Stirling engine

Abstract

To provide a Stirling engine capable of reducing an ineffective space which does not contribute to the operation of an expansion piston and a compression piston, thus increasing an output with efficient drive of the engine.SOLUTION: The Stirling engine includes a body storing operative gas, and a heater arranged in the body for giving heat from a heat source to the operative gas. The Stirling engine further includes a cooler arranged in the body for cooling the operative gas, the expansion piston arranged in the body via the heater and an expansion space for the operative gas, and the compression piston arranged in the body via the cooler and a compression space for the operative gas. The expansion piston and the heater are linearly aligned in the body in the operating direction of the expansion piston. The cooler and the compression piston are linearly aligned in the body in the operating direction of the compression piston.SELECTED DRAWING: Figure 1

Description

[Technical field]

[0001] The present invention relates to a Stirling engine. [Background technology]

[0002] For example, Patent Document 1 discloses a device in which a heat exchanger is provided in a duct through which exhaust air passes, which converts water into steam using heat in the exhaust air, and the steam is guided to a heated object, which is then heated by the heat of condensation. The above heat exchanger, which uses water as a medium (heat medium) for heat exchange, is also called a thermosiphon. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] JP 2010-101299 A Summary of the Invention [Problem to be solved by the invention]

[0004] In Patent Document 1, a piston called a displacer moves up and down in an expansion space formed inside the Stirling engine. However, in the configuration of Patent Document 1, there is a void space in the expansion space that does not contribute to the up and down movement of the displacer. For example, in the expansion space, when the displacer is at the top position, the internal space is a space whose volume does not change even if the displacer moves up and down, and this space becomes a void space that does not contribute to the up and down movement of the displacer. If such a void space exists, the engine cannot be driven efficiently, and it becomes difficult to increase the engine output. In particular, in an α-type Stirling engine, since there are two pistons (an expansion piston and a compression piston), a void space may also exist in the compression space.

[0005] The present invention has been made to solve the above problems, and its object is to provide a Stirling engine that can reduce the dead space that does not contribute to the operation of the expansion piston and the compression piston, thereby driving the engine efficiently and increasing the output. [Means for solving the problem]

[0006] A Stirling engine according to one aspect of the present invention is a Stirling engine comprising: a body that contains a working gas; and a heater that is disposed within the body and that imparts heat from a heat source to the working gas. The engine further comprises a cooler that is disposed within the body and that cools the working gas; an expansion piston that is disposed within the body via the heater and an expansion space of the working gas; and a compression piston that is disposed within the body via the cooler and a compression space of the working gas, wherein the expansion piston and the heater are disposed in a straight line in the direction of movement of the expansion piston within the body, and the cooler and the compression piston are disposed in a straight line in the direction of movement of the compression piston within the body. Effect of the Invention

[0007] According to the above-mentioned configuration, it is possible to reduce the void space that does not contribute to the operation of the expansion piston and the compression piston, thereby enabling the engine to be driven efficiently and increasing output. [Brief description of the drawings]

[0008] [Figure 1] 1 is an explanatory diagram showing a schematic configuration of a Stirling engine according to an embodiment of the present invention; [Diagram 2] FIG. 2 is an explanatory diagram showing changes in pressure and volume in an expansion space within the main body of the Stirling engine. [Diagram 3] FIG. 4 is an explanatory diagram showing changes in pressure and volume in a compression space in the main body. [Figure 4] FIG. 2 is an explanatory diagram showing another configuration of the Stirling engine. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0009] DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described with reference to the drawings.

[0010] <1. Basic structure of Stirling engine> 1 is an explanatory diagram showing a basic configuration of a Stirling engine 100 according to an embodiment of the present invention. The Stirling engine 100 includes a thermosiphon 1 and an engine unit 20.

[0011] (1-1. Thermosyphon) Thermosiphon 1 contains a heat medium that receives heat from a heat source HS. The heat source HS can be, for example, factory waste heat. The heat source HS may also be solar heat or geothermal heat. The heat source HS moves through a flow path FP. The flow path FP is, for example, composed of a heat exhaust pipe.

[0012] Thermosiphon 1 has a first pipe 1a, a second pipe 1b, and a third pipe 1c as pipes through which a heat medium flows. First pipe 1a is located inside flow path FP. Second pipe 1b and third pipe 1c are located outside flow path FP. Thus, a portion of thermosiphon 1 is disposed in flow path FP.

[0013] The second pipe 1b is located downstream of the first pipe 1a in the direction in which the heat medium flows. The first pipe 1a and the second pipe 1b are connected via a first connection part 11. The first connection part 11 is provided on a wall surface of the flow path FP. The end of the second pipe 1b opposite to the end connected to the first pipe 1a is connected to an upper part of the main body 30 of the engine part 20.

[0014] The third pipe 1c is located upstream of the first pipe 1a in the direction in which the heat medium flows. The first pipe 1a and the third pipe 1c are connected via a second connection part 12. The second connection part 12 is provided on the wall surface of the flow path FP. The end of the third pipe 1c opposite to the end connected to the first pipe 1a is connected to the lower part of the main body 30.

[0015] The heat transfer medium contained in the thermosiphon 1 is, for example, water. Water is liquid at room temperature, but at high temperatures it boils and turns into gaseous steam. Steam also condenses into water (condensed water). Therefore, steam and condensed water are also included in the heat transfer medium. The heat transfer medium, in either a liquid or gaseous state, flows through the piping of the thermosiphon 1 and circulates between the heat source HS (flow path FP) and the engine section 20.

[0016] More specifically, when the heat medium (here, water) in the first pipe 1a is heated by the heat source HS (for example, exhaust heat), the water evaporates and becomes steam. The steam passes from the first pipe 1a through the second pipe 1b and is introduced from above into the main body 30 of the engine section 20. The steam releases condensation heat to a heater 40 (described later) in the main body 30, thereby heating the heater 40. After releasