EP1649142A1

EP1649142A1 - Compressed air rotary engine

Info

Publication number: EP1649142A1
Application number: EP04767760A
Authority: EP
Inventors: André-Laurent BERNARD
Original assignee: BERNARD Cecile
Current assignee: BERNARD Cecile
Priority date: 2003-07-24
Filing date: 2004-07-22
Publication date: 2006-04-26
Anticipated expiration: 2024-07-22
Also published as: CN1829854B; ATE422601T1; CN1829854A; EP1649142B1; WO2005010322A1; DE602004019421D1

Abstract

The invention relates to a compressed air engine comprising a stator (1) and a rotor (2), cylinders and concentrics describing a volume chamber (V), at least one pipe (P) for supplying compressed air to at least one decompression chamber (Va) belonging to said volume (V) and defined by a piston (7) and retractable bottom (8) and at least one pipe (6) for removing residual air (R) at the end of a decompression cycle. The inventive engine is characterised in that each air supply pipe (5) is connected to means for injecting a defined quantity and volume of compressed air into the decompression chamber when the piston (7) moves on the supply pipe (5).

Description

ROTARY COMPRESSED AIR ENGINE DESCRIPTION

FIELD OF THE INVENTION

The invention relates to a rotary compressed air motor essentially comprising:

- a cylindrical and concentric stator and rotor;

- A chamber delimited, longitudinally, by the cylindrical walls facing said stator and said rotor and, laterally, by two facing flanges;

- At least one pressure air inlet pipe in at least one decompression chamber belonging to said volume and at least one pipe for discharging residual air at the end of the decompression cycle; each decompression chamber being delimited, longitudinally, at one end, by a wall, acting as a piston, integral with the rotor and extending to the stator and, at the other end, by a wall, retractable, arranged upstream the corresponding air inlet pipe, integral in translation with the stator and extending to the rotor, associated with a means adapted to make it retractable during the passage of the piston. TECHNOLOGICAL BACKGROUND

There are many prior art documents describing compressed air motors, in particular those using pistons and cylinders of the jack type or using more or less sophisticated decompression chambers.

Their realization is not always easy and their yield is generally low to consider a profitable exploitation.

SUMMARY OF THE INVENTION

The invention aims to produce a rotary motor of simple, new and original design, making it possible to achieve high yields.

To this end, it relates to an engine which is essentially characterized in that each air inlet pipe is associated with a means suitable for blowing, into the corresponding decompression chamber, after the passage of the piston over the inlet pipe, a quantity of air of well determined pressure and volume.

According to particular features of the invention: - the means adapted to move the retractable wall during the passage of the piston, is chosen from mechanical devices with cams, electromechanical relays and pneumatic cylinders; - The means adapted to move the retractable wall during the passage of the piston, is the piston itself which has a shape adapted to disengage said wall during its passage;

the means adapted to breathe into the decompression chamber, after the passage of the piston over the air intake pipe, a quantity of air under well defined pressure is chosen from mechanical, electromechanical and pneumatic devices with valves or with valves;

- The means adapted to breathe into the decompression chamber, after the passage of the piston over the air intake pipe, a well defined quantity of air under pressure, is a retractable shutter valve for closing the end of said pipe, which has a shape adapted to release said end under the effect of the passage of said piston.

PRESENTATION OF THE FIGURES

The characteristics and advantages of the invention will appear more clearly on reading the following detailed description of at least one preferred embodiment of the latter given by way of non-limiting example and shown in the accompanying drawings.

In these drawings:

- Figure 1 is a cross-sectional view AA of the rotary motor; - Figure 2 is a diametrical sectional view BB of said motor;

- Figure 3 is a cross-sectional view AA of the rotary engine comprising two decompression chambers;

- Figure 4 is a principle view of a triangular piston chamber;

- Figure 5 is an abacus giving the pressure received by the piston for an injection of volume 100 times lower than that of the chamber and according to the position of the piston in its stroke;

- Figure 6 is a principle view of a compressor with triangular compression chamber associated with a motor with rectangular decompression chamber;

- Figure 7 is an abacus giving, in the case of a triangular compression chamber, the variations of the successive heights of a piston as a function of its position along its stroke.

