CA2473077C - Reciprocating double acting compressor - Google Patents

Reciprocating double acting compressor Download PDF

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Publication number
CA2473077C
CA2473077C CA 2473077 CA2473077A CA2473077C CA 2473077 C CA2473077 C CA 2473077C CA 2473077 CA2473077 CA 2473077 CA 2473077 A CA2473077 A CA 2473077A CA 2473077 C CA2473077 C CA 2473077C
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Canada
Prior art keywords
compressor
screw
pistons
double acting
cylinders
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Expired - Fee Related
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CA 2473077
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French (fr)
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CA2473077A1 (en
Inventor
Afif Abou-Raphael
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Individual
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Individual
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Priority to CA 2473077 priority Critical patent/CA2473077C/en
Priority to PCT/CA2004/001450 priority patent/WO2006010238A1/en
Publication of CA2473077A1 publication Critical patent/CA2473077A1/en
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Publication of CA2473077C publication Critical patent/CA2473077C/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B5/00—Machines or pumps with differential-surface pistons
    • F04B5/02—Machines or pumps with differential-surface pistons with double-acting pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/01—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being mechanical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • F04B39/064—Cooling by a cooling jacket in the pump casing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

The prior art includes compressors having a lot of turning elements and requiring a lot of maintenance, while the volume of their cylinders is limited, and their delivered flow is affected by the high temperature that heats up the air inside their cylinders before compression.

The present invention provides a design of a reciprocating double acting compressor, operated by a Screw of a screw jack that needs a fairly little torque to compress air, while communicating a linear and reciprocating movement to all pistons of the said compressor. This compressor is simple and efficient, it allows variable flows, according to the volume and the number of cylinders used with every compressor, that have no limit of number, length or diameter. In addition, the entire compressor is water-cooled, including the pistons and the interior of their respective cylinders, in order to admit cold free air, that increases the demanded flow.

Description

Reciprocating double acting compressor.

This invention relates to the construction of a reciprocating double acting compressor, using the force, the linear and reciprocating movement of the screw of a simple machine-like screw jack.

The prior art includes compressors having a lot of turning elements and requiring a lot of maintenance. In these compressors, powerful motors are needed in order to develop the necessary torque for the compression of air. In addition, the air flow is already limited by the volume in cubic feet that they displace per minute, and the high temperature that exists inside their cylinders and heats up the admitted air before compression, increasing its volume and reducing its quantity.

The subject of this invention is a reciprocating double acting compressor that is operated by a screw of a screw jack that needs a fairly little torque to compress air, and communicates a linear and reciprocating movement to all pistons of the said reciprocating double acting compressor. This compressor is simple and efficient; it allows variable flows according to the volume and the number of cylinders used that have no limit of number, length or diameter. In addition, the entire compressor is water-cooled including the pistons and the interior of their respective cylinders, in order to admit cold free air that increases the flow of compressed air.

The embodiment of this invention includes the following:
1- A frame, that supports large forces caused by the pressure of compressed air that counteract on the screw of the screw jack, through the pistons that are attached to it, during the compression of the air in the cylinders of the said reciprocating double acting compressor.
2- A screw jack, used to overcome large resistant forces as the one developed by the pressure of the compressed air on the total surface of all the pistons of the same compressor, that are compressing air at the same time during the same cycle. This screw jack transmits the force and the linear and reciprocating movement of its screw to all the pistons of the said reciprocating double acting compressor the subject of the present invention, while pushing-in or pulling-back, or pushing-in and pulling-back at the same time the said pistons. Air is admitted and compressed inside the respective cylinders of the said pistons, two times by period according to the configuration of the said compressor.

The screw jack includes:

A- A screw that is driven by a free turning gear-nut located in a boring machined in a brace affixed to the main frame described above which is capable, of sustaining big stress caused by the force of the pressure of the compressed air. This force is the result of the pressure that exerts on the surface of all the pistons of the said compressor during the compression and the exhaust of the compressed air. A little torque is needed to push-in or to pull-back the said pistons inside their respective cylinders, in order to overcome the said force through the screw of the screw jack. The said screw is set to move in a straight line, either to the right or to the left according to the direction of the rotation of the motor of the said screw jack.

B- A pinion used to operate the above mentioned free-turning gear-nut that can be combined to a gearbox, in order to provide a controlled linear and reciprocating movement to the screw of the said screw jack, in order to control the frequency of the cycles of the compressor C- A mechanical, electrical, hydraulic, or pneumatic motor to provide the needed torque, and motion to the said screw of the screw jack. In the example of the present application the chosen motor is electrical.

D- A casing full of oil to lubricate the screw and all of the gears of the screw jack.

E- Electrical contactors needed to operate circuit breakers that are used to control the rotation of the motor of the said screw jack at the end of every cycle. The rotation of the motor can be clockwise or counter clockwise. The linear and reciprocating movement applied to the pistons in their respective cylinders through the screw of the screw jack, enhances admission of free air in every cylinder on one side of the pistons.
In addition, at the same time compression is enhanced of the air present in the same cylinders by the other side of the same respective pistons.

F- A tongue that is affixed to the screw of the screw jack, and used to stop and restart the motor of the said screw jack at the end of the exhaust stroke of the compressed air of every cycle. This tongue, controls the motor through the above described electrical contactors. In addition these contactors are distant one from the other, exactly the same distance of the run that any one of the pistons travels inside its respective cylinder, from the beginning of the compression stroke to the end of the exhaust stroke of the same cycle.
3- Cylinders, in which double acting pistons are moved alternatively by said screw of said screw jack, in order to suck-in air then to compress it, and finally to exhaust it compressed at a predetermined discharge pressure, toward an air tank two times in every period.
4-Inlet and outlet valves placed on both ends of each cylinder of the said double acting compressor.
This compressor can be built with one cylinder, but the linear and reciprocating movement of its screw of the screw jack, allows us to install cylinders on one or on both ends of the said screw according to the configurations of every compressor. The number of cylinders is calculated according to the flow of compressed air needed. In addition all of the pistons have the same length, which is exactly equal to the same distance of the run that the said screw of the screw jack, travels from the beginning of the compression stroke to the end of the exhaust stroke of the same cycle.
Same or different diameters the cylinders of the same compressor can have, while all of these cylinders are set to operate all the time in a parallel way.

The pistons of the compressor are joined together and moved like only one piston by the linear and reciprocating movement that the screw of the screw jack transmit to them without the need of any crank or crank handle, through:

A- Couplings and intermediary coupling shafts that are installed between every two pistons of every two cylinders that are placed one after the other.

B- Brace attached to all pistons of all cylinders that are placed side by side on every end of the screw of the screw jack through connections. This brace is attached to the said pistons in a way to have the screw pushing-in or pulling-back all the pistons directly without the need of any coupling shafts of the sort described above.
Said compressor is water cooled in order to recuperate the heat that is produced during the air compression, through a heat exchanger. In addition, the pistons can equally have a cooling system connected to the main cooling system, in order to be able to cool at the same time the pistons and the interior of their respective cylinders. The cooling of the interior of the cylinders permits the admission of a bigger quantity of cold free air in order to provide a bigger flow of compressed air.
Cooling water is delivered to said pistons through flexible hoses that are attached from one side to the main lines of the main cooling system, and from the other side, to the screw of the screw jack that transits the water to the pistons. This is feasible because of the configuration of the compressor, the subject of the present invention, and the linear and reciprocating movement that the screw of the screw jack communicates to the pistons.

The torque needed to operate the screw of the screw jack, in order to overcome the force created by the pressure that exerts by the compressed air on the surface of all the pistons that are compressing air at the same time, is relatively very small. To calculate the torque needed for the screw jack while pushing-in or pulling-back the pistons of the compressor, the following formula is applied:
(The total force to overcome expressed in Newton x the pitch of the screw of the screw jack expressed in meters) / (2 x pi 3.1416).

The force that exerts on the pistons between the beginning of the compression stroke and the beginning of the exhaust stroke is:
Average registered pressure at the beginning of the exhaust stroke of the compressed air expressed in Newton per centimetre square N/cm2 (= discharge pressure / 2)) x the surface of all pistons that are compressing air at the same time expressed in centimetre square cm2.

The force that exerts on the pistons between the beginning and the end of the exhaust stroke is:
Constant registered pressure at the beginning of the exhaust stroke expressed in Newton N
centimetre square cm2 x the surface of the same pistons expressed in centimetre square cm2.
During compression the volume of the compressed air decreases for about the half, when the value of the pressure under which the initial volume is taken, will be doubled and added 1.
As examples:
Under 1 bar of pressure the volume, of free air becomes 1/2, and the pressure is: [(0 x2) +1 = 1 bar].
Under 3 bars of pressure the volume of free air becomes (1/2 divided by 2 =
1/4), and the pressure is: [(1 x 2) + 1= 3 bars].
And Under 7 bars of pressure the volume of free air becomes (1/4 divided by 2 = 1/8), and the pressure is: [(3 x 2) + 1= 7 bars].

