JPH09113047A - Stirling apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a Starling apparatus which improves the performance by improving a heat regenerator disposed at the expansion side cylinder in a structure for improving the thermal storage performance in a two-piston drive type Stirling apparatus. SOLUTION: A plurality of gas impermeable partition plates 22 are obliquely provided in a cylindrical heat regenerator 20 to form the regenerator 20 by a plurality of oblique split pieces 21, which are so effectively used to increase the distance of the flow of gas due to the oblique flow of the compressed operating gas and expanded operating gas in the regenerator 20 to increase the thermal regenerating efficiency, thereby increasing the thermal storage amount.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a two-piston drive type Stirling machine in which an expansion side cylinder and a compression side cylinder communicate with each other through a gas flow path, and more particularly, a tubular heat regenerator arranged in the expansion side cylinder. To improve the heat storage performance of the.

[0002]

2. Description of the Related Art FIG. 2 is a schematic cross-sectional view of a two-piston drive type staring machine, wherein 1 is a compression side cylinder 11.
The compression piston 2 inserted in the
The expansion piston 3 inserted in the drive mechanism 3 is a crank mechanism that reciprocates the compression piston 1 and the expansion piston 2 with a certain phase difference, and the drive portion 4 is formed in front of the compression piston 1. A gas compression space 5 indicates a gas expansion space formed in front of the expansion piston 2. Reference numeral 6 denotes a gas flow path that connects the gas compression space 4 and the gas expansion space 5 to each other. In the gas flow path 6, a gap type heat exchanger 7 is arranged on the gas compression space 4 side, while the gas expansion space 5 is provided. A heat regenerator 8 and a heat exchanger (radiation fin) 9 are arranged on the side.

The expansion-side cylinder 12 is composed of an inner cylinder 13 and an outer cylinder 14, and the gas passage 6 and the gas expansion space 5 are provided between the inner cylinder 13 and the outer cylinder 14.
The heat regenerator 8 is housed in an annular space 15 formed so as to communicate with the heat regenerator.

At the bottom of the annular space 15, the gas inlet space 1 into which the working gas from the gas passage 6 first flows.
6 are formed as a ring-shaped cavity and are continuously formed, and a gas inlet 17 is formed at one location on the bottom surface of the gas inlet space 16. Therefore, the working gas flowing from the gas inlet 17 rises from the gas inlet space 16 and passes through the heat regenerator 8 to flow into the gas expansion space 5.

The gap type heat exchanger 7 provided in the compression side cylinder 11 is provided with a gap portion 19 between the outer peripheral wall of the inner cylinder of the cylinder and the inner peripheral wall of the outer cylinder having radiating fins. The heat is released to the outside when the compressed gas passing through the gap portion 19 passes. 10 is a compression piston 1 and an expansion piston 2
The flow path for back pressure adjustment in the rear space of and is shown.

With the above structure, when the driving unit 3 is driven first,
The compression piston 1 moves to the side of the gas compression space 4, and the working gas such as helium or nitrogen filling the gas compression space 4 that is difficult to liquefy is compressed. The compressed working gas is cooled by exchanging heat with the outside air in the gap type heat exchanger 7. Then, the working gas further flows into the heat regenerator 8 via the gas flow path 6. The working gas that has flowed into the heat regenerator 8 stores heat when passing through the filler inside, and the working gas flows into the gas expansion space 5.

After that, the expansion piston 2 in the gas expansion space 5 descends with a certain phase difference from the compression piston 1. As a result, the gas expansion space 5 is expanded, and the high-pressure working gas that has flowed into the gas expansion space 5 from the heat regenerator 8 expands rapidly, and the pressure of the working gas drops sharply, so that the working gas becomes a low temperature. Eventually, when the expansion piston 2 starts to rise and the compression piston 1 retracts, the working gas having a low temperature returns to the gas compression space 4 through the heat regenerator 8. At this time, cold heat is stored in the heat regenerator 8.

By the above-mentioned steps, one heat cycle is completed, and this step is repeated by the reciprocating movement of the driving section, whereby the temperature around the gas expansion space is gradually lowered.

[0009]

As described above, in the two-piston type Stirling machine for taking out cold heat by letting the compressed working gas and the expanded working gas come and go between the two cylinders through the heat regenerator 8, the heat regenerator 8 is used. Heat is stored such that high temperature compressed working gas draws high heat and low temperature expanded working gas draws cold, but the larger the amount of heat stored at that time, the more efficiently the Stirling machine can operate and the better the performance. It will be.

Therefore, in order to increase the amount of heat stored in the heat regenerator 8, the working gas is allowed to pass through the heat regenerator 8 over a long distance, so that the heat regenerator 8 is effectively used and the heat is regenerated. The efficiency can be improved. From this point of view, it is conceivable to increase the length of the tubular heat regenerator 8.

However, in the space area occupied by the components existing between the gas compression space and the gas expansion space such as the heat regenerator 8 and the gas flow path 6, the compressed working gas is sent to the gas expansion space, Also, when the expanded working gas returns to the gas compression space, it becomes a gas retention part, which becomes a dead volume that reduces the amount of effective gas that flows between the two cylinders, reducing the gas compression rate and reducing the performance of the Stirling machine. It causes to worsen. Therefore, the heat regenerator 8 whose length is simply increased as described above cannot be said to be an appropriate measure because the dead volume also increases due to the increase in the volume.

The present invention has been made in view of the above points, and a Stirling machine having improved performance by being modified into a heat regenerator capable of improving heat regeneration efficiency without increasing dead volume. The purpose is to provide.

