JPH09264191A - Stirling equipment volume chamber structure - Google Patents

Abstract

(57) Abstract: In a Stirling machine, it is possible to effectively achieve isothermalization in which a change in working gas in an expansion stroke or a compression stroke approaches an isothermal change. A working gas G flowing into a volume chamber 3 through a gas passage 4 having a regenerative heat exchanger 5 is used as an expansion or compression process in a Stirling cycle or a reverse Stirling cycle to change the volume of the volume chamber 3. In a Stirling machine that expands or compresses with expansion, the volume chamber 3 is divided into a plurality of compartments 3a each of which changes in volume in the process of expansion or compression.
To 3c, and among the sub-chambers 3a to 3c, the first sub-chamber 3a to which the gas passage 4 is connected and the other sub-chambers 3b and 3c.
Are communicated with each other through the compartment communication passages 7a and 7b, and the compartment communication passages 7a and 7b are provided with isothermal heat exchangers 8a and 8b for exchanging heat between the working gas G and the isothermal heating medium L.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a Stirling engine, a Stirling refrigerator / heat pump, or a Stirling machine such as a heat / power machine for carrying out a Stirling cycle and a reverse Stirling cycle in parallel. Structure of a Stirling machine that expands or compresses a working gas, which has flowed into a volume chamber through a gas passage equipped with a container, as a process of expansion or compression in a Stirling cycle or a reverse Stirling cycle with a volume change of the volume chamber. Regarding

[0002]

2. Description of the Related Art Conventionally, in a Stirling machine, expansion or compression of a working gas in an expansion chamber or a compression chamber (both chambers are collectively referred to as a volume chamber in this specification) causes an isothermal change according to a theoretical cycle. Expansion, accompanied by a temperature drop, and
It is known that compression causes adiabatic expansion and changes in adiabatic compression tendency with temperature rise, resulting in adiabatic loss and reducing device efficiency. In order to solve this problem, the following methods (a) to (c) have been proposed as means for isothermalizing the expansion and compression of the working gas in the volume chamber to approach isothermal changes.

(A) As shown in FIG. 7, the head of the cylinder 1 forming the volume chamber 3 has a conical shape, and the piston 2 also has a conical shape corresponding to the conical shape. The wall 1a is used as a finned heat transfer wall, and the cylinder chamber (volume chamber 3
A method of exchanging heat between the working gas G (inside) and the external heat medium L for isothermalization (that is, the heat source heat medium that maintains the working gas G at an isothermal temperature by exchanging heat with the working gas G).

(B) As shown in FIG. 8, the head of the cylinder 1 forming the volume chamber 3 is formed in a concavo-convex shape having a plurality of conical shapes, and the piston 2 is also formed in a concavo-convex shape corresponding thereto. Then, similarly to the above (a), the uneven wall 1a ′ of the cylinder head is used as a finned heat transfer wall to perform the expansion or compression process in the cylinder chamber (volume chamber 3).
A method of exchanging heat between the working gas G (inside) and the heat medium L for external isothermalization.

That is, in any of the methods (a) and (b), the heat transfer area between the working gas G in the volume chamber 3 and the external isothermal heating medium L is calculated based on the volume of the volume chamber 3. By ensuring a large value, heat exchange between the working gas G in the volume chamber 3 and the heat medium L for isothermalization is promoted, and thereby expansion or compression of the working gas G in the volume chamber 3 approaches an isothermal change. It is something to try.

(C) As shown in FIG. 9, the wall 1a "of the cylinder 1 forming the volume chamber 3 is provided with fins for exchanging heat between the working gas G in the cylinder chamber and the external heat medium L for isothermalization. Gas passage 4 to the cylinder chamber as well as a heat transfer wall
Has a structure in which the working gas G is introduced in the tangential direction of the circumferential surface of the cylinder chamber, and the working gas flows in from the gas passage opening 4a, whereby the cylinder chamber (inside the volume chamber 3)
A method of swirling the working gas G with.

That is, in this method (c), the working gas G in the volume chamber 3 is swirled to form the finned heat transfer wall formed by the working gas G in the volume chamber 3 and the cylinder wall 1a ". Maintain good heat transfer with the working gas G
The heat exchange with the isothermal heat transfer medium L is promoted so that the expansion and compression of the working gas G in the volume chamber 3 can be brought close to the isothermal change.

[0008]

However, the above (a)
In the method (b), when the piston 2 is near the top dead center (that is, when the distance between the piston 2 and the cylinder head is small), the working gas G in the volume chamber 3 and the outside Although a relatively high heat transfer coefficient with the isothermal heat medium L can be secured, when the piston 2 is located on the bottom dead center side and the distance between the piston 2 and the cylinder head is large, the volume Since the hydraulic diameter related to the heat transfer of the working gas G in the chamber 3 increases and the thermal resistance increases, the heat transfer coefficient between the working gas G in the volume chamber 3 and the external heat medium L for isothermalization. Therefore, the tendency of adiabatic change cannot be sufficiently avoided, and the effect of isothermalization that brings expansion and compression of the working gas G in the volume chamber 3 closer to the isothermal change is still low.

Further, in the method (c), a higher isothermal effect can be obtained and the device efficiency is improved to some extent as compared with the methods (a) and (b) by promoting heat exchange due to swirling flow. However, the achievement of isothermalization is still insufficient for the same reason as in (a) and (b), and the working gas G is swirled for the improvement in equipment efficiency due to the isothermal effect. A large proportion is a decrease in equipment efficiency (so-called flow loss) caused by energy consumption, and as a result, improvement in equipment efficiency due to isothermalization cannot be sufficiently achieved.

In view of the above situation, the main object of the present invention is to effectively expand or compress the working gas in the expansion chamber or the volume chamber as the compression chamber in the expansion or compression process of the Stirling cycle or the reverse Stirling cycle. Is to approach the isothermal change, and thereby to further improve the device efficiency of the Stirling machine.

[0011]

[Means for Solving the Problems]

[Invention of Claim 1] In the invention of Claim 1,
When the volume chamber 3 is used as the expansion chamber, the gas passage 4
From the first subchamber 3a to the first subchamber 3a and from the first subchamber 3a to the other subchambers 3b and 3c via the subchamber communication passages 7a and 7b, the volume of each of the subchambers 3a to 3c is increased. Although the working gas G is expanded in the compartments 3a to 3c, even if the expansion of the working gas G in each of the compartments 3a to 3c is accompanied by the temperature drop due to adiabatic expansion, in the case of the first compartment 3a, The first branch 3a is located in the first branch 3a.
While a large amount of working gas G including working gas G flowing out from the gas to the other compartments 3b and 3c flows in from the gas passage 4,
Since the adiabatic expansion in the first sub-chamber 3a is limited to that according to the volume change of the self-chamber, the temperature drop Δt1 due to the adiabatic expansion in the first sub-chamber 3a is calculated from the first sub-chamber 3a to the other sub-chambers 3b,
It is smaller than when there is no outflow of working gas to 3c.

