JP2000265853A - Thermal engine capable of independently selecting compression ratio and expansion ratio - Google Patents

Abstract

PROBLEM TO BE SOLVED: To generate the power making use of the energy small in temperature difference such as that of the solar light by continuously arranging a low- temperature cylinder, a compression cylinder, a high-temperature cylinder and an expansion cylinder, and operating adjacent pistons with the specified phase difference. SOLUTION: A low-temperature cylinder 10, a compression cylinder 12, a high-temperature cylinder 30 and an expansion cylinder 32 are continuously arranged, and adjacent pistons are operated with the phase difference of 180 deg.. A heater 1 is provided in the middle of a pipe in which a working fluid flows between the cylinders 12, 30, and a cooler 2 is provided in the middle of a pipe in which a working fluid flows between the cylinders 32, 10. The working fluid is adiabatically compressed by the movement of the pistons 11, 13 in the cylinders 10, 12, and the working fluid is isochorically heated by the movement of the pistons 13, 31 in the cylinders 12, 30. The working fluid is adiabatically expanded by the movement of the pistons 31, 33 in the cylinders 30, 32, the working fluid is cool-compressed by the movement of the pistons 33, 11 in the cylinders 32, 10, and the motion of these pistons is taken out as the power.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention improves the thermal efficiency of a heat engine and makes effective use of available heat energy. Energy is the foundation of industry and can be used as a power source for all types of power currently used, such as generators, cars and ships. Effective use is made of natural energy such as solar heat, ocean temperature difference, and other energy with a small temperature difference.

[0002]

2. Description of the Related Art In thermodynamics, the Carnot cycle is the heat engine with the highest thermal efficiency. The reason is that it is a reversible engine in a closed container. But the Carnot Institute has not been realized. The Stirling engine is a reversible engine because the displacer reciprocates in a closed container in the same manner as the Carnot cycle, and the process can be operated in either direction. Therefore, the thermal efficiency is assumed to be the same as that of the Carnot cycle. However, the thermal efficiency is very low in practice. There are various reasons, but the biggest reason is that the dead space other than the stroke volume is large. However, the dead space is a passage for the working fluid and cannot be reduced to zero as long as there are heaters, heat exchangers, and coolers. Enlarging these devices to improve heat exchange only wastefully expands and contracts the working fluid in the dead space. For this reason, the thermal efficiency of the Stirling engine is not improved. However, since the Stirling engine is of an external combustion type, it has little effect of exhaust gas pollution due to combustion, has no impact noise due to explosion combustion, and has low noise.

Since a gasoline engine or a diesel engine has almost no dead space, its thermal efficiency is good. However, it is cooling while being a heat engine. Therefore, the theoretical thermal efficiency based on thermodynamics and the thermal efficiency based on actual equipment are far apart. The theoretical thermal efficiency of the Otto cycle, which is the mainstream of today's engines, is equivalent to the thermal efficiency of the Carnot cycle that operates between high and low temperatures. However, the high temperature is the combustion temperature,
Cool because the material is intolerable. The exhaust gas temperature is accordingly higher. However, the thermal efficiency is 25% to 30%. When the temperature on the high temperature side decreases, the pressure decreases and the output decreases. The higher the temperature, the higher the pressure and the higher the output.

In a gasoline engine or a diesel engine, one cylinder piston performs four strokes of working fluid intake, compression, ignition combustion heating expansion, and exhaust. Therefore, the compression ratio = expansion ratio. Therefore, the exhaust gas of the engine is not sufficiently expanded and is discharged while having high temperature and high pressure energy. A turbine is provided in the exhaust path to effectively use the energy of the exhaust gas, and the power of the turbine is used to compress the intake air to increase the output and thermal efficiency. This device is called a turbo. However, the thermal efficiency of the turbo itself is not good. Turbo is no longer necessary if the engine is fully expanded.

[0005]

SUMMARY OF THE INVENTION A heat engine having a theoretical thermal efficiency higher than that of the Carnot cycle is produced. If the thermal efficiency of the Otto cycle corresponds to the thermal efficiency of the Carnot cycle, the thermal efficiency of the Carnot cycle can be made larger by making the adiabatic expansion of the Otto cycle larger than the adiabatic compression. The Otto cycle is characterized by equal volume heating. The equal volume heating can obtain high temperature and high pressure with little heat energy. The expansion mechanism and compression mechanism are dedicated. The expansion ratio is increased so that the pressure of the working fluid after the completion of the expansion becomes the pressure before the suction. Do not cool the engine. Keeps warm and prevents heat loss. When the engine is cooled, the effect is reduced by half even if the compression ratio or the high temperature is increased. Determine the maximum temperature for the heat resistant temperature of the material and keep it warm to prevent heat loss. Since the combustion temperature is high between the internal combustion engines, an external combustion engine is used and a heat exchanger is attached. Since the external combustion engine burns at normal pressure, the combustion temperature is low and the exhaust gas is less polluted. Further, since the heat exchanger is used as a heat source, any heat source such as waste heat, reaction heat, hot spring heat and the like can be used.