DETAILED DESCRIPTION OF THE INVENTION

The rotary compressed air motor shown in the figures includes:

- a cylindrical and concentric stator (1) and a rotor (2); - A volume chamber (V) delimited, longitudinally, by the cylindrical walls opposite said stator and said rotor and, laterally, by two flanges (3) and (4) facing;

- at least one pipe (5) for supplying pressurized air (P) into at least one decompression chamber (Va) belonging to said volume (V) and at least one air discharge pipe (6) residual (R) at the end of the decompression cycle. Each decompression chamber (Va) is delimited, longitudinally, at one end, by a wall (7), acting as a piston, integral with the rotor (2) and extending to the stator (1) and, at the other end, by a retractable wall (8), disposed upstream of the corresponding air inlet pipe (5), integral in translation with the stator (1) and extending to the rotor (2), associated to a means adapted to make it retractable during the passage of the piston (7). Each air inlet pipe (5) is associated with a means suitable for blowing, into the corresponding decompression chamber (Va), after the passage of the piston (7) over said inlet pipe, a quantity of air under pressure (P) well defined at each rotor revolution.

The means adapted to move the retractable wall (8) when. of the passage of the piston (7), can be chosen from mechanical cam devices, electromechanical relays and pneumatic cylinders. It can also be the piston (7) itself which has a shape (fig. 1) adapted to disengage said wall during its passage.

The means adapted to breathe into the decompression chamber (Va), after the passage of the piston (7) over the air intake pipe (5), a well-defined amount of pressurized air (P) is chosen. among mechanical, electromechanical and pneumatic devices with valves or valves.

It can also be a retractable valve (9) for closing the end of said pipe (5), which has a shape adapted to release said end under the effect of the passage of said piston. The retractable wall (8) is associated with a means, in particular a spring, adapted to return it to its initial position after the passage of the piston (7).

The retractable valve (9) is associated with a means, in particular a spring, adapted to return it to its initial position after the passage of the piston (7). The piston (7) can be produced by means of an elastic blade bearing on the cylindrical inner wall of the stator (1). Several decompression chambers (Va), each associated with a pressurized air supply line (5), a residual air discharge line (6), a piston (7) and a retractable wall (8), are arranged uniformly distributed

(fig.3) around the chamber (V) in order to add their effects. Several assemblies, each comprising a stator (1), a rotor (2), flanges

(3) and (4), at least one piston (7) and at least one retractable wall (8) associated with inlet (5) and outlet (6) pipes, are juxtaposed on the same shaft

(10) in order to add their effects.

The operation of the rotary motor is explained below. The rotation of the piston (7) integral with the rotor (2) first encounters the wall (8) integral in translation with the stator (1) which retracts during the passage of said piston to close as soon as the latter has crossed said obstacle .

The decompression chamber (Va) fills with pressurized air as soon as said piston has crossed the inlet pipe (5). The volume of said chamber then represents a small part of the volume (V) of the overall circular chamber. The expansion of this volume exerts on the piston a decreasing pressure (PV = constant) as it moves. This pressure is therefore a direct function of the initial supply pressure and exerts a torque proportional to it.

A simple needle is therefore sufficient to control the system in question (removal of the gearbox).

At the end of expansion, when the piston (7) has passed through the evacuation pipe (6), the residual air (R) is either evacuated into the atmosphere or recycled.

Principles

A turbine dedicated to compressing atmospheric air at room temperature delivers more than 1 Ncm ³ compressed to 5 bars from a motor energy consumption of 1 joule. A second contiguous turbine of different size is wedged on the same shaft (for example) drives the first.

It uses air at a pressure of 5 bars. This pressure can be increased by raising the temperature of the heat exchange with calories produced by compression. Energy production being greater than 1 joule per Ncm ³ consumed.

The verification of the calculation for a compression chamber is set out below. By projecting this, we obtain a triangular piston which expels the air from a jack as shown in Figure 4 where (E) is the inlet of the fluid, (S) the outlet thereof,

(H) the height of the chamber and (C) the stroke of the piston.

We arbitrarily retain the dimensions that we will find in the description of the turbine and which are 25.4 cm for the outside diameter of the chamber and 5 cm for the height and 10 cm for the width of the latter.

We also retain 44.76 kg for the engine torque; 0.204 m x 44.7 kg x 9.81

= 89 m / N for the moment of the couple; 2τrx M = 559 joules for the work absorbed per revolution and 60 rpm for the speed. Thus, the piston represented in linear receives a force of 44.76 kg (arbitrary), its stroke (C) is 16 cm and it consumes a work of 44.76 kg x 0.16 mx 9.81 = 70 joules for move the volume of the chamber which is 16 x 5 x 10/2 = 400 cm ³ .