Then, the first branch chamber 3a to the branch chamber communication passage 7a
The working gas G flowing into the next second compartment 3b via the heat exchanges with the isothermal heat transfer medium L in the compartment communication passage 7a while always maintaining a high heat transfer coefficient. ,
As a result, the temperature drop Δt1 in the first compartment 3a is recovered and then flows into the second compartment 3b.

Here, the second branch 3b is replaced by the second branch 3b.
In the case where the second branch chamber 3b is a branch chamber in which the working gas G flows out from b to the next third branch chamber 3c via the branch communication passage 7b, the second branch chamber 3b also has the same function as the first branch chamber 3a.
The temperature drop Δt2 due to the adiabatic expansion in the second compartment 3b is smaller than that when the working gas does not flow into the third compartment 3c, and thus the temperature drops Δt1 and Δt2 due to the adiabatic expansion in the respective compartments 3a and 3b. By being suppressed, the volumetric chamber 3 as a whole effectively achieves isothermal expansion that brings the expansion of the working gas G close to the isothermal change.

Further, when the second compartment 3b is a terminal compartment, the temperature drop due to adiabatic expansion is suppressed in the second compartment 3b because the working gas does not flow out from the second compartment 3b to the next compartment. However, since the temperature drop Δt1 due to the adiabatic expansion in the first compartment 3a is suppressed as described above, isothermalization that brings the expansion of the working gas G close to an isothermal change is effective for the volume chamber 3 as a whole. Will be achieved.

On the other hand, when the volume chamber 3 is used as a compression chamber, the other compartments 3c and 3b are connected to the first compartment 3a via the compartment communication passages 7b and 7a, and the first compartment 3a is connected to the gas passage 4.
The working gas G is compressed in each of the compartments 3a to 3c while the volume of each of the compartments 3a to 3c is reduced while the working gas 4 is flowing out to each of the compartments 3a to 3c. Even if it is accompanied by a temperature rise, when looking at the first compartment 3a, the working gas G whose temperature has risen due to adiabatic compression in the other compartments 3c, 3b is
The temperature rise is eliminated by heat exchange while maintaining a high heat transfer coefficient with the isothermal heat transfer medium L in the isothermal heat exchangers 8b and 8a in 7a, and then the other compartments 3c and 3b
While flowing into the compartment 3a and mixing with the working gas G in the first compartment 3a, the adiabatic compression in the first compartment 3a is limited to that according to the volume change of the own compartment, so the first compartment 3a
The temperature rise Δt1 due to the adiabatic compression is smaller than that in the case where the working gas does not flow from the other compartments 3c and 3b through the isothermal heat exchangers 8b and 8a.

Then, here, the second branch chamber 3b communicating with the first branch chamber 3a via the branch chamber communication passage 7a, and the next third branch chamber 3c from the second branch chamber 3b via the branch chamber communication passage 7b.
In the case of the branch chamber communicating with the second branch chamber 3b, the second branch chamber 3b is also the same as the case of the first branch chamber 3a.
The temperature rise Δt2 due to the adiabatic compression in Fig. 2 is smaller than that in the case where there is no working gas inflow from the third compartment 3c via the isothermal heat exchanger 8b.
By suppressing the temperature rise due to adiabatic compression in a and 3b, isothermalization that brings compression of the working gas G close to isothermal change is effectively achieved as a whole of the volume chamber 3.

If the second compartment 3b is a terminal compartment, the second compartment 3b does not flow into the second compartment 3b from the third compartment 3c via the isothermal heat exchanger 7b. In 3b, the temperature rise due to adiabatic compression occurs without being suppressed, but since the temperature rise Δt1 due to adiabatic compression in the first compartment 3a is suppressed as described above, the volume chamber 3 still remains.
As a whole, the isothermalization that brings the compression of the working gas G close to the isothermal change is effectively achieved.

That is, according to the first aspect of the invention, the hydraulic diameter relating to heat transfer between the working gas and the isothermal heating medium is reduced in the process of flowing the working gas through the compartment communication passage between the compartments. As a result, heat is exchanged while always maintaining a high heat transfer coefficient to equalize the expansion stroke and compression stroke of the entire volume chamber, so that the piston stroke is the same as in the conventional methods of (a) and (b) above. The position (that is, the volume change phase of the volume chamber) does not significantly reduce the heat transfer coefficient between the working gas and the heat medium for isothermalization, and as a result, these (a) and (b) Compared with the conventional method, the expansion and compression of the working gas can be made to approach the isothermal change more effectively, and the adiabatic loss in the Stirling machine can be effectively reduced.

In addition, basically, the above-mentioned effective isothermalization can be achieved without using the swirling flow accompanied by the flow loss as in the above-mentioned conventional method (C). The efficiency of the entire Stirling machine can be effectively improved, and in particular, a great effect can be obtained for the Stirling refrigerator / heat pump in which the adiabatic loss is a major factor of the decrease in the machine efficiency as compared with the Stirling engine. You can

[Invention of Claim 2] In the invention of Claim 2 (see FIG. 1), the volume chamber 3 is divided into three or more compartments 3a to 3a.
3c, and among these compartments 3a to 3c, for the first compartment 3a to which the gas passage 4 is connected, the other compartments 3b and 3c after the second compartment are sequentially arranged through the compartment communication passages 7a and 7b. Connected in series, and connecting the plurality of branch chambers 7a, 7a
By providing the heat exchangers 8a and 8b for isothermalization to b respectively, as described in the above [Invention of Claim 1], when the volume chamber 3 is used as an expansion chamber, a series connection is made. Among the divided compartments 3a to 3c, for each of the two or more compartments 3a and 3b except the compartment 3c of the terminal, the temperature drops Δt1 and Δt2 due to adiabatic expansion in the compartments 3a and 3b.
Can be made smaller than that when there is no sequential outflow of working gas to the terminal side.

Further, when the volume chamber 3 is used as a compression chamber, among the compartments 3a to 3c connected in series, two or more compartments 3a and 3b excluding the terminal compartment 3c are connected to the compartments 3a and 3b. Temperature rise Δt due to adiabatic compression
1 and Δt2 can be made smaller than in the case where there is no sequential inflow of working gas from the terminal side.

That is, according to the invention of claim 2,
For each of the two or more compartments, it is possible to suppress a temperature drop due to adiabatic expansion and a temperature rise due to adiabatic compression in the compartments. For example, as one embodiment of the invention according to claim 1, a first compartment and a second compartment are provided. In comparison with a configuration in which only two chambers are provided and only the first sub-chamber suppresses temperature change due to adiabatic change, the volume chamber as a whole is isothermalized in the expansion stroke and compression stroke, and further, the device efficiency is further improved. Can be achieved.

[Invention of Claim 3] In the invention of Claim 3 (see FIG. 1), a cylinder 1 having a multi-stage structure in which the inner diameter is gradually reduced toward the head side, and each step portion of this cylinder 1 With the piston 2 having a multi-stage structure including a plurality of stages of piston portions 2a to 2c, the divided spaces na to nc are formed at the tip side of the piston portions 2a to 2c of each stage in each stage of the cylinder 1. These partitioned spaces na to nc are referred to as the above-mentioned branch chambers 3a to 3c, respectively. In this configuration, the partition spaces na as the compartments 3a to 3c are accompanied by volume changes of the partition spaces na to nc due to the piston movement.
~ Nc to expand or compress the working gas G.