[0006]

FIG. 9 is a diagram illustrating the principle of operation of the present invention. The heat engine runs in a closed cycle. 4 cylinders
Connect the individual piston with one rod. Strokes are the same. From the left, a low-temperature cylinder (10), a compression cylinder (12), a high-temperature cylinder (30), and an expansion cylinder (32). The heater (1) is placed between the compression cylinder (12) and the hot cylinder (30). Cooler (2) between expansion cylinder (32) and low-temperature cylinder (10)
Put. High temperature cylinder (30) and compression cylinder (12)
Have the same cross-sectional area. The cross-sectional area of each of the other cylinders is calculated as follows. If the stroke of each cylinder is the same, the sectional area ratio = volume ratio. Since the engine operates in a cycle, the moving mass of the working fluid in each stroke is the same. It is assumed that the working fluid is an ideal gas, and the working fluid follows the equation (1) of the ideal gas. Where p = pressure, V = volume, m = mass, R = gas constant, T = absolute temperature.

[0007]

(Equation 1)

[0008] The state formula of the working fluid in each cylinder is represented by a subscript. It is assumed that the low temperature cylinder before compression = 1, the compression cylinder after compression = 2, the high temperature cylinder before expansion = 3, and the expansion cylinder after expansion = 4. Based on the state of the working fluid in the low-temperature cylinder before compression. Equation 2 holds because the mass m of each step is the same and the gas constant R is common.

[0009]

(Equation 2)

In equation (2), V1 / V2 = compression ratio = ε2. The ratio of the cross-sectional area of the cold cylinder (10) to the compression cylinder (12) is ε2. When adiabatic compression is performed by setting the specific heat ratio of the working fluid to κ, the pressure p2 after compression is expressed by Equation 3 and the temperature T2 is expressed by Equation 4
It is represented by

[0011]

(Equation 3)

[0012]

(Equation 4)

If the volume of the heater (1) is constant and the sectional areas of the compression cylinder (12) and the high-temperature cylinder (30) are equal, there is no change in the volume due to the movement of the piston. When the working fluid is heated to the same volume and the heating temperature is given to determine the temperature T3, the pressure p3 is expressed by Expression 5.

[0014]

(Equation 5)

The pressure p3 according to the equation (5) is a state in which the heater (1) is entirely heated to T3, and the high-temperature cylinder (30)
In the initial state. The pressure p3 is adiabatically expanded to p4. If p4 = p1, the expansion pressure becomes the suction pressure for adiabatic compression. The adiabatic expansion ratio ε4 is represented by Expression 6.

[0016]

(Equation 6)

If p4 = p1 = atmospheric pressure = 1atm, p
3 becomes like Equation 7.

[0018]

(Equation 7)

The high temperature cylinder (30) and the expansion cylinder (3
The ratio of the cross-sectional areas in 2) is ε4. Temperature T4 after adiabatic expansion
Is represented by Equation 8.

[0020]

(Equation 8)

Since p4 = p1, the expansion cylinder (3
The ratio ε5 of the cross-sectional area between 2) and the low-temperature cylinder (10) is expressed by Expression 9.

[0022]

(Equation 9)

In summary, the sectional area of each cylinder is as follows. The cross-sectional area of the compression cylinder (12) is made smaller than that of the low-temperature cylinder (10), and the ratio of the cross-sectional area is the compression ratio ε2.
And Compression cylinder (12) and high temperature cylinder (30)
Have the same cross-sectional area. The cross-sectional area of the expansion cylinder (32) is made larger than that of the high-temperature cylinder (30), and the ratio of the cross-sectional areas is the expansion ratio ε4. The expansion cylinder (32) and the low-temperature cylinder (10) have the same pressure, and the ratio of the cross-sectional areas is the ratio ε5 between the temperature after expansion and the temperature after cooling. Since each stroke is the same, the cross-sectional area can be replaced by the stroke volume.

In FIG. 9, it is assumed that the piston moves without resistance and that the rod does not occupy the volume in the cylinder. Place the piston at the left end with such a device. FIG. 9 shows a position slightly moved to the right from the left end. The working fluid in each cylinder is in the following state. The inside of the low-temperature cylinder (10) is replaced with an uncompressed working fluid at the temperature after cooling. The inside of the compression cylinder (12) has the same pressure as the inside of the heater (1), and has a temperature mixed with the temperature after the adiabatic compression and the inside of the heater.
The inside of the high-temperature cylinder (30) is at the pressure and temperature after heating. The pressure inside the expansion cylinder (32) is the same as that of the cooler (2) and the low-temperature cylinder (10) at the temperature after the adiabatic expansion.

Free the piston. The piston moves to the right due to the pressure difference across the expansion piston (33). The compression piston (13) and the hot piston (31) have the same cross-sectional area and the same pressure, and the action of the forces acts in opposite directions, thus canceling each other. However, the working fluid in the compression cylinder (12) is pushed and enters the heater (1), where it is heated and the pressure increases. The working fluid in the expansion cylinder (32) is pushed, enters the cooler (2), is cooled and compressed, and enters the low temperature cylinder (10). Since the volume ratio of the two cylinders is the temperature ratio, the volume decreases as the temperature decreases, but the pressure does not change. Since the pressure is initially the same before and after the low temperature piston (11), the movement is free. As a result, the piston moves to the right. As the piston moves to the right, the pressure of the working fluid during expansion decreases and the pressure of the working fluid during compression increases. Eventually the pressure balances, but the piston reaches the right end due to inertia. The working fluid has moved by the volume of one cylinder. If only the piston is at the left end without changing the working fluid, it will be in the initial state. This concludes one process.

