FR3086013A1 - VOLUMETRIC TURBINE AND EXPLOSION ENGINE INCLUDING THIS VOLUMETRIC TURBINE - Google Patents

Abstract

The present invention relates to a volumetric turbine (1) comprising a casing (2) inside which a rotor (3) drives two blades (31) in rotation along a first axis of rotation corresponding to the shaft (30) of the rotor (3), the casing (2) comprising an inlet orifice (22) for fluid and an outlet orifice (23) for fluid. According to the invention, the casing (2) comprises a constriction (25) occupying a radial portion of its volume, the constriction (25) being arranged so as to isolate the intake orifice (22) from the orifice d exhaust (23) while the blades (31) are mounted mobile in rotation according to a second axis of rotation perpendicular to the shaft (30) of the rotor (3) in order to pass through the throttle (25). The present invention also relates to an internal combustion engine (5) incorporating at least one volumetric turbine (1).

Description

Description

Title of the invention: Volumetric turbine and internal combustion engine including this volumetric turbine The present invention is in the field of converting the kinetic energy of a flow of fluid into electrical energy and / or motive energy.

More particularly, the present invention relates to a volumetric turbine generating electrical energy or participating in generating motive energy.

In general, a volumetric turbine comprises a casing in which a rotor drives blades in rotation along an axis of rotation corresponding to the shaft of the rotor. The housing has a fluid intake port and a fluid exhaust port.

Conventionally, the rotor is coupled to an alternator which makes it possible to produce electrical energy when it is driven by the rotor.

[0005] However, it is possible to note recurring problems on the volumetric turbines of the state of the art. More particularly, despite a precise adjustment of the blades to the internal walls of the casing, it is frequent that part of the fluid is not evacuated from the casing when the fluid reaches the fluid exhaust port. The non-discharged fluid is entrained by the blade in a new compression and / or decompression cycle. This problem tends to decrease the efficiency of the volumetric turbine.

In this context, the applicant has developed a technical solution which aims to improve the efficiency of a conventional volumetric turbine through an original technical solution.

More specifically, a first aspect of the present invention relates to a volumetric turbine comprising a housing inside which a rotor drives two blades in rotation along a first axis of rotation corresponding to the rotor shaft, the housing having a fluid inlet port and a fluid exhaust port.

The volumetric turbine is characterized in that the casing has a throttle occupying a radial portion of its volume, the throttle being arranged so as to isolate the intake orifice from the exhaust orifice while the blades are mounted mobile in rotation along a second axis of rotation perpendicular to the rotor shaft in order to pass through the throttle.

Advantageously, the cooperation between each blade, the throttle and the exhaust port makes it possible to optimize the evacuation of the fluid flow at the end of the compression or expansion cycle. This characteristic contributes to optimizing the production yield of electrical energy or motive energy.

According to a first characteristic of the first aspect of the invention, the blades are connected to the rotor shaft through a plate extending within the casing perpendicular to the rotor shaft, each blade is rotatably mounted on the plate along the second axis of rotation.

In particular, each blade is rotatably mounted along the second axis of rotation within an aperture formed on the plate, the aperture having a section corresponding to the longitudinal section of each blade.

According to a second characteristic of the first aspect of the invention, each blade has an axis of rotation providing them with mobility along the second axis of rotation, one end of the axis of rotation being connected to actuating transmission means, upstream and downstream of the throttle, a rotation of each blade along the second axis of rotation. The transmission means comprise a gear piece disposed at the end of the axis of rotation, the gear piece being configured to transmit to the axis of rotation of each blade a 90 ° rotational movement.

In addition, the transmission means comprise a rail mounted fixed relative to the housing, the end of the axis of rotation of each blade being engaged with the rail which comprises two mechanical transmitters respectively arranged downstream and upstream of the constriction so as to cause the rotation of each blade via the end of their axis of rotation.

According to a third characteristic of the first aspect of the invention, the throttle includes a light extending in a plane perpendicular to the shaft of the rotor.

A second aspect of the invention relates to an internal combustion engine which is characterized in that it comprises an intake light connected to the exhaust orifice of a first volumetric turbine designed according to the first aspect of the invention, and ensuring the function of a compression turbine for a fuel / oxidizer mixture.