Further, the annular arrangement flow paths fa and fb formed in the peripheral wall portion of the cylinder 1 are used as the compartment communication passages 7a and 7b, and the respective partition spaces na are formed by the annular arrangement flow paths fa and fb.
To nc are communicated with each other, and the heat transfer wall is used for exchanging heat between the isothermal heat transfer medium L and the internal working gas G, which flow the flow path walls 10a and 10b of the annular arrangement flow paths fa and fb to the outside. As the heat exchangers 8a and 8b for isothermalization
With this configuration, the temperature drop of the working gas G due to the adiabatic expansion in the partitioned spaces na to nc as the compartments 3a to 3c and the temperature rise of the working gas G due to the adiabatic compression are generated by the annular arrangement flow path fa, Partitioned spaces na to nc via fb
Recover and eliminate in the process of working gas distribution.

That is, according to the third aspect of the present invention, since a plurality of compartments are partitioned and formed in the cylinder with one set of cylinders and pistons, for example, the plurality of compartments are individually formed by different cylinders and pistons. The structure of the device can be made simpler and more compact than that of the above structure.

Also, since the flow passage wall of the annular arrangement flow passage formed in the cylinder peripheral wall portion is used as the heat transfer wall to constitute the isothermal heat exchanger, for example, the isothermal heat exchanger is separated from the cylinder. As compared with a structure in which the compartment structure communication passage of a tube structure is provided as the body structure of, the simplification and compactness of the device structure can be achieved more effectively.

[Invention of Claim 4] In the invention of Claim 4 (see FIG. 3), the cylinder 1 in which an annular recess 20 opening toward the inside of the cylinder is formed in the cylinder head, and the cylinder-side annular Due to the piston 2 having the annular projection 21 located at the distal end inside the recess 20, the distal end side of the piston side annular projection 21 and the central hole portion of the piston side annular projection 21 and, in some cases, the inside of the cylinder. , The partition spaces na ′ to n on the outer side of the piston side annular projection 21 on the piston tip side, respectively.
c ′ is formed, and these partitioned spaces na ′ to nc ′ are respectively defined as the compartments 3a to 3c. Further, in this configuration, each partition space n as each of the compartments 3a to 3c is accompanied by a change in volume of each partition space na 'to nc' due to movement of the piston.
The working gas G is expanded or compressed at a'to nc '.

Further, the annular arrangement flow paths fa 'and fb' formed in the peripheral wall portion of the cylinder side annular recess 20 are used as the compartment communication passages 7a and 7b, and the annular arrangement flow paths fa 'and fb' are provided.
The divided spaces na ′ to nc ′ are communicated with each other by the channel wall 23 of the annular arrangement channels fa ′ and fb ′.
By configuring a and 23b as heat transfer walls for exchanging heat between the heat medium L for isothermal circulation and the working gas G therein, the heat exchangers 8a and 8b for isothermalization can be formed.
The temperature drop of the working gas G due to adiabatic expansion in the partitioned spaces na ′ to nc ′ as the compartments 3 a to 3 c and the temperature rise of the working gas G due to adiabatic compression are stored in the annular arrangement flow path f.
It recovers and eliminates in the working gas distribution process across the partitioned spaces na ′ to nc ′ via a ′ and fb ′.

That is, according to the invention described in claim 4, as in the case of the invention described in claim 3, since a plurality of compartments are partitioned and formed in one cylinder by one set of cylinder pistons, Since the heat exchanger for isothermalization is constituted by using the flow passage wall of the annular arrangement flow passage formed in the peripheral wall portion of the side annular concave portion as the heat transfer wall, the device structure can be made simple and compact, and particularly, In order to partition and form a plurality of compartments, since the annular concave portion on the cylinder side and the annular protrusion on the piston side are occluded and arranged, the device structure can be effectively made compact especially in the axial direction of the cylinder. You can

[Invention of Claim 5] In the invention of Claim 5 (see FIG. 1), the chamber wall 14 of the compartment 3c is supplied with an isothermal heating medium L and an internal working gas G. Is used as a heat transfer wall for heat exchange, the temperature drop due to adiabatic expansion of the working gas G in the compartment 3c and the temperature rise due to adiabatic compression are used for isothermal outside the compartment via the chamber wall 14 of the compartment 3c. This is suppressed by heat exchange between the heat medium L and the working gas G in the inside of the compartment, and as a result, as described above, in the working gas distribution process between the compartments 3a to 3c via the compartment communication passages 7a and 7b, In cooperation with heat exchange between the working gas G and the heat medium L for isothermalization by the heat exchangers 8a, 8b for isothermalization to achieve isothermalization, the expansion stroke and compression stroke of the volume chamber 3 as a whole Achieves isothermal, and consequently, improved equipment efficiency, more effectively.

[Invention of Claim 6] In the invention of Claim 6 (see FIG. 4), the swirl guide 36 is provided with respect to the working gas G flowing into the compartment 3b or 3a from the compartment communication passage 7a.
The swirling flow component is applied to the working gas G, which has recovered and eliminated the temperature drop due to adiabatic expansion and the temperature rise due to adiabatic compression in the isothermal heat exchanger 8a in the compartment communication passage 7a. Effectively promotes mixing with the working gas G in the compartment that is located indoors and has a temperature drop due to adiabatic expansion or a temperature rise due to adiabatic compression, and thereby a temperature drop due to adiabatic expansion in the compartment 3b or 3a. Further, the effect of suppressing the temperature rise due to adiabatic compression by the above mixing is further ensured.

Further, when the invention is carried out in parallel with the invention described in claim 5, the heat transfer between the chamber wall 31 of the compartment 3b as the heat transfer wall and the working gas G in the compartment 3b is performed by the swirling flow. By this, heat exchange between the isothermal heat transfer medium L and the working gas G via the chamber wall 31 of the compartment 3b causes a temperature drop due to adiabatic expansion and a temperature rise due to adiabatic compression in the compartment 3b. To obtain a higher suppression effect.

Therefore, according to the sixth aspect of the present invention, equalization of the expansion stroke and compression stroke of the entire volume chamber can be achieved more effectively, and a flow loss for causing swirling occurs, but Due to the excessive isothermal effect, the device efficiency can be further improved.

[0034]

BEST MODE FOR CARRYING OUT THE INVENTION

[First Embodiment] FIGS. 1 and 2 show a structure of a volume chamber used as an expansion chamber or a compression chamber in performing a Stirling cycle or a reverse Stirling cycle.
A volume chamber 3 is formed in the cylinder 1 by the piston 2 and the gas passage 4 for allowing the working gas G to periodically flow in and out of the volume chamber 3.

