WO2011065569A1 - Air compressor, power generator using the same and drive device for power generator - Google Patents

Abstract

An air compressor is provided with: a plurality of cylinder units, each having a cylinder and a piston; and a piston driving mechanism which is linked to each of the pistons of the plurality of cylinder units and drives each of the pistons simultaneously. Each cylinder of the plurality of cylinder units has a cylinder hole of a predetermined length. Each piston is disposed so as to move back and forth within a cylinder hole in such a way that a first space is formed at one side and a second space is formed at the other side in the longitudinal direction of the cylinder hole. The plurality of cylinder units are sequentially connected from the furthest-upstream cylinder unit which is positioned furthest upstream and in communication with the atmosphere, to the furthest-downstream cylinder unit which is positioned furthest downstream and in communication with a supply unit, and the plurality of cylinder units are mutually connected in such a way that the first space of a cylinder unit positioned at the upstream side is in communication with the second space of a cylinder unit positioned at the downstream side. The volume of each cylinder unit is set in such a way that the volume decreases gradually from the furthest-upstream cylinder unit to the furthest-downstream cylinder unit.

Description

AIR COMPRESSION DEVICE, POWER GENERATION DEVICE USING THE SAME, AND DRIVE DEVICE FOR POWER GENERATION DEVICE

The present invention relates to an air compressor capable of compressing air at high pressure, a power generator using the same, and a drive device for the power generator.

So far, power generators using various powers have been developed. For example, Japanese Patent Laid-Open No. 2008-303865 has a plurality of buckets arranged so as to circulate in water and a compressor that discharges compressed air into the water, and stores the air released into the water by the compressor in the bucket. The bucket is driven underwater by the buoyancy of the air stored in the bucket, and the generator is rotated using this driving force.

In such a conventional power generation apparatus, in order to rotate the generator with a large torque, it is necessary to release air from a deep part in order to obtain a strong driving force of the bucket, in other words, a large buoyancy of the bucket. However, since the water pressure is high at a deep water location, the air must be compressed and output at a high pressure. Therefore, the compressor that discharges air into the water is necessarily increased in size, or it is necessary to output high power. In this situation, a compressor with high energy is required to obtain a large amount of power, but there is a limit to increasing the energy of the compressor. On the other hand, if the compressor energy is set appropriately, There was a problem that the power generation efficiency was extremely low.

On the other hand, there is a demand for an air compressor capable of exhausting high pressure compressed air or outputting a large force by introducing the atmosphere so as to be applied not only to the field of power generators but also to various technical fields. . *

JP 2008-303865A

An object of the present invention is to provide an air compressor having high energy efficiency that can solve the above-mentioned problems of the prior art and meet the above-mentioned demand, and a power generator having high power generation efficiency using the air compressor. is there.

In order to achieve the above object, an air compressor according to an embodiment of the present invention includes a plurality of cylinder units each having a cylinder and a piston, and each piston connected to each piston of the plurality of cylinder units. And a piston drive mechanism for simultaneously driving the two.

Each cylinder of the plurality of cylinder units has a cylinder hole of a predetermined length, and each piston forms a first space on one side in the longitudinal direction of the cylinder hole and a second space on the other side. So as to reciprocate in the cylinder hole.

The plurality of cylinder units are sequentially connected from the most upstream cylinder unit located at the most upstream and communicated with the atmosphere to the most downstream cylinder unit located at the most downstream and communicated with the supply unit, and the first cylinder unit located upstream. Are connected to each other so that the space of the cylinder unit communicates with the second space of the cylinder unit located on the downstream side, and the volumes of the plurality of cylinder units are set so as to gradually decrease from the most upstream cylinder unit to the most downstream cylinder unit. Has been.

Furthermore, the power generator according to the present invention is configured to drive a generator using the air compressor.

It is a schematic block diagram which shows the electric power generating apparatus which concerns on 1st Example of this invention. It is a front view which shows the structure of the electric power generating apparatus in 1st Example. It is a side view of the electric power generating apparatus shown by FIG. It is a side view which shows the air compressor in the electric power generating apparatus shown by FIG. FIG. 5 is a plan view of the air compression device shown in FIG. 4. It is a one part enlarged view of the structure of the air compressor shown by FIG. It is a front view of the electric power generating apparatus which concerns on 2nd Example of this invention. It is a side view of the electric power generating apparatus shown by FIG. It is a top view of the electric power generating apparatus shown by FIG. It is the schematic of the air compressor which comprises the electric power generating apparatus shown by FIG.

FIG. 1 to FIG. 3 schematically show the configuration of a first embodiment of a power generator using an air compressor according to the present invention. In addition, the air compression apparatus which concerns on this invention is not limited to being used for a power generator, You may apply so that arbitrary apparatuses may be driven using the compressed air.

As shown in FIG. 1, the power generator in the first embodiment includes a power generator 16 (see FIG. 3), a drive device 30 that drives the power generator 16, and an air compressor 20 that starts the drive device. ing.

The drive device 30 is composed of a rotation mechanism 50 in the first embodiment. The rotating mechanism 50 includes a water tank 10 filled with a fluid, for example, water, a plurality of buckets 14 movably provided in the water tank, and a bucket moving mechanism 28 that supports the buckets 14. .

As shown in FIGS. 1 to 3, the water tank 10 has, for example, a vertical shape extending in the vertical direction, and the plurality of buckets 14 can be moved in the vertical direction by a bucket moving mechanism 28. The bucket moving mechanism 28 spans the upper sprocket 11 disposed above the water tank 10, the lower sprocket 12 disposed below the water tank, and the upper sprocket 11 and the lower sprocket 12 to attach a plurality of buckets 14. And a chain 13. The bucket 14 is continuously attached along the longitudinal direction of the chain 13.

In order to drive the plurality of buckets 14 by buoyancy in the water, air is introduced into the water of the water tank 10 by the air compressor 20 (FIG. 1). The air compressor 20 has a discharge port 23 provided in the lower part of the water tank 10, and introduces compressed air into the water from the discharge port 23 via a valve mechanism 29. The air introduced into the water is accommodated in the bucket 14 and imparts buoyancy to the bucket. Due to the buoyancy of the air, as indicated by an arrow in FIG. 1, the bucket 14 moves upward, whereby the chain 13 moves upward and downward in the water, and the upper sprocket 11 and the lower part The sprocket 12 is rotated. In this manner, the bucket 14 can move underwater by buoyancy, and the upper and lower sprockets 11 and 12 can be rotated via the chain 13.

A rotating shaft 15 rotatably attached to the water tank 10 is connected to the upper sprocket 11 via a chain 26, and the rotating shaft 15 is connected to the rotating shaft 15 via a transmission mechanism 27 as shown in FIG. It connects with the generator 16 arrange | positioned under the outer side. Briefly, the transmission mechanism 27 includes a sprocket 27a attached to the rotary shaft 15 and a chain 27d spanned over the sprocket 27c attached to the rotary shaft 16a of the generator 16 via the intermediate mechanism 27b (see FIG. 3). As described above, the sprockets 11 and 12 are rotated as the bucket 14 and the chain 13 move in the water, whereby the generator 16 is rotated and power is generated.

The plurality of buckets 14 are formed of, for example, a container body that is open on one side and closed on the other side. When each bucket 14 moves in the upward direction as shown by reference numeral 14a in FIG. 2, the opening portion faces downward, and when it moves in the downward direction as shown by reference numeral 14b, the opening portion Is formed so as to face upward. Therefore, the air discharged from the discharge port 23 provided in the lower part of the water tank 10 is accommodated in the bucket 14 with the opening portion facing downward, and the leakage of air from the bucket 14 is suppressed. . Therefore, as described above, buoyancy is generated in the bucket 14 and the chain 13 can be rotated by moving upward. On the other hand, when the bucket 14 moves upward in the vicinity of the water surface W and starts moving in the downward direction, the direction of the bucket 14 is opposite and the opening is directed upward. Here, when the bucket 14 is located at the uppermost part, it is necessary that the positions of the water surface W of the water filled in the water tank 10 and the upper sprocket 11 are set so that the bucket comes out of the water surface. When the bucket leaves the water surface, the air in the bucket 14 is released into the atmosphere.