Advantageously, the use of a volumetric turbine according to the first aspect of the invention as a compression turbine makes it possible to optimally compress the fuel / oxidizer mixture before it is admitted into the engine intake port. explosion. The characteristics of the volumetric turbine of the first aspect of the invention ensure optimal injection of the fuel / oxidizer mixture at the intake port. This optimization increases the efficiency of the internal combustion engine.

According to a first characteristic of the second aspect of the invention, the internal combustion engine comprises an internal combustion chamber connected to a second light-turbining turbine ensuring an expansion turbine function after explosion, the inlet light of the turbine of trigger being connected to the exhaust port of the compression turbine.

According to a second characteristic of the second aspect of the invention, the compression turbine and the expansion turbine are mounted on the same rotor.

According to a third characteristic of the second aspect of the invention, the internal combustion engine has a distribution channel disposed between the exhaust orifice and the intake port, the distribution channel varying between an open state and a closed state as a function of the stroke of at least one blade of the compression turbine and / or the stroke of one blade of the expansion turbine. Preferably, the distribution channel is formed in a distribution disc mounted on the same rotor as the compression turbine and the expansion turbine. Other features and advantages will appear in the detailed description which follows of two examples non-limiting embodiments of the invention which are illustrated by FIGS. 1 to 8 placed in the appendix and in which:

Figure 1 is a representation of a cross section of the housing of a volumetric turbine according to a first embodiment of the invention;

Figure 2 is a representation of a top view of the transmission means ensuring a rotation of the blades along an axis of rotation perpendicular to the axis of the rotor;

Figure 3 is a representation of a side view of the transmission means of Figure 2;

Figure 4 is a representation of a cross section of a housing having three levels of blades distributed in a fluid transfer chamber;

FIG. 5 is a diagrammatic representation of an internal combustion engine in accordance with a second embodiment of the invention, the internal combustion engine being equipped with a compression turbine connected to an expansion turbine through a explosion;

Figure 6 is a representation of a longitudinal section A-A of Figure 5; Figure 7 is a representation of a longitudinal section B-B of Figure 5; and Figure 8 is a representation of a cross section C-C of Figure 5. The invention described in this document relates to a volumetric turbine 1.

As illustrated in Figures 1 and 4 to 8, the volumetric turbine 1 has a housing 2 whose internal walls 20 define a fluid transfer chamber 21. In the present example, the casing 2 has a cylindrical shape. Preferably, the casing 2 has a cylindrical shape with a circular base.

Typically, the casing 2 comprises an inlet orifice 22 which ensures the entry of a pressurized fluid inside the transfer chamber 21. Here, the pressurized fluid can be formed by gas, water, fuel etc.

In this example, the housing 2 also includes an exhaust port 23 for fluid. The exhaust port 23 allows the fluid to be removed after a compression or expansion cycle. The intake port 22 and the exhaust port 23 are arranged at a determined radial distance from each other.

In practice, a new compression or expansion cycle starts when a determined quantity of a flow of fluid enters, via the inlet port 22, into the transfer chamber 21, between two blades 31. At the same time , a compression or expansion cycle ends when a determined quantity of a flow of fluid circulating in the transfer chamber 21 between two blades 21, is evacuated through the exhaust orifice 23.

The housing 2 is equipped with a rotor 3 which extends longitudinally in the fluid transfer chamber 21. Conventionally, the rotor 3 is rotatably mounted relative to a stator 24 secured to the casing 2. The rotor 3 is rotatably mounted around a first axis of rotation. The first axis of rotation corresponds to the shaft 30 of the rotor 3.

In this example, the volumetric turbine 1 comprises at least two blades 31 which are rotated by the rotor 3. The blades 31 are rotated along the first axis of rotation. Here, each blade 31 is delimited by a contour 310 which is adjusted to the internal walls 20 of the casing 2. Thus, the contour 310 of the blades 31 may have a longitudinal section of various geometric shapes. Figures 1 and 4 illustrate a contour 310 of the blade 31 comprising a longitudinal section in the form of a quadrilateral. More particularly in the example in FIG. 4, the contour 310 has a side 311 in contact with the lateral internal walls 20 of the casing 2 which forms an arc of a circle in order to adjust to the internal walls 20 of the casing 2. This shape of the contour 310 of the blade 31 makes it possible to provide, inside the same casing 2, several levels of blades 31 adjusted to each other by their contour 310 having a straight side in common. More specifically and as illustrated in FIGS. 1 and 4 to 7, each blade 31 is connected to the shaft 30 of the rotor 3 through an axis of rotation 312. However, here the axis of rotation 312 is not not configured free to rotate. This characteristic makes it possible to maintain each blade 31 in a plane perpendicular, on the one hand, to the movement of the flow of fluid inside the transfer chamber 21, and on the other hand, to the shaft 40 of the rotor 3. This characteristic makes it possible to optimize the torque of the volumetric turbine 1.