We will see in the turbine described that the torque was determined by the counter pressures exerted at each advance of the piston on an increasingly reduced surface and calculated so that the compressor turbine delivers in a capacity where the pressure (controlled by a valve) does not exceed 5 bars.

As long as the pressure in the capacity does not reach the set pressure, the power absorbed is lower. We will ignore it.

We note that the virtual piston thus diagrammed produces 400 Ncm ³ which correspond to 80 cm3 compressed at 5 bars.

We see that with an absorbed joule, the virtual cylinder in this configuration, delivers 400cm / 70 joules = 5.7 cm ³ .

We will find in the calculation of the compression turbine the work absorbed for a rotation which is written as: 2τrx Moment 89 m / N = 559 joules. As during this rotation, there will be two compression chambers delivering at each quarter turn, the delivery will be: 400 Ncm ³ x 2 x 4 = 3200 Ncm ³ .

Or: 1 joule = 3200/559 = 5.7 Ncm ³

Verification of the calculation for a motor chamber

Here again, to facilitate the demonstration, imagine the engine chamber of the turbine in a virtual cylinder.

Let's take the same dimensions as those described in the turbine, that is to say:

Volume = 800 cm ³ (since the piston is not profiled), piston surface = 50 cm ²

(5cm H x 10 cm W and stroke = 16 cm (virtual). The diagram in FIG. 5 represents the pressure (P) received by the piston for an injection of 1/100 ^ee of the volume of the chamber per cycle, therefore the corresponding force as a function of the position (C) of the piston in its course:

- in position 0 5 bars x 8 cm = 40 sides = 5 bars x 50 cm ² _ = 250 kg

- in position 1 40 / (8 + 1/8 x 100) = 0.37 bars x 50 cm ² = 16.5 kg

- in position 2 40 / (8 + 2/8 x 100) = 0.19 bars x 50 cm ² = 9.5 kg

- in position 3 40 / (8 + 3/8 x 100) = 0.13 bar x 50 cm ² = 6.5 kg

- in position 4 40 / (8 + 4/8 x 100) = 0.09 bar x 50 cm ² = 4.5 kg

- in position 5 40 / (8 + 5/8 x 100) = 0.08 bar x 50 cm ² = 4.0 kg

- in position 6 40 / (8 + 6/8 x 100) = 0.065 bar x 50 cm ² = 3.25 kg

- in position 7 40 / (8 + 7/8 x 100) = 0.056 bar x 50 cm ² = 2.8 kg

- in position 8 40 / (8 + 8/8 x 100) = 0.05 bar x 50 cm ² = 2.5 kg

The total pressure exerted on the piston is the average of the sum of the pressures, that is: 6/9 = 0.67 bar

Similarly, the average of the couples is: 301, 55/9 = 33.5 kg

Note that each turbine chamber receives an average pressure of 0.67 bar per pulse. But the pressure decreases between the shock at the start where it is at its maximum of 5 bars which gives a shock of 5 bar x 50 cm ² = 250 kg and the pressure at the end of the stroke of 0.05 bars which gives a residual : 0.05 x 50 cm ² =

2.5 kg (of torque to compensate for friction).

In practice, this leads to:

- to wedge different chambers so that the rotation is continuous (star mounting);

- to reduce or increase the percentage of the volume injected so as to obtain a more or less significant residual force, for example with a percentage injected of 1/50 ^e we will have a residual: 5 bars x 16 cm ³ = 80 sides / (16 + 800) = 0.10 bar.

Of course double, which also doubles the torque: 0.1 bx 50 cm ² = 5 kg.

The final pressure is multiplied in proportion to the percentage of the chamber selected.

But energy production is not proportional to consumption.

With 1/100 ^e we obtain a torque (taking into account the engine configuration) of: 0.67 bar x 50 cm ² = 33.5 kg.

Whereas for 1/50 ^th the average pressure becomes: (5 + 0.74 + 0.37 + 0.26 + 0.18 + 0.16 + 0.13 + 0.112 + 0.1) / 9 = 0.784 bar and therefore the average torque becomes: 0.784 bar x 50 cm ² = 39.2 kg.

The consumption which for 1/100 ^e of the volume consumed is:

(800 cm ³ x 5 bar) / 100 = 40 Ncm ³ is doubled if the percentage decreases: (800/50) x 5 = 80 Ncm ³ .