These observations help to configure the conception of the reciprocating double acting compressor the subject of the present invention. According to the following:

The volume of the imprisoned air inside the cylinder becomes half of the initial admitted volume of the free air (FAD), when the piston of the compressor is pushed-in or pulled-buck half of its run, during the beginning of the compression. In addition the pressure increases from 0 bar g to 1 bar g, If the piston advances again, half of the remaining distance of its run, or 3/4 of its total run (L), the volume of the compressed air becomes 1/4 of the initial volume of the free air admitted initially into the cylinder. In addition the pressure increases from 1 bar g to 3 bars g.

And if the piston continues to advance until half of the half of the remaining distance of its run or 7/8 of its total run (L), the volume of the compressed air becomes 1/8 of the initial volume of free air admitted into the cylinder. In addition the pressure increases from 3 bars g to 7 bars g.

Hence a dead gap exists between the beginning of the compression stroke and the beginning of the exhaust stroke of the same cycle, where the compressor does not deliver compressed air. Then, In order to have a steady and continuous flow of compressed air, the dead gap that is equal to: 1/2 of the total run of the piston for a discharge pressure of 1 bar, 3/4 of the total run of the piston for a discharge pressure of 3 bars, and 7/8 of the total run of the piston for a discharge pressure of 7 bars, has to be eliminated, by adding more compressors to share equally the total flow, while the timing of the cycles of all compressors are synchronized in order to have a steady and continuous flow of compressed air, according to the following:

For a discharge pressure of 1 bar, the gap is 1/2 then we need 2 compressors For a discharge pressure of 3 bars, the gap is 3/4 then we need 4 compressors.

For a discharge pressure of 7 bar, the gap is 7/8 then we need 8 compressors.

As an example, for 7 bars of discharge pressure, the full flow needed has to be divided between 8 compressors in order to deliver a continuous flow without interruption. The 8 compressors are put to work according to the following:
When the first compressor finishes to exhaust its compressed air toward the air tank, the second compressor must start directly its own exhaust stroke, by sending its compressed air to the same air tank. Then the second compressor is followed by the third compressor, then by the forth compressor, then by the fifth compressor, then by the sixth compressor, then by the seventh compressor, then by the eighth compressor, then by the first compressor that is now ready to start another exhaust stroke.
And so on to perpetuate the compression as long as the pistons are pushed-in and pulled back while admitting and compressing air.

The total power needed to admit, compress and exhaust the total flow of air, is equal to the sum of all the individual power of all the compressors used to deliver the said flow permanently, continually and without any interruption.

Hence, the result is that the use of this reciprocating double acting compressor the subject of the present invention is practical and operational with no limit of flow, speed of translation of the screw of the screw jack or the discharge pressure of the compressed air needed.

The compression of the air in this reciprocating double acting compressor the subject of the present invention is done accordingly to the following:

With a compressor having one cylinder:
1- Before running the compressor, all of its components have to be in place:

2- Let's consider that free exists already inside the cylinder of the compressor, and the piston is in the beginning of its run of this cycle which is equal to the depth of its respective cylinder.

3- The tongue that is affixed to the screw of the screw jack of the said compressor, sets on a first electrical contactor, in order to set on a first circuit breaker. Then the electric motor starts turning in the right direction needed to push-in the said piston in its respective cylinder through the screw of the screw jack that is affixed to it.

4- The gear-nut starts turning freely in its bore of the brace that is a part of the main frame, when it is operated by the above mentioned motor, through the pinion that can be combined to a gear box. A
linear and reciprocating movement is then transmitted to the pistons through the screw of the screw jack, while the said screw of the said screw jack is transmitting the needed force to the pistons of the said compressor, in order to compress and exhaust the compressed air toward an air tank.
5- As the compressor is reciprocal and double acting, it means that, while compressing air in the cylinder by one side of the piston, free air will be sucked-in by the other side of the same piston in the same cylinder.
6- When the piston arrives at the end of its run, at this moment all the compressed air of that cycle is compressed and expelled to the air tank, while it has sucked-in, all the needed free air to fill up the same cylinder, but by its other side.
7- The motor is set off at the end of the first cycle, through the above-mentioned tongue that operates a second electrical contactor. Then through a second circuit breaker, the said motor is restarted to turn in the other direction needed to pullback the same piston in the same cylinder, through the same screw of the same screw jack.
8- The same way, the gear-nut starts turning freely in the other direction, while pulling the same piston in the other direction that starts another cycle. The imprisoned air is then compressed in the same cylinder by the other side of the same piston, and fresh free air is admitted in the same cylinder by the other side of the same piston that was compressing during the previous cycle.
9- At the end of its new run, which is the same run traveled in the other direction for the previous cycle the piston finishes to exhaust the new batch of compressed air. At the same time fresh free-air is sucked-in by the other side of the said piston in order to fill up the same cylinder in order to start another new cycle of compression.
10- Again, at the end of the run of the piston, the said tongue sets on the first circuit breaker, through the first contactor, in order to stop the motor before restarting it to turn in the other direction. A new cycle of compression and admission on one side and on the other of the same piston is then in the work.
11- The screw and the gears of the screw jack are kept lubricated by the oil, which is in the casing of the said screw jack.
12- During the compression of the air, 80 to 93% of the needed energy is lost in heat. In order to irecuperate a good part of this lost energy, a full water-cooling system is used to cool the entire compressor, and a heat exchanger is installed in order to recuperate a good portion of the lost energy.

The pistons and their respective cylinders are cooled through drillings machined in the pistons that are supplied by cooling water, through flexible hoses used to connect the inlet and the outlet of the cooling water to the main cooling system. This cooling system is possible because of the simple configuration and the simple functioning of the present compressor the subject of the present invention.

The following formula is used to calculate the expended volume affected by the temperature.
V1.T1 = V2.T2 Where V 1 is the volume at the temperature T 1 T 1 is the temperature of the air before heating it, in degrees Kelvin.
V2 is the volume at the temperature T2 T2 is the temperature of the air after heating it, in degrees Kelvin.
The other aspects of this invention:

A- A compressor with two cylinders installed one cylinder on each end of the screw of the screw jack; where the said screw operates the two pistons as follow:

1- The cylinders of the compressor with two cylinders, can have the same or different diameters, but they must have the same length, because that all of their pistons travel one distance at the same time between the beginning of compression stroke and the end of the exhaust stroke of the same cycle, which is equal to the total run (L) of the screw of the screw jack that pushes-in and pulls-back all of the pistons at the same time in their respective cylinders, according to the cycle that can be in one direction or in the other, because of the linear and a reciprocating movement of the said screw of the said screw jack.
The functioning of these two cylinders is done in a parallel way, that means; when there is admission in one cylinder on one side of its piston, it will be compression in the same cylinder but by the other side of the same piston, exactly the same thing will happen in parallel and at the same time in the other cylinder of the same compressor, and the operation will be for both of them;
admission with admission, and compression with compression.

2- The pistons of the same compressor are attached one on each end of the screw of the screw jack that transmits its force and its motion with its direction to both pistons at the same time while operating them in parallel as described above. Hence, the distance that the screw travels in one direction or in the other, does not change for one or for two pistons, but the power needed for its operation is proportional, to the force to overcome and which is exerting at the same time on the total surface of both pistons, by the pressure of the compressed air inside the two respective cylinders of the compressor.

B- A multi-cylinder compressor that has a number of cylinders installed on one or two sides of the same screw jack, where the said screw operates all of the pistons as follow:

1- The screw of the screw jack will be made like the one of a compressor with one cylinder, if the cylinders with their pistons are installed on one side of the screw of the screw jack. Or like the one of a compressor with two cylinders, if the cylinders with their pistons are installed on both sides of the said screw of the said screw jack.

2- The pistons on each side of the compressor are attached together in a way that, the first pistons adjacent to the said screw receive directly the force and the movement of the said screw. The force and the movement of the screw is then transmitted to the other pistons of the other cylinders, through intermediary coupling shafts and couplings that have to be installed between every two adjacent pistons on each side. This configuration favors a parallel functioning for all of the said cylinders and their pistons as described above for the functioning of a compressor with two cylinders. Hence, the distance traveled by the screw in one direction or in the other, does not change like for one or for two cylinders. The power needed for the operation of the compressor is proportional too to the force to overcome that is exerting at the same time on the total surface of all the pistons, by the pressure of the compressed air inside the cylinders of the same compressor.

