WO2006010238A1

WO2006010238A1 - Compressor comprising dual-action pistons

Info

Publication number: WO2006010238A1
Application number: PCT/CA2004/001450
Authority: WO
Inventors: Afif Abou-Raphael
Original assignee: Afif Abou-Raphael
Priority date: 2004-07-27
Filing date: 2004-08-04
Publication date: 2006-02-02
Also published as: CA2473077C; CA2473077A1

Abstract

The invention relates to a compressor comprising dual-action pistons. Standard compressors use very powerful motors in order to generate the force necessary for the compression of compressed air. The invention relates to the production of a compressor that uses low power motors, comprising dual-action pistons and one or more cylinders. According to the invention, there are no cylinder length or diameter restrictions, owing to the simple machine operation thereof, e.g. that of a jack screw. In this way, very large high drag forces can be overcome, such as the force generated by the pressure of the compressed air which presses against the surface of the pistons during the air compression cycle, by means of a relatively-low torque which is applied to the screw and the reciprocating linear motion that the screw of the above-mentioned jack screw communicates to the pistons of the cylinders.

Description

Double acting piston compressor

The present invention relates to the manufacture of a cylinder compressor, using the force and the reciprocating linear motion of the screw of a single machine such as a screw jack.

According to Canadian Patent No. 2328580, the transformation of the potential energy of the compressed gases by means of the potential energy of the liquids, requires plants that use, among other things, compressed air by conventional compressors, which are composed inter alia a large number of rotating elements which require a lot of maintenance, and which use very powerful motors to develop the force necessary for compression of the compressed air. 80 to 93% of this energy is lost in heat during the compression of the air, in addition, the flow of compressed air is already limited by the volume in cubic feet that these compressors move by the minute, and the high temperature prevailing inside their cylinders, which heats the air admitted to be compressed, which increases its volume and decreases its quantity.

To overcome these drawbacks by having the compressor one of the most economical and one of the most efficient, it has used a double-acting compressor, single cylinder or multiple cylinders. This compressor is simple and efficient, it can provide variable flow rates according to the volume and the number of cylinders used which have no length or diameter limits, thanks to its operation by a simple machine such as a cylinder to screw, which allows to overcome very strong resistant forces such as the force which is developed by the pressure of the compressed air which exerts on the surface of a piston of a compressor during the cycle of the compression of the air, by means of a relatively low torque moment which will be applied to its screw, and the reciprocating linear motion that said screw of said screw jack communicates with the pistons of said cylinders. This screw jack operates by weak motors, electric, mechanical, hydraulic or pneumatic, even the muscular strength of a man can be the means used to operate the compressor the subject of the present invention.

The construction of this compressor includes:

1- A solid assey chassis to withstand the stresses of very large forces, caused by the pressure of the compressed air which acts against the screw of the screw jack via the

1

/ EUL REPLACEMENT (RULE 26) pistons which are securely attached to said screw by compressing air in the compressor cylinders,

2- A screw jack which allows to overcome very strong resistant forces, such as the force which develops by the pressure of the compressed air which exerts at the same time on the total surface of the pistons of the compressor during the cycle of the compression air, and which transmits the force and movement of its screw to the pistons of said compressor the subject of the present invention, to push or pull as the case, compressing the air in their respective cylinders twice per period .

This screw jack includes:

A screw actuated by a nut-and-drive gear which turns crazy in a bore machined in a very solid frame forming part of the same frame above mentions who is able to withstand the stress of the force that will be exerted by the compressed air on compressor pistons during compression, yet it requires a small moment of torque to overcome with said screw jack screw the subject of the present invention, which pushes or pulls the piston that is secured to it during compression air.

B- A pinion that can be combined with a gearbox to give a linear reciprocating motion to the screw of the screw jack through its gear-nut mentioned above, to push and pull at the same time all the pistons in their respective cylinders dependent on the compressor, in a manner to control the frequency of their cycles which determine the compressed air flow of the compressor the subject of the present invention.

C- A motor to operate the screw jack. Here the engine chosen is electric.

D- A crankcase filled with oil to lubricate the screw and the gears of the screw jack.

E- Electrical contactors that actuate electrical circuit breakers necessary to stop and restart the motor of the screw jack in one direction or the other by creating a linear movement to its alternate which is necessary to alternate at the same time the translation of each piston in its cylinder in a manner to promote the admission of air into the cylinder on one side of the piston and at the same time to promote the compression of the air which is on the other side of the same piston in the same cylinder.

F- A tab which is fixed on the screw of said jack screw, used to stop and restart the motor of the screw jack at the end of the exhaust of each cycle, by actuating the above mentioned contactors which are separated between them from a distance exactly equal to the

2 f REPLACEMENT CLAUSE (RULE 26) distance of a single piston of the compressor described inside its respective cylinder, from the beginning of the admission of air until the end of the escape of the compressed air to the tank of the central patent No .: 2328580.

3- A cylinder in which a double-acting piston is actuated by the screw screw mentioned above, to suck in air, and then to compress it and push it back to the tank of the central patent No. 2328580, twice a year, with intake and exhaust valves on either side of the cylinder. This compressor can be manufactured with a single cylinder, but thanks to the reciprocating screw of the screw jack that allows us to install cylinders on both sides of the screw jack screw, other configurations can be made with two or more cylinders depending on the air flow demanded.

To further increase the flow of the same compressor, one can install cylinders on either side of the same screw of the same screw jack of the same compressor. The cylinders on both sides must have pistons that have the same length that is equal to the same distance that the screw of the screw jack travels from the beginning of the compression of each cycle until the end of the exhaust of the air of the same cycle, but may have different diameters. All these cylinders always operate in parallel because all their pistons are connected together and actuated by the same linear reciprocating movement that the same screw of the same screw jack transmits them without the need for connecting rods and cranks, thanks to intermediate axes of coupling which will be installed between each two pistons of each two cylinders placed one after the other, or will be operated directly and at the same time by the screw of the same screw jack, thanks to the use of the same frame and fasteners which are integral with all the pistons of all the cylinders which are installed next to each other on each side of the screw of the screw jack.

This compressor is water cooled to recover the heat lost during air compression, by heating the water of the power plant of the Canadian patent No. 2328580 with a heat exchanger, then to put back a good part from this heat to the air that is in the power bells of the plant, which greatly increases the energy efficiency of this plant. The heating increases the volume of the air in the power bells of said power plant, and then move a larger volume of liquid, where the upward thrust on the motor bells is equal to the weight of the liquid moved.

The compressor pistons may further include a cooling system which will also be connected to the heat exchanger to help cool the interior of the cylinders of said compressor the subject of the present invention, causing the admission and compression of the compressor. a larger amount of air by increasing the flow of the compressor to further increase the efficiency of said above mentioned plant.

The cooling water of the pistons will be communicated to them by means of flexible hoses which are integral on one side, pipes of the main cooling system, and on the other side, the screw of the screw jack which communicates the water. pistons, or they will be attached directly to the pistons themselves. This is feasible because the screw communicates to the pistons a reciprocating linear movement, and the configuration of the compressor allows it,

The moment torque required to advance or retreat the screw jack screw, the subject of the present invention, is very small compared to the force to be overcome, which is the force exerted by the compressed air on the surface of all pistons simultaneously compressing air and which are integral with said screw jack screw, if we neglect the weight of said pistons and friction. This torque moment is managed by the following formula: The torque moment required for each step forward or backward of the screw, is equal to:

[The total force to be defeated expressed in Newtons x the pitch of the screw expressed in meters] / (2 x 3.1416).

The necessary work for all the distance to be traveled by the screw, from the beginning of the compression until the end of the exhaust of the compressed air, is equal to:

{[FI (mean compressed air pressure recorded at the beginning of the exhaust in newtons / cm2 x the piston surface in cm2) x the pitch of the screw in meters x (the distance to be traveled between the beginning of the compression to the beginning of the exhaust in meters / the pitch of the screw in meters)] / (2 x 3.1416)} + {[F2 (the constant pressure of the compressed air recorded at the beginning of the exhaust in newtons / cm2 x the piston surface in cm2) x the pitch of the screw x (the distance to be traveled between the beginning of the exhaust until the end of the exhaust in meters / the pitch of the screw in meters) ] / (2 x3.1416)}. Ex.l: If the pressure recorded at the beginning of the exhaust air is 7kgs / cm2 or 70 N / cm2, the total surface of the piston compressing the air is 1000 cm2, the pitch of the cylinder screw to screw is 0.008 meters, and the distance traveled by the screw of the screw jack from the beginning of the exhaust until the end of the exhaust is 1 meter.

The total force to be overcome from the beginning of the escape until the end of the escape will be: (7 kegs / 2) x 1000 cm2 x 10 Newton = 35,000 N.

the torque moment for each step of the screw will be: (35000 newtons x 0.008) / (2 x 3.1416) =

45 mN.

The total value of the work needed to overcome this force of 35,000 newtons over a distance of Im will be: 45 mN x number of steps (lm / 0.008 meters) = 5.625 mN.

Ex.2: Take for example 210 cubic meters of air at atmospheric pressure of 1.01325 bar (FAD) and try to study the variation of the volumes if we compress this quantity of air to lbar, 3 bars, and 7 bars, in the same cylinder by the same piston.

Under a pressure of 1 bar, the 210 cubic meters will be according to Boyle's law:

210 meters Newtons, x (1.01325 bar +0 bar) /(1.01325 bar +1 bar) = 106 cubic meters, about half of the 210 cubic meters.

Under a pressure of 3 bars, the 210 cubic meters will be according to Boyle's law:

210 meters Newtons. X (1.01325bar +0 bar) /(1.01325 bars + 3 bars) = 53 cubic meters, about half of the 106 cubic meters.

