The present invention refers to a thermal rotary motor. Thermal motors comprising eccentric stators and rotors, hydraulic vane motors are known in the state of the art.

Disadvantageously, the thermal motors of the prior art develop a low torque. The object of the present invention consists in realising a thermal rotary motor which is capable of developing a very high torque capable of moving very heavy loads of the order of weight of tons.

According to the invention, such aim is reached with a motor according to claim 1.

Other features are comprised in the dependent claims.

The features and advantages of the present invention will be more apparent from the following description, which is to be understood as exemplifying and not limiting, with reference to the appended schematic drawings, wherein:

Figure 1 is an uncovered top view of the motor according to the present invention; Figure 2 is a sectional view of Figure 1.

With reference to the aforementioned figures, a motor 100 is shown comprising a stator 20 comprising a body 22 and a cavity 200 carved inside the body 22.

The stator 20 comprises two base walls 29, an upper base wall and a lower base wall and inner walls 28 rising upwards in a vertical direction starting from the lower base wall until reaching the upper base wall. The two base walls 29 and the inner walls 28 define the cavity 200 of the stator 20.

The motor 100 comprises a rotor 10 housed inside the cavity 200. The rotor 10 is rotatably mounted with the stator 20 and rotates around a pivot axis R.

The rotor 10 is of cylindrical shape and comprises a discoidal body 11 which comprises outer walls 18 and two circular base walls 12, an upper circular base wall and a lower circular base wall. The outer walls 18 rise in a vertical direction starting from the lower circular base wall until reaching the upper circular base wall. Each circular base wall 12 comprises a geometric diameter which is smaller than the horizontal geometric dimensions of the base walls 29 of the stator 20. Each circular base wall 12 comprises a geometric centre Cl.

The motor 100 comprises a shaft 30 fixedly mounted with the rotor 10 and placed along the pivot axis R.

The pivot axis R is a vertical geometric axis passing through the geometric centre Cl and is perpendicular to first horizontal geometric planes identified respectively by the base walls 29 of the stator 20 and to second horizontal geometric planes identified respectively by the circular base walls 12 of discoidal body 11 of the rotor 10.

The stator 20 has a shape which substantially follows a geometric cylinder.

The stator 20 comprises a cylindrical portion 282 which accurately follows the geometric cylinder. The inner walls 28 of the cylindrical portion 282 and the two base walls 29 of the cylindrical portion 282 of the stator 20 form a portion of the geometric cylinder. Each of the two base walls 29 comprises a portion of circular base wall that comprises a geometric centre, which, projected vertically on the pivot axis R, coincides with the geometric centre Cl of the circular base walls 12 of the discoidal body 11 of the rotor 10, as shown in figure

1.

The stator 20 comprises an oval portion 280 which is flattened along a radial direction in such way as to reduce the geometric radius of the geometric cylinder so that an outer wall portion 18 of the discoidal body 11 of the rotor 10 rotates in contact with the inner wall 28 of a first portion 281 of the oval portion 280 of the stator 20 as shown in Figure 1.

The first portion 281 of the stator 20 comprises a geometric set of tangent points, which define a tangency between the rotor 10 and the stator 20, wherein the tangent points are placed along a vertical geometric line.

The rotor 10 comprises a multiplicity of radial housings 14 carved inside the discoidal body 11.

Each radial housing 14 of the multiplicity of radial housings 14 comprises a through opening 15 carved on said outer walls 18 inside the discoidal body 11. The through opening 15 sets the inside of the radial housing 14 in communication with the cavity 200.

The rotor 10 comprises a multiplicity of elastic means 45. Each elastic means 45 of the multiplicity of elastic means 45 is housed inside a respective radial housing 14 of the multiplicity of radial housings 14. Each elastic means 45 is adapted to pass from a position of maximum compression to a position of maximum elongation. The position of maximum compression corresponds to a position of minimum elongation. The rotor 10 comprises a multiplicity of blades 40. Each blade 40 of the multiplicity of blades 40 is mounted with an elastic means 45 of the multiplicity of elastic means 45 and is in a thrust position against inner walls 28 of the stator 20 and in a sliding position against the two base walls 29 of the stator 20.

During the rotation of the rotor 10 around the pivot axis R each blade 40 of the multiplicity of blades 40 always remains in a thrust position against inner walls 28 of the stator 20 and in a sliding position against the two base walls 29 of the stator 20.