Reference numeral 5 denotes a regenerative heat exchanger interposed in the gas passage 4. The regenerative heat exchanger 5 exchanges heat with the circulating working gas G to store and radiate heat. Further, 6 is a heat exchanger for heat input / output which is interposed in the gas passage 4 on the volume chamber 3 side of the regenerative heat exchanger 5, and the heat exchanger 6 for heat input / output heats the working gas G and the outside. And heat exchange with the heat medium L.

Although not shown in the figure, the other end side of the gas passage 4 is connected to another volume chamber via another heat exchanger for heat input / output, and the space between both volume chambers is accompanied by a piston operation. Then, the working gas G is made to reciprocate through the above heat exchangers, and a staring cycle or a reverse Stirling cycle is carried out.

In the execution of the Stirling cycle, when the volume chamber 3 is used as an expansion chamber, the heat exchanger 6 for heat input and output functions as a heater for heating the working gas G by the high temperature heating medium L. , Other heat input / output heat exchangers
It functions as a radiator for radiating the working gas G to the low-temperature heat medium. Also, in the implementation of the Stirling cycle,
When the volume chamber 3 is used as a compression chamber, the heat input / output heat exchanger 6 functions as a radiator for radiating the working gas G to the low-temperature heat medium L, and other heat input / output heat exchangers , Which functions as a heater for heating the working gas G by the high temperature heating medium.

On the other hand, in the execution of the reverse Stirling cycle, when the volume chamber 3 is used as the expansion chamber,
The heat input / output heat exchanger 6 functions as a heat absorber that absorbs the working gas G in the low-temperature heat medium L, and the other heat input / output heat exchangers are radiators that radiate the working gas G in the high-temperature heat medium. Function as. Further, in the execution of the reverse Stirling cycle, when the volume chamber 3 is used as the compression chamber,
The heat input / output heat exchanger 6 functions as a radiator for radiating the working gas G to the high temperature heat medium L, and the other heat input / output heat exchangers are heat absorbers for absorbing the working gas G into the low temperature heat medium. Function as.

The volume chamber 3 is divided into a plurality of compartments 3a to 3c each of which changes in volume in the process of expansion or compression, and of these compartments 3a to 3c, the first compartment to which the gas passage 4 is connected. The other compartments 3b and 3c are communicated with the compartment 3a through the compartment communication passages 7a and 7b, and the compartment gas passages 7a and 7b are connected to the working gas G and the isothermal heating medium L (this example). Then, the heat exchanger 8 for isothermal heat exchange with the heat medium L to be exchanged in the heat exchanger 6 for heat input / output is the same).
a and 8b are provided.

The cylinder 1 has a three-stage structure in which the inner diameter is gradually reduced toward the head side. Correspondingly, the piston 2 has three stages of piston portions 2a ... It has a three-stage structure with 2c,
With this cylinder / piston structure, in each step of the cylinder 1, partitioned spaces na to nc are formed on the tip side of the piston portions 2a to 2c of each step, and these partitioned spaces na to nc are divided into first to third spaces. The compartments 3a to 3c are provided.

The peripheral walls of the second and third stages of the cylinder 1 are the cylinder inner walls 9a, 9b and the cylinder outer walls 10a, 1 respectively.
0b, so that in the second stage of the cylinder 1, the cylinder inner wall 9a and the cylinder outer wall 10a are formed.
The flow path fa formed in an annular shape between the first partition chamber 3 and
and the second branch chamber 3b as the branch chamber communication passage 7a,
Further, in the third stage of the cylinder 1, the cylinder inner wall 9b
The annular flow passage fb formed between the cylinder outer wall 10b and the cylinder outer wall 10b serves as a compartment communication passage 7b that communicates the second compartment 3b and the third compartment 3c.

That is, the first compartment 3a connecting the gas passage 4
On the other hand, the second and third branch chambers 3b and 3c are connected to the branch chamber communication passage 7
They are sequentially connected in series via the above-mentioned annular arrangement flow paths fa and fb as a and 7b.

The cylinder inner walls 9a and 9b and the cylinder outer wall 10 which form the flow passage walls of the annular arrangement flow passages fa and fb.
Among the a and 10b, a large number of fins 12a and 12b are provided on the inner and outer surfaces of the cylinder outer walls 10a and 10b, whereby the cylinder outer walls 10a and 10b and the heat transfer medium L and the flow path for isothermalization outside thereof are provided. As the heat transfer wall with fins for exchanging heat with the working gas G inside, the heat exchanger 8 for isothermalization described above is used.
a and 8b are configured.

Reference numeral 13 denotes the cylinder outer walls 10a, 10 described above.
b and a fin flow path wall (heat transfer wall) 6a of the working gas flow path in the heat input / output heat exchanger 6, the case is for forming a heat medium jacket, and the heat medium L is provided inside the case 13. By flowing the heat, the heat exchange between the working gas G and the heat medium L in each of the heat input / output heat exchanger 6 and the isothermal heat exchangers 8a and 8b is performed.

A large number of fins 15 are provided on the outer surface of the cylinder upper wall 14, and the case 13 also surrounds the cylinder upper wall 14 with fins, which is the chamber wall of the third branch chamber 3c. With the cylinder upper wall 14 as a heat transfer wall, the working gas G in the third compartment 3c is also heat-exchanged with the external isothermal heating medium L.

The fins 12b formed on the inner surfaces of the cylinder outer walls 10a and 10b have a shape extending in the axial direction of the cylinder.
Moreover, the fin tip is a fin contacting the cylinder inner walls 9a and 9b. By arranging the fins 12b in parallel in the cylinder circumferential direction, the annular arrangement flow channels fa and fb have fine flow channels extending in the cylinder axis direction. A large number of flow passages are arranged in the cylinder circumferential direction.

In the above structure, when the volume chamber 3 is used as an expansion chamber, the annular passages fa, fb from the gas passage 4 to the first branch chamber 3a and from the first branch chamber 3a to the branch chamber communication passages 7a, 7b. Through the second and third compartments 3b, 3
While the working gas G is sequentially flown into the chambers c, the volumes of the chambers 3a to 3c are expanded by the piston movement, and the chambers 3a to 3c are
The working gas G is expanded at 3c.

In this expansion stroke, when looking at the first subchamber 3a, the working gas G flowing into the first subchamber 3a from the first subchamber 3a to the second and third subchambers 3b, 3c.
A large amount of working gas G including the gas flows in from the gas passage 4,
On the other hand, since the adiabatic expansion in the first compartment 3a is limited to that according to the volume change of the own compartment, the temperature drop Δt1 of the working gas G due to the adiabatic expansion in the first compartment 3a is from the first compartment 3a. This is smaller than when there is no outflow of working gas into the second and third compartments 3b and 3c.

Then, from the first compartment 3a to the annular arrangement flow path f
The working gas G flowing into the next second compartment 3b via a is
Heat is exchanged with the isothermal heat transfer medium L while always maintaining a high heat transfer rate through the finned cylinder outer wall 10a as a heat transfer wall constituting the isothermal heat exchanger 7a, whereby the first sub-compartment 3
After recovering the temperature drop Δt1 at a, the second compartment 3b
Flows into.

Here, looking at the second branch 3b,
For the same reason as in the case of the first branch 3a described above, the second
Temperature drop Δt of working gas G due to adiabatic expansion in compartment 3b
2 is smaller than that when there is no outflow of working gas to the third compartment 3c, and subsequently, the working gas G flowing from the second compartment 3b into the next third compartment 3c via the annular arrangement flow path fb is , Heat is exchanged with the isothermal heat transfer medium L while always maintaining a high heat transfer rate through the finned cylinder outer wall 10b as a heat transfer wall constituting the isothermal heat exchanger 7b.
After recovering the temperature drop Δt2 in the compartment 3b, it flows into the third compartment 3c.

In the third compartment 3c, since there is no outflow of the working gas from the third compartment 3c to the next compartment, the temperature drop Δt3 of the working gas G due to adiabatic expansion is produced without being suppressed. As described above, the first and second branch chambers 3
Since the temperature drops Δt1 and Δt2 due to adiabatic expansion in a and 3b are suppressed, isothermalization in which the expansion of the working gas G approaches the isothermal change is effectively achieved in the volume chamber 3 as a whole.

On the other hand, when the volume chamber 3 is used as a compression chamber, the third and second branch chambers 3c and 3b to the branch chamber communication passage 7b,
Working gas G to the first branch chamber 3a via the annular arrangement flow paths fb and fa as 7a, and from the first branch chamber 3a to the gas passage 4
Each of the compartments 3a to 3 by moving the piston while letting out the
The working gas G is compressed in each of the compartments 3a to 3c as the volume of c is reduced.

In this compression process, when looking at the first compartment 3a, the working gas G whose temperature has risen due to adiabatic compression in the second compartment 3b while being mixed with the working gas from the third compartment 3c is the heat for isothermalization. After eliminating the temperature rise by heat exchange while maintaining a high heat transfer coefficient with the isothermal heat transfer medium L via the finned cylinder outer wall 10a as a heat transfer wall constituting the exchanger 7a, the second Branch 3b to first branch 3
While it flows into a and mixes with the working gas G in the first compartment 3a, the adiabatic compression in the first compartment 3a is limited to that according to the volume change of the own compartment. The temperature increase Δt1 due to the adiabatic compression is caused by the inflow of the working gas from the second compartment 3b through the isothermal heat exchanger 7a (the third compartment 3).
It is smaller than the case where there is no working gas G flowing out from c).

When looking at the second compartment 3b, for the same reason as in the case of the first compartment 3a, the temperature rise Δt2 in the second compartment 3b due to the adiabatic compression is the same as the heat exchanger for isothermalization. This is smaller than when there is no working gas inflow from the third compartment 3c via 7b.

In the third compartment 3c, since there is no inflow of the working gas from the other compartments through the isothermal heat exchanger, the temperature rise Δt3 due to adiabatic compression is not suppressed but a net result occurs. As described above, the first and second compartments 3a,
Since the temperature rises Δt1 and Δt2 due to the adiabatic compression in 3b are suppressed, isothermalization that brings the compression of the working gas G close to the isothermal change is effectively achieved in the volume chamber 3 as a whole.

By the way, in a structure in which the respective compartments 3a to 3c have the same volume, the respective compartments produced when there is no outflow of the working gas into the other compartments in the expansion stroke or the inflow of the working gas from the other compartments in the compression stroke. Temperature change of the working gas G due to adiabatic expansion and adiabatic compression in 3a to 3c (this is equivalent to the temperature change that occurs in a simple volume chamber that does not divide the volume chamber and is not equipped with an isothermal heat exchanger). ) Is Δt, the temperature change Δt1, of the working gas G due to adiabatic expansion and compression in each of the compartments 3a to 3c occurring in the volume chamber structure of the present example.
Δt2 and Δt3 are Δt1 = Δt / 3, Δt2 = Δt / 2, Δt3 = Δt, and therefore the average working gas temperature change Δtav of the volume chamber 3 in the volume chamber structure of this example is Δtav = ( Δt1 + Δt2 + Δt3) / 3 = {(Δt / 3) + (Δt / 2) + Δt} /3=0.61·Δt. That is, there is an isothermal effect of about 39%.

In the volume chamber structure of this example, as described above, the cylinder upper wall 14 which is the chamber wall of the third compartment 3c is used as a finned heat transfer wall to make the working gas G in the third compartment 3c also isothermal. By adopting a configuration for exchanging heat with the heating medium L,
Working gas G due to adiabatic expansion and compression in the third compartment 3c
The temperature change Δt3 is also suppressed so that the isothermal of the expansion stroke and the compression stroke of the volume chamber 3 as a whole can be achieved more effectively.

[Second Embodiment] FIG. 3 shows a volume chamber structure obtained by changing the structure of the volume chamber structure shown in the first embodiment. The main change is the formation structure of each of the compartments 3a to 3c. There is a change in.

That is, in this volume chamber structure, the head of the cylinder 1 is formed with an annular recess 20 that opens toward the inside of the cylinder. Correspondingly, the tip of the piston 2 has a cylinder-side annular recess. An annular projection 21 for positioning the tip is formed inside 20. With this cylinder-piston structure, in the cylinder 1, the outer portion of the piston side annular projection 21 of the piston tip side and the piston side annular projection 21 are formed. Tip side and piston side annular projection 2
The divided spaces na ′ to nc ′ in the central hole in FIG.
And these partitioned spaces na ′ to nc ′ are defined as first to third compartments 3 a to 3 c.

The outer peripheral wall of the cylinder-side annular recess 20 has a double wall structure of the cylinder inner wall 22a and the cylinder outer wall 23a, and the inner peripheral wall of the cylinder-side annular recess 20 has the cylinder inner wall 22b and the cylinder outer wall. 23b, which has a double-wall structure, whereby an annular passage f formed between the cylinder inner wall 22a and the cylinder outer wall 23a at the outer peripheral wall of the cylinder-side annular recess 20.
a ′ is a compartment communication passage 7a that communicates the first compartment 3a and the second compartment 3b, and is formed between the cylinder inner wall 22b and the cylinder outer wall 23b in the inner peripheral wall of the cylinder-side annular recess 20. The annular flow path fb ′
The second branch chamber 3b and the third branch chamber 3c communicate with each other as a branch chamber communication passage 7b.

That is, the above-mentioned annular arrangement flow paths fa 'and f
b ′ allows the second and third compartments 3 to be compared to the first compartment 3a.
b and 3c are sequentially connected in series.

Of the cylinder inner walls 22a and 22b and the cylinder outer walls 23a and 23b forming the flow passage walls of the annular arrangement flow passages fa 'and fb', the cylinder outer wall 23 is formed.
A large number of fins 24a and 24b are provided on the inner and outer surfaces of the a and 23b, whereby the cylinder outer walls 23a and 23b are formed.
Is the heat medium L for isothermalization and the working gas G inside the flow path.
Isothermal heat exchangers 8a and 8b are configured as fin-bearing heat transfer walls for exchanging heat between and.

Similar to the volume chamber structure shown in the first embodiment, 13 is the above-mentioned cylinder outer walls 23a, 23b and the finned flow path wall (heat transfer wall) of the working gas flow path in the heat input / output heat exchanger 6. ) 6a is a case for forming a heat medium jacket, and the heat medium L is circulated inside the case 13 so that the heat input / output heat exchanger 6 and the isothermal heat exchanger 8
Heat exchange between the working gas G and the heating medium L for each of a and 8b is performed.

In the above structure, when the volume chamber 3 is used as an expansion chamber, as in the volume chamber structure shown in the first embodiment, from the gas passage 4 to the first branch chamber 3a and the first branch chamber thereof. 3a via the annular arrangement flow paths fa 'and fb' as the compartment communication passages 7a and 7b.
While sequentially flowing the working gas G into the chambers 3c, the volumes of the chambers 3a to 3c are expanded by moving the pistons, and the chambers 3a are expanded.
The working gas G is expanded at ~ 3c.

On the other hand, when the volume chamber 3 is used as the compression chamber, this is also the same as the volume chamber structure shown in the first embodiment, from the third and second compartments 3c and 3b to the compartment communication passage 7.
The first through the annular arrangement flow paths fb, fa as b, 7a
While flowing the working gas G into the branch chamber 3a and from the first branch chamber 3a to the gas passage 4, the respective branch chambers 3a are moved by the piston movement.
Working gas G in each of the compartments 3a to 3c accompanied by volume reduction of 3 to 3c
Compress.

[Third Embodiment] FIG. 4 shows a volume chamber structure obtained by modifying the volume chamber structure shown in the first or second embodiment described above. The main changes are in the compartments 3a and 3b. The point is that the working gas G to be flowed in is swirled.
In the volume chamber structure shown in FIG. 4, the volume chamber 3 is divided into two compartments 3a and 3b.

That is, in this volume chamber structure, the cylinder 1 has a two-stage structure in which the inner diameter becomes smaller toward the head side, and correspondingly, the piston 2 has a two-stage piston for each step portion of the cylinder 1. It has a two-stage structure including the portions 2a and 2b. With this cylinder-piston structure, at each stage portion in the cylinder 1, the piston portion 2 of each stage is formed.
Forming partitioned spaces na "and nb" on the tip side of a and 2b,
These partitioned spaces na "and nb" are divided into first and second compartments 3
a and 3b.

Further, the cylinder upper wall 31 serving as the chamber wall of the second branch chamber 3b is formed in a conical shape, and correspondingly, the second-stage piston portion 2b is also formed in a conical shape. A large number of fins 31a, 34 are provided on the inner and outer surfaces of the shaped cylinder upper wall 31, and the cylinder upper wall 31 is used as a heat transfer wall to form the working gas G in the second compartment 3b and the external isothermal heat transfer medium L. It is designed to exchange heat with and.

That is, in the structure in which the cylinder upper wall 31 which is the chamber wall of the second branch chamber 3b is used as the heat transfer wall, the cylinder upper wall 31 and the second-stage piston portion 2b are formed in a conical shape as described above. The heat transfer area between the working gas G in the second compartment 3b and the external heat medium L for isothermalization is large relative to the volume of the second compartment 3b (that is, relative to the amount of working gas in the second compartment 3b). Secure).

The second peripheral wall portion of the cylinder 1 has a double wall structure including a cylinder inner wall 32 and a cylinder outer wall 33, whereby an annular arrangement is formed between the cylinder inner wall 32 and the cylinder outer wall 33. The flow path fa ″ is connected to the first branch chamber 3
It serves as a compartment communication passage 7a for communicating the "a" with the second compartment 3b.

Of the cylinder inner wall 32 and the cylinder outer wall 33 forming the flow passage wall of the annular arrangement flow passage fa ″,
A large number of fins 34 continuing from the outer surface of the cylinder upper wall 31 are provided on the outer surface of the cylinder outer wall 33, and thereby the cylinder outer wall 33 is provided with an isothermal heating medium L and a working gas G inside the flow path. As a heat transfer wall with fins for heat exchange,
The isothermal heat exchanger 8a is configured.

Reference numeral 35 is a case for forming a heating medium jacket surrounding the cylinder outer wall 33 and the cylinder upper wall 31, and by circulating the heating medium L inside the case 35,
With the heat exchange between the working gas G in the second compartment 3b having the cylinder upper wall 31 as the heat transfer wall and the heat medium L for isothermalization, and the heat exchanger 8a for isothermalization having the cylinder outer wall 33 as the heat transfer wall. The heat exchange between the working gas G and the isothermal heat transfer medium L is performed.

In this example, the heat exchanger 6 for heat input / output is provided.
The case for forming the heat medium jacket is formed separately from the case 35.

Annular arrangement flow path f as the compartment communication passage 7a
In a ", a spiral fin 36 is provided as a swirl guide tool for imparting a swirl flow component to the circulating working gas G. The spiral fin 36 guides the working gas, and the spiral fin 36 is used in an expansion stroke when used as an expansion chamber. First branch 3a to second branch 3b
When used as a compression chamber, the working gas G that flows into the first branch chamber 3a from the second branch chamber 3b is swirled in the compression stroke.

That is, after the temperature drop due to adiabatic expansion and the temperature rise due to adiabatic compression are recovered and eliminated by the isothermal heat exchanger 8a, the working gas G flows into the other compartment (3b or 3a). In doing so, the working gas G is swirled to flow into the other compartments, so that the inflow working gas G causes a temperature drop due to adiabatic expansion and a temperature rise due to adiabatic compression in the destination compartments 3b and 3a. By effectively mixing with the working gas G in the compartment, the effect of suppressing the temperature drop due to adiabatic expansion and the temperature rise due to adiabatic compression in the compartment by the above mixing is further ensured.

Further, in any of the use as the expansion chamber and the compression chamber, in the process of sucking the working gas into the second compartment 3b, the spiral fin 36 flows into the second compartment 3b. The swirl flow component is given to the working gas G to
By swirling the working gas G in the compartment 3b, heat transfer between the cylinder upper wall 31 as a heat transfer wall and the working gas G in the second compartment 3b is promoted, whereby the cylinder upper wall 31 is passed through. The effect of suppressing the temperature drop due to adiabatic expansion and the temperature rise due to adiabatic compression in the second compartment 3b can be further enhanced by the heat exchange between the working gas G in all the compartments and the heat medium L for isothermalization. .

In the spiral fin 36, the heat transfer between the working gas G and the isothermal heat transfer medium L together with the fin 34 on the outer surface of the cylinder outer wall 33 of the isothermal heat exchanger 7a. It also functions as a fin for heat transfer that secures a large area.

[Fourth Embodiment] FIGS. 5 and 6 show a volume chamber structure obtained by further modifying the volume chamber structure shown in the above-described first embodiment. The main change is that of the compartment communication passage 7a. ，
The point is that the formation structure of the annular arrangement flow paths fa and fb as 7b is rationalized, and the connection form of the gas passage 4 to the volume chamber 3 divided into a plurality of compartments 3a to 3c is changed.