Under a pressure of 7 bars, the 210 meters Newtons, will be according to the law of Boyle:

210 cubic meters x (1.01325 bars + 0 bar) /(1.01325 bars + 7 bars) = 26.5 cubic meters, about half of 53 cubic meters.

According to these calculations we notice that the volume decreases by about half each time we double the pressure under which we take the volume and we add 1. [(pressure x 2) + 1] check:

210 cubic meters at 0 bar, become 106 cubic meters at the pressure of: [(O bar x 2) +1 = lbar

106 cubic meters at 1 bar, become 53 cubic meters at the pressure of: [(I bar x 2) +1] = 3 bars.

53 cubic meters at 3 bars, become 26.5 cubic meters at the pressure of: [(3 bars x 2) +1]

= 7 bar.

This finding helps to configure the screw jack compressor the subject of the present invention. This means that inside the cylinder of said compressor mentioned above, when the piston moves forward or back halfway during the beginning of the compression, the volume of air trapped inside the cylinder becomes the about half, air (FAD) that was admitted into the cylinder, and its pressure rises from 0 bar to 1 bar. (

106metres cubes / 210 cubic meters) x 100 = 50% = 1/2.

If the piston continues to advance to half of the remaining half of its course, that means, when it is 3/4 of its total distance (L), the volume of the compressed air will be 1/4 of its initial volume (FAD) and its pressure rises from 1 bar to 3 bars: (53 cubic meters / 210 cubic meters) x 100 = 25% = 1/4.

And if the piston continues to advance to half of the remaining half of its course it means, when it is 7/8 of its total course (L), the volume of compressed air will be 1/8 of its initial volume (FAD) and its pressure rises from 3 bars to 7 bars. (26.5 cubic meters / 210 cubic meters) x 100 = 12.5% = 1/8.

The final pressure of the compressed air that is necessary for the proper functioning of the plant will be controlled by a pre-adjusted pressure regulator that will be installed on the pneumatic circuit of the plant. So the volume of compressed air and sent to the tank of said plant will be affected by this pressure according to Boyle's law.

The ratio of the volume of the compressed air at 7 bar and escaped from the constant pressure of 7 bars towards the above-mentioned central tank mentioned in this example, to the volume of the same air at atmospheric pressure (FAD) will be: (26.5 cubic meters / 210 cubic meters) x 100 = 12.619%

If the radius of the piston that compresses the 210 cubic meters of air is 0.50 m. its surface that compresses the air will have an area of:

0.50 mx 0.50 mx 3.1416 = 0.7854 square meters or 7854 cm2.

So the total course of the piston, from the beginning of the compression until the end of the exhaust of the compressed air will be: 210 cubic meters / 0.7854 square meters = 267.380 meters.

The distance the piston must travel to escape 26.5 cubic meters of compressed air will be:

Volume / area of the piston. 26.5 cubic meters / 0.7854 square meters = 33,741 meters.

So the ratio of the remaining course to the piston to escape the compressed air since it reaches 7 bar until the end of the exhaust, the total course (L) of the same piston, the beginning of compression to the end of the exhaust air will be: 33,740 meters / 267,380 meters x 100 = 12,619%.

It is found that the ratio of the volume of the compressed air and escaped to the tank mentioned above to the volume of the same air at atmospheric pressure (FAD) is equal to the same ratio as the course remaining at the piston to complete the exhaust of the compressed air, the total path (L) of the same piston from the beginning of the compression until the end of the exhaust of the compressed air.

Then the screw of the screw jack will have to push the piston on a distance equal to 87.381% (100% less 12.619% = 87.381%) of the total course (L) of the piston which is 267.380 meters to arrive until the beginning of the exhaust of compressed air which reaches a volume of 26.5 cubic meters of compressed air at 7 bars: 267.380 meters x 87.381% = 233.640 meters

All these calculations are done to arrive at the following result:

The energy required to compress the air to the pressure of 7 bars, which is the pressure chosen for an example plant of Canadian Patent No. 2328580, is equal to:

{[3.5 bar (the mean of the air pressure between 0 bar and 7 bar) x the total area of the pistons compressing the air at the same time (in cm2) x 10 (newtons per kg) x (the number of not the screw jack screw the same compressor that will be necessary for the piston to advance from 87.381% of the distance (L) between the beginning of the compression and the beginning of the exhaust of the compressed air which reached a volume of 26.5 cubic meters of compressed air at 7 bars, (L x 87.381% / 0.008 meters the pitch of the screw)] divided by / 2 x 3.1416)}.

The energy required to escape the compressed air at the constant pressure of 7 bar, which is the pressure chosen for a central example of the Canadian patent No. 2328580, is equal to: {[7 bar, constant pressure of the air escapes x la total surface of the pistons compressing the air at the same time x 10 newtons x the number of threads of the screw jack of the same compressor which will be necessary for the piston to advance 12.619% of the total stroke (L) of the piston, start of compression until the end of the exhaust of the compressed air, (L x 12.619% / 0.008 meters, the pitch of the screw)] divides by / (2 x 3.1416)}.

Ex.3: The piston surface is: 7.854 cm2 or 0.7854 m2

The total length (L) of the piston from the beginning of the compression until the end of the exhaust of the compressed air is: 267,380 meters

the distance that the screw of the screw jack makes to push the pistons to the beginning of the exhaust, where the pressure of the air is restored to 7 bars, is: 233,640 meters.

So the number of steps from the beginning of the compression until the beginning of the escape will be:

233,640 meters / 0.008 meters = 29,205 steps

the path that the screw of the screw jack makes to push the piston from the beginning of the exhaust until the end of the exhaust of the compressed air at the constant pressure of 7 bars is:

33,741 meters

So the number of steps from the beginning of the escape to the end of the escape will be:

33,740 meters / 0.008 meters = 4,218 steps.

The energy required to push or pull (double-acting compressor) the piston in its cylinder to reach the beginning of the exhaust of the compressed air will be:

7.854 cm 2 x (7bar / 2) x 10 newtons x 0.008 mx 29,205 steps / (2 x 3.1416) = 10,221,750 mN ouj gills The energy required to push or pull the piston in its cylinder from the beginning of the exhaust until the end of the exhaust of the compressed air at the constant pressure of 7 bars is: 7.854 cm2 x 7 x 10 newtons x 0.008 x 4,218 steps / (2 x 3.1416) = 2,952,600 mN or joules

Then the total energy required for the screw jack screw to push or pull the piston in its cylinder from the beginning of compression until the end of the exhaust of the compressed air at 7 bar, for each cycle of compression in this compressor, will be: 10,221,750 mN + 2,952,600 mN = 13,174,350 mN or joules,

The power of the motor to be used to operate the screw jack is:

13,174,350 joules / (60 sec x 746 watts for each steam horse) = 294 horsepower

Now we have the calculations of the power of the compressor which gives us a flow of 210 cubic meters of air (FAD) delivered to 7 bars, which allows to determine the design of the compressor to use.

Ex.4: A flow of 20 cubic meters of air (FAD) compressed at 7 bars, requires a conventional compressor of 150 horsepower approximately.

And if we do the calculations of the rule of three for a flow rate of 210 cubic meters of air per minute, the power of the compressor will be: (150 horsepower / 20 cubic meters) x 210 cubic meters3 = 1.575 horsepower.

Compared to 294 horsepower the power of the compressor needed to give the same rate of 210 cubic meters of air per minute according to the compressor method of the present invention.

If the efficiency of the compressor is 70% we will have: 210 cubic meters of air x 70% = 147 cubic meters

So for the flow of 210 cubic meters one needs a compressor of:

(294 horsepower / 147 cubic meters) x 210 cubic meters = 420 horsepower. Result of the power to save compared to a conventional compressor for the same flow of 210 cubic meters of air: 1,575 horsepower Less 420 horsepower = 1155 horsepower.

Practical conclusion:

Between the beginning of the compression and the beginning of the compressed air exhaust, the compressor does not supply compressed air, which means that we have to find a way to fill this vacuum. It has been seen in the preceding calculations, for example, that the ratio of the volume of the compressed air to the initial volume (FAD) admitted into the cylinders of the compressor is 1/8 or 12.5% for the pressure of 7 bars, and it is equal to the ratio of the distance that the screw must travel from the beginning of the exhaust to the total escape of the compressed air, to the total distance between the beginning of the compression and the end of the exhaust which is 1/8.

So to have a continuous flow of compressed air for the plant to operate continuously, it is necessary that the flow of 210 m3 of air (FAD) that was chosen as an example, be shared and delivered by 8 compressors of 26.25 m3 (FAD) (210/8 = 26.25m3) of flow per minute for each, and these 8 compressors must escape their air in a successive and continuous way, it means that when the first compressor finishes to escape its air , the second compressor must begin to escape immediately followed by the third, then by the fourth, then by the fifth, then by the sixth, then by the seventh, then by the eighth, then by the first which will be at the point of recommencing a new exhaust cycle, and so on.

Again, if the pressure of the compressed air used in another plant is 1 bar for example.

The ratio will be 1/2 according to the previous calculations, or 50% (100% / 2 = 50%), that means that the void to fill will be 50%, or half the distance between the beginning of the compression and the end of the exhaust of the compressed air. So, in this case, you have to have 2 compressors to deliver the flow of 210 cubic meters of air (FAD) in a successive and continuous way for the plant to work reliably: When the first compressor finishes escape its air, the second compressor must directly start its exhaust cycle, and when the second compressor reaches the end of its cycle exhaust, the first will be at the point of starting a new exhaust cycle and so on.

The total power required to compress and escape the flow of 210 cubic meters of air (FAD) per minute, necessary for the proper operation of the plant that is chosen in the example, is equal to the total of all the powers of all compressors used to deliver a continuous and shared flow for the plant to be efficient and operational. Then the result will be that the use of this compressor the subject of the present invention is operational and practical regardless of the flow rate, the speed of translation of the screw jack screw or the pressure of compressed air requested.

The compression of the air by means of this compressor, which is the subject of the present invention, is as follows:

With a single cylinder compressor:

1- When all the elements of the compressor are assembled:

2- Take for example that the air is already present inside the cylinder and the piston is at the beginning of its path that it must cross to compress the air and then escape to the tank of the central of the Canadian patent No 2328580.

3- a first contactor which is actuated by a tab fixed on the screw of the screw jack, goes into closed position to actuate a circuit breaker which turns the motor in the right direction which determines the direction of translation of the screw of the cylinder to screw that pushes the piston attached to it, in the same direction as the screw above mentions.

4- The motor begins to rotate to rotate the worm gear of the screw of the screw jack which turns crazy in a bore of the frame that supports the whole compressor, in turn, the screw starts its translation by pushing the piston in its cylinder by compressing the air which is there and by driving it towards the tank of said power station.

5- As the compressor is double action, it means that by compressing the air in the cylinder on one side of the piston, the air will be sucked into the same cylinder on the other side of the same piston.

6- At the end of its stroke the piston will have completed the escape of the compressed air, and at the same time will have admitted on the other side all the air necessary to fill the same cylinder.

11 REPLACEMENT LEVEL (RULE 26) 7- At this moment, the tab that controls the contactors actuates a second contactor which actuates a second circuit breaker, to stop the motor then restart it in the other direction.

8- In the same way, the motor rotates the worm gear of the screw of the screw jack in the other direction, to push back the piston, which starts at that moment, the compression of one side of the piston where the air is in the cylinder, and on the other side of the same piston, the admission of air into the same cylinder of the same piston.

9- Arrive at the end of his new race which is the same as the one crossed before but in the opposite direction, the piston will have finished the escape of the compressed air, and at the same time will have admitted on the other side all the air needed to fill the cylinder.

10- Again, at this moment, the tab that controls the contactors actuates the first contactor which actuates the first circuit breaker to stop the engine then to restart it again in the other direction, start a new cycle of compression and release. amission on both sides of the same piston in the same cylinder.

11- The screw and gears of the screw jack are lubricated by the oil in the housing of the screw jack.

12- During the compression of the air, 80 to 93% of the necessary energy is lost in heat. So to recover a good part of this lost heat, we used a water cooling system for the entire compressor, to be able to recover a good part of the heat lost during the compression, thanks to a heat exchanger which helps to heat the water of the basin of the plant of the patent No. 2328580.

Optionally, the pistons can be cooled as well, through holes that are machined or molded and flexible hoses that connect the intake and return of the cooling water to the main cooling system. This helps to cool the inside of the cylinders at the same time.

Cooling the inside of the cylinders by means of their own pistons has never been possible before in this way, because of the configuration of the other conventional compressors and the complexity of their operation compared to the operation of the present compressor the subject of the present invention.

The volume of the air is affected by the temperature according to the following formula:

Vl / V2 = T2 / T1 where Vl is the volume at temperature T1.

Tl is the temperature of the air before warming, in degrees Kelvin.

V2 is the volume at temperature T2.

T2 is the temperature after warming, in degrees Kelvin.

Ex.5: If the temperature of 210 cubic meters of air is 20 degrees Celsius or 293 degrees

Kelvin

At 343 degrees Kelvin the 210 cubic meters will be: 210 cubic meters x 343/293 = 246 cubic meters.

The volume increase is: 246 cubic meters - 210 cubic meters = 36 cubic meters. Or: (36 cubic meters / 210 cubic meters) x 100% = 17%

This means that the plant that uses this flow, gives 17% more energy with an increase of (343 - 293) = 50 degrees.

If one makes the calculations of the power of the power station which uses this flow of 210 cubic meters of air with 7 bars, one will have:

The average volume of compressed air in the power bells of this plant is approximately 15 cubic meters according to Boyle's law and the method followed in the example of Canadian Patent No. 2328580.

So the power of this plant, if its rotation speed is 47 rpm, will be:

(15 cubic meters x 1000 kgs / m3 x 9.81 N x 1.406 meters (the motor radius of the plant) x 2 x 3.1416 x 47 rpm) divided by 60 secs. = 1,018,294 joules or 1,365 horsepower.

At 40% efficiency: 1,365 horsepower x 40% = 546 horsepower

with 17% more, the power of the plant will be

[(546 horsepower xl7%) + 546 horsepower] = 639 horsepower

13

SUBSTITUTE SHEET (RULE 26.) So the positive energy that the plant produces with the flow of the compressor taken as an example of the present invention will be: 639 horsepower less 420 horsepower = 219 horsepower

This is with a 70% efficiency for the compressor and 40% for the plant. We can imagine the positive power we can have with better performance!

Other aspects of this invention:

A- a two-cylinder compressor, which has a single cylinder installed on each side of the screw jack where the same screw actuates the two pistons as follows:

The cylinders of a two-cylinder compressor may have the same diameter or different diameters, but their respective pistons must have the same length, because they traverse from the beginning of the compression until the end of the at the same time, the same distance which is traversed by the screw of the screw jack which pushes or pulls them into their respective cylinders according to the cycle which will be on one side or the other of the translation Linear screw of the screw jack, which is equal to the distance between the beginning of the compression and the end of the exhaust of each cycle. The operation of these two cylinders is in parallel, it means that when there is admission in a cylinder on one side of its piston there will be compression in the same cylinder but on the other side the same piston, exactly, the same thing occurs parallel and at the same time in the second cylinder of the same compressor, it means, compression with compression, and admission with admission.

2- The two pistons of the same compressor are attached on both sides to the screw of the screw jack which operates them parallel and at the same time, so The distance that the screw crosses in one direction or another does not vary for one or two cylinders but the power required for its operation will be proportional to the force to be overcome and which exerts at the same time on the total surface of the two pistons by the air which is compressed at the same time inside the two cylinders.

B- a multiple cylinder compressor which has cylinders installed on one side or both sides of the screw jack where the same screw actuates all the pistons in the following way:

14 SUBSTITUTE REPLACEMENT (RULE 26) - The screw jack will be made as that of a single-cylinder compressor, if the cylinders and their pistons were installed on one side of the screw of the screw jack, or as that of a two-cylinder compressor, if the cylinders and their pistons were installed on both sides of the screw of the screw jack.

- The pistons on each side are attached together in a way that the first piston adjacent to the screw on either side, receives the force and the reciprocating linear movement of the screw and transmits them directly and at the same time to the other pistons other cylinders on each side via an intermediate coupling pin and a coupling that is installed between each two adjacent pistons of each two adjacent cylinders also on each side, which promotes parallel operation for all the cylinders and their pistons as described above for the operation of a two-cylinder compressor. So the distance that the screw crosses in one direction or another, does not vary as for one or two cylinders, but the power required for its operation will also be proportional to the force to overcome that exerts at the same time on the surface total of all the pistons of all the cylinders by the air that is compressed at the same time inside all the cylinders of the same compressor.

- The pistons and cylinders of a multi-cylinder compressor are made in the same way as the cylinders and pistons of a two-cylinder compressor, but the mandatory use of integral intermediate axes of each two pistons of each two cylinders which will be installed in series one after the other, will be required so that the same screw of the same screw jack can operate them together and in one fell swoop.

- Instead of using large cylinders with special dimensions, several standard size cylinders will be used to compensate for the same volume of a single large cylinder if a large airflow is needed, which helps to increase the efficiency of the same compressor and lower the cost of its manufacture according to the power used. The advantage of using this screw jack compressor, the subject of the present invention, is to produce different compressed air flow rates in an efficient manner with the use of low power engines which consume much less energy. energy that conventional compressors providing the same air flow as we saw above, in the example of the calculation of the power of the two kinds of compressors.

As there are no dimensional limits in the manufacture of this compressor, and although it can be manufactured in many ways and different materials. It has been represented for the clarity and ease of its examination on 27 figures.

Short description of the drawings:

1 represents a front view in section along the line A-A of FIG. 2 of a single-cylinder compressor.

2- Figure 2 shows a schematic view from above of a two-cylinder compressor coupled to the tank of the plant of Canadian Patent No. 2328580, and the heat exchanger.

3- Figure 3 is a schematic side view of a central Canadian patent No. 2328580

4-5-6-7-8- Figures 4 to 8 show sectional views along the line AA of Figure 2 of a single cylinder compressor, showing the piston pushed into its cylinder by the screw of screw jack, from the beginning of the compression of the air by the left side of the piston, until the end of the exhaust of the compressed air. In addition we see the aspiration of the air by the right side of the same piston from the beginning of the admission until the total filling of the cylinder.

FIGS. 9 to 13 show cross-sectional views along line AA of FIG. 2 of the same single-cylinder compressor, showing the piston pulled to the right in its cylinder by the same screw of the same screw jack, from the beginning of the compression of the air by the right side of the piston, until the end of the exhaust of the compressed air. In addition we see the suction of the air by the left side of the same piston from the beginning of the admission until the total filling of the cylinder.

FIGS. 14 and 15, if placed in order 15-14 from left to right, represent sectional views along line AA of FIG. 2 for a two-cylinder compressor and other of the same screw of the same screw jack.

16-18- Figures 16 to 18, if they are placed in the order 18-17-16 from left to right, they represent views of faces in section along the line AA of Figure 2 of a cylinder compressor multiple placed on either side of the same screw of the same screw jack.

19 is a schematic view from above of a six-cylinder compressor placed in groups of three, one next to the other, on either side of the same screw of the same cylinder. screw.

FIG. 20 is a schematic top view of a multi-roll compressor located on one side of the screw jack screw.

21 is a right view of FIG.

22 is a left view of FIG.

23 is a schematic top view of a multiple cylinder compressor placed on either side of the same screw of the same screw jack.

Fig. 24 shows a sectional front view of the screw jack screw and the single piston of a single cylinder compressor which are made of a single piece.

25 shows a front view in section of the same screw of the same screw jack which operates at the same time on both sides of its path two pistons of a two-cylinder compressor. 26 shows a front view in section of the same screw of the same screw jack which operates at the same time on both sides of its path of the pistons of a multiple cylinder compressor.

27-Figure 27 shows an enlarged sectional front view of a piston.

Figs. 28 to 37 show schematic views of 8 compressors used in groups as an example, to share equally, and to deliver In a continuous manner, the compressed air at 7 bar of the flow rate which is necessary for a reliable and continuous operation of the plant of the example of the present application.

Other objects and advantages will become apparent from the following description given with reference to the accompanying drawings which represents by way of non-limiting example, an embodiment of the present invention.

On the drawing:

Figure 1 shows a front view in section along the line AA of Fig.2 of a single cylinder compressor. It shows the cylinder 1, the piston 2, the screw 3 of the screw jack 3- A, the nut-gear 4 which turns idly in the bore 6-A of the armature 6 to alternate the direction of movement of the screw 3, the motor 11 which rotates the gear-nut 4 by means of the pinion 5 through the axis 26, the tongue 7 which actuates the electrical contactors 8 and 9 which control an electric circuit breaker 9-A-8- A serving to control the direction of rotation of the motor 11 which determines the direction of translation of the screw 3 of the screw jack 3-A each time the piston 2 reaches the end of a cycle of the compression of the in one direction or another. The valve 15 of the admission of air into the cylinder 1 on the left side 46 of the piston 2, the valve 12 of the exhaust of the compressed air to the reservoir 39 of the unit E of FIG. line 22, the valve 14 of the admission of air into the cylinder 1 on the right side 47 of the piston 2, the valve 13 of the exhaust of the compressed air to the reservoir 39 of the unit E of FIG. through line 23, the cooling water 16 of the cylinder 1, the main lines 33 and 34 of the main cooling system, the inlet 18 and the outlet 17 of the cooling water of the piston 2, the flexible hoses 35 and 36 that connect the water of cooling the piston 2 to the main cooling system during operation of the compressor to cool the inside of the cylinder 2 through the passage 16- A which is in the piston. The housing 19 which contains the oil 20 which serves to lubricate the screw 3 and all the gears of the screw jack 3 -A, the coupling 10 which serves to fix the screw 3 to the pistons which are not an integral part of the screw of the screw jack, and to connect the flexible hoses 35 and 36 to facilitate the cooling of the pistons and the inside of their respective cylinders, during the operation of said compressor, in addition it serves to hold the tongue 7 in place so that it moves with the screw 3 of the screw jack 3 -A on either side, the same distance that the piston passes through its cylinder between the beginning of the compression and the end of the exhaust of the compressed air of each cycle.

FIG. 2 represents a diagrammatic view from above of a two-cylinder compressor coupled to the reservoir 39 of the plant E of FIG. 3, and to the heat exchanger 43 which serves to recover the heat lost during the compression of the air. It shows the screw jack 3- A which action on both sides two pistons 2 and 2-A in two cylinders 1 and 1-A, the air inlets 24 and 25 of the cylinder 1, the inputs of the air 24-A and 25-A of the cylinder 1-A, the lines 22 and 23 which passes the compressed air from the cylinder 1 to the reservoir 39 through the line 37, the lines 22-A and 23 -A which passes through the compressed air from the cylinder 1-A to the reservoir 39 through the line 38, the pressure gauge 41 which indicates the pressure of the compressed air in the reservoir 39, the regulator 42 of the pressure of the compressed air which determines the pressure maximum of the air leaving the compressor, the line 40 which passes the compressed air to the central E of Figure 3, the main lines 33 and 34 which serve for the cooling water of said compressor to flow through the cylinders 1 and 1-A and the pistons 2 and 2-A, through the lines 17 and 18 and the heat exchanger 43 which serves to recover the heat lost during the compression air in the compressor, by the water of the basin 1-E of the central E of Figure 3 which flows through the lines 44 and 45.

FIG. 3 represents a schematic view of the central unit E of the Canadian patent No. 2328580. It shows the line 40 which carries the compressed air from the reservoir 39 of FIG. 2 through the pressure regulator 42 to the rotary joint 18-E the central E, the lines 44 and 45 through which the water of the basin 1-E of the central E circulates through the heat exchanger 43 of Figure 2 to recover the heat produced by the compression of air. The hot water in the basin is used to heat the air in the power bells of the E plant, which results in a substantial increase in the power of the plant E because the hot air increases in volume to move a larger amount of liquid, where the thrust on the motor bells, is equal to the weight of the liquid moved.

FIG. 4 represents a front view in section along the line AA of FIG. 2 of a single-cylinder compressor, showing the piston 2 at the beginning of the compression of the air by the side 46, it is pushed into its cylinder 1 by the screw 3 of the screw jack 3-A. It also shows that the valve 12 of the exhaust of the compressed air on the side 46 and the valve 13 of the exhaust of the air on the side 47 which are closed, the valve 15 of the admission of the air on the side 46 which is still closed, and the valve 14 of the air intake of the side 47 which begins to open to facilitate the admission of air into the cylinder 1 on the side 47 of the same piston 2 when it starts to sink into the cylinder 1 by compressing the air on the side 46. Again we see the tab 7 which actuated the switch 8 which controls the circuit breaker 9-A-8-A of the motor 11 for that it turns in the right direction to send the screw 3 of the screw jack 3-A to the left.

FIG. 5 represents a front view in section along the line AA of FIG. 2 of a single-cylinder compressor, showing the piston 2 which has just crossed half its travel to the left, and the volume of the compressed air which has just dropped by half and where its pressure has just increased by 1 bar according to the calculations of Example 2 of the present disclosure. It also shows that the valve 12 of the exhaust of the compressed air on the side 46 and the valve 13 of the exhaust of the air on the side 47 which are closed, the valve 15 of the admission of the air on the side 46 which is still closed, and the valve 14 of the admission of the air on the side 47 which is always open so that the air continues to enter the same cylinder 1 on the side 47 of the same piston 2, and the tongue 7 which is in the middle of its stroke between switches 8 and 9.

FIG. 6 represents a front view in section along the line AA of FIG. 2 of a single-cylinder compressor, showing the piston 2 at 3/4 of its stroke or at 1/4 of the end of the compression, and the volume of compressed air that has just dropped by 3/4 of its original volume (FAD) where it is made to 1/4 of its initial volume (FAD), and where its pressure is returned to 3 bars according to calculations of Example 2 of the present disclosure. It also shows that the valve 12 of the exhaust of the compressed air on the side 46 and the valve 13 of the exhaust air on the side 47 which are always closed, the valve 15 of the intake of the air air on the side 46 which is still closed, and the valve 14 of the admission of the air of the side 47 which is still open so that the air continues to enter the same cylinder 1 on the side 47 of the same piston 2, and the tongue 7 which is 3/4 of its stroke between the contactors 8 and 9 or 1/4 of the end from his run to the left.

FIG. 7 shows a front view in section along the line AA of FIG. 2 of a single cylinder compressor, showing the piston 2 at 7/8 of its stroke or at 1/8 of the end of the compression and the exhaust of the compressed air, and the volume of the compressed air which comes down from 7/8 of its volume where it is returned to 1/8 of its initial volume (FAD), and where its pressure is returned to 7 bars according to the calculations of Example 2 of the present disclosure. It also shows that the valve 12 on the side 46 which has just opened so that the compressed air passes to the reservoir 39 of the plant E through the line 22 and then through the line 37, so that the air pressure The compressed air required for the proper operation of the central unit E is adjusted to 7 bar by the pressure regulator 42. The air outlet valve 13 on the side 47 of the same piston 2 which is always closed, the valve 15 of the admission of the air on the side 46 which is still closed, the valve 14 of the admission of the air on the side 47 which is always open so that the air continues to enter the same cylinder 1 on the side 47 of the same piston 2, and the tongue 7 which is 7/8 of its stroke between the contactors 8 and 9 or 1/8 of the end of its race to the left for this cycle.

Figure 8 shows a front view in section along the line A-A of FIG. 2 of a single-cylinder compressor, showing the piston 2 at the end of its stroke where it evacuated all the compressed air at the constant pressure of 7 bars to the reservoir 39. It also shows that the valve 12 of the side 46 of the piston 2 which is always open, the valve 13 of the exhaust air on the side 47 of the same piston 2 which is still closed, the valve 15 of the air intake on the side 46 of the same piston 2 which is closed, the valve 14 of the admission of the air on the side 47 which is always open until the end of the admission of air into the cylinder 1 on the side 47 of the same piston 2, and the tongue 7 which has just completed its race for this cycle, by actuating the switch 9 to stop the motor 11 and then restart it in the other direction so that the screw 3 of the screw jack 3-A starts to pull the piston 2 in the other direction by starting a new cycle.