Here, each blade 31 is connected to the shaft 30 of the rotor 3 through a plate 32. The volumetric turbine 1 comprises at least one plate 32. In practice, the plate 32 is integral with the shaft 30 The plate 32 is connected to the shaft 30 through at least two radial fins 33 extending from an inner radial edge 320 of the plate 32 towards the shaft 30. In the example of FIG. 2, the plate 32 is connected to the shaft 30 through four radial fins 33.

The plate 32 extends, in the transfer chamber 21, along a plane perpendicular to the shaft 30 of the rotor 3. Advantageously, the plate 32 has a peripheral edge 34 adjusted to the internal walls 20 of the casing 2.

In order to accommodate each blade 31, the plate 32 has an aperture 35 for each blade 31. The aperture 35 has a section corresponding to the longitudinal section of each blade 31. The aperture 35 is delimited by an edge 350 The border 350 has dimensions slightly greater than those of the contour 310 of the blade 31 that the aperture 35 accommodates. By the dimensions of each blade 31 and of each aperture 35, the outline 310 of each blade 31 is adjusted to the edge 350 of the aperture 35 which receives it.

In the example illustrated in Figures 1 and 7, each blade 31 is rotatably mounted on the plate 32 through its axis of rotation 312. The axis of rotation 312 corresponds to a second axis of rotation which is perpendicular to the shaft 30 of the rotor 3. More particularly, each axis of rotation 312 has a first end 313 engaged in a smooth bearing 36 formed near the peripheral edge 34 of the plate 32.

The axis of rotation 312 includes a second end 314 opposite the first end 313. The second end 314 has a portion engaged in a plain bearing 37 disposed at the inner radial edge 320 of the plate 32.

In addition, each blade 31 is rotatably mounted in an aperture 35 through its axis of rotation, within an aperture 35 formed on the plate 32.

More particularly, each blade 31 is movable between a retracted position and a deployed position.

In the retracted position, a blade 31 extends in the same plane as the plate 32 and closes the opening 35.

In the deployed position, a blade 31 extends in a plane perpendicular to the plate 32 and opposes the flow of fluid moving in the transfer chamber 21.

As illustrated in Figures 1 and 4 to 8, the housing 2 has at least one constriction 25 which occupies a radial portion of the volume of the transfer chamber 21. The constriction 25 comprises a light 250 extending along a plane perpendicular to the shaft 30 of the rotor 3. The light 250 punctually reduces, at the level of said radial portion, the volume of the transfer chamber 21. Preferably, the light 250 is dimensioned so that the plate 32 passes to the through the throttle 25 without friction.

In this example, the constriction 25 is arranged so as to isolate the intake port 22 from the exhaust port 23. Downstream and near a first end 251 the constriction 25 is positioned the inlet orifice 22. While upstream and near a second end 252 of the constriction 25 is positioned the exhaust port 23. The ends 251, 252 of the constriction 25 are opposite l one of the other.

Remarkably, the position of the exhaust orifice 23 upstream of the throttle 23 and the point reduction in the volume of the transfer chamber 21, contribute to optimizing the evacuation of the fluid flow at the end a compression or expansion cycle. These characteristics also contribute to increasing the output of electrical or driving energy production from the volumetric turbine 1. Ingeniously, the mobile nature of the blades 31 along the second axis of rotation perpendicular to the shaft 30 of the rotor 3, allows them to pass through the constriction 25. More particularly, each blade 31 is configured so as to pass into the retracted position when its aperture 35 arrives near the second end 252 of the constriction 25. Conversely, when the aperture 35 of a blade 31 exceeds the first end 251 of the constriction 25, each blade 31 is configured so as to pass from its retracted position to its deployed position.