Preferably each blade 40 comprises an end 48 which remains in thrust contact against the inner walls 28 of the stator 20 throughout the rotation of the rotor 10.

The end 48 of the blade 40 comprises cross sections of rectangular shape so as to be able to have a greater contact surface against the inner walls 28 of the stator 20.

The blade 40 remaining in thrust position against inner walls 28 of the stator 20 passes from a first position where the blade 40 is completely inside the housing 14 which corresponds to the position of maximum compression of the elastic means 45 to a second position where a greater portion of the blade 40 is outside the housing 14, which corresponds to the position of maximum elongation of the elastic means 45.

The blade 40 is in the first position when, during the rotation of the rotor 10, the outer wall 18 of the discoidal body 11 of the rotor 10 is in contact with the inner wall 28 of the first portion 281 of the oval portion 280 of the stator 20.

The blade 40 is in the second position when, during the rotation of the rotor 10, the end 48 of the blade 40 is in contact with the inner walls 28 of the cylindrical portion 282 of the stator 20.

The blade 40 is in an intermediate position between the first and the second position when, during the rotation of the rotor 10, the end 48 of the blade 40 is in contact with the inner walls 28 of other portions of the oval portion 280 of the stator 20.

The invention is based on a thermal expansion of the fluid which remains in the liquid phase, but which is in volumetric expansion due to the increase in temperature.

The fluid used is alcohol in the liquid phase, or mercury in the liquid phase, or other liquids capable of having a strong thermal expansion caused by a heat exchanger 70 of the motor 100.

A multiplicity of spheres or microspheres made of a material adapted to expand more due to thermal heating, for example a metal with high thermal expansion, can also be immersed inside the fluid, giving the fluid greater pressure against the blades 40 and making the action of the motor 100 more effective.

As shown in Figure 1, the motor 100 comprises a fluid feeder 60.

The fluid feeder 60 comprises a heating chamber 73. The heat exchanger 70 is mounted with the heating chamber 73 to heat the fluid contained in the heating chamber 73 keeping it in the liquid phase.

The heat exchanger 70 is advantageously able to increase the temperature of the fluid causing it to expand violently but remaining in the liquid phase.

The heat exchanger 70 is for example an electric coil placed around the heating chamber 73.

Inner walls 28 of the oval portion 280 of the stator 20 comprise a inlet through opening 26. The through opening 26 connects in fluid connection the cavity 200 with the heating chamber 73 so as to increase the temperature of the fluid before entering a first narrow volume 211 of the cavity 200.

During operation, the blades 40 receive a fluid dynamic thrust caused by a change in the volume of the heated fluid in the heating chamber 73 where the fluid is heated before entering a first narrow volume 211 of the cavity 200 through the through opening 26.

As shown in particular in Figure 1, the rotor 10 comprises twelve housings 14 placed along radial axes spaced of angles of thirty sexagesimal degrees from one another so as to be advantageously spaced of the same measure along an arc of geometric circumference that follows the circular base wall 12 of the discoidal body 11 of the rotor 10. The angles are measured on the circular base wall 12 of the discoidal body 11 of the rotor 10. Corresponding twelve blades 40 and twelve elastic means 45 are provided, each placed inside the respective housing 14.

The cavity 200 of the stator 20 comprises a multiplicity of narrow volumes 21.As shown in Figure 1, the narrow volumes 21 are twelve.

Each narrow volume 21 of the multiplicity of narrow volumes 21 is comprised between two consecutive blades 40, the outer wall 18 of the discoidal body 11 of the rotor 10, the inner wall 28 of the stator 20 and the upper and lower base walls 29 of the stator 20.

A same narrow volume 21 of the cavity 200 can be further subdivided into smaller volumetric portions by means of a greater number of blades 40.

The narrow volume 21 which is placed at the outlet of the inlet through opening 26 is called the first narrow volume 211.

Advantageously, the inlet through opening 26 is carved in a portion of the inner wall 28 of the oval portion 280 of the stator 20 at a short angular distance from the first portion 281 of the oval portion 280 of the stator 20 as shown in Figure 1, where a short distance means that the inlet through opening 26 opens a passage to the fluid coming from the heating chamber 73 towards the first narrow volume 211.

The first narrow volume 211 is still more advantageously narrow, in fact it comprises the first portion 281 of the oval portion 280 of the stator 20.

The fluid that is suddenly heated in the heating chamber 73 undergoes a sudden thermal change and the fluid volume change forces the fluid to violently enter through the inlet through opening 26 towards the inside of a first narrow volume 211 of the cavity 200.