FIG. 9 represents a front view in section along the line AA of FIG. 2 of a single-cylinder compressor, showing the piston 2 pulled by the screw 3 of the screw jack 3-A in its cylinder 1 towards the right at the beginning of the compression of the air in the same cylinder 1 by its side 47, It also shows that the valve 12 of the compressed air exhaust on the side 46 and the valve 13 of the exhaust air on the side 47 which are closed, the valve 15 of the admission air on the side 46 which is open to facilitate the admission of air into the same cylinder 1 on the side 46 of the same piston 2 when it begins to sink in the same cylinder 1 by compressing the air which- there is on the side 47 to the right, and the valve 14 of the admission of air on the side 47 which is closed. Again we see the tab 7 which actuated the switch 9 which controls the circuit breaker 9-A-8-A of the motor 11 to turn in the right direction by sending the screw 3 in the desired direction.

FIG. 10 shows a front view in section along the line AA of FIG. 2 of a single-cylinder compressor, showing the piston 2 which has just crossed half of its travel to the right, and the volume of the compressed air which has just dropped by half, and where its pressure has just increased by 1 bar according to the calculations of Example 2 of the present disclosure. It also shows that the valve 12 of the exhaust of the compressed air on the side 46 of the piston 2 and the valve 13 of the exhaust of the air on the side 47 of the same piston 2 which are closed, the valve 15 of the intake of air on the side 46 of the piston 2 which is always open so that the air continues to enter the same cylinder 1, the valve 14 of the air intake of the side 47 which is closed, and the tongue 7 which is in the middle of its stroke between the contactors 8 and 9.

FIG. 11 shows a front view in section along the line AA of FIG. 2 of a single-cylinder compressor, showing the piston 2 at 3/4 of its stroke or at 1/4 of the end of the compression of the side 47 of the piston 2, and the volume of the compressed air which has just dropped by 3/4 of its volume (FAD) where it is returned to 1/4 of the initial admitted volume (FAD), and where its pressure is made at 3 bars according to the calculations of Example 2 of the present disclosure. It also shows that the valve 12 of the exhaust of the compressed air on the side 46 of the piston 2, and the valve 13 of the exhaust of the air on the side 47 of the same piston 2 which are always closed, the valve 15 of the admission of the air on the side 46 of the piston 2 which is always open so that the air continues to enter the same cylinder 1, the valve 14 of the air inlet of the side 47 of the same piston 2 which is always closed, and the tongue 7 which is 3/4 of its stroke between the contactors 8 and 9 or 1/4 of the end of its stroke to the right.

FIG. 12 shows a front view in section along the line AA of FIG. 2 of a single-cylinder compressor, showing the piston 2 at 7/8 of its stroke or at 1/8 of the end of the compression and exhaust of this cycle, and the volume of compressed air that has just dropped by 7/8 of its initial volume (FAD) where it is rendered at 1/8 of its initial volume allowed (FAD) and where its pressure is made to 7 bar according to the calculations of Example 2 of the present disclosure. It also shows that the valve 13 on the side 47 of the piston 2 has just opened so that the compressed air passes to the same reservoir 39 of the plant E through the line 23 through the same main line 37 which has passed through the compressed air on the side 46 of the same piston 2, because the pressure of the compressed air necessary for the proper operation of the present unit E is the same which is adjusted to 7 bar by the same regulator 42 of the pressure, the valve 12 of the exhaust air on the side 46 of the same piston 2 which is always closed, the valve 14 of the air intake on the side 47 of the same piston 2 which is still closed, the valve 15 of the admission of the air from the side 46 of the piston 2 which is always open so that the air continues to enter the same cylinder 1, and the tongue 7 which is 7/8 of its stroke between the contactors 8 and 9 or 1/8 from the end of his race to the right.

FIG. 13 shows a front view in section along the line AA of FIG. 2 of a single-cylinder compressor, showing the piston 2 at the end of its stroke, where it has evacuated all the compressed air at constant pressure 7 bar to the reservoir 39. It also shows that the valve 13 of the exhaust air on the side 47 of the piston 2 is still open, the valve 12 of the exhaust air on the side 46 of the same piston 2 which is closed, the valve 14 of the air intake on the side 47 of the same piston 2 which is closed, the valve 15 of the air inlet of the side 46 of the piston 2 which is always open until at the end of admission of the air into the same cylinder 1 on the side 46 of the same piston 2, and the tongue 7 which has just completed its travel to the right by actuating the contactor 8 to stop the engine 11 and then to restart it again to the left so that the screw 3 of the screw jack 3-A starts to push the piston 2 to the left, in starting a new compression cycle on the side 46 and admission of the air on the side 47 of the same piston 2 in the same cylinder 1.

Figures 14 and 15 show views of faces, in section along the line A-A of Figure 2 for a two-cylinder compressor. If we place figure 14 on the right and figure 5 on the left, we see a compressor consisting of 2 cylinders placed on either side of the screw 3 of the screw jack 3 -A. Again we see the screw 3 of the screw jack 3 -A, which is attached to the piston 2 to the left and the piston 2- A to the right by the couplings 10, the gear-nut 4, the pinion 5, the tab 7, the contactors 8 and 9, the motor 11. To the left of the screw jack 3- A on

.23. FOBLT UE TM ⁵ LAtBTeTT (RULE 2S) see the cylinder 1, the piston 2 attached to the screw 3 of the screw jack 3-A by the coupling 10, the exhaust valves 12 and 13, the intake valves 14 and 15. To the right we see the piston 2- A in its cylinder 1-A, which is attached to the screw 3 of the screw jack 3- A also by another coupling 10, so that it operates in parallel with the piston 2 of the cylinder 1 by the same screw 3 of the screw jack 3 -A, that means, when there is compression on the side 46 of the piston 2 in the cylinder 1, there will be compression on the side 49 of the piston 2-A in the cylinder 1-A, and at the same time the suction is in the cylinder 1 on the side 47 of the piston 2 and in the cylinder 1-A on the side 48 of the piston 2- A. In the other direction of translation of the screw 3 of the screw jack 3-A, the compression will be on the side 47 of the piston 2 in the cylinder 1 and the side 49 of the piston 2- A in the cylinder 1-A, but the admission is on the side 46 of the piston 2 in the cylinder 1 and the cot 49 of the piston 2 in the cylinder A-1-A. FIG. 14 also shows the inlets 17 and 18 of the cooling water of the pistons 2 and 2 A, the flexible hoses 35 and 36 which communicate the cooling water to the pistons 2 and 2 A during compressor operation.

Figures 16 to 18 show sectional views along the line A-A of Figure 2 for a multiple cylinder compressor placed on either side of the screw 3 of the screw jack 3-A. If FIG. 17 in the middle, Fig.18 on the left and Fig.16 on the right we see a compressor composed of 4 cylinders, but it can be made of many more cylinders. This compressor, like those that are single- or twin-cylinder, is a double-acting compressor, and all its cylinders operate in parallel, but the force that the screw 3 of the screw jack 3- A must exert at the same time to compress the air found in all the cylinders is equal to the pressure of the compressed air expressed for example in newtons / cm 2, multiplied by the total surface of the pistons which compress air at the same time, expressed in square centimeters. This force is enormous compared to the moment of torque that the motor 11 of the screw jack 3-A must develop so that the screw 3 can push and pull at the same time all pistons compressing air.

Between the beginning of the compression and the beginning of the exhaust of the compressed air, the force exerted on all the pistons is equal to the average pressure of the compressed air, multiplied by the total surface of all the pistons which compress look at the same time. And between the beginning of the exhaust and the end of the exhaust of the air, the force exerted on all the pistons is equal to the constant pressure of the compressed air, multiplied by the total surface of all the pistons which compress air at the same time. The following formula must be applied for calculate the total torque moment needed to complete air compression from start to end of exhaust.

The energy required to compress and then escape the compressed air of the compressor is equal to:

the average pressure between the beginning of the compression and the beginning of the escape of the air in newtons / square centimeters x by the total surface of all the pistons in square centimeters x by the number of steps of the screw 3 of the screw jack 3-A (distance between start of compression and start of exhaust in meters / pitch of screw 3 of 3-A screw jack in meters) divided by (2 x 3.1416)} more {[the constant pressure between the beginning of the exhaust and the end of the exhaust of the air in newtons / square centimeters x by the total surface of all the pistons in square centimeters x by the number of steps of the screw 3 of the screw jack 3-A (distance between the start of the exhaust and the end of the air exhaust in meters / the pitch of the screw 3 of the screw jack 3-A in meters)] divided by ( 2 x 3.1416)

In these figures 16 to 18, we see the screw 3 of the screw jack 3-A, which is attached to the pistons 2 to the left and to the piston 2- A to the right by the couplings 10, the nut-gear 4, the pinion 5, the tongue 7, the contactors 8 and 9, and the motor 11. To the left of the screw jack we see the cylinder 1, the piston 2 attached to the screw 3 of the screw jack 3-A by the coupling 10, the exhaust valves 12 and 13 and the intake valves 14 and 15 of the cylinder 1, also seen to the left of the cylinder 1, the cylinder 1-B, its exhaust valve 12-B and 13 -B, its intake valves 14-B and 15-B and its piston 2-B which is firmly attached to the piston 2 of the cylinder 1 by the intermediate coupling pin 52 and the coupling 10 which transmit the force and the reciprocating linear motion of the screw 3 of the screw jack 3-A to the piston 2-B through the piston 2. On the right we see the cylinder 1-A, its exhaust valves 12-A and 13-A, its 14-A intake valves and 15-A and its piston 2- A, also to the right of the cylinder 1-A, the cylinder 1-C, its exhaust valves 12-C and 13-C, its valves 14-C and 15 -C and its piston 2-C which is firmly attached to the piston 2-A of the cylinder 1-A by the intermediate coupling axis 52 and the coupling 10 which also transmit the force and the reciprocating linear movement of the screw 3 from the 3-A screw jack to the 2-C piston through the 2-A piston. All cylinders of this multiple compressor work together and in parallel with the same screw 3 of a single screw jack 3-A according to the same method explained above for the two-cylinder compressor, it means that when there is compression on the side 46 of the piston 2 in the cylinder 1, there will be the

