WO2015104191A1

WO2015104191A1 - 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)

Info

Publication number: WO2015104191A1
Application number: PCT/EP2014/079297
Authority: WO
Inventors: Silla Martini
Original assignee: ANTONELLO, Antonio
Priority date: 2014-01-08
Filing date: 2014-12-24
Publication date: 2015-07-16

Abstract

A hydraulic fluid motor/hydraulic motor with vanes which comprises: a driving shaft (2'), a rotor (2), a stator, two lateral flanges for sealing, a delivery channel, an outflow channel, a plurality of vanes (G), bearings, static and dynamic seals, springs for the vanes and external closure means called "shells" (5).

Description

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)

The present invention relates to a new hydraulic motor with vanes, which is characterized in that the vanes are not accommodated in the rotor but on the stator, a plurality of vanes arranged in a circle on adapted slots which are provided radially on the stator, an adapted spring for each vane pushes it against the surface of the rotor which is coaxial to the stator.

The rotor is integral with a shaft that is coaxial to the inner cylindrical surface of the stator and has a surface that is not completely cylindrical, in fact the surface of the rotor is cylindrical for the first quarter, then arc- shaped so as to define a ramp for the second quarter, then cylindrical again for another quarter and the last quarter is arc-shaped again so as to define a second ramp that reconnects with the start of the first cylindrical surface, the cylindrical surface and the ramp on the first half-circumference of the rotor are identical to and opposite from the other two surfaces of the other half, the fluid penetrates from the center of the hollow shaft and exits onto the surface of the rotor where it encounters the vanes which act as a barrier.

The surface of the rotor is not completely cylindrical and has a special profile that is divided into four parts: the first part is cylindrical, the second part is shaped like a ramp, the third part is cylindrical again and the fourth part reconnects with the start of the first part and is shaped like a ramp, the first two surfaces are identical to and opposite from the second two.

To better describe the four surfaces of the rotor it is possible to explain them as follows: for the first ninety degrees the surface of the rotor is cylindrical and concentric to the inner cylindrical surface of the stator and distanced therefrom by a distance calculated in advance as a function of the cubic capacity of the motor that it is desired to obtain, in the second ninety degrees of the circumference of the rotor one can see the surface as a continuation of the first surface, again cylindrical in shape but diverging in an arc shape and thus creating a ramp that ends with its peak almost adjacent to the aforementioned inner cylindrical surface of the stator, the gap is of the order of a hundredth of a millimeter in order to prevent losses of charge owing to "hazardous" leaks of the fluid, in the third ninety degrees we again find a cylindrical surface that is identical to and opposite from the first, the junction of the aforementioned peak of the ramp with the start of the aforementioned surface gives rise to a protuberance with a net jump equal to the aforementioned distance calculated in advance from the inner cylindrical surface of the stator, in the fourth ninety degrees of circumference we again find a ramp identical to and arranged opposite from the first, obviously the peak of the second ramp connects with the start of the first cylindrical surface of the rotor thus creating a second protuberance that is identical to and arranged opposite from the first.

The two protuberances serve as push points for the thrust of the fluid under pressure, which emerges at the surface of the rotor from two radially opposite channels, the exit point of the two channels must be as close as possible to the end of the ramps, in the initial part of the two cylindrical surfaces of the rotor.

The fluid under pressure enters axially at the center of the hollow end of the driving shaft and proceeds until it reaches the center of the rotor from where it proceeds to the surface thereof through two radially opposite channels, both the channels are connected to the central cavity of the driving shaft.

When the fluid exits at the surface, it finds itself simultaneously in two mutually opposite chambers, the chambers are delimited: by the cylindrical surface of the rotor, by the inner cylindrical surface of the stator, by the protuberance of the end-of-ramp peak, by the vane extending from the slot of the stator which right at that moment defines a bulkhead or barrier since the aforementioned vane is in contact with the cylindrical surface of the rotor, and also by the two abutment surfaces of the two lateral closing flanges, which are spaced by a few ten thousandths of a millimeter from the faces of the rotor, an infinitesimal distance in order to reduce the leaks of the fluid to almost zero.

The vane does not yield to thrust and thus it acts as a bulkhead to the fluid under pressure, the increase in volume of the fluid, which enters the aforementioned mutually opposite chambers through the two aforementioned radially opposite channels of the rotor, thus acts in the opposite direction against the aforementioned mutually opposite protuberances of the rotor, this entails the rotation of the rotor, during the rotation the incoming vane, after having passed the peak of the corresponding ramp, is pushed by the spring against the facing cylindrical surface of the rotor, the moment when the mouth of the channel that is defined radially on the rotor passes the incoming vane, that vane substitutes the previous one, i.e. the outgoing vane, which also acts as a bulkhead, but is no longer under pressure, and is made reenter the accommodation slot by the ramp of the rotor, at the same time the same vane acts as a bulkhead against the outflowing fluid which, owing to the reduction in volume between the ramp in rotation and the inner cylindrical surface of the stator, forces the fluid into an adapted recess that is defined centrally to that ramp, the fluid is collected and sent into a lateral channel that leads into the left- hand face of the rotor at an annular recess that is defined in the abutment surface of the left-hand flange in order to then be sent outside the aforementioned flange through adapted ducts that are internal thereto.

The left-hand flange is provided with a central bushing or a bearing in order to accommodate the hollow end of the driving shaft, from the outside of the flange, by way of a delivery pipe, the fluid under pressure arrives centrally and then encounters the aforementioned hollow shaft, an adapted sealing ring for rotating shafts prevents the fluid from bypassing it and proceeding directly to the outflow. At the center of the right-hand flange a combined bearing for the driving shaft has been fitted, which is a bidirectional radial and axial bearing, the bearing ensures the axial and radial rigidity of the driving shaft in order to prevent any seizing on the abutment surfaces of the two lateral flanges which skim the faces of the rotor by a few ten thousandths of a millimeter, the rotating shaft exits the right-hand flange in order to bring the mechanical energy outside.

Each complete revolution of the rotor applies thrust to all the vanes twice, the fluid under pressure acts on the vanes only when they come into contact with the cylindrical surface of the rotor which is coaxial to and spaced apart from the inner cylindrical surface of the stator, before the vane under pressure concludes the contact with the cylindrical surface of the rotor and begins the contact with the surface of the ramp, the other vane is already in contact with the aforementioned cylindrical surface of the rotor thus taking away pressure from the previous one, the aforesaid operation is carried out by the vane arranged opposite so as to obtain two simultaneous thrusts and two simultaneous outflows twice per revolution, this is true for all of the plurality of vanes that are accommodated in the respective slots.

Currently there are several types of hydraulic fluid motors/hydraulic motors on the market, which are: fixed cubic capacity vane motors, variable cubic capacity vane motors, axial piston motors, radial piston motors, fixed and variable cubic capacity piston motors, orbital motors, external- gearwheel motors, internal-gearwheel motors, both with fixed cubic capacity, combined motors, multiple motors, hybrid motors, etc.

All the motors listed differ in their technical characteristics and in their principles of operation, each motor has various different applications and is chosen on the basis of specific requirements, sometimes the cost also influences the choice.

