JP2002004941A - Stirling cycle equipment - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the power generating efficiency of stirling cycle equipment and increase the effective utilization factor of an exhaust gas. SOLUTION: This stirling cycle device comprises a heat input side cylinder chamber 5a and a radiating side cylinder chamber 5b where a working gas G is allowed to be come in and out in accompany with the operation of pistons 3a and 3b through a working gas passage 6a including a heat regenerator 8A, a radiator 9A for rediating the working gas G to the external on the side of the radiating side cylinder chamber 5 with respect to the heat regenerator 8A, and a heater 7A for heat exchanging the working gas G and an exhaust gas H of a combustion device 1 and heating the same, a catalyst layer X is formed for burning an unburned component contained in the exhaust gas H of the combustion device 1 by the action of a catalyst in a process for supplying the exhaust gas to the heater 7A.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a Stirling cycle device for executing a Stirling cycle using combustion exhaust gas for heating a working gas, and more particularly to a working gas accompanying a piston operation through a working gas passage provided with a heat regenerator. A heat input side cylinder chamber and a heat radiation side cylinder chamber that move back and forth are provided, and a radiator that radiates working gas to the outside on the heat radiation side cylinder chamber side than the heat regenerator, and the heat regenerator more than the heat regenerator. The present invention relates to a Stirling cycle device provided with a heater that heats working gas by exchanging heat with combustion exhaust gas of a combustion device on a side of a heat input side cylinder chamber to heat the working gas.

[0002]

2. Description of the Related Art Conventionally, in a Stirling cycle apparatus of this type, in order to heat working gas (that is, heat input to the apparatus) by using combustion exhaust gas of a combustion apparatus, the combustion exhaust gas discharged from the combustion apparatus is directly heated. It was introduced into the vessel to exchange heat with the working gas.

[0003]

However, since the heater simply exchanges heat between the combustion exhaust gas and the working gas through the heat transfer wall in the heater, the conventional Stirling cycle device uses the combustion exhaust gas as the combustion exhaust gas. The unburned components contained are not used for the operation of the equipment, but are discharged from the heater together with the exhaust gas after heat exchange, which reduces the effective utilization rate of the exhaust gas and the power generation efficiency of the Stirling cycle equipment. Therefore, there is a problem that the energy efficiency of the entire system including the combustion device is reduced. In this regard, there is still room for improvement in promoting energy saving and further increasing the output of the Stirling cycle device. .

[0004] In view of this situation, the main problems of the present invention are:
It is an object of the present invention to provide a Stirling cycle device that is effective in improving the effective utilization rate of the combustion exhaust gas and the power generation efficiency of the Stirling cycle device through a rational and simple improvement, and that is further superior in environmental protection.

[0005]

Means for Solving the Problems [1] In the invention according to the first aspect, a heat input side cylinder chamber and a heat radiation side cylinder chamber through which a working gas flows back and forth with a piston operation through a working gas passage provided with a heat regenerator. A radiator for radiating working gas to the outside on the side of the radiating side cylinder chamber relative to the heat regenerator, and a device for burning the working gas on the side of the heat input side cylinder chamber relative to the heat regenerator. In a Stirling cycle device provided with a heater that heats and exchanges heat with the combustion exhaust gas, a catalyst layer that combusts unburned components contained in the combustion exhaust gas of the combustion device by a catalytic action in a process of supplying the combustion exhaust gas to the heater. Provide.

That is, in the Stirling cycle, the efficiency increases as the working gas is heated to a higher temperature in the heating of the working gas by the heater, but according to the above configuration, the unburned components contained in the combustion exhaust gas of the combustion device are reduced. The combustion gas is burned by the catalytic action of the catalyst layer in the process of supplying the combustion exhaust gas to the heater, and the combustion heat of the unburned components increases the temperature of the combustion exhaust gas in the heater to heat the working gas to a higher temperature. As a result, the power generation efficiency of the Stirling cycle device can be effectively increased as compared with the conventional device, and the effective utilization rate of the combustion exhaust gas can be effectively increased. This makes it possible to make the Stirling cycle device more excellent in terms of production.

[0007] Further, the flue gas after heat exchange discharged from the heater does not contain unburned components or contains only a small amount of unburned components. In addition, it is possible to make the Stirling cycle device more excellent in terms of environmental protection.

[2] In the invention according to claim 2, claim 1
In carrying out the invention according to the first aspect, an engine or a gas turbine is used as the combustion device.