[0026]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described with reference to the drawings based on embodiments. FIG. 1 shows a heat engine which can be operated continuously based on the operation principle of FIG. Each cylinder is placed independently, with a phase angle of 18
Operated by 0 ° crankshaft (3) and crank (4). Cryogenic cylinder (10) and compression cylinder (12)
A compression ventilation path (20) having a compression ventilation valve (16) is provided therebetween. Similarly, an expansion ventilation passage (40) having an expansion ventilation valve (36) is provided between the high temperature cylinder (30) and the expansion cylinder (32). The low temperature cylinder (10) has a low temperature inlet valve (14), and the compression cylinder (12) has a compression outlet valve (1).
8) is provided. Similarly, the high temperature cylinder (30) is provided with a high temperature inlet valve (34), and the expansion cylinder (32) is provided with an expansion outlet valve (38). Each valve is switched by a cam (5) at the top dead center or the bottom dead center of the piston. Vent valve (16, 3
6) and the inlet / outlet valves (14, 18, 34, 38) are, in principle, not simultaneously opened to prevent the working fluid from penetrating. Since the gap at the top dead center of each piston is a dead space, it approaches zero. The size of the cylinder is the same as the concept in FIG. Compression cylinder (12) and high temperature cylinder (3
In the case of 0), when the stroke volume is small and operation is difficult with the same stroke of each piston, the diameter of the cylinder is increased and the stroke is reduced. Also, the stroke is changed by making the cylinder diameter equal.

The low temperature piston (11) and the high temperature piston (3)
1) is at the bottom dead center. It is assumed that the compression piston (13) and the expansion piston (33) are at the top dead center. All valves are closed. The crankshaft (3) rotates slightly to the right. Both vent valves (16, 36) open. The cold piston (11) rises, the compression piston (13) descends and the working fluid is gradually adiabatically compressed. The hot piston (31) rises, the expansion piston (33) descends and the working fluid adiabatically expands with the highest pressure difference. This expansion is the driving force. When the low temperature piston (11) and the high temperature piston (31) reach the top dead center, and the compression piston (13) and the expansion piston (33) reach the bottom dead center, the compression and the expansion are completed. Double ventilation valve (16, 36)
Closes.

The crankshaft (3) further rotates clockwise. The cold inlet valve (14), compression outlet valve (18), hot inlet valve (34), and expansion outlet valve (38) open. The expansion piston (31) goes up and the cold piston (11) goes down.
The working fluid moves from the expansion cylinder (30) through the cooler (2) to the cold cylinder (10). The working fluid is cooled and compressed, the specific volume decreases and the density increases while maintaining the pressure. In the compression cylinder (12), when the compression outlet valve (18) is opened, the working fluid flows backward from the high pressure heater (1) side. The pressure in the heater (1) decreases and the pressure in the compression cylinder (12) increases. Compression piston (1
3) goes up and the hot piston (31) goes down. The working fluid moves from the compression cylinder (12) through the heater (1) to the hot cylinder (30). The working fluid does not change in volume during movement, but is heated to a constant volume and the pressure and temperature rise. The low-temperature piston (11) and the high-temperature piston (31) have a bottom dead center, the compression piston (13) and the expansion piston (33) have a top dead center, and the valves (14, 18, 34, and 38) are closed to 1 The cycle is completed. Further, the crankshaft (3) rotates clockwise, and the cycle continues.

FIG. 2 shows a heat engine using the functions of FIG. 1 on both sides of each piston. In the principle diagram of FIG. 9, adiabatic compression, equal volume heating, adiabatic expansion, and cooling / compression of the working fluid are performed simultaneously. Similarly, in FIG. 2, during the expansion stroke, suction into the high-temperature cylinder (30) and exhaust from the expansion cylinder (32) are performed. During the compression stroke, suction into the low-temperature cylinder (10) and exhaust from the compression cylinder (12) are performed. As a result, the heat engine of FIG. 2 performs adiabatic compression, equal volume heating, adiabatic expansion, and cooling / compression simultaneously and continuously. In FIG. 1, the compression cylinder (1
2) The diameter of the high-temperature cylinder (30) is small, and it is difficult to secure a stroke by rotating the crank (4).
The problem can be solved by making the rod parallel to the cylinder.

FIG. 3 is a view in which the compression cylinder (12) of FIG. 2 is omitted when the temperature difference is small. When the temperature difference is small, when the temperature is increased by adiabatic compression, the temperature approaches or exceeds the heating temperature. Therefore, the heating calorie becomes smaller,
In addition, work by adiabatic expansion is used to compress the working fluid, so that the output is reduced and the thermal efficiency is reduced. The heat engine of the present invention calculates the expansion ratio and the compression ratio so that the maximum thermal efficiency is obtained according to the temperature difference between the heat sources. When the temperature difference becomes small, the expansion ratio and the cooling / compression ratio become the same, so that adiabatic compression becomes unnecessary. Therefore, the compression stroke is omitted, and the low-temperature piston (1) is used in the low-temperature cylinder (10).
In 1), a certain amount of the uncompressed working fluid is moved from the cooler (2) to the heater (1). In FIG. 3, the expansion piston (33) pushes the working fluid into the cooler (2) both during ascending and descending.
The low-temperature cylinder (10) also has a low-temperature piston (11)
While on the rise and fall, it receives the working fluid on one side and pushes it out on the other side. In the low-temperature cylinder (10), the low-temperature outlet valve (2
When (2, 23) is opened, the working fluid flows backward from the high pressure heater (1) side. The pressure of the heater (1) decreases, but when the working fluid enters the heater by the low temperature piston (11), the entire amount is heated and the heater returns to the original pressure. The stroke volume ratio is as follows. The cold cylinder (10) and hot cylinder (30) have the same volume. High temperature cylinder (30)
And the volume ratio of the expansion cylinder (32) is the expansion ratio. The volume ratio between the expansion cylinder (32) and the low-temperature cylinder (10) is the temperature ratio between the temperature after expansion and the temperature after cooling. This is Figure 9
It is the same idea.