The cyclical kinematics which results from the structure of the volumetric turbine 1 facilitates its maintenance and optimizes its longevity.

As illustrated in Figures 1 to 4 and 6 to 8, the volumetric turbine 1 comprises transmission means 4. The transmission means 4 ensure the kinematics of each blade 31 and their passage from their retracted position to their deployed position and vice versa. In fact, the transmission means 4 actuate upstream and downstream of the throttle 25 a rotation of each blade 31 along the second axis of rotation.

For these purposes, each blade 31 is connected to the transmission means 4 through its second end 314 of the axis of rotation 312.

In the example illustrated in Figures 3 and 4, the transmission means have a gear piece 40 disposed at the second end 314 of the axis of rotation 312. This gear piece 40 is configured to transmit to the axis of rotation 312 of each blade 31 a rotational movement of 90 °.

In practice, the transmission means 4 comprise a rail 41 mounted fixed relative to the housing 2. In this example, the rail 41 is mounted on the stator 24. The rail 41 forms a circle whose central axis corresponds to the shaft 30 of the rotor 3.

Thus, the second end 314 of the axis of rotation 312 of each blade 31 is engaged, via the engagement piece 40, with the rail 41. In operation, the engagement piece 40 slides on the rail 41 with the sandstone of the rotation of the plate 32. The rail 41 keeps the engagement piece 40.

In order to transmit a rotational movement of 90 ° to the axis of rotation of each blade 31 upstream and downstream of the throttle 25, the rail 41 comprises two mechanical transmitters 42. The two mechanical transmitters 42 occupy respective positions corresponding to the downstream position and the upstream position of the throttle 25. Thus, the mechanical transmitters 42 cooperate with the engagement part 40 so as to cause a rotation of 90 ° of each blade 31 causing it to pass from its deployed position to its retracted position and vice versa.

As illustrated in Figures 2 and 3, the engagement piece 40 is formed by a quadrangular piece. The quadrangular part has two lateral faces 400 connected by four edges 401. Furthermore, the four edges 401 are connected to each other by stops 402. Each stop 402 is countersunk thus forming a notch 404 extending from a lateral face 400 to the other. The quadrangular part comprises a through hole 403 and corresponding to the central axis of each lateral face 400. The hole 403 makes it possible to secure the engaging part 40 at the second end 314 of the axis of rotation 312.

In this example, the engagement piece 40 slides on the rail 41 on a wafer 401 between each mechanical transmitter 42. At each mechanical transmitter 42, the rail 41 has a recess 43. The mechanical transmitter 42 is formed by a rod 44 secured to the stator 24 and perpendicular to the rail 41. The rod 44 is secured to the stator 24 on either side of the recess 43 (illustrated in FIG. 3). Here, the rod 44 extends above the recess 43 of the rail 41.

Thus, when the engagement piece 40 comes into contact with the mechanical transmitter 42, the notch 404, in the proximal position of the mechanical transmitter 42, engages in the rod 44 which induces a rotation of 90 ° of the piece d meshing 40. The meshing piece 40 transmits the rotational movement of 90 ° to the axis of rotation 312 of the blade 31.

In practice, by design of the transmission means, each blade 31 has two deployed positions and two retracted position. The two deployed positions and the two retracted positions are identical due to the symmetrical design of each blade 31.

In the example of Figure 4, the volumetric turbine 1 has three plates 32 which extend respectively in the transfer chamber 21 according to three different levels. Advantageously, a constriction 25 is arranged on the rotation stroke of each plate 32. Preferably, the three constrictions 25 are superimposed, that is to say, that the three constrictions 25 are located at the same position of the casing 2, according to three different levels. Indeed, the first end 251 and the second end 252 of each constriction 25 are located on the same axis which extends longitudinally relative to the casing 2.

In addition, each plate 32 carries at least two blades 31 also mounted movable in rotation between two positions, a deployed position and a folded position.

In this example, in order to simultaneously actuate each blade 31 arranged on three different plates, the transmission means 4 comprise a first rail 411 secured to the stator 24 disposed on a first side 26 of the casing

2. The first rail 411 is secured to the stator 24 through a set of lugs 412 which hold the rail 411 away from the stator 24.