This allows us to note that depending on what the turbine receives by injection, the work / consumption ratio varies according to the formula:

W = Force in kg x displacement in meters x 9.81 to obtain joules which gives: - for 1/100 ^th = 33.5 kg x 0.16 x 9.81 = 52.5 joules / 40 Ncm ³ = 1 , 3 joule / Ncm ³

- for 1/50 ^th = 39.2 kg x 0.16 x 9.81 = 61.5 joules / 80 Ncm ³ = 0.769 joule / Ncm ³

The engine part

The engine chamber (Cm) receives, per pulse and per revolution, a percentage of its volume at a selected pressure. It has a rectangular profile. Its exact capacity is calculated since it is a ring profile by subtracting from the total area of the largest circle, the area of the small inner circle.

We will take the case of a 25.4 cm outside diameter chamber; for 5 cm radius difference (chamber height):

12.7 x 12.7 x 3.14 = 506.62 cm ² 7.7 x 7.7 x 3.14 = 286.24 cm ² / 320.38 cm ²

By retaining a chamber depth of 10 cm, the volume is written:

320.37 x 10 = 3203.8 cm ³ .

The surface of the piston being 5 x 10 = 50 cm ² , by exerting on it a pressure of 0.67 bars (Figure 6) which represents the average pressure of one hundredth of the volume of the chamber supplied at 5 bars, we obtain a force of 0.67 x 50 = 33.5 kg.

The displacement of the piston on the mean diameter multiplied by this force represents the work W = F x D which is written thus for a turbine: W = 2τr x D x couple x 9.81 =

6.28 x 0.204 mx (0.67 bar x 50 cm ² ) x 9.81 = 421 joules.

The expenditure of Ncm ³ of air used at this pressure of 5 bars is calculated by converting the compressed cm ³ into normal cm ³ , and for this example, in hundredths of the volume. Each room debits eight times per turn, namely:

3203.8 cm ³ x 5 bars x 8 times per turn / 4 rooms x 100 = 320.38 Ncm ³ / turn

What can be translated and which will remain constant for any type of engine: 1 Ncm ³ generates a work of 421/320 = 1, 3 joule. in isothermal condition. This coefficient being calculated under isothermal conditions. Considering the engine warming up, say at a temperature of 909 ° absolute while the blown air remains at room temperature, say 303 ° absolute, the average pressure for a perfect exchange would be three times higher. (use of a solar mirror for example).

The engine part could also be coupled to the compressor part to recover the calories.

The compressor part

We have established by successive experiments that, unlike the engine, the ratio between the joules consumed and the production varies somewhat depending on the technology used and the profile of the compression chambers (Ce). We will develop here the calculations for a defined compressor, so as to explain the operation. To facilitate understanding, we retain a compressor identical to the engine in the example above. Knowing that the profile of the compression chambers may, depending on the desired results, be produced so as to “smooth” the variation curve of the absorbed torque, we retain to simplify our demonstration a profile (F), such as that of FIG. 6 . the volume of the compression chamber will be half that of the motor (3203.8 cm ^3/2 = 1601, 9 cm ^3).

Since there are 4 chambers in the reversible exposed system taken for this example, a compression chamber has a volume of: 3203.8 / 4 = 800.95 / 2 = 400.475 cm ³ (triangular profile). The compressor part must only consist of compression chambers with a triangular profile.

To visually assess the energy absorbed by the compressor to bring the air drawn from atmospheric pressure to 5 bars, we consider the profile of a chamber, as shown in Figure 7, length 400.475 cm ³ x 2/5 cm high = 160.19 cm. (base of the projected triangle for a height of 5 cm and 10 cm deep)

From the measurements noted on the attached chart, we can write that, when the piston goes from position 0 to 1, the volume of the chamber becomes: Length = 12.816 cm x Height = 4.1 x Depth 10/2 = 262.728 cm ³ this in isothermal condition PV = cte (we will see below the influence of temperatures) the relative pressure becomes:

1 atm. x 400.475 cm ³ / 262.725 = 1.524 absolute or 0.524 relative pressure. This pressure being exerted on a reduced surface of the piston with each advance:

H 4.1 cm x W 10 cm = 41 cm ² the absorbed force is: 0.524 x 41 cm = 21, 484 kg

Let’s remember to do the integration afterwards, it takes 21.484 kg to go from 0 to

0.524 bar relative pressure.