In the heat engine of the present invention, the volume of the heater (1) and the volume of the cooler (2) do not become a dead space unlike the Stirling engine, but the volumes of the compression ventilation passages (20, 21) and the expansion ventilation passage ( 40, 41) The volume tends to be a dead space. Therefore, this volume is made as small as possible. Vent valve (1
6, 17, 36, 37) through the ventilation paths (20, 21, 40,
The influence of the dead space is reduced by providing the downstream side of 41). The dead space is a major factor especially for low temperature differential heat engines. In this case, the number of rotations is reduced, and the moving amount of the working fluid per time is reduced. And increase the cylinder volume,
The inflated ventilation passages (40, 41) are narrowed to make the dead space smaller overall.

FIG. 4 shows a heat engine composed of two cylinders, large and small. A heat engine in which the number of cylinders is reduced before and after a large piston (33) as an expansion cylinder (32) and a low-temperature cylinder (10), and before and after a small piston (31) as a high-temperature cylinder (30) and a compression cylinder (12). . The size of each cylinder is the same as in FIG.
On the basis of the ratio between the volume of the high-temperature cylinder (30) and the volume of the expansion cylinder (32), the ratio of the volume of the expansion cylinder (32) to the volume of the low-temperature cylinder (10) is determined by the thickness of the rod. Cryogenic cylinder (10) volume and compression cylinder (1
2) The volume is slightly compressed by the volume of the piston rod of the hot piston (31). Piston rods may be provided on both sides of the small piston (31) so that the compression cylinder (12) and the hot cylinder (30) have the same stroke volume.

FIG. 5 shows a heat engine using the principle diagram of FIG. 9 as a rotating piston. The left is the compressor and the right is the prime mover. In the compressor, a compressor rotor (6) is provided inside a compressor casing (60).
1) rotates. The compressor rotor (61) is provided with three compressor vanes (63). The space between the casing and the rotor is partitioned by vanes. This space is defined as an operation room. Two of the operation chambers are a low-temperature operation chamber (64) and a compression operation chamber (65). The other is an inlet / outlet chamber for the heater (1) and the cooler (2). It also serves as a partition for both. The prime mover has the same structure as the compressor. Two of the operation chambers are referred to as a high-temperature operation chamber (74) and an expansion operation chamber (75). Another one
One is an inlet / outlet chamber for the heater (1) and the cooler (2). It also serves as a partition for both. The shafts are directly connected and rotate synchronously. FIG. 5 shows a case where the piston in the principle diagram of FIG. 9 is at the left end or the right end. Each operation room is separated by a vane and is independent. In the working chamber connected to the heater (1), a small gap is formed between the working chamber and the casing because the rotor rotates, but the working fluid is divided into an inlet and an outlet. The pressure difference is the difference between the heater (1) pressure and the cooler (2) pressure. Since this pressure difference is large, always keep the vane in the middle. Therefore, the entrance chambers (63, 73) and the exit chambers (66, 76) are made small. The capacity of each operation chamber is the same as the concept in FIG. A feature of the rotary piston heat engine is that there is no ventilation path in the reciprocating heat engine, so that a dead space cannot be formed. The structure is simple because there is no valve.

FIG. 6 shows a heat engine in which the number of the vanes (62, 72) is four, the entrance chamber and the exit chamber are enlarged, and the movement of the vanes (62, 72) is moderated. FIG. 6 shows a case where the piston in the principle diagram of FIG. 9 is at the left end. Exit room (66,
In 76), the casing (60, 70) is provided with a bypass as indicated by a dotted line so that the working fluid flows freely so that the working fluid is not compressed until the vanes (62, 72) rotate from this position to the intermediate position. Therefore, it is the same as the passage of the working fluid without vanes. Further rotation to the right causes the vanes to enter the inlet chambers (63, 73). Entrance room (63,
At 73), a bypass is similarly provided in the casing (60, 70) to an intermediate position so that the working fluid can flow freely. The capacity of each operation chamber is the same as the concept in FIG.

FIG. 7 shows a heat engine which compresses and expands with one casing (50) and a rotor (51). The rotor (51) rotates in the casing (50). FIG. 7 is rotated rightward as indicated by the arrow. The rotor is provided with six vanes (52). The operating chamber leading to the heater (1) is divided into a compression outlet chamber (66) and a hot inlet chamber (73). The pressure difference between the two corresponds to the pressure drop of the heater (1). Between the position of the vane (52) in FIG. 7 and the partition, a bypass is provided in the casing to allow the working fluid to flow freely. The same applies to the working chamber leading to the cooler (2). However, when the compression ratio and expansion ratio increase, the low temperature inlet chamber (63),
The movement of the vane (52) in the expansion outlet chamber (76) becomes large, and in order to make this smooth, the number of the vanes (52) is increased by several and the curve of the casing (50) is made gentle. The upper left side of the operation chamber connected to the cooler (2) is a low-temperature operation chamber (64).
Becomes Further on the right side is a compression operation chamber (65). The right end is a passage leading to the heater (1). The lower right is the high temperature operation chamber (74), and the lower left is the expansion operation chamber (75). The capacity of each operation chamber is the same as the concept in FIG.

FIG. 8 shows a rotary piston heat engine in which the compression stroke of FIG. 7 is omitted. The operation is the same as in FIG. Rotor (5
1) has five operating chambers fitted with five vanes (52). Two are in the inlet and outlet chamber of the working fluid with the heat exchanger,
The use of two in the expansion stroke is the same as the concept of FIG. One only moves the working fluid from the low temperature section to the high temperature section. The volume of each operation chamber is as follows. The volumes of the low temperature operation chamber (64) and the high temperature operation chamber (74) are the same.
The volume ratio between the high-temperature operation chamber (74) and the expansion operation chamber (75) is the expansion ratio. Expansion operation chamber (75) and low temperature operation chamber (64)
Is a temperature ratio. Increasing the volume of the working chamber increases the movement of the vane (52). In this case, too, the number of vanes (52) is increased to make the movement of the vane (52) gentle, and the curve of the casing (50) is made gentle.

A regenerator (7) is provided in the heat engine in FIG. The heat engine of FIG. 3 can also be provided with a regenerator (7), but is omitted. 1 and 4, the regenerator (7) can be provided as a low temperature differential heat engine if the low temperature cylinder (10) and the compression cylinder (12) have the same volume, but they are omitted. The working fluid that has undergone adiabatic expansion has a certain temperature. The working fluid entering the heater (1) remains at the outlet temperature of the cooler (2). The two exchange heat to warm the working fluid before heating at the temperature after expansion. Accordingly, the burden on both the heater (1) and the cooler (2) is reduced, and the heat efficiency is increased.

FIG. 12 shows a method of using the waste heat of the high temperature differential heat engine as a heat source of the low temperature differential heat engine to increase the overall thermal efficiency. The temperature after the adiabatic expansion of the high temperature differential heat engine is sufficiently high and can be used as a heat source for the low temperature differential heat engine. The working fluid after the adiabatic expansion discharged from the high temperature differential heat engine of the right heat engine in FIG. 12 passes through the heat exchanger (8), enters the cooler (2), and enters the low temperature operation chamber. On the other hand, the working fluid discharged from the left low-temperature differential heat engine passes through the regenerator (7), enters the heat exchanger (8), is heated, and enters the high-temperature operating chamber of the low-temperature differential heat engine.
The thermal efficiency increases by the amount of heat recovered in the heat exchanger (8). Further, the load on the cooler (2) of the low temperature differential heat engine is reduced by installing the regenerator (7).

As shown in FIG. 13, when the regenerator (7) is eliminated, if the heat exchanger (8) can perform 100% heat exchange, the load on the cooler (2) of the high temperature difference heat engine is reduced, but the low temperature difference is reduced. Only the heat efficiency of the heat engine can be recovered, and the total heat efficiency is the same as the method of FIG. However, as long as there is a heat source, using several low temperature differential heat engines will increase the overall thermal efficiency.

The heat engine of the present invention changes the internal pressure in response to a load change. The heat engine of the present invention is an external combustion engine, and the working fluid is sealed. The working fluid on the high temperature side has a high pressure, and has a low pressure on the low temperature side. The mass of the sealed working fluid is constant. The expansion ratio and compression ratio do not change. Also, the temperature ratio is constant. Therefore, the mass of the working fluid in the heat engine is changed according to the load with respect to the load fluctuation. Changing the mass changes the amount of heat exchanged at a constant temperature. Changing the mass of the working fluid in a given volume changes the pressure. After all, the pressure in the heat engine is changed according to the load. As the pressure, the pressure after expansion or the pressure before compression is detected.

FIG. 14 is a system diagram of a control system. A pressure tank (85) for storing a working fluid in the heat engine is provided. When the load increases, the pressure regulating valve (86) opens and the cooler (2) opens
The working fluid is injected into the inlet. Working fluid immediately cooler (2), low temperature cylinder (10), compression cylinder (12)
To increase the internal pressure of the heat engine. Conversely, when the load decreases, the pressure-lowering regulating valve (87) is opened, and the working fluid before heating is collected in the pressure tank (85). The internal pressure of the heat engine decreases.
Thus, the internal pressure of the heat engine is increased or decreased according to the load,
At the same time, the fuel as an external combustion engine is increased or decreased by the fuel adjusting valve (81) so that the temperature is kept constant. However, the fuel control valve (81) adjusts the temperature change due to the transient change and the temperature change due to other disturbances. When the pressure on the side of the cooler (2) changes twice in a constant-temperature heat engine, the pressure on the side of the heater (1) also changes twice. When the pressure on the side of the cooler (2) changes from 1 atm to 2 atm, the pressure on the side of the heater (1) becomes 9.32 atm when the initial pressure is 4.66 atm. The output changes accordingly. In this way, the output can control the internal pressure of the heat engine and increase the output to an allowable pressure at the operating temperature.

[0042]

FIG. 10 shows the theoretical pV by the heat engine of the present invention.
It is an example of a diagram. The numbers representing the state of the working fluid in the graph of FIG. 10 are as follows. It is assumed that the low temperature cylinder before compression = 1, the compression cylinder after compression = 2, the high temperature cylinder before expansion = 3, and the expansion cylinder after expansion = 4. Based on the state of the working fluid in the low-temperature cylinder before compression. This number is also used as a subscript in the following formula. As an example, the working fluid is air.

