WO2013050818A2 - Volumetric hydraulic motor for pressurized systems also indicated to profit by the pressure in excess of aqueducts and similar for the purpose of producing electrical energy - Google Patents

Volumetric hydraulic motor for pressurized systems also indicated to profit by the pressure in excess of aqueducts and similar for the purpose of producing electrical energy Download PDF

Info

Publication number
WO2013050818A2
WO2013050818A2 PCT/IB2012/000616 IB2012000616W WO2013050818A2 WO 2013050818 A2 WO2013050818 A2 WO 2013050818A2 IB 2012000616 W IB2012000616 W IB 2012000616W WO 2013050818 A2 WO2013050818 A2 WO 2013050818A2
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
vanes
cylinder
volumetric
hydraulic motor
Prior art date
Application number
PCT/IB2012/000616
Other languages
French (fr)
Other versions
WO2013050818A3 (en
Inventor
Silla Martini
Original Assignee
Silla Martini
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Silla Martini filed Critical Silla Martini
Publication of WO2013050818A2 publication Critical patent/WO2013050818A2/en
Publication of WO2013050818A3 publication Critical patent/WO2013050818A3/en

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/34—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members
    • F01C1/344—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F01C1/3441—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F01C1/3442—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0827—Vane tracking; control therefor by mechanical means
    • F01C21/0845—Vane tracking; control therefor by mechanical means comprising elastic means, e.g. springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/106—Stators; Members defining the outer boundaries of the working chamber with a radial surface, e.g. cam rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3441—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F04C2/3442—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/18—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F01C21/183—Arrangements for supercharging the working space
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet

Definitions

  • the present invention relates to an innovative volumetric hydraulic motor designed for the production of mechanical energy and also to take advantage of the pressures in excess of the aqueducts and similar, in order to produce electric power and to perform at the same time also the task of a pressure reducer.
  • the motor or volumetric turbine according to the invention is equipped with a rotor with at least four equally spaced vanes with thrust springs, the rotor of the turbine is characterized by the fact of being coaxial with the inner surface of the containing cylinder and not in the eccentric shape as in the case of a vane pump.
  • vanes of the rotor protrude from their quadrangular seats up to touch the inner surface of the "cylinder" whilst laterally the vanes result in an almost creeping contact with the flat surfaces of the two internal lateral flanges so as to create a movable bulkhead with a centesimal coupling between the outline of the vanes with the corresponding surfaces of containment.
  • the other half of the "cylinder” is instead characterized by an "inclined plane” which protrudes from the inner surface of the "cylinder”, from the point at which "fuses” with the same throughout its height, to continue in the shape of a converging arc until it almost touches after about half the circumference of the "cylinder” the cylindrical surface of the rotor, giving rise at the same time to a bulkhead integral with the "cylinder” for the water which enters under pressure in the "thrust sector" immediately after the bulkhead itself.
  • the four vanes act as movable bulkheads which divide into four parts, the useful space of the cylindrical circular crown and during the rotation follow the inner surface of the "cylinder” entering and exiting from the corresponding quadrangular seats of the rotor, the springs provided guarantee a constant thrust on the vanes which must crawl across half the internal cylindrical surface of the "cylinder” and the other half on the aforementioned "inclined plane” which forces the vanes to return into their seats during the rotation of the rotor.
  • the pressurized water enters the containing cylinder through an opening that leads in the "thrust sector” in the proximity of the said bulkhead, which acts as a barrier to incoming water forcing the same to follow a one way direction, leaving the bulkhead at its "shoulders".
  • an electrical generator which can increase or decrease the load to be input into the network, the increase or decrease of the load depends on the pressure of the water in the water network, which must remain nearly constant, when users close the taps the water pressure increases thus it must be reduced the flow and consequently the number of revolutions of the turbine, to act as a brake to the turbine shaft provides the abovementioned electric generator that increases the load, the whole is regulated by remote control.
  • the turbine according to the invention is able to vary the flow of the water exiting it, braking the shaft obtains a reduction of revolutions and the turbine, being volumetric, also behaves as a pressure reducer.
  • the main purpose of the present invention is to provide a volumetric turbine and/or hydraulic volumetric motor able to vary the number of turns and consequently also the output flow rate of the fluid (water/oil) simply by taking more or less mechanical energy from the driving shaft of the turbine itself.
  • Another very important purpose that the present invention aims is to provide a turbine and/or hydraulic motor that functions in a circuit and/or pressurized system.
  • Yet another very important purpose that the present invention aims is to provide a turbine and/or hydraulic motor in order to exploit the torque of a vane rotor by providing a new principle of operation with a consequent state of the innovative technique which allows the pressurized fluid to cause the rotation of the rotor producing mechanical energy on the motor shaft.
  • Another very important purpose that the present invention aims is to provide a turbine/motor for water/oil which functions by the pressure difference between inlet and outlet of the turbine/motor.
  • the present invention aims is to be able to replace the pressure reducing valves installed on the water distribution systems with the turbines according to the invention that do not dissipate the energy of excess pressure but that take advantage of it in order to produce electricity.
  • a turbine and/or hydraulic motor functioning with water and/or oil under pressure able to transform the energy of pressure in torque or torque on the motor shaft in order to have mechanical energy available for then be converted into electrical energy by means of suitable electric generators, characterized by comprising a cylinder for containing an inner rotor cylindrical and coaxial, with two lateral flanges, bearing and mechanical seal rings for the motor shaft, vanes, minimum four, for the rotor, of springs for the vanes, a pipe for the entry of water under pressure, of three or more channels for the discharge of water, pressure gauges, indicators of flow rate, of a support structure, of an electric generator, of eventual pulleys or variable speed drives for the drive shaft, a tachometer, a control panel and a filter on the inlet pipe for water impurities.
  • Figure 1 shows a three dimensional view of the volumetric hydraulic motor according to the invention, with arrows showing the entry and exit of the oil or water from the appropriate channels suitably positioned on the surface of the "cylinder", at the center we see the motor shaft coaxial to the two lateral flanges fastened with screws to the aforementioned "cylinder", the arrow on the shaft indicates the direction of rotation of the rotor;
  • FIG 2 shows the hydraulic motor sectioned, we see the rotor equipped with four equally spaced vanes pushed by springs, it is also seen that the rotor is coaxial to the inner surface of the "cylinder” for about half the circumference and for the other half instead we note that the inner surface of the "cylinder” is shrinking in arcuate eccentric shape with respect to the rotor and that at the end just touching the surface of the cylindrical rotor giving rise to a bulkhead for the oil/water (fluid) which enters with pressure by the express channel close to of the said bulkhead and leading to the beginning of the "thrust sector", the arrows indicate the pressurized fluid which pushes one of the vanes that is in the useful space of the said "thrust sector", we note well also the three exit channels for the fluid that have been positioned in the exhaust sector and leading into said shrinking surface, the arrows show the exit and entry of the fluid and the one in the center shows the direction of obliged rotation of the rotor;
  • Figure 3) shows the same section of figure 2) with the rotor which has undergone, looking at the figure, a rotation of twenty degrees clockwise and we note well the vane extracted from its quadrangular seat of the rotor until it touches the inner surface of the "cylinder" at the beginning of the "thrust sector", while, looking at figure 2), we see the same vane completely retracted into its quadrangular seat in correspondence of the bulkhead, we notice also the arrows that indicate the entry of water under pressure which surrounds the aforementioned bulkhead just exited and that also indicate the thrust on the previous vane, at the center we see the arrow indicating the direction of rotation in a clockwise direction and the degrees paths, again in Figure 3) we see the fluid that escapes from the three channels of discharge, all the arrows indicate the movement and path of the fluid;
  • Figure 4) shows the same section of figure 2) and 3) with the rotor which has undergone a rotation of forty-five degrees allowing the cited vane, at first completely retracted Fig. 2) and then just extracted Fig. 3) to be in the place of start thrust having completely crossed the outfall of the entrance channel, in fact we see the pressurized water arrows that push the vane while the previous one is not urged by the pressure thrust limiting to "accompany" up to the first discharge channel the water trapped between the vane and the previous one, we repeat that all the arrows indicate the direction of the fluid and the corresponding mechanical movements;
  • FIG 5) illustrates a cross-section in three-dimensional view of the hydraulic motor and/or volumetric turbine according to the patent, at the center is possible to see the rotor with the four quadrangular seats or splits for the housing of the vanes with their own central motor drive shaft which is positioned inside the "cylinder", above the cylinder we notice the seat of the inlet channel for the fluid at the beginning of the "thrust sector", the edge of the "cylinder” we see the two lateral flanges with the OR sealing ring for the flat surfaces of the "cylinder” and in the center the seat of the mechanical seal rings for the motor shaft, at the ends can be seen the flanges with the central seat for the bearings equipped with cracks to protect the bearings from possible losses of the above mentioned mechanical seal rings inserted in the two aforementioned lateral flanges;
  • FIG 6) shows a three-dimensional view of the rotor assembly to one of the two lateral flanges, we note the vanes in exploded views, protruding from the corresponding quadrangular equidistant cracks or seats, to better highlight the thrust springs supplied, to the left we see the "cylinder” where there are particularly seen two of the three outlet channels for the fluid entailing in the camming surface and the inlet channel for the pressurized fluid communicating with the beginning of the inner cylindrical surface of the "cylinder” ("thrust sector") in proximity of the bulkhead resulting from the eccentric processing carried out on the inner surface of the "cylinder”;
  • FIG 7) shows in a three-dimensional view the "cylinder” with the rotor equipped with vanes positioned internally at the same, in this figure the three arrows indicate the bulkhead that skims the outer surface of the rotor to block the passage of water or oil in pressure from the concentric space of the "thrust sector” to that eccentric of the "discharge sector", here we see well also the inlet channel for the pressurized fluid that goes to lead in the vicinity of the said bulkhead in said "thrust sector”;
  • FIG 8) shows the hydraulic motor or hydraulic turbine completely sectioned, in the center can be seen that the springs push the respective vanes in contact with the corresponding points of the cylindrical and eccentric surface of the "cylinder", we note the fixing screws on the flanges and central bearings with the respective mechanical seal rings for the shaft and not that seal the "cylinder" to the two lateral flanges, are clearly seen also the seats of the respective splines on the crankshaft and in particular it can be observed the calibrated coupling of the flat surfaces of the rotor with the equally flat ones of the flanges enclosing it, even the vanes skims, almost touching, the said inner surfaces of said flanges;
  • Figure 9) shows the same section of figure 2), 3) and 4) with the difference that the rotor has eight vanes instead of four, also the output channels are increased in relation to the number of vanes, four as instead of three, with more vanes is obtained a more regular thrust with less pressure loss even if the friction increases the advantage on the power increases with the same proportion to the inlet flow rate and pressure in the hydraulic motor in question, in the figure it's represented the cited motor at the beginning of operation the arrows on the inlet channel show the thrust on the vane which has just passed the useful light of the cited channel, while the vane which follows is in correspondence of the bulkhead completely retracted into its seat on the rotor;
  • Figure 1 0 shows the same section of figure 9), we see that the rotor has rotated a few degrees by venting the vane out from its seat just after the bulkhead invading the start of the useful space of the "thrust sector", the arrows show the water and/or oil under pressure which surrounds the cited vane which continue up to the front vane that thrusted from the fluid provides to transfer the kinetic energy and pressure to the rotor which, through the shaft, turns it into mechanical energy.
  • the hydraulic motor volumetric and/or volumetric hydraulic turbine according to the invention is manifested particularly useful for the production of mechanical and electrical energy and is substantially composed of a containing cylinder ("cylinder") 2) equipped with a channel 3) for the entry of water and/or oil under pressure that from now on we will define only by the name of "fluid", and with multiple output channels for the "fluid” 4), 5) and 6) or as in the variant of Fig.
  • the cylindrical rotor 1 5 results internal to the "cylinder” 2) and coaxial to the same for about half the inner surface 30 and for the other half 31 ) is eccentric, the rotor 1 5) is equipped with at least four cracks or quadrangular seats 7", 8", 9"and 10" for housing the respective vanes 7, 8, 9 and 1 0, the said vanes are pushed by the respective compression springs 1 1 supplied, all calibrated with the same thrust force, the rotor is equipped with a drive shaft 1 6 with a key 1 7, which rotates on bearings 35' which are mounted on the respective annular seats 35 of the two flanges 34, the flanges 34 are assembled to two lateral flanges 31 and 32 with screws 34" and the aforementioned side flanges are in turn assembled to the "cylinder” 2 with screws 42, two special static sealing rings OR 36 guarantee the seal with the flat surfaces of the" cylinder ", in the seats 37, at the center of the afores
  • FIG 5) illustrates in an exploded view the hydraulic motor and/or volumetric turbine and as previously described can be added that the two lateral flanges 32 and 31 are equipped with a shallow 32' with the threaded holes 39 for the housing of the two flanges 34 and 38 with apposite screws staying in their seats 34" and 38", also the two flanges 32 and 31 are assembled to the "cylinder" 2 with apposite screws housed in respective seats 42 and 41 by tightening the screws on the same corresponding threaded holes 2', we note also that the two lateral flanges have a shallow 2" for the penetration of the "cylinder” up to touching the flat surface of the above mentioned shallow 2" so that the ring seal OR 36 appears compressed on the two flat surfaces of the cited "cylinder” to ensure a perfect seal.
  • I S the motor shaft in the form of mechanical energy.
  • a vane pump has a rotor eccentrically positioned to the containing cylinder with the cylindrical surface that almost touches the inner cylindrical surface of the containing cylinder, in almost all models, the rotor has two opposed vanes, the inlet channel is positioned in 5 the vicinity of the point where the rotor almost touches the said inner surface of the aforementioned cylinder containment while the output channel is positioned symmetrically on the opposite side.
  • the novelty consists in that the vanes 7, 8, 9 and 10 are pushed in a portion where the inner cylindrical surface of the containing cylinder 30 is coaxial with the rotor 1 5, so the vane, at first in correspondence to the bulkhead 27 moving it extends until it reaches to touch the said surface 30 and remains in this position from the point 22 to point 23 of the cylindrical surface 30 for all of the "thrust sector" 18' - 1 8 ensuring a perfect contact with the surface 30 and showing to be an excellent "plug" for the fluid under pressure 3', which enters from the channel 3.
  • the secret of this invention is characterized by the fact of having created a "thrust sector or channel", where the fluid 3' is channeled to push an obstacle that obstructs the said channel, in this case the obstacle is the vane that coming out of its seat completely obstructs the channel of propagation of the fluid under pressure, the direction of the said fluid 3' is an obliged direction, the bulkhead 27 adjacent to the inlet channel 3 does not allow fluid to flow in that direction, if the vane were to be pushed a straight channel would behave like a piston, but since the hydraulic motor according to the invention, provides a channel of rectangular cylindrical shape formed by the rotor 1 5 in the form inserted coaxially into the "cylinder” 2 with the inner cylindrical surface having a diameter greater than that of the rotor, the two lateral flanges 32 and 31 hermetically enclosing the flat surfaces of the aforementioned "cylinder” 2 giving origin to a real room or cylindrical circular crown, called “thrust sector” which extends for approximately half the inner circum
  • the hydraulic motor and/or volumetric turbine for oil and/or water under pressure operates as follows: first we must have an inlet pipe for the fluid, for example water, we assume that the water comes from the main pipe of a water line with a constant pressure and that enters from the inlet channel 3 of the turbine (see figure 1 ), 2), 3), and 4), looking at figure 2) we see the water 3' come by pressure from channel 3 flowing onto chamber 1 8', the water 3' cannot go left because it finds the bulkhead 27 which prevents its passage, then it must run right into the cylindrical circular crown called "thrust sector", where it meets the vane 8 that obstructs the passage but the strength of the water 3' pushes the cited vane 8 and it moves it, the arrows 21 show the pressure energy of the water on the vane 8, the vane 8 is housed in a special calibrated quadrangular seat 8" of the rotor 1 5 and moving causes the rotation of the said rotor transmitting the force at the same, the rotor 1 5
  • the hydraulic motor according to the invention is characterized by having a bulkhead 27 easily overcome by the vanes that follow the "inclined plane" 30' for the return and to have a "thrust sector” coaxial with the rotor 1 5 to impede to the vanes, which undergo the push in that stretch, to create friction with the inner cylindrical surface 30 of the "cylinder" 2.
  • the output channels 4, 5 and 6, which then all converge into one are of vital importance, especially the channel 6 that if there was not the engine would clog due to the internal fluid that does not find "the last discharge vent" in a restricting volume like the chamber 1 9', the other channels are positioned to not create impediments to the discharge flow pushed by the vanes, the ideal would be to create a shallow or channel at the center of the "inclined plane" 30' for communicating all three channels for the discharge leaving one for the attachments, the vanes would anyhow fall back in their seats during the rotation in such as they slide at the sides of the above mentioned central shallow, is only a matter of construction, the important is to achieve the purpose of discharging the fluid by removing all structural obstacles.
  • the hydraulic motor is created to operate in a pressurized system, this means that can be maintained under pressure even the discharge fluid and the motor operates however, the important thing is that there is a pressure difference between inlet and outlet, the motor according to the invention works by pressure difference, the incoming one must be clearly higher than that of outgoing one, with equal pressure the hydraulic motor stops.
  • the rotor of the hydraulic motor according to the invention can only turn in one direction, as the outcome vanes after the bulkhead 27 would get stuck bumping against the bulkhead itself if the rotor was running on the contrary, the invention thus has only one direction of rotation in the clockwise or counterclockwise sense depending on how the components have been assembled which are symmetrical except for the "cylinder".
  • the type of water flowing in the pipe is very important, for example, if we have a pipe that delivers water from a reservoir at high altitude you must analyze it to see if it's muddy, sandy, rich or poor in mineral salts, etc., done that you proceed to the choice of building materials best suited to the case and so on each site is and will be different even if it could vary slightly, then in those cases it can be adopted a tolerance on the construction specifications.
  • the hydraulic motor or volumetric turbine displacement of the invention is to be considered a real and proper jewel of technology, from my point of view it should have a name that identifies it, like all machines of the fluid dynamics are listed and explained in formulas or calculations for the dimensioning, the machine according to the invention has a high performance, all depends on the tolerances of the mechanical coupling of the moving elements.
  • the machine according to the invention can be compared to a piston inserted into a cylinder of annular shape, to move the piston we must cap internally the said annular cylinder and enter a fluid between the said cap and the internal piston, one would see the piston make the entire turn around then stop against the cap, in the case of the hydraulic motor according to the invention the said cap results by the 27 and the piston results from one of the vanes of the rotor, but in this case the vane does not stop when it reaches the bulkhead cited above because it passes it reentering in its proper quadrangular seat for then outcome again to be pushed by the fluid.

Abstract

The present industrial invention concerns a vane volumetric turbine which is characterized by having the rotor concentric with the containment cylinder and non-eccentric as in all existing vane pumps. The necessity of having devised the new system is born by the problem of exploiting the pressurized system of aqueducts and the like in order to produce electricity, as is known, the operating pressure in a water network varies continuously in the various time slots as a function of consumption of water by users. In certain aqueducts the pressure is very high and it is necessary to reduce it with suitable pressure reducing devices that dissipate the energy of excess pressure. The volumetric turbine according to the invention exploits the pressure and water flow in a single direction of rotation, the water enters by a dedicated channel in the cylinder of containment of the turbine and is forced to continue channeled between the rotor and the inner surface of the said cylinder. The rotor is equipped with four equally spaced vanes that are housed freely in the corresponding calibrated grooves, suitable calibrated springs provide to push outwards the said vanes which end their run when they encounter the inner surface of the containing cylinder. Two lateral flanges are coupled hermetically to the containing cylinder enclosing the rotor with its side surfaces in a form almost sliding on the surfaces internally flat of the two concentric flanges, which are also equipped with mechanical seal rings and bearings for the rotor shaft. The inner surface of the containing cylinder results for half the circumference coaxial to the cylindrical surface of the rotor and for the other half eccentric, a processing better described hereinafter with the aid of the accompanying figures. The pressurized water enters the turbine through a delivery pipe and flows internally to the same in a quadrangular channel obtained by the coupling of the rotor with the containing cylinder whose width is defined by the two internal surfaces of said side flanges. In the proximity of the inlet water pipe we find, on one side, a bulkhead that almost touches the rotor which prevents the passage of water and on the other the start of the said quadrangular channel. When the turbine is stationary one of the four vanes is always located in the stretch of the quadrangular channel thrust, ready to receive the force of water under pressure to begin the rotation. When the vanes during the rotation meet the eccentric inner surface of the containing cylinder are forced to reenter into their seat up to fully retract after half a revolution of the rotor. The drainage channels are arranged in the eccentric semi-circumference so as to favor the exit of water from the turbine and depend on the number of vanes of which the rotor is fitted.

