KR20020074353A - An engine used oil pressure - Google Patents

Abstract

PURPOSE: An engine using hydraulic pressure is provided to drive a vehicle by generating compressed air by the hydraulic pressure, generating compressed hydraulic pressure by combustion gas and using the compressed hydraulic pressure. CONSTITUTION: An engine using hydraulic pressure is composed of a fluid storing tank(100), a compressed air generating unit(200), a fuel supply unit(300), a burning unit(400) for burning the fuel supplied from the fuel supply unit(300), a wheel driving unit(500) for rotating a drive rotary shaft(900), a compressed fluid generating unit(600), and a hydraulic pressure storing unit(800) for storing the compressed fluid and supplying the compressed air to the compressed air generating unit(200). The compressed air generating unit(200) generates the compressed air and returns the fluid used for generating the compressed air to the fluid storing tank(100).

Description

Hydraulic Engine {AN ENGINE USED OIL PRESSURE}

The present invention relates to an engine using hydraulic pressure, and more particularly, to generate compressed air using hydraulic pressure, and to pressurize the hydraulic pressure under pressure using compressed combustion gas generated by burning the compressed air and fuel together. The present invention relates to an engine using oil pressure that enables the driving of a vehicle by rotating the drive shaft of the wheel in the forward and reverse directions by using the oil pressure in the pressurized state.

In general, an engine refers to an engine that converts thermal energy, electrical energy, potential energy, and the like into mechanical energy to perform work, and among them, a thermal engine using thermal energy is most commonly commercialized.

The heat engine may be divided into an external combustion engine and an internal combustion engine, and among them, an internal combustion engine may be further divided into a gasoline engine and a diesel engine.

The above-described gasoline engine and diesel engine have a four-stroke cycle of intake, compression, explosion, and exhaust, and the connecting rod and the crankshaft are interlocked to operate the wheels of the vehicle and the like.

However, the above-described conventional engines have the following problems.

First, the crankshaft, which converts the reciprocating operation of the piston from the straight line into rotational movement, is the most essential component of gasoline and diesel engines, and must be very complex and require precision, high strength, and durability. The crankshaft has a disadvantage in that it takes up a lot of weight and volume ratio in the engine.

Secondly, the compression ratio and the expansion ratio of the engine are inevitably fixed due to the characteristics of the fixed crankshaft. For an engine having such a fixed compression ratio and the expansion ratio, load adaptability according to the output load fluctuation of the engine is achieved only by adjusting the speed of the engine. Therefore, there is a problem that a separate transmission is required for an automobile engine.

Third, the engine with the rotational force on the crankshaft increases the fuel consumption rate of the engine because the engine can not store the surplus rotational energy of the engine.

Therefore, there is a problem in that the development of an engine of a different method in which the generator and the battery and the driving motor in parallel with the engine is required.

Fourth, there is an unavoidable problem that a separate proper lubrication system is inevitable in the piston ring, crankshaft and valve system of the engine.

Fifth, since the engine of the mechanical mechanism can not store energy, a starter motor that starts the engine by charging electric energy to the battery and then starting a separate motor should be essential.

Sixth, since the maximum torque of the engine is fixed, an expensive transmission should be essential.

Seventh, the engine which consists of four strokes of intake, compression, explosion and exhaust by the crankshaft, the opening and closing timing of the intake valve and exhaust valve and the fuel Precision is required, such as the timing of explosions must be very accurate.

Eighth, since gasoline engines and diesel engines obtain rotational power by explosive power when fuel is combusted, about 30% of the combustion heat source of the fuel is lost by the engine's cooling heat, and about 30% by high temperature exhaust gas emission. The heat loss is made, there is a huge problem of heat loss of the engine.

The present invention was devised to solve the above problems, and generates a compressed air by using the hydraulic pressure, and pressurized hydraulic pressure using the compressed combustion gas generated by burning the compressed air and fuel together The purpose of the present invention is to provide an engine using hydraulic pressure that enables driving of a vehicle by rotating a drive shaft such as a wheel in a forward and reverse direction by using the hydraulic pressure in the pressurized state.

1 is a view showing the overall configuration of an engine using hydraulic pressure according to the present invention.

2 and 3 are views showing the operating state of the compressed air generating means according to the present invention.

4 and 5 are views showing the operating state of the pressurized fluid generating means according to the present invention.

6 is a view showing the configuration of a fuel supply means and a combustion means according to the present invention.

7 to 10 is a view showing the configuration of the wheel drive means and the operating state thereof according to the present invention.

11 is a view showing a preferred connection relationship between the piston rod constituting the compressed air generator and the first and second pistons in the configuration of the compressed air generating means according to the present invention.

12 is an exploded perspective view of the main portion of the wheel drive means according to the present invention.

Figure 13 is a side longitudinal sectional view of the wheel drive means according to the present invention.

<Description of the symbols for the main parts of the drawings>

100: fluid storage tank 200: compressed air generating means

220: compressed air generator 201: cylinder body

202,203: Left and right discharge port 204,205: Left and right balance port

206,207 Common port 208 Piston rod

209,210: first piston 211,212: second piston

213: load guide 213a: guide

214,215: Communication port 216,217: Left and right cover

218,219,218a, 219a: Check valve for air inlet / outlet

240: first controller 221: direction switching valve body

222,223 Common port 224 Inflow port

225,226: Drain port 227: Outflow port for direction change

230: direction switching valve body 232: cover

270: second controller 241: control valve body

242,243,244,245,246: first, second, third, fourth, fifth space part

247,248,249,250: first, second, third and fourth partition walls

251,252,253,254: 1st, 2nd, 3rd, 4th slide ball

255: Square switch discharge port 256,257,258,259: Connection port

261,262: inlet port 263: first control valve body

264: first slide member 265: second control valve body

266: second slide member 219a, 219b: cylinder liner

300: fuel supply means 400: combustion means

401: fuel injection nozzle 402: inner cylinder

402a: air inlet 403: ignition means

404: outer cylinder 404a: air inlet

404b: exhaust port 500: wheel drive means

501: driving body 502: cylindrical body

503: cylindrical roller 504: rotary rotor

504a: roller guide groove 504b: fluid movement path

504c: fluid supply path 510: shift means

511: transmission body 511a: partition wall

512: shifting plunger 512a: piston

513,514 branch pipe 515 pressure reducing valve

516: reversing valve 600: pressurized fluid generating means

610: pressurized fluid generator 611: cylinder body

612,613: Left and right fluid discharge port 614,615: Left and right balance port

616,617: fluid inlet port 618,619: fluid outlet port

620: piston rod 621, 622: first piston

623,6324: second piston 625: rod guide

625a: Rod guide 626,627,628,629,630,631: Communication port

632,633: Left and right cover634,635,636,637: Check valve for fluid inlet / outlet

640,640 ': Combustion gas alternating feeder641,641': Left and right directional valve body

642,642 ': Combustion gas first inlet port 363,643': Combustion gas discharge port

644,644 ': First exhaust port645, 645': Combustion gas exhaust port

646,646 ': fluid inlet port 647,647': fluid outlet port

650,650 ': Left and right directional valve body 670: Controller

671: valve body for control

672,673,674,675,676: 1st, 2nd, 3rd, 4th, 5th space

680,681,682,683: 1st, 2nd, 3rd, 4th partition wall

680a, 681a, 682a, 683a: 1st, 2nd, 3rd, 4th slide ball

681b: Directional discharge port 685,686,687,688: Connection port

690,691 Inflow port 692 First control valve body

693: first slide member 695: second control valve body

696: second slide member 700: cooling tank

710: first turbocharger 711, 713: first, third inlet

712,714: 2nd, 4th outlet 715: coaxial

716,717: first and second fan 720: second turbocharger

721,723: 1st, 3rd inlet 722,724: 2nd, 4th outlet

725: same axis 726,727: third and fourth fans

730, 750: pump 740: heat exchanger

900a: Fly Wheels

The engine using the hydraulic pressure according to the present invention for achieving the above object, the fluid is stored, the fluid storage tank capable of entering and exiting; Compressed air generating means for receiving and supplying pressurized fluid to generate and discharge the air introduced from the outside in a compressed state, and to feed back the fluid used to generate the compressed air to the fluid storage tank; Fuel supply means for supplying fuel; Combustion means for combusting the fuel supplied from the fuel supply means with compressed air generated by the compressed air generating means; Wheel drive means for rotating the drive rotation shaft of the wheel in the forward and reverse directions depending on whether the pressurized fluid is supplied; The compressed combustion gas generated by the combustion means is supplied to generate a pressurized fluid transferred from the fluid storage tank in a pressurized fluid state to discharge a part of the fluid to the wheel driving means, and discharge the supplied and used combustion gas. Pressurized fluid generating means; Receiving and storing the remaining compressed fluid generated from the pressurized fluid generating means, characterized in that it comprises a pressure storage means for releasing a portion of the pressurized fluid to the compressed air generating means.

Hereinafter, a preferred embodiment of the engine using the hydraulic pressure according to the present invention will be described in detail with reference to the accompanying drawings.

1 is a view showing the overall configuration of the engine using the hydraulic pressure according to the present invention, Figures 2 and 3 is a view showing the operating state of the compressed air generating means according to the present invention, Figures 4 and 5 according to the present invention Figure 6 is a view showing the operating state of the pressurized fluid generating means, Figure 6 is a view showing the configuration of the fuel supply means and the combustion means according to the present invention, Figures 7 to 10 are the configuration and operation of the wheel drive means according to the present invention 11 is a view showing a preferred connection relationship between the piston rod constituting the compressed air generator and the first and second pistons among the components of the compressed air generating means according to the present invention, and FIG. Fig. 13 is a side sectional view of the wheel drive means according to the present invention in an exploded perspective view.

As shown, the engine according to the present invention includes a fluid storage tank 100, compressed air generating means 200, fuel supply means 300, combustion means 400, and wheel drive means 500. And a pressurized fluid generating means 600 and a pressure storing means 800.

The accumulator means 800 is a function of releasing the stored fluid at a high pressure due to the injection of nitrogen gas while storing the fluid at ordinary times as well as a function of receiving and storing the fluid from the outside again. In general, the industrial application.

The fluid storage tank 100 is a fluid is stored, it is configured to be able to flow in and out.

The compressed air generating means 200 receives the pressurized fluid, generates and discharges the air introduced from the outside in a compressed state, and feeds back the fluid used to generate the compressed air to the fluid storage tank 100. Do it.

The combustion means 400 serves to combust the fuel supplied from the fuel supply means 300 with the compressed air generated by the compressed air generating means 200.

The wheel driving means 500 rotates the driving rotary shaft 900 of the wheel in the forward and reverse directions depending on whether the fluid is supplied, and the fly wheel 900a is rotated together with the driving rotary shaft of the wheel driving means 500. do.

The pressurized fluid generating means 600 receives the compressed combustion gas generated by the combustion means 400, generates a fluid introduced from the fluid storage tank 100 in a pressurized state, and generates a part of the wheel driving means. Emission to 500, and serves to discharge the previously used combustion gas.

The accumulator means 800 receives and stores the remaining pressurized fluid generated from the pressurized fluid generating means 600 and discharges a part of the stored pressurized fluid to the compressed air generating means 200. .

The compressed air generating unit 200 is compressed from the compressed air generator 220 by receiving a compressed air generator 220 for generating compressed air in both directions and a pressurized fluid discharged from the accumulating means 800. And a second controller 270 for controlling the operation of the first controller 240 according to the operation of the compressed air generator 220. .

2 and 3, the compressed air generator 220 described above includes a cylinder body 201, a piston rod 208, a first piston 209, 210, and a second piston ( 211) 212, a rod guide 213, left and right covers 216 and 217, and check valves 218 (218a) 219 and 219a for air inlet / outlet.

The cylinder body 201 includes a pair of left and right discharge ports 202 and 203 spaced apart by a predetermined distance, and left and right balance ports 204 and 205 spaced apart from each other between the left and right discharge ports 202 and 203. The common ports 206 and 207 are spaced apart from each other to correspond to the left and right balance ports 204 and 205 to serve as inflow and outflow, and are formed in the shape of openings at both ends of which are empty.