In other words, in this configuration, the combustion exhaust gas (so-called engine exhaust gas or turbine exhaust gas) discharged from the engine or gas turbine with the generation of power in the engine or gas turbine is supplied to the heater through the catalyst layer. Perform a Stirling cycle.

That is, with this configuration, in addition to the power generation by the engine or the gas turbine, the power generated by the Stirling cycle can be further obtained by effectively using the exhaust gas of the engine or the gas turbine. Power can be generated with high efficiency by the use of the catalyst layer, and thus a high-efficiency power generation system capable of obtaining extremely large power for the fuel supplied to the engine or the gas turbine as a whole can be provided. .

[3] In the invention according to claim 3, the invention according to claim 2
In carrying out the invention according to the present invention, an output shaft of a cycle device that outputs power generated in an execution Stirling cycle by the flow of working gas between the heat input side cylinder chamber and the heat radiation side cylinder chamber, and the engine or An output shaft on the drive source side that outputs the generated power of the gas turbine is connected to an input shaft of the same load device.

That is, according to this configuration, the power generated by the Stirling cycle using the exhaust gas of the engine or the gas turbine is added to the power generated by the engine or the gas turbine (assist power), and the output value is increased. These generated powers can be intensively input to the same load device, whereby the efficiency of the generated power as a whole system can be further improved, and the effects of the inventions according to claims 1 and 2 can be obtained. Together, it is a very useful system.

[0013]

FIG. 1 shows an engine-driven Stirling cycle device that performs a Stirling cycle and a reverse Stirling cycle in parallel.
a, the first to third pistons 3a, 3b, 3c as a first piston group, and the fourth to sixth pistons 4a, 4a,
4b and 4c are connected.

The first cylinder chamber 5a containing the first piston 3a and the second cylinder chamber 5b containing the second piston 3b communicate with each other through a working gas passage 6a.
a, heaters 7A in order from the first cylinder chamber 5a side,
A heat regenerator 8A and a radiator 9A are interposed.

The third cylinder chamber 5c, in which the third piston 3c is housed, communicates with the second cylinder chamber 5b through a working gas passage 6b, and the working gas passage 6b is connected to the side of the third cylinder chamber 5c. Heat absorber 10A, heat regenerator 11 in order from
A, a radiator 12A is interposed.

Similarly, a working gas passage 14 connects the fourth cylinder chamber 13a containing the fourth piston 4a and the fifth cylinder chamber 13b containing the fifth piston 4b.
a, heaters 7 in order from the fourth cylinder chamber 13a side.
B, a heat regenerator 8B, a radiator 9B, and a sixth cylinder chamber 13c in the working gas passage 14b for communicating the sixth cylinder chamber 13c containing the sixth piston 4c with the fifth cylinder chamber 13b. A heat absorber 10B, a heat regenerator 11B, and a radiator 12B are provided in this order from the side of 13c.

The heaters 7A and 7B are heat input sections for heating the working gas G by exchanging heat with the high-temperature gas H and heating the radiator 9A.
A, 9B, 12A, and 12B are heat-dissipating units that exchange heat between the working gas G and the cooling fluid W and radiate heat to the outside (in other words, a heat output unit whose temperature level is lower than that of the heat-input high-temperature gas H). The heat absorbers 10A and 10B are cold output units that exchange heat between the working gas G and the cooling fluid C to cool the cooling fluid C.

Further, the heat regenerators 8A, 8B, 11A, 11
B (regeneration heat exchanger) is composed of a gas permeable packed bed filled with a heat storage material, and has first and fourth cylinder chambers 5a, 13
The heat regenerators 8A and 8B on the side of the “a” receive heat when the working gas G flows between the first and fourth cylinder chambers 5a and 13a and the second and fifth cylinder chambers 5b and 13b due to the piston operation. First and fourth cylinder chambers 5 which are input side cylinder chambers
a, the stored heat of the passing working gas G from the side of 13a, and the passing working gas G from the side of the second and fifth cylinder chambers 5b, 13b which are the radiation side cylinder chambers are heated by the stored heat. Repeat that.

On the other hand, the third and sixth cylinder chambers 5c, 13c
The heat regenerators 11A and 11B on the side of the side move the working gas G between the third and sixth cylinder chambers 5c and 13c and the second and fifth cylinder chambers 5b and 13b due to the piston operation. Third and sixth cylinder chambers 5 which are cylinder chambers
The stored cold energy of the passing working gas G from the sides c and 13c is stored, and the passing working gas G from the second and fifth cylinder chambers 5b and 13b, which are the radiating cylinder chambers, is cooled by the stored cold energy. Repeat that.