In the first embodiment, the plurality of buckets 14 are mounted on the chain 13 so as to partially overlap. Specifically, as shown in FIG. 2, it is arranged so that the bottom side opposite to the openings of other buckets 14 arranged adjacent to each other is inserted into the opening of the bucket 14. . That is, the intervals between the buckets 14 are arranged close together. Thereby, it can suppress that the vortex which generate | occur | produced in the back of the bucket 14 which advances underwater by the rotation of the chain 13 becomes resistance when the subsequent bucket 14 advances.

As shown in FIG. 2, two air compression devices 20 are provided and are arranged on each side of the drive device 30, but it is sufficient that at least one air compression device is provided.

The air compression device 20 includes a plurality of cylinder units 100 as shown in FIGS. Each of these cylinder units 100 has a cylinder 21 and a piston 22. Each piston 22 of the plurality of cylinder units 100 is connected to a piston drive mechanism 101 (FIG. 4) and is simultaneously driven by the piston drive mechanism 101. The piston drive mechanism 101 includes an arm 25 connected to each piston 22 and an arm drive mechanism 55 that drives the arm. One end of the arm 25 is rotatably attached to the water tank 10 or an appropriate frame, and the other end can be swung (see the arc-shaped arrow in FIG. 4 and FIG. 6). As shown in FIG. 4, the arm drive mechanism 55 has a rotating plate 25 c rotated by a motor 25 a and one end rotatably attached to a position deviated from the rotation center of the rotating plate 25 c and the other end rotatable to the arm 25. And a rod 25b attached thereto. When the motor 25a rotates, the rotating plate 25c is rotated, and the rod 25b is reciprocated with the rotation of the rotating plate, and the arm 25 swings. In short, as shown in FIG. 4, the arm drive mechanism 55 converts the rotational force of the drive motor 25a into the reciprocating motion of the rod 25b, whereby the arm 25 is swung.

Each cylinder 21 of the plurality of cylinder units 100 has a cylinder hole of a predetermined length, and each piston 22 forms a first space 22a on one side in the longitudinal direction of the cylinder hole and on the other side. It arrange | positions so that the inside of a cylinder hole may reciprocate so that the 2nd space 22b may be formed (refer FIG. 6).

As shown in FIG. 1, the plurality of cylinder units 100 are located on the most upstream side and communicate with the atmosphere from the most upstream cylinder unit 100U located on the most downstream side and communicate with the supply unit, that is, the drive unit 30. 100D, which are sequentially connected to each other and connected to each other so that the first space 22a of the cylinder unit located on the upstream side communicates with the second space 22b of the cylinder unit located on the downstream side. The volume is set so as to gradually decrease from the most upstream cylinder unit 100U to the most downstream cylinder unit 100D.

In the air compressor 20 in the illustrated embodiment, as shown in FIG. 4, the plurality of cylinder units 100 are arranged side by side so as to be parallel to each other. In the illustrated embodiment, each cylinder 21 has the same inner diameter, that is, a cross-sectional area in the direction perpendicular to the longitudinal direction, but has a different length. For example, the length is gradually reduced from the upstream toward the downstream. In other words, each cylinder 1 is set so that the volume of the cylinder hole gradually decreases from upstream to downstream. In addition, the cylinder unit 100 is arrange | positioned so that the center of a longitudinal direction may be located on the same straight line. In other words, when a plurality of cylinder units are assembled, these cylinder units are arranged such that the center lines in the longitudinal direction are located on the same line.

Here, the arrangement and connection states of the cylinder units constituting the air compressor 20 are shown in an enlarged manner in FIG. In FIG. 6, for the cylinder unit, the cylinders of three cylinder units from the upstream (lower end in FIG. 6) are denoted by reference numerals 21, 121, and 221 for convenience. As shown in FIG. 6, in each cylinder 21, 121, 221, the first space 22 a, 122 a, 221 a on one end side and the second space 22 b, 122 b on the other end side in the longitudinal direction inside the cylinder hole. Pistons 22, 122, and 222 that are partitioned into 221b and reciprocate in the cylinder holes are arranged.

Further, since each of the pistons 22, 122, 222 is connected to the arm 25 along the longitudinal direction, all the pistons 22, 122, 222 connected to the swing end side of the arm 25 are all. At the same time, it reciprocates in each cylinder hole at the same period. That is, the pistons 22, 122, 222 move in the same direction within the cylinders 21, 121, 221. In other words, all the pistons 22, 122, 222 move simultaneously to one end side or the other end side. It will be.

Further, the cylinders 21 and the like described above are connected via the check valve 24 so that the first and second spaces 22a and 22b partitioned by the pistons 22 and the like of the adjacent cylinders 21 and the like communicate with each other. It is connected. Specifically, the longest first cylinder 21 located at the lowermost end in FIG. 6 and the second cylinder 121 having the second length shorter than the first cylinder 21 are the first space 22a on one end side of the first cylinder 21. And the second space 122b on the other end side of the second cylinder 121 communicate with each other via a check valve 24, and the second space 22b on the other end side of the first cylinder 21 The first space 122a on one end side of the second cylinder 121 communicates with and is connected via the check valve 24. At this time, each check valve 24 is configured such that air flows from the first cylinder 21 to the second cylinder 121. In this case, the first cylinder 21 is located on the upstream side, and the second cylinder 121 is located on the downstream side. Similarly, the other cylinders are located on the downstream side as shown in FIG. 6, and the lower the cylinder length, the more downstream the cylinder is located.

Similarly to the above, the second cylinder 121 located on the upstream side and the third cylinder 221 located on the downstream side are the first space 122 a on one end side of the second cylinder 121 and the other end of the third cylinder 221. The second space 222b on the side communicates with and is connected via the check valve 24. The second space 122b on the other end side of the second cylinder 121 and the one end side of the third cylinder 221 are connected to each other. The first space 222 a communicates with and is connected via the check valve 24. Hereinafter, the same applies to the other cylinders.

Although not shown, the first space on one end side and the second space on the other end side of the cylinder 21 arranged on the most downstream side are each in communication with a discharge port 23 extending into the water tank 10. Accordingly, the compressed air flowing into the first space on one end side and the second space on the other end side of the cylinder 21 arranged on the most downstream side is moved from the discharge port 23 into the water tank 10 by the movement of the piston 22. And is accommodated in the bucket 14.

In the above-described configuration, the piston 22 of each cylinder unit 100 is simultaneously moved in the same direction by the piston drive mechanism 101, so that air flows from the upstream cylinder 21 to the downstream cylinder 21 each time. The air inside is sequentially compressed, and high-pressure air can be discharged from the underwater discharge port 23 toward the bucket 14 from the most downstream cylinder 21.

Next, the operation of the above power generator will be described. First, when the arm 25 shown in FIG. 6 is driven to swing from the other end side (right side) to the one end side (left side), the piston 22 in the first cylinder 21 shown at the lowermost stage also moves to the one end side. At this time, the swing of the arm 25 causes the piston 122 in the second cylinder 121 located above, that is, the downstream side to move to one end side. Similarly, the piston 122 in the third cylinder 221 located further above, that is, downstream. The piston 222 also moves to one end side. In this way, the pistons 22 in all the cylinders 21 are simultaneously moved to one end side where the swing end of the arm 25 is moved.

As a result, the air in the left space, that is, the first space 22a on the one end side with respect to the piston 22 of the first cylinder 21 is pushed out by the piston 22, and the second end on the other end side of the second cylinder 121 on the downstream side. It flows into the space 122b through the check valve 24. That is, when the pistons 22 and 122 of the cylinders 21 and 121 are simultaneously moved to one end side of the cylinders 21 and 121, the air in the first space 21a on the one end side of the upstream first cylinder 21 is It flows into the second space 122b on the other end side of the second cylinder 121 on the downstream side. At this time, since the volume of the second cylinder 121 is smaller than the volume of the first cylinder 21, the air flowing into the second cylinder 121 is further compressed.

At the same time, the piston 122 of the second cylinder 121 is pushed to one end side by the compressed air flowing into the second space 122b on the other end side in addition to the driving force of the swinging arm 25. Then, the air in the first space 122a on one end side of the second cylinder 121 flows into the second space 222b on the other end side of the third cylinder 221 located further downstream. At this time, as described above, the volume in the third cylinder 221 on the further downstream side is formed to be small, so that the air flowing into the third cylinder 221 is further compressed. In this way, the operation described above works sequentially for all the cylinders on the downstream side, and the air can be gradually compressed to a high pressure as it goes downstream.

After that, when the arm 25 swings so that the piston 22 etc. moves to the other end side of each cylinder 21 etc. which is opposite to the above, the space of each cylinder 21 etc. opposite to the above, The compressed air will flow in sequentially from the upstream side to the downstream side. Therefore, the air can be compressed at all times.

Thus, in the air compression device, air can be compressed stepwise by the plurality of cylinders 21 and the like. At this time, the piston 22 or the like of the downstream cylinder 21 or the like into which air flows from the upstream cylinder 21 or the like is a force that moves the compressed air flowing in from the upstream side to push the air further to the downstream cylinder. Is energized. Thus, the force of pressing the piston by the compressed air is transmitted to the pistons installed in all the downstream cylinders. Therefore, by using the plurality of cylinders 21 and the like, the air can be compressed as it proceeds downstream, and the necessary force at that time is further urged together with the compressed air flowing in from the upstream side. As a result, even when the air is compressed to a high pressure, the pressing force by the compressed air from the upstream cylinder 21 or the like is urged against the pistons 22 or the like of all the cylinders 21 or the like. Even if the force urging the piston 22 and the like by driving 25 is small, highly compressed air can be obtained. That is, an air compressor with extremely high energy efficiency can be realized.

Compressed air in the cylinder located on the uppermost stage, that is, on the most downstream side, is discharged from the air compressor 20 described above to the vicinity of the bottom surface in the water tank 10 from the discharge port 23 shown in FIG. Then, in the vicinity of the bottom surface in the water tank 10, the discharged air flows into the bucket 14 whose opening is directed downward so as to move upward, and is stored in the bucket 14. As a result, buoyancy due to the air accumulated in the bucket 14 is generated, and the chain 13 can be rotated. Due to the rotation of the chain 13, the generator 16 shown in FIG. 3 is rotated to generate power. When the bucket 14 moves upward in the vicinity of the water surface W and starts moving in the downward direction, the direction of the bucket 14 is opposite and the opening is directed upward. Thereby, the air in the bucket 14 is discharged into the atmosphere.

As described above, power generation efficiency is also improved by generating power using the buoyancy of air compressed by an air compression device with higher energy efficiency. In the above configuration, it is possible to use the rotary drive device using air buoyancy without providing a generator. In such a case, the energy efficiency can be improved.

Next, a specific example when the first embodiment is implemented will be described.

Table 1 shows the amount of work and the calculation of power in and out when each cylinder has a cylinder diameter: φ320mm and stroke (hereinafter referred to as ST): 26-22cm. As a result, the calculation efficiency was 11.03 times, a high efficiency that could not be predicted by conventional devices.

到達 The ultimate pressures in Table 1 are all the first cylinder volume / next volume = ST26 / next ST (26 / 23.5 because it is sucked into the third volume during the second calculation). The differential pressure is the total difference required to suck and push the initial pressure at the start of the piston received from the previous cylinder into the next cylinder volume, and because it is sucked and pushed into the next volume, it must be equal to its ultimate pressure. Don't be.

This is based on the fact that “compressed air has the same pressure everywhere”. Total maximum ultimate force = differential pressure x cylinder cross section, total work amount = maximum ultimate force x ST / 2, "total" attached to the head of the term is intended to match the amount of air movement that does not require work and the amount of work that requires replenishment It is.

The volume ratio is that of the next cylinder volume, and the volume ratio = next ST / own ST, and this molecular component with respect to the total work amount is a work-free air movement. Replenishment work amount = total work amount−moving work (equivalent). The net supply power can be calculated from the replenishment work amount x2 / the own ST. Therefore, all the air compression mechanisms are based on “PxV = constant” and “compressed air has the same pressure everywhere”. No other theorems or principles are necessary.

The cylinder unit's sliding resistance 設置 (all horizontal installation operation is about 1/3 of the upward ratio, and the cylinder diameter is φ200mm due to the sliding speed limitation even in the smallest practical scale), the unit pressure loss decreases as the cylinder diameter increases. I understood. Air leakage from cylinders, check valve cracking pressure loss, piping resistance and air trapped in piping between cylinders (both negligible ranges), motor conversion / deceleration efficiency combined 85% (reduction ratio approx. 1/25: allowable torque Calculated from the above, the conversion efficiency of the motor itself is 99.5%), inertia resistance around the kite arm etc. (The material of the swing arm is aluminum, the crank swing transmission method from the flywheel transmission characteristics, after shock attenuation at both ends, Considering the motor required torque at zero and the cylinder end position at the maximum load, all cylinders are equipped with cushions), an efficiency of about 70% was secured.

The results in Table 1 are not directly related to the supply power that compresses a constant amount of atmospheric pressure to discharge pressure and the buoyancy recovery power.

In order to cope with the load fluctuation of the generator, the levitation speed is measured and the air supply amount is automatically adjusted, and at the time of starting, it is necessary to fill all of the bucket vertical rows with air.
About buoyancy recovery method and air compressor:
As a method of effectively recovering all the discharge air (buoyancy) regardless of the air discharge timing, a bucket conveyor is provided in the water tank, and a reverse bucket attached continuously to each chain link is used to receive the discharge air at the lower rotating part. By doing so, buoyancy was continuously obtained and power could be recovered.

Unlike in the atmosphere, when the bucket spacing is even a little, resistance to repel the water in front and eddy current resistance in the rear are added. In this example, the two buckets are in close contact with each other and the two types of resistance are theoretically Eliminate the resistance by maximally reducing the relative speed between the water and the bucket by installing the necessary water flow guide plates on the inner and upper and lower rotating parts of the chain with the same cross section as the left and right straight parts. It was possible to realize it thoroughly.
Widen the upper surface of the aquarium to facilitate water surface management, adjust the bucket capacity and shape, etc., try to effectively collect buoyancy until the end, discharge less unnecessary air and fill empty buckets without resistance Various considerations were made.

Specifically, the pitch of the reverse bucket conveyor chain is 100 mm, the reverse bucket is simply and firmly fixed continuously for each link, and 10 reverse buckets per meter are constantly receiving buoyancy and the levitation speed. Up to about 0.7 m / s, it was considered that operation was possible, but in this specific example, all were set to 0.4 m / s. The entry / exit power and estimated efficiency are as shown in Table 1.

In general, when the cylinder combination is the same, the efficiency decreases when the water tank is raised. However, in the case of the device shown in Table 4 (calculation of work load and power in / out of 48m water depth set of 33 rodless cylinders) Increase the number of cylinders and increase the number of cylinders, the discharge pressure is reached by repeating the effect of no-work air movement equivalent to the gain work of the push-in method and the replenishment work little by little, and the supply power is reduced and the efficiency is increased by increasing the number of cylinders It was proved by this calculation example that the improvement was inductively proved, and that the number of water tanks could be increased easily by increasing the number of tanks, and that the efficiency was still improved.

The output was about 50 times as much as the calculated power.

To summarize what can be said about the power generation device using the air compression device in this specific example as compared with the conventional power generation device, it is superior to all that, “No matter where it is installed + if there is a place, a device of a certain scale can be installed + accordingly. Power generation is possible anywhere + compact + continuous intermittent operation option + medium is only water and air ”.

Next, a second embodiment of the present invention will be described with reference to FIGS.

In the power generation apparatus according to the second embodiment, unlike the power generation apparatus according to the first embodiment described above, the power generation apparatus does not generate power by buoyancy and does not have a water tank. Instead, the rotation conversion mechanism 60 is connected to the piston of the cylinder unit 321 having the smallest volume located in the most downstream of the cylinder unit group in the air compressor 20. The rotation converting mechanism 60 is configured to rotate the generator 16 by converting the reciprocating motion of the piston into a rotating motion. The rotation converting mechanism 60 includes a slide arm 31 that is movable along the longitudinal direction of the cylinder unit 321 in conjunction with the reciprocating movement of the piston, and a sprocket / chain mechanism 33 that converts the movement of the slide arm 31 into a rotational motion. Two one-way clutches 32 and a transmission mechanism 61 for transmitting the rotation of the sprocket / chain mechanism 33 to the generator 16 are provided. The transmission mechanism 61 includes a shaft 34 connected to the one-way clutch 32 and a chain 35 connected to the shaft 34.