The piston rod 208 is moved left and right in the longitudinal direction inside the cylinder body 201.

The first pistons 209 and 210 are formed to have a predetermined gap with the inner wall surface of the cylinder body 201, and are formed to be stepped with the piston rod 208 and provided at both ends of the piston rod 208, respectively. do.

The second pistons 211 and 212 are in close contact with the inner surface of the cylinder body 201 and are slidably installed, and are formed to be stepped with the first pistons 209 and 210 so that the first pistons 209 are provided. Each end of 210 is provided.

The rod guide 213 is disposed on an inner wall surface of the cylinder body 201 corresponding to the left and right discharge ports 202 and 203, and an inner surface thereof is an outer surface of the first piston 209 and 210. A guide portion 213a which is in intimate contact and protrudes on the inner surface to guide the piston rod 208 left and right in intimate contact with the outer surface of the piston rod 208, and the left and right balance ports 204 and 205. ) And communication ports 214, 215, 214a and 215a in communication with the common ports 206 and 207.

The left and right covers 216 and 217 are installed at both ends of the cylinder body 201.

The air inlet / outlet check valves 218, 218a, 219, and 219a are respectively provided in pairs on the left and right covers 216 and 217 so that the second pistons 211 and 212 and the cylinder body are provided. Two left and right spaces S1 and S2 formed between both ends of the 201 allow inflow and outflow of air.

On the other hand, the first controller 240 includes a direction switching valve body 221, a direction switching valve body 230, and a cover 232.

The direction switching valve body 221 is a common port (222, 223) that serves as the inlet / outlet of the fluid with the compressed air generator 220, and the pressurized fluid of the pressure storage means 800 is discharged and introduced A single inlet port 224, two drain ports 225 and 226 formed with the inlet port 224 in the middle and connected to the fluid storage tank 100 shown in FIG. It has a flow-out port 227 for the inside, and is formed in the shape of the opening of both ends which is empty inside.

The direction switching valve body 230 is provided by an elastic spring 232a supported by the cover 232 in the direction switching valve body 221 in accordance with the presence or absence of fluid inflow into the direction switching inlet / outlet port 227. The inlet port 224 communicates with any one of the two common ports 222 and 223 while elastically sliding in the left and right directions, and the remaining common ports of the two drain ports 225 and 226. Communicate with either.

The cover 232 is installed at one end of the direction switching valve body 221.

The reference numeral 235 denotes an impact buffer space portion formed on the stepped portion 221a formed on the inner side of the direction switching valve body 230 when the direction switching valve body 230 moves by the elastic spring 232a from side to side ( When entering into S) serves to prevent the rapid movement of the direction switching valve body 230.

The second controller 270 includes a control valve body 241, a first control valve body 263, a first slide member 264, a second control valve body 265, and a second slide. Member 266.

The control valve body 241 includes five first, second, third, fourth, and fifth space parts 242 (243) (244) (245) (246), which are sequentially divided and partitioned; A first slide hole 251 formed through the first partition wall 247 partitioning the first space part 242 and the second space part 243, the second space part 243 and the third space part; A second slide hole 252 formed through the second partition wall 248 that partitions 244, and branches from the second slide hole 252 to the second partition wall 248 so that the first controller ( To the discharge port 255 for changing the direction so that the fluid can flow into and out of the 240 and the third partition wall 249 partitioning the third space portion 244 and the fourth space portion 245. A fourth slide hole 254 formed through the third slide hole 253 formed therethrough, a fourth slide hole 254 formed through the fourth partition wall 250 dividing the fourth space portion 245 and the fifth space portion 246, and Each of the first space portion 242 and the fifth space portion 246 is connected to the compressed air generator 220. Four connection ports 256, 257, 259 and 258 for communication, and an inlet port 261 through which some pressurized fluid of the accumulating means 800 is discharged and introduced into the second space 243. And a drain port 262 for draining the fluid in the fourth space 245 to the fluid storage tank 100 shown in FIG. 1 to control the valve for directional change.

The first control valve body 263 is installed in the first slide hole 251 so as to be able to slide in close and right directions so as to open and close the second slide hole 252, and the discharge port 255 for changing the direction. ) Serves to control the communication between the inlet port 261.

The first slide member 264 is installed in the first space 242 so as to be elastically intimately slidable through the elastic spring 268, and the first control valve body 263 It is fixed at one end.

The second control valve body 265 is installed in the third and fourth slides 244 and 245 so as to be slidably moved from side to side to switch the direction while opening and closing the third slide hole 253. It serves to control the communication between the discharge port 255 and the inlet port 262.

The second slide member 266 is installed in the fifth space 246 so as to be elastically intimately slidable through the elastic spring 258a, and the second control valve body 265 It is fixed at one end.

Here, the cylinder liners 219b and 219a are further interposed between the second pistons 211 and 212 and the cylinder body 201, and end portions of the cylinder liners 219b and 219a and the rod guides. A gap between the end portions of the sieve 213 may be maintained to allow the fluid to be discharged to the left and right discharge ports 202 and 203.

Meanwhile, as shown in FIG. 11, the second pistons 211 and 212 have partition walls 211c for dividing the interior into first and second spaces S1 and S2. The openings of the second pistons 211 and 212 corresponding to 216 and 217 are provided with a closing member 211b for closing the first space S1 in a vacuum state, and the first piston 209. The 210 is formed in a cylindrical shape having an empty inside and is coupled to one end of the second piston 211 and 212 so as to communicate with the second space S2, and the piston rod 208 has an empty inside. It is formed in a cylindrical shape that is coupled to the second piston 209, 210, the partition wall 211c and the piston rod 208 is provided with a check valve (211a) (208a), respectively, the first Pistons 211 and 212 are formed with communication holes 211d communicating with inner wall surfaces of the cylinder liners 219b and 219a.

Here, the drawing shown in FIG. 11 illustrates the one located on the left side of the first and second pistons shown in FIGS. 2 and 3 for convenience.

Referring to the operation of the first and second piston shown in FIG. 11 as follows.

When the piston rod 208 reciprocates from side to side as described above, the fluid between the piston rod 208 between the cylinder liner 219b flows in the direction of the arrow (a) and then the second piston 211 and the cylinder liner After moving to the gap between 219b, a predetermined amount of pressurized fluid is intentionally leaked into the second piston ring 211e of the second piston 211 to be utilized as a lubricating action on the first piston ring 211f. After the fluid is discharged to the communication port (211d) formed in the piston 211 and the drain port (211h) of the oil ring (211g) flows in the direction of the arrow (b), and then filled in the second space (S2), After flowing in the direction of the arrow c, it returns to the space between the piston rod 208 and the cylinder liner 219b through the check valve 208a.

Therefore, according to the fluid flow path as described above, the supply of fluid having a lubricating component according to the contact between the cylinder liner 219b and the second piston 211 according to the reciprocating motion of the piston rod 208, respectively, Lubrication can be performed to the second piston rings 211e and 211f.

On the other hand, the combustion means 400 includes a fuel injection nozzle 401, an inner cylinder 402, an ignition means 403, and an outer cylinder 404.

The fuel injection nozzle 401 serves to spray the fuel supplied from the fuel supply means 300 into an atomized state.

The inner cylinder 402 surrounds the fuel injection nozzle 401 and has a lower opening shape having an air inlet 402a through which air is introduced.

The ignition means 403 serves to ignite the fuel sprayed from the fuel injection nozzle 401.

The outer cylinder 404 is installed to surround the inner cylinder 402 so that a predetermined space with the inner cylinder 402, the upper side so that the compressed air generated by the compressed air generating means 200 flows in An air inlet 404a is provided at the lower side, and an exhaust port 404b through which the combustion gas in which fuel and air are combusted by the ignition means 403 is discharged.

On the other hand, the pressurized fluid generating means 600, the pressurized fluid generator 610 and the combustion gas generated in the combustion means 400 is alternately supplied to the left and right of the pressurized fluid generator 610 to press the pressurized Combustion gas alternating feeders 640 and 640 'for operating the fluid generator 610 to generate pressurized fluid and a portion of the pressurized fluid generated by the operation of the pressurized fluid generator 610 to bypass the combustion. And a controller 670 for alternately driving control of the gas alternating feeders 640 and 640 '.

The pressurized fluid generator 610 includes a cylinder body 611, a piston rod 620, first pistons 621 and 622, second pistons 623 and 624, and a rod guide 625. ), Left and right covers 632, 633 and check valves 634, 635, 636, 637 for fluid inlet / outlet.

The cylinder body 611 may include a pair of left and right fluid discharge ports 612 and 613 spaced apart by a predetermined distance, and left and right balance ports 614 spaced apart from each other between the left and right fluid discharge ports 612 and 613 ( 615, and a pair of fluid inlet ports 616 spaced apart from each other by a predetermined distance corresponding to the left and right fluid discharge ports 612, 613, and left and right balance ports 614, 615. 619 and a pair of fluid discharge ports 618 and 617 spaced apart by a predetermined distance between the fluid inlet ports 616 and 619 and connected to the accumulator means 800. It has the shape of the opening at both ends which is empty.

The piston rod 620 is moved left and right in the longitudinal direction inside the cylinder body 611.

The first pistons 621 and 622 are formed to have a predetermined gap with the inner wall surface of the cylinder body 611, and are formed to be stepped with the piston rod 620 and provided at both ends of the piston rod 620, respectively. do.

The second pistons 623 and 624 are formed to have a predetermined gap with the inner wall surface of the cylinder body 611, and the second pistons 623 and 624 are separate as illustrated in FIG. The piston ring is installed to maintain the airtight between the piston and the inner wall surface of the cylinder body 611 by sliding in close contact with the inner wall surface of the cylinder body 611, and the first piston 621, 622 and It is formed to be stepped and provided at each end of the first piston (621) (624).

The rod guide 625 is disposed on an inner wall surface of the cylinder body 611 corresponding to the left and right fluid discharge ports 612 and 613, and an inner surface thereof is an outer surface of the first pistons 621 and 622. And a guide portion 625a protruding from the inner surface to guide the left and right in close contact with the outer surface of the piston rod 620 and the left and right balance ports 614 of the cylinder body 611. And communication ports 630, 631, 626, 628 and 629 communicating with the 615, the fluid inlet ports 616, 619, and the fluid discharge ports 618, 617.

The left and right covers 632 and 633 are provided at both ends of the cylinder body 611.

On the other hand, the above-described configuration and connection relationship between the first, second piston 621, 622, 623, 624, piston rod 620 of the compressed air generator is a configuration of the compressed air generating means of the embodiment of the present invention The same applies to the configuration, and the description thereof will be omitted in detail as described in FIG. 11.

According to the configuration and connection of the first and second pistons 621, 622, 623, and 624 and the piston rod 620 described above, the cylinder according to the reciprocating motion of the piston rod 620 along the fluid flow path The cooling action of the second pistons 623 and 624 due to the lubrication action of the second pistons 623 and 624 is lubricated by the contact between the liner 660 and the second pistons 623 and 624. Is done.

The fluid inlet / outlet check valves 634, 635, 636, 637 are installed on the fluid inlet ports 616, 619 and the fluid outlet ports 618, 617 of the cylinder body 611. do.

On the other hand, the combustion gas alternate supply 640, 640 ', the left and right direction switching valve body 641, 641' and the left and right direction switching valve body 650, 650 '.

The left and right directional valve body 641, 641 'is the first inlet port 642, 642' of the combustion gas into which the compressed combustion gas generated by the combustion means 400 first flows, and the first inlet port of the combustion gas Combustion gas introduced through the 642 and 642 'is discharged into the left and right spaces S1 and S2 formed between the second pistons 623 and 624 and the left and right covers 632 and 633. Gas discharge ports 643 and 643 ', first exhaust ports 644 and 644' through which the combustion gas in the left and right spaces S1 and S2 are first exhausted, and the first exhaust ports 644 and 644 Combustion gas exhaust ports 645 and 645 'through which the exhaust gas exhausted through') is exhausted to the outside, fluid inflow ports 646 and 646 'through which fluid is introduced, and the fluid inflow port 646 Fluid discharge ports 647 and 647 'allow the fluid introduced through 646' to be discharged to serve to switch the direction of the piston rod 620 from side to side.