The parameters that count in the choice of a hydraulic motor are: cubic capacity in cmVrevolution, flow-rate in liters/min, torque in N-m, power in kW, speed in revs/min, pressure difference between inflow and outflow in BAR, volumetric yield, mechanical yield, total yield.

For each type of motor the following are also important: the minimum and maximum flow-rate values, the minimum and maximum pressure values, the minimum and maximum temperature of the oil, the type of oil to use, the expected number of hours of running time before requiring maintenance, and many other factors.

The hydraulic liquids are important, in a hydrostatic transmission the hydraulic liquid is the (almost) incompressible means that transmits the energy delivered by the pump to the rotary user device (the motor) in the form of force or torque and angular speed.

In hydraulics, a motor performs the function of a pump in reverse, because it converts the hydraulic energy originating from the pump back to mechanical energy.

Just like a pump, the motor is a volumetric machine, i.e. it is capable of handling the conveyance of liquid by way of variations of volume of its internal chambers.

The principle of operation common to all hydraulic motors is simple: the liquid introduced through the supply coupling acts on the active parts (gearwheels, vanes, axial or radial pistons) thus generating a useful tangential component that imposes a rotation speed and a motor torque on the shaft.

The best definition of a hydraulic fluid motor is the following: a hydraulic fluid motor is a volumetric motor, which when powered by the flow of a liquid dispensed by a pump develops a rotation speed (n) and a torque (M) on the shaft.

The function of the motor is to convert the hydraulic power delivered by the pump to mechanical power, proportional to the product (M) x (n).

The hydraulic motor is used in situations when a high torque is necessary with reduced encumbrances in order to move rotary elements, when the mechanical solution is difficult, or when the use of electricity is not possible or is hazardous for the work environment.

The most important characteristics of a hydraulic motor are: the torque, the breakaway torque, the minimum and maximum number of revolutions, the yield, the reduced encumbrance with respect to the torque that it can generate.

The types of hydraulic motors are: fixed cubic capacity motor, in which the volume of fluid absorbed for each revolution (cubic capacity) cannot be varied, (gearwheels, orbital, vanes, axial and radial pistons).

A motor with fixed cubic capacity ensures a constant output torque.

The number of revolutions can be varied by adjusting the flow-rate of the delivery pump, by way of an adapted control valve.

In a motor with variable cubic capacity, the volume of fluid for each revolution can be varied (axial pistons).

A motor with variable cubic capacity provides a variable torque and a very ample control over revolutions.

A bidirectional motor can invert the direction of rotation of the output shaft, by changing the direction of flow of the oil internally.

Hydraulic motors are divided into two different groups: fast motors and slow motors.

Fast motors of from 500 to 6,000 revs/min and beyond, fixed cubic capacity of from 2.5 to 1,000 cc.

Fast motors are divided into two classes: low torque and high torque.

External and internal gearwheel motors (gerotors), with vanes, are in the first class.

Axial piston motors and orbital motors have a high torque.

The principal aim of the present invention is to overcome the technical characteristics of the above mentioned motors while seeking also to reduce the drawbacks thereof, by providing a hydraulic fluid motor and/or hydraulic motor that differs from the principle of operation of the hydraulic motors known up to now with an absolutely new state of the art that is capable of ensuring a high breakaway torque and high torque with the motor at speed, as well as high power with excellent mechanical and volumetric yield.

Another very important aim of the present invention is to provide a hydraulic fluid motor that is impossible to over-rev by increasing the flow- rate of the fluid or by suddenly removing the load from the driving shaft.

Another very important aim of the present invention is to provide a hydraulic fluid motor that does not cause the inner rotation of the fluid or changes of direction thereof, usually these phenomena happen in the hydraulic motors known up to now; this characteristic of the motor would reduce the risks of a rapid deterioration of the hydraulic fluid.

A further very important aim of the present invention is to provide a hydraulic fluid motor characterized in that the parts subject to wear (vanes) can be replaced by acting manually from the outside of the motor without having to open or disassemble it.

The further very important aim of the present invention is to provide a hydraulic fluid motor that is proof against water hammers and pressure overloads.

Another very important aim of the present invention is to provide a hydraulic fluid motor with unlimited cubic capacities but without for this reason having to have problems of losses of charge owing to the leakage of fluid between the thrust chambers and the abutment surfaces of the lateral flanges.

A very useful and very important aim of the present invention is to provide a volumetric hydraulic motor for water supply networks for use as a turbine connected to a generator for the production of electricity.

An important and bold aim of the present invention is to provide a hydraulic fluid motor that is extremely small in order to be capable of reaching a rotation rate that is unthinkable with the principles of operation of the motors that exist currently.

These and other aims which will become better apparent hereinafter are achieved by a hydraulic fluid and/or hydraulic motor, characterized in that it comprises: a stator, with two lateral flanges, a rotor that is arranged inside the stator between the aforesaid flanges, a driving shaft that is integral with the rotor, a plurality of through slots that are arranged radially on the stator at a regular distance from each other, a plurality of vanes, one for each slot, springs, one for each vane, covers or shells for externally and hermetically closing the aforesaid slots, an annular recess that is defined on the abutment surface of the left-hand flange, internal channels in the aforesaid flange which communicate with the outside for the outflow of the fluid, a bushing or bearing for the left-hand end of the driving shaft, a sealing ring for high pressures on the left-hand end of the driving shaft, a central coupling to the left-hand flange for the delivery pipe of the fluid under pressure, a central cavity on the left-hand end of the driving shaft which penetrates down to the "nucleus" of the rotor, two radially opposite channels that are connected with the aforesaid central cavity and lead to the surface of the rotor, two mutually opposite ramps on the surface of the rotor, two cylindrical surfaces on the rotor which are coaxial to and spaced apart from the inner cylindrical surface of the stator, a combined bearing or the like being provided on the right-hand flange for the driving shaft in order to support radial and axial loads and at the same time prevent shifting of the driving shaft, a sealing ring for rotating shafts for sealing the driving shaft exiting from the aforesaid right-hand flange of a support for the motor.

Further characteristics and advantages of the invention will become better apparent from the detailed description of a specific, but not exclusive, embodiment, illustrated by way of non-limiting example in the accompanying drawings wherein:

Figure 1 is a cross-sectional view of the hydraulic fluid motor, taken half-way, to clearly show the eight vanes (in this case) that are accommodated symmetrically on the respective calibrated seats (slots) of the stator, outside the stator one can see eight hermetically-sealed shells with their respective compression springs which act centrally on the bottom of the vanes, in the center one can see the hollow driving shaft with the rotor integral therewith, furthermore one can see the symmetric profile of the aforesaid rotor with two identical and mutually opposite ramps which are the continuation of two cylindrical surfaces, which are also mutually opposite and coaxial to the inner cylindrical surface of the stator and are spaced apart from it, while one can see the two radially opposite channels shown with dotted lines which are connected to the central cavity of the driving shaft and come out after the peak of the aforesaid ramps and at the start of the two cylindrical surfaces of the rotor, on the left-hand face of the rotor one can see two arc-like slits that communicate with the respective recess that is defined in the aforesaid ramps, the recess on the ramps and the arc-like slits that are connected thereto are needed for the passage of the outflowing fluid;