[0013]

In order to achieve the above-mentioned object, the invention of claim 1 carries out a compression operation with a compression side cylinder through a tubular heat regenerator provided so as to surround the expansion side cylinder. In a Stirling machine in which gas and expansion working gas flow back and forth through a gas flow path and cold heat is taken out from the expansion side cylinder, a plurality of gas impermeable partition plates are obliquely interposed in the tubular heat regenerator. The gas is allowed to flow obliquely through each of the plurality of divided pieces for constituting the heat regenerator divided by the partition plates.

According to a second aspect of the invention, the compression working gas and the expansion working gas flow back and forth between the compression side cylinder and the compression side cylinder through the tubular heat regenerator provided so as to surround the expansion side cylinder. In the Stirling machine in which cold heat is taken out from the expansion side cylinder, the tubular heat regenerator has a gas-impermeable gap between split pieces formed by cutting in a plurality of diagonal directions. It is made by assembling and assembling by inserting a partition plate.

[0015]

Embodiments of the present invention will be described below with reference to the drawings.

As shown in FIG. 1, a tubular heat regenerator 20.
Is formed by a plurality of divided pieces 21 which are formed by cutting in an oblique direction at an appropriate inclination angle with respect to the axial direction p, that is, four divided pieces 21 in the embodiment. Then, a partition plate 22 formed of a gas-impermeable material such as resin or plastic is inserted between each of the split pieces 21, and each partition plate 22 and each of the split pieces are bonded using an adhesive or the like. 21 and 21 are bonded to each other to form a tubular heat regenerator 20.

Thus, structurally, a plurality of partition plates 22 are obliquely inserted into the tubular heat regenerator 20, and a plurality of inclined divided pieces 21 separated from each other by the partition plate 22 are assembled. With the heat regenerator 20, the working gas is the heat regenerator 20.
When passing through each of the divided pieces 21, the working gas is strongly affected by the gas flow obliquely flowing along the partition plates 22, 22 at both ends of the divided pieces 21 as shown by the arrow a in the figure.
As a whole, the inside of 1 will flow diagonally.

As a result of the working gas obliquely flowing in the heat regenerator 20 as described above, the working gas flowing distance becomes longer, the amount of heat stored in the heat regenerator 20 increases, and the heat regenerator of the same height is used. As compared with the case where the gas flows straight, the heat regeneration efficiency can be increased.

Further, even if the working gas passage distance becomes long,
Since it does not extend the conventionally thought cylindrical heat regenerator vertically long, there is no concern about increase in volume, it does not lead to increase in dead volume by reducing regeneration efficiency, and improves performance of Stirling equipment. You will be able to contribute.

[0020]

As described above, according to the first aspect of the present invention, the compression working gas and the expansion working gas are passed between the compression side cylinder and the compression side cylinder through the tubular heat regenerator provided so as to surround the expansion side cylinder. In the Stirling machine where the heat flow comes and goes from the expansion side cylinder through the gas flow path, the heat regenerator is inserted by diagonally interposing a gas impermeable partition plate formed of resin or plastic in the heat regenerator. Since it is a collective structure of a plurality of inclined divided pieces, the gas flowing through the heat regenerator flows obliquely in each inclined divided piece, and the gas flowing distance becomes long,
The heat regenerator is effectively used to increase the amount of heat storage and improve the heat regeneration efficiency.

Further, the flow of a gas advantageous for increasing the heat regeneration efficiency over a long distance can be achieved without adopting the method of vertically extending the cylindrical heat regenerator, which is increased in volume. With the heat regenerator of the present invention whose volume is suppressed, it is possible to provide a Stirling machine capable of improving the performance without inviting an increase in the dead volume that lowers the gas compression ratio of the Stirling machine.

According to a second aspect of the present invention, in a tubular heat regenerator, a plurality of divided pieces formed by cutting in an oblique direction are formed by interposing gas-impermeable partition plates between them.
It can be easily formed by binding with an adhesive, does not have a particularly complicated structure, and has a small number of parts and can be easily manufactured at low cost.

[Brief description of the drawings]

FIG. 1 is a structural perspective view of a heat regenerator of the present invention formed by a plurality of inclined divided pieces.

FIG. 2 is a schematic sectional view of a two-piston driven Stirling machine.

[Explanation of symbols]

 1 compression piston 2 expansion piston 4 gas compression space 5 gas expansion space 6 gas flow path 8 heat regenerator 11 compression side cylinder 12 expansion side cylinder 20 heat regenerator 21 split piece 22 partition plate

Claims (2)

[Claims] 1. The compression working gas and the expansion working gas flow back and forth between the compression side cylinder and the compression side cylinder through a tubular heat regenerator provided so as to surround the expansion side cylinder,
In a Stirling machine in which cold heat is taken out from the expansion side cylinder, a plurality of gas impermeable partition plates are obliquely intervened in the tubular heat regenerator, and the plurality of heat regenerators divided by these partition plates. A Stirling machine characterized in that gas is circulated obliquely through each of the divided pieces for construction. 2. The compression working gas and the expansion working gas move back and forth between the compression side cylinder and the compression side cylinder through a tubular heat regenerator provided so as to surround the expansion side cylinder,
In a Stirling machine in which cold heat is taken out from the expansion side cylinder, the tubular heat regenerator has a gas-impermeable gap between split pieces formed by cutting in a plurality of diagonal directions. A Stirling machine characterized by being assembled by binding and inserting a partition plate.