The left and right direction switching valve body (650, 650 ') is in the interior of the left and right direction switching valve body (641, 641') slide closely in the vertical direction by the elastic force of the springs (651, 651 ') According to the presence or absence of pressurized fluid into the fluid inflow ports 646 and 646 ', the combustion gas initial inflow ports 642 and 642' and the combustion gas discharge port 643 of the left-directional switching valve body 641 ( 643 'and the combustion gas initial exhaust port 644, 644' and the combustion gas exhaust port 645, 645 'is in communication, the combustion of the right-direction switching valve body 641' The first gas inlet port 642, 642 ′ and the combustion gas discharge port 643, 643 ′ communicate with each other, and the first gas exhaust port 644, 644 ′ and the combustion gas exhaust port 645 ( 645 ') is to be regretted.

The controller 670 includes a control valve body 671, a first control valve body 692, a first slide member 693, a second control valve body 695, and a second slide member. Consisting of 696.

The control valve body 671 may be divided into five first, second, third, fourth, and fifth space parts 672, 673, 674, 675, and 676 sequentially divided. The first slide hole 680a and the second space portion 673 and the third space portion 674 formed through the first partition wall 680 partitioning the first space portion 672 and the second space portion 673. The second slide hole (681a) formed through the second partition wall (681) for partitioning) and the second partition wall (610) branched from the second slide hole (681a) and the pressurized fluid generator (610) A third slide hole formed through the discharge port 681b for changing the direction of the fluid to be allowed to flow in and through the third partition wall 682 partitioning the third space portion 674 and the fourth space portion 675 from each other; 682a, a fourth slide hole 691 formed through the fourth partition wall 683a which divides the fourth space part 675 and the fifth space part 676, and the first space part 672. ) And each of the fifth spaces 676 to generate the pressurized fluid. Four connection ports 685, 686, 687 and 688 which communicate with the 610 and into the second space 673 and the fourth space 675 of the accumulating means 800. An inlet port 690 through which some pressurized fluid is discharged and a discharge port 690a through which the pressurized fluid is drained back to the fluid storage tank 100 serves to control the direction switching valve.

The first control valve body 692 is installed in the first slide hole 680a so as to be slidably moved from side to side, and opens and closes the second slide hole 681a. And to control the communication between the inlet port 690.

The first slide member 693 is installed in the first space 672 in close contact with the elastic force of the spring 694, and is fixed to one end of the first control valve body 692.

The second control valve body 695 is installed in the third and fourth slide holes 674 and 675 so as to be slidably moved to the left and right to switch the direction while opening and closing the third slide hole 682a. It serves to control the communication between the discharge port 681a and the inflow port 690a.

The second slide member 696 is installed to be slidably close to the elastic force of the spring 697 in the fifth space 676, and is fixed to one end of the second control valve body 695.

On the other hand, the wheel drive means 500 comprises a drive body 501, a cylindrical body 502, a cylindrical roller 503, a rotary rotor 504, and a transmission means 510.

As shown in detail in FIG. 13, the driving body 501 includes a driving body 501, a rotation shaft 900, a first plate 530, a second plate 531, and a cylindrical body ( 502, a circular roller 503, and a rotary rotor 504.

The driving body 501 is formed with a pressurized fluid inlet 501a at a front portion thereof so that pressurized fluid generated by the pressurized fluid generating means 600 is introduced therein, and a fluid outlet 501b is provided at a lower rear side of the driving body 501. Is formed into an empty cylindrical shape.

The rotating shaft 900 is rotatably installed in the driving body 501, and a fly wheel 900a is installed on the rotating shaft 900 to evenly rotate the rotating force of the rotating shaft 900 according to the pulsation of the pressurized fluid. It is smooth and connected to the wheel.

The first plate 530 is installed perpendicular to the inner front end of the driving body 501, the through-hole 530b through which the rotating shaft 900 is formed is formed in the center, the pressurized fluid inlet 501a The fluid supply window 530a of a predetermined section is formed to introduce the fluid introduced through the filter.

The side plate cylindrical body 530c protruding to one side of the first plate 530 is intimately slid inside the cylindrical guide member 505 including the pressurized fluid inlet 501a surrounding the first plate 530 to prevent leakage of the pressurized fluid. In addition, the first plate 530 and the cylindrical body 502 have a constant adhesive force.

The second plate 531 is vertically spaced apart from the first plate 530 at the rear end of the driving body 501, and a through hole 531b is formed in the center through which the rotating shaft 900 penetrates. The fluid discharge window 531a is formed in a predetermined section through which fluid is discharged to the periphery so as not to correspond to the fluid supply window 530a.

The cylindrical body 502 is interposed between the first and second plates 530 and 531 so as to be movable in an elastic force of the spring 503 up and down inside the driving body 501, and both ends thereof. Is formed in a bilateral opening shape in intimate contact with the first and second plates 530 and 531.

The rotary rotor 504 is accommodated in the cylindrical body 502 is coupled to the rotating shaft 900, the roller guide groove 504a for the circular roller 503 is inserted and lifted up and down flexibly A plurality of radially circumferential surfaces are formed on the outer circumferential surface of the central point, and a plurality of fluid supply passages 504c are formed on the vertical inner surface forming the roller guide grooves 504a.

The shifting means 510 receives a portion of the pressurized fluid generated by the pressurized fluid generating means 600 to elastically move the cylindrical body 502 in the vertical direction to increase the forward and reverse rotational speed of the driving rotary shaft 900. Accelerates.

The shifting means 510 includes a transmission body 511 and a shifting plunger 512 in more detail.

The transmission body 511 is provided on the upper side of the drive body 501 and has a partition wall 511a for partitioning an internal space up and down.

The shifting plunger 512 has a piston 512a which is slidably installed in the lower space S1 of the transmission body 511, and has an upper end penetrating the partition wall 511a to the upper space S2. The lower end penetrates through the driving body 501 and contacts the outer circumferential surface of the cylindrical body 502.

Two branch conduits 514 and 513 branch on the pressurized fluid inlet pipe 516 flowing into the pressurized fluid inlet, one of which is connected in communication with the lower space S1, and the other is connected to the upper space ( A pressure reducing valve 515 is provided on the branch pipe 513 connected to the upper space S2, and a reverse valve 517 is installed on the branch pipe 514 connected to the lower space S1. do.

Meanwhile, in the exemplary embodiment of the present invention described above, the cooling tank 700, the first turbocharger 710, the second turbocharger 720, the pump 730, and the heat exchanger 740 may be further provided.

The cooling tank 740 accommodates the compressed air generating means 200, the combustion means 400 and the pressurized fluid generating means 600 to cool them, and the cooling water is filled therein.

The first turbocharger 710 has a first inlet 711 into which outside air is introduced and a second outlet 712 through which the inlet air is sucked into the compressed air generating means 200 and the pressurized fluid generating means 600. And a third inlet 713 into which the waste combustion gas is supplied and used, and a fourth outlet 714 through which the introduced waste combustion gas is discharged, and the outside air at both ends thereof through the same shaft 715. And first and second fans 716 and 717 that rotate when the waste combustion gas passes.

The second turbocharger 720 may include a first inlet 723 through which the waste combustion gas discharged from the second outlet 714 of the first turbocharger 710 flows and a second through which the introduced waste combustion gas may be discharged. The outlet 724 and the third inlet 721 through which the wet steam in the cooling tank 700 flows in and the introduced wet steam are discharged in the condensed water state, a part of which is supplied to the combustion means 400, and the rest is pressurized. Third and fourth fans having a fourth discharge port 722 to be supplied to the fluid generating means 600, and rotates when the waste combustion gas and the wet steam pass through the same shaft 725 at both ends thereof. 727 and 726.

The pump 730 is installed on the fourth outlet 722 of the second turbocharger 720.

The heat exchanger 740 heat-exchanges the waste combustion gas discharged from the fourth outlet 722 of the second turbocharger 720 and extracts only the coolant contained in the double again to bypass the cooling tank 700. Play a role.

Referring to the operation of the engine using the hydraulic pressure according to the present invention configured as described above are as follows.

First, as shown in FIG. 1, when the start switch 801 and the stop switch 802 are turned on, the fluid discharged from the accumulator means 800 is moved along the line L1 at a predetermined pressure and then the line ( Branched at L2) is introduced into the inlet port 224 of the first controller 240 constituting the compressed air generating means 200.

Here, the pressurized fluid to the wheel drive means 500 is the flow and flow block depending on whether the stop switch 802 is on or off.

A description with reference to FIG. 2 is as follows.

As shown in FIG. 2, the direction switching valve body 230 of the first controller 240 constituting the compressed air generating unit 200 has a burnt of the elastic spring 232 unless a separate hydraulic pressure is applied from the outside. The inlet port 224 and the common port 223 communicate with each other by the force, and the common port 222 and the drain port 225 communicate with each other, while the common port 223 and the drain port 226 communicate with each other. To make the mutual unpaid and to make the common port 222 and the inlet port 224 mutually unpaid.

In the above state, the fluid supplied from the line L2 is introduced into the inlet port 224 and then discharged from the common port 223 through the inside of the direction switching valve body 221, and then the compressed air generating means 200. It is introduced into the common port 207 of the compressed air generator 220 constituting the).

As described above, the fluid introduced into the common port 207 of the compressed air generator 220 is introduced through the communication port 215 formed in the rod guide 213 and the guide portion 213a of the rod guide 213. The amount of the fluid flowing into the right space S3 partitioned by is gradually increased.

As the amount of fluid flowing into the right space S3 increases, the piston rod 208 moves to the right.

As described above, while the piston rod 208 moves to the right side, the second piston 212 located on the right side maintains airtightness with the cylinder liner 219a located on the right side, and the second piston 212 and the cylinder liner 219a. ) And the space S2 formed by the cover 217 is gradually reduced.

Here, as the piston rod 208 moves to the right as described above, the area of the right space S3 decreases while the area of the left space S4 decreases while the fluid contained in the rod guide body ( After being drained through the communication port 214 of the 213 and the common port 206 of the cylinder body 201, the common formed in the direction switching valve body 221 constituting the first controller 240 along the line (L10) Drained through the port 222 and the drain port 225, the drained fluid flows along the line (L11) as shown in Figures 1 and 2 are introduced into the fluid storage tank 100.

Meanwhile, as the space S2 is reduced, the air located in the space S2 is compressed through a check valve 218a for discharging air in a compressed state, as shown in FIGS. 1 and 6. It flows in along the line L3 to the air inlet 404a formed in the outer cylinder 404 which comprises ().

As described above, as the piston rod 208 moves to the right side, the space portion S2 is gradually reduced while the space portion S1 is gradually enlarged, and the air inlet check valve 219 is generated by the vacuum suction force. Air of outside air flows into this space part S1 through (circle).

Here, the above-mentioned outside air may be simply air outside the compressed air generator 220.

However, in the embodiment of the present invention, while the piston rod 208 moves to the right side, the space portion S2 is reduced while the vacuum suction force generated in the space portion S1 is gradually expanded. As shown in FIG. 1, the filter 760 is affected, and the air of the outside air is introduced through the first inlet 711 after being filtered by the filter 760 after the vacuum suction force. After rotating the first fan 716, it is discharged through the second outlet 712, and then flows along the line L4, and thereafter branches in the lines L4a and L4b, and FIGS. 2 and 3. As shown in the drawing, the air inlet check valves 219 and 219a reach the front end.

The description so far describes the air inflow and generation process when the piston rod 208 moves to the right.

As described above, the distance that the piston rod 208 has moved to the right is a predetermined value, preferably the first piston 209 located on the left side is in contact with the inner surface of the rod guide body 213, as shown in FIG. When the piston rod 208 is further moved to the right by a predetermined distance while moving enough to form a gap (or a sealed space), the space area of the gap is reduced.