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REPLACEMENT PASS (RULE 26) compression on the side 49 of the piston 2 -A in the cylinder 1-A, and at the same time there will be compression on the side 54 of the piston 2-B of the cylinder 1-B thanks to the intermediate coupling axis 52 which is secured to one side of the piston 2, and the other side of the piston 2-B, also there will be compression on the side 51 of the piston 2-C of the cylinder 1-C through the axis coupling intermediate 52 which is integral on one side, the piston 2-A, and the other side of the piston 2-C. The suction is in this case, on the side 47 of the piston 2 in the cylinder 1, on the side 48 of the piston 2- A in the cylinder 1-A, the side 53 of the piston 2-B in the cylinder 1-B and on the side 50 of the piston 2-C in the cylinder 1-C. In the other direction of the translation of the screw 3 of the screw jack 3-A, the compression will be on the side 47 of the piston 2 in the cylinder 1, on the side 53 of the piston 2-B in the cylinder 1-B, the side 48 of the piston 2- A in the cylinder 1-A, and the side 50 of the piston 2-C in the cylinder 1-C, but the admission is on the side 46 of the piston 2 in the cylinder 1, on the side 49 piston 2-A in the cylinder 1-A, the side 54 of the piston 2-B in the cylinder 1-B, and the side 51 of the piston 2-C in the cylinder 1-C. This configuration will be used in all multi-cylinder compressors, regardless of the number of cylinders that will be coupled to the same compressor on one side or both sides of the same screw 3 of the same 3-A screw jack that will be used with the same compressor.

Figure 19 is a schematic top view of a six-cylinder compressor placed in groups of three on either side of the screw jack 3-A. it is seen to the left of the screw jack 3 -A, the left side of the screw 3 attached to the armature 58 which serves to simultaneously maneuver all the pistons 2, PI, and P-2 in the cylinders 1, CI and C-2 through the fasteners 57 which connect the pistons 2, PI, and P-2 to the armature 58. To the right of the screw jack 3-A, we see the right side of the screw 3 attached to the armature 58 which serves to maneuver at the same time all the pistons 2- A, P-3, and P-4 in the cylinders 1-A, C-3 and C-4 by means of the fasteners 57 which connect the pistons 2-A, P-3, and P-4 has the frame 58.

Figure 20 shows a schematic top view of a 27-cylinder compressor placed on the left side of the screw jack 3 -A. It shows the screw jack 3 -A, the screw 3, the piston 2 of the cylinder 1 which is integral with the piston 2-B of the cylinder 1-B via the coupling pin 52 and the coupling 10, the piston 2-B of the cylinder 1-B which is integral with the piston P-8 of the cylinder C-8 via the intermediate coupling axis 52 and the coupling 10, the piston PI of the cylinder CI which is secured to the piston P-5 of the cylinder C-5 via the coupling pin 52 and the coupling 10, the piston P-5 of the cylinder C-5 which is integral with the piston P-7 of the C-7 cylinder via the axis

SUBSTITUTE SHEET (RULE 26) coupling intermediate 52 and the coupling 10, the piston P-2 of the cylinder C-2 which is integral with the piston P-6 of the cylinder C-6 via the intermediate coupling shaft 52 and the coupling 10, the piston P-6 of the cylinder C-6 which is integral with the piston P-9 of the cylinder C-9 via the intermediate coupling shaft 52 and the coupling 10. In addition, the armature 58 through which the screw 3 of the screw jack 3-A which operates at the same time and in parallel all the pistons of all the cylinders through the fasteners 57.

FIG. 21 represents a right view of FIG. 20. It shows the first nine cylinders of the nine rows of cylinders of the same compressor, the screw jack 3-A which operates at the same time all the pistons of all the cylinders thanks to the armature 58 and the joints 57 by which the nine first pistons of the first nine cylinders are attached to the armature 58.

FIG. 22 represents a left view of FIG. 20. It shows the last nine cylinders of the nine rows of cylinders of the same compressor, the screw jack 3-A and the frame 58.

FIG. 23 represents a schematic view from above of an 18-cylinder compressor placed on both sides of the 3-A screw jack in groups of nine cylinders on each side. It shows on the left, the screw jack 3 -A, the left side of the screw 3, the piston 2 of the cylinder 1 which is integral with the piston 2-B of the cylinder 1-B via the intermediate axis 52 and the coupling 10, the piston 2-B of the cylinder 1-B which is integral with the piston P-8 of the cylinder C-

8 via the intermediate coupling pin 52 and the coupling 10, the piston PI of the cylinder CI which is integral with the piston P-5 of the cylinder C-5 via the intermediate axis of coupling 52 and the coupling 10, the piston P-5 of the cylinder C-5 which is integral with the piston P-7 of the cylinder C-7 via the intermediate coupling shaft 52 and the coupling 10, the piston P-2 of the cylinder C-2 which is integral with the piston P-6 of the cylinder C-6 via the intermediate coupling pin 52 and the coupling 10, the piston P-6 of the cylinder C -6 which is integral with the piston P-9 of the cylinder C-

9 through the intermediate coupling pin 52 and the coupling 10. In addition we see the armature 58 through which the screw 3 of the screw jack 3-A pushes or pulls in parallel all the pistons of all the cylinders on the left side of the compressor through the fasteners 57. To the right of the screw jack 3-A we see the right side of the screw 3, the piston P-3 of the cylinder C-3 which is secured to the piston P- 10 of cylinder C-10 via the intermediate axis

27

REWIPLAtEWIfMT SHEET (RULE 26) 52 and the coupling 10, the piston P-10 of the cylinder C-10 which is secured to the piston P-12 of the cylinder C-12 by the intermediate coupling pin 52 and the coupling 10, the piston 2- A cylinder 1-A which is integral with the piston 2-C of the cylinder 1-C via the intermediate coupling axis 52 and the coupling 10, the piston 2-C of the cylinder 1-C which is secured to the piston P-13 of the cylinder C-13 via the intermediate coupling pin 52 and the coupling 10, the piston P-4 of the cylinder C-4 which is integral with the piston PI l of the CI cylinder 1 through the intermediate coupling pin 52 and the coupling 10, the piston PI l CI cylinder 1 which is integral with the piston P-14 cylinder C-14 through the Intermediate coupling pin 52 and the coupling 10. In addition we see the frame 58 through which the screw 3 of the screw jack 3-A which is used to maneuver at the same time all the pistons of all the c ylinders of the same compressor on the right side, through the fasteners 57.

Fig. 24 is a sectional front view of the screw 3 of the 3A screw jack and the simple piston of a single cylinder compressor which are made of a single piece. It shows the piston 2 with its faces 46 and 47, the screw 3, the tongue 7, and the coupling 10.

Figure 25 shows a front view in section of the screw 3 of the screw jack 3- A and two pistons of a two-cylinder compressor. It shows the piston 2 with its faces 46 and 47, the piston 2- A with its faces 48 and 49, the screw 3, the coupling 10, the grooves 27 where the sealing segments are placed to compress the air, and the lines that serve to cool the pistons.

Figure 26 shows a front view in section of the screw 3 of the screw jack 3-A and the pistons of a multiple cylinder compressor. It shows, the pistons 2 with its faces 46 and 47, the piston 2-A and its faces 48 and 49, the piston 2-B and its faces 53 and 54, and the piston 2-C and its faces 50 and 51 the intermediate coupling axes 52 and the couplings 10 which are used to actuate all the pistons at the same time, the grooves 27, and the lines which serve to cool the pistons and the inside of the cylinders.

Figure 27 shows an enlarged sectional front view of a single piston. It shows the piston 2, the coupling 10 which serves to solidify the piston to the screw 3 of the screw jack 3-A, or on the intermediate coupling pin 52, which serves as an extension between each two pistons of each two cylinders that are installed one after the other in the same compressor has multiple cylinders, so that the screw 3 of the 3-A screw jack can operate all their pistons together in one fell swoop, and the 16-A bore where the water flows through the piston to cool it, and at the same time to cool the interior of its respective cylinder.

Figures 28 to 37 show schematic views of 8 compressors used in groups as an example, for even sharing, and for continuously delivering the compressed air at 7 bar of flow that is required for reliable operation. and continuous from the central of the example of the present application, regardless of the speed of translation, or the distance between the beginning of compression and the end of the exhaust of compressed air, which are the same for all the screws 3 of all the screw jacks 3-A which are used with said compressors. These compressors are independent of each other. So to have a continuous flow of compressed air to power the plant permanently, it is necessary that the flow of air (FAD) that is needed, is shared, compressed, escaped and delivered equitably in a successive manner and continuous by these said compressors which have the same flow rates per minute for each, that means that when the first compressor finishes to escape its compressed air, the second compressor must directly start to escape followed by the third, then by the fourth etc ..., then by the first which will be at the point of starting a new exhaust cycle, and so on according to the following demonstration:

In Figure 28 we see the compressor A at the beginning of its exhaust cycle at the same time that the compressor H has finished escaping its compressed air.

In Figure 29 we see the compressor B at the beginning of its exhaust cycle at the same time that the compressor A has finished escaping its compressed air.

In Figure 30 we see the compressor C at the beginning of its exhaust cycle at the same time that the compressor B has finished escaping its compressed air.