3- The pistons and the cylinders of the same multi-cylinder compressor must have the same length for all of the pistons, but the cylinders can have the same or different diameters, the same way as for the cylinders and the pistons of a compressor with two cylinders. However the use of intermediary coupling shafts and couplings between every two adjacent pistons of each side is mandatory, to permit to the same screw of the same screw jack to operate them together at once like if they are only one piston.

4- The use of an undetermined number of cylinders, in order to increase the flow of the compressor. The cylinders can be installed on one or two ends of the said screw that operates the pistons in their respective cylinders.

To those skilled in the art to which the invention relates, may changes in construction and widely differing embodiments and applications of the invention will suggest themselves without departing from the scope of the invention as defined in the appended claims. The disclosures and the descriptions herein are purely illustrative and are not intended to be in any sense limiting.

For a better understanding of this invention and to facilitate its examination, it is represented in the following 37 Figures.

Brief description of the drawings:

Figure 1 a front cross-sectional view along line A-A of figure 2 of a compressor with one cylinder.
Figure 2 a top schematic representation of a compressor with two cylinders joined to the air tank of the power plant of the Canadian patent no 2328580, and to the heat exchanger.

Figure 3 a side schematic view of a power plant of a PRIOR ART of the Canadian patent no 2328580.

Figures 4, 5, 6, 7 and 8 front views along line A-A of figure 2 of a compressor with one cylinder during all the steps of air admission on the right and compression to the left.

Figures 9, 10, 11, 12 and 13 front views along line A-A of figure 2 of a compressor with one cylinder during all the steps of air admission on the left and compression to the right.

Figures 14 and 15, if they are placed from left to right in the order of 15-14, they represent front cross sectional view along line A-A of figure 2 of a compressor with two cylinders placed on both ends of the screw of the screw jack.

Figures 16, 17 and 18, if they are placed from left to right in the order of 18-17-16, they represent front cross sectional view along line A-A of figure 2 of a compressor having multiple cylinders.
Figure 19 a top schematic representation of a compressor having six cylinders placed side by side by groups of three, on each end of the screw of the screw jack.

Figure 20 a top schematic representation of a compressor having 27 cylinders placed on one side of the screw of the screw jack.

Figure 21 a right view of figure 20.
Figure 22 a left view of figure 20.

Figure 23 a top schematic representation of a compressor having multiple cylinders placed on each end of the same screw of the same screw jack.

Figure 24 a front cross-sectional view of a screw of a screw jack and a simple piston of a compressor with one cylinder made in one piece.

Figure 25 a front cross-sectional view of a screw of a screw jack that operates at the same time, two pistons of a compressor with two cylinders attached on both ends of the said screw.

Figure 26 a front cross-sectional view of a screw of a screw jack operating at the same time pistons that are attached on both ends of the said screw of a multi-cylinder compressor.

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

Figures 28, 29, 30, 31, 32, 33, 34, 35, 36 and 37 schematic representations of eight compressors used to deliver a continuous and reliable flow.

When considered with the description herein, the characteristics of the invention are apparent from the accompanying drawings, which exemplify an embodiment of the invention for purposes of illustration only, and in which -Figure 1 is a front cross-sectional view along line A-A of figure 2 of a compressor having one cylinder including the cylinder 1, the piston 2, and the screw 3 of the screw jack 3-A. The free turning gear-nut 4 sitting in the bore 6-A of the brace 6 of the frame 21, which is used to operate and alternate the movement of the screw 3 of the screw jack 3-A. The motor 11 used to operate the gear-nut 4 through the shaft 26 and the pinion 5. The tongue 7 which is used to operate the electrical contactor 8 at the end of every cycle to the left, and the electrical contactor 9 at the end of the second cycle of every period to the right, in order to set on and off the circuit breaker 9-A-8-A, in a way to turn on and off the motor 11, in one direction or in the other to give a linear and a reciprocating movement to the screw 3 of the screw jack 3-A. The inlet valve 15 of the admission of air in the cylinder 1 on the left side 46 of the piston 2, the outlet valve 12 of the exhaust of compressed air toward the air tank 39 of the power plant E of figure 3 through the line 22, the inlet valve 14 of the admission of air in the same cylinder 1 on the right side 47 of the same piston 2, the outlet valve 13 of the exhaust of compressed air toward the air tank 39 of the same power plant E of figure 3 through the line 23, the cooling water 16 of cylinder 1, the principal conduits 33 and 34 of the principal cooling system, the water inlet 18 and the water outlet 17 used to transit the water to and out of the piston 2, the flexible hoses 35 and 36 used to join the cooling system of the piston 2 to the main cooling system during the functioning of the compressor in order to cool off the inside of the cylinder 1 through the passage 16-A of the piston 2. The casing 19 that holds the oi120 in order to lubricate the screw 3 and all of the gears of the screw jack 3-A. The coupling 10 which is used to attached the screw 3 of the screw jack 3-A to the adjacent piston of the same compressor, to connect the flexible hoses 35 and 36 in order to facilitate the cooling off of the piston 2 and the inside of its respective cylinder 1 as described above during the functioning of the compressor, and to hold in place the tongue 7 to allow it to move with the screw 3 of the screw jack 3-A
to the right or to the left depending on the situation, the same distance that the piston 2 travels between the beginning of compression stroke and the end of the exhaust stroke of every cycle of the compressor.

Figure 2 is a top schematic representation of a compressor with two cylinders joined to the air tank 39 of the power plant E of the Canadian patent no 2328580 and to the heat exchanger 43 that is used to recuperate the lost heat during the compression of the air, including the screw jack 3-A that operates piston 2 in cylinder 1, and piston 2-A in cylinder 2-A. The air inlets 24 and 25 of cylinder 1, and the air inlets 24-A and 25-A of cylinder 1-A, the conduits 22 and 23 that transits the compressed air coming from cylinder 1, to the air tank 39 through the conduit 37, the conduits 22-A
and 23-A that transit the compressed air coming from cylinder 1-A, to the air tank 39 through the conduit 38. The pressure gauge 41 of the compressed air that shows the pressure inside the air tank, the conduit 40 that transit the compressed air from the air tank 39 to the power plant E of figure 3.
The main lines 33 and 34 of the main cooling system of the said compressor, the water inlet 18 and the water outlet 17 used to circulate the water through cylinder 1, cylinder 1-A, piston 2 and piston 2-A. The heat exchanger 43 that is used to transfer the heat from the water of the cooling system of the compressor to the water of the pool 1-E of the power plant E of figure 3, by circulating the said water of the pool 1-E through the said heat exchanger 43 by the lines 44 and 3- Figure 3 is a side schematic view of a power plant of the PRIOR ART of the Canadian patent no 2328580 including the line 40 that feeds the power plant E with compressed air coming from the air tank 39 of figure 2, through the pressure gauge 41 and the rotary transfer joint 18-A. The lines 44 and 45 that are used to circulate the water of the pool 1-E of the power plant E through the heat exchanger 43 of figure 2 in order to recuperate the heat that is produced during the compression of air. The hot water of the pool serve to heat up the air of the ascending containers of the power plant E in order to expend its volume, at the same time the buoyant force applied on the said ascending containers will increase substantially, creating an increase in the power of the said power plant 3, because, that the buoyant force is equal to the weight of the displaced water.

Figure 4 is a front cross-sectional view along line A-A of figure 2 of a compressor with one cylinder, showing the piston 2 in the beginning of the cycle of compression to the left by its side 46 when it is pushed-in by the screw 3 of the screw jack 3-A in its respective cylinder 1, including in addition the outlet valves 12 of the left side 46 of piston 2 that is closed, the outlet valve 13 of the right side 47 of piston 2 that is closed, the inlet valve 15 of the left side 46 of piston 2 that is closed, the inlet valves 14 that starts to open to permit the admission of free air in the same cylinder 1 by side 47 of the same piston 2 that is posted to start going in cylinder 1 in order to start compressing by its side 46 and admitting by its side 47. Figure 4 includes too, the tongue 7 that auctioned already the contactor 8 in order to set on the circuit breaker 9-A-8-A of the motor 11 to turn it in the right direction in order to push-in to the left the piston 2 in its cylinder 1 through the screw 3 of the screw jack 3-A.

Figure 5 is a front cross-sectional view along line A-A of figure 2 of a compressor with one cylinder, showing piston 2 in the middle of its run to the left, and the volume of the compressed air that became half of the initial volume that was admitted as free air in cylinder 1, the pressure of this air at this moment is 1 bar g according to the calculations in example 2 of this disclosure. Figure 5 includes in addition the outlet valves 12 of the left side 46 of piston 2 that is closed, the outlet valve 13 of the right side 47 of piston 2 that is closed, the inlet valve 15 of the left side 46 of piston 2 that is closed, the inlet valves 14 that is open to permit the admission of free air in the same cylinder I by side 47 of the same piston 2, and the tongue 7 that is in the middle of its run between the electrical contactors 8 and 9.