Description

VOLUMETRIC HYDRAULIC MOTOR FOR PRESSURIZED SYSTEMS ALSO INDICATED TO PROFIT BY THE PRESSURE IN EXCESS OF AQUEDUCTS AND SIMILAR FOR THE PURPOSE OF PRODUCING ELECTRICAL ENERGY
[0001 ] The present invention relates to an innovative volumetric hydraulic motor designed for the production of mechanical energy and also to take advantage of the pressures in excess of the aqueducts and similar, in order to produce electric power and to perform at the same time also the task of a pressure reducer.
[0002] The motor or volumetric turbine according to the invention is equipped with a rotor with at least four equally spaced vanes with thrust springs, the rotor of the turbine is characterized by the fact of being coaxial with the inner surface of the containing cylinder and not in the eccentric shape as in the case of a vane pump.
[0003] The diameter of the rotor results inferior than the diameter of the inner cylindrical surface of the containing cylinder, (which we will call from now on simply "cylinder"), the difference in diameter determines the displacement of the turbine, two lateral flanges, with airtight closing delimit and define the useful space of the said displacement, at the center of the side flanges have been provided the housings for the bearings and the mechanical seal rings for the rotor shaft.
[0004] After the assembling of the two lateral flanges with the "cylinder" is obtained by a watertight cylindrical chamber that contains the cylindrical rotor with its removable vanes supplied, the two flat surfaces of the said rotor result crawling, almost touching the respective flat surfaces of the mentioned flanges which are assembled respecting a centesimal tolerance so as to minimize any leakage of water under pressure inside the "cylinder", nulling or almost the load losses.
[0005] The vanes of the rotor, driven by springs, protrude from their quadrangular seats up to touch the inner surface of the "cylinder" whilst laterally the vanes result in an almost creeping contact with the flat surfaces of the two internal lateral flanges so as to create a movable bulkhead with a centesimal coupling between the outline of the vanes with the corresponding surfaces of containment.
[0006] Between the "cylinder" and the cylindrical rotor, both of equal height, it had been obtained a useful space in the shape of a cylindrical circular crown, for about half the circumference of the "cylinder" the cylindrical surface of the rotor with the inner surface of the aforementioned "cylinder" are coaxial and it's just in this coaxial space that occurs the thrust of the vanes that follow in the rotation, from now on we will call "thrust sector" the said coaxial semi-circumference.
[0007] The other half of the "cylinder" is instead characterized by an "inclined plane" which protrudes from the inner surface of the "cylinder", from the point at which "fuses" with the same throughout its height, to continue in the shape of a converging arc until it almost touches after about half the circumference of the "cylinder" the cylindrical surface of the rotor, giving rise at the same time to a bulkhead integral with the "cylinder" for the water which enters under pressure in the "thrust sector" immediately after the bulkhead itself. [0008] The four vanes act as movable bulkheads which divide into four parts, the useful space of the cylindrical circular crown and during the rotation follow the inner surface of the "cylinder" entering and exiting from the corresponding quadrangular seats of the rotor, the springs provided guarantee a constant thrust on the vanes which must crawl across half the internal cylindrical surface of the "cylinder" and the other half on the aforementioned "inclined plane" which forces the vanes to return into their seats during the rotation of the rotor.
[0009] The pressurized water enters the containing cylinder through an opening that leads in the "thrust sector" in the proximity of the said bulkhead, which acts as a barrier to incoming water forcing the same to follow a one way direction, leaving the bulkhead at its "shoulders".
[001 0] The decreasing part of the bulkhead serves instead as "inclined plane" to make regress progressively the rotor vanes in their seats while crawling on the "inclined plane", which encompasses about half the circumference of the "cylinder".
[001 1 ] In the semi-circumference is where the return of the blades, which from now on we shall call "discharge area", the inner surface of the "cylinder" is eccentric to the rotor and eccentric in this space are provided three points of exit for the water which are spaced and positioned in the "cylinder" in relation to the number of vanes used, except the ones in the vicinity of the bulkhead integral with the "cylinder".
[001 2] During the rotation, immediately after the said bulkhead, one after the other, the said vanes, previously obliged to regress into the corresponding quadrangular seats by the aforementioned "inclined plane", protrude from their quadrangular seats obstructing the passage of water in the "thrust sector", thus receiving a thrust that is proportional to the pressure of the water and to the blocking surface of the vane itself which grazes the aforesaid two lateral flanges.
[001 3] During the thrust phase the vane rests hard on its quadrangular seat of the rotor and it does not occur additional friction burden on the inner surface of the "cylinder" that in that portion is coaxial to the shaft of the rotor itself.
[001 4] After each quarter turn the thrust passes to the next vane while the first is no longer subjected to any strain with exception to the one of having to push the water toward the spillway.
[001 5] After having completed a full turn all four vanes have provided for their own thrust and the amount of water used is equal to the difference between the internal volume of the "cylinder" with that of the cylindrical rotor, thus the number of revolutions of the turbine depends on the ratio between the water flow in the supply pipe with the said volume.
[001 6] The more precise are the internal couplings the higher will be the turbine efficiency, the consumption of the vanes is also very important and it depends on several factors such as: the number of revolutions, the thrust force of the springs on the vanes, the roughness of the surfaces, the materials employed, the purity of water, the working pressure and nevertheless by the accuracy and the tolerances of the mechanical processing considering however that the water under pressure creates a "life-saving bearing" filtering in between the metal components in rotation.
[001 7] To the motor shaft of the turbine is connected an electrical generator which can increase or decrease the load to be input into the network, the increase or decrease of the load depends on the pressure of the water in the water network, which must remain nearly constant, when users close the taps the water pressure increases thus it must be reduced the flow and consequently the number of revolutions of the turbine, to act as a brake to the turbine shaft provides the abovementioned electric generator that increases the load, the whole is regulated by remote control.
[001 8] The turbine according to the invention is able to vary the flow of the water exiting it, braking the shaft obtains a reduction of revolutions and the turbine, being volumetric, also behaves as a pressure reducer.
[001 9] Currently on the market are not found turbines with these requirements, there are conventional turbines as: Pelton, Kaplan, Francis, Banki and others, but none that can be installed in a pressurized circuit and which performs the task of being able to vary the flow rate output, perhaps with a gear volumetric pump or by pistons you can get some results turning them into turbines or hydraulic motors, but no doubt with very low yields and high costs.
[0020] The main purpose of the present invention is to provide a volumetric turbine and/or hydraulic volumetric motor able to vary the number of turns and consequently also the output flow rate of the fluid (water/oil) simply by taking more or less mechanical energy from the driving shaft of the turbine itself.
[0021 ] Another very important purpose that the present invention aims is to provide a turbine and/or hydraulic motor that functions in a circuit and/or pressurized system. [0022] Yet another very important purpose that the present invention aims is to provide a turbine and/or hydraulic motor in order to exploit the torque of a vane rotor by providing a new principle of operation with a consequent state of the innovative technique which allows the pressurized fluid to cause the rotation of the rotor producing mechanical energy on the motor shaft.
[0023] Another very important purpose that the present invention aims is to provide a turbine/motor for water/oil which functions by the pressure difference between inlet and outlet of the turbine/motor.
[0024] Not the least very important purpose that the present invention aims is to be able to replace the pressure reducing valves installed on the water distribution systems with the turbines according to the invention that do not dissipate the energy of excess pressure but that take advantage of it in order to produce electricity.
[0025] Yet another very important purpose that the present invention aims is to be able to realize hydraulic motors with the principle of operation according to the invention to replace the gear or pistons motors in those cases where the application results advantageous.
[0026] These and other objects are achieved with a turbine and/or hydraulic motor functioning with water and/or oil under pressure able to transform the energy of pressure in torque or torque on the motor shaft in order to have mechanical energy available for then be converted into electrical energy by means of suitable electric generators, characterized by comprising a cylinder for containing an inner rotor cylindrical and coaxial, with two lateral flanges, bearing and mechanical seal rings for the motor shaft, vanes, minimum four, for the rotor, of springs for the vanes, a pipe for the entry of water under pressure, of three or more channels for the discharge of water, pressure gauges, indicators of flow rate, of a support structure, of an electric generator, of eventual pulleys or variable speed drives for the drive shaft, a tachometer, a control panel and a filter on the inlet pipe for water impurities.
[0027] Further characteristics and advantages will become apparent from the detailed description of a particular but not exclusive embodiment, illustrated only by way of non-limitative example in the accompanying figures in which:
[0028] Figure 1 ) shows a three dimensional view of the volumetric hydraulic motor according to the invention, with arrows showing the entry and exit of the oil or water from the appropriate channels suitably positioned on the surface of the "cylinder", at the center we see the motor shaft coaxial to the two lateral flanges fastened with screws to the aforementioned "cylinder", the arrow on the shaft indicates the direction of rotation of the rotor;
[0029] Figure 2) shows the hydraulic motor sectioned, we see the rotor equipped with four equally spaced vanes pushed by springs, it is also seen that the rotor is coaxial to the inner surface of the "cylinder" for about half the circumference and for the other half instead we note that the inner surface of the "cylinder" is shrinking in arcuate eccentric shape with respect to the rotor and that at the end just touching the surface of the cylindrical rotor giving rise to a bulkhead for the oil/water (fluid) which enters with pressure by the express channel close to of the said bulkhead and leading to the beginning of the "thrust sector", the arrows indicate the pressurized fluid which pushes one of the vanes that is in the useful space of the said "thrust sector", we note well also the three exit channels for the fluid that have been positioned in the exhaust sector and leading into said shrinking surface, the arrows show the exit and entry of the fluid and the one in the center shows the direction of obliged rotation of the rotor;
[0030] Figure 3) shows the same section of figure 2) with the rotor which has undergone, looking at the figure, a rotation of twenty degrees clockwise and we note well the vane extracted from its quadrangular seat of the rotor until it touches the inner surface of the "cylinder" at the beginning of the "thrust sector", while, looking at figure 2), we see the same vane completely retracted into its quadrangular seat in correspondence of the bulkhead, we notice also the arrows that indicate the entry of water under pressure which surrounds the aforementioned bulkhead just exited and that also indicate the thrust on the previous vane, at the center we see the arrow indicating the direction of rotation in a clockwise direction and the degrees paths, again in Figure 3) we see the fluid that escapes from the three channels of discharge, all the arrows indicate the movement and path of the fluid;