Regarding the specific structure, the heaters 7A and 7B
A large number of heat transfer tubes 15 are annularly arranged side by side in a cylinder central axis direction inside the case 7x attached to the heads of the first and fourth cylinder chambers 5a and 13a. A gas inlet 7i for injecting the hot gas H into the central hole portion and a gas outlet 7o for discharging the hot gas H from the outer peripheral side of the heat transfer tube annular arrangement group are provided in the body case 7.
x, and the first and fourth cylinder chambers 5a, 13
a, one end of the heat transfer tube 15 having a U-shaped conduit is connected to the first and fourth cylinder chambers 5a and 13a, and the other end of the heat transfer tube 15 Are communicated with the working gas passages 6a and 14a.
The working gas G discharged and sucked by the a and 13a is heated by exchanging heat with the high-temperature gas H during the passage of the heat transfer tube 15 through the heat transfer tube 15.

On the other hand, the heat absorbing heat exchangers 10A and 10B
A triple heat transfer tube 16 composed of a bayonet-type inner tube, a middle tube surrounding the same, and an outer tube surrounding the same is placed in a state surrounding the third and sixth cylinder chambers 5c, 13c in the cylinder center axis direction. Arranged in parallel to the ring, the third with the piston operation
Working gas G discharged and sucked by the sixth cylinder chambers 5c and 13c
Is passed through the gap passage between the inner tube and the middle tube in each triple heat transfer tube 16, and in the passage process, each triple heat transfer tube 16
The fluid C to be cooled passed through the inside of the inner tube in the first embodiment and the gap passage between the middle tube and the outer tube in each triple heat transfer tube 16.
The cooling target fluid C is cooled by exchanging heat between the working gas G (for example, cold water or brine).

Further, the first and fourth cylinder chambers 5a, 13a
The radiators 9A and 9B on the side of the first and second radiators 9A and 9B each have a triple heat transfer tube 17 composed of a bayonet-type inner tube, a middle tube surrounding the same, and an outer tube surrounding the same.
The working gas G flowing back and forth between the working gas passages 6a and 14a in accordance with the piston operation is arranged in a gap between the inner pipe and the middle pipe in each triple heat transfer pipe 17 by arranging the working cylinder G in a ring shape surrounding the fourth cylinder chambers 5a and 13a. The cooling fluid W (for example, cooling water) is passed through the passages, and in the passage process, is passed through the inner tube of each triple heat transfer tube 17 and the gap passage between the middle tube and the outer tube of each triple heat transfer tube 17. ) And the working gas G are heat-exchanged to release the working gas G.

Similarly, the third and sixth cylinder chambers 5c, 13
The radiators 12A and 12B on the side of c are provided with a triple heat transfer tube 18 composed of a bayonet-type inner tube, a middle tube surrounding the same, and an outer tube surrounding the same, as viewed in the center direction of the cylinder center axis. , The sixth cylinder chambers 5c, 13c are arranged side by side in an annular shape so as to surround the cylinder chambers 5c, 13c.
b is passed through the gap passage between the inner pipe of each triple heat transfer tube 18 and the inside of the inner pipe of each triple heat transfer tube 18, and the working gas G of each triple heat transfer tube 18 in the passage process. The cooling fluid W and the working gas G, which pass through the clearance passage between the middle pipe and the outer pipe, exchange heat with the working gas G,
Has a structure to radiate heat.

The cooling target fluid C cooled by the heat absorbers 10A and 10B is used for various cooling purposes such as cooling and article cooling, and the radiators 9A, 9B, 12A and 12B release heat of the working gas G ( Cooling fluid W heated for cooling)
Is used for various heating applications such as hot water supply, heating, and article heating.

That is, in the above structure, the respective pistons 3a, 3b, 3c of the first piston group are operated in conjunction with each other in a predetermined phase difference relation, and the respective pistons 4a, 4b, 4c of the second piston group are similarly operated. By interlocking operation with a predetermined phase difference relation, a cylinder chamber pair of the first cylinder chamber 5a and the second cylinder chamber 5b and the fourth cylinder chamber 13a
And the fifth cylinder chamber 13b with respect to the cylinder chamber pair,
A Stirling cycle in which power is generated by heat input from the heaters 7A and 7B (that is, the heaters 7A and 7A in the first and fourth cylinder chambers 5a and 13a, which are cylinder chambers on the heat input side).
A power is generated by expanding the working gas G heated by the heating chamber 7B, and the expanded working gas G is dissipated by the radiators 9A and 9B to the second and fifth cylinder chambers 5 which are the radiating cylinder chambers.
b, 13b), and the generated power is output to the crankshaft 2.