It should be noted that the first rail 411 has a first portion 413 which extends in a plane proximal to the stator 24. In addition, the first rail 411 comprises a second portion 414 of the stator 24 which extends in a distal plane of the stator 24. The first portion 413 is disposed at a shorter distance from the stator 24 than the second portion 414. The distance between the first rail 411 and the stator 24 is determined by the length of the legs 412.

Remarkably, the passage from the first portion 413 to the second portion 414 coincides with the passage of each blade 31 from its deployed position to its retracted position and vice versa.

The transmission means 4 comprise a second rail 416 secured to the stator 24 and disposed on a second side 27 of the casing 2. Parallel to the first rail 411, the second rail 416 is secured to the stator 24 by lugs 412. The second rail 416 also includes a first portion 413 and a second portion 414, however their position is reversed relative to their position on the first rail 411.

Furthermore, the second end 314 of each blade 31 is connected through its engagement piece 40 to a rod 45. The rod 45 has two ends 450 respectively connected to the first rail 411 and to the second rail 416.

Thus, the configuration of each rail 411, 416 and their portions 413, 414 induce a translational movement of the rod 45 as a function of the travel of its ends 450 on the rails 411, 416.

Advantageously, the engagement piece 40 is rotatably mounted relative to the rod 45. This design allows it to transform the longitudinal translational movement of the rod into rotational movement, thus causing the axis of rotation 312 of the blades 31.

This specific design of the transmission means 4 forms a cam mechanism which makes it possible to synchronize the rotation of each blade 31 arranged in the same position on different plates 32.

It is thus possible to optimize the design of the volumetric turbine 1 by providing, inside the casing 2, a determined number of plates 32 over several stages.

The staging of synchronized plates 32 makes it possible to optimize the output of electrical energy or motive power from the volumetric turbine

1.

In the example illustrated in Figures 5 to 8, the positive displacement turbine 1 is integrated with an internal combustion engine 5. In this example the positive displacement turbine 1 performs the function of a compression turbine 10 of a fuel / oxidizer mixture which is inserted into the inlet 22.

Typically, the internal combustion engine 5 includes an explosion chamber 50 which includes an intake port 51. The compressed fuel / oxidizer mixture enters the explosion chamber 50 through the intake port 51. The chamber with an explosion 50 also comprises a volumetric turbine 1 ensuring the function of an expansion turbine 100 after explosion. In order to trigger the explosion, the explosion chamber 50 is equipped with at least one spark plug 52. Preferably, the compression turbine 10 and the expansion turbine 100 are mounted on the shaft 30 of the same rotor 3. In order to release the exhaust gases from the explosion, the expansion turbine 100 has an exhaust port 55 disposed upstream of its throttle 25 (illustrated in FIG. 8).

In this example, the intake port 51 is connected to the exhaust port 23 of the compression turbine 10. For this purpose, the internal combustion engine 5 has a distribution channel 53 disposed between the port exhaust 23 and the intake port 51. More particularly, the distribution channel 53 varies between an open state and a closed state as a function of the stroke of at least one blade 31 of the compression turbine 10 and / or the stroke of at least one blade 31 of the expansion turbine 100.

The distribution channel 53 is configured so as to pass from its closed state to its open state when a blade 31 of the compression turbine 10 arrives near the first end 251 of the throttle 25. At the same time, fact that the compression turbine 10 and the expansion turbine 100 are mounted on the same shaft 30, a blade 31 of the expansion turbine 100 arrives near the second end 252 of its throttle 25 when the distribution channel 53 passes from its closed state to its open state. Following this synchronization, the explosion chamber 50 is temporarily formed cyclically during the passage of the distribution channel 53 in its open state.

Thus, the synchronization of the operation of the compression turbine 10, the expansion turbine 100 and the distribution channel 53 makes it possible to optimize the transfer of the fuel / oxidant mixture from the compression turbine 10 to the expansion turbine 100.

In this example, the distribution channel 53 is formed in a distribution disc 54 mounted on the same rotor 30 as the compression turbine 10 and the expansion turbine 100. The distribution disc 54 rotates within a housing 56 which is specific to it (illustrated in FIGS. 5, 6 and 8).