In Figure 31 we see the compressor D at the beginning of its exhaust cycle at the same time that the compressor C has finished escaping its compressed air.

In Figure 32 we see the compressor EE at the beginning of its exhaust cycle at the same time that the compressor D has finished escaping its compressed air. In Figure 33 we see the compressor F at the beginning of its exhaust cycle at the same time that the compressor EE has finished escaping its compressed air.

In Figure 34 we see the compressor G at the beginning of its exhaust cycle at the same time that the compressor F has finished escaping its compressed air.

In Figure 35 we see the compressor H at the beginning of its exhaust cycle at the same time that the compressor G has finished escaping its compressed air.

In Figure 36 we see the compressor A at the beginning of its exhaust cycle at the same time that the compressor H has finished escaping its compressed air.

In Figure 37 we see the compressor B at the beginning of its exhaust cycle at the same time that the compressor A has finished evacuating its compressed air.

In this way, these compressors supply the central air with the compressed air flow that is necessary for its proper operation, but according to the pressure of the air required which determines the number of compressors to be used.

If the requested pressure is 1 bar, then we will need a group of two compressors, and if the requested pressure is 3 bar, at that moment we will need a group of 4 compressors, and so on .

The total power required to continuously compress and escape, the throughput that is required for reliable and continuous operation of any plant, is equal to the total of all the powers of all the compressors that are used to deliver that flow in a continuous and shared way for the plant to be efficient and operational.

Although this compressor can be manufactured in many ways and different materials, it can have very different dimensions depending on the amount of compressed air that needs to be produced.

And although the drawing does not show the methods of carrying out the present invention, it gives a general idea of clear assey.

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SUBSTITUTE TEXT (RULE 26) Before starting the compressor the subject of the present invention must have all their elements in place:

The pressure of the compressed air will be determined in order to be able to inject the compressed air into the motor bells of the central unit E of the Canadian patent No. 2328580 of FIG. 3, and it will be controlled by a pressure regulator 42. For the present the pressure has been chosen to be 7 bar or 7 kgs / cm 2, and for the plant to operate reliably, it is necessary to have a group of 8 compressors to share the total flow of said plant according to the demonstration of FIGS. .

2- The lines 37 and 38 which pass the compressed air to the reservoir 39 of the unit E from the compressor the subject of the present invention, will be joined to all the outlets of the compressed air 22 ... and 23 .. .. of all said compressors of the same group.

3- The main lines 33 and 34 of the cooling system of said compressors will be connected to all lines 17 and 18 which communicate the cooling water to the cylinders and their piston to be able to circulate the cooling water between the compressors and the heat exchanger 43.

4- The lines 44 and 45 will be connected to the pool 1-E of the central E of FIG. 3 to circulate the water of said central unit E through the heat exchanger 43, to heat the water of the basin 1-E with the heat generated during the compression of the air in the compressors the subject of the present invention.

5- The plant E of the 2328580 patent will be in place to receive the compressed air from the reservoir 39 through the line 40.

Finally, after all the components of each of these compressors and the power plant are in place, and after it is certain that the compressors will operate in an orderly manner so that the flow is delivered in a continuous manner, each of these compressors is started, all of which work, in the same way, but their individual exhaust cycles will be shifted so that the compressed air is sent to the plant in a continuous and uninterrupted manner. The distance traveled from the beginning of the

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LOSS OF REPLACEMENT (RULE 26) compression until the beginning of the exhaust of compressed air in the case of 7 bars of pressure in each cycle by each piston or by all the pistons of the same compressor, depending on whether it is one or more cylinders, is equal to 7 times the distance between the start of the escape and the end of the escape of the same cycle. Then for each compressor there are the flow rates of the other 7 compressors to compensate for the dead time of each, which makes the operation of said plant possible in a continuous and efficient manner.

The individual operation of these compressors is as follows:

In Figure 4 we see the tongue 7 which touched the switch 8 to actuate the motor 11 in the direction that allows the pinion 5 to turn the nut-gear 4 which begins to move the screw 3 of the screw jack 3-A to the left, to push the piston 2 also to the left by starting the compression of the air by the side 46 in the cylinder 1, at the same time, air will be sucked through the valve 14 in the same cylinder 1 but on the side 47 of the same piston 2.

FIGS. 5 to 7 show the screw 3 which continues to push the piston 2 to the left while continuing to compress the air on the side 46 in the cylinder 1, at the same time the piston 2 continues to suck air from the side 47 through the valve 14 in the same cylinder 1.

In Figure 7 we see that the volume of the air is made to 1/8 of the initial volume of air admitted into the cylinder 1 at atmospheric pressure (FAD), where its pressure is returned to 7 bars according to calculations of Example 2 of the present disclosure, at this time, the valve 12 begins to open to let out the compressed air to the reservoir 39 through the line 22. In this Figure 7 we see that the screw 3 continue to push the piston 2 to the left in its cylinder 1.

In FIG. 8 it can be seen that the piston 2 has arrived at the end of its stroke to the left after having pumped all the compressed air towards the reservoir 39, by the side 46, and after having admitted by the side 47, the entire air required to fill the cylinder 1 on the side 47 to be compressed when the piston is pulled to the right by the same screw 3 of the screw jack 3 -A. When the piston 2 has arrived at the end of its stroke, we see the tongue 7 which touches the switch 9 to stop the motor 11 and then restart it to the right to start another compression cycle

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LOSS OF REPLACEMENT (RULE 26) by the side 47, and admission of the air by the side 46 in the same piston 1, which is detailed in Figures 9 to 13 according to the same method of Figures 4 to 8. But the piston 2 will be pulled to the right to compress by the side 47 and aspire by the side 46.

If the compressor is two-cylinder and are placed on both sides of the screw 3 of the screw jack 3- A according to Figures 15, 14. When the motor 11 turns the pinion 5, the gear 4 rotates to move the screw 3 linearly on either side as appropriate. If the screw 3 moves to the left it pushes the piston 2 in its cylinder 1 through the coupling 10 to the left to compress the air on the side 46 of the piston 2, and suck air by the side 47 of the same piston 2 in the same cylinder 1, at the same time the screw 3 pulls the piston 2-A in its cylinder 1-A through the coupling 10 to the left to compress the air on the side 49 and suck air by the side 48 of the same piston 2-A in the same cylinder 1-A. And if the screw 3 moves to the right, it pulls the piston 2 in its cylinder 1 through the coupling 10 to compress the air on the side 47 and suck air by the side 46 of the same piston 2 in the same cylinder 1, at the same time the screw 3 pushes the piston 2-A in its cylinder 1-A through the coupling 10 to the right to compress the air on the side 48 and suck air by the side 49 of the same piston 2 -A in the same cylinder 1-A.

If the compressor is multi-cylinder and are placed on both sides of the screw 3 of the screw jack 3-A according to Figures 18, 17, and 16. When the motor 11 turns the pinion 5, the gear 4 rotates to move the screw 3 linearly on either side according to the case explained above for a cylinder with two cylinders. If the screw 3 moves to the left, it pushes the piston 2 in its cylinder 1 through the coupling 10 to the left to compress the air on the side 46 of the piston 2 and suck air by the side 47 of the same piston 2 in the same cylinder 1, and this movement will be transmitted to the piston 2-B of Figure 18 through the intermediate coupling axis 52 and the coupling 10 which attach the piston 2 to the piston 2-B, for that the piston 2-B compresses the air at the same time by the side 54 in its cylinder 1-B and suck air by the side 53 of the same piston 2-B in the same cylinder 1-B, at the same time the screw 3 pulls the piston 2-A in its cylinder 1-A through the coupling 10 to the left to compress the air on the side 49 and suck air by the side 48 of the same piston 2-A in the same cylinder 1-A, and this movement will be transmitted to the piston 2-C of FIG. 17 through the intermediate coupling axis 52 and the coupling 10 which attach the piston 2-A to the piston 2-C, so that the piston 2-C compresses the air at the same time also by the side 51 in its cylinder 1-C and draw air by the side 50 of the same piston 2-C in the same cylinder 1-C.

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SUBSTITUTE SHEET (RULE 2B) And if the screw 3 moves to the right, it pulls the piston 2 in its cylinder 1 through the coupling 10 to the right to compress the air on the side 47 and suck air by the side 46 of the same piston 2 in the same cylinder 1, and this movement will be transmitted at the same time to the piston 2-B of Figure 18 through the intermediate coupling axis 52 and the coupling 10 which attach the piston 2 to the piston 2-B, so that the piston 2-B compresses the air by the side 53 in its cylinder 1-B and draws air by the side 54 of the same piston 2 in the same cylinder 1-B, at the same time the screw 3 pushes the piston 2-A in its cylinder 1- A through the coupling 10 to the right to compress the air on the side 48 and suck air by the side 49 of the same piston 2-A in the same cylinder 1- A, and this movement will be transmitted at the same time also to the piston 2-C of Figure 16 through the intermediate coupling axis 52 and the coupling 10 which attach the piston 2- A to the piston 2-C, so that the piston 2-C compresses the air by the side 50 in its cylinder 1-C and draws air from the side 51 of the same piston 2 in the same cylinder 1 -C.

Finally, the compressed air of the reservoir 39 will be sent to the power bells of the central E of the Canadian Patent No. 2328580 of Figure 3 through the line 40 and the rotary joint 18-E.

The result that we have just had of this invention is to be able to produce compressed air with economical compressors, simple and easy to build and operate, which consume much less energy than conventional compressors that we know at the present time, which helps the Canadian patent No. 2328580, especially in order to be able to produce electrical energy everywhere, to solve the energy problem that is now being tested.