Figure 2 is a cross-sectional view of the hydraulic fluid motor in Figure 1 showing the first step of thrust of the fluid under pressure which originates from the hollow center of the driving shaft through the two radially opposite channels that are connected thereto and which come out in the mutually opposite thrust chambers, the fluid under pressure uses the vanes A and E as push points for simultaneously discharging the pressure on the two end-of-ramp protuberances of the rotor, in this starting step the breakaway torque on the driving shaft is detected;

Figure 3 is a cross-sectional view of the hydraulic fluid motor in

Figures 1 and 2, in this figure one can see that the rotor has completed one- eighth of a revolution (forty-five degrees), showing the second step of thrust, now the fluid under pressure uses the vanes B and F as push points for exerting thrust on the aforesaid protuberances, while the vanes A and E are no longer subjected to the pressure of the fluid, between the vanes B and A and also between the vanes F and E (the space between one vane and the next is defined with the name "cell"), the fluid remains depressurized and trapped while awaiting reduction in volume in order to be able to exit at the outflow;

Figure 4 is a cross-sectional view of the hydraulic fluid motor in the previous figures, in this figure one can see that the rotor has completed another one-eighth of a revolution for a total of ninety degrees, showing the third step of thrust, the vanes involved in providing the aforesaid push points are the vanes C and G, while in the cells between the vanes C and B as well as between the vanes G and F the fluid remains depressurized as in the previous cells in Figure 3, furthermore one can see that the cells defined by the vanes B and A as well as those defined by the vanes F and E are subjected to an evident reduction in volume owing to the ramps in rotation, the fluid is thus forced to flow out through the recess of the mutually opposite ramps that are connected with the arc-like slots that can be seen on the left-hand face of the rotor;

Figure 5 is a cross-sectional view of the hydraulic fluid motor in the previous figures, in this figure one can see that the rotor has completed another one-eighth of a revolution for a total of one hundred and thirty-five degrees, showing the fourth step of thrust, now the vanes involved in providing the push point for the fluid under pressure are the vanes D and H, while in the cells between the vanes D and C as well as between the vanes H and G the fluid remains depressurized, while in the cells between the vanes C and B— B and A, as well as between the vanes G and F— F and E the fluid is pushed to flow out for the progressive reduction to zero by the aforesaid mutually opposite ramps in rotation, in this figure one can say that the rotor has completed almost a half revolution, which is completed when the rotor returns to the position in Figure 2;

Figure 6 is a three-dimensional view of the rotor integral with the driving shaft, in the upper figure one can see the inflow of the fluid to the center of the hollow end of the driving shaft, one can also see the recess on the ramp and the arc-like slot that is connected therewith and which comes out on the left-hand face of the rotor, also in the upper figure one can see the mouth of one of the two radially opposite channels for the passage of the fluid originating from the central cavity of the aforesaid shaft, one can furthermore see the upper end-of-ramp protuberance that is designed to thrust the fluid under pressure and is arranged opposite the other, the lower figure shows the right-hand face of the rotor showing the driving shaft for the transmission of mechanical energy, in the second figure one can also see the second, opposite ramp with the other recess, identical to and opposite from the first, one can furthermore see that in the right-hand face of the rotor there are no arc-like slots for the fluid outflow but a cylindrical protuberance designed for contact with the thrust bearing;

Figure 7 is a cross-sectional view taken along the line A-A of the hydraulic fluid motor, to the left of the figure, on the transverse cross- section of the stator, one can see the fluid that enters from the center and passes along the two mutually opposite channels in order to come out in the corresponding chambers, that is to say, between the end-of-ramp protuberance and the vane already in contact with the two cylindrical surfaces of the rotor, in the right-hand half of the drawing one can see the fluid entering from the center of the hollow shaft, the arrows show the incoming fluid and then they also show the fluid proceeding through the aforesaid mutually opposite channels and coming out in the two aforesaid mutually opposite chambers, one can see the left-hand flange with the central bushing for the hollow end of the driving shaft, at the center of the right-hand flange one can see the combined bearing, two axial and one radial, in contact with the cylindrical protuberance of the rotor, there is a ferrule on the driving shaft to close the bearing with preloading, while there is a second ferrule with left-handed threading to lock the radial bearing on the right-hand flange, since a sealing ring for rotating shafts is inserted between one ferrule and the other, adapted screws lock the two ferrules on the stator, internally enclosing the rotor, also in the cross-section taken along the line A-A one can see the abutment surfaces of the two ferrules which are separated from the faces of the rotor by a few ten thousandths of a millimeter;

Figure 8 is a cross-sectional view taken along the line B-B of the hydraulic fluid motor, on the left of the figure, on the transverse cross- section of the stator one can see the fluid in the cells between the vanes B and A as well as between the vanes A and B and, below, between the vanes F and E as well as between the vanes E and D, all the aforesaid vanes are at the ramp in rotation, the arrow in the center shows the anticlockwise direction of rotation, one can also see the two mutually opposite arc-like slots on the face of the rotor with the fluid exiting therefrom, the arrows show the exiting fluid, on the right of the figure one can see the cross- section taken along the line B-B of the hydraulic fluid motor, one can see that no fluid is entering from the center of the hollow shaft, this is to better show the outflow phase only, note in particular the fluid inside the recess of the ramps which passes through the arc-like slots and which comes out at the annular recess defined on the abutment surface of the left-hand flange, the fluid in the aforesaid recess passes through adapted channels that are defined on the bottom of the annular recess and lead to the circular chamber inside the left-hand flange in order to then exit outside the threaded aperture, note also the fluid that flows in the lateral channels of the vanes that are re-entering their seats because they are pushed by the two ramps in rotation, the fluid that earlier entered the space behind the vane has to flow out owing to the reduction in volume caused by the re-entry of that vane;

Figure 9 is a cross-sectional view taken along the line C-C of the hydraulic fluid motor, on the left of the figure, on the transverse cross- section of the stator one can see that the radially opposite channels of the rotor are at the incoming vanes after passing the peak of the corresponding ramp, one can see that they are suspended owing to the fluid under pressure that exits from the two radially opposite channels of the rotor, the other vane in contact with the cylindrical surface of the rotor acts as a barrier to the fluid thus creating a push point thereat in order to be able to put pressure on the end-of-ramp protuberances, on the right of the figure one can see the cross-section of the hydraulic fluid motor, in this cross-section one can see the fluid entering from the center of the hollow shaft and flowing along the two radially opposite channels of the rotor until it exits into the thrust chambers, one can furthermore see the upper vane detached from the stator in order to show the useful space or space that can be traveled by the spring and by the bottom of the vane, one can also see the fluid in the two channels that are defined on the left-hand side of the vane;

Figure 10 is a three-dimensional view of the rotor integral with the driving shaft, one can clearly see the vanes that occupy the same position as when they are accommodated in the slots of the stator, the absence of the stator is to better show their function, in this figure arrows show the path and the direction of the fluid, as well as the movements of the mechanical parts;

Figure 11 is a three-dimensional view of the rotor with the driving shaft, one can also see the insert removed and on it one can see the annular recess defined on the abutment surface that is intended to skim the left-hand face of the rotor, one can also see a plurality of holes on the bottom of the aforesaid annular recess, one can also see the dotted lines that indicate the boundaries of the arc-like slots that mate with the circles that delimit the annular recess, and the recess on the ramp of the rotor also clearly shows the corresponding arc-like slot;

Figure 12 is an exploded view of the hydraulic motor according to the invention showing the essential components of the hydraulic fluid motor, one can see the left-hand flange 28, the insert for the outflow passages 30, the rotor 2 integral with the driving shaft 2, the cam ring (stator) 1 with the slits for the accommodation of the vanes, the right-hand flange 31 , the ring for the driving shaft which is adapted to contain and preload the thrust bearing, the ferrule for the right-hand flange for locking the radial bearing;

Figure 13 shows the driving shaft with the rotor incorporated, note in particular the recess on one of the two ramps which is identical to and symmetrical with that of the other ramp, the arrows that enter the aforesaid recess indicate the outflowing fluid which, thrust by the vanes, goes on to occupy the space in the annular recess of the insert 30, the arrow 27 indicates the fluid exiting outside the motor, the arrows 25 indicate the passage of the fluid from the recess that is defined on the ramps of the rotor, the arrow 15 indicates the entry of the fluid under pressure;

Figure 14 shows a variation of the motor, one can see three radially- arranged channels that are connected with the hollow center of the driving shaft, with this type of rotor three simultaneous thrusts are obtained that increase the breakaway torque and what is more, the obtainable power also increases in proportion, obviously the diameter of the stator and the number of vanes must be scaled;

Figure 15 shows another variation of the motor, one can see a single channel that is connected to the hollow center of the driving shaft, with this type of rotor the thrust occurs tangentially to the rotor on the single protuberance, the pressure of the fluid in this situation also acts radially against the driving shaft thus penalizing the radial bearings, the breakaway torque is lower but with this type of rotor with a single delivery one can reduce the size of the motor considerably.

With reference to the figures, the hydraulic fluid motor/hydraulic (oil hydraulic) motor, in order to be able to obtain mechanical energy on the driving shaft by supplying the delivery pipe with a fluid under pressure, for example hydraulic oil, is characterized in that it comprises a stator, also known as a casing, a rotor, a driving shaft, a left-hand lateral flange, a right- hand lateral flange, radial bearings, axial bearings, static and dynamic sealing rings, one or more bushings, holes and channels for the delivery of the fluid and for the outflow thereof, an optional drainage channel, screws and supports for assembly.

In Figure 1 one can see a cross-section through the motor to show the inside of it, in particular to show the central part where the thrust occurs, at the center one can see the rotor 2 positioned coaxially to the stator 1, one can see the vanes 6 which are arranged radially on the stator 1 , and all accommodated at the same distance from each other on adapted through slots 1 " of the stator 1 which allow them to perform an alternating radial sliding, adapted compression springs 8 push the vanes 6 against the surface of the rotor 2 so as to ensure the seal at starting time, adapted shells 5 fixed with screws from outside ensure the hermetic seal of the aforesaid slots 1 " with their vanes accommodated internally, the play between the vane and the slot is of the order of a few hundredths of a millimeter in order to prevent losses of charge when the fluid leaks; the vanes 6 are provided with one or more channels 6' that are defined vertically on the face that is subjected to the pressure of the fluid and are needed to make the fluid under pressure reach the bottom of the vanes 6, specifically in the chamber 5' that surrounds the entire bottom of the vane 6 and where the spring 8 in the central hole 7' is also accommodated, the rotor 2 is integral with the driving shaft 2' which is hollow 9 at the left-hand end for the entry of the fluid under pressure, at the center of the rotor two radially opposite channels 9' have been defined which are connected with the aforesaid cavity 9 of the driving shaft 2', the two channels 9' come out on the cylindrical surface 11 of the rotor 2 which is coaxial to the inner cylindrical surface 1 ' of the stator 1, the cylindrical surface 11 of the rotor 2 is traced from the point 14 to the point 13 to then proceed on a diverging path to form a ramp 12 that is traced from the point 13 until the point 14', then from the point 14' until the point 14 the surface of the rotor 2 is still cylindrical and coaxial to the surface of the stator, this short cylindrical portion of the rotor is needed to ensure a greater seal at the vane 6 and must necessarily have a greater length than the thickness of the vane, note in particular the two mutually opposite channels 9' that open out immediately after the peak of the ramp 12 and at the start of the cylindrical surface 11 of the rotor 2, one can see that said surface 11 is spaced apart from the cylindrical surface , the value of such spacing determines the cubic capacity of the motor on the entire round angle, one can see that the cylindrical surface 11 , the ramp 12 and the short cylindrical portion at the end of the ramp, for a total of one hundred and eighty degrees, are identical to and opposite from the surfaces that cover the remaining one hundred and eighty degrees, the cylindrical surfaces 11 are needed for the thrust phase, while the ramps 12 are needed to make the vanes 6 re-enter their slots 1 ", each vane is forced to re-enter after a rotation of one hundred and eighty degrees of the rotor 2, on the left-hand side of the rotor 2 one can see two arc-like slots 3 that are identical and mutually opposite, the aforesaid slots are connected with their recess 4 which is defined at the center of the ramp 12, the dotted lines indicate the profile of the recess, during the passing of the ramps at the vanes, one can see that the space is reduced to zero and the fluid must flow through the aforesaid recesses 4 and into the connected slots 3.

In Figure 2 we have the same cross-section as in Figure 1, this Figure to Figure 5 show the sequence of one complete revolution of the rotor 2 with the various phases in succession, here one can see the arrows 15 that indicate the fluid under pressure which enters from the center 9 of the hollow shaft 2' to then proceed through the radially opposite channels 9', the arrows 15' indicate the radial direction, initially the vane 6 of the shell A forms a barrier to the fluid that enters the cell 10, the spring 8 causes a radial thrust 8' on the vane 6 against the cylindrical surface 11 of the rotor, the fluid expands on the yielding part which is the rotor 2 by acting tangentially thereto against the protuberance defined by the end-of-ramp peak 14, the arrow 16 shows the direction of thrust against the aforesaid protuberance, one can see that the fluid enters the channels 6' of the vane 6 by pushing on the bottom of the vane, the arrow 18 indicates the thrusting force which depends on the pressure of the fluid, simultaneously the same thrust occurs on the protuberance arranged opposite, the breakaway torque is thus double, the arrow 20 indicates the direction of rotation of the rotor 2 and consequently of the driving shaft 2' which is coaxial to the rotor 2, one can further see the arrows 19 that show the direction of the vanes 6 that are pushed by the "inclined plane" of the corresponding ramp 12 that initiated the rotation.

Figure 3 shows the next phase, here one can see the vane 6 of the shell B which has formed a barrier to the entering fluid 15', the rotor 2 has performed a rotation of forty-five degrees, the vane 6 of the shell A remains neutral, only the thrust 8' of the spring 8 keeps it adhering to the surface of the rotor 2 at the point where the cylindrical part finishes and the ramp begins, no arrow, except the one that indicates the aforesaid thrust of the spring, is visible, the fluid, now without pressure, trapped in the cells formed by the vanes 6 of the shells A and B and of the mutually opposite ones E and F, the fluid remains in that position until such point as the reduction in volume caused by the action of the ramp forces it to exit via the arc-like slot 3, one can see that the vanes corresponding to the shells H and D which are re-entering, the arrows 19 indicate the movement, while the vanes of the shells C and G have reached total reentry because they are at the end of the ramp, no arrow, except that of the spring 8 (a constant force that acts with equal intensity on all the vanes at any work phase), it is possible to see that the fluid trapped in the two cells does not rotate together with the rotor, thus it does not cause additional friction or even heating (a not inconsiderable peculiarity that enriches the state of the art used on this invention).

In Figure 4 one can see the rotor 2 which has performed a further forty-five degrees of revolution, now the vanes affected by the thrust are the vanes for the shells C and G, the arrows 17 and 18 indicate the passage of the fluid under pressure, the cells for the vanes of the shells B and C as well as F and G have the fluid 21 trapped in them while the cells of the vanes 6 of the shells A and B as well as E and F are in contact with the ramps in rotation which cause the reduction in volume of the fluid 22 which exits via the arc-like slots 3, the arrows 25 show the exiting fluid, the arrows 26 show the fluid, which was earlier accommodated in the accommodation space of the bottom of the vanes, flowing through the channels of the vanes for the reduction in volume owing to the reentry of those vanes, the fluid is added to the fluid trapped in the aforesaid cells to then exit via the aforesaid arclike slots, the vanes of the shells D and H have fully re-entered.

Figure 5 shows the rotor which has performed one hundred and eighty degrees of rotation, thus completing the inflow and outflow of the fluid, now it is the vanes of the shells D and H that act as barrier to the incoming fluid while the cells of the shells C and D as well as G and H are static, the cells for the shells C and B— B and A as well as G and F— F and E are being reduced in volume, the space 23 is also approaching zero resulting in the outflow of the very last drop of fluid, if we examine the sequences closely one can see that the vanes are progressively alternated, one after the other they perform the steps, acting twice per complete revolution on the same service, another consideration concerns the fact that the fluid under pressure enters the space of the shells in order to increase the thrust on the bottom of the vanes thus ensuring the seal thereof against the cylindrical surfaces of the rotor 2, if the tolerances of the couplings are very fine then extremely high yields can be produced.

If the flow-rate of the fluid were to be increased, the rotor would not over-rev because the seal of the vanes against the rotor would decrease owing to the fact that the vanes do not have the necessary time to finish the stroke against the rotor before the start of the ramp and thus the fluid would bypass and flow out via the recess of the ramps and then through the arc- like slots and so to the exit.

Figure 6 is a three-dimensional view of the rotor 2 seen from both sides in order to show the recess 4 on the ramps 12 and to better show the start 13 of the ramps 12 and the end of the cylindrical surfaces 11 , while also showing the channels 9' that come out at the start of the aforesaid surfaces 11, the two end-of-ramp protuberances 14 can also be seen.

Figure 7 shows the cross-section taken along the line A-A of the motor, here one can see the fluid entering from the cavity 9 of the driving shaft 2' and proceeding via the two radially opposite channels 9' that are defined in the rotor 2, the fluid leads into the two mutually opposite chambers 10 and finds at one end the vanes 6 of the shells 5 designated by the letters A and E, which act as a barrier to the fluid, and at the other end finds the end-of-ramp protuberances, part of the fluid flows in the channels of the two aforesaid vanes, thus exerting a pressure on the bottom, ensuring they have a strong traction on the cylindrical surface 11 of the rotor 2, in this first step of starting, the rotor 2 begins to rotate anticlockwise owing to the pressure on the aforesaid protuberances, the arrow 20 indicates the direction of rotation.

Also in this figure, on the right of the drawing one can see that all the other vanes adhere to the surface of the rotor 2 by way of the thrust 8' owing to the spring, one can further see the shells 5 that are fixed externally to the stator 1 with screws 39 which are accommodated in the respective threaded seats 38, on the right one can clearly see the two lateral flanges 29 and 31 which are fixed to the stator 1 via the threaded seats 41 of the stator 1 , the screws 29' and 31 ' ensure the coupling.

Also in the cross-section on the right, one can see the arrows 15 of the fluid under pressure entering from the central cavity 9 of the shaft 2' and proceeding through the mutually opposite channels 9' of the rotor 2 to come out in the opposite space 10, one can further see the static gasket seals 40 in each assembled piece, in the center one can see the sealing ring 32 that precedes the bushing 37, one can see that the rotor 2 has side faces that almost touch the abutment surface of the right-hand lateral flange 31 and the abutment surface of the insert 30 that is accommodated concentrically on the left-hand lateral flange 29.

Figure 8 shows the cross-section taken along the line B-B of the motor, and shows the outflow phase of the fluid 24 that is trapped in the recess 4 of the ramps 12, in both cross-sections one can see the vanes 6 in contact with the ramps 12 which obstruct the fluid in spaces with a decreasing cross-section 22 and 23 during the rotation of the rotor 2, one can see the fluid passing via the two arc-like slots 3 and expanding in the annular recess 3' of the insert 30 and then from the aforesaid recess it passes through the holes 3" until it reaches the annular chamber 28' and then exits outside through the threaded aperture 28, the arrows 24, 25 and 27 show the path of the fluid destined to outflow, the arrows 26 show the fluid that earlier entered at the bottom 5' of the vanes 6 and which is now outflowing owing to the reduction in volume in the slots owing to the vane 6 which, pushed by the ramps 12, re-enters the accommodation slot 1 " (clearly indicated in Figure 1).

Figure 9 shows the cross-section taken along the line C-C of the motor, with a particular position of the rotor 2 to show the task of the vanes 6, in the top left one can see the shell 5 in the position A detached from the stator 1 , one can clearly see the spring 8, the rectangular seat 5' for the space necessary for the vane when it fully re-enters in the slot and in the center the hole or niche T that ensures the anchoring of the spring 8 that was previously inserted in the central hole 7 of the bottom of the vane 6, the arrows 17 on the lateral channels of the vanes show the fluid entering the aforesaid rectangular seat 5'.

Also in Figure 9 one can see the output driving shaft 2" with the seat of the key 36, the arrow 20 indicates the direction of rotation, the ferrule 34 has a left-handed threading 27 corresponding to that of the shaft 2" while the ferrule 33 has a right-handed threading like that of the right-hand flange 31, this is in order to prevent unscrewing during rotation which can be caused by the friction of the sealing ring 35 for rotating shafts, the ferrule 34 acts against the axial bearing 32', while the ferrule 33 locks the radial bearing 32 on the right-hand flange 31 , this is a combined bearing in order to ensure the radial and axial stability of the driving shaft 2' and of the stator 2 integral therewith, the cylindrical protuberance 43 of the rotor 2 rests on the inner (thrust) axial bearing 32', this solution shows the possibility of obtaining the aforesaid stability, other solutions (not illustrated) can be obtained, for example with two conical roller bearings or the like which are assembled against the faces of the stator if the space allows it.

In Figures 7, 8 and 9 one can see that on the left-hand end of the driving shaft 2", the end with the hollow center 9, for reasons of space a bushing 37 has been used, which acts as a bearing, any solution, with particular bearings, such as, for example, a ferro fluid bearing or other, roller bearings can substitute the aforesaid bushing (bearings not illustrated).