As the inner area of the gap is gradually reduced as described above, the fluid filled therein is discharged through the left discharge port 202 located on the left side and transferred along the line L5, and then the connection port of the second controller 270 is provided. It is introduced into the first space 242 through the (270).

When the fluid is introduced into the first space portion 242 of the second controller 270 as described above, the amount of fluid gradually increases in the first space portion 242 to the left of the first slide member 264. To make the slide move.

Here, since the hydraulic force is greater than the elastic force of the elastic spring 268, the first slide member 264 is able to slide to the left.

As described above, as the first slide member 264 slides to the left side, an end of the first control valve body 263 connected to the first slide member 264 opens the first slide hole 252, As the first slide hole 252 is opened, the direction switching discharge port 255 and the inlet port 261 can communicate with each other.

As described above, when the direction switching discharge port 255 and the inlet port 261 are in communication with each other, as shown in FIG. 1, the fluid having a predetermined pressure from the accumulator means 800 is line L1. After being transferred through), it is introduced into the inlet port 261 through the line (L6) branched from this line (L1) as shown in FIG.

As described above, the fluid discharged from the accumulator means 800 flowing into the inlet port 261 is discharged from the discharge port 255 through the inside of the control valve body 241 and is along the direction switching line L7. It flows into the inflow and outflow port 227 of the direction switching valve body 221 constituting the controller 240.

On the other hand, when the direction switching discharge port 255 and the inflow port 261 are in communication with each other, the second control valve body 265 does not communicate with the direction switching discharge port 255 and the drain port 262 mutually. To be in a state of

The reason why the direction switching discharge port 255 and the drain port 262 are not communicated with each other is as follows.

First, the fluid filled in the space S3 is introduced through the communication port 215a of the rod guide 213 while the piston rod 208 constituting the compressed air generator 220 is moved in the right direction. After being discharged from the right balance port 205 of the cylinder body 201 flows into the connection port 259 of the control valve body 241 constituting the second controller 270 along the line (L8).

Then, the fluid filled in the space (S3) in the process of the piston rod 208 constituting the compressed air generator 220 is moved to the right direction through the right discharge port 203 of the cylinder body 201 After being discharged, it is introduced into the connection port 258 of the control valve body 241 constituting the second controller 270 along the line (L9).

As the fluid is introduced into the connection port 259 and the connection port 258 of the control valve body 241 as described above, the second slide member (5) in the fifth space 246 constituting the second controller 270 ( 266 does not move in any direction and eventually the second control valve body 265 cannot move due to the elastic force of the elastic spring 268a, so that the direction switching discharge port 255 and the drain port 262 cannot be moved. It is mutually unhappy.

The description so far describes a process in which compressed air is generated through the air discharge check valve 218a after external air is introduced through the air inlet check valve 219 in the compressed air generating unit 200.

Hereinafter, the process of generating compressed air through the air discharge check valve 218 after the external air is introduced through the air inlet check valve 219a in the compressed air generating unit 200 will be described.

As shown in FIG. 2, when fluid flows into the inflow and outflow port 227 of the direction switching valve body 221 constituting the first controller 240 along the direction switching line L7, as shown in FIG. 3. Similarly, since an external pressure called fluid acts on the direction switching valve body 230 of the first controller 240 constituting the compressed air generating means 200, the elastic spring (left) in the direction switching valve body 221 is leftward. 232) to overcome the elasticity and move.

As described above, when the direction switching valve body 230 moves leftward from the inside of the direction switching valve body 221, the inlet port 224 and the common port 222 communicate with each other, and also the common port ( While allowing the 223 and the drain port 226 to communicate with each other, the common port 222 and the drain port 225 are mutually uncomfortable, and the common port 223 and the inlet port 224 are mutually uncommunicated.

In such a state, the fluid discharged from the accumulator means 800 is moved along the line L1 at a predetermined pressure and then branched in the line L2 to form the compressed air generating means 200. Inflow to the inlet port 224 of (240).

As described above, the fluid supplied through the line L2 is introduced into the inlet port 224 and then discharged from the common port 222 through the inside of the direction switching valve body 221 and then the compressed air generating means 200. It is introduced into the common port 206 of the compressed air generator 200 forming a.

As described above, the fluid introduced into the common port 206 of the compressed air generator 220 is introduced through the communication port 214 formed in the rod guide 213, and is introduced into the guide portion 213a of the rod guide 213. The amount of fluid flowing into the partitioned left space S4 is gradually increased.

As the amount of fluid flowing into the left space S4 increases, the piston rod 208 moves to the left.

As described above, while the piston rod 208 moves to the left side, the second piston 211 located on the left side maintains airtightness with the cylinder liner 219b located on the left side and the second piston 211 and the cylinder liner 219b. ) And the space S1 formed by the cover 216 is gradually reduced.

Here, as the piston rod 208 is moved to the left as described above, the area of the left space S4 is increased while the area of the right space S3 is decreased, and the inside of the right space S3 is reduced. The received fluid is drained through the communication port 215 of the rod guide 213 and the common port 207 of the cylinder body 201, and then the direction switching valve constituting the first controller 240 along the line L12. Drained through the common port 223 and the drain port 226 formed in the main body 221, the drained fluid flows along the line (L13) as shown in Figures 1 and 3 fluid storage tank 100 Flows into).

On the other hand, as the space (S1) is reduced as described above, the air located in the space (S1) through the air discharge check valve 218 in a compressed state as shown in Figs. It flows in along the line L14 to the air inlet 404a formed in the outer cylinder 404 which comprises the means 400. As shown in FIG.

As described above, as the piston rod 208 moves to the left side, the space portion S1 is gradually reduced while the space portion S2 is gradually enlarged by the vacuum suction force generated by the vacuum suction force. Air of outside air flows into this space part S2 through).

Here, the above-mentioned outside air may be simply air outside the compressed air generator 220.

However, in the embodiment of the present invention, while the piston rod 208 moves to the left side, the space portion S1 is reduced, while the vacuum suction force generated in the space portion S2 is gradually increased when the space portion S2 is gradually enlarged. As shown in FIG. 1, the filter 760 is affected, and the air of the outside air is introduced through the first inlet 711 after being filtered by the filter 760 after the vacuum suction force. After rotating the first fan 716, it is discharged through the second outlet 712, and then flows along the line L4, and thereafter branches in the lines L4a and L4b, and FIGS. 2 and 3. As shown in the drawing, the air inlet check valves 219 and 219a reach the front end.

The description so far describes the air inflow and generation process when the piston rod 208 moves to the left.

As described above, the distance that the piston rod 208 has moved to the left is a predetermined value, preferably the first piston 210 for the right side is in contact with the inner surface of the rod guide body 213, as shown in FIG. 3. When the piston rod 208 is further moved to the left by a predetermined distance while moving enough to form a gap (or a closed space), the space area of the gap is reduced.

As the inner area of the gap is gradually reduced as described above, the fluid filled therein is discharged through the right discharge port 203 located on the right side and transferred along the line L9, and then the connection port of the second controller 270 is provided. It is introduced into the fifth space 246 through 258.

When the fluid flows into the fifth space portion 246 of the second controller 270 as described above, the amount of fluid gradually increases in the fifth space portion 246 to the left of the second slide member 266. To make the slide move.

Here, since the hydraulic force is greater than the elastic force of the elastic spring 268a, the second slide member 266 is able to slide to the left.

As described above, as the second slide member 266 slides to the left side, the end of the second control valve body 265 connected to the second slide member 266 opens the third slide hole 253, As the third slide hole 253 is opened, the direction switching discharge port 255 and the drain port 262 can communicate with each other.

As described above, when the direction change discharge port 255 and the drain port 262 are in communication with each other, as illustrated in FIG. 3, the direction change inflow and outflow direction of the first controller 240 through the line L7. The fluid acting on the port 227 flows in the reverse direction and flows through the discharge port 255 for directional change, and then discharges to the drain port 262 and then flows into the fluid storage tank 100 along the line L16. will be.

On the other hand, when the direction switching discharge port 255 and the drain port 262 communicate with each other, the first control valve body 263 does not mutually communicate the direction switching discharge port 255 and the inlet port 261. To be in a state of

The reason why the direction changing discharge port 255 and the inflow port 261 are mutually unsuccessful will be described as follows.

In the above description of FIG. 2, when the piston rod 208 is completely moved to the right, the pressure of the fluid acting as the connection port 257 is lost, and the elastic spring 268 is restored to its original state in the compressed state. The first control valve body 263 closes the second slide hole 252 by pushing the first slide member 264 to the right.

In the above state, the fluid filled in the space S4 in the process of moving the piston rod 208 constituting the compressed air generator 220 to the left direction is the communication port 214a of the rod guide 213. After the flow through the discharged from the left balance port 204 of the cylinder body 201 flows into the connection port 256 of the second controller 270 along the line (L17).

Then, the fluid filled in the space (S4) during the piston rod 208 constituting the compressed air generator 220 is moved in the right direction through the left discharge port 202 of the cylinder body 201 After being discharged, it is introduced into the connection port 257 of the control valve body 241 constituting the second controller 270 along the line (L5).

As the fluid flows into the connecting port 256 and the connecting port 257 of the control valve body 241 as described above, the first slide member (in the first space 246 constituting the second controller 270) 264 does not move in any direction, so that the ejection port 255 and the inflow port 261 for direction switching are mutually unacceptable.

As described above, as the direction switching discharge port 255 and the inflow port 261 are not communicated with each other, and the direction switching discharge port 255 and the drain port 262 communicate with each other, the first controller through the line L7. Since the fluid acting on the direction switching inlet / outlet port 227 of the direction switching valve body 221 constituting the 240 flows to the reverse port and flows to the drain port 262, the valve body 221 for direction switching The direction switching valve body 230 that has been moved in the left direction from the inside of the is moved in the right direction by the restoring force of the elastic spring 232.

Eventually, as shown in FIG. 2, the direction switching valve body 230 of the first controller 240 constituting the compressed air generating unit 200 in an initial state may have an elastic spring unless a separate hydraulic pressure is applied from the outside. The inflow port 224 and the common port 223 communicate with each other by the elastic force of the 232, and the common port 222 and the drain port 225 communicate with each other while the common port 223 and The drain port 226 is mutually unpaid, and the common port 222 and the inlet port 224 are in a mutually unpaid state.

The description so far has described a process in which compressed air is generated through the air discharge check valve 218 after external air is introduced through the air inlet check valve 219a in the compressed air generating unit 200, and the present invention. Compressed air generating means 200 is a first process of generating compressed air through the air discharge check valve 218a after the external air is introduced through the air inlet check valve 219, and check for air inlet After the external air is introduced through the valve 219a, the second process of repeatedly generating compressed air through the air discharge check valve 218 is repeatedly performed.

Therefore, the compressed air generating means 200 according to the present invention can generate the compressed air in both directions.

The description so far has described a process of generating compressed air in the compressed air generating means 200, and hereinafter, a process of burning in the combustion means 300 using the generated compressed air will be described.

As shown in FIG. 6, the compressed air transferred through the line L14 or the line L3 is introduced through the air inlet 404a provided in the outer cylinder 404 constituting the combustion means 400.

Part of the compressed air introduced as described above is introduced between the outer cylinder 404 and the inner cylinder 402 to flow out into the combustion air tool 402a formed in the inner cylinder 402, the remaining of the compressed air compressed As air flows out through the space between the outer cylinder 404 and the inner cylinder 402 to the lower end of the inner cylinder 402, the inner cylinder 402 is cooled to mix with the combustion gas in which combustion is completed, thereby the temperature of the compressed combustion gas. Lowers to a constant temperature.

At the same time, the fuel supply means 300 pumps the fluid in the fuel tank 301 by pumping the pump 302 so that fuel is injected through the fuel injection nozzle 401.

As described above, the fuel injected from the fuel injection nozzle 401 and the air introduced through the air inlet 402a of the inner cylinder 402 are mixed and then ignited and combusted by the ignition means 403. .

As described above, the combustion gas ignited by the ignition means 403 is discharged through the exhaust port 404b formed at the lower end of the outer cylinder 404.