Specifically, in the air compressing device 20 in the second embodiment, as shown in FIGS. 7 to 10, in particular, FIG. 10, the compressed air in the cylinder 321 having the smallest volume located on the most downstream side is supplied to the uppermost stream. The discharge is made to return to the cylinder 322 having the largest volume located at the position. At this time, when the slide arm 31 moves in conjunction with the reciprocating motion of the piston of the cylinder 321, the chain of the sprocket / chain mechanism 33 rotates. By using the two one-way clutches 32, the reciprocating operation of the slide arm 31 is converted into rotation in a fixed direction by the sprocket / chain mechanism 33. The rotational force generated by the sprocket / chain mechanism 33 is transmitted to an upwardly extending shaft 34 in the transmission mechanism. When the shaft 34 rotates, the chain 35 disposed above rotates in conjunction with the rotation. As the chain 35 rotates, the generator 16 connected to the chain 35 rotates and can generate power.

Here, in the power generator configured as described above, the most compressed air is discharged from the cylinder 321 located at the most downstream side so as to flow into the cylinder 322 located at the further upstream side. The piston does not require a force due to the swing drive of the arm 25 or can reciprocate with only a small force. In this 2nd Example, since it is generating with the reciprocating movement of this piston, it can be said that it is a power generator with high energy conversion efficiency. In the above configuration, it is possible to use the rotary drive device using air buoyancy without providing a generator. In such a case, the energy efficiency can be improved.

Next, a specific example when the second embodiment is implemented will be described.

The principle of this embodiment is a compressed air recursive power generator.

In order to explain this basic theory and configuration, a total of 16 cylinder units each having a cylinder of φ125 mm and stroke (hereinafter referred to as ST) of 75 to 56.5 cm were used.

The features of this device are that it does not use a water tank, that the first cylinder sucks and returns the compressed air that has reached the final cylinder, and that the piston of the final cylinder unit is not connected to the swinging arm and is dedicated to output, with a one-way clutch That is, the generator is driven directly through the high-speed transmission system. For this reason, a constant speed is required and, for example, a cylindrical cam is generally used. However, since the generator-side flywheel has the effect of equalizing speed, the supply-side transmission can also use the flywheel.

Therefore, the weight is reduced by not using a water tank, and flywheel transmission characteristics using air compression characteristics provide extremely improved efficiency, and flywheel transmission has a buffering effect at both ends, realizing high-speed operation with a cylindrical cam transmission ratio. We were able to. At this time, smooth operation with low vibration and low noise was obtained.

Specific examples of the air compressor are shown in Table 9.

The calculation of the work by piping system and cylinder, and the result of this and the working phenomenon of the suction system by cylinder, including the operating phenomenon, are shown.

These results are summarized in Table 5 (or 8).

In this case, since the # 4 cylinder rod requires constant speed operation, the swing arm is not connected, only for output, therefore there is no internal supply work, and it moves at constant speed due to the generator side flywheel effect. The combined efficiency of the gas characteristics and the supply side flywheel transmission characteristics was extremely high, and the effect of buffering both ends of the cylinder was added, and the piston was able to move at high speed, smoothly and with low vibration and low noise.

«Important here is that # 3 cylinder is sucked up to # 3 cylinder via # 1 cylinder suction, and # 4 cylinder has the same suction effect as connecting with swing arm. In addition, the # 4 cylinder not only outputs externally, but also contributes to improving efficiency by demonstrating the assist effect that exceeds the majority of the net replenishment of the # 1 cylinder.

The calculation results are physical calculations based on the premise that there is no air leak. To compensate for these phenomena, it is possible to replenish air from outside with a filter in the lower left piping system diagram.

Here, the efficiency of 31.03 times is the physical calculation efficiency, which is a marvelous value, but the main reason is that air movement of the same volume does not require work. By adding a small amount of push-in to this, the total amount of air is moved to the next cylinder. Accumulation results are obtained by this repetition.

Table 10 shows the results of studies with 2 cylinders and 1 cylinder.

Combination of air characteristics and transmission characteristics When combining air compression characteristics and flywheel transmission characteristics examination, the load in the cylinder direction is in line with the flywheel axis at the cylinder end compression limit (maximum ultimate pressure) position. It is noted that the total load and the load in the direction of rotation of the motor become zero, and the compression on the opposite side from zero starts gently.

This is because the initial pressure is received from the previous cylinder, so the zero start is naturally proportional to the compression distance and reaches the maximum attainment force at the cylinder end. In the characteristics.

In Table 9, the supply power is calculated simply from the total amount of replenished work, but what is important here is the load on the motor other than the sum of the net supply power as well as the gain or no-work transfer effect. This reaching force is not proportional to the compression distance from both ends and starts from a zero directly proportional to the reaching force, which is a gas (air) characteristic. *

As a result of Table 9, the calculated output is 492w, the supply power is 15.868w, and the efficiency is 31.03 times. When this effect is combined, the supply power is 6w, which is a remarkable improvement, and the estimated actual efficiency is 400 / It was found that 6 = 66.67 times.

The power generation device using the air compression device in this specific example is also superior to the conventional power generation device in that “ no matter the installation location + any size device can be installed if there is a place + therefore power generation anywhere + compact + It was found that “ continuous intermittent stable operation selection freedom + air is the only medium ”.

As a general rule, this power generation device can reduce the actual amount of power used, and can be installed anywhere in the site, and can be installed at a predetermined scale and can generate power anywhere. We can meet the demands of global advanced society while promoting promotion.

As described above, the air compressor according to the present invention is configured as described above, so that an air compressor with high energy efficiency can be realized, and further, energy efficient rotation can be achieved by using this. A drive device and a power generation device with high power generation efficiency can be realized.
Table 1 Work set and power entry / exit power of 4 cylinders set depth 1.94m core 1.6m (numbers not shown in the table indicate head side, EN stands for work load)
(Cylinder diameter φ320 cross-sectional area, head side 32 ² xπ / 4 = 804.25 cm ² , rod side (32 ² -5.6 ² ) xπ / 4 = 779.62 cm ² , ST is a combination of 26 to 22).

Basic policy: The premise of this design is to divide and distribute 2 discharges of 1 reciprocation / 1 s into 4 buckets (all the calculation methods in this section adopt the suction method).
Discharge work: ST22 discharge pressure is 1.94m to 1.194kg / cm ² , discharge volume 20910.4 / 1.194 = 17512.9cc compression distance 17512.9 / 804.25 = 21.78cm, so from the compression side
The required amount of work to start discharging at 22-21.78 = 0.22cm is 9.97737 (0.22 / 2 + 21.78) = 214.4644kg-cm (calculation at the bottom of the above table, others are as shown).
Calculation input: Because of 1s1 round trip, 304.1009 + 313.4081 = 617.509kg-cm / s = 6.1751kg-m / s = 0.06054kw per 1s. At an estimated efficiency of 0.7, 0.06051 / 0.7 = 0.086486 kW.
Calculated output: The average volume at the center of the conveyor in the water tank is the head side (20910.4 / 1.194 + 20910.4) /2=19211.65cc, the rod side (20270 / 1.194 + 20270) /2=18623.3cc, and this discharges once a round twice per second. 1921.65 + 18623.3 = 37835cc divided into four equal parts, average water drainage volume per bucket 37835/4 = 9458.7cc, so the average buoyancy is 9..4587kg, 18 active buckets, 9.4587x18 = 170.26kg, levitation speed At 0.4m / s, the output is 170.26x0.4 = 68.1029kg-m / s = 0.6677kw.
Estimated output efficiency 0.6, 0.6677x0.6 = 0.4006 kW. From the above, the supply power is 90w from a commercial motor and 400w power generation is possible. Therefore, the estimated actual efficiency is 400/90 = 4.44 times, and the physical calculation efficiency is 0.6677 / 0.06051 = 11.03 times.

Explanation of the principle The above buoyancy is calculated from the mass of water discharged by air and PxV = constant, ultimate pressure (because it is pushed into 26 / next ST--matches the next volume ratio with respect to ST26), total maximum ultimate force (as shown) )-Total work (same as above), the movement is the movement that does not require work, and the replenishment is the net supply work that needs to be replenished to compress and suck into the next volume, where PxV = constant and where the compressed gas is However, the reach of the net supply is literally based on the same pressure.