[0031 ] Figure 4) shows the same section of figure 2) and 3) with the rotor which has undergone a rotation of forty-five degrees allowing the cited vane, at first completely retracted Fig. 2) and then just extracted Fig. 3) to be in the place of start thrust having completely crossed the outfall of the entrance channel, in fact we see the pressurized water arrows that push the vane while the previous one is not urged by the pressure thrust limiting to "accompany" up to the first discharge channel the water trapped between the vane and the previous one, we repeat that all the arrows indicate the direction of the fluid and the corresponding mechanical movements;
[0032] Figure 5) illustrates a cross-section in three-dimensional view of the hydraulic motor and/or volumetric turbine according to the patent, at the center is possible to see the rotor with the four quadrangular seats or splits for the housing of the vanes with their own central motor drive shaft which is positioned inside the "cylinder", above the cylinder we notice the seat of the inlet channel for the fluid at the beginning of the "thrust sector", the edge of the "cylinder" we see the two lateral flanges with the OR sealing ring for the flat surfaces of the "cylinder" and in the center the seat of the mechanical seal rings for the motor shaft, at the ends can be seen the flanges with the central seat for the bearings equipped with cracks to protect the bearings from possible losses of the above mentioned mechanical seal rings inserted in the two aforementioned lateral flanges;
[0033] Figure 6) shows a three-dimensional view of the rotor assembly to one of the two lateral flanges, we note the vanes in exploded views, protruding from the corresponding quadrangular equidistant cracks or seats, to better highlight the thrust springs supplied, to the left we see the "cylinder" where there are particularly seen two of the three outlet channels for the fluid entailing in the camming surface and the inlet channel for the pressurized fluid communicating with the beginning of the inner cylindrical surface of the "cylinder" ("thrust sector") in proximity of the bulkhead resulting from the eccentric processing carried out on the inner surface of the "cylinder";
[0034] Figure 7) shows in a three-dimensional view the "cylinder" with the rotor equipped with vanes positioned internally at the same, in this figure the three arrows indicate the bulkhead that skims the outer surface of the rotor to block the passage of water or oil in pressure from the concentric space of the "thrust sector" to that eccentric of the "discharge sector", here we see well also the inlet channel for the pressurized fluid that goes to lead in the vicinity of the said bulkhead in said "thrust sector";
[0035] Figure 8) shows the hydraulic motor or hydraulic turbine completely sectioned, in the center can be seen that the springs push the respective vanes in contact with the corresponding points of the cylindrical and eccentric surface of the "cylinder", we note the fixing screws on the flanges and central bearings with the respective mechanical seal rings for the shaft and not that seal the "cylinder" to the two lateral flanges, are clearly seen also the seats of the respective splines on the crankshaft and in particular it can be observed the calibrated coupling of the flat surfaces of the rotor with the equally flat ones of the flanges enclosing it, even the vanes skims, almost touching, the said inner surfaces of said flanges;
[0036] Figure 9) shows the same section of figure 2), 3) and 4) with the difference that the rotor has eight vanes instead of four, also the output channels are increased in relation to the number of vanes, four as instead of three, with more vanes is obtained a more regular thrust with less pressure loss even if the friction increases the advantage on the power increases with the same proportion to the inlet flow rate and pressure in the hydraulic motor in question, in the figure it's represented the cited motor at the beginning of operation the arrows on the inlet channel show the thrust on the vane which has just passed the useful light of the cited channel, while the vane which follows is in correspondence of the bulkhead completely retracted into its seat on the rotor;
[0037] Figure 1 0) shows the same section of figure 9), we see that the rotor has rotated a few degrees by venting the vane out from its seat just after the bulkhead invading the start of the useful space of the "thrust sector", the arrows show the water and/or oil under pressure which surrounds the cited vane which continue up to the front vane that thrusted from the fluid provides to transfer the kinetic energy and pressure to the rotor which, through the shaft, turns it into mechanical energy.
[0038] With reference to said figures, the hydraulic motor volumetric and/or volumetric hydraulic turbine according to the invention, globally indicated by the number 1 ), is manifested particularly useful for the production of mechanical and electrical energy and is substantially composed of a containing cylinder ("cylinder") 2) equipped with a channel 3) for the entry of water and/or oil under pressure that from now on we will define only by the name of "fluid", and with multiple output channels for the "fluid" 4), 5) and 6) or as in the variant of Fig. 9) and 10) with the channels 4x, 5x, 6x and 7x, the cylindrical rotor 1 5 results internal to the "cylinder" 2) and coaxial to the same for about half the inner surface 30 and for the other half 31 ) is eccentric, the rotor 1 5) is equipped with at least four cracks or quadrangular seats 7", 8", 9"and 10" for housing the respective vanes 7, 8, 9 and 1 0, the said vanes are pushed by the respective compression springs 1 1 supplied, all calibrated with the same thrust force, the rotor is equipped with a drive shaft 1 6 with a key 1 7, which rotates on bearings 35' which are mounted on the respective annular seats 35 of the two flanges 34, the flanges 34 are assembled to two lateral flanges 31 and 32 with screws 34" and the aforementioned side flanges are in turn assembled to the "cylinder" 2 with screws 42, two special static sealing rings OR 36 guarantee the seal with the flat surfaces of the" cylinder ", in the seats 37, at the center of the aforesaid two flanges 31 and 32, have been assembled two mechanical seal rings 37' for the seal with the shaft 1 6, two seger 1 6' in external contact with the above- mentioned bearings 35' of the aforementioned shaft 1 6 ensure the positioning of the central rotor 1 5.
[0039] In Figure 1 ) it's shown, in a three-dimensional view, the volumetric hydraulic motor or volumetric turbine according to the invention, is noted the inlet channel 3, the arrow indicates the fluid under pressure 3' which enters into the "cylinder" 2, the channels 4, 5 and 6 are those of exit and the arrows 4', 5' and 6' show the direction of the fluid which escapes from the cylinder 2, are seen the two lateral flanges 31 and 32 assembled to the "cylinder" with apposite screws, at the center we notice the drive shaft 1 6 protruding from the two side bearings 35' that are integral with the two flanges 34 that are also assembled with screws to the above flanges 31 and 32, also noted are the splits 34' of the flanges 34 which serve to discharge eventual fluid losses without compromising the above-mentioned bearings 35' after the exhaustion of the interior mechanical seal rings which act on the motor shaft 1 6. [0040] In Figure 2) it is possible to see the section of the hydraulic motor or volumetric turbine 1 ), we note well the inner rotor 1 5 with its cylindrical surface coaxial to about half of the inner cylindrical surface 30 of the "cylinder" 2 with the center mating to that of rotor 1 5 identified by the numeral 28, the aforementioned cylindrical surface 30 extends for about one hundred and eighty degrees from the point 22 and ending at point 23, this arc of a concentric circle with the front cylindrical surface of said rotor 1 5 gives rise to a circular semi-crown and was defined as the "thrust sector" 1 8' and 1 8, approximately the other half of the inner surface 30' of the "cylinder" 2, results eccentric with respect to the rotor 1 5, with the center detectable by the number 29, an arc of circle that runs from point 23 and ends at point 1 4 skimming by almost touching the cylindrical surface of the rotor 1 5, the useful volume 1 9 and 1 9' defined by the aforementioned arc of a circle 30' with the front cylindrical surface of the rotor 1 5 has been called "discharge sector" , the bulkhead 27 which develops from the point 14 to point 22 for the entire height of the "cylinder" prevents or almost to the pressurized fluid to pass directly in the aforementioned "discharge sector", thus, the pressurized fluid that enters from the channel 3 is forced to propagate in the "thrust sector" starting from the compression chamber 1 8' and then go to 1 8 pushing the vane 8 with the force of the pressure, the arrows 21 show the thrust exerted by the fluid on the vane 8, the arrows 3' show the route of the said fluid entering from the channel 3 and then escaping from the drainage channels 4, 5 and 6 connected with the "discharge sector", the arrows 3", 4', 5' and 6' show the path and the outputs of the depressurized fluid. [0041 ] Still in Figure 2) we see the vanes 7, 8, 9 and 10 driven by the respective springs 1 1 to touch the corresponding inner surface of the "cylinder" 2 which, results for one half cylindrical 30 and for the other half eccentric 30' with respect to the rotor 1 5, during the rotation of the rotor 1 5 the mentioned vanes go in and out of the corresponding quadrangular seats 7", 8", 9" and 10", better visible in Figures 5), 6) and 7), following the profile of the different inner surfaces of the "cylinder" 2.
[0042] Again in Figure 2) we notice the vane 7 below the bulkhead 27, the cited vane is completely retracted into its quadrangular seat 7" of the rotor 1 5, the spring/s 1 1 resulting compressed and the arrow 7' indicates the direction of the thrust given by the aforementioned spring on the vane which stops in contact with the final part of the surface 30' in correspondence of the bulkhead 27, the arrow 24 indicates the entrance of the fluid in channel 1 2 which connects the space below the vane 7 where the springs 1 1 are housed with the outside, the pressure of the fluid entering from the channel 1 2 further pushes the vane against the inner surface of the "cylinder" in step 14, while the fluid 3' propagates in the compression chamber 1 8' pushing the vane 8, the arrows 21 show the direction of force, arrow 3" shows that the fluid is led up to the outputs from the vane 8 that pushes it into the "thrust sector" 18.
[0043] In Figure 3) we find the same section of figure 2) and we note that in the center the rotor 1 5 has undergone a rotation of twenty degrees in a clockwise direction (looking at the figure), the vane 7, pushed by the spring 1 1 and by the fluid 24 has outcome from its quadrangular seat stopping against the cylindrical surface 30, we notice the fluid 3' that envelops it but which keeps passing pushing the vane 8, the vane 7 in this position is not urged by the fluid which surrounds it until it goes beyond the outlet of the input channel 3.
[0044] In Figure 4) we see the same section of figure 2) and 3), at the center we see that the motor shaft has undergone a rotation of forty-five degrees with respect to that in Figure 2), we also notice that the vane 7 has passed the outlet of the inlet channel 3, we see the arrows 3' that indicate the fluid pressure in chamber 1 8' against the abovementioned vane 7, the arrows 21 which acted first (see fig. 3) on the vane 8 now are acting on the 7 and the fluid 3' in the "thrust sector" 1 8 loses pressure and is "accompanied" the first output channel 4 from the blade 8.
[0045] Still in Figure 4) we see the three output channels 4), 5) and 6) which must all converge into a single channel (not shown) to balance the output pressure, especially if they have to serve a mains water supply with a constant pressure of at least two atmospheres, when the cited three channels are combined into a single channel the useful space within the "discharge sector" 19 and 19' will be completely invaded by the fluid with a lower pressure than that of entry, the pressure difference will allow to the hydraulic motor and/or volumetric turbine to operate with a power proportional to the aforementioned pressure difference.