The first narrow volume 211 has a volume which corresponds to a fluid volume change caused by the heating of the fluid itself in the heating chamber 73.

The body 22 of the stator 20 comprises a housing 23 adapted to rotatably mount at least a first end 31 of the shaft 30, where the housing 23 is placed along the pivot axis R and houses rotation means 80 adapted to allow a rotation of the first end 31 of the shaft 30 around the pivot axis R.

The rotation means 80 are ball bearings or other equivalent rolling elements which are adapted to allow a rotation of the shaft 30 around the pivot axis R, reducing friction.

At least one of the base walls 29 of the stator 20 comprises at least one drain 50 adapted to allow the passage of the fluid from the cavity 200 towards the outside.

As shown in Figure 2, a multiplicity of drains 50 is provided, for example six drains 50, that is, one drain 50 for every two consecutive volumetric portions 21 into which the cavity 200 is subdivided.

The heated fluid enters the first narrow volume 211, thrusts the blade 40 causing the rotor 10 to rotate and the fluid outflows from a first drain 51 of the multiplicity of drains 50.

Almost all of the fluid that entered the first narrow volume 211 will exit from the first drain 51. The other drains 50 are provided to allow the exit of residual portions of the fluid which may remain inside the cavity 200.

Advantageously, in order to recycle the fluid exiting the drains 50, the fluid feeder 60 is connected to said drains 50 by means of channels 55.

As shown in Figure 2, the fluid feeder 60 comprises still more advantageously a first accumulation chamber 71 for the fluid which is connected in fluid communication with the multiplicity of drains 50. The first accumulation chamber 71 is adapted to contain the fluid discharged from the cavity 200.

Preferably, the motor 100 advantageously comprises also a tank (not shown in the figures).The tank is in fluid communication by means of the channels 55 both with said at least one drain 50 and with the first accumulation chamber 71 of the fluid feeder 60. A valve

89 is mounted between the channel 55 and the first accumulation chamber 71. The tank works like a radiator and receives the fluid outflowing from the drain 50, cools it by passing it, for example, in a cooling coil and then re-introduces it into the fluid feeder 60 to re-introduce it into the cavity 200 and make the cycle of the fluid advantageously closed for a greater fluid recycling.

Preferably the cooling radiator is ventilated to decrease the fluid temperature more quickly.

It is still more preferably provided, as shown in Figure 2, that the shaft 30 comprises a cam 93 and that the first accumulation chamber 71 comprises a first elastic means 91 and a first piston 81 elastically moved by the first elastic means 91.

The cam 93 comprises an elliptical or oval disc or in any case comprises an asymmetrical portion.

The first elastic means 91 tends to thrust the first piston 81 towards the cam 93.

When the shaft 30 rotates around the pivot axis R, the cam 93 thrusts the first piston 81 alternately over time so that the piston 81 passes from a position of greater compression of the fluid inside the first accumulation chamber 71 to a position of less compression of the fluid inside the first accumulation chamber 71.

Still more preferably the fluid feeder 60 as shown in Figure 1 can comprise a second accumulation chamber 72. The second accumulation chamber 72 is connected in fluid connection with the first accumulation chamber 71 by means of a first channel 61 of the fluid feeder 60. A valve 88 is provided between the first accumulation chamber 71 and the second accumulation chamber 72.

Still more advantageously it is provided that the first channel 61 comprises a first valve 84 adapted to control the flow of the fluid from the first accumulation chamber 71 to the second accumulation chamber 72.

The fluid which is thrusted by the first piston 91 and which passes from the first accumulation chamber 71 to the second accumulation chamber 72 is accumulated in the second accumulation chamber 72.

The second accumulation chamber 72 is connected in fluid connection with the heating chamber 73 by means of a second channel 62 of the fluid feeder 60 which is also equipped with a second valve 83 adapted to control the flow of the fluid from the second accumulation chamber 72 to the heating chamber 73 Furthermore, the second valve 83 advantageously protects the second accumulation chamber 72 from any backflows of the fluid heated in the heating chamber 73.

The mass of fluid circulating in the motor 100 is much greater than that contained in the second accumulation chamber 72 and in the heating chamber 73.

Still more advantageously, the second accumulation chamber 72 further comprises a second elastic means 92 and a second piston 82 elastically moved by the second elastic means 92.