The above calculation output was entered from the average volume at the center of the conveyor, but the total atmospheric pressure volume for one discharge twice per second coincides with the initial cylinder head / rod side total, so 20270 + 20910.4 = 41180.4cc It becomes. Since this is equally divided into four buckets, the average is 41180.4 / 4 = 10295.1cc per bucket. This is equivalent to the volume of air on the top of the water tank that drains water. According to “buoyancy is the mass of water drained”, the specific gravity of water is 1 on the upper surface of the water tank, so 10295.1 cc × 1 = 10295.1 g = 10.2951 kg.

Also, since the absolute pressure of the discharge part is 1.194 kg / cm ² , this volume v becomes P = V = 10295.1 / 1.194 = 8622.4cc from the relation of 10295.1 × 1 = vx1.194, so this buoyancy is Similarly, the average buoyancy is 8.6224 kg, the average buoyancy is (10.2951 + 8.6224) /2=9.4588 kg, and the output is the same as the above output up to 0.6677 kw (Note that the conversion unit is 1 kw = 102 kg-m / s = 10200 kg- cm / s), and there is no distinction between suction and pushing in the output.

There are an indentation method and a suction method. Hereinafter, the suction method will be described.

Turning first to the description of the head-side only, the first cylinder, because the air atmospheric pressure volume 20910.4cc is sucked pushed to the second cylinder 19865Cc, ultimate pressure p ₁ than PXV = constant, 20910.4x1 = 19865xp _{1 Thus, p 1 = 20910.4 / 19865 =} 1.052625 kg / cm 2, the difference 0.052632 kg / cm ^2, and composed. The ultimate force is 42.32929 kg as the product of the area, and the total work amount = the ultimate force × ST26 cm / 2 = 550.2807 kg-cm. This volume ratio 24.7 / 26 = 0.95 only moves, and no work is required. Therefore, the replenishment work amount is 550.2807 x 0.05 = 27.514 kg-cm, and this replenishment reach force is 42.32929 x 0.05 = 2.1165 kg. The second cylinder originally sucks and pushes atmospheric pressure 20910.4cc into the third volume 18900c, so the ultimate pressure is 20910.4 / 18900 = 1.10637 kg / cm ² , and the differential pressure with the previous is 1.10637-1.052625 = 0.053745 kg / cm ² The same is true for the following reaching force. The fourth cylinder is not more than the total work amount and is omitted as it is the same as the discharge position. However, for the fourth cylinder, the total work and replenishment amount match. Next, points to keep in mind are described below.
1. The second cylinder volume of the first cylinder is a non-working air movement, and the replenishment work amount is 27.514 kg-cm, which is 0.05, and this is repeated until the third cylinder. The "work" formula is followed, and the discharge pressure is reached with this slight replenishment work total.
2. Supply power must be 617.509kg-cm / s because the total work amount for replenishment in the above table is 1s1 round trip.
3. Since this net supply reaching force also receives initial pressure from the previous cylinder, it starts from zero at the beginning and is directly proportional to the compression distance and reaches the maximum reaching force at the cylinder end.
4). At the cylinder end compression limit (maximum ultimate force) position, the load in the flywheel rotational direction is aligned with this axis, and the cylinder load direction is in a straight line. To start.
5. For the calculation of the trapezoid of the work volume of the fourth cylinder with the same area (see Fig. 4), there should be no problem in terms of characteristics due to the general flywheel effect.

Since the number of cylinder units used is as small as four, the total estimated actual efficiency remains 0.7, and in the case of buoyancy recovery, the distance between the centers is as short as 1.6 m and adjustment is easy, and the levitation speed is 0.4 m / s. Therefore, it was assumed that 0.8x0.75 = 0.6, because the efficiency is 0.8 and the conversion efficiency of the generator is 0.75 to 0.8 (manufacturer).
Note: Because the differential pressure of ST22 is 0.0122 kg / cm ² (equivalent to 12.2 cm of water column), the widened water surface on the top of the aquarium should be managed within +8-2 cm in terms of water column for 1.94 m.

Table 2 Set of 2 cylinders, water depth 1.94m, core 1.6m work load and power calculation (numbers not shown in the table indicate head side, EN stands for work load)
(Cylinder diameter φ320 cross-sectional area, head side 32 ² xπ / 4 = 804.25 cm ² , rod side (32 ² -5.6 ² ) xπ / 4 = 779.62 cm ² , ST is a combination of 26 and 22).

Discharge position: This item is omitted because it matches Table 1.
Calculation input: Since it is 1s1 round trip, 491.4017 + 506.9262 = 998.3279kg-cm / s = 9.9833kg-m / s = 0.097875kw Therefore, the calculation efficiency is 0.6677 / 0.097875 = 6.82 times
Table 3 Cylinder set water depth 1.94m Core 1.6m work load and power calculation (The numbers in the table do not indicate the head side, EN stands for work load)
(Cylinder diameter φ320 cross-sectional area, head side 32 ² xπ / 4 = 804.25 cm ² , rod side (32 ² -5.6 ² ) xπ / 4 = 779.62 cm ² , ST is one of 26).

Discharge position: ST22 discharge pressure is 1.94m to 1.194kg / cm ² , discharge volume: 20910.4 / 1.194 = 17512.9cc compression distance 17512.9 / 804.25 = 21.78cm, so from the compression side
26-21.78 = Discharge starts at a position of 4.22cm. The required work volume is 156.0245 (4.22 / 2 + 21.78) = 3727.4253kg-cm (calculation at the bottom of the above table, others are as shown). Calculation input 1s1 round trip, so 363.12736 + 3727.4253 = 7340.6989 kg-cm / s = 73.407kg-m / s = 0.71968kw Therefore, the calculation efficiency is 0.6677 / 0.71968 = 0.93 times. The stepless input is reduced and the efficiency is improved, but the output is not changed. Tables 1 to 3 are examples of this, and this is true, because compression and buoyancy are not directly related to the insulator link formula, and general energy theory calculations and power calculations are not valid. As shown in the table, compression and buoyancy calculations must be performed separately, and results will not be obtained.
Table 4 Set of 33 lotless cylinders, 48m depth of work and entry / exit power calculation (This table shows an example of calculation method only for theoretical explanation, cylinder diameter φ100 cross section 10 ² xπ / 4 = 78.5398 The following combinations are used for the cm ² trooke, and the compression mechanism calculates 1 bucket 2 reciprocating 2 discharges per 4 buckets (EN is the work load)

(This calculation is for explanation of theoretical calculation ignoring the sliding guarantee speed. If all cylinders are made large and the volume is the same, the sliding speed can be lowered without changing the conditions.)
Discharge position: The discharge pressure of ST26 changes from a water depth of 48 m to an absolute pressure of 5.8 kg / cm ^{2. When} this pressure is reached, discharge of this compressed air starts from the bottom of the water tank. The position is 11781 / 5.8 / 78.5398 = 23.2cm (78.5398 is the cylinder cross section), and the piston starts to discharge from the compression side at the position of 26-23.2 = 2.8cm.
The work required for one discharge in the final ST26 is 2.4347 (2.8 / 2 + 23.2) = 59.8936 kg-cm, and the rest is as described in the above table ().
Calculation output: Water depth discharge volume is 11781 / 5.8 = 2031.2cc, average volume is (2031.2 + 11781) /2=6906.1cc, distributed to 2 buckets, average buoyancy per one is 6.9061 / 2 = 3.453kg, number of effective buckets 482 The total buoyancy can be assumed to be 3.453 x 482 = 1663.37 kg, the levitation speed is 0.4 m / s, and the output is 1663.37 x 0.4 = 665.748 kg-m / s = 6.527 kw.
Supply power: 672.306kg-cm = 6.72306kg-m 2 times / 1s 6.72306x2 = 13.4461kg-m / s = 0.1318kw
Calculation efficiency: Therefore, calculation efficiency reaches 6.527 / 0.1318 = 49.52 times and 50 times.

Table 5 Two cylinders set, 0.9m core depth 0.5m work load and power calculation (for basic data verification )
(Cylinder diameter φ100 cross section rod side (10 ² -2.5 ² ) xπ / 4 = 73.63 cm ² , 10 ² xπ / 4 = 78.54 cm ² , ST is a combination of 16.6 and 15.6, EN in this table is work load ).