However, the distribution channel 53 could also be equipped by any means allowing it to pass from an open state to a closed state and vice versa. For example, the distribution channel 53 may include a solenoid valve fulfilling this function.

The cooperation between the compression turbine 10, the expansion turbine 100, the distribution channel 53 and the explosion chamber 50 makes it possible to optimize the efficiency of the internal combustion engine 5.

As illustrated in Figures 5 to 8, the expansion turbine 100 is built on the same principle as the compression turbine 10 but has some design adjustments so as to optimize the transformation of the kinetic energy induced by the explosion in motor energy.

For this purpose, it is necessary that the pressure tapping space defined between two blades 31 is sealed. As illustrated in FIGS. 5 to 8, the expansion turbine 100 includes sealing means in the form of sets of segments. In particular, the constriction 25 comprises sets of segments 253 which extend radially within the lumen 250. The sets of segments 253 can be disposed at the only ends 251, 252 of the constriction 25. However, it is also possible to have sets of segments 253 with regular spacing between each end 251, 252 of the throttle 25. By optimizing the sealing of the throttle 25, the sets of segments 253 contribute to improving the torque of the expansion turbine 100.

In this context, the blades 31 have a circular contour 310 which facilitates segmentation. Indeed, a set of segments 315 is arranged on the contour 310 of the blade 31 in order to ensure the sealing of the plate 32 when the blade 31 is in the retracted position.

Furthermore, the casing 2 is also equipped with sets of segments 28 which extend around the periphery of the internal walls 20 on either side of the plate 32. The peripheral edge 34 of the plate 32 is thus fitted in a U-shaped profile created by a set of segments 28 above the plate 32 and a second set of segments 28 disposed below the plate 32.

As illustrated in Figures 5 to 7, the casing 2 can also include sets of segments 57 arranged on the internal walls of the housing 56. These sets of segments 57 make it possible to seal the housing 56 and if necessary transfer of the fuel / oxidizer mixture when the distribution channel 54 passes into its open state.

The throttle 25 may include at least one lubricator 253 for lubricating the plate 32. This characteristic makes it possible to optimize the longevity of the expansion turbine 100 and to facilitate its maintenance.

As illustrated in Figures 5 and 6, the compression turbine 10 and the expansion turbine 100 both have a throttle 25. Although mounted on the same rotor 3, the throttle 25 of each turbine 10,100 is offset radially. This configuration optimizes the transfer of compressed fuel / oxidizer. Indeed, the transfer takes place at the end of the compression cycle while a blade 31 of the compression turbine 10 arrives upstream of the throttle 25 and a blade 31 of the expansion turbine 100 begins a new cycle of expansion downstream of the throttle 25 of the expansion turbine 100.

Advantageously, the kinematics of the internal combustion engine 5 involves continuous admission at the intake port 22 of the compression turbine 10. At the same time, the exhaust port 55 of the expansion turbine 100 also achieves a continuous exhaust.

The kinematics of a conventional combustion engine causes an angular variation of the crankshaft relative to the connecting rod, however, the torque is optimal only when the crankshaft and the connecting rod are perpendicular. Conversely, according to the invention each blade 31 of the expansion turbine extends in a plane perpendicular to the shaft 30 of the rotor 3 throughout its effective stroke which corresponds to its stroke in pressure tap. This characteristic makes it possible to optimize the torque of the internal combustion engine 5.

In addition the use of two volumetric turbines 1 respectively fulfilling a function of compression turbine and expansion turbine, both coupled with a distribution channel 53 ensures compactness of the internal combustion engine 5. As an indication, this compactness parameter can be interesting in the context of a hybrid vehicle.

The design of the internal combustion engine 5 tends to reduce manufacturing costs by a reduced number of parts compared to a conventional internal combustion engine. Furthermore, the continuity of the kinematics of the rotation movement of the compression turbine and of the expansion turbine makes it possible to increase the longevity of the internal combustion engine 5 compared to a conventional engine whose piston and crankshaft work according to reciprocating motion causing energy loss.