Figure 10 shows the rotor 2 with the vanes 6 positioned as if they were accommodated in the corresponding slots 1 " of the stator 1 (these can be seen in Fig. 1, one can see the fluid entering under pressure from the center 9 of the driving shaft 2', indicated by the arrow 15, above one can see the same fluid exiting from one of the two radially opposite channels 9', note in particular the vane in position H with the spring 8 that pushes the vane 6 against the cylindrical surface 11 that is coaxial to the inner cylindrical surface of the stator Γ, shown here by a dotted circle, one can see the space 10 (thrust space or cell) formed by the vane H and the peak of the ramp 12 (protuberance), as well as by the two abutment surfaces of the lateral flanges (not shown in this figure), the vane H is not rotating because it is accommodated in the slot of the stator, therefore the pressure of the fluid acts tangentially to the rotor, against the aforesaid protuberance, the arrow 16 symbolizes the pressure of the fluid, the arrow 20 shows the rotor in movement, the vane in position A is about to pass by the peak of the ramp 12 in order to then, without support, end up against the aforesaid cylindrical surface 11 , the cylindrical surface 11 covers one quarter, better if more, of a round angle, the remainder, until it covers half a round angle, is occupied by the divergent surface 12 in the form of a radial ramp, at the point 13, indicated by a symbolic dotted line, the aforesaid cylindrical surface ends and the aforesaid ramp begins, the other half of the surface of the rotor is identical to and opposite from the first, even the second channel 9' exits from the diametrically opposite side of the rotor 2, immediately after the end of the second ramp 12 at the start of the second cylindrical surface 11, both arrows 16 show the simultaneous thrust of the fluid, the two pressures that act simultaneously exert an equal pressure that is directed radially and therefore they do not penalize the bearings of the driving shaft 2'.

One can see the arrows 17 on the channels 6' of the vane 6 (position H) which indicate the fluid that is destined to end up on the bottom of that vane, this entails an increase of thrust in the vane 6 against the cylindrical surface 11 of the rotor 2 which ensures the seal, the arrow 18 shows such thrust which is directly proportional to the pressure of the fluid, one can see that the channels 6' are logically defined on the surface of the vane facing toward the origin of the fluid which exits from the diametrically opposite channels 9'.

The fluid that ends up in the cell formed by the vanes H and G is no longer subjected to thrust, it is not entrained by the rotor 2 and it stays there until such time as the peak of the ramp 12, which skims the inner cylindrical surface Γ of the stator 1 by a few ten thousandths of a millimeter, arrives proximate to the vane H progressively reducing the space down to zero, this happens for all the vanes which are affected one after the other twice after one complete round angle, both in thrust and in outflow, since there are two ramps 12 and they are perfectly mutually opposite.

The arrows 25' show the fluid, which earlier was trapped between one vane and the next, being pushed into the central recess 4 of the ramp 12 owing to the aforementioned reduction in volume, the arrows 25 show the same fluid exiting laterally on the face of the rotor 2 from the arc-like slots 3 that are connected to the aforesaid recess 4, one can further see the vane in the position F which is thrust by the ramp 12 outwardly, sliding in its accommodation slot, the arrow 19 shows the direction and the thrust force which overcomes the force 8' of the spring 8 behind, the arrows 26 on the channels 6' of the vane in position F show the fluid, which earlier penetrated with force during the thrust step, being forced, owing to the aforesaid reduction of space on the accommodation slot, to exit and join the outflowing fluid.

Simultaneously the opposite vane, the one in position B, is also subjected to the same operation, all the vanes 6 twice per revolution of the rotor 2 are affected, one after the other, by the thrust pressure and then by the outflow of the fluid, the simultaneous thrust on the aforesaid protuberances entails a doubled breakaway torque on the driving shaft and a slightly greater torque at speed.

In Figure 11 one can see the driving shaft 2" positioned axially with respect to the insert 30, one can see the annular recess 3' that is defined on the abutment surface and on the bottom of the aforesaid recess one can see the through holes 3", one can also see that the outer diameter of the recess is smaller than the diameter of the cylindrical surface 11 of the rotor 2, the position of the rotor 2 after the calculated approach to the aforementioned insert 30 can be seen from the dotted profile shown on the abutment surface, also note the lines 3/3 that accompany the profile of the arc-like slots 3 in order to show their position as falling within the two circumferences that delimit the aforementioned annular recess 3', one can clearly see the recess 4 on the ramp 12 which is connected with the arc-like slot 3, the arrow 14 indicates the end-of-ramp peak, the arrow 11 indicates the cylindrical surface of the rotor 2 which is coaxial to the inner cylindrical surface Γ of the stator 1, the arrow 13 indicates the end of the cylindrical surface and the start of the diverging surface 12 (ramp), the arrow 14' indicates the point where the ramp ends, the surface of the rotor 2 between the arrow 14' and the arrow 14 is cylindrical and coaxial to that of the stator with a length that is slightly greater than the thickness of the vane, this is in order to prevent the fluid from leaking when the vane arrives at the point 14 during the rotation of the rotor 2.

In Figure 12 one can see the parts of the motor seen in an exploded view, at the top left-hand side there is the left-hand flange 29, note the output hole for the outflowing fluid 28, inside one can see the cylindrical surface 28' which has a greater diameter than that of the insert 30 so as to create a cylindrical annulus that is connected to the through holes 3" of the recess 3', inside the cylindrical surface 28' of the flange 29 one can see the hole 42 which is connected to the outside for an optional connection of the drainage channel and also the through holes 29' for the locking screws, at the center of the insert 30 one can see the bushing 37 for the hollow end of the driving shaft 2', at the top right-hand side one can see the rotor 2, on the ramp one can see the recess 4 with the connected arc-like slot, also note the hole 9' of one of the two delivery channels, at the bottom left-hand side one can see the stator 1 with the through slots 1 " for the vanes, note the threaded holes 38 for the hermetically-sealing shells and the threaded holes 41 for the assembly of the lateral flanges, beside the stator 1 one can see the right-hand lateral flange 31 with the through holes 3 for assembly on the stator 1, the threaded holes 31 " are used to fix the assembled motor to the work point, lastly one can see the ferrule 34 for the driving shaft and the ferrule 33 for the right-hand flange.

Figure 13 shows the left-hand flange 29 with the insert 30 assembled and, to the side, the rotor 2 integral with the driving shaft 2', note in particular the cylindrical part as well, the arrows 15' indicate the fluid exiting under pressure from the diametrically opposite channels 9', the arrows 24 show the outflowing fluid entering the recess 4 of the ramp and passing through the corresponding arc-like slots 3, the arrows 25 show the direction of the outflowing fluid converging at the annular recess 3' of the insert 30, the arrow 27 indicates the fluid flowing out from the hole 28, passing from the aforementioned recess 3' through the through holes 3" inside it, the arrow 15 indicates the fluid under pressure entering in the hollow shaft 2'.