When the pressure of the fluid inside the heating chamber 73 drops below a predetermined pressure threshold then the second piston 92 thrusts the fluid from the second accumulation chamber 72 towards the heating chamber 73 to bring the pressure of the fluid contained inside of the heating chamber 73 back to the predetermined pressure. As regards the operation of the motor 100, the heated and volume-dilated fluid violently enters the first narrow volume 211 of the cavity 200. The heated and dilated fluid, while remaining in the liquid phase, thrusts the blades 40 of the first narrow volume 211, the inner walls 28 of the stator 20 and the outer walls 18 of the rotor 10 at the first narrow volume 211, causing the rotor 10 to rotate around the pivot axis R. The blades 40 advantageously allow obtaining a greater thrust of the fluid since they increase the wall of the rotor 10 exposed to the fluid. The blades 40 contribute to the rotation of the rotor 10 thanks to the thrust of the fluid that is present in the first narrow volume 211 of the cavity 200 of the stator 20. The fluid thrusts on the projecting part of the blade 40 which is outside the rotor 10 and creates a pressure force which is tangent to the rotor 10 forcing it to rotate around the pivot axis R and creating an extremely high torque to thrust very heavy loads.

Advantageously, the motor 100 is a thermal rotary motor which is capable of developing a very high torque capable of moving very heavy loads of the order of weight of tons.

Advantageously, the motor 100 operates with a fluid which remains in a liquid state and in the case of alcohol it is ecologically sustainable.

Advantageously, the motor 100 allows the fluid to be used in a closed cycle, being ecologically sustainable.

Advantageously, the rotor 10 of the motor 100 according to the present invention turns at low speed, that is at 5 or 6 revolutions per minute, given the fact that it develops a very high torque.

Alternatively, it is provided that the heat exchanger 70 is a flame fed by a gaseous comburent and that the flame is placed to heat the heating chamber 73.

Alternatively, a drain 50 for each volumetric portion 21 is provided into which the cavity 200 is subdivided.

Alternatively, it is possible to provide that the housings 14 are in a number other than twelve, for example that they are six. In this alternative, the six housings 14 are placed along radial axes spaced of angles of sixty sexagesimal degrees from each other so as to be advantageously spaced of the same measure along the arc of geometric circumference. If the housings 14 were different in number from six or twelve, then it would be necessary to ensure that the housings 14 are spaced from each other of the same measure along the arc of geometric circumference .

Alternatively, it is provided that the blades 40 are replaced by pistons.

Alternatively, it is possible to provide a multiplicity of accumulation chambers 71, 72 of the fluid feeder 60 upstream of the heating chamber 73. Advantageously, a greater number of accumulation chambers 71, 72 allows to better regulate the flow of the fluid towards the heating chamber 73.

Alternatively, it is possible to provide that the flow feeder 60 comprises a single accumulation chamber 71, 72.

Alternatively, it is possible to provide that the inlet through opening 26 is carved in a base wall 29 of the stator 20 in order to insert the fluid inside the first narrow volume 211 of the cavity 200.

Alternatively, at least one of the base walls 29 of the stator 20 comprises a single drain 50.

Alternatively, it is provided that the blades 40 can be fitted with gaskets.

Alternatively, an alternative stator 20 is provided which is not shown in the figures. The alternative stator 20 comprises a cylindrical-shaped cavity 200 comprising two alternative base walls 29 which are circular. Each first circular alternative base wall 29 comprises a second geometric centre C2 which is spaced of a horizontal measure D with respect to the geometric centre Cl, in which the horizontal measure D is measured on the base wall 29. According to this alternative, the second geometric center C2 is spaced of the horizontal measure D from the geometric centre Cl so that the outer wall portion 18 of the discoidal body 11 of the rotor 10 rotates in contact with the inner wall 28 of the first portion 281.

Still alternatively, it is possible to provide that the stator 20 comprises two oval portions 280 and that the rotor 10 rotates in contact with the inner wall 28 of two first portions 281 of the two oval portions 280 of the stator 20. The two oval portions 280 are opposite each other with respect to the geometric centre of the rotor 10.

Still alternatively it is possible to provide for four oval walls 280 to be opposite each other.

Still alternatively, it is also possible to provide for an inlet through opening 26 for each oval wall 280.

The invention thus conceived is susceptible to many modifications and variants, all falling within the same inventive concept; furthermore, all details can be replaced by equivalent technical elements. In practice, the materials used, as well as the dimensions thereof, can be of any type according to the technical requirements.