is controlled through an articulated collar18by actuators35that with their combined movement, cause its precise and well controlled oscillation.

A spherical articulation collar19at the base of the bell17supports respective rings20and21with the interposition of a bearing220integral with the external surface of the collar19.

A guide22is integral respectively with the ring20envisaged for the external impeller6in which a lever of a leverage system25slides connected with each blade6of the external impeller3.

A guide23is integral respectively with the ring21envisaged for the internal impeller4in which a lever of a leverage system26slides connected with each blade6of the internal impeller4.

The guide22(one per blade) of the external impeller3allows the controlled two-directional movement of the leverages24of the blade without interfering with the other directions on the impeller plane.

The guide23(one per blade) of the internal impeller4allows the controlled two-directional movement of the leverages27without interfering with the other directions on the impeller plane.

The leverage system24(each one per blade) for moving the blades of the external impeller3is activated by the respective sliding articulation22controlling the angulation of the blade at each fraction of a revolution of the impeller. It is integral in the fulcrums on the respective impeller.

A leverage system25pulling the bearing collar20is integral in the fulcrums and pulled in turn by the external impeller3.

A leverage system26pulling the bearing collar21is integral in the fulcrums and pulled in turn by the internal impeller4.

A leverage system27(each one per blade) for moving the blades of the internal impeller4is activated by the respective sliding articulation29controlling the angulation of the blade at each fraction of a revolution of the impeller it is integral in the fulcrums on the respective impeller.

A central movement collar28is supported and moved by sliding articulations29that slide in respective slots34and supports the respective rotation bearing collars20and21of the impellers3and4.

Four sliding articulations29support and move the central collar28and are controlled by respective lower levers30.

The four lower movement levers30of the sliding articulation29, as well as moving it, support the central collar28. They are manoeuvred and suspended by a respective shaft31.

Four control and support shafts31of the lower levers30are controlled in rotation by upper levers32and each one is articulated in a support33.

Four upper movement levers32of the shaft31are controlled by an actuator system35. Four sustaining supports and articulations of the lever and shaft assembly30)31)32) are integral with the extended part of the upper body02.

Four sliding slots34of the sliding articulation29are an integral part of the central movement collar28.

The four actuators are arranged at 90 degrees in a plan view. They are articulated onto the body2. Their coordinated movement, by acting on the levers32, allows a precise and controlled movement of the central collar28.

InFIG. 7, by way of example, a leverage system is represented, consisting of a quadrilateral24,27, both for the blade6of the internal impeller4and the external one3. One of the ends of an arm226is articulated to each axis225, whose other end is articulated to one of the ends of a connection rod227whose other end is articulated to one of the ends of a lever228articulated in a pivoted point229to the bottom of the respective impeller3,4. The lever228is rocking-lever articulated to a sliding block230in a guide231integral with the collar ring rotating on the bearing220.

FIG. 10shows the actuator system35in which each actuator351has a piston stem at whose free end one of the ends of an arm352is articulated, whose other end is articulated to pin353rotating in a flange354integral with the machine body. An end of the pin353is articulated to one of the ends of an arm354whose other end is articulated to a pin355housed in a housing356integral with the collar28.

FIG. 11shows a preferred pull embodiment of the collar-slot-block assembly in coincidence with the respective impeller.

In it each impeller3,4is articulated at its bottom to one of the ends of a first elbow lever400at whose other end a first rod401is articulated in turn articulated to a shackle402which is also articulated to a lug403integral with the ring232. A first orientation lever404is also articulated to the shackle402articulated in405to the bottom of the impeller3,4. A second rod404is also articulated to the shackle402in turn also articulated to a second elbow lever407to which one of the ends of a third rod408is articulated, whose other end is articulated to a third elbow lever409to which a fourth rod410is articulated joined to a second shackle411to which a second orientation lever412is also articulated and it is articulated to a second lug413integral with the ring232and to which a fifth rod414is articulated in turn articulated to a fourth elbow lever415which is also articulated to the aforementioned first elbow lever400.