In addition, a separate hot water nozzle 405 may be installed at the outlet of the combustion means 400 to directly mix the working fluid of the high temperature water into the combustion heat source, thereby making it an expanded steam, and ejecting it from the outlet of the combustion means 400.

Combustion gas discharged through the exhaust port 404b is the first inlet of the combustion gas formed in the combustion gas alternating feeders 640 and 640 'constituting the pressurized fluid generating means 600, as shown in FIGS. 1, 4 and 5. It enters ports 642 and 642 '.

Hereinafter, the pressurized fluid generating means 600 will be described step by step.

First, as shown in FIG. 4, the initial state of the flue gas alternating feeder 640 constituting the pressurized fluid generating means 600 is determined by the repulsive force of the ball spring 651. In the elevated state, the combustion gas first inlet port 642 and the combustion gas discharge port 643 are in communication with each other, and the first exhaust port 644 and the combustion gas exhaust port 645 are in mutual communication with each other.

On the other hand, the initial state of the flue gas alternating feeder 640 'constituting the pressurized fluid generating means 600 is a state in which the right-direction switching valve body 650' is lowered by the elastic force of the carbon spring 651 '. The combustion gas first inlet port 642 'and the combustion gas discharge port 643' are mutually uninterrupted, and the first exhaust port 644 'and the combustion gas exhaust port 645' are in communication with each other.

Compressed combustion gas generated by the combustion means 400 as the pressurized fluid generating means 600 having the state of the combustion gas alternating feeder 640 and 640 'as described above is line L20 as shown in FIG. Compressed combustion gas is introduced into the first inlet port (642, 642 ') through.

However, since the flue gas first inlet port 642 ′ of the flue gas alternating supply 640 ′ is in mutual communication with the flue gas discharge port 643 ′, the flue gas flowing through line L20 is the first inlet of flue gas It does not flow into the port 642 ′, but flows into the combustion gas first inlet port 642 of the flue gas alternating feeder 640.

As described above, when the combustion gas is introduced into the combustion gas initial inlet port 642 of the combustion gas alternating supply 640, the combustion gas is discharged through the interior of the left turn valve body 641 with a predetermined pressure. After discharged from the port 643, the fluid flows into the space S1 formed between the left cover 632 and the second piston 623 constituting the pressurized fluid generator 610.

As described above, as the amount of combustion gas flowing into the space S1 at a predetermined pressure increases, the piston rod 620 moves in the right direction.

As described above, while the piston rod 620 moves to the right side, the second piston 624 located on the right side maintains airtightness with the cylinder liner 660 located on the right side and the right side of the second piston 624. The space S2 formed by the cover 633 is gradually reduced.

As described above, as the space S2 is reduced, the combustion gas filled in the space S2 is compressed through the inside of the right-turn valve body 641 'through the first exhaust port 644' in a compressed state. It is discharged to the outside through the gas exhaust port 645 '.

As described above, the combustion gas discharged through the combustion gas exhaust port 645 'is transported along the line 26, as illustrated in FIGS. 4 and 1, to form a first turbocharger 710. The second fan 717 is rotated along with the first fan 716 which is introduced into the inlet 713 and the exhaust gas introduced into the third inlet 713 is rotated through the same shaft 715. Therefore, it is discharged through the fourth discharge port 714.

As described above, the exhaust gas discharged from the fourth outlet 714 flows back into the first inlet 723 constituting the second turbocharger 720. After the two fans 727 are rotated, they are discharged from the second outlet 724 and then passed through a heat exchanger 740 that is heat exchanged by the cooling blower fan 770.

As described above, the exhaust gas passing through the heat exchanger 740 is condensed and the air component is discharged to the atmosphere, while the condensate is pumped by the pump 750 and transferred along the line 27 to the cooling tank 700. It is recovered again.

On the other hand, in the above description, as the piston rod 620 moves to the right, the area of the right space S3 is increased, whereas the area of the left space S4 is reduced, resulting in the following actions.

First, among the actions generated on the left side space S4 side, first, the distance that the piston rod 620 moves to the right is a predetermined value, preferably the first piston 621 located on the left side is the rod guide 625. When the piston rod 620 is further moved to the right by a predetermined distance while being in contact with the inner side of the center to form a gap (or a closed space) as shown in FIG. 4, the gap of the gap The space area is reduced.

As the inner area of the gap is gradually reduced as described above, the fluid filled therein is discharged through the left fluid discharge port 612 located on the left side and transferred along the line L21, and then the connection port of the controller 670 It flows into the first space 672 through 686.

When the fluid flows into the first space portion 672 of the controller 670 as described above, the amount of fluid gradually increases in the first space portion 672 to push the first slide member 693 to the left. To make the slide moveable.

Here, since the hydraulic force is greater than the elastic force of the elastic spring 694, the first slide member 693 can slide to the left.

As described above, as the first slide member 693 slides to the left side, an end of the first control valve body 692 connected to the first slide member 693 opens the second slide hole 681a. As the two slide holes 681a are opened, the discharging port 681b and the inflow port 690 for direction switching can communicate with each other.

As described above, when the direction switching discharge port 681b and the inlet port 690 are in communication with each other, as shown in FIG. 1, the fluid having a predetermined pressure from the accumulator means 800 is line L1. After being transferred through), it is introduced into the inlet port 690 through the line L22 branched from this line L1 as shown in FIG. 4.

As described above, the fluid discharged from the accumulator means 800 flowing into the inlet port 690 is discharged from the discharge port (681b) for directional change over the inside of the control valve body 671 is along the line (L23) After being transported, it is introduced into the fluid inlet ports 646 and 646 'of the flue gas alternating feeders 640 and 640' along the lines L24 and L25 bidirectionally branched from this line L23.

Next, second of the actions generated on the left space S4 side, the fluid pre-filled in the left space S4 passes through the communication port 627 formed in the rod guide 625 through the cylinder body 611. After being discharged from the fluid discharge port 618 formed in the and passes through the fluid discharge check valve 635.

After passing through the fluid discharge check valve 635 as described above is transferred along the line (L28), as shown in Figure 1, the line extending from the accumulating means 800 through the line (L28b) It is fed back to L1a. Here, the branch line L1b and the line L1c branch into the line L1a.

The line L1b is connected to the line L1, and the line L1c is connected to the wheel driving means 500.

Next, first of the actions occurring at the right space S3 side, as shown in FIG. 1, after the fluid discharged from the fluid storage tank 100 is transferred through the line L29, the line As shown in FIG. 4 through the line L29a branched from L29, the fluid inflow port 619 of the cylinder body 611 is introduced through the fluid inflow check valve 637, and this fluid inflow port is provided. The fluid introduced into 619 is introduced into the space S3 through the communication port 629 of the rod guide 625.

As described above, the fluid introduced into the space S3 is introduced through the communication port 631 of the rod guide 625, and then discharged from the right balance port 615 of the cylinder body 611 to discharge the line L30. Accordingly, it is introduced into the connection port 688 of the control valve body 671 constituting the controller 670.

Then, the fluid introduced into the space S3 is discharged through the right discharge port 613 of the cylinder body 611, and then the control valve body 671 of the control valve 671 constituting the controller 670 along the line L31. It flows into the connection port 687.

As described above, the fluid flows into the connection port 688 and the connection port 687 of the control valve body 671 and the second slide member 696 in the fifth space 676 constituting the controller 670. Does not move in any direction and eventually the second control valve body 695 cannot move even by the elastic force of the elastic spring 697, so that the directional discharge discharge port 681b and the drain port 690a are mutually unacceptable. Will be.

The description so far describes a process in which the pressurized fluid is generated through the check valve 635 for discharging the fluid in the pressurized fluid generating means 600.

Hereinafter, a process of generating the compressed fluid through the check valve 636 for discharging the fluid in the pressurized fluid generating means 600 will be described.

As shown in FIG. 4, the fluid discharged from the accumulating means 800 flowing into the inlet port 690 passes through the inside of the control valve body 671 and is discharged from the direction switching discharge port 681b to form a line ( After being transported along L23, fluid inlet ports 646 and 646 'of the flue gas alternating feeders 640 and 640', respectively, along lines L24 and L25 branched bidirectionally in this line L23. When it flows in, the state of the left-right direction switching valve body 650 (650 ') which comprises the combustion gas alternating supply 640 (640') is reversed.

Hereinafter, a process of reversing the state of the left and right direction switching valve bodies 650 and 650 'constituting the combustion gas alternating feeders 640 and 640' will be described.

First, when the fluid is introduced into the fluid inlet port 646 through the line L24, the fluid flows downward in the left direction switching valve body 641 to move the left direction switching valve body 650 downward. Pressurized to move to.

In this case, while the elastic spring 561 is in a compressed state, the left direction switching valve body 650 moves downward.

Here, when the buffer valve 652 is in contact with the stepped portion 652a which is stepped on the lower inner wall of the valve valve body 641 in the process of moving the left direction switching valve body 650 downward, A gap is formed, and this buffering gap prevents the leftward switching valve body 650 from rapidly moving downward and mitigates the shock generated when moving downward.

On the other hand, when the left direction switching valve body 650 is completely moved as described above, the combustion gas initial inlet port 642 and the combustion gas discharge port 643 formed in the left direction switching valve body 641 is While the non-communication state occurs, the first exhaust port 644 and the combustion gas exhaust port 645 communicate with each other.

Next, when the fluid is introduced into the fluid inlet port 646 'through the line L25, the pressurized fluid flows upwardly in the rearward switching valve body 641' and the rightward switching valve body 650. ') Is pressed to move upward.

In this case, while the elastic spring 561 'is in a compressed state, the right direction switching valve body 650' is moved upward.

Here, the buffer part 652 'is formed on the stepped part 652a', which is stepped on the upper inner wall of the right direction switching valve body 641 'while the right direction switching valve body 650' moves upward. When in contact, a buffer gap is formed. This buffer gap prevents the rightward switching valve body 650 'from operating rapidly in the upward direction and mitigates the shock generated when moving upward. Given.

On the other hand, as described above, when the right direction switching valve body 650 'is completely moved in the upward direction, the combustion gas initial inlet port 642' formed on the right direction valve body 641 'and the combustion gas discharge port ( 643 'are in communication with each other, while the first exhaust port 644' and the combustion gas exhaust port 645 'are not in communication with each other.

Combustion gas generated by the combustion means 400 described above with the pressurized fluid generating means 600 having the state of the combustion gas alternating feeders 640 and 640 'is the line L20, as shown in FIG. ) Is introduced into the combustion gas initial inlet port (642) (642 ').

However, since the combustion gas first inlet port 642 of the combustion gas alternating air changer 640 is mutually inconsistent with the combustion gas discharge port 643, the combustion gas flowing through the line L20 is the first combustion gas inlet port ( 642), it is introduced into the combustion gas initial inlet port 642 'of the combustion gas alternating supply 640'.

As described above, when the combustion gas flows into the combustion gas initial inlet port 642 'of the alternating feeder 640', the combustion gas has a predetermined pressure and opens the inside of the right-direction switching valve body 641 '. After being discharged from the combustion gas discharge port 643 ′, it is introduced into the space S2 formed between the right cover 633 and the second piston 624 constituting the pressurized fluid generator 610.

As described above, as the amount of combustion gas flowing into the space S2 at a predetermined pressure increases, the piston rod 620 moves to the left direction.

As described above, while the piston rod 208 is moved to the left side, the second piston 623 located on the left side is kept airtight with the cylinder liner 660 located on the left side, and the second piston 623 and the left cover 632 are provided. The space S1 formed by) is gradually reduced.

As described above, as the space S1 is reduced, the combustion gas filled in the space S1 is exhausted through the interior of the left turn valve body 641 through the first exhaust port 644 in a compressed state. It is discharged to the outside through the port 645.

As described above, the combustion gas discharged through the combustion gas exhaust port 645 is transported along the line L40, as illustrated in FIGS. 5 and 1, to form a third inlet constituting the first turbocharger 710. 713, the exhaust gas introduced into the third inlet 713 is rotated along with the first fan 716 which is rotated through the same shaft 715. Discharged through the fourth discharge port 714.