Discharge position: Discharge start at 1303.76 / 1.09 / 78.54 = 15.23cm, 15.6-15.23 = 0.37cm, supply NE is 2.03398 x (0.37 / 2 + 15.23) = 31.3538kg-cm
Supply: (31.7536 + 33.8711) = 65.6247kg-cm / s = 0.656247kg-m / s = 6.434w (The purpose of this machine is to verify the theoretical calculation values including the following output).
Output: Discharge volume, rod side 1222.26 / 1.09 = 1121.34cc, average 1171.8cc, buoyancy 1.1718kg, head side 1303.76 / 1.09 = 1196.1cc average 1249.9cc
The buoyancy is 1.249.93kg, the average buoyancy is (1.1718 + 1.24993) / 2, the average buoyancy is 1.2109kg, the number of effective buckets is 6 and it is not divisible by 4, 1.2109-1.1718 =
0.039 maximum 0.039 x 2 = 0.078 kg unbalance occurs, but ignored, total 1.1718 + 1.2499 = 2.4217 kg. Dividing this into 4 buckets equals 2.4217 / 4 = 0.6054 kg, 0.6054 x 6 = 3.6325 kg. It is possible to arrange all the manipulatable range and basic materials, contributing to the high precision design ahead. The output at speed 0.4m / s is 3.6325x0.4 = 1.453kg-m / s = 14.245w, and the calculation efficiency is 14.245 / 6.434 = 2.21 times.

In the case of one cylinder, the output is the same and the power supply is the result shown in the table below.

Discharge position 1303.76 / 1.09 / 78.54 = 15.23cm, discharge starts, 16.6-15.23 = 1.37cm, supply NE is 7.0686 x (1.37 / 2 + 15.23) = 112.4968kg-cm
Supply: Same as above, output is 105.464 + 112.4968 = 217.9608kg-cm / s = 2.1796kg-m / s = 21.3687w, efficiency is 14.245 / 21.3687 = 0.67 times.
Table 7 Load of 13 sets of 13 cylinders, water depth 3.54m core 3.2m work load and power calculation .
Head side 20 ² xπ / 4 = 314.16 cm ² Rod side (20 ² −4 ² ) xπ / 4 = 301.59 cm ^{2 The} numerical values in the table below indicate the head side (EN in this table indicates the amount of work).

Ultimate pressure: Maximum pressure at the end point position required to push into the next cylinder volume. First volume (11938cc) / each next volume = first ST (38cm) / next ST.
Differential pressure: This is the final position pressure difference that is pushed into the cylinder from the pressure pushed in by the previous cylinder, and is calculated by each ultimate pressure minus the previous ultimate pressure.
Maximum load: From the above, it is simply the pressure difference x cross-sectional area (Note that the following EN becomes energy if per unit time, but here is the abbreviation for work).
Necessary EN: Total required work including the gain received from the previous one to push into the next cylinder, calculated with each maximum load xST / 2.
Gain EN: The principle of “all the pressure in the gas is the same”, because the pressure applied to the previous cylinder has the same cross-section, the amount of work required for the front cylinder is always the same gain as the assist gain work through the air between the pistons. This is the theory of the present invention, which is automatically received as gain work at each ST / pre-ST ratio for EN.
Clearing EN: Necessary work amount-The amount of gain received from the front cylinder, which is the amount of work that requires each net replenishment (-minutes contribute to reducing the reduction input to the swing arm).
Achieving force for net supply: Each cylinder end maximum pressing force limited to the amount of work that requires the above net replenishment. Supply power source specifications, including the separate sheet transmission characteristics, are determined based on this and calculated by Clearing ENx2 / ST The Note that 1.354 kg / cm ² of the final cylinder is the discharge pressure, and the required amount of work is the following special calculation .
Basic design policy: The design is 1 reciprocation / 1s, the same mechanism is displaced 180 degrees, 2 units are mounted on both sides of the water tank with a single drive source, and the total of 4 discharges are equally distributed to 4 buckets.
Discharge position calculation: The discharge start position of the final ST28.5 is 11938 / 1.354 (discharge pressure) /314.16 (cross section) = 28.06 cm, 28.5-28.06 = 0.44 cm from the compression side.
Work required for discharge: Therefore, the work EN required for the final cylinder ST28.5 is 6.49274 (0.44 / 2 + 28.06) = 183.6147 kg-cm, and the calculation is as shown in the above table.
Average buoyancy: 11938x301.59 / 314.16 (cross-sectional area ratio) = 11460cc on the atmospheric pressure volume rod side, so the average combined on the head side is (11938 + 11460) / 2 = 11699cc, and the average volume at the discharge part 11699 / 1.354 = 8640cc This average volume is (11699 + 8640) /2=10169.5cc, and the average buoyancy per bucket is 10.17kg with a total of 4 discharges per second.
Recovery power: 34 effective buckets, buoyancy meter 10.17x34 = 345.78kg levitation speed 0.4m / s, output 345.78x0.4 = 138.3kg-m / s = 1.356kw, deceleration conversion efficiency combined 0.6 0.6x1.356 = 0.8136 kw is the estimated net recovery output power.
Supply power: (98.82 + 102.94) x2 = 403.52kg-cm / s = 4.0352kg-m / s = 0.03956kw Assuming that the actual supply efficiency is 0.7, 0.03956 / 0.7 = 0.0565kw.
Input / output power: Based on the above results, supply from commercial motors / generators is 60 w. Output is 400 x 2 = 800 w. Therefore, the estimated actual efficiency is 800/60 = 13.33 times.
Transmission characteristics: About the flywheel transmission characteristics of this compression mechanism,
At the time of continuous operation, pay attention to the fact that the flywheel transmission characteristic is that the required torque flagwheel shaft is fully loaded and the prime mover load is zero at the maximum reached position of the net supply. In fact, it is still reduced.
Preparation for operation: After filling the tank with the required amount of water, fill the appropriate amount of air in all the vertical buckets on the outlet (no generator load).
・ The drive source of this equipment is equipped with a brake, and there is a margin of about 1/3 of the bucket capacity. At the scale of this equipment, it starts because it can supply 15 kg of buoyancy to the bottom bucket. Braking control of the attached electromagnetic clutch / bucket single feed sensor and the cylinder end sensor to brake the drive source, and repeating this a little extra regardless of the levitation speed, all are almost averaged at a fixed predetermined amount .
-The above control is an intermittent feed of two buckets except for the first discharge because the compression mechanism of this equipment is almost continuous and equally divided into two buckets in one cylinder path.
-However, if the center distance of the bucket becomes large and it does not start with only one, adjust the stop position and apply the discharged air to the edge of the bucket to distribute it to double the buoyancy.
Note: When two sets of compressors are installed and discharged every 180 degrees, a 90-degree phase displacement seems to be common, but the other is the maximum at the middle position, and the maximum result is the net supply above. The force is 1.5 times the force, whereas the 180 degree displacement is zero for the prime mover torque at both ends due to the transmission characteristics. However, in the future commercialization and sales promotion where the average 180 degree displacement at both ends is optimal, this supply can demonstrate the net recovery power of 800w at 60w, and the efficiency will be doubled.

Table 8 Two sets of four cylinders mounted, water depth 1.34m, core 1m work load and power calculation (cylinder diameter φ140 cross section rod side (14 ² -4 ² ) xπ / 4 = 141.372cm ² , 14 ² xπ / 4 = 153.938 cm ² , stroke is 16.6 to 24 below combination).