Figure 6 is a front cross-sectional view along line A-A of figure 2 of a compressor with one cylinder, showing piston 2 at 3/4 of the beginning of its run to the left or at 1/4 of the end the present cycle, and the volume of the compressed air that became 1/4 of the initial volume that was admitted as free air in cylinder 1, the pressure of this air at this moment is 3 bars g according to the calculations in example 2 of this disclosure. Figure 6 includes in addition the outlet valves 12 of the left side 46 of piston 2 that is closed, the outlet valve 13 of the right side 47 of piston 2 that is closed, the inlet valve 15 of the left side 46 of piston 2 that is closed, the inlet valves 14 that is open to permit the admission of free air in the same cylinder 1 by side 47 of the same piston 2, and the tongue 7 that is at 3/4 Of the beginning of its run to the left between the electrical contactors 8 and 9, or at 1/4 of the end of the same run of the same cycle.

Figure 7 is a front cross-sectional view along line A-A of figure 2 of a compressor with one cylinder, showing piston 2 at 7/8 of the beginning of its run to the left or at 1/8 of the end of the present cycle, and the volume of the compressed air that became 1/8 of the initial volume that was admitted as free air in cylinder 1, the pressure of this air at this moment is 7 bars g according to the calculations in example 2 of this disclosure. Figure 7 includes in addition the outlet valves 12 of the left side 46 of piston 2 that has just opened to permit the exhaust of the compressed air out of cylinder 1 toward the air tank 39 of figure 2 through lines 22 and 37, the outlet valve 13 of the right side 47 of piston 2 that is closed, the inlet valve 15 of the left side 46 of piston 2 that is closed, the inlet valves 14 that is open to permit the admission of free air in the same cylinder 1 by side 47 of the same piston 2, and the tongue 7 that is at 7/8 Of the beginning of its run to the left between the electrical contactors 8 and 9, or at 1/8 of the end of the same run of the same cycle.

Figure 8 is a front cross-sectional view along line A-A of figure 2 of a compressor with one cylinder, showing piston 2 at the end of its run to the left where it had already expelled all of the compressed air at the constant pressure of 7 bars g toward the air tank 39 of figure 2 through line 22.
Figure 6 includes in addition the outlet valves 12 of the left side 46 of piston 2 that is still open permitting the end of the exhaust of the compressed air toward the air tank 39 of figure 2, the outlet valve 13 of the right side 47 of piston 2 that is closed, the inlet valve 15 of the left side 46 of piston 2 that is closed, the inlet valves 14 that is still open to finalize the admission of free air in the same cylinder 1 by side 47 of the same piston 2, and the tongue 7 that had finished its run to the left for the present cycle by shutting off the motor 11 through the electrical contactor 9. Now the compressor is ready to start a new cycle to the right.

Figure 9 is a front cross-sectional view along line A-A of figure 2 of a compressor with one cylinder, showing the piston 2 in the beginning of the a new cycle of compression to the right by its side 47 when it is pulled-back by the same screw 3 of the same screw jack 3-A
in the same cylinder 1, including in addition the outlet valves 12 of the left side 46 of piston 2 that is closed, the outlet valve 13 of the right side 47 of piston 2 that is closed, the inlet valves 14 of the left side 46 of piston 2 that is closed, the inlet valves 15 that starts to open to permit the admission of free air in the same cylinder 1 by side 46 of the same piston 2 that is posted to start going to the right in cylinder 1 in order to start compressing by its side 47 and admitting by its side 46. Figure 9 includes in addition, the tongue 7 that already operated the electrical contactor 9 in order to set on the circuit breaker 9-A-8-A that starts the motor 11 to turn in the appropriate direction in order to pull-back to the right the same piston 2 in the same cylinder 1 through the same screw 3 of the same screw jack 3-A.

Figure 10 is a front cross-sectional view along line A-A of figure 2 of a compressor with one cylinder, showing piston 2 in the middle of its run to the right, and the volume of the compressed air that became half of the initial volume that was admitted as free air in cylinder 1, the pressure of this air at this moment is 1 bar g according to the calculations in example 2 of this disclosure. Figure 10 includes in addition the outlet valves 12 of the left side 46 of piston 2 that is closed, the outlet valve 13 of the right side 47 of piston 2 that is closed, the inlet valves 14 of the left side 46 of piston 2 that is closed, the inlet valve 15 of the left side 46 of piston 2 that is open to permit the admission of free air in the same cylinder 1 by side 46 of the same piston 2, and the tongue 7 that is in the middle of its run to the right between the electrical contactors 8 and 9.

Figures 11 is a front cross-sectional view along line A-A of figure 2 of a compressor with one cylinder, showing piston 2 at 3/4 of the beginning of its run to the right or at 1/4 of the end the present cycle to the right, and the volume of the compressed air that became 1/4 of the initial volume that was admitted as free air in cylinder 1, the pressure of this air at this moment is 3 bars g according to the calculations in example 2 of this disclosure. Figure 11 includes in addition the outlet valves 12 of the left side 46 of piston 2 that is closed, the outlet valve 13 of the right side 47 of piston 2 that is closed, the inlet valves 14 of the left side 46 of piston 2 that is closed, the inlet valve 15 of the left side 46 of piston 2 that is open to permit the admission of free air in the same cylinder 1 by side 47 of the same piston 2, and the tongue 7 that is at 3/4 Of the beginning of its run to the right between the electrical contactors 8 and 9, or at 1/4 of the end of the same run of the same cycle.

Figure 12 is a front cross-sectional view along line A-A of figure 2 of a compressor with one cylinder, showing piston 2 at 7/8 of the beginning of its run to the right or at 1/8 of the end of the present cycle, and the volume of the compressed air that became 1/8 of the initial volume that was admitted as free air in cylinder 1, the pressure of this air at this moment is 7 bars g according to the calculations in example 2 of this disclosure. Figure 12 includes in addition the outlet valves 12 of the left side 46 of piston 2 that is closed, the outlet valves 13 of the right side 47 of piston 2 that has just opened to permit the exhaust of the compressed air out of cylinder 1 toward the air tank 39 of figure 2 through lines 23 and 37, the inlet valves 14 of the right side 46 of piston 2 that is closed, the inlet valve 15 of the left side 46 of piston 2 that is open to permit the admission of free air in the same cylinder 1 by side 47 of the same piston 2, and the tongue 7 that is at 7/8 Of the beginning of its run to the right between the electrical contactors 8 and 9, or at 1/8 of the end of the same run of the same cycle.

Figure 13 is a front cross-sectional view along line A-A of figure 2 of a compressor with one cylinder, showing piston 2 at the end of its run to the right where it had already expelled all of the compressed air at the constant pressure of 7 bars g toward the air tank 39 of figure 2 through the lines 23 and 37. Figure 13 includes in addition the outlet valves 12 of the left side 46 of piston 2 that is closed, the outlet valve 13 of the right side 47 of piston 2 that is still open permitting the end of the exhaust of the compressed air toward the air tank 39 of figure 2, the inlet valves 14 of the right side 46 of piston 2 that is closed, the inlet valve 15 of the left side 46 of piston 2 that is still open to finalize the admission of free air in the same cylinder 1 by side 47 of the same piston 2, and the tongue 7 that had finished its run to the right for the present cycle by shutting off the motor 11 through the electrical contactor 9. Now the compressor is ready to restart a new cycle to the left, and the compression of air continuous as long as the power plant 3 is running and the power is connected to the motor 11, as explained above in the calculations of the power of the compressor that shows a substantial positive difference between the production of energy in the said power plant 3 of the Canadian patent no 2328580 and the consumption of the compressors that supply the same power plant.