[0046] Always looking at the figure 4) and observing the vanes 9 and 10 we note that the same reenter within their quadrangular seat 9" and 10", the arrows 9' and 10' indicate precisely the cited reenter that is clearly caused by the sliding contact with the eccentric surface 30' of the "cylinder" during the rotation of the rotor 1 5, the arrow 16' indicates the direction of rotation in a clockwise direction, looking at the figure, we see also arrows on the channels 1 2 of the aforementioned vanes that indicate the outcome of fluid from the chamber below the vanes 9 and 1 0 to allow the return, of course the above-mentioned chambers that house the springs 1 1 are enclosed by the two lateral flanges 31 and 32.
[0047] Figure 5) illustrates in an exploded view the hydraulic motor and/or volumetric turbine and as previously described can be added that the two lateral flanges 32 and 31 are equipped with a shallow 32' with the threaded holes 39 for the housing of the two flanges 34 and 38 with apposite screws staying in their seats 34" and 38", also the two flanges 32 and 31 are assembled to the "cylinder" 2 with apposite screws housed in respective seats 42 and 41 by tightening the screws on the same corresponding threaded holes 2', we note also that the two lateral flanges have a shallow 2" for the penetration of the "cylinder" up to touching the flat surface of the above mentioned shallow 2" so that the ring seal OR 36 appears compressed on the two flat surfaces of the cited "cylinder" to ensure a perfect seal.
[0048] Still in figure 5) we see the holes 40 on the side flanges 32 and 31 which are of a diameter just above that of the motor shaft 1 6, internally to the aforementioned hole 40 has been obtained the seat 37 for the housing of the mechanical seal ring which ensures the seal with the shaft 1 6, if the above-mentioned mechanical seal ring should deteriorate over the time the symmetrical cracks 34' and 38' formed in the two flanges 34 and 38 would let go down by gravity the above-mentioned losses without touching the two bearings housed externally in the seats 35. [0049] In Figure 6) we see well the rotor 1 5 assembled on the motor shaft 1 6 both coaxial to the side flange 31 ), this figure serves to well highlight the removable vanes 7, 8, 9 and 1 0 with the compression springs 1 1 provided, as well as the corresponding calibrated quadrangular seats 7", 8", 9 "and 1 0", in two of the cited quadrangular seats is possible to see the channel 1 2 which extends up to the base of the respective seats 7" and 8", as already said the channel 1 2 serves for the passage of fluid to compensate for the change in volume under the vanes during their displacement and also to increase the force of the springs when the said vanes are located in the thrust chamber at the beginning of the "thrust sector".
[0050] Still in Figure 6) we see the "cylinder" 2 on which are marked by arrows points of arrival and departure of the two inner surfaces of the "cylinder" 2, the point 1 4 indicates the end of the eccentric surface 30' and the point 22 indicates the beginning of the cylindrical surface 30 while the point 23 indicates where the two aforementioned surfaces are "fused" for an homogeneous continuation, the threads 44, 45 and 46 (not visible) serve for the winding of the corresponding output channels for the fluid , while the thread 43 which leads to the beginning of the "thrust sector" is for the winding of the inlet channel for the fluid under pressure, the threaded holes 2', present in both flat faces of the "cylinder" 2 serve for the screws housed in the corresponding through holes 41 present in both lateral flanges 31 and 32.
[0051 ] In Figure 7) we see the rotor 1 5 with the vanes 7, 8, 9 and 1 0 inserted in the corresponding calibrated quadrangular seats 7", 8", 9" and 1 0", the arrows 9 'and 10' indicate that the vanes 9 and 10 are returning in their respective quadrangular seats while crawling on the eccentric surface 30' of the "cylinder" starting from the passage on the point 23 to end completely reentered getting to the point 14 in correspondence of the bulkhead 27.
[0052] Still in Figure 7) we notice the bulkhead 27 adjacent the threaded opening 43 and it can be deduced easily enough that the fluid can only follow the direction 18', 1 8 in the "thrust sector" occupied in turn by the said vanes which follow one another during the rotation of the rotor 1 5, thereby imposing them the force of pressure in order to obtain a nearly constant thrust which is transmitted to the rotor 1 5 giving rise to a uniform circular motion if the fluid 3' incoming possesses a constant pressure and flow rate, even in the output however there must be a constant pressure.
[0053] In Figure 8) we see the longitudinal section of the hydraulic motor or volumetric turbine according to the invention, we note the "pack" assembly of the side flanges 32 and 31 by screws on the respective threaded holes 2' of the "cylinder" 2 inserted into the corresponding through holes 42 and 41 of the aforementioned side flanges, also the two flanges 34 and 38 with bearings 35 for the shaft 1 6 are assembled to the corresponding side flanges 32 and 31 by screws housed in the through holes 34 "and 38" and then screwed in the corresponding threaded holes 2' of the "cylinder" 2, in this figure it's the well seen the "cylinder" 2 which penetrates up to touch on the two shallows 2" of the side flanges 32 and 31 delimiting with precision the "thrust sector" and the "discharge sector" formed with the cylindrical rotor 1 5 provided with removable vanes 7, 8, 9 and 1 0 pushed by springs 1 1 , also the hermetic seal is assured by the two sealing rings OR 36 with the flat surfaces of the "cylinder".
[0054] Still in figure 8) we see the vane 7 and the contra-posed vane 9 which perfectly close the passage of fluid, the calibrated couplings increase the efficiency of the hydraulic motor according to the invention, we notice the space 9" below the vane 9 where are housed the springs 1 1 , also the seat 1 7 of the key for the rotor 1 5 is clearly visible in the center of the drive shaft 1 6, we notice the two mechanical seal rings 37' housed in the corresponding seats of the side flanges 32 and 31 , also the flat surfaces of the rotor 1 5 result sliding, almost touching, the respective flat surfaces of said lateral flanges to prevent as much as possible the passage of fluid under pressure, the more accurate the mentioned coupling and the smaller the pressure drop, also the vanes have to be calibrated for the same reason, the vanes are constructed of a material that is not subject to seizure such as Teflon, bronze, carbon, ceramics and other specific alloys (known materials).
[0055] In Figure 9) we find the same section of figure 2), 3) and 4) with the variation that the inner rotor has eight vanes, increasing the number of the vanes undoubtedly reduces the load losses, and even if frictions increase due to rubbing of the aforementioned vane with the inner surface of the "cylinder" for half concentric and half eccentric relative to the rotor there is always an advantage, by increasing the number of the vanes is reduced in proportion also the useful space on the compression chamber 1 8' reducing accordingly all the lengths of the couplings and then consequently also the load losses are reduced by having fewer dispersions of pressurized fluid which seeps from the couplings in rotary movement.
[0056] Still in Figure 9) we see that the drainage channels 4x, 5x, 6x and 7x are increased in ratio to the number of the vanes, four instead of three, this increase is necessary because the usable space between a vane and the other is progressively reduced during the rotation passing from the space 1 9 at 1 9' and then to 1 9" to finish to 1 9'" and since the fluid is not compressible if there are no adequate discharges the hydraulic motor is blocked by the fluid itself.
[0057] Always in figure 9) we see the arrows 3'x of the fluid under pressure which enters from the channel 3x, we notice the vane 7 in correspondence of the bulkhead, the arrow 7' indicates that the said vane is pushed by the spring 1 1 and pressurized fluid from the 3'x that passes from the channel 1 2 adjacent to the vane reaching the bottom of the same, the fluid pushes against the bulkhead and against the vane 8, the arrows 21 show that the vane yields under the pressure of the fluid under pressure leaning hard on the opposite surface of its calibrated quadrangular seat yielding the strength received at the rotor, the arrow 1 3 indicates the point of support of the vane, as we see on the vane 8 there isn't the arrow indicating the force of spring 1 1 , this means that the cited vane is "nailed" in that position under the strong thrust of the fluid 3'x, thus the friction of the vane 8 with the cylindrical surface 30 of the "cylinder" does not increase with the increasing pressure of the fluid so allowing the rotation of the rotor, all the vanes except that which is subject to thrust, in this case the vane 8, crawls on the surface 30 and 30' on the same the arrow indicates that the friction is due to the thrust force of the spring 1 1 , then the friction during the rotation is proportional to the force of thrust of the spring.
[0058] In Figure 1 0) we find the same section of figure 9) with the 5 difference caused by the fact that the rotor is rotated a few degrees in a clockwise direction looking at the figure, a small rotation to allow the vane 7, at first compressed in correspondence of the bulkhead, of escaping from its calibrated quadrangular seat, in this figure we want to show the fluid under pressure 3'x which surrounds the cited vane and which continues the
10 journey into the chamber 1 8' by pushing on the vane 8 until the vane 7 does not cross the outlet of the channel 3x, after having passed the outlet of the cited vane 7 will behave exactly as the vane 8 in the position shown in Figure 9), and so on a vane after another will all be pushed by the fluid under pressure yielding the force received to the rotor and consequently to
I S the motor shaft in the form of mechanical energy.
[0059] The operation of the invention is simple and the state of technology used allows to understand already in theory that everything fits and works and that the principle of operation is devised to be considered new, although at first sight the hydraulic motor according to the invention 0 looks like a vane pump.
[0060] Let's assume that a vane pump has a rotor eccentrically positioned to the containing cylinder with the cylindrical surface that almost touches the inner cylindrical surface of the containing cylinder, in almost all models, the rotor has two opposed vanes, the inlet channel is positioned in 5 the vicinity of the point where the rotor almost touches the said inner surface of the aforementioned cylinder containment while the output channel is positioned symmetrically on the opposite side.
[0061 ] If one were to reverse the role of the vane pump to transform it into hydraulic motor it should enter the fluid under pressure from the suction channel but will not occur any results in that the vane that is emerging from its seat must adhere to the inner surface of the containment cylinder that is divergent, with the pressure of the fluid the vane cannot escape from its quadrangular seat in that the friction that would be created with the surfaces of the same calibrated seat will be greater than the thrust force of the spring below the vane, then the fluid would pass between the vane and the inner cylindrical surface of the containing cylinder without pushing on the vane, even supposing to increase the spring force to make adhere the vane on said cylindrical surface there would be a fluctuating push running from a minimum to a maximum where the eccentric space is greater for restart after a half turn from the minimum of before to return to the maximum and so on, but this is not possible for the fact explained before that the vane cannot escape and therefore cannot adhere acting as a cap to the fluid under pressure.
[0062] These and other findings, reasoning on the principle of operation of a vane pump, lead to deduce that the system cannot function, in the case of the hydraulic motor according to the invention instead the problems described above do not exist as the principle of operation is changed, the novelty consists in that the vanes 7, 8, 9 and 10 are pushed in a portion where the inner cylindrical surface of the containing cylinder 30 is coaxial with the rotor 1 5, so the vane, at first in correspondence to the bulkhead 27 moving it extends until it reaches to touch the said surface 30 and remains in this position from the point 22 to point 23 of the cylindrical surface 30 for all of the "thrust sector" 18' - 1 8 ensuring a perfect contact with the surface 30 and showing to be an excellent "plug" for the fluid under pressure 3', which enters from the channel 3.