It is clear that all the technical elements composing the various elements which have just been described, being borrowed from very well known techniques. It is useless to represent in detail everything that is not on the drawings.

Claims

CLAIMS:

The embodiments of the invention, for which an exclusive right of ownership or privilege is claimed, are defined as follows.

1-piston compressor with double action, comprising:

A chassis assey solid to withstand the stresses of very large forces, caused by the pressure of the compressed air against the worm screw acts via the pistons that are securely attached to said screw by compressing the air in the compressor cylinders,

one or more cylinders with pistons and intake and exhaust valves that are double acting, used to admit, compress and escape compressed air with a frequency of two cycles per period

a screw jack, to communicate through its screw to the compressor pistons the subject of the present invention, a linear reciprocating movement and a force that allows them to suck air into their respective cylinders on one side of the pistons at the same time compressing air on the other side of the same pistons in their respective cylinders, with the help of a relatively low torque moment capable of overcoming the great force created by the pressure of the piston. compressed air that exerts on the entire surface of all the pistons that compress air at the same time,

an electric, mechanical, hydraulic, pneumatic or even manual motor for actuating the screw of the jackscrew through a nut-gear which turns crazy in a bore machined in a frame forming part of the same frame of the same compressor mentioned above, giving said screw is reciprocated linearly to communicate with the piston cylinders of the compressor,

electrical, electronic, mechanical, hydraulic, pneumatic or other controls to control the direction of rotation of the screw jack motor, each time the pistons arrive at the end of

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LOSS OF REPLACEMENT (RULE 26) the exhaust of each cycle, to allow the screw of the screw jack to pull or to push again and at the same time the same pistons of all the cylinders of the same compressor, so that they start again every time a new cycle of compression,

an oil-filled housing necessary to lubricate the screw and gears of the screw jack,

a cooling system for the entire compressor including the inside of the cylinders through their respective pistons,

a heat exchanger used to recover the heat lost during the compression of the air,

a reservoir for storing compressed air produced by the compressor, and a pressure regulator for controlling the compressed air pressure of the plant of Canadian Patent No. 2328580, the compressor being characterized by the screw jack comprising :

a screw jack, to communicate through its screw to the compressor pistons the subject of the present invention, a linear reciprocating movement and a force that allows them to suck air into their respective cylinders on one side, compressing air at the same time, on the other side in their respective cylinders with the help of a relatively low torque moment able to overcome the great force that is created by the pressure of the compressed air that exerts on the entire surface of all pistons that compress air at the same time, at a rate of two cycles per period,

a nut-gear which turns idly by the aid of a pinion which is rotated by the screw jack motor, into a bore machined in a solid frame forming part of the same frame which supports said compressor, to move the screw of said jack to screw, giving it a linear reciprocating motion. The strength of this frame is essential so that the screw can overcome through all the pistons of all the cylinders, the great pressure that is exerted by the air during its compression, without it deforms:

a motor, electric, mechanical, hydraulic, pneumatic, or even manual, serving to actuate the screw of the screw jack, directly through its gear-nut and a pinion or a gearbox for controlling the speed of translation of said screw, which controls the flow of the same compressor,

a crankcase filled with oil for lubricating the screw and the gears of the screw jack,

electrical, electronic, mechanical, hydraulic, pneumatic or other controls to control the direction of rotation of the screw jack motor each time the pistons arrive at the end of the exhaust of each cycle, to allow the screw of the cylinder to screw to pull or push again and at the same time the same pistons of all the cylinders of the same compressor, so that they start each time a new compression cycle,

2- A compressor as claimed in claim 1 and characterized by: a relatively low moment torque that is applied to the screw of the jack which operates all the pistons of all the cylinders of the same compressor in one fell swoop, for that they compress the air in their respective cylinders, this moment of torque is able to overcome the great force that is created by the pressure of the compressed air which exerts on the whole surface of all the pistons which compress the at the same time and at a rate of two cycles per period,

3. Compressor as claimed in claim 1 and characterized by: the same diameter or different diameters for the cylinders of the same compressor, two or more cylinders,

all pistons of all cylinders of the same dual cylinder or multiple cylinder compressor, which must have the same length, which is equal to the distance between the beginning of the compression and the end of the exhaust of the compressed air of each cycle, and which is equal to its turns at the distance on which the screw of the screw jack moves alternately to perform each cycle from the beginning of the intake until the end of the escape of air compressed,

the use of many small cylinders instead of oversized cylinders for the production of large airflows, which is allowed by the compressor configuration the subject of the present invention, the arrangement of the cylinders of the same compressor which can be one after the other, in this case, the use of coupling pin and coupling between each two pistons of each two cylinders on each side of the screw screw jack that are placed one after the other, will be mandatory for the same screw of the same screw jack of the same compressor can operate at once. Or the arrangement of cylinders of the same compressor that can be next to each other, in this case the use of a frame and fasteners that connect the pistons to the frame will be necessary for the same screw of the same screw jack of the same compressor can operate all the pistons at once.

an indeterminate number of cylinders or rows of cylinders for use with the same compressor, within the limits of its power.

the installation of cylinders on one or both sides of the same screw jack, also to influence the flow rate of said compressor,

the operation of all the pistons of all the cylinders of the same compressor by the single screw of the same screw jack of the same compressor.

the parallel operation of all the cylinders of the same compressor, that means that the compression of the air is done at the same time in all the cylinders on one side of their respective pistons, at the same time as the admission of the air that is on the other side of the same pistons in the same cylinders respective.

A compressor as claimed in claim 1 and characterized by:

Electrical contactors or other means necessary to operate electrical circuit breakers or other means to stop and restart the screw jack motor, in either direction each time the pistons arrive at the end of a compression cycle, by creating a linear reciprocating movement to the screw of the screw jack, which is necessary to alternate the translation of the pistons which are integral therewith, in their respective cylinders in a way to favor at the same time, one side of the pistons the compression then the exhaust of the compressed air and on the other side of the same pistons the admission of the air in the same cylinders, a tab which is fixed on the screw of the screw jack to operate the above mentioned contactors by describing a distance exactly equal to the distance that the pistons of the same

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SUBSTITUTE TEXT (RULE 26) compressor describe at the same time inside their respective cylinders, from the beginning of the admission of air, until the end of the exhaust of the compressed air of the same cycle.

5. A compressor as claimed in claim 1 and characterized by: a cooling system of the interior of the compressor cylinders by means of their pistons, which helps to cool at the same time the air admitted into these cylinders, which helps to increase the flow of the same compressor.

The compressor as claimed in claims 1 and 2, characterized by:

Flexible hoses that communicate the cooling water of the main cooling system to the pistons during operation of the compressor to facilitate cooling of the interior of the cylinders of said compressor.

A compressor as claimed in claim 1 and characterized by:

The pistons on each side which are attached together, in a manner that the first piston adjacent to the screw on either side of the screw jack, receives the force and the reciprocating linear movement of said screw jack screw and the transmits directly and at the same time to the other pistons of the other cylinders on the same side via a coupling and an intermediate coupling shaft that is installed between each two adjacent pistons of each two adjacent cylinders also on the same side which promotes parallel operation for all cylinders and their pistons. So the distance that the screw crosses in one direction or another, which does not vary with the number of cylinders used with the same compressor, but the power required for the operation of said compressor will also be proportional to the force to overcome that exerts in same time on the surfaces of all the pistons of all the cylinders by the air which is compressed at the same time inside all the cylinders of the same compressor.

8. A compressor as claimed in claim 1 and 7 and characterized by: a coupling which serves to solidify the screw of the screw jack to the adjacent pistons, and to solidify the intermediate coupling axes to the adjacent pistons so that the screw of the same screw jack can operate at the same time all the pistons of all the corresponding cylinders, and hold the flexible hoses of the piston cooling system during the operation of the compressor to facilitate the cooling of the pistons themselves and inside their respective cylinders, which helps to increase the amount of air admitted into the cooled cylinders.

9- Compressor as claimed in claim 1 and characterized by: the use of a heat exchanger which serves to recover the heat lost during the compression of the air, by heating the water of the basin of the patent center No. 2328580, which helps to increase the power of the plant.

The compressor as claimed in claims 1 and 9, and characterized by: heating the water in the central pond of the Canadian Patent No. 2328580 by the heat recovered from the heat lost during the compression of the air in the cylinders of the compressor, to help increase the power of the plant by heating the compressed air that is in its motor bells, which helps move a greater amount of liquid, where the thrust on the power plant bells is equal to the weight of the displaced liquid.

The compressor as claimed in claim 1 and further characterized by: The use in groups, compressors of the compressor type which is the subject of the present invention, for sharing equally, and for delivering in a continuous manner the compressed air flow that is necessary for a reliable and continuous operation of the plant of the Canadian Patent No. 2,327,880, regardless of the speed of translation, or the distance between the beginning of compression and the end of the exhaust of the compressed air, which are the same for all the screws of all the screw jacks which are used with said compressors. These compressors are independent of each other, so to have a continuous flow of compressed air for the plant to operate permanently, it is necessary that the air flow rate (FAD) that is needed for said central , either shared and delivered by compressors that have the same flow rates per minute for each, and these compressors must escape their air in a successive and continuous way, that means that when the first compressor finishes to escape its compressed air , the second compressor must directly begin to escape followed by the third, then by the fourth etc ..., then by the first which will be at the point of starting a new exhaust cycle, and so on,

the total power required to continuously compress and leak the flow that is necessary for reliable and continuous operation of the plant, which is equal to the total of all the powers of all the compressors used to deliver a continuous and shared throughput for the plant to be efficient and operational.

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REPLACEMENT LEAF (RULE 26)