Figures 14 and 15 are front cross-sectional views along line A-A of figure 2 of a compressor with two cylinders, if they are placed from left to right in the order of 15-14, they represent a full front cross sectional view along line A-A of a compressor with two cylinders placed on both ends of the same screw of the same screw jack, they include in addition the screw 3 of the screw jack 3-A, attached to piston 2 to the left and to piston 2-A to the right through the couplings 10, the free turning gear-nut 4, the pinion 5, the tongue 7, the electrical contactors 8 and 9, and the motor 11. To the left piston 2 is in cylinder 1 which includes, the inlet valves 12 and 13 and the outlet valves 14 and 15. To the right piston 2-A is in cylinder 1-A which includes, the inlet valves 12-A and 13-A
and the outlet valves 14-A and 15-A, the piston 2-A of cylinder 1-A is attached to the right end of the screw 3 through the coupling 10 in order to run in parallel with piston 2 of cylinder 1, it means when there is compression on the left side 46 of piston 2 in cylinder 1, there is compression on the left side 49 of piston 2-A in cylinder 1-A, but the admission of free air will be in cylinder 1 by the right side 47 of piston 2 and in cylinder 1-A by the right side 48 of piston 2-A. Figure 14 includes the water inlet 18 and the water outlet 17, the flexible hoses 35 and 36 that are used to connect the water of the compressor's cooling system to the pistons 2 and 2-A in order to cool off the said pistons and the inside of their respective cylinder 1 and 1-A, during the operation of the compressor.
Figures 16 to 18 are front cross-sectional views along line A-A of figure 2 of a compressor with 4 cylinders. If we place figure 17 in the middle, figure 18 to the left and figure 16 to the right, we see a compressor composed of 4 cylinders, but this kind of multi-cylinder compressors can be made with a bigger number of cylinders depending on the needed flow of compressed air.
This multi-cylinder compressor is a reciprocating double acting one too, and all of its cylinders work in parallel exactly like the ones with two cylinders, but the power needed for its operation in order to permit to the screw 3 of the screw jack 3-A to push-in or pull-back all of the pistons in their respective cylinders, is proportional to the force to overcome and which is exerting at the same time on the total surface of all the said pistons of all the cylinders of the same compressor, this force is equal to the pressure of the compressed air in Newton per square centimeter time the total surface of all of the pistons that are compressing air at the same time Figures 16 to 18 include when placed in the order of 18-17-16, the screw 3 of the screw jack 3-A, which is attached to the left, to piston 2 of cylinder 1, and to the right, to piston 2-A of cylinder 1-A, through couplings 10, the free turning gear-nut 4, the pinion 5, the tongue 7, the electrical contactors 8 and 9, the motor 11. The inlet valves 14 and 15, the outlet valves 12 and 13 of cylinder 1. The inlet valves 14-A and 15-A, and the outlet valves 12-A and 13-A of cylinder 1-A. To the left of cylinder 1 there is cylinder 1-B with; its inlet valves 14-B and 15-B, its outlet valves 12-B and 13-B, and its piston 2-B which is attached to piston 2 of cylinder 1 by an intermediary coupling shaft 52 and a coupling 10 that are used to transmit the force, the linear and alternative motion of the screw 3 of the screw jack 3-A of the same compressor to piston 2-B through piston 2 of cylinder 1. To the right of cylinder 1-A there is cylinder 1-C with; its inlet valves 14-C and 15-C, its outlet valves 12-C and 13-C, and its piston 2-C which is attached to piston 2-A of cylinder 1-A the same way by an intermediary coupling shaft 52 and a coupling 10 that are used equally to transmit the same force and the same linear and alternative movement of the screw 3 of the screw jack 3-A to piston 2-C
through piston 2-A of cylinder 1-A. All of the cylinders of this multi-cylinder compressor work together and in a parallel way with the same screw 3 of the same screw jack 3-A, according to the same method explained above for the compressor with two cylinders, it means, when there is translation to the left, compression will occur by side 46 of piston 2 in cylinder 1, by side 49 of piston 2-A in cylinder 1-A, by side 54 of piston 2-B in cylinder 1-B, and by side 51 of piston 2-C in cylinder 1-C. And inlet in this same cycle to the left will occur by side 47 of piston 2 in cylinder 1, by side 53 of piston 2-B in cylinder 1-B, by side 48 of piston 2-A in cylinder 1-A, and by side 50 of piston 2-C in cylinder 1-C. But when there is translation to the right, the compression will occur by side 47 of piston 2 in cylinder 1, by side 48 of piston 2-A in cylinder 1-A, by side 53 of piston 2-B
in cylinder 1-B, and by side 50 of piston 2-C in cylinder 1-C. And inlet in this same cycle to the right will occur by side 46 of piston 2 in cylinder 1, by side 54 of piston 2-B in cylinder 1-B, by side 49 of piston 2-A in cylinder 1-A, and by side 51 of piston 2-C in cylinder 1-C. This configuration will be followed in all multi-cylinder compressors, either the cylinders are on one or two ends of the screw 3 of the screw jack 3-A of the same compressor.

Figure 19 is a top schematic representation of a compressor having six cylinders placed side by side by groups of three on each end of the same screw 3 of the same screw jack 3-A, including to the left of the screw jack 3-A; the left end of the screw 3 attached to the brace 58 that is used to operate at the same time all of the pistons 2, P-1, and P-2 in their respective cylinders 1, C-i and C-2 through the connections 57 that connect the said pistons 2, P-1, et P-2 to the brace 58. To the right of the same screw jack figure 19 includes the right end of the same screw 3 attached to another brace 58 in order to operate at the same time all of the pistons 2-A, P-3, and P-4 in their respective cylinders 1-A, C-3 and C-4 through connections 57 that connect the said pistons 2-A, P-3, et P-4 to the brace 58.

Figure 20 is a top schematic representation of a multi-cylinder compressor having all of its cylinders on one side of the screw 3 of the screw jack 3-A., including the piston 2 of cylinder 1 joined to piston 2-B of cylinder 1-B through an intermediary coupling shaft 52 and a coupling 10, the piston 2-B of cylinder 1-B joined to piston P-8 of cylinder C-8 through another intermediary coupling shaft 52 and another coupling 10, the piston P-1 of cylinder C-1 joined to piston P-5 of cylinder C-5 through another intermediary coupling shaft 52 and another coupling 10, the piston P-5 of cylinder C-5 joined to piston P-7 of cylinder C-7 through another intermediary coupling shaft 52 and another coupling 10, the piston P-2 of cylinder C-2 joined to piston P-6 of cylinder C-6 through another intermediary coupling shaft 52 and another coupling 10, the piston P-6 of cylinder C-6 joined to piston P-9 of cylinder C-9 through another intermediary coupling shaft 52 and another coupling 10.
In addition figure 20 includes a brace 58 through which the screw 3 of the screw jack 3-A operates at the same time, and in a parallel way, all of the pistons of all of the cylinders of the same compressor, through the connections 57.

Figure 21 is a right representation of figure 20 including the first nine cylinders of the nine rows of cylinders of the same compressor, the screw jack 3-A that operates at the same time all of the 27 cylinders of the same compressor through the brace 58 and the connections 57 through which the first nine pistons of the first nine cylinders are connected to the screw 3.

Figure 22 is a left view of figure 20 including the last nine cylinders of the nine rows of cylinders of the same compressor, the screw jack 3-A, the brace 58 and the connections 57.

Figure 23 is a top schematic representation of a multi-cylinder compressor having its cylinders attached to both ends of the same screw 3 of the same screw jack 3-A by groups of nine cylinders. It includes to the left of the screw jack 3-A, the left end of the screw 3, the piston 2 of cylinder 1 joined to piston 2-B of cylinder 1-B through an intermediary coupling shaft 52 and a coupling 10, the piston 2-B of cylinder 1-B joined to piston P-8 of cylinder C-8 through another intermediary coupling shaft 52 and another coupling 10, the piston P-1 of cylinder C-1 joined to piston P-5 of cylinder C-5 through another intermediary coupling shaft 52 and another coupling 10, the piston P-5 of cylinder C-5 joined to piston P-7 of cylinder C-7 through another intermediary coupling shaft 52 and another coupling 10, the piston P-2 of cylinder C-2 joined to piston P-6 of cylinder C-6 through another intermediary coupling shaft 52 and another coupling 10, the piston P-6 of cylinder C-6 joined to piston P-9 of cylinder C-9 through another intermediary coupling shaft 52 and another coupling 10, and a brace 58 attached on one of its sides to the pistons 2, p-1 and P-2, and on the other side to the left end of the screw 3 of the screw jack 3-A through connections 57, in order to operate at once all of the pistons of the left side in their respective cylinders. Figure 23 includes to the right of the screw jack 3-A, the right end of the same screw 3, the piston P-3 of cylinder C-3 joined to piston P-10 of cylinder C-10 through an intermediary coupling shaft 52 and a coupling 10, the piston P-10 of cylinder C-10 joined to piston P-12 of cylinder C-12 through another intermediary coupling shaft 52 and another coupling 10, the piston 2-A of cylinder 1-A
joined to piston 2-C of cylinder 1-C through another intermediary coupling shaft 52 and another coupling 10, the piston 2-C
of cylinder 2-C joined to piston P-13 of cylinder C-13 through another intermediary coupling shaft 52 and another coupling 10, the piston P-4 of cylinder C-4 joined to piston P-11 of cylinder C-11 through another intermediary coupling shaft 52 and another coupling 10, the piston P-11 of cylinder C-11 joined to piston P-14 of cylinder C-14 through another intermediary coupling shaft 52 and another coupling 10, and another brace 58 attached on one of its sides to the pistons 2-A, P-3 and P-4, and on the other side to the right end of the screw 3 of the screw jack 3-A
through other connections 57, in order to operate at once, all of the pistons of the right side with all of the pistons of the left side described above in their respective cylinders. Because of this configuration the said compressor the subject of the present invention can be operated easily and effectively without any difficulties while producing any amount of cfin of compressed air.