As described above, the exhaust gas discharged from the fourth outlet 714 flows back into the first inlet 723 constituting the second turbocharger 720. After the two fans 727 are rotated, they are discharged from the second outlet 724 and then passed through a heat exchanger 740 that is heat exchanged by the cooling blower fan 770.

As described above, the exhaust gas passing through the heat exchanger 740 is condensed and the air component is discharged to the atmosphere, while the condensate is pumped by the pump 750 and transferred along the line 27 to the cooling tank 700. It is recovered again.

Meanwhile, in the above description, as the piston rod 620 moves to the left side, the area of the right space S3 is increased, whereas the area of the left space S4 is increased. .

First of all, the first piston 622 positioned on the right side of the rod guide body 625 has a predetermined value of a distance in which the piston rod 620 moves to the right. When the piston rod 620 is further moved by a predetermined distance while being in contact with the inner side of the c) to form a gap GAP as shown in FIG. 5, the space area of the gap is reduced.

As the inner area of the gap is gradually reduced as described above, the fluid filled therein is discharged through the right fluid discharge port 613 located on the right side and transferred along the line L31, and then the connection port of the controller 670 687 is introduced into the fifth space 696a.

When the fluid flows into the fifth space portion 696a of the controller 670 as described above, the amount of fluid gradually increases in the fifth space portion 696a to push the second slide member 696 to the left. To make the slide moveable.

Here, since the hydraulic force is greater than the elastic force of the elastic spring 697, the second slide member 696 is able to slide to the left.

As the second slide member 696 slides to the left as described above, the end of the second control valve body 695 connected to the second slide member 696 opens the third slide hole 682a. As the three slide holes 682a are opened, the direction switching discharge port 681b and the drain port 690a can communicate with each other.

As described above, when the direction switching discharge port 681b and the drain port 690a are in communication with each other, as illustrated in FIG. 5, the combustion gas alternate supply 640 through the line L24 and the line L25. The fluid acting on the fluid inflow ports 646 and 646 'of the 640' is reversed to flow in the direction changing discharge port 681b and then discharged to the drain port 690a and then the line L41. It is introduced into the fluid storage tank 100 along.

On the other hand, when the direction switching discharge port 681b and the drain port 690a communicate with each other, the first control valve body 592 does not mutually pass through the direction switching discharge port 681b and the inflow port 690. To be in a state of

The reason why the direction switching discharge port 681b and the inflow port 690 are mutually unstable as described above is as follows.

In the above-described description of FIG. 5, since the vacuum suction force acts in the space S4 while the piston rod 620 is completely moved to the left side, the fluid flows from the fluid storage tank 100 along the line L29. As shown in FIG. 5 through the line L29b branched from this line L29, it is introduced into the fluid inlet port 616 of the cylinder body 611 through a fluid inlet check valve 637, The fluid introduced into the fluid inflow port 616 is introduced into the space S4 through the communication port 626 of the rod guide 25.

As described above, the fluid introduced into the space S4 is introduced through the communication port 630 of the rod guide 625 and then discharged from the left balance port 614 of the cylinder body 611 to draw the line L21. Accordingly, it is introduced into the connection port 685 of the control valve body 671 constituting the controller 670.

Then, the fluid introduced into the space S4 is discharged through the left discharge port 612 of the cylinder body 611 and then the control valve body 671 constituting the controller 670 along the line L21a. Flows into the connection port 686.

As described above, the fluid flows into the connection port 685 and the connection port 686 of the control valve body 671 and the first slide member 693 in the first space 672 constituting the controller 670. Does not move in any direction, and eventually the first control valve body 692 cannot move even by the elastic force of the elastic spring 694, and thus the direction switching discharge port 691b and the inflow port 690 are mutually unstable. Will be.

As described above, the direction switching discharge port 691b and the inflow port 690 are not communicated with each other, and the direction switching discharge port 691b and the drain port 690a communicate with each other. The fluid acting on the fluid inlet ports 646 and 646 'of the left and right direction switching valve bodies 641 and 641' constituting the combustion gas alternating feeder 640 and 640 'flows backward to the drain port ( Since it flows to 690a, the left-right switching valve body 650 and 650 'which comprise the combustion gas alternating feeder 640 and 640' is returned to an original state as shown in FIG.

On the other hand, the second action of the piston rod 620 is generated in the right space (S3) side in the process of moving to the left, the fluid pre-filled in the right space (S3) communication formed in the rod guide 625 After being discharged from the fluid discharge port 618 formed in the cylinder body 611 via the port 628, it passes through the fluid discharge check valve 636.

After passing through the fluid discharge check valve 636 as described above is transferred along the line (L42), as shown in Figure 1, after flowing in the line (L42), the line (L42a) to the line (L1a) Is fed back.

The description so far has described the process of generating the compressed fluid through the check valve 636 for discharging the fluid in the pressurized fluid generating means 600, the pressurized fluid generating means 600 according to the present invention is a check valve for fluid inlet A first process in which the fluid introduced through the 637 is discharged through the fluid discharge check valve 635 in a pressurized state, and the fluid discharged through the fluid inlet check valve 634 in the pressurized state are checked for fluid discharge. The second process discharged through the valve 636 is repeatedly performed.

Therefore, the pressurized fluid generating means 600 according to the present invention is capable of generating pressurized fluid in both directions.

On the other hand, as shown in Figure 1 during the operation of the pressurized fluid generating means 600 and the compressed air generating means 200 according to the present invention, a cooling action for additionally cooling them occurs, which will be described below. I would like to.

First, since the second fan 727 constituting the second turbocharger 720 is rotated in the foregoing description, the second fan 727 is rotated through the same shaft 725 as the second fan 727. Because of the rotation of the fan 726 inside the cooling tank 700, some air flows out along the line L50, and the vacuum state is achieved.

As described above, as the cooling tank 700 is in a vacuum state, since the cooling water filled therein is formed at a boiling point of 100 degrees or less, the cooling water is kept constant at 100 degrees C or less, and vaporization is performed at 100 degrees C or less. The steam flows into the suction port of the vacuum fan 726 and returns to condensed water by the negative pressure greater than atmospheric pressure at the outlet of the vacuum fan 726, thereby generating hot water having a high calorific value in the condensed water. The water flows along the line L51 and then flows into the outer cylinder 404 constituting the combustion means 400 via the line L51b branched from this line L51, as shown in FIG. 6. It serves to lower the overall temperature of the combustion means (400).

Meanwhile, the hot water transferred through the line L51a branched from the line L51 after being transported along the line L51 is a combustion gas alternating feeder 640 and 640 as shown in FIGS. 4 and 5. After passing through the inside of the left and right directional valve body 64, 641 'through the hot water inlet (653, 653') formed in the ') formed in the left and right directional valve body 650 (650') After ascending along the inner passages 654 and 654 ', the gas is discharged through the exhaust gas discharge ports 645 and 645'.

As described above, it is possible to prevent the combustion gas alternating feeders 640 and 640 'from being deteriorated by supplying hot water into the combustion gas alternating feeders 640 and 640'.

The description so far has described a process in which the pressurized fluid is generated in the pressurized fluid generating means 600. Hereinafter, a process of driving the wheel driving means 500 using the pressurized fluid generated in the pressurized fluid generating means 600 will be described. Let's explain.

First, as shown in FIG. 1, when a fluid in a pressurized state is supplied through line L1c, a portion of the fluid is transferred through line 516, as shown in FIG. 7, while the rest is It is branched to a line 516a branched from this line 516.

Here, the fluid branched to the line 516a is branched back to the line 513 and the line 514 branched from the line 516a.

When the pressurized fluid is transferred through the path as described above, since the pressure reducing valve 515 and the backward valve 514 are closed as shown in FIG. 7, the fluid through the line 513 and the line 514 is closed. Even if is transferred does not have any effect on the upper space (S2) and the lower space (S1) constituting the transmission means (510).

Since the fluid does not affect the transmission means 510 as described above, the cylindrical body 502 is moved upward by the elastic force of the carbon spring 520, and eventually the upper inner surface of the driving body 501. Is in contact with.

As described above, since the cylindrical body 502 is moved upward by the elastic force of the ball spring 520, and the rotary rotor 504 always maintains its current position, the cylindrical body 502 and the rotary rotor Between the 504, the eccentric spaces S3 and S4 are formed on the upper side so as to be symmetrical to the left and right on the basis of the vertical lines 1, respectively.

In addition, when the cylindrical body 502 is moved upward by the elastic force of the ball spring 520, the ball springs 521 supporting the respective circular rollers 503 are cylindrical body 502 ) Is compressed or expanded to appropriately support the moving distance in the upward or downward direction to support the circular roller 503. Accordingly, the circular rollers 503 are also accommodated in the roller guide groove 504a. The depths are in different states.

As described above, the pressurized fluid transferred through the line 516 in the above state is as shown in FIGS. 7, 12, and 13, through the fluid supply window 530a formed in the first plate 530. Supplied.

Here, the formation region of the fluid supply window 530a may cover the roller guide groove 504a corresponding to a, b, c, and d as shown in FIG. 7.

Therefore, the fluid supplied through the fluid supply window 530a flows only into the roller guide grooves 504a corresponding to a, b, c, and d.

Subsequently, the fluid introduced into the roller guide grooves 504a corresponding to a, b, c, and d is blocked by the second plate 531 as shown in FIG. 12 to traverse in the longitudinal direction of the rotary rotor 504. It is not discharged and flows out through the fluid supply path 504c formed on the vertical inner surface of the roller guide groove 504a.

As described above, the pressurized fluid flowing out through the fluid supply path 504c is filled into the eccentric space S4, as shown in FIG. 7.

As described above, when the pressurized fluid is filled into the eccentric space S4, the rotary rotor 504 starts to rotate in the clockwise direction about the rotation shaft 900.

Here, the principle that the rotary rotor 504 is to be described below.

The eccentric space (S4) is a circular roller 503 corresponding to the roller guide groove at the point a and the circle corresponding to the roller guide groove at the point b by the shape of the cylindrical body 502 and the rotary rotor 504 There is an area difference in the portion adjacent to the roller 503.

That is, since the area of the eccentric space S4 of the portion adjacent to the circular roller 503 at point a is larger than the area of the eccentric space S4 of the portion adjacent to the circular roller 503 at point b, this area difference is different. Eventually, the rotary rotor 504 starts to rotate.

Here, the area difference of the eccentric space is also applied to the b-c point and the c-d point, of course.

Due to the above principle, the rotation rotor 504 is rotated by a predetermined angle so that the fluids in the eccentric space S4 are sequentially transferred to the eccentric space S3, and the fluid passed to the eccentric space S3 is the second plate. After being discharged through the fluid discharge window 531a formed at 531, as shown in FIG. 13, it is discharged to the outside of the wheel driving means 500 through the fluid discharge port 501b formed at the driving body 501.

The fluid discharged to the outside of the wheel driving means 500 is transferred along the line L60 and is drained into the fluid storage tank 100 as shown in FIG. 1.

7 described above, the rotation of the rotary rotor 504 together with the rotary shaft 900 has been described when the vehicle is moving forward at a low speed.

Hereinafter, the acceleration of the vehicle in the forward direction will be described.

As shown in FIG. 8, when the pressure reducing valve 515 is opened at a constant value, the fluid flowing in the line 516 is moved to the line 513 through the pressure reducing valve 515.

The fluid moved to the line 513 as described above is introduced into the upper space (S2) formed in the transmission body 511 constituting the transmission means 510.

As the amount introduced into the upper space S2 increases, the fluid acts to move the shift plunger 512 downward.

Due to the fluid filled in the upper space (S2) as described above, the shifting plunger 512 moves a predetermined value in the downward direction, and thus the cylindrical body 502 also overcomes the elastic force of the elastic spring 520 in the downward direction. While moving to a predetermined value.

Here, since the range in which the cylindrical body 502 moves downward is determined by the opening degree of the pressure reducing valve 515, the horizontal center line of the cylindrical body 502 is a predetermined value than the horizontal center line of the rotating shaft 900. The pressure reducing valve 515 must be controlled to be above.

As described above, when the horizontal center line of the cylindrical body 502 is above a predetermined value above the horizontal center line of the rotating shaft 900, the rotary rotor 504 is rotated at a higher speed than the state of FIG.

Meanwhile, when the reverse valve 517 is operated while the pressure reducing valve 515 is stopped, the fluid flowing in the line 516 moves to the line 514 through the reverse valve 517.

The fluid moved to the line 514 as described above is introduced into the lower space (S1) formed in the transmission body 511 constituting the transmission means 510.

As the amount introduced into the lower space S1 increases, the pressurized fluid acts to move the shifting plunger 512 downward to maximize as shown in FIG. 9.

As described above, when the shifting plunger 512 moves downward to maximize, the cylindrical body 502 overcomes the elastic force of the carbon spring 520 and eventually reaches the maximum inner side of the lower portion of the driving body 501. It is in a state of approaching.

As described above, the cylindrical body 502 rotates with the cylindrical body 502 because the cylindrical body 502 is maximally moved downward to overcome the elastic force of the elastic spring 520 and the rotary rotor 504 always maintains its current position. Between the rotors 504, the eccentric spaces S5 and S6 are formed on the lower side symmetrically from side to side with respect to the vertical line l, respectively.

And, as described above, when the cylindrical body 502 is moved to the maximum in the downward direction by the elastic force of the ball spring 520, the ball springs 521 supporting the respective circular rollers 503 are cylindrical The circular rollers 503 are compressed or expanded in correspondence with the movement distance in the upward or downward direction of the 502 to support the circular rollers 503. Accordingly, the circular rollers 503 are also provided in the roller guide grooves 504a. The stored depths become different from each other, and eventually the state shown in FIG.

Here, it is specified that the state shown in FIG. 9 is opposite to the state shown in FIG. 7.

In the above state, as described above, the pressurized fluid transferred through the line 516 may be configured to close the fluid supply window 530a formed in the first plate 530, as shown in FIGS. 9, 12, and 13. Supplied through.

Here, the formation region of the fluid supply window 530a may cover the roller guide groove 504a at points a, b, c, and d as shown in FIG. 9.

Therefore, the fluid supplied through the fluid supply window 530a flows only into the roller guide groove 504a at points a, b, c, and d.

Thereafter, the fluid flowing into the roller guide grooves 504a at the a, b, c, and d points is blocked by the second plate 531 to extend in the longitudinal direction of the rotary rotor 504, as shown in FIG. It is not discharged, but is discharged through the fluid supply path 504c formed on the vertical inner surface of the roller guide groove 504a.

As described above, the fluid discharged through the fluid supply path 504c is filled into the eccentric space S5.

As described above, when the fluid is filled into the eccentric space (S5), the rotary rotor 504 starts to rotate in a counterclockwise direction about the rotation axis (900).

That is, the reverse of the case of Figure 7 will eventually be to reverse the wheel drive means (500).

Here, the principle that the rotary rotor 504 is rotated in the counterclockwise direction will be described below.

The eccentric space (S5) is a circular roller 504a corresponding to the roller guide groove at the point h by the shape of the cylindrical body 502 and the rotary rotor 504, and a circle corresponding to the roller guide groove at the point d There is an area difference in the portion adjacent to the roller 504a.

That is, since the area of the eccentric space S5 of the portion adjacent to the circular roller 504a at the point h is larger than the area of the eccentric space S5 adjacent to the circular roller 504a at the point d, Eventually, the rotary rotor 504 starts to rotate counterclockwise.

Here, of course, the area difference of the eccentric space (S5) is also applied to the d-c point and the c-b point.

Due to the above principle, the rotary rotor 504 is rotated by a predetermined angle so that the fluids in the eccentric space S5 are sequentially transferred to the eccentric space S6, and the fluid passed to the eccentric space S6 is the third plate. After being discharged through the fluid discharge window 531a formed at 531, as shown in FIG. 13, it is discharged to the outside of the wheel driving means 500 through the fluid discharge port 501b formed at the driving body 501.

The fluid discharged to the outside of the wheel drive means 500 is transferred along the line L60 and returned to the inside of the fluid storage tank 100 as shown in FIG. 1.

As mentioned above, according to the above-mentioned description, the wheel of a vehicle etc. becomes rotatable in the front-back direction.

As described above, according to the engine using the hydraulic pressure according to the present invention, the compressed air is generated using the hydraulic pressure, which is a fundamentally different structure compared to the existing engine, which is currently developed, and the compressed air and fuel are generated. By using the combustion gas generated by combustion together to generate the pressurized oil pressure, and by using the pressurized oil pressure by rotating the drive shaft of the wheel in the forward and reverse direction to enable the drive of the vehicle, the existing many engines have Problems can be solved.

Claims (17)

A fluid storage tank 100 in which a fluid is stored and which can flow in and out thereof; Compressed air generating means 200 for receiving the pressurized fluid to generate and discharge the air introduced from the outside in a compressed state, and to feed back the fluid used to generate the compressed air to the fluid storage tank (100); Fuel supply means 300 for supplying fuel; Combustion means (400) for combusting the fuel supplied from the fuel supply means (300) with the compressed air generated by the compressed air generation means (200); Wheel driving means 500 for rotating the driving rotary shaft 900 of the wheel in the forward and reverse directions depending on whether the fluid is supplied; The compressed combustion gas generated by the combustion means 300 is supplied to generate the fluid introduced from the fluid storage tank 100 into a pressurized fluid state, and a part of the fluid is discharged to the wheel driving means 500. And pressurized fluid generating means for discharging the used combustion gas 600; In addition to receiving and storing the remaining pressurized fluid generated from the pressurized fluid generating means 600, and the accumulating means 800 for discharging a portion of the stored pressurized fluid to the compressed air generating means 200, Hydraulic engine characterized in that. The method of claim 1, The compressed air generating means 200, A compressed air generator 220 for generating compressed air in both directions; A first controller (240) for controlling driving so that compressed air is discharged in both directions from the compressed air generator (220) by receiving the fluid discharged from the accumulating means (800); And a second controller (270) for controlling the driving of the first controller (240) according to the driving of the compressed air generator (220). The method of claim 2, The compressed air generator 220, A pair of left and right discharge ports 202 and 203 spaced apart by a predetermined distance, left and right balance ports 204 and 205 spaced apart from each other between the left and right discharge ports 202 and 203, and the left and right balance ports 204 A cylinder body 201 having common openings 206 and 207 spaced apart from each other in correspondence with the &lt; RTI ID = 0.0 &gt; 205 &lt; / RTI &gt; A piston rod 208 moved left and right in the longitudinal direction in the cylinder body 201; A pair of first pistons 209 and 210 which are formed to have a predetermined gap with the inner wall surface of the cylinder body 201 and are formed to be stepped with the piston rod 208 and are provided at both ends of the piston rod 208, respectively. )and; It is in close contact with the inner surface of the cylinder body 201 is slidably installed, and is formed to be stepped with the first piston 209 (210) and a pair of provided at each end of the first piston (209, 210) Second pistons 211 and 212; It is disposed on the inner wall surface of the cylinder body 201 corresponding to the left and right discharge ports 202, 203, the inner surface is in close contact with the outer surface of the first piston 209, 210, the piston rod In contact with the outer surface of the 208 in close contact with the guide portion 213a protruding from the inner surface to guide the left and right, and the left and right balance port 204, 205 and the common port 206, 207 are communicated with A rod guide 213 having communication ports 214, 215, 214a and 215a; Left and right covers 216 and 217 installed at both ends of the cylinder body 201; Two pairs of left and right covers 216 and 217, respectively, are installed in the air to the two left and right spaces S1 and S2 formed between the second piston 211 and 212 and both ends of the cylinder body 201. Engine using a hydraulic pressure, characterized in that consisting of check valves (218) (218a) (219) (219a) for the air inlet / outlet to enable the inlet and outlet of the. The method of claim 2, The first controller 240, Common ports 222 and 223 which serve as inflow and outflow of fluid to and from the compressed air generator 220, and a single inlet port 224 through which some pressurized fluid of the pressure storage means 800 is discharged and introduced; It is formed with the inlet port 224 in the middle and has two drain ports 225 and 226 connected to the fluid storage tank 100 and a direction switching outlet port 227, the inside of which is empty A direction switching valve body 221 having an opening shape at both ends; The inflow port 224 is slid close to the left and right directions by the elastic force of the spring 232a in the direction switching valve body 221 in accordance with the presence or absence of pressurized fluid flow into the direction switching inlet and outflow port 227. A direction switching valve body 230 to communicate with any one of the two common ports 222 and 223 and the other common port to communicate with any one of the two drain ports 225 and 226; An engine using hydraulic pressure, characterized in that the cover 232 is installed on the direction switching valve body 230. The method of claim 2, The second controller 270 is, Five first, second, third, fourth, and fifth space parts 242 (243), 244, 245 and 246 separated in order, and the first space part 242 The first slide hole 251 formed through the first partition wall 247 partitioning the second space portion 243, and the second partition partitioning the second space portion 243 and the third space portion 244. The second slide hole 252 formed through the wall 248 and branched from the second slide hole 252 to the second partition wall 248 are discharged / mouthed out of the fluid with the first controller 240. The third slide hole 253 formed through the direction switching discharge port 255 and the third partition wall 249 partitioning the third space portion 244 and the fourth space portion 245 so as to communicate with each other. And a fourth slide hole 254 formed through the fourth partition wall 250 partitioning the fourth space portion 245 and the fifth space portion 246, and the first space portion 242 and the first space portion 242. Four flues that allow each of the fifth space portions 246 to communicate with the compressed air generator 220. Ports 256, 257, 259 and 258, and inlet ports through which some fluid of the accumulating means 800 is discharged and introduced into the second space portion 243 and the fourth space portion 245. A control valve body 241 having 261 and 262 for controlling the direction switching valve; It is installed in the first slide hole 251 so as to be slidably moved from side to side to close and open the second slide hole 252 to control the communication between the discharge port 255 for switching the direction and the inlet port 261. A first control valve body 263; A first slide member 264 installed in the first space 242 so as to be slidably close to the elastic force of the spring 268, and fixed to one end of the first control valve body 263; The third and fourth slides (244, 245) are installed in close proximity to the left and right to move the slide, while opening and closing the third slide hole 253, the discharge port 255 and the inlet port (262) for switching direction A second control valve element 265 for intermittent communication of the &lt; RTI ID = 0.0 &gt; In the fifth space 246 is installed to be in close slidable by the elastic force of the spring 268a, but consisting of a second slide member 266 fixed to one end of the second control valve body 265 Hydraulic engine characterized in that. The method of claim 3, wherein Cylinder liners 219b and 219a are further interposed between the second pistons 211 and 212 and the cylinder body 201, and end portions of the cylinder liners 219b and 219a and the rod guides ( An engine using hydraulic pressure, characterized in that the fluid is discharged to the left and right discharge ports (202, 203) by maintaining a gap between the ends of the (213). The method of claim 3, wherein The second pistons 211 and 212 have partition walls 211c for dividing the interior into first and second spaces S1 and S2 and correspond to the left and right covers 216 and 217. The opening of the two pistons 211 and 212 is provided with a closing member 211b for closing the first space S1 in a vacuum state. The first pistons 209 and 210 are formed in a hollow cylindrical shape and are coupled to one end of the second pistons 211 and 212 so as to communicate with the second space S2. The piston rod 208 is formed in a cylindrical shape with an empty inside is coupled to the first piston 209, 210, The partition wall 211c and the piston rod 208 are provided with check valves 211a and 208a, respectively. The first piston (211) (212) engine using a hydraulic pressure, characterized in that the communication hole (211d) is formed in communication with the inner wall surface of the cylinder liner (219b) (219a). The method of claim 1, The combustion means 400, A fuel injection nozzle 401 for spraying the fuel supplied from the fuel supply means 300 into an atomized state; An inner cylinder 402 having a lower opening shape surrounding the fuel injection nozzle 401 and having an air inlet 402a through which air is introduced; Ignition means (403) for igniting fuel sprayed from the fuel injection nozzle (401); It is installed to surround the inner cylinder 402 so that a predetermined space is made with the inner cylinder 402, and an air inlet 404a is provided on the upper side so that the compressed air generated by the compressed air generating means 200 is introduced. It is provided, the engine using a hydraulic pressure, characterized in that made of a closed outer cylinder 404 is provided with an exhaust port 404b for discharging the combustion gas in which fuel and air is combusted by the ignition means 403 . The method of claim 8, Compressed air flowing into the inlet 404a of the outer cylinder 404 from the combustion means 400 An air inlet 402a of the inner cylinder 402 configured to burn a portion of the heavy compressed air with fuel in the inner cylinder 402; The inner cylinder 402 configured to mix with the combustion gas at the end of the inner cylinder while the remaining compressed air flows out along the outer circumferential surface of the inner cylinder 402 from the combustion means 400 to cool the inner cylinder 402. Sufficient space S between the outer cylinder 404; The hot water having a high calorific value is injected into the lower end of the outer cylinder 404, which is a point after the combustion is completely completed in the inner cylinder 402 of the combustion means 400, thereby lowering the high temperature of the compressed combustion gas and high temperature. Engine using hydraulic pressure, characterized in that the hot water nozzle 405 is further provided to the combustion means 400 outlet side to guide the expansion of the number of steam The method of claim 1, The pressurized fluid generating means 600, A pressurized fluid generator 610; Combustion gas alternating feeder for operating the pressurized fluid generator 610 to generate the pressurized fluid by alternately supplying the compressed combustion gas generated by the combustion means 400 to the left and right of the pressurized fluid generator 610 ( 640 and 640 '; And a controller 670 for bypassing a portion of the pressurized fluid generated according to the driving of the pressurized fluid generator 610 so that the combustion gas alternating feeders 640 and 640 'are alternately driven and controlled. Hydraulic engine. The method of claim 10, The pressurized fluid generator 610, A pair of left and right fluid discharge ports 612 and 613 spaced apart by a predetermined distance, left and right balance ports 614 and 615 spaced apart from each other between the left and right fluid discharge ports 612 and 613, and the left and right fluid discharge ports A pair of fluid inlet ports 616 and 619 spaced apart from each other by a predetermined distance corresponding to the ports 612 and 613 and the left and right balance ports 614 and 615 and the fluid; It is provided with a pair of fluid discharge ports 618 and 6417 spaced apart by a predetermined distance between the inflow ports 616 and 619 and connected to the accumulating means 800, and the cylinder body having an open shape at both ends of which is empty. 611; A piston rod 620 which is moved left and right in the longitudinal direction in the cylinder body 611; A pair of first pistons 621 and 622 which are formed to have a predetermined gap with the inner wall surface of the cylinder body 611 and are formed stepwise with the piston rod 620 and are provided at both ends of the piston rod 620, respectively. )and; It is in close contact with the inner surface of the cylinder body 611 is slidably installed, and is formed to be stepped with the first piston 621, 622 is provided in each end of the pair of first piston 621, 622 Second pistons 623 and 624; It is disposed on the inner wall surface of the cylinder body 611 corresponding to the left and right fluid discharge port 612, 613, the inner surface is in intimate contact with the outer surface of the first piston 621, 622, the piston A guide part 625a protruding from the inner surface to guide the left and right in close contact with the outer surface of the rod 620, the left and right balance ports 614 and 615 of the cylinder body 611 and the fluid inlet port ( A rod guide 625 having communication ports 630, 631, 626, 627, 628, 629 in communication with 616, 619 and fluid discharge ports 618, 617; Left and right covers 632 and 633 provided at both ends of the cylinder body 611; Fluid inlet / outlet check valves 634, 635, 636 and 637 installed on the fluid inlet ports 616 and 619 and the fluid outlet ports 618 and 617 of the cylinder body 611. Engine using hydraulic pressure, characterized in that made. The method of claim 10, The combustion gas alternate supply 640, 640 ', Combustion gas introduced through the combustion gas first inlet port (642, 642 ') and the combustion gas first inlet port (642, 642') for the first time the compressed combustion gas generated in the combustion means 400 is introduced Combustion gas discharge ports 643 and 643 'for discharging into the left and right spaces S1 and S2 formed between the second pistons 623 and 624 and the left and right covers 632 and 633, respectively. First exhaust ports 644 and 644 'through which the combustion gas in the spaces S1 and S2 are first exhausted, and combustion gases exhausted through the first exhaust ports 644 and 644' are exhausted to the outside. Combustion gas exhaust ports 645 and 645 ', fluid inflow ports 646 and 646' through which pressurized fluid flows, and another fluid outflow and inflow port 647 through which fluid can be freely flowed in and out. 647 ') and the left and right direction switching valve body 641 (641') for switching the direction of the piston rod (620) from side to side; The left and right direction switching valve body 641, 641 'is moved in close contact with the vertical force by the spring force of the spring 651 (651'), the pressure to the fluid inlet port 646, 646 ' Depending on whether the fluid flows, the first and second inlet ports 642 and 642 'and the combustion gas discharge ports 643 and 643' of the left and right directional valve valves 641 and 641 'are opened and the combustion is performed. The first gas inlet port 644, 644 ′ and the combustion gas exhaust port 645, 645 ′ communicate with each other, and the first inlet port 642 of the left and right directional valve valves 641, 641 ′ is in communication with each other. And the combustion gas discharge ports 644 and 644 'and the combustion gas exhaust ports 645 and 645' to communicate with each other. An engine using hydraulic pressure, characterized in that the left and right direction switching valve body (650) (650 '). The method of claim 10, The controller 670 is, Five first, second, third, fourth, and fifth space parts 672, 673, 674, 675 and 676 sequentially divided and the first space part 672 and the fifth space part. The first slide hole 680a formed through the first partition wall 680 partitioning the second space portion 673, and the second partition wall partitioning the second space portion 673 and the third space portion 674. A second slide hole (681a) penetrated through the (681), and branched from the second slide hole (681a) to the second partition wall (681) to allow the flow of fluid with the pressurized fluid generator (610). A third slide hole 682a formed through the direction switching discharge port 681b, a third partition wall 682 dividing the third space part 674 and the fourth space part 675, and the first A fourth slide hole 691 formed through the fourth partition wall 683a that divides the fourth space portion 675 and the fifth space portion 676, and the first space portion 672 and the fifth space portion. 676 to communicate each with the pressurized fluid generator 610. Some pressurized fluids of the accumulating means 800 are discharged into the two connection ports 685, 686, 687, and 688, and the second space 673 and the fourth space 667. A control valve body 671 having an inlet port 690 and a discharge port 690a through which the pressurized fluid is drained back to the fluid storage tank 100 to control the direction switching valve; It is installed in the first slide hole 680a so as to be slidably moved from side to side to close and open the second slide hole 681a to control the communication between the direction switching discharge port 681b and the inlet port 690. A first control valve body 692; A first slide member 693 installed in the first space 672 so as to be intimately slidable by an elastic force of the spring 694, and fixed to one end of the first control valve body 692; The third and fourth slide holes 674 and 675 are installed to be slidably moved from side to side in close contact with each other so as to open and close the third slide hole 682a and discharge direction 681a and the inlet port ( A second control valve body 695 for intermittently communicating 690a; In the fifth space portion 676 is provided to be in close slidable by the elastic force of the spring (697), consisting of a second slide member 696 fixed to one end of the second control valve body (695) Hydraulic engine characterized in that. The method of claim 1, The wheel drive means 500, A pressurized fluid inlet 501a is formed in the front portion so that the pressurized fluid generated by the pressurized fluid generating means 600 is introduced therein, and a fluid outlet 501b is provided in the lower rear side thereof, and the inside of the hollow shape is driven. A main body 501; A rotation shaft 900 rotatably installed in the driving body 501 and connected to the wheel; It is installed perpendicularly to the inner front end of the drive body 501, the through-hole 530b through which the rotating shaft 900 is formed is formed in the center, the fluid introduced through the pressurized fluid inlet 501a to the peripheral portion A first plate 530 on which a fluid supply window 530a in a predetermined section is formed; An inner rear end portion of the driving body 501 is vertically spaced apart from the first plate 530, and a through hole 531b is formed in the center thereof to penetrate the rotating shaft 900, and the fluid supply window 530a. A second plate 531 having a fluid discharge window 531a in a predetermined section through which the fluid is discharged to the periphery thereof so as not to correspond to the periphery; The first and second plates 530 and 531 are interposed between the first and second plates 530 and 531 so as to be elastically movable up and down in the driving body 501, and both ends of the first and second plates 530 and 531. A cylindrical opening 502 having a bilateral opening in intimate contact with; A circular roller 503 having a predetermined length; The roller guide groove 504a, which is accommodated in the cylindrical body 502 and coupled to the rotational shaft 900, is inserted into the circular roller 503 so that it can be lifted and lowered elastically on the outer peripheral surface radially from the center point. A plurality of rotation rotors 504 are formed and a plurality of fluid feeding paths 504c are formed on a vertical inner surface forming the roller guide grooves 504a; Receiving a portion of the pressurized fluid generated by the pressurized fluid generating means 600 to move the cylindrical body 502 with the elastic force of the spring 520 in the vertical direction to forward and reverse rotational speed of the drive rotary shaft 900 Engine using hydraulic pressure, characterized in that it comprises a transmission means for accelerating (510). The method of claim 13, The shift means 510, A transmission main body 511 which is provided on an upper side of the driving body 501 and has a partition wall 511a for partitioning an internal space up and down; A piston 512a is slidably installed in the lower space S1 of the transmission body 511, and an upper end thereof is positioned in the upper space S2 through the partition wall 511a, and a lower end thereof is driven. It includes a shift plunger 512 penetrates the body 501 to contact the outer peripheral surface of the cylindrical body 502, Two branch conduits 514 and 513 are branched on the pressurized fluid inlet pipe 516 flowing into the pressurized fluid inlet, one of which is connected to the lower space S1, and the other is connected to the upper space ( In communication with S2), A pressure reducing valve 515 is provided on the branch line 513 connected to the upper space S2, and a reverse valve 517 is provided on the branch line 514 connected to the lower space S1. . The method of claim 14, Fly wheel 900a on the rotating shaft 900 of the wheel driving means 500 to evenly rotate the rotational power of the rotating shaft 900 having pulsation by a pressurized fluid having an unspecified pulsating pressure supplied to the wheel driving means 500. ) Is an engine using hydraulic pressure, characterized in that is further provided The method of claim 1, A cooling tank (700) filled with cooling water for receiving the compressed air generating means (200), the combustion means (400) and the pressurized fluid generating means (600) and cooling them; The first inlet 711 into which the outside air is introduced and the waste combustion gas supplied to the second outlet 712 and the pressurized fluid generating unit 600 which are sucked into the compressed air generating unit 200 are used. It has a third inlet 713 and the fourth discharge port 714 through which the introduced waste combustion gas is discharged, and rotates when the outside air and the waste combustion gas pass through both ends of the same shaft 715. A first turbocharger 710 having a first and a second fan 716, 717; The first inlet 723 through which the waste combustion gas discharged from the second outlet 714 of the first turbocharger 710 is introduced, the second outlet 724 through which the introduced waste combustion gas is discharged, and the cooling tank ( The third inlet 721 into which the wet steam flows into the 700 and the introduced wet steam are discharged in the condensed water state, a part of which is supplied to the combustion means 400, and the rest of which is supplied to the pressurized fluid generating means 600. And a fourth outlet 722 having third and fourth fans 727 and 726 that are rotated when the waste combustion gas and the wet steam pass at both ends thereof through the same shaft 725. A second turbocharger 720; A pump 730 installed on a fourth outlet 722 of the second turbocharger 720; Further a heat exchanger 740 for heat-exchanging the waste combustion gas discharged from the fourth outlet 722 of the second turbocharger 720 to extract only the coolant contained in the double again and bypasses the cooling water 700 to the cooling tank 700. An engine using hydraulic pressure, characterized in that it is provided.