In parallel with this Stirling cycle, the cylinder chamber pair of the second cylinder chamber 5b and the third cylinder chamber 5c and the cylinder chamber pair of the fifth cylinder chamber 13b and the sixth cylinder chamber 13c are , The reverse Stirling cycle (that is, the heat absorber 10) by the applied power from the engine 1 and the generated power of the Stirling cycle.
The working gas G is expanded in the third and sixth cylinder chambers 5c and 13c, which are the heat absorbing side cylinder chambers, with the heat absorbed in A and 10B, and the expanded working gas G is released in the radiators 12A and 12B. A cycle of compression in the second and fifth cylinder chambers 5b and 13b, which are the radiation-side cylinder chambers, is executed to make the heat pump function.

In order to execute the above-mentioned Stirling cycle, in the Stirling cycle device of this embodiment, the high-temperature gas H for heat input supplied to the heaters 7A and 7B is:
Combustion exhaust gas (engine exhaust gas) discharged from the connected engine 1 is supplied to both heaters 7 through gas supply paths 19A and 19B.
A, then supplied to the series 7B, also these gas supply passage 19A, the 19B, the catalyst layer to combust the unburned components such as H ₂ and CO contained in the combustion exhaust gas H of the connecting engine 1 by the catalytic action X catalytic converter 20A,
20B is interposed.

That is, in the effective use of the flue gas H of the connected engine 1 as a high-temperature gas for heat input, the unburned components contained in the flue gas H are burned by the catalyst layer X, and Heater 7A by combustion heat,
The temperature of the combustion exhaust gas at 7B is increased to heat the working gas G to a higher temperature, thereby increasing the power generation efficiency of the Stirling cycle and increasing the effective utilization rate of the combustion exhaust gas H.

A phase control device 21 changes the phase difference relationship between the first piston 3a with respect to the second and third pistons 3b and 3c and the phase difference relationship between the fourth piston 4a with respect to the fifth and sixth pistons 4b and 4c. By adjusting the phase difference relationship by the phase control device 21, the heaters 7A and 7B
Of heat input, heat absorption by heat absorbers 10A and 10B, heat release by heat radiators 9A, 9B, 12A and 12B, engine 1
By changing the ratio of the input power from the input device, the device characteristics are adjusted to a desired value.

22a and 23a are first and fourth pistons 3
Connecting rods a and 4a, 22b and 23b are connecting rods of the second and fifth pistons 3b and 4b, and 22c and 24c are connecting rods of the third and sixth pistons 3c and 4c.

The first and fourth pistons 3a, 4a and the third and sixth pistons 3c, 4c are respectively provided with cylinder chambers 5a, 13a, 5c, 13c on the piston tip side and piston bases communicating with the cylinder chambers. End side sub-cylinder chamber 5
a ', 13a', 5c ', 13c' (gas paths 6a, 14
a, 6b, and 14b), whereby the bending force constantly applied to the crankshaft 2 from the piston side due to the working gas pressure is reduced.

As the working gas G, various gases including helium gas and air can be used.

In short, in the Stirling cycle device of the present embodiment, the heat input side cylinder chambers 5a, 13a for moving the working gas G back and forth with the piston operation through the working gas passages 6a, 14a interposed with the heat regenerators 8A, 8B. And the heat-dissipating cylinder chambers 5b and 13b are provided.
A radiators 9A, 9B for radiating the working gas G to the outside on the side of the radiating cylinder chambers 5b, 13b than the radiators 9A, 9B, and A, 8B;
Cylinder chambers 5a, 5 on the heat input side rather than heat regenerators 8A, 8B
In an apparatus configuration in which heaters 7A and 7B for heating the working gas G by exchanging heat with the combustion exhaust gas H on the side of 3a are provided, unburned components contained in the combustion exhaust gas H are removed by the heaters 7A and 7B.
There is provided a catalyst layer X that is burned by a catalytic action in a process of supplying combustion exhaust gas to the fuel cell.