Suppose that the following numbers are inserted in each step. Standard value of normal pressure and normal temperature Pressure P1 = 1atm = 101.33 kPa Temperature T1 = 300 ゜ K = 27 ° C. Specific heat ratio κ = 1.4 Specific volume v1 = RT1 / P1 = 0.85 kL / kg Compression ratio ε2 = 3 After heating Temperature T3 = 600 ゜ K Expansion ratio ε4 = 3.6

When adiabatic compression is performed at a compression ratio of ε2 = 3, the pressure becomes P2 = 4.66 atm as shown in Expression 10, and the temperature becomes Expression 1
As in the case of 1, T2 = 466 ゜ K. The specific volume is
As in 2, v2 = 0.283 kL / kg.

[0045]

(Equation 10)

[0046]

[Equation 11]

[0047]

(Equation 12)

When the compression outlet valve (18) opens after the adiabatic compression, the working fluid flows into the compression cylinder (12). The pressure in the heater (1) decreases and the pressure in the compression cylinder (12) increases. The value is determined by the heater (1) and the compression cylinder (1).
It depends on the volume ratio of 2). Assuming that the temperature after heating T3 = 600 ° K., the pressure after heating becomes P3 = 6 atm as shown in Expression 13.

[0049]

(Equation 13)

When adiabatic expansion is performed with an expansion ratio ε4 = 3.6, the pressure becomes P4 = 1 atm as shown in Expression 14, and the temperature becomes Expression 15
Thus, T4 = 359 ゜ K. Specific volume is v2 = v3
Therefore, v4 = 1.02 kL as shown in Expression 16.

[0051]

[Equation 14]

[0052]

(Equation 15)

[0053]

(Equation 16)

The working fluid after expansion is cooled. The cooler of the heat engine of the present invention has a constant volume, and the expansion cylinder volume and the low temperature cylinder volume are in a temperature ratio. P5 = P4 = 1atm = P1 without changing the pressure of the working fluid. Since the pressure is 1 atm, air does not flow in and out of any part of the pipe between the expansion cylinder outlet and the compression cylinder inlet to communicate with the atmosphere. Therefore, during this time the system is open and the work is zero. Temperature is T5 = 300３００K = T1
And The specific volume is v6 = 0.85 kL /
kg = v1. Cooling reduces specific volume, reduces internal energy, and thermal efficiency depends only on temperature. The thermal efficiency is 56% as shown in Expression 18.

[0055]

[Equation 17]

[0056]

(Equation 18)

The thermal efficiency of the Carno cycle depends on the high temperature and low temperature of the adiabatic change of the compression ratio = expansion ratio. The heat engine of the present invention has a compression ratio <expansion ratio and cannot be compared with a Carno cycle. Assuming that the compression ratio ε2 = 3 = expansion ratio, the thermal efficiency becomes ηL = 35.6% as shown in Expression 19. If ε4 = 3.6 = compression ratio in accordance with the expansion ratio, the thermal efficiency becomes ηH = 40.1% as shown in Expression 20. When the high-side temperature is set to 600 ° K and the low-side temperature is set to 300 ° K, the thermal efficiency of the Carno cycle is calculated.
5.66, and ηK = 50%.

[0058]

[Equation 19]

[0059]

(Equation 20)

[0060]

(Equation 21)

The engine of the present invention has both a compression ratio and an expansion ratio smaller than those of the Carno cycle, but has improved thermal efficiency. Since the Otto cycle is the compression ratio = expansion ratio, it becomes the thermal efficiency calculated by the Carno cycle. The thermal efficiency of Expression 18 is higher than the thermal efficiency of Expression 21 because the compression energy is small.

FIG. 11 is an example of a pV diagram of the low temperature differential heat engine. In the OTEC, low temperature differential operation is performed, eliminating the adiabatic compression stroke. The numbers representing the state of the working fluid in the graph of FIG. 11 are as follows. Low temperature cylinder before transfer =
1, high temperature cylinder before expansion = 2, expansion cylinder after expansion = 3. Based on the state of the working fluid in the low-temperature cylinder before transfer. This number is also used as a subscript in the following formula. As an example, the working fluid is air. The expansion ratio is calculated.

Let's look at each step of this operation. Suppose you put the following numbers in each step. Standard value of normal pressure and normal temperature Pressure P1 = 1atm = 101.33kPa Low temperature T1 = 10 ° C (283 ° K) High temperature T2 = 30 ° C (303 ° K) Specific heat ratio κ = 1.4 Specific volume v1 = RT1 / P1 = 0.802 kL / kg Expansion ratio ε4 = 1.05 Temperature after heating T2 = 303 Assuming K, the pressure is
P2 = 1.07 atm. The specific volume remains unchanged v1 = v2.

[0064]

(Equation 22)

Assuming that the adiabatic expansion ratio is ε4 = 1.05, the pressure is P3 = 1 atm as shown in Expression 23. The temperature is also the number 24
T3 = 297 ° K. The specific volume becomes v3 = 0.842 kL / kg as in Equation 25.

[0066]

(Equation 23)

[0067]

(Equation 24)

[0068]

(Equation 25)

When cooled, the pressure P4 = P3 = 1atm = p
One. Temperature T4 = 283２８K = T1. Since the specific volume is a temperature ratio, v4 = 0.802 kL / kg =
It becomes v1 and returns to the reference value.

[0070]

(Equation 26)

As described above, the cycle operation can be performed without the compression stroke. The thermal efficiency is 30% as shown in Equation 27.

[0072]

[Equation 27]

The thermal efficiency of the Carno cycle depends only on temperature. Therefore, the thermal efficiency is 6.6% as shown in Expression 28.