Basic policy: The design is 1 reciprocation / 1s, the same two compression mechanisms are displaced 180 degrees, and a single drive source is installed on both sides of the water tank.
Discharge position: Discharge position of ST14.8 2555.4 / 1.134 / 153.938 = 14.64cm, so the discharge starts at 14.8-14.64 = 0.16cm from the compression side, this value is seemingly small, but the difference from the discharge pressure 1.134-1.123784 = 0.0102 It corresponds to 10.2 cm in terms of water column difference at kg / cm ² , and the water level can be controlled by measures to widen the upper surface of the water tank. It does not enter the final cylinder and does not pass through (see Fig. 4) and functions safely.
Discharge work: Supply EN of final cylinder is 1.905506x (0.16 / 2 + 14.64) = 28.049kg-cm (otherwise calculation is as shown)
Calculated supply: 33.6657 + 30.9146 = 64.58326kg-cm / s = 0.65483kgm / s, 0.65483x2 = 1.30966 kgm / s = 0.01284kw = 12.84w
Calculated output: Water tank atmospheric pressure side (2555.4 + 2346.8) /2=2451.1cc, precisely the depth of the position received from the lower bucket from the discharge is 1.18m, this average volume is 2451.1 / 1.118 = 2192.4cc1 bucket average Buoyancy is (2.4511 + 2.1924) /2=2.322kg Number of effective buckets 12 Total buoyancy 2.322x12 = 27.86kg Lifting speed 0.4m / s Output 27.86x0.4 = 11.144kg-m / s = 0.10925kw = 109.25w It is.
Actual efficiency: supply 12.84 / 0.7 = 18.34w, output 109.25x0.6 = 65.55w, from this result, generally 25w from the commercial motor, 65w generator, actual efficiency 65/25 = 2.6 times It becomes.
Transmission characteristics: Considering the reaction force from the swing arm at both ends of the compression limit and the fact that the flywheel shaft is responsible for all of it and the motor is not loaded, the motor can be 6w and the actual efficiency is 65/6 = 10.83 times.

Table 9 Compressed air return type generator cylinder suction system (Figure 11 is arranged and arranged)
Work load and entry / exit power calculation for the 4-cylinder set (numbers not classified in the table indicate the head side, EN stands for work load)
(Cylinder diameter φ320 cross-sectional area, head side 32 ² xπ / 4 = 804.25 cm ² , rod side (32 ² -5.6 ² ) xπ / 4 = 779.62 cm ² , ST is a combination of 26 to 22).

Basic policy and explanation
1. The premise of this design is to switch between 1 reciprocation / 1 s 2 times without using a water tank (all of the calculation methods in this section adopt the suction method).
2. The most downstream cylinder unit is exclusively for output, not connected to the swing arm, and constant speed is ensured by the generator flywheel.
3. Even in this case, the # 4 cylinder can be sucked by the # 1 cylinder, and the # 4 cylinder can suck the # 3 cylinder with the same suction force as the swing arm combination.
4. The suction effect of the # 1 cylinder from the # 4 cylinder begins with a pressure of 1.181818 kg / cm ² unlike the atmospheric pressure suction, and the phenomenon of returning to 1 at the end point is correct, but the maximum and necessary places where force is unnecessary It returns to 1, and the triangular part of the ultimate pressure of 40.21kg is irrelevant to no-work air movement, but it has the effect of assisting the necessary work up to the intersection A. The upper part beyond this is restricted by the swing arm Since there was no increase in speed, it was a wasteful force that was not regenerated as power. The work requiring replenishment was assisted, and the area ratio after intersection A to all triangles was 0.39, which was calculated in the lower part of the above table # 1 cylinder.
5. As a result, the external output power of the # 4 cylinder is 2549.635 kg-cm on the head side and the replenishment is 82.1297 kg-cm, so the calculation efficiency is 2549.635 / 82.1297 = 31.03 times.
6. This is because the output in 1s cycle is 2549.635 + 2549.635 × 779.62 / 804.25 (cross-sectional area ratio) = 5021.2kg-cm / s = 50.212 kg-m / s = 492w supply is 79.6145 + 82.1297 = 161.744kg -cm / s = 1.6174 kg-m / s = 15.868w.
7. The above calculation is performed by the “suction method”, and this non-working air movement effect is proved to be extremely high.

Table 10 shows the results of the compressed air recursive generator cylinder suction method.

Calculation of work and entry / exit power of 2 cylinders set (Numerical values not shown in the table indicate head side, EN stands for work)
(Cylinder diameter φ320 cross-sectional area, head side 32 ² xπ / 4 = 804.25 cm ² , rod side (32 ² -5.6 ² ) xπ / 4 = 779.62 cm ² , ST is a combination of 26 and 22).

Basic policy and explanation
1. The premise of this design is to switch between 1 reciprocation / 1 s 2 times without using a water tank (all the calculation methods in this section adopt the suction method in Fig. 4-13).
2. The most downstream cylinder rod is for output only, not connected to the swing arm, constant speed is secured by the generator flywheel, and the same mechanism can be used on the supply side.
3. Even in this case, the # 4 cylinder can be sucked by the # 1 cylinder, and the # 4 cylinder can suck the # 3 cylinder with the same suction force as the swing arm combination.
4. The suction effect of the # 1 cylinder from the # 4 cylinder begins with a pressure of 1.181818 kg / cm ² unlike the atmospheric pressure suction, and the phenomenon of returning to 1 at the end point is correct, but the maximum and necessary places where force is unnecessary Return to 1. The triangular portion of the ultimate pressure of 123.71kg is irrelevant to no-work air movement, but has the effect of assisting the necessary work up to the intersection A. Since the upper part beyond this is the swinging arm restraint, there is no increase in speed. As for the work requiring replenishment that would not be regenerated, the area ratio after the intersection A with respect to all triangles with the assisting 22.52 was 0.73, and this was calculated in the lower part of the # 1 cylinder in the above table.
5. As a result, the external output power of the # 4 cylinder is 1608.519 kg-cm on the head side and the replenishment is 213.71 kg-cm, so the calculation efficiency is 1608.519 / 213.71 = 7.53 times.
6. This is because the output in 1s cycle is 1608.519 (1 + 779.62 / 804.25 (cross-sectional area ratio) = 3167.8kg-cm / s = 31.678 kg-m / s = 310.57w, supply is 213.71x
(1 + 779.62 / 804.25) = 420.88kg-cm / s = 4.2088 kg-m / s = 41.263w.
・ The above calculation is performed by the “suction method”, and this non-working air movement effect is proved to be extremely high.
8. The case of one cylinder is also shown for reference.

Table 11 Two cylinders set depth 0.911m core 0.5m work load and power calculation (for basic data verification)
(W rod cylinder diameter φ100 cross section (10 ² -2.5 ² ) xπ / 4 = 73.63 cm ² , ST is 16.6 and 15.6 in combination)

Discharge position: 1222.26 / 1.0911 / 73.63 = 15.21cm, discharge starts, 15.6-15.21 = 0.39cm, supply NE is 1.988782 x (0.39 / 2 + 15.21) = 30.62237kg-cm
Supply: 32.9826x2 = 65.9652kg-cm / s = 0.659652kg-m / s = 6.467w (The purpose of this device is to verify the theoretical calculation including the following output).
Output: Discharge volume, 1222.26 / 1.0911 = 1120.21cc, the average is (1222.26 + 1120.21) /2=1171.24cc, this discharge 2 times / 1s because the levitation speed is 0.4m / s, it is 1172.24x2 / 4 = 586.12cc, the average buoyancy is 0.5861kg, and the number of effective buckets is 6, so the total is 0.586x6 = 3.516kg, and the experiment verification work can arrange all the basic materials other than the theory that can be handled manually, Contributes to high precision design ahead. The output at a speed of 0.4 m / s is 3.516x0.4 = 1.2606kg-m / s = 12.359w, and the calculation efficiency is 12.359 / 6.467 = 1.91 times.

場合 If this is executed with one cylinder, the output will be the same and the power supply will be as shown in the table below.

Discharge position: Discharge starts at 1222.26 / 1.0911 / 73.63 = 15.21cm, 16.6-15.21 = 1.39cm, supply NE is 6.70769 x (1.39 / 2 + 15.21) = 106.68581kg-cm
Supply output: Same as above, output is 106.6858x2 = 213.3716kg-cm / s = 2.1337kg-m / s = 20.9186w, efficiency is 12.359 / 20.9186 = 0.59 times.

Table 13 Calculation of work load and power in / out of cylinder 2 set (1 prototype)
Cylinder diameter φ100 cross section Head side 78.54 cm ² , Rod side (10 ² -2.5 ² ) xπ / 4 = 73.63 cm ² , ST is 16.6 and 15.6 in combination.