[0063] No hydraulic machine on the market today uses a similar principle, one must consider that the motor or turbine according to the invention produces energy by exploiting the pressure and flow of a fluid such as water or oil (the most common), the hydraulic motor behaves as a piston with no return, a piston infinitely long, in fact, the principle is the same, stopper on one side to vent the other, a piston is cylindrical in shape in order to have an annular seal with an absolute perfection, in the case of the motor according to the invention is not possible to have a propagation channel of circular shape as the cylinder for the piston but necessarily must be of square or rectangular shape, the vane, in this case replaces the said piston, transferring to the rotor the energy or force of pressure supplied by the pressurized fluid, the route is not linear but circular and the vane after each complete revolution done from the rotor is pushed for a section path of circular crown related to the number of vanes of which the rotor is fitted.
[0064] To prevent to the fluid under pressure 3' to propagate in both directions around the rotor 1 5 has been created a bulkhead 27 which develops on the other side with an eccentric surface 30' with respect to the rotor 1 5 in motion to force all of the aforementioned vane to return to their quadrangular seats during the rotation of the said rotor 1 5 and then escape from their said seat after having passed the point 1 4 of the cited bulkhead 27, pushed by the spring 1 1 below and from the fluid 3' under pressure which enters the channel 1 2 adjacent to the vanes themselves.
[0065 ] The secret of this invention is characterized by the fact of having created a "thrust sector or channel", where the fluid 3' is channeled to push an obstacle that obstructs the said channel, in this case the obstacle is the vane that coming out of its seat completely obstructs the channel of propagation of the fluid under pressure, the direction of the said fluid 3' is an obliged direction, the bulkhead 27 adjacent to the inlet channel 3 does not allow fluid to flow in that direction, if the vane were to be pushed a straight channel would behave like a piston, but since the hydraulic motor according to the invention, provides a channel of rectangular cylindrical shape formed by the rotor 1 5 in the form inserted coaxially into the "cylinder" 2 with the inner cylindrical surface having a diameter greater than that of the rotor, the two lateral flanges 32 and 31 hermetically enclosing the flat surfaces of the aforementioned "cylinder" 2 giving origin to a real room or cylindrical circular crown, called "thrust sector" which extends for approximately half the inner circumference of "cylinder" 2, while the other half circumference is called "discharge sector", the quadrangular channel formed by the cited union of the components is occupied, by a bulkhead 27 which almost touches the surface of the cylinder 1 5 until they almost touch and from an "inclined plane" of cylindrical shape 30' which is eccentric with respect to said rotor 1 5, for about half of the inner cylindrical surface of the aforementioned "cylinder" 2, the vanes adhere to the surface 30 and then crawl on the restricting surface 30' for the above-mentioned indentation on corresponding quadrangular seats during rotation of the rotor 1 5.
[0066] The hydraulic motor and/or volumetric turbine for oil and/or water under pressure according to the invention operates as follows: first we must have an inlet pipe for the fluid, for example water, we assume that the water comes from the main pipe of a water line with a constant pressure and that enters from the inlet channel 3 of the turbine (see figure 1 ), 2), 3), and 4), looking at figure 2) we see the water 3' come by pressure from channel 3 flowing onto chamber 1 8', the water 3' cannot go left because it finds the bulkhead 27 which prevents its passage, then it must run right into the cylindrical circular crown called "thrust sector", where it meets the vane 8 that obstructs the passage but the strength of the water 3' pushes the cited vane 8 and it moves it, the arrows 21 show the pressure energy of the water on the vane 8, the vane 8 is housed in a special calibrated quadrangular seat 8" of the rotor 1 5 and moving causes the rotation of the said rotor transmitting the force at the same, the rotor 1 5 in turn transmits the force to the motor shaft 1 6 in the form of mechanical energy.
[0067] Looking again at the figure 2 we see the arrow 1 6' at the center of the shaft 1 6, this means that the rotor 1 5 is rotating clockwise, the rotation allows the vane 7, which is located in correspondence of the bulkhead 27, completely retracted into its calibrated quadrangular seat 7" of the rotor 1 5, to go beyond the point 14 for then escape thrusted by the spring 1 1 supplied and by the water pressure 3' which penetrates through the channel 1 2 to reach the space under the mentioned vane 7, where they are housed the spring 1 1 . [0068] Looking at the Figure 3) we see that the vane 7 has moved, escaping from its calibrated quadrangular seat 7" until it touches the inner cylindrical surface 30 of the "cylinder" 2 and the arrow 7' indicates the above-mentioned movement, the water 3' continues to enter and the vane 8 continues to move by rotating the rotor 1 5 further, this thrust 21 on the vane 8 continues until the vane 7 has not passed the outlet of the channel 3 and the water 3' limits to surround the vane 7 just emerged continuing to push the vane 8.
[0069] Looking at the Figure 4) we see that the vane 7 has completely passed the aforementioned outlet, indicated with number 22', this done the water passage 3' is obstructed by the "new" vane 7 which now receives the same pushing thrust 21 that before was receiving the vane 8, the vane 7 as the 8 transmit the force received from the water 3' to the rotor 1 5, thus, a vane after the other cause the regular rotation of the rotor 1 5, the speed of rotation depends on the flow rate of the water 3' and by the pressure difference between the existing inlet and outlet from the turbine.
[0070] Looking at the figures 2), 3) and 4) we see that during the said rotation vanes 9 and 10 are coming back in the respective calibrated quadrangular seats 9" and 10", the said return is made possible by the eccentric surface 30', relative to the rotor 1 5, which starts from the point 23 and ends at point 14 in correspondence of the bulkhead 27, the water present in the space existing below the vanes 9 and 10 to return it shall be forced to escape from the channel 12, the arrow 25 shows that this happens, while the arrows 9' and 10' show the direction of movement of the corresponding vanes that are precisely returning into their seats 9" and 1 0".
[0071 ] Summarizing, the hydraulic motor according to the invention is characterized by having a bulkhead 27 easily overcome by the vanes that follow the "inclined plane" 30' for the return and to have a "thrust sector" coaxial with the rotor 1 5 to impede to the vanes, which undergo the push in that stretch, to create friction with the inner cylindrical surface 30 of the "cylinder" 2.
[0072] Also the output channels 4, 5 and 6, which then all converge into one (not shown in the figures) are of vital importance, especially the channel 6 that if there was not the engine would clog due to the internal fluid that does not find "the last discharge vent" in a restricting volume like the chamber 1 9', the other channels are positioned to not create impediments to the discharge flow pushed by the vanes, the ideal would be to create a shallow or channel at the center of the "inclined plane" 30' for communicating all three channels for the discharge leaving one for the attachments, the vanes would anyhow fall back in their seats during the rotation in such as they slide at the sides of the above mentioned central shallow, is only a matter of construction, the important is to achieve the purpose of discharging the fluid by removing all structural obstacles.
[0073] The hydraulic motor is created to operate in a pressurized system, this means that can be maintained under pressure even the discharge fluid and the motor operates however, the important thing is that there is a pressure difference between inlet and outlet, the motor according to the invention works by pressure difference, the incoming one must be clearly higher than that of outgoing one, with equal pressure the hydraulic motor stops.
[0074] The rotor of the hydraulic motor according to the invention can only turn in one direction, as the outcome vanes after the bulkhead 27 would get stuck bumping against the bulkhead itself if the rotor was running on the contrary, the invention thus has only one direction of rotation in the clockwise or counterclockwise sense depending on how the components have been assembled which are symmetrical except for the "cylinder".
[0075] One consideration is that of knowing how fluid they operate, whether it is oil, there are no particular problems: first, because the fluid is a lubricant, second because the hydraulic motor would be installed in a closed circuit with appropriate filters etc., if instead the hydraulic motor is installed in a pipeline to act as a turbine to produce electricity things change, and not by little, having water available as a fluid, which is not lubricant, must be careful about the materials used especially if it's drinking water, all the moving parts must not seize and also should not warm up much, you have to use self-lubricating materials suitable for food (all known materials), wear is also important, we need the vanes, as they will consume the most be made of a material softer than that used for the cylinder, for the side flanges, for the rotor and for other components not mentioned.
[0076] To design a volumetric turbine for aqueducts according to the invention it is necessary that this has a very low number of revolutions, but with a great torque moment or torque, to do this is necessary to increase the displacement of the turbine, thus is necessary to increase the volume of the cylindrical circular crown, then we must increase the diameter of the "cylinder" and the height of the same and in proportion will be realized the rotor, increasing the displacement should be needed more water to make a complete turn, and then once predetermined the maximum number of revolutions which must have a turbine working with water under pressure is sufficient to know the flow rate of the main pipe to proceed with the dimensioning, an easy calculation being a volumetric machine.
[0077] Also the type of water flowing in the pipe is very important, for example, if we have a pipe that delivers water from a reservoir at high altitude you must analyze it to see if it's muddy, sandy, rich or poor in mineral salts, etc., done that you proceed to the choice of building materials best suited to the case and so on each site is and will be different even if it could vary slightly, then in those cases it can be adopted a tolerance on the construction specifications.
[0078] The hydraulic motor or volumetric turbine displacement of the invention is to be considered a real and proper jewel of technology, from my point of view it should have a name that identifies it, like all machines of the fluid dynamics are listed and explained in formulas or calculations for the dimensioning, the machine according to the invention has a high performance, all depends on the tolerances of the mechanical coupling of the moving elements.
[0079] The machine according to the invention can be compared to a piston inserted into a cylinder of annular shape, to move the piston we must cap internally the said annular cylinder and enter a fluid between the said cap and the internal piston, one would see the piston make the entire turn around then stop against the cap, in the case of the hydraulic motor according to the invention the said cap results by the 27 and the piston results from one of the vanes of the rotor, but in this case the vane does not stop when it reaches the bulkhead cited above because it passes it reentering in its proper quadrangular seat for then outcome again to be pushed by the fluid.
[0080] In order to govern the hydraulic motor according to the invention is sufficient to have an incoming and an outgoing pressure gauge, a flow indicator or outlet flow rate, an electric generator, possibly with permanent multi-stage magnets, a control panel, etc... all known systems. The overall dimensions of the machine according to the invention may be different, for a fluid such as water is recommended oversizing for the purpose of increasing the displacement to be able to reduce the number of revolutions, as already said the water do not lubricates and for this reason it is better to have a slow machine with a high torque moment or torque. Holding firmly the principle of operation, the materials employed, as well as the contingent shapes, may be any, without thereby outcoming from the scope of the present invention.