Figure 24 is a front cross-sectional view of a the screw 3 and a simple piston 2 of a compressor with one cylinder made in one piece, including the piston 2 with its faces 46 and 47 and the ring grooves 27, the screw 3, the tongue 7 and the coupling 10.

Figure 25 is a front cross-sectional view of the same screw of the same screw jack which operates at the same time two pistons of a compressor with two cylinders including the piston 2 with its faces 46 and 47, the piston 2-A with its faces 48 and 49, the screw 3, the couplings 10 and the ring grooves 27.

Figure 26 is a front cross-sectional view of the same screw 3 of the same screw jack 3-A that operates at the same time the pistons of a multiple cylinder compressor including the piston 2 with its faces 46 and 47, the piston 2-A with its faces 48 and 49, the piston 2-B, with its faces 53 and 54, the piston 2-C with its faces 50 and 51, the ring grooves 27, the intermediary coupling shafts 52 and the couplings 10 that are used to attached all of the pistons to the screw 3 in order to operate them at once like if they are only one piston.

Figure 27 is an enlarged front cross-sectional view of a piston including the piston 2, the coupling that is used to attach the piston to the screw 3 of the screw jack 3-A or to an intermediary coupling shaft 52, the ring grooves 27, and the drillings 16-A where the water of the cooling system circulates to cool off the piston and the interior of its respective cylinders Figures 28 to 37 are schematic representations of eight compressors used in a group as an example to share and deliver a flow of air, compressed at discharge pressure of 7 bars g, in an equal, continuous and reliable way. All of these compressors are independents and identical and are put to work as follow:

When the compressor H ends the exhaust of its compressed air, the compressor A
must start exiting directly its own compressed air, followed by the compressor B, then by the compressor C, then by the compressor D, then by the compressor E, then by the compressor F, then by the compressor G, then by the compressor H and so on, according to the following description in the individual drawings:

Figure 28 includes the compressor A at the beginning of its exhaust stroke, corresponding with the end of the exhaust stroke of compressor H.

Figure 29 includes the compressor B at the beginning of its exhaust stroke, corresponding with the end of the exhaust stroke of compressor A.

Figure 30 includes the compressor C at the beginning of its exhaust stroke, corresponding with the end of the exhaust stroke of compressor B.

Figure 31 includes the compressor D at the beginning of its exhaust stroke, corresponding with the end of the exhaust stroke of compressor C.

Figure 32 includes the compressor EE at the beginning of its exhaust stroke, corresponding with the end of the exhaust stroke of compressor D.

Figure 33 includes the compressor F at the beginning of its exhaust stroke, corresponding with the end of the exhaust stroke of compressor EE.

Figure 34 includes the compressor G at the beginning of its exhaust stroke, corresponding with the end of the exhaust stroke of compressor F.

Figure 35 includes the compressor H at the beginning of its exhaust stroke, corresponding with the end of the exhaust stroke of compressor G.
Figure 36 includes the compressor A at the beginning of its exhaust stroke, corresponding with the end of the exhaust stroke of compressor H.

Figure 37 includes the compressor B at the beginning of its exhaust stroke, corresponding with the end of the exhaust stroke of compressor A.
For another example, if the pressure of the compressed air is 1 bar g, then we need a group of 2 compressors, and if the pressure needed is 3 bars g, then we need a group of 4 compressors, and so on.

It should be understood, of course, that this compressor can be built from various materials and in different dimensions according to the quantity of compressed air required. The drawings do not show every step in the construction of the present invention, but they set out the overall result clearly.
This reciprocating compressor can be used as an example, to run a power plant of the sort of the Canadian patent no 2328580, that uses compressed air as fuel. Then, a heat exchanger can be used too in this case, to recuperate the lost energy during the air compression., by transferring the heat that is produced during the compression to the water of the pool of the said power plant, where another time this heat will be transferred to the air of the ascending containers, that expends the volume of the imprisoned air. The consequences of this heat recuperation is the displacement of a bigger quantity of water by the expended compressed air volume of the ascending containers, where the buoyant force that exerts upwardly, is equal to the weight of the displaced water.

Before starting a power plant that works with a flow of compressed air and the corresponding compressors the subject of the present example of this disclosure, all of their components have to be in place:

1- The pressure of the compressed air is predetermined in order to build the power plant accordingly. For the present example the corresponding power plant works with a flow of compressed air at a pressure of 7 bars g, and is controlled by a pressure regulator 42 and monitored by a pressure gauge 41. For a continuous and reliable functioning of this power plant, a group of 8 similar compressors is needed in order to share equally the total flow of compressed air needed for the good functioning of the said power plant according to the demonstrations in figures 28 to 37.

2- The line 37 that transit the compressed air which is coming from the compressors the subject of the present example, toward the air tank 39 of the power plant E of figure 3, will be connected to the outlet lines 22... and 23...of all of the 8 compressors.

3- The principal lines 33 and 34 of the main cooling system of all of the 8 compressors, will be connected to all of the lines 17 and 18 to circulate the water of the cooling system between the 8 compressors and the heat exchanger 43.

4- The lines 44 and 45 will be connected to the pool 1-E of the power plant E
of figure 3, to circulate the water through the heat exchanger 43, in order to heat the water of the said pool 1-E
with the heat that is produced during the compression.

5- The power plant E of the Canadian patent no 2328580 will be in place to receive the compressed air of all 8 compressors in a continuous flow all through its operation, through the air tank 39, the pressure regulator 42 and the line 40.
Finally, when all of the components of each one of these compressors, and the ones of the corresponding power plant, will be in place, we make sure that all 8 compressors are ready to work in the right manner. Then we start each one of the said 8 compressors that all are identical, but their individual cycles have different timing. This way a reliable and continuous delivery without interruption of the total needed flow of compressed air is assured for a good and reliable functioning of the said power plant. The distance of the run of each cycle of each compressor, from the beginning of the air compression stroke to the beginning of the compressed air exhaust stroke, is 7 times the distance of the run from the beginning to the end of the exhaust stroke of the same cycle, without any exception for compressors with one or with multiple cylinders all of these compressors work in a parallel way as described above. Hence, for every compressor there is the flow of the other 7 compressors of the same group, to compensate its gap of dead time that exists between the end of the exhaust stroke of every cycle and the beginning of the exhaust stroke of the following cycle The individual functioning of each one of the compressors is detailed as follow:

Figure 4 shows the tongue 7 when it touched the contactor 8 in a way to set on the circuit breaker 9-A-8-A of figure 1, in order first, to stop the motor 11, and then to restart it to turn in the other direction. This rotation allows the pinion 5 to turn the gear-nut 4 freely in its groove 6-A of the brace 6 of the frame 21. Figure 4 shows too, that the screw 3 of the screw jack 3-A is pushing to the left, the piston 2 in its respective cylinder 1. This stroke of compression is by the side 46 of the piston 2 in the cylinder 1, and at the same time, the inlet stroke in the same cylinder 1, is by the side 47 of the same piston 2.

Figures 5 to 7 show the said screw 3 that is continuing to push-in, the said piston 2 to the left while compressing by side 46, and admitting free air by side 47 through the inlet valve 14 in the same cylinder 1.

Figure 7 shows the volume of the compressed air that became 1/8 of the initial volume of the admitted free air (FAD), where the pressure of this compressed air is now 7 bars g as described above in the present disclosure. At this moment, the outlet valve 12 begins to open letting the compressed air to flow out of the compressor and going into the air tank 39 of figure 2 through the lines 22 and 37.
Figure 8 shows that the piston 2 has arrived at the end of its run to the left. Figure 8 shows too that the piston 2 has pushed out of cylinder 1 by its side 46, all of the compressed air of the present cycle, into the air tank 39 of figure 2, and has admitted in the same cylinder 1 by the side 47 all of the needed free air for the next cycle to the right. Figure 8 shows at the same time the tongue 7 that has touched the contactor 9 in a way to set on the circuit breaker 9-A-8-A of figure 1, in order;
first to stop the motor 11, and then to restart it to turn in the other direction, permitting the pinion 5 to turn the gear-nut 4 freely in its groove 6-A of the brace 6 of the frame 21, in the right direction needed to pull-back to the right the same piston 2 in the same cylinder 1 through the same screw 3 of the same screw jack 3-A, starting then a new stroke of compression by the side 47 of the same piston 2 in the same cylinder 1, and starting at the same time an inlet stroke in the same cylinder 1 by the side 46 of the same piston 2 as detailed in figures 9 to 13 according to the same methods described in figures 4 to 8, but the difference is that the same piston 2 will be pulled-back in the same cylinder 1 to perform compression by side 47 and admission by side 46.

If the compressor has one cylinder attached to each end of the screw 3 of the screw jack 3-A as shown in figures 14 and 15, the motor 11 turns the pinion 5, then the gear-nut 4 turns freely in its groove 6-A of the brace 6 of the frame 21 in order to give a linear and alternative movement to the screw 3 of the screw jack 3-A. Then if the said screw 3 is pushed to the left, at the same time it transmits to piston 2 its force and movement in order to push it in cylinder 1 equally to the left, through a coupling 10, in a way to compress air in cylinder 1 by side 46 of the piston 2 and to suck-in free air by side 47 of the same piston 2 in the same cylinder 1. Because both cylinders of the same compressor work in parallel, then at the same time the screw 3 of the screw jack 3-A pulls-back equally to the left piston 2-A through another coupling 10, in order to compress air by side 49 and suck in free air by side 48 of the same piston 2-A in the same cylinder 1-A.
When the left piston is pulled-back in the same cylinder 1 to the right in the following cycle of the same compressor, it experiences admission by side 46 and compression by side 47, at the same time piston 2-A will be pushed in cylinder 1-A to admit free air by side 49 and compress by side 48.
The work of the electrical contactors 8 and 9, the electrical circuit breaker 9-A-8-A and the motor 11 of the screw jack 3 are the same for any compressor with one or with two cylinders.

If the compressor has more then one cylinder attached to each end of the screw 3 of the screw jack 3-A as shown in figures 18, 17 and 16, When the motor 11 turns the pinion 5, the gear-nut 4 turns freely in its groove 6-A of the brace 6 of the frame 21, in order to give a linear and reciprocating movement to the screw 3 of the screw jack 3-A. as explained above for a compressor with two cylinders. If the said screw 3 is pushed-in to the left, at the same time it transmits to piston 2 its force and its movement in order to push it in cylinder 1 equally to the left through a coupling 10, in a way to compress air in cylinder 1 by side 46 and to suck-in free air by side 47, at the same time the same force and the same movement of the screw 3 of the screw jack 3-A will be transmitted to piston 2-B of figure 18, through an intermediary coupling shaft 52 and another coupling 10 that attach piston 2 to piston 2-B in a way to let piston 2-B compress air at the same time by side 54 in cylinder 1-B, and suck in free air by side 53 of the same piston 2-B in the same cylinder 1-B.
Again at the same time, the screw 3 of the screw jack 3-A, pulls-back to the left piston 2-A in cylinder 1-A through another coupling 10, in order to compress air by side 49, and suck-in free air by side 48. At the same time the same force and the same movement of the screw 3 of the screw jack 3-A will be transmitted to piston 2-C of figure 16, through another intermediary coupling shaft 52 and another coupling 10 that attach piston 2-A to piston 2-C, in a way to let piston 2-C compress air at the same time by side 51 in cylinder 1-C, and suck in free air by side 50 of the same piston 2-C in the same cylinder 1-C. And if the screw 3 of the screw jack 3-A travels to the right, it pulls back to the right piston 2 in cylinder I in order to compress by side 47 and suck in free air by side 46 in the same cylinder 1, this motion will be transmitted at the same time to piston 2-B of figure 18 to be pulled-back to the right in order to compress by side 53 and suck in free air by side 54 in the same cylinder 1-B, in addition and at the same time, the same screw 3 of the same screw jack 3-A
pushes-in to the left piston 2-A to compress by side 48 and suck in free air by side 49 in the same cylinder 1-A, this movement will be transmitted at the same time to piston 2-C
of figure 16 to be pushed-in to the right, in order to compress by side 50 and suck in free air by side 51 in the same cylinder 1-C. The work of the electrical contactors 8 and 9, the electrical circuit breaker 9-A-8-A
and the motor 11 of the screw jack 3 are the same for any compressor with one, with two, or with multiple cylinders.

Finally, the compressed air of the air tank 39 will be transferred to the containers with thrust of the power plant E of figure 3 of the Canadian patent no 2328580 through the line 40 and the rotary transfer joint 18-E

The result of this invention is to produce compressed air with compressors that are simple, economical, and easy to operate.

It should be understood of course, that the foregoing disclosure relates to only a preferred embodiment of the invention. This disclosure is intended to cover all changes, and modifications of the example of the invention herein chosen for the purposes of the disclosure, which do not constitute departures from the spirit and scope of the invention.

Ex. 1: Study of the torque needed to operate the screw of the screw jack of the reciprocating double acting compressor the subject of the present invention If the registered discharge pressure at the beginning of the exhaust stroke of the compressed air is 7kgs/cm2 or 70 N/cm2, the total surface of the piston is 1000 cm2, the pitch of the screw of the screw jack is 0.008 m, and the run between the beginning and the end of the exhaust is: 1 m.

Hence, the total force to overcome from the beginning to the end of the exhaust is:
(7 kgs/cm) x 1000 cm2 x 10 N = 35,000 N.

The torque needed for every screw pitch is:
(35,000 N x 0,008 m) / (2 x 3.1416) = 45 mN.

Ex.2: Study of the variations of the volume of 2.10 m3 of air, taken at an atmospheric pressure of 1.01325 bars (FAD), and compressed at 1 bar g, 3 bars g and 7 bars g in the same cylinder by the same piston.

Under a pressure of 1 bar g, the 2.10 m3 become according to Boyle's law:
2.10 m3 x (1.01325 bars + 0 bar g) /(1.01325 bars +1 bar g) = 1.06 m3, almost half of the 2.10 m3.
Under a pressure of 3 bars g, the 210 m3 become according to Boyle's law:
2.10 m3 x(1.01325 bars + 0 bar g) / (1.01325 bars +3 bars g) = 0.53 m3, half of the 1.06 m3.
Under a pressure of 7 bars g, the 2.10 m3 become according to Boyle's law:
2.10 m3 x (1.01325 bars + 0 bar g) / (1.01325 bars +7 bars g) = 0.265 m3, half of the 0.53 m3.

The conclusion of the above detailed calculations is, that the volume of the compressed air decreases for about the half, when the value of the pressure under which the initial volume is taken, will be doubled and added 1, [(pressure x 2) + 1]. In order to verify it we take a look at the following of the above detailed calculations:

2.10 m3 at 0 bar g, became 1.06 m3 at the pressure of: [(0 bar g x 2) +1 = 1 bar g 1.06 m3 at 1 bar g, became 0.53 m3 at the pressure of: [(1 bar g x 2) +1] = 3 bars g.
0.53 m3 at 3 bars g, became 0.26.5 m3 at the pressure of: [(3 bars g x 2) +1 =
7 bars g.

These observations help to configure the conception of the reciprocating double acting compressor the subject of the present invention.

The volume of the imprisoned air inside the cylinder, becomes half of the initial volume of the free air (FAD) admitted initially into the cylinder, and its pressure increases from 0 bar g to 1 bar g, when the piston of the above mentioned compressor is pushed-in or pulled-back half of its run during the beginning of the compression.
( 1.06m3 /2.10m3)x 100 =50%= 1/2.

The volume of the compressed air becomes 1/4 of the initial volume of the free air admitted initially into the cylinder, and its pressure increases from 1 bar g to 3 bars g, when the piston advances again, half of the remaining distance of its run, it means when it is pushed-in or pulled-back 3/4 of its total run (L), (0.53 m3/ 2.10 m3) x 100 = 25% = 1/4.

And the volume of the compressed air becomes 1/8 of the initial volume of free air admitted into the cylinder, If the piston continues to advance until half of the half of the remaining distance of its run, it means when it is pushed-in or pulled-back 7/8 of its total run (L), its pressure increases from 3 bars g to 7 bars g.
( 0.265 m3 / 210 m3) x 100 = 12.5% = 1/8.

Ex3: If the temperature of the 2.10 cubic meters of air is 20 degrees Celsius or 293 degrees Kelvin, At 343 degrees Kelvin the 2.10 cubic meters become: 2.10 m3 x 343 / 293 = 2.46 m3.
The expansion of the volume is:
2.46 m3- 2.10 m3= 0.36 m3, or: (0.36 m3/ 2.10 m3) x 100% = 17 %
It means that the power plant using this flow, can give 17% more energy with an augmentation of:
(343 - 293) = 50 degrees.