Calculate the work in and out at 1 cycle / s.
Total supply: 20.8936 + 19.5874 = 40.481kg-cm / s = 0.40481kg-m / s = 3.9687w (The purpose of this device is to verify the theoretical calculation values including the following output).
Total output: 76.085 kg-cm / s = 0.60885 kg-m / s = 7.4593w, the calculation efficiency is 7.4593 / 3.9687 = 1.88 times. However, since this prototype does not have a generator-side flywheel, it does not seem to have an averaging effect .

Verification experiment procedure The verification experiment is performed with two cylinders, and the second output is not connected to the swing arm, and the output varies from 0 to 2.505 kg.
When this output is measured at the output cylinder position for each rotation angle of the flywheel, it becomes 2.349 kg on the head side and 2.349 kg on the rod side (specifically, the cylinder is measured by shaking sideways with M6 bolts for rod block mounting together with FB etc.) Hang the string so that it does not hit the ball and hang the weight through the pulley).

This measurement is simple, but it is an extremely important foundation consolidation experiment that can be used to confirm the grasp of the phenomenon while taking the actual efficiency out of the range of estimation so far.

This verification experiment apparatus does not use a generator. Therefore, since there is no generator-side flywheel, the output load averaging continuous operation can be performed. However, using a constant torque reduction motor 25w2000rpm, 240 / 7.5 = 32rpm at 2000x3 / 25 = 240rpm (3w) Sprocket acceleration 32 x 32/17 (number of mounted sprocket teeth) = 60.23 rpm (practical device does not exceed 60 rpm), continuous operation experiment, vibration noise, check valve cracking countermeasure effect, low sliding resistance grease, LM guide effect Measure bodily feelings
If this motor rotation speed is set to 160 rpm, it becomes 2 w, but rotation below 100 rpm is unstable and impossible.

Table 14 Calculation of workload and power in and out of two cylinders, single drive system (prototype for basic data verification)
Cylinder diameter φ100 cross section Head side 78.54 cm ² , Rod side (10 ² -2.5 ² ) xπ / 4 = 73.63 cm ² , ST is 16.6 and 15.6 in combination.

The basics of this case are the push-in method. Output from the # 2 cylinder is equivalent to the gain equivalent when there are multiple push-in cylinders of the # 1 cylinder. To calculate.
Total supply: 41.7873 + 39.1749 = 80.9622kg-cm / s = 0.809622kg-m / s = 7.9375w (The purpose of this device is to verify the theoretical calculation including the following output).
Total output: 39.27 + 36.815 (cross-sectional area ratio) = 76.085 kg-cm / s = 0.60885 kg-m / s = 7.459w, calculation efficiency is 7.594 / 7.9375 = 0.94 times.

Verification experiment procedure The verification experiment is with two cylinders, the second one is exclusively for output and is not coupled to the swing arm, so the external output varies from 0 to 5.0346 kg as it is.
When this output is measured at the output cylinder position for each rotation angle of the flywheel, the maximum value is 5.0346 kg on the head side and 4.7199 kg on the rod side. Hang so that the kite does not hit, and hang the weight through the pulley.

Specifically, the calculated values of the weight of each spindle at 15 ° rotation angle and the flywheel outer circumference tangential force are shown.
Although this measurement is simple, it is an extremely important foundation consolidation experiment that can be used to confirm the grasp of the phenomenon while taking the actual efficiency out of the range of estimation so far.
This verification test device does not use a generator, and therefore there is no generator-side flywheel. Therefore, unlike actual motors, continuous operation that averages the output load is not possible. Using 25w2000rpm, 240 / 7.5 (gear reduction ratio) at 2000x3 / 25 = 240rpm (3w) = 32rpm This is sprocket speed increase 32x32 / 17 (number of mounted sprocket teeth) = 60.23ppm (Practical equipment does not exceed 60rpm) Thus, the ball valve valve is subjected to a continuous operation experiment instead of the check valve, and sensation measurement such as vibration noise, check valve cracking countermeasure effect, low sliding resistance grease and LM guide effect is measured.

If this motor speed is set to 160 rpm, it becomes 2 w, but rotation below 100 rpm becomes unstable and experiment below this is impossible.

In the above-described embodiments, the case where the air compression device according to the present invention is applied to a power generation device has been described. However, the present invention is not limited to such an embodiment, and an ordinary compressor supplies air into water (explosion). It can be used as a compressor for various fields.
While various preferred embodiments of the present invention have been described, it is to be understood that the present invention is not limited to these embodiments and that various modifications and changes can be made to these embodiments.

Claims (11)

1. A plurality of cylinder units each having a cylinder and a piston;
   A piston drive mechanism coupled to each piston of the plurality of cylinder units,
   Each cylinder of the plurality of cylinder units has a cylinder hole of a predetermined length, and each piston forms a first space on one side in the longitudinal direction of the cylinder hole and a second on the other side. Arranged to reciprocate in the cylinder hole to form a space;
   The piston drive mechanism is configured to drive each piston simultaneously in a cylinder,
   The plurality of cylinder units are sequentially connected from the most upstream cylinder unit located at the most upstream and communicating with the atmosphere to the most downstream cylinder unit located at the most downstream and communicating with the supply unit, and are connected to the upstream side. Connected to each other so that one space communicates with a second space of the cylinder unit located on the downstream side,
   The air compression device in which the volumes of the plurality of cylinder units are set so as to gradually decrease from the most upstream cylinder unit to the most downstream cylinder unit.
2. The plurality of cylinder units have the same cross-sectional area in the direction perpendicular to the longitudinal direction of the cylinder, but are formed such that the lengths of the cylinders are different from each other. The air compression device according to claim 1, wherein the air compression device is formed to be short.
3. The air compression device according to claim 1, wherein the plurality of cylinder units are arranged so as to be parallel to each other, and each piston is coupled along a longitudinal direction of the arm.
4. The air compression device according to claim 1, wherein the piston drive mechanism includes an arm connected to the piston of each cylinder unit and provided slidably and an arm drive mechanism that swings the arm.
5. A rotating mechanism for rotating the generator;
   The air compression device according to claim 1, wherein the rotation mechanism is activated.
   The rotating mechanism includes a water tank filled with water,
   A plurality of buckets arranged in the water of the aquarium and capable of containing air;
   A bucket moving mechanism that movably supports the plurality of buckets,
   The drive device for a generator, wherein the air compressor is configured to supply compressed air into the water in the water tank so as to direct the plurality of buckets by buoyancy.
6. 6. The drive device according to claim 5, wherein the adjacent buckets are arranged so as to overlap each other so that a part of the other bucket is located in an opening portion of the predetermined bucket around the rotation mechanism.
7. A drive device according to claim 5;
   And a generator driven by the driving device.
8. A rotation conversion mechanism for rotating the generator;
   The air compression device according to claim 1, wherein the rotation conversion mechanism is activated.
   The rotation conversion mechanism is connected to the piston of the most downstream cylinder unit of the air compressor, and converts the reciprocating motion of the piston into a rotational motion to rotate the generator. .
9. A drive device according to claim 8;
   And a generator rotated by the driving device.
10. A plurality of cylinder units each having a cylinder of a predetermined length and a piston that divides the inside of the hole of the cylinder in the longitudinal direction into one end side space and the other end side space and reciprocates in the cylinder hole; A drive device having an arm that reciprocally drives the pistons of the cylinder simultaneously at the same cycle, and
    The plurality of cylinders are connected so that a space in the predetermined cylinder located on the upstream side communicates with a space in the other cylinder located on the downstream side, and the volume in the cylinder on the downstream side is Formed smaller than the volume in the upstream cylinder,
    When the pistons of the cylinders simultaneously move to one end side of the cylinders, the air in the one end side space of the upstream cylinder flows into the other end side space of the downstream cylinder, When the pistons of the cylinders simultaneously move to the other end side of the cylinders, the air in the other end side space of the upstream cylinder flows into the one end side space of the downstream cylinder. Air compression method.
11. A driving method using air compressed by the air compression method according to claim 10, wherein the rotating mechanism is installed in water and rotates in an upward direction and a downward direction, and the rotating mechanism. And a plurality of buckets equipped with the opening facing downward when moving in the upward direction, and with the opening facing upward when moving downward, The air compressed by the air compression method is discharged from the inner space of the cylinder arranged at the most downstream position into the bucket with the opening directed downward at the lower position of the rotating mechanism, and into the bucket. A rotation driving method in which the rotating mechanism is rotated by buoyancy of accumulated air.
    

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