Claims

7. Volumetric hydraulic motor or volumetric turbine for pressurized systems operating with the passage of a fluid such as water and/or oil for the production of mechanical energy and/or electrical characterized in that it comprises of: a containing cylinder, a rotor with drive shaft , of four vanes or a plurality of vanes, of quadrangular seats on the rotor for the housing of said vanes, of compression springs for the vanes, of two lateral flanges equipped with sealing OR rings, and rings of a mechanical seal for the shaft, of a further two lateral flanges provided with bearings for the motor shaft, an inlet channel for the fluid under pressure, of three or a plurality of channels for the fluid outlet, a bulkhead between the cylindrical surface inside of the containing cylinder and the cylindrical surface of the rotor, of a surface eccentric with respect to the rotor which develops in a semicircle for about half of the inner cylindrical surface of the containing cylinder, a cylindrical surface coaxial to the rotor which extends for approximately half of the inner cylindrical surface of the containing cylinder, of pressure gauges, tachometer, electric generator, flow meters and supports.
Z. Volumetric hydraulic motor or volumetric turbine according to the first claim characterized in that the rotor 1 5 is coaxial to the cylindrical surface 30 of the containing cylinder 2.
3. Volumetric hydraulic motor or volumetric turbine according to the first claim characterized in that the rotor 1 5 results eccentric with respect to the cylindrical surface 30' of the containing cylinder 2.
4. Volumetric hydraulic motor or volumetric turbine according to previous claims characterized in that on the inner surface of the cylinder 2 has been obtained a bulkhead 27 between the extremes of the surfaces 30 and 30' at points 1 4 and 22.
5. Volumetric hydraulic motor or volumetric turbine according to previous claims characterized in that on the quadrangular seats of the rotor 1 5 for the housing of the blades is housed in a channel 1 2 for the fluid under pressure, adjacent to the surface of the said vanes to put in communication the outside with the space below the said vanes.
6. Volumetric hydraulic motor or volumetric turbine according to one or more of the preceding claims characterized in that the fluid under pressure 3' enters the containing cylinder 2 flowing immediately after the bulkhead 27 and precisely in the semicircular crown 1 8' - 18 which it develops between the cylindrical surface 30 of the containment cylinder 2 and the concentric opposite surface of the rotor 1 5, a space defined "thrust sector".
7. Volumetric hydraulic motor or volumetric turbine according to one or more of the preceding claims characterized in that on the eccentric cylindrical surface 30' with respect to the rotor 1 5 have been provided at least three output channels for the fluid.
8. Volumetric hydraulic motor or volumetric turbine according to one or more of the preceding claims characterized in that on the eccentric cylindrical surface 30' with respect to the rotor 1 5 has been provided a central shallow as long as the said surface for the passage of the output fluid and communicating with the outside through a single channel.
9. Volumetric hydraulic motor or volumetric turbine according to claims 1 and 3, characterized in that the cylindrical surface 30' resulting eccentric with respect to the rotor 1 5 extends for approximately half the circumference and serves as an "inclined plane" to force the sliding vanes to return to their quadrangular seats during the rotation of said rotor in correspondence of said surface 30'.
10. Volumetric hydraulic motor or volumetric turbine for circuits operating with pressurized oil or water for the production of mechanical energy and/or electricity from the water distribution systems, characterized in that is comprising one or more of the features described and/or illustrated.
PCT/IB2012/000616 2011-04-01 2012-03-27 Volumetric hydraulic motor for pressurized systems also indicated to profit by the pressure in excess of aqueducts and similar for the purpose of producing electrical energy WO2013050818A2 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITTV2011A000045 2011-04-01
IT000045A ITTV20110045A1 (en) 2011-04-01 2011-04-01 HYDRAULIC VOLUMETRIC ENGINE FOR PRESSURIZED SYSTEMS ALSO INDICATED TO EXPLOIT THE EXCESSIVE PRESSURE OF AQUEDUCTIVE AND SIMILAR NETWORKS IN ORDER TO PRODUCE ELECTRICITY.

Publications (2)

Publication Number Publication Date
WO2013050818A2 true WO2013050818A2 (en) 2013-04-11
WO2013050818A3 WO2013050818A3 (en) 2013-05-30

Family

ID=44554853

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/IB2012/000616 WO2013050818A2 (en) 2011-04-01 2012-03-27 Volumetric hydraulic motor for pressurized systems also indicated to profit by the pressure in excess of aqueducts and similar for the purpose of producing electrical energy

Country Status (2)

Country Link
IT (1) ITTV20110045A1 (en)
WO (1) WO2013050818A2 (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITMI20130135A1 (en) * 2013-01-31 2014-08-01 Brigaglia Alberto HYDRAULIC VOLUMETRIC MACHINE FOR WATER NETS IN PRESSURE.
CN106368737A (en) * 2016-08-19 2017-02-01 唐翊翃 Hydrodynamic force conversion device
WO2017161428A1 (en) * 2016-03-24 2017-09-28 Lage Silva Hamilton Da Penha Vane pump with concentric rotor, in particular for non-newtonian fluids

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1280903A (en) * 1961-01-26 1962-01-08 Explosion turbine
US4098256A (en) * 1976-04-29 1978-07-04 Sieck Charles A Heating system
US4399654A (en) * 1982-02-19 1983-08-23 David Constant V Power plant having a free piston combustion member
NL1010348C2 (en) * 1998-10-19 2000-04-20 Air Propulsion International N Pneumatically drivable motor which can also act as a compressor for compressing a gaseous medium, in particular air.
US6662774B1 (en) * 2003-02-05 2003-12-16 Martin S. Toll Rotary internal combustion engine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITMI20130135A1 (en) * 2013-01-31 2014-08-01 Brigaglia Alberto HYDRAULIC VOLUMETRIC MACHINE FOR WATER NETS IN PRESSURE.
WO2014118119A1 (en) * 2013-01-31 2014-08-07 BRIGAGLIA, Alberto Volumetric hydraulic machine for pressurized water supply
WO2017161428A1 (en) * 2016-03-24 2017-09-28 Lage Silva Hamilton Da Penha Vane pump with concentric rotor, in particular for non-newtonian fluids
CN106368737A (en) * 2016-08-19 2017-02-01 唐翊翃 Hydrodynamic force conversion device
CN106368737B (en) * 2016-08-19 2018-04-13 唐翊翃 A kind of fluid dynamic reforming unit

Also Published As

Publication number Publication date
WO2013050818A3 (en) 2013-05-30
ITTV20110045A1 (en) 2012-10-02

Similar Documents

Publication Publication Date Title
CA2859772C (en) Positive displacement expander
RU2683005C2 (en) External gear pump integrated with two independently driven prime movers
JP6364419B2 (en) Rotary lobe pump with direct drive
EP2497949A1 (en) Plunger water pump
CN107882786B (en) Static and dynamic flow real-time matching system of closed pump control single-rod hydraulic cylinder
EA021161B1 (en) Driving arrangement for a pump or compressor
JP5611221B2 (en) Sliding vane pump
US2725013A (en) Rotary engine
WO2013050818A2 (en) Volumetric hydraulic motor for pressurized systems also indicated to profit by the pressure in excess of aqueducts and similar for the purpose of producing electrical energy
CN103732921B (en) Micropump and supporting member and method of work for micropump
CN104500492A (en) Electro-hydrostatic actuator driven by double-butterfly-shaped cooperative flow distribution pump
JP5331250B2 (en) Renewable energy generator
WO2017032271A1 (en) Rotating apparatus and rotating system applying pressing gate valve mechanism, and fluid machinery
KR20100085899A (en) Infinite variable speed device
EP2871371B1 (en) Switching unit, hydraulic machine and power generating apparatus
AU2012283238B2 (en) Downhole hydraulic pump
WO2015104191A1 (en) Hydraulic fluid motor with vanes accommodated on the stator, the fluid under pressure enters via the hollow shaft and proceeds radially in the rotor through adapted channel(s)
Salam Hydraulic pumps
CN103363053A (en) Hydraulic transmission device
EP2873870B1 (en) Spool valve assembly, hydraulic machine and power generating apparatus
SHINODA et al. Development of a low-pressure water hydraulic motor
RU2476725C2 (en) Rotary hydraulic machine
EP3276180A1 (en) Pump
CN104500507A (en) Valve-distributed servo pump with inverted spools and sleeves
RU2311560C2 (en) Adjustable guide-vane pump

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 12718331

Country of ref document: EP

Kind code of ref document: A2

122 Ep: pct application non-entry in european phase

Ref document number: 12718331

Country of ref document: EP

Kind code of ref document: A2