Figure 14 shows a variation of the hydraulic fluid motor according to the invention, in this drawing, one can see a rotor 2 with three delivery channels 9' for the fluid under pressure which enters from the cavity 9 of the shaft 2', the stator 1 is provided with a higher number of vanes and has a greater diameter, one can see three ramps and three arc-like slots 3 for the outflow, the space necessary for the thrust step and for the outflow step increases, and there also needs to be a higher number of vanes in order to ensure operation without causing the rotor to seize, if the vanes were fewer in number and thus spaced further apart from each other then the fluid would flow out before the vane that is intended to thrust had made a seal with the cylindrical surface of the rotor.

This solution entails a breakaway torque multiplied by three, because there are three end-of-ramp protuberances that are subjected to a simultaneous thrust of the incoming pressurized fluid.

This solution can be useful in certain work environments, in particular where a high breakaway torque is necessary.

The rotor may have more than three delivery channels accompanied by corresponding push points and vane reentry points with the corresponding outflow points, and the diameter of the stator and the number of vanes must also be proportional as must the driving shaft and so on.

Another consideration to make is knowing that for every increase in diameter of the motor, as a consequence there is also an increase in the cubic capacity thereof calculated as the cubic centimeters necessary for each complete revolution of the rotor, for every three hundred and sixty degrees, this is common knowledge but it is as well to say it.

Figure 15 shows a second variation of the hydraulic fluid motor, according to the invention, in this variation note that there is a single delivery channel 9' on the rotor 2, this solution entails a rotor 2 and a stator 1 of reduced dimensions, the possibility of reducing the diameters derives from the fact that the cylindrical surface 11 of the rotor 2 covers an angle of at least a hundred and eighty degrees starting from the point 14 and ending at the point 13, the remaining surface diverges to form a cylindrical ramp 12 that ends with the peak at the point 14' almost touching the inner cylindrical surface of the stator 1, from the point 14' to the point 14 the surface of the rotor 2 is again cylindrical and coaxial to the aforementioned inner surface of the stator 1, a distance between the two aforesaid points that exceeds the thickness of the vane in order to not have losses of charge owing to leakage of the fluid under pressure when the tip of the vane is proximate to the point 14.

Note further the arc-like slot 3 for the outflow of the fluid, as explained previously, the fluid exits therefrom in order to pass through the annular recess of the left-hand flange and from this to the outside, the fluid exits owing to the reduction in volume caused by the ramp 12 in rotation which encounters the touching vanes.

A rotor with a single delivery channel penalizes the bearings of the driving shaft because a radial load is created toward the center, in addition the rotating mass is not balanced owing to the difference in machining.

This type of motor, however, can be useful because of the small dimensions that are possible, the breakaway torque is lower than in motors with more delivery channels on the rotor and there may be vibrations as if it were an eccentric rotor, which is nothing serious if the application environment justifies the choice, the principle of operation is still the same.

Looking at Figure 1 one can see the central shaft 2', which is concentric to the inner cylindrical surface of the stator 1, one can see the rotor 2 which is integral with the driving shaft, the surface of the rotor has a specific profile, the arrow 11 shows two cylindrical surfaces that are coaxial to the shaft 2' and also to the inner cylindrical surface Γ of the stator 1, the aforementioned mutually opposite and identical surfaces cover an angle of about ninety degrees from the point 14 to the point 13, their continuation from the point 13 to the point 14' is cylindrical but diverging to form a ramp 12 the peak of which skims the inner surface Γ of the stator 1 by a few ten thousandths of a millimeter, from the point 14' to the point 14 the surface of the rotor is again cylindrical and coaxial to the shaft 2' and to the surface .

In the stator eight through slots 1 " have been defined which are equally spaced apart and are arranged radially, each slot accommodates a calibrated vane 6 that is free to slide internally, each vane has a spring 8 in the central hole 7 of the bottom, the other end of the spring 8 is anchored in the central hole V of the covering or shell 5, each shell has a static gasket seal 5" for a watertight seal which surrounds the aforesaid slot 1 ", in each vane 6 two channels 6' have been defined for the passage of the fluid, for example oil.

Looking at the rotor 2, one can see the hole or central cavity 9 that is connected to two radially opposite channels 9' that exit in the surface of the rotor at the start of the cylindrical surface 11 in the chamber or cell 10, the arrows 8' indicate the constant thrust toward the center which acts constantly on each vane, on the shells 5 a dead slot 5' has also been defined for receiving the vane 6 during the reentry and for accommodating the fluid when it enters and exits via the channels 6' of the vane 6.

On the left-hand face of the rotor 2, the one on the side of the hollow end 9 of the shaft 2', two arc-like slots 3 have been defined which are concentric to the shaft 2', the aforesaid slots are connected to a recess 4 that is defined at the center of the two ramps 12.

Operation of the motor according to the invention is the following, in Figures 1, 2, 3, 4 and 5 one can see the steps, in Figure 1 the motor is stationary, the vanes in position A and F are in contact with the cylindrical surface 11 of the rotor 2, all the other vanes are also in contact with the surface of the rotor that faces the vanes, all are pushed by the force 8' of the spring 8, in Figure 2 the fluid 15 is entering from the center of the driving shaft 9 and with direction 15' propagates through the channels 9' up until the chambers 10, the vanes A and F act as a barrier to the fluid, the arrow 17 shows the fluid also passing via the channels 6' of the aforesaid vanes A and F thus ending up in the bottom thereof, the arrow 18 indicates an increase in thrust toward the center which is proportional to the pressure of the fluid, in this manner the seal is ensured, the arrow 16 shows the pressure of the fluid against the end-of-ramp protuberances and the rotor 2 begins to rotate, the arrow 20 shows the anticlockwise direction, the vanes in position B and G have completely re-entered their slots and are pushed by the spring 8 against the portion of cylindrical surface that skims the inner cylindrical surface Γ of the stator 1.

Figure 3 shows that the rotor 2 has performed one-eighth of a revolution, the vanes B and E now substitute the previous vanes A and F and act as a barrier to the fluid, the fluid 21 that is in the cells between the vanes A and B and between the vanes E and F lacks pressure energy and stays in that position to then be sent to outflow by the action of the aforesaid ramps 12, as one can see the thrust chamber 10 is between the vanes B and C and between the vanes F and G, every one-eighth of a revolution the aforesaid chamber 10 changes the cells following the outflows of the channels 9'.

Figure 4 shows that the rotor 2 has performed another one-eighth of a revolution, one can see the ramps 12 are in contact with the vanes A and E, while the vanes B and F are coming into contact with the aforesaid ramps, as one can see there is no arrow shown on the vanes B and F, this means that they are neutral, on the other hand one can see the arrow 19 on the vanes A and E which indicates the reentry movement into the corresponding slots of the aforesaid vanes which are pushed by the diverging ramp 12, in these two vanes one can see the arrows 26 which show the backflow of the fluid toward the recess 3 that is defined in the center of the corresponding ramp, the fluid 22 trapped between the vanes A and B and between the vanes E and F owing to the reduction in volume must also necessarily enter the aforesaid recess 4 in order to then exit from the connected arc-like slots 3, the fluid 24 exits from the aforesaid slots, the arrows 25 show such outflow, as one can see the thrust steps repeat every one-eighth of a revolution, every one-eighth because there are eight vanes, but the number may vary according to constructional requirements.