Claims (21)

1- Reciprocating double acting compressor, including a solid frame, that supports the strain of any force caused by a pressure of compressed air counteracting on a screw of a screw jack through pistons that are attached to said screw, during the compression of said air in all cylinders of said reciprocating double acting compressor;

said cylinders in which said double acting pistons are moved alternatively by the screw of the screw jack of the compressor, in order to suck-in air into their respective cylinders, then to compress and finally to exhaust the air, compressed at a predetermined discharge pressure toward an air tank;

inlet and outlet valves placed on both ends of each cylinder of the said compressor, that admit free-air and exhaust compressed air, two times in every period;

said screw jack, to overcome resistant forces as the one developed inside the cylinders of the compressor and counteracting on all of the pistons during compression strokes;

a mechanical, electrical, hydraulic, or pneumatic motor to provide a torque, and motion to said screw of the said screw jack, electrical contactors needed to operate circuit breakers that are used to control the motor of the said screw jack;

a cooling system for the entire compressor including the pistons and the interior of all the corresponding cylinders.
2- Reciprocating double acting compressor, as claimed in claim 1 and characterized by:
said screw, that is driven by a free turning gear-nut located in a boring machined in a brace affixed to said frame of said compressor.
3- Reciprocating double acting compressor, as claimed in claim 1 and characterized by:
a pinion combined to a gear box to give a linear and reciprocating movement to said screw of said screw jack, through said free turning gear-nut, in order to control the frequency of cycles of compression that determine the flow of compressed air of said compressor the subject of the present invention.
4- Reciprocating double acting compressor, as claimed in claim 1 and characterized by:
a casing full of oil to lubricate said screw and all gears of said screw jack.
5- Reciprocating double acting compressor, as claimed in claim 1 and characterized by:
a tongue, affixed to said screw of said screw jack, that is used to stop and restart the motor of said screw jack at the end of every exhaust stroke of compressed air of every cycle, through the electrical contactors and the circuit breakers.
6- Reciprocating double acting compressor as claimed in claim 1 and characterized by:
the contactors that are distant one from the other, exactly the same distance of a run that any one of the said pistons of said compressor, travels inside its respective cylinder from the beginning of said compression stroke to the end of said exhaust stroke of any cycle.
7- Reciprocating double acting compressor as claimed in claim 1 and characterized by:
a linear and reciprocating movement of said screw of said screw jack, that allows said compressor to be build with one, two or even with multiple cylinders according to the flow of compressed air needed.
8- Reciprocating double acting compressor as claimed in claim 1 and characterized by:
a small torque that is needed to push-in or to pullback said screw of said screw jack of said reciprocating double acting compressor the subject of the present invention.
9- Reciprocating double acting compressor as claimed in claim 1 and characterized by:
the use of an undetermined number of cylinders in order to increase the flow of said compressor, that are installed on one or on both ends of said screw of said screw jack that operates said pistons in their respective cylinders.
10- Reciprocating double acting compressor as claimed in claim 1 and 9, and characterized by:
a functioning in a parallel way of all said cylinders.
11- Reciprocating double acting compressor as claimed in claim 1, 9 and 10, and characterized by:
a diameter that is the same or different, for said cylinders of said compressor.
12- Reciprocating double acting compressor as claimed in claim 1, 9, 10 and 11, and characterized by:
the same length of each of the cylinders of the said compressor, that is equal to the total run located between the beginning of the air compression stroke and the end of the air compressed exhaust stroke of any cycle.
13- Reciprocating double acting compressor as claimed in claim 1 and characterized by:
pistons that are installed in line and attached together in a way that, the first piston adjacent to the said screw, receives the force and the linear and reciprocating movement, in order to transmit them directly and at the same time to the other pistons of the other cylinders.
14- Reciprocating double acting compressor as claimed in claim 1 and 13, and characterized by:
intermediary coupling shafts and couplings that must be installed between every two adjacent pistons of each side of the screw, in order to operate them all at once in a parallel way as if they are only one piston.
15- Reciprocating double acting compressor, as claimed in claim 1 and characterized by:
cylinders that are installed side by side, and their respective pistons are operated directly by the screw of the screw jack.
16- Reciprocating double acting compressor as claimed in claim 1 and 15 and characterized by:
braces used to attach through connections, all pistons of all cylinders that are placed in rows one beside the other on every end of the screw of the screw jack, in a way to have said screw, pushing-in or pulling-back directly on all of the pistons.
17- Reciprocating double acting compressor as claimed in claim 1 and characterized by:
a cooling system for the pistons of the compressor, that is connected to the main cooling system, in order to cool off at the same time the pistons and the interior of their respective cylinders.
18- Reciprocating double acting compressor, as claimed in claim 1 and characterized by:
flexible hoses that are used to circulate water of said cooling system in order to cool said pistons and the inside of their respective cylinder during the operation of the compressor.
19- Reciprocating double acting compressor, as claimed in claim 1, 16 and 17, and characterized by:
drillings machined in said pistons, in order to circulate water through said pistons to be able to cool said pistons and the interior of said cylinders.
20- Reciprocating double acting compressor as claimed in claim 1 and characterized by:
an interruption of said air flow of compressed air, between said end and said beginning of said exhaust stroke of any cycle.
21- A multi-unit double acting compressor assembly comprising a number of double acting compressor units used to share and deliver without interruption, and in an equal way, a continuous and reliable flow of air, each double acting compressor unit is characterized by:
a solid frame, that supports the strain of any force caused by a pressure of compressed air counteracting on a screw of a screw jack through pistons that are attached to said screw, during the compression of said air in all cylinders of said multi-unit double acting compressor assembly;

said cylinders in which said double acting pistons are moved alternatively by the screw of the screw jack of said double acting compressor unit, in order to suck-in air into their respective cylinders, then to compress and finally to exhaust the air, compressed at a predetermined discharge pressure toward an air tank;

inlet and outlet valves placed on both ends of each cylinder of said double acting compressor unit, that admit free-air and exhaust compressed air, two times in every period;

said screw jack, to overcome resistant forces as the one developed inside the cylinders of said double acting compressor unit and counteracting on all of the pistons during compression strokes;
said screw, that is driven by a free turning gear-nut located in a boring machined in a brace affixed to said frame of said double acting compressor unit;

a pinion combined to a gear box to give a linear and reciprocating movement to said screw of said screw jack, through said free turning gear-nut, in order to control the frequency of cycles of compression that determine the flow of compressed air of said double acting compressor unit the subject of the present invention.

a mechanical, electrical, hydraulic, or pneumatic motor to provide a torque, and motion to said screw of the said screw jack, electrical contactors needed to operate circuit breakers that are used to control the motor of the said screw jack;

a cooling system for the entire double acting compressor unit including the pistons and the interior of all the corresponding cylinders.
CA 2473077 2004-07-27 2004-07-27 Reciprocating double acting compressor Expired - Fee Related CA2473077C (en)

Priority Applications (2)

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CA 2473077 CA2473077C (en) 2004-07-27 2004-07-27 Reciprocating double acting compressor
PCT/CA2004/001450 WO2006010238A1 (en) 2004-07-27 2004-08-04 Compressor comprising dual-action pistons

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CA 2473077 CA2473077C (en) 2004-07-27 2004-07-27 Reciprocating double acting compressor

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CA2473077C true CA2473077C (en) 2006-10-24

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RU2578748C1 (en) * 2015-02-19 2016-03-27 Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Омский государственный технический университет" Piston compressor with independent liquid cooling
RU2600215C1 (en) * 2015-04-29 2016-10-20 Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Омский государственный технический университет" Piston compressor with independent cooling of cylinder
RU175178U1 (en) * 2017-06-26 2017-11-24 Федеральное государственное бюджетное образовательное учреждение высшего образования "Омский государственный технический университет" PISTON COMPRESSOR

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EP3667083A1 (en) * 2018-12-10 2020-06-17 Picote Solutions Inc. Air pump system
CN114439610A (en) * 2021-12-22 2022-05-06 王依杭 Single-cylinder diesel engine

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US1881479A (en) * 1932-10-11 Clay gun piston position indicating means
US4653986A (en) * 1983-07-28 1987-03-31 Tidewater Compression Service, Inc. Hydraulically powered compressor and hydraulic control and power system therefor

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2578748C1 (en) * 2015-02-19 2016-03-27 Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Омский государственный технический университет" Piston compressor with independent liquid cooling
RU2600215C1 (en) * 2015-04-29 2016-10-20 Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Омский государственный технический университет" Piston compressor with independent cooling of cylinder
RU175178U1 (en) * 2017-06-26 2017-11-24 Федеральное государственное бюджетное образовательное учреждение высшего образования "Омский государственный технический университет" PISTON COMPRESSOR

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