In position 2, you need: (1 x 400.475 x 2) / (9.612 cm x 3.1 x 10) - 1 = 1.688 bar, hence a force of: 1.688 x 3.1 x 10 = 52.328 kg.

In position 3, you need: (400.475 x 2) / (6.4 x 2 x 10) - 1 = 5.257 bars, hence a force of: 5 bars x 2 x 10 = 100 kg.

Note here that we have chosen to only discharge at 5 bars (pressure which we therefore use to calculate the torque instead of 5,257 bars). In position 4, therefore for 5 bars: 5 bars x 1 x 10 = 50 kg.

With this profile, the average torque is therefore 44.76 kg for 5 bar discharge pressure, the energy consumed is: 6.28 x 0.204 x 44.76 x 9.81 = 562 joules to obtain the chamber flow at 5 bars: 400.475 Ncm3 x 8 times per revolution =

3203.8 Ncm ³ . Of course, the invention is not limited to the embodiments described and shown for which other variants may be provided, in particular in:

- the types of stators, rotors and flanges and the nature of the constituent materials;

- types and shapes of pistons and retractable partitions; - the types of means suitable for moving the retractable wall and for blowing air into the inlet pipe;

- the number of decompression chambers and associated circuits; and extend it to all applications intended to set in motion any device or any land, water or air vehicle, either totally or in addition, regardless of the complementary energy source used.

Claims

1- Rotary compressed air motor essentially comprising: a) a cylindrical and concentric stator (1) and a rotor (2); b) a volume chamber (V) delimited, longitudinally, by the cylindrical walls facing said stator and said rotor and, laterally, by two flanges (3) and (4) facing; c) at least one pipe (5) for supplying pressurized air (P) in at least one decompression chamber (Va) belonging to said volume (V) and at least one discharge pipe (6) for the residual air (R) at the end of the decompression cycle; each decompression chamber (Va) being delimited, longitudinally, at one end, by a wall (7), acting as a piston, integral with the rotor (2) and extending to the stator (1) and, at the other end, by a retractable wall (8), disposed upstream of the corresponding air inlet pipe (5), integral in translation with the stator (1) and extending to the rotor (2), associated to a means adapted to make it retractable during the passage of the piston (7); characterized in that each air inlet pipe (5) is associated with a means suitable for blowing, into the corresponding decompression chamber (Va), after the passage of the piston (7) over the inlet pipe (5 ), a quantity of air of well determined pressure and volume. 2- rotary motor according to claim 1, characterized in that the means adapted to move the retractable wall (8) during the passage of the piston (7), is chosen from mechanical devices with cams, electromechanical relays and pneumatic cylinders . 3- rotary motor according to claim 1, characterized in that the means adapted to move the retractable wall (8) during the passage of the piston (7) is the piston (7) itself which has a shape (F) adapted to release said wall during its passage. 4- rotary motor according to claim 1, characterized in that the means adapted to breathe into the decompression chamber (Va), after the passage of the piston (7) on the air inlet pipe (5), a quantity of air under pressure (P) well defined, is chosen from mechanical, electromechanical and pneumatic devices with valves or valves. 5- rotary motor according to claim 1, characterized in that the means adapted to breathe into the decompression chamber (Va), after the passage of the piston (7) on the air inlet pipe (5), a well-defined amount of air under pressure (P) is a retractable valve (9) for closing off the end of said pipe (5) , which has a shape adapted to release said end under the effect of the passage of said piston. 6- rotary motor according to claim 3, characterized in that the retractable wall (8) is associated with a means, in particular a return spring, adapted to return it to its initial position after the passage of the piston (7). 7- rotary motor according to claim 5, characterized in that the retractable valve (9) is associated with means, in particular a return spring, adapted to return it to its initial position after the passage of the piston (7). 8- Rotary motor according to claim 1, characterized in that the piston (7) is produced by means of an elastic blade bearing on the cylindrical inner wall of the stator (1). 9- Rotary motor according to any one of the preceding claims, characterized in that several decompression chambers (Va), each associated with a supply line for pressurized air (5), with a supply line residual air discharge (6), a piston (7) and a retractable wall (8), are arranged uniformly distributed around the chamber (V) in order to add their effects. 10- rotary motor according to any one of the preceding claims, characterized in that several assemblies, each comprising a stator (1), a rotor (2), flanges (3) and (4), at least one piston (7) and at least one retractable wall (8) associated with inlet (5) and discharge (6) pipes, are juxtaposed on the same shaft (10) in order to add their effects.