Claims (12)

Claims 1. Volumetric turbine (1) comprising a casing (2) inside which a rotor (3) drives two blades (31) in rotation according to a first axis of rotation corresponding to the shaft (30) of the rotor (3) , the casing (2) comprising an inlet orifice (22) for fluid and an outlet orifice (23) for fluid, characterized in that the casing (2) comprises a throttle (25) occupying a radial portion of its volume, the throttle (25) being arranged so as to isolate the intake orifice (22) from the exhaust orifice (23) while the blades (31) are mounted movable in rotation along a second axis of rotation perpendicular to the shaft (30) of the rotor (3) in order to pass through the throttle (25). 2. Volumetric turbine (1) according to claim 1, characterized in that the blades (31) are connected to the shaft (30) of the rotor (3) through a plate (32) extending within the casing (2) perpendicular to the shaft (30) of the rotor (3), each blade (31) is rotatably mounted on the plate (32) along the second axis of rotation. 3. Volumetric turbine (1) according to claim 2, characterized in that each blade (31) is rotatably mounted along the second axis of rotation within an aperture (35) formed on the plate (32), the aperture (35) having a section corresponding to the longitudinal section of each blade (31). 4. Volumetric turbine (1) according to one of claims 1 to 3, characterized in that each blade (31) has an axis of rotation (312) providing them with mobility along the second axis of rotation, one end (314) of the axis of rotation (312) being connected to transmission means f <4 \ Js v »t * j .Sî t * ï t * zs ΓΠ f *} ss.r? λ λ y if Ί î ^ ssî Ί! ss. 4 “? · * Λ> · * · ΐ ·> ssi'mss.'n“ îi j SZX Vm * i XX XSZXX AXX SZXX ί X · * · * ZZ> A v * X »xZ» jSLX X * ZZ1 L LsZZ ί ί L ”(25), a rotation of each blade (31) along the second axis of rotation. 5. Volumetric turbine (1) according to claim 4, characterized in that the transmission means (4) comprise a meshing piece (40) disposed at the end (314) of the axis of rotation (312), the engagement piece (40) being configured to transmit to the axis of rotation (312) of each blade (31) a rotational movement of 90 °. 6. Volumetric turbine (1) according to one of claims 4 and 5, characterized in that the transmission means (4) comprise a rail (41) mounted fixed relative to the housing (2), the end (314) of the axis of rotation (312) of each blade (31) being engaged with the rail (41) which (42) respectively arranged downstream and upstream of Ι / '¢ 24¼ t * · "" SiTrî ^ st * · . * hi OR \ msni ¢ 24 y * ¢ 24 »y * a * ï Ί si a * h τ γιυ'ϊ * kk> Lk * k · CÂl <1 · tZ * k 1 kkt Ç f% * 4> * kk > At U “Ü k <ka x2> A * * kk> CA Qkk AA Lk“ k ”CA“ kk Λ A * Zk J · kL ”îZw <kk * k * Xk * <A> * kX AA VA · ΖΪ each blade (31) via the end (314) of their axis of rotation (312). 7. Volumetric turbine (1) according to one of claims 1 to 6, characterized in that the constriction (25) comprises a lumen extending along a plane perpendicular to the shaft (30) of the rotor (3). 8. Internal combustion engine (5), characterized in that it comprises an intake light (51) connected to the exhaust orifice (23) of a first volumetric turbine (1) designed according to one of claims 1 to 7 and providing a compression turbine function (10) of a fuel / oxidizer mixture. 9. Internal combustion engine (5) according to claim 8, characterized in that it comprises an internal combustion chamber (50) connected to a second volumetric turbine (1) providing an expansion turbine function (100) after explosion, the intake port (51) of the expansion turbine (100) being connected to the exhaust port (23) of the compression turbine. 10. Internal combustion engine (5) according to claim 9, characterized in that the compression turbine (10) and the expansion turbine (100) are mounted on the same rotor (30). 11. Internal combustion engine (5) according to one of claims 8 to 10, characterized in that it possesses a channel of 5 distribution (53) arranged between 1 'orifice of exhaust (23) and the intake light (51), the channel distribution (53) varying between a open state and a state closed as a function of the stroke of at least one blade (31) of the compression turbine (10) and / or of the stroke 10 of a blade (31) of the expansion turbine (100). 12. Internal combustion engine (5) according to claim 11, characterized in that the distribution channel (53) is formed in a distribution disc (54) mounted on the same rotor (30) as the compression turbine (10) and the expansion turbine (100).