[0074]

[Equation 28]

Without the adiabatic compression stroke, the heater inlet temperature is the cooled temperature T1 = 283 ° K. This temperature is lower than the temperature after adiabatic expansion T3 = 297 ° K. The two are heat-exchanged by the regenerator (7). Since the working fluid mass is the same, the heat exchange efficiency appears only in the temperature change of both. Assuming that the heat exchange efficiency is 100%, the expanded temperature T3 = 297 ° K is cooled to T4 = 283 ° K. The temperature after cooling T1 = 283 ° K is heated to T1 ′ = 297 ° K. The thermal efficiency is theoretically 100% as shown in Expression 29.

[0076]

(Equation 29)

The fact that the thermal efficiency becomes 100% in theory is a characteristic of this low temperature differential heat engine. In particular, when this heat engine is used for ocean thermal energy conversion, the temperature drop of surface water is 6 ° C. or less under the above conditions, and the amount of low-temperature deep water used is minimized. This low temperature differential heat engine is suitable for use in which a heat source is circulated and used. The thermal efficiency of 100% can convert 100% of the amount of heat received as a heat engine, and is not a numerical value including the thermal efficiency on the heating side.

As shown in FIG. 12, two heat engines are connected, and a low temperature differential heat engine is operated by using the exhaust temperature after adiabatic expansion of a high temperature differential heat engine having a compression mechanism as a heat source. . The numerical values of the high-temperature differential heat engine and the calculated values are applied to the numerical values from Expression 10 to Expression 18. The heat source of the low temperature differential heat engine has an exhaust gas temperature of 359 K calculated by the equation (15). Assuming that the low-temperature side is 300 ° K and the calculations from Equations 22 to 27 are performed, the following is obtained. T1 = 300 ゜ K T2 = 359 ゜ K T3 = 341 ゜ K T4 = 300 ゜ K = T1 η = 30.5%

In FIG. 12, the amount of heat received by the heat exchanger (8) on the low temperature differential heat engine side is 30.5% of the exhaust heat amount of the high temperature differential heat engine. When all of this heat is output, the total thermal efficiency becomes 69.4% theoretically as shown in Expression 30.

[0080]

[Equation 30]

In FIG. 13, the regenerator (7) is omitted from FIG. Therefore, the heat exchanger (8) can perform 100% heat exchange. However, in the low temperature differential heat engine, heat is radiated to the cooler, and the thermal efficiency becomes 30.5%. Eventually, the total thermal efficiency is the same as Equation 30, which is 69.4%.

In the heat engine shown in FIG. 3 or FIG. 8, even a small change in the temperature does not significantly affect the thermal efficiency. If all of the exhaust heat is theoretically changed to the heat supplied by the regenerator (7), this heat engine becomes a heat engine with a theoretical heat efficiency of 100%. In an actual machine, there is mechanical loss, leakage, windage loss, heat radiation, conversion efficiency of a heat exchanger, etc., and the thermal efficiency does not reach 100%. However, the amount of heat of cooling, the amount of heat of exhaust, and the like, which are intentionally discarded, disappear.

[Brief description of the drawings]

FIG. 1 shows a principle diagram of a heat engine using a cylinder and a piston.

FIG. 2 is a principle view of a heat engine using both sides of a piston in the heat engine of FIG. 1;

FIG. 3 is a principle diagram of a low temperature differential heat engine in which a compression cylinder is omitted from the principle diagram of FIG. 2;

FIG. 4 is a heat engine having two cylinders.

FIG. 5 is a heat engine in which a direct acting piston is a rotating piston and a valve mechanism is eliminated. Put the compressor and turbine separately,
FIG. 4 is a sectional principle view of a heat engine having three vanes.

6 is a sectional principle view of the heat engine of FIG. 5 with four vanes.

FIG. 7 is a sectional principle view of a heat engine in which six vanes are installed on a rotor in order to perform compression and expansion with one case and a rotating piston.

8 is a sectional principle view of a low temperature differential heat engine in which a compression operation chamber is omitted from the heat engine of FIG. 7 and five vanes are installed in a rotor.

FIG. 9 shows a basic principle diagram of the present invention.

FIG. 10 is an example of a pV diagram of the heat engine according to the present invention.

FIG. 11 is a pV diagram 1 of the low temperature differential heat engine according to the present invention.
It is an example.

FIG. 12 is a heat engine system combining a high temperature difference and low temperature difference heat engine according to the present invention.

FIG. 13 is a heat engine system combining a high temperature difference and low temperature difference heat engine according to the present invention.

FIG. 14 is a system diagram of output control of a heat engine according to the present invention.

[Explanation of symbols]

 Reference Signs List 1 heater 2 cooler 3 crankshaft 4 crank 5 cam 6 camshaft 7 regenerator 8 heat exchanger 10 low-temperature cylinder 11 low-temperature piston 12 compression cylinder 13 compression piston 14 low-temperature inlet valve 15 low-temperature inlet valve 2 16 compression ventilation valve 17 compression Vent valve 2 18 Compression outlet valve 19 Compression outlet valve 2 20 Compression vent 21 Compression vent 2 30 High temperature cylinder 31 High temperature piston 32 Expansion cylinder 33 Expansion piston 34 High temperature inlet valve 35 High temperature inlet valve 2 36 Expansion vent valve 37 Expansion vent valve 2 38 Expansion outlet valve 39 Expansion outlet valve 2 40 Expansion air passage 41 Expansion air passage 2 50 Casing 51 Rotor 52 Vane 53 Shaft 60 Compressor casing 61 Compressor rotor 62 Compressor van 63 Low temperature inlet chamber 64 Low temperature operation chamber 65 Compressive operation Room 66 Compression outlet room 70 Expander case Ring 71 expander rotor 72 expander vane 73 high temperature inlet chamber 74 high temperature operating chamber 75 expansion operating chamber 76 expansion outlet chamber 80 temperature detector 81 fuel regulating valve 82 temperature controller 83 speed detector 84 pressure detector 85 pressure tank 86 pressurization Adjusting valve 87 Pressure reducing adjusting valve 88 Pressure regulator