That is, in this volume chamber structure, similarly to the first embodiment described above, the cylinder 1 has a three-stage structure, and the piston 2 is provided with three-stage piston portions 2a to 2b for each step of the cylinder 1. With the three-stage structure, this cylinder / piston structure forms partition spaces na to nc on the tip side of the piston portions 2a to 2c at each step at each step in the cylinder chamber 1, but these partition spaces na to nc A gas passage 4 is connected to the first sub-chamber 3a on the cylinder head side as a first sub-chamber 3a, a second sub-chamber 3b, and a third sub-chamber 3c in order from the one located on the cylinder head side.

The peripheral wall portion of the cylinder 1 has a single wall structure instead of the double wall structure.
a and the peripheral wall 40b of the second stage, the peripheral walls 40a, 40
An annular fin 4 extending in the circumferential direction on the inner and outer surfaces of b.
A large number of fins 1 and 42 are formed side by side in the axial direction of the cylinder, and among the fins 41 and 42 of the peripheral walls 40a and 40b, the fins 41 on the inner surface side penetrate the fins 41 on the inner surface side in the axial direction of the cylinder. A large number of holes 43 are formed by arranging them in the cylinder circumferential direction.

In other words, with the hole 43 of the fin 41 on the inner surface side of the peripheral wall 40a of the third step, the branch chamber connecting the piston 2 and the peripheral wall 40a of the third step to connect the first branch chamber 3a and the second branch chamber 3b. An annular arrangement flow path fa is formed as the passage 7a, and the fins 4 on the inner surface side of the second peripheral wall 40b are formed.
With the hole 43 of No. 1, the piston 2 and the peripheral wall 40b of the second stage
An annular arrangement flow path fb is formed between and as a compartment communication passage 7b that communicates the second compartment 3b and the third compartment 3c.

Then, these peripheral walls 40a, 40b having fins 41, 42 formed on the inner and outer surfaces are subjected to heat exchange between the heat medium L for isothermalization and the internal working gas G in the annular arrangement flow channels fa, fb. Isothermal heat exchangers 8a and 8b are configured as fin-bearing heat transfer walls.

That is, by forming the annular arrangement flow paths fa and fb as the compartment communication passages 7a and 7b with the holes 43 formed in the inner fin 41 in this way, the peripheral wall of the cylinder 1 is formed into the annular arrangement flow path fa, It is not necessary to use a double-wall structure for forming fb, and the structure is simplified, and working gases for circulating isothermal heat exchangers 8a and 8b in annular arrangement flow paths fa and fb are used. A large heat transfer area for G can be secured.

Reference numeral 44 is a cylindrical body for forming the heating medium jacket surrounding the second-stage peripheral wall 40a and the third-stage peripheral wall 40b,
By operating the isothermal heat transfer medium L inside the cylindrical body 44, the isothermal heat exchangers 8a and 8b having the third-stage peripheral wall 40a and the second-stage peripheral wall 40b as heat transfer walls operate. Heat exchange between the gas G and the isothermal heating medium L is performed.

Further, 45 is the peripheral wall 4 of the first stage of the cylinder 1.
0c (that is, the chamber wall of the third compartment 3c) is a tubular body for forming the heating medium jacket. By circulating the heating medium L for isothermalization inside the tubular body 45, the peripheral wall 40 of the first stage is formed.
Heat is exchanged between the working gas G in the third compartment 3c having c as a heat transfer wall and the heat transfer medium L for isothermalization.

Reference numeral 46 denotes a guide bar which is slidably engaged with a guide hole 47 formed at the tip of the piston 2, and the piston 2 is engaged by the guide hole 47 and the guide bar 46.
Guide the reciprocating movement of.

Reference numeral 48 is a vent hole for communicating the inside of the guide hole 47 with the volume chamber 3 (the second branch chamber 3b in this example) in the cylinder, and with respect to the operation of the piston 2 toward the bottom dead center side. Allows the working gas G to flow into the inside of the guide hole 47 through the vent hole 48, and for the operation of the piston 2 toward the top dead center side, the guide hole 47 of the guide hole 47 passes through the vent hole 48. The working gas G inside is made to flow out into the volume chamber 3. That is, the inside of the guide hole 47 becomes a closed space so that the piston operation is not hindered.

Further, in the present example, the inside of the guide hole 47 is made to function as a part of the second compartment 3b by forming the vent hole 48.

Other Embodiments Next, other embodiments will be listed. The number of compartments 3a to 3c (that is, the number of divisions of the volume chamber 3) is not limited to 2 to 3, and the volume chamber 3 may be divided into four or more compartments. Good.

Instead of forming a plurality of compartments 3a to 3c, each of which changes in volume in the process of expansion or compression, in a set of cylinders and pistons as in the above-described embodiments, each compartment 3a to 3c is individually formed. A form formed by a cylinder and a piston may be adopted.

The compartment communication passages 7a and 7b may be formed by a tube structure different from that of the cylinder 1, instead of being formed as the internal flow path of the cylinder 1 as in the above-described embodiments.

The isothermal heat exchangers 8a and 8b provided in the compartment communication passages 7a and 7b are also the cylinder outer walls 10a, 10b, 23a, 23b and 33 as in the above-described embodiments.
May be configured as a container different from the cylinder 1 instead of the configuration as a heat transfer wall.

As the working gas G, various gases such as nitrogen gas and air can be adopted, and the isothermal heat transfer medium L can be used.
Also, various fluids such as water can be applied.

For the first branch chamber 3a connecting the gas passage 4,
The other branch chambers 3b and 3c after the second branch chamber are connected to the branch chamber communication passage 7a,
In the case of adopting the form of serial connection via 7b, the other compartments 3b, 3c after the second compartment to be connected in series
The number of rooms may be three or more.

With respect to the first branch chamber 3a connecting the gas passage 4,
The plurality of other branch chambers 3b and 3c are respectively connected to the branch chamber communication passages 7a and 7a.
b connected in parallel via b, and the other compartments 3b and 3c connected in parallel to the first compartment 3a in this way
In addition, it is also possible to adopt a mode in which other branch chambers are connected in series via a branch communication passage.

In each of the above-described embodiments, the cylinder wall portion serving as the chamber wall of the first compartment 3a is a heat transfer wall for exchanging heat between the internal working gas G and the external isothermal heating medium L. The compartment walls other than the compartments may also be heat transfer walls for exchanging heat between the internal working gas G and the external isothermal heat transfer medium L.

The swirl guide for imparting swirl flow component to the working gas G flowing into the compartments 3b, 3a from the compartment communication passage 7a is limited to the structure like the spiral fin 36 shown in the third embodiment. However, various other shapes and structures can be adopted, such as using a propeller-shaped guide vane.