Figure 5 shows that the rotor has performed a further quarter turn, now affected by the thrust are the vanes H and D, while in the previous Figure 4 the vanes were G and C, as one can see the cycle is repeated, vane after vane, now the rotor has performed almost a half-turn and the fluid 23 between the vanes A and B and between the vanes E and F is also entering the aforesaid recess 4 in order to join the previous fluid, note in particular that the volume of the fluid 23 is being reduced to zero, the peak of the ramps 12 is approaching the vanes B and F, at this point the rotor will have performed a half-turn, one hundred and eighty degrees and in the other half- turn all the thrust steps will be repeated, the arrow 16 will always be present against the known protuberances, in the outflow the arrows 25 will indicate the passage from the known slots 3 of the fluid 22, 26 and 23, we further note that on the vanes A and E there are no arrows, except the known thrust 8', this is because the two aforementioned vanes are not in motion because they have reached the stroke limit in their accommodation slots.

Now we will look at Figure 10, all the vanes are positioned as if they were accommodated in their respective slots, one can see the arrow 20 which shows that the rotor is rotating, as explained previously the arrows 15' show the fluid under pressure entering the mutually opposite chambers 10, when the fluid under pressure enters from the center of the motor body, the rotor begins to turn as described previously, the fluid passing through the two mutually opposite channels 9' is further projected to the peripheral region, against the inner cylindrical surface of the stator, by way of the centrifugal force produced by the speed of the rotor 2, the liquid in this manner stores a (potential) energy which will be converted to flow-rate or head (or kinetic energy) which will be added to the pressure energy that comes from the delivery channel 9, the motor will therefore have the two aforesaid forms of energy available, which will increase its yield.

Also in Figure 10 one can see the fluid 25' entering the recess 4 owing to the aforesaid reduction in volume owing to the ramps in rotation with respect to the vanes which do not rotate, the arrows 25 show the fluid flowing out from the arc-like slots 3.

In Figure 13 one can see the arrows 25 which show the direction of the fluid and also the point of arrival at the annular recess 3' of the insert 30, in effect the left-hand face (in this case) of the rotor 2 is designed to skim (after mounting) the abutment surface of the insert 30, the fluid as a result of the very fine coupling tolerances must proceed until it flows out of the hole 28 of the left-hand flange 29 first passing through the holes 3" of the aforesaid recess 3' which are connected with an inner annular chamber that is connected to the aforesaid exit hole 28, the arrow 27 shows the outflowing fluid.

One consideration to be made derives from the fact that the rotor can have a radial channel 9' that is connected to the hollow center 9 of the driving shaft 2' (variation of Figure 15), two radially and diametrically opposite channels 9', according to the preferred embodiment described and illustrated in the present patent application, three channels arranged radially and equidistantly (variation in Figure 14) or a plurality of channels if the circumference of the rotor 2 allows it and also according to the breakaway torque that it is desired to obtain.

Summing up, the hydraulic liquid enters under pressure from the hollow shaft and then propagates to the surface of the rotor through one or more channels that are defined internally thereto and are connected to the aforementioned cavity of the driving shaft, the fluid when it comes out on the aforesaid surface meets a vane that acts as a barrier or as a bulkhead and thus discharges the pressure energy onto the single moveable part of the rotor and specifically against the known end-of-ramp protuberance the peak of which skims over the inner cylindrical surface of the stator, the rotation begins and during it the vanes that act as a barrier succeed each other, at the same time, the vanes come into contact with the ramp which forces them to reenter their slot and at the same time the ramp also reduces the aforementioned volume to zero thus causing the outflow to the outside of the liquid through the previously-described channels on the rotor and on the left-hand flange, the foregoing entails the conversion of the pressure energy to mechanical energy on the driving shaft.

An important function of the vanes is to have an incorporated spring valve in order to guard against excess pressure of the thrust oil by making it bypass to the outflow.

Without affecting the principle of operation that governs the invention, the contingent forms, the materials used, and the type of liquid fluid used for the operation of the motor according to the invention can be any and can be modified at any time without for this reason extending beyond the scope of the present inventive concept.

The disclosures in Italian Patent Application No. TV2014A000001 from which this application claims priority are incorporated herein by reference.

Where technical features mentioned in any claim are followed by reference signs, those reference signs have been included for the sole purpose of increasing the intelligibility of the claims and accordingly, such reference signs do not have any limiting effect on the interpretation of each element identified by way of example by such reference signs.

Claims

1. A hydraulic fluid motor/hydraulic motor with vanes which comprises: a driving shaft (2'), a rotor (2), a stator, two lateral flanges for sealing, a delivery channel, an outflow channel, a plurality of vanes (G), bearings, static and dynamic seals, springs for the vanes and external closure means called "shells" (5).

2. The hydraulic fluid motor/hydraulic motor according to claim 1, characterized in that the vanes (6) are accommodated in adapted slots which are provided in the stator casing or stator (1) and not on the rotor as in all eccentric hydraulic motors with vanes.

3. The hydraulic fluid motor/hydraulic motor according to claim 1 or 2, characterized in that the vanes (6) with the spring (8) can be removed from the outside by removing the shells (5) that are screwed to the stator.

4. The hydraulic fluid motor/hydraulic motor according to one or more of the preceding claims, characterized in that the fluid arrives in the thrust chambers (10) through the hollow end (9) of the driving shaft (2') to then proceed via at least one channel (9') of the rotor (2) which is connected to the said hollow end.

5. The hydraulic fluid motor/hydraulic motor according to one or more of the preceding claims, characterized in that the fluid, after having pushed the end-of-ramp protuberance(s) (14), remains trapped between one vane and the next (a cell) and does not rotate together with the rotor (2).

6. The hydraulic fluid motor/hydraulic motor according to one or more of the preceding claims, characterized in that the fluid exiting from the channel (9') acquires energy by way of the centrifugal force which is added to the pressure energy of the delivery.

7. The hydraulic fluid motor/hydraulic motor according to one or more of the preceding claims characterized in that the fluid trapped between one vane and the next is sent to outflow by way of the reduction in volume owing to the action of the ramp(s) (12) in rotation through a space (4) (of the recess type) that is connected with an arc-like opening (3) that is aligned with an annular recess (3') that is defined on the abutment surface of the left-hand flange (29), and then through the internal channels therein to the outside through the chamber (28') and to the threaded opening (28).

8. The hydraulic fluid motor/hydraulic motor according to one or more of the preceding claims, characterized in that each channel (9') of the rotor corresponds to a portion of cylindrical surface (11) that is coaxial to and distanced from, according to the cubic capacity that it is desired to obtain, the inner cylindrical surface ( ) of the stator, followed by a ramp (12) for the outflow of the fluid and which also serves to make the vanes reenter their slots.

9. The hydraulic fluid motor/hydraulic motor according to one or more of the preceding claims, characterized in that the breakaway torque of the hydraulic fluid motor depends on the number of protuberances (14) that are defined on each ramp end (12) which are identical and opposing or equally spaced apart in order to obtain thrust forces that act simultaneously on the rotor in order to not penalize the bearings of the driving shaft, and also in order to prevent vibrations owing to the centrifugal force that acts on the masses of the rotor should they not be equally distributed.