Further, the engine 1 is used as a combustion device as a combustion exhaust gas generation source.
a, 13a and the cycle device side output shaft 2a (the first and fourth crankshafts 2) that outputs the power generated in the execution Stirling cycle due to the flow of the working gas G between the radiating side cylinder chambers 5b and 13b. The output shaft 1a of the engine 1 is connected to the input shaft of the same load device (the input shaft of the portion where the reverse Stirling cycle is performed, that is, the crankshaft 2) by connecting the connecting rods 22a and 23a of the pistons 3a and 4a to each other.
Of the connecting rods 22 of the second and fifth pistons 3b and 4b
b, 23b and the connecting rods 22c, 24c of the third and sixth pistons 3c, 4c).

[Another Embodiment] Next, another embodiment of the present invention will be listed.

The catalyst of the catalyst layer X for combusting unburned components contained in the combustion exhaust gas H by a catalytic action may be any catalyst having a function of burning unburned components, such as a palladium-based catalyst or a platinum-based catalyst. Various structures can be used, and the structure of the catalyst layer X can adopt various structures such as a structure in which a catalyst supporting material is formed into a honeycomb structure and a structure in which a granular material is filled.

In the above-described embodiment, the catalyst layer X is interposed in the gas supply paths 19A and 19B for the heaters 7A and 7B.
A, 7B may be provided at the combustion exhaust gas inlet.

In the above-described embodiment, the output shaft 1a of the engine 1 and the output shaft 2a of the cycle device for outputting the generated power of the Stirling cycle are connected to the input shaft 2b of the same load device.
In this configuration, the combustion exhaust gas (engine exhaust gas) of the engine 1 is supplied as a working gas heating source to the heaters 7A and 7B of the Stirling cycle execution unit. Combustion exhaust gas (turbine exhaust gas) of the gas turbine in a configuration in which the output shaft of the cycle device that outputs the generated power of the Stirling cycle is connected to the input shaft of the same load device.
May be supplied to the heater of the Stirling cycle execution unit as a working gas heating source.

Further, in the embodiment of the invention according to claim 2, a system for inputting the power generated by an engine or a gas turbine as a combustion exhaust gas supply source to a heater and the power generated by a Stirling cycle to different load devices. It may be configured.

In the embodiment of the present invention, the combustion device as a combustion exhaust gas supply source for the heater is not limited to a combustion type power generation device such as an engine or a gas turbine, but may be used for heating or incineration. For example, the combustion device may be used for purposes other than power generation.

In the above-described embodiment, the apparatus for executing the Stirling cycle and the reverse Stirling cycle in parallel has been described. However, the present invention relates to the apparatus for executing only the Stirling cycle and the Stirling cycle in combination with another cycle such as the Rankine cycle. The present invention can be applied to various Stirling cycle devices such as a device that executes in a complex state, and the use of the power generated by the execution Stirling cycle is not limited to the heat pump drive, but may be any application.

In the above-described embodiment, the device configuration in which the first piston group and the second piston group execute two sets of Stirling cycles has been described, but the device configuration in which only one set of Stirling cycles is executed may be used. The specific structure of the Stirling cycle device to which the present invention is applied may be any.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view showing a device configuration.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Combustion apparatus, engine, turbine 1a Output shaft on drive source side 2a Output shaft on cycle equipment side 2b Input shaft of load device 3a, 3b Piston 5a Heat input side cylinder chamber 5b Radiation side cylinder chamber 6a Working gas passage 7A Heater 8A Heat regenerator 9A Radiator H Combustion exhaust gas X Catalyst layer

Claims (3)

[Claims] 1. A heat input side cylinder chamber and a heat radiation side cylinder chamber for allowing a working gas to flow back and forth with a piston operation through a working gas passage interposed with a heat regenerator, wherein the heat radiation side cylinder chamber is provided rather than the heat regenerator. A radiator for radiating the working gas to the outside on the side, and a heater for heating the working gas by exchanging heat with the combustion exhaust gas of the combustion device on the side of the heat input side cylinder chamber than the heat regenerator is provided. A Stirling cycle device, wherein a Stirling cycle device is provided with a catalyst layer that combusts unburned components contained in the combustion exhaust gas of the combustion device by a catalytic action in a process of supplying the combustion exhaust gas to the heater. 2. The Stirling cycle device according to claim 1, wherein an engine or a gas turbine is used as the combustion device. 3. An output shaft on a cycle device side for outputting power generated in an execution Stirling cycle due to a flow of working gas between the heat input side cylinder chamber and the heat radiation side cylinder chamber, and the engine or the gas turbine. 3. The Stirling cycle device according to claim 2, wherein an output shaft on the drive source side for outputting the generated power is connected to an input shaft of the same load device.