In each of the above embodiments, the isothermal heat transfer medium L for exchanging heat with the working gas G in the isothermal heat exchangers 8a and 8b.
The same heat medium is used as the heat medium L for exchanging heat with the working gas G in the heat exchanger 6 for heat input and output, but in some cases, these heat mediums are different from each other, or alternatively, the gas is different. It is also possible to omit the heat input / output heat exchanger 6 provided in the passage 4 and to perform only heat exchange between the working gas G and the isothermal heat transfer medium L on the cylinder side.

Fins (fins) provided on the part to be the heat transfer wall
The specific shape and arrangement form of can be changed in various ways, and when fins are provided on the inner surface of the cylinder chamber as the volume chamber 3, the piston side where the tip is positioned between these fins on the inner surface side The fin 2 may be provided in the piston 2 and the piston 2 may be operated in a state in which the alternate arrangement of the fin on the inner surface of the cylinder and the fin on the piston side is maintained.

The present invention is a Stirling engine, a Stirling refrigerator / heat pump, or various types of Stirling equipment for carrying out a Stirling cycle or a reverse Stirling cycle, such as a heat / power equipment for carrying out a Stirling cycle and a reverse Stirling cycle in parallel. Applicable to

It should be noted that reference numerals are added to the claims for convenience of comparison with the drawings, but the present invention is not limited to the configurations of the accompanying drawings by the entry.

[Brief description of drawings]

FIG. 1 is a vertical cross-sectional view showing a first embodiment.

FIG. 2 is a transverse sectional view showing the first embodiment.

FIG. 3 is a longitudinal sectional view showing a second embodiment.

FIG. 4 is a vertical cross-sectional view showing a third embodiment.

FIG. 5 is a longitudinal sectional view showing a fourth embodiment.

FIG. 6 is a cross-sectional view showing a fourth embodiment.

FIG. 7 is a longitudinal sectional view showing a conventional structure.

FIG. 8 is a vertical sectional view showing another conventional structure.

FIG. 9 is a vertical cross-sectional view showing another conventional structure.

[Explanation of symbols]

 5 Regeneration heat exchanger 4 Gas passage 3 Volume chamber G Working gas 3a to 3c Branch chamber 3a First branch chamber 3b, 3c Other branch chambers 7a, 7b Branch chamber communication passage L Isothermal heat transfer medium 8a, 8b Isothermal heat exchanger 1 Cylinder 2 Piston 2a to 2c Piston part na to nc Partition space fa, fb Annular arrangement flow path 10a, 10b Flow path wall (heat transfer wall) 20 Cylinder side annular recess 21 Piston side annular projection na 'to nc' Partition space fa ' , Fb 'Annularly arranged flow path 23a, 23b Flow path wall (heat transfer wall) 14, 31, 40c Chamber wall (heat transfer wall) 36 Branching guide tool

Claims (6)

[Claims] 1. A working gas (G) introduced into a volume chamber (3) through a gas passage (4) having a regenerative heat exchanger (5) is expanded or compressed in a Stirling cycle or a reverse Stirling cycle. A volume chamber structure of a Stirling machine that expands or compresses with a volume change of the volume chamber (3) as a stroke, wherein the volume chamber (3) has a plurality of volumes each of which changes volume during the expansion or compression stroke. The sub-chambers (3a to 3c) are divided, and among the sub-chambers (3a to 3c), the first sub-chamber (3a) to which the gas passage (4) is connected is divided into other sub-chambers (3
b) and (3c) are communicated with each other through the branch chamber communication passages (7a) and (7b), and the working gas (G) is supplied to the branch chamber communication passages (7a) and (7b).
A volume chamber structure of a Stirling machine provided with heat exchangers (8a), (8b) for isothermalization for exchanging heat with the heat medium (L) for isothermalization. 2. The volume chamber (3) is divided into three or more compartments (3a to 3c), and the first compartment to which the gas passage (4) is connected among the compartments (3a to 3c). In contrast to (3a), the other branch chambers (3b) and (3c) after the second branch chamber are connected to the branch chamber communication passage (7).
a) and (7b) are sequentially connected in series, and each of the plurality of compartment communication passages (7a) and (7b) is provided with the heat exchangers (8a) and (8b) for isothermalization. Item 3. The volume chamber structure of the Stirling machine according to Item 1. 3. In the structure in which the volume chamber (3) is formed in the cylinder by the cylinder (1) and the piston (2), the inner diameter of the cylinder (1) is gradually reduced toward the head side. In addition to having a multi-stage structure, the piston (2) has a multi-stage structure including a plurality of stages of piston portions (2a to 2c) for each stage of the cylinder (1). 1)
Each of the compartments (na to nc) compartmentalized and formed in the interior of the compartment is defined as the compartment (3a to 3c), and the first compartment connecting the gas passage (4) among the compartments (na to nc) The flow passages (fa) and (fb) for communicating the other divided spaces (nb) and (nc) with the divided space (na) as (3a) are arranged in an annular shape on the peripheral wall of the cylinder (1). The annularly arranged flow paths (fa) and (fb) are formed to form the compartment communication passages (7a) and (7).
b), and the flow path walls (10) of the annular arrangement flow paths (fa), (fb).
The a) and (10b) are heat exchangers (8a) for isothermalization as heat transfer walls for exchanging heat between the isothermal heating medium (L) and the working gas (G) inside. , (8b)
The volume chamber structure of the Stirling machine according to claim 1 or 2, which is configured. 4. A structure in which the volume chamber (3) is formed in the cylinder by a cylinder (1) and a piston (2), and an annular shape opening toward the inside of the cylinder is formed in the head of the cylinder (1). While forming the recess (20),
An annular projection (21) is formed at the tip of the piston (2) to locate the tip inside the cylinder-side annular recess (20), and a partition space (na) is defined inside the cylinder by this cylinder-piston structure. '-Nc') are defined as the compartments (3a-3c), and among these compartments (na'-nc '), the compartments as the first compartment (3a) connecting the gas passage (4) For (na '), other partitioned spaces (nb'), (n
The flow passages (fa ′) and (fb ′) for communicating the c ′) are formed in the peripheral wall portion of the cylinder side annular recess (20) in an annular arrangement, and the annular arrangement passages (fa ′) and (f ′) are formed. fb ′) is used as the compartment communication passages (7a) and (7b), and the flow passage walls (2) of the annular arrangement flow passages (fa ′) and (fb ′) are formed.
3a) and (23b) as heat transfer walls for exchanging heat between the isothermal heat transfer medium (L) and the working gas (G) inside, and the isothermal heat exchanger (8a). , (8
The volume chamber structure of the Stirling machine according to claim 1 or 2, which constitutes b). 5. A chamber wall (1) of the compartments (3c), (3b).
4. The heat transfer walls 4), 31) and 40c are heat transfer walls for exchanging heat between the isothermal heat transfer medium L and the working gas G inside. The volume chamber structure of the Stirling machine according to 3 or 4. 6. A swirl guide (36) for imparting a swirl flow component to the working gas (G) flowing into the compartments (3b), (3a) from the compartment communication passage (7a). The volume chamber structure of the Stirling machine according to 2, 3, 4, or 5.