Claims (10)

[Claims] 1. A low-temperature cylinder (10), a compression cylinder (12), a high-temperature cylinder (30), an expansion cylinder (3).
2) Four cylinders are provided. The adjacent piston is operated at a phase difference of 180 °. A heater (1) is provided between the compression cylinder (12) through which the working fluid flows and the high-temperature cylinder (30). Similarly, a cooler (2) is provided between the expansion cylinder (32) and the low-temperature cylinder (10). The stroke volume ratio of each cylinder is as follows. Cryogenic cylinder (1
The working fluid is adiabatically compressed by the movement of the pistons (11, 13), and is moved from the low-temperature cylinder (10) to the compression cylinder (12). Compression cylinder (12) and high temperature cylinder (3
The working fluid is heated to an equal volume by moving the pistons (13, 31) and moved from the compression cylinder (12) to the high-temperature cylinder (30). The volume ratio between the high-temperature cylinder (30) and the expansion cylinder (32) is defined as an expansion ratio. The working fluid is adiabatically expanded by the movement of the pistons (31, 33), and is moved from the high-temperature cylinder (30) to the expansion cylinder (32). The volume ratio between the expansion cylinder (32) and the low-temperature cylinder (10) is defined as the temperature ratio before and after the cooler (2), and the working fluid is cooled and compressed by the movement of the pistons (33, 11). (1
Move to 0). Pistons (11, 13, 31, 3
3) is a valve (14-18, 34-3) at the top dead center or the bottom dead center.
8) A heat engine that opens and closes and switches the working fluid passage to perform cycle operation. The function of claim 1 is provided before and after the piston (11, 13, 31, 33), and the working fluid is subjected to a suction stroke on the opposite side during a compression stroke in the low-temperature cylinder (10),
The compression cylinder (12) discharges to the heater (1) on the opposite side during the compression stroke. On the other hand, in the high temperature cylinder (30), the suction stroke is performed on the opposite side during the expansion stroke, and in the expansion cylinder (32), the exhaust stroke to the cooler (2) is performed on the opposite side during the expansion stroke. Thus, the pistons (11, 13, 3)
1, 33) Front and rear cylinders (10, 12, 30, 32)
A heat engine that performs alternating functions in a room. 3. A heat engine according to claim 2, wherein said heat engine operates with two heat sources having a low temperature difference, wherein said compression cylinder is omitted. 4. Four cylinder chambers are formed by using two large and small cylinders and a front and rear of a piston. The four cylinder chambers have the function of the heat engine of the first aspect. The expansion cylinder (32) is provided before the piston (33) of the large cylinder, and the low-temperature cylinder (10) is provided after the expansion cylinder. The high temperature cylinder (30) is located before the small cylinder piston (31), and the compression cylinder (12) is located behind the small cylinder piston (31). A heat engine that reduces the number of cylinders and pistons by making the ratio of the stroke volume of the expansion cylinder (32) and the low-temperature cylinder by the thickness of the piston rod. 5. A heat engine using the heat engine of claim 1 as a rotary piston, wherein three operating chambers are partitioned by three vanes (52) provided on a casing (50) and a rotor (51). Are made, and the shaft (53) is directly connected and rotated. One is a compressor and the other is a prime mover. A heater (1) is provided between the working fluid compressor outlet and the prime mover inlet. A cooler (2) is provided between the motor outlet and the compressor inlet. One of the working chambers of the compressor is an entrance / exit chamber to the external heat exchanger. The other two operation chambers are a low-temperature operation chamber (64) having a cylinder volume ratio of claim 1 and a compression operation chamber (65). Similarly, one of the operation chambers of the prime mover is an entrance / exit room for the external heat exchanger. A high-temperature operating chamber (7) having a cylinder volume ratio according to claim 1 and two other operating chambers.
4) and a rotary heat engine having an expansion operation chamber (75). 6. A rotary heat engine having the function of claim 5, wherein one working chamber is provided for each of the heater (1) and the cooler (2), and four vanes (52) are provided. 7. An operating chamber is formed by six or more vanes (52) provided on a casing (50) and a rotor (51). The four operation chambers are a low-temperature operation chamber (64), a compression operation chamber (65), a high-temperature operation chamber (74), and an expansion operation chamber (75) in the same manner as the cylinder volume ratio of claim 1, and the other are heaters. (1) A rotary heat engine serving as a communication chamber with the cooler (2). 8. The heat engine according to claim 7, wherein the heat engine is operated by two heat sources having a low temperature difference, wherein the number of vanes is reduced by one and the compression operation chamber is omitted. 9. The heat engine according to claim 3, wherein the working fluid after expansion and the working fluid before heating are heat-exchanged by a regenerator (7) to reduce a cooling load and a heating load. Heat engine. 10. The working fluid discharged from the heat engine according to claim 1, 2, 4, 5, 6, or 7 is used as a heat source. 8
Heat engine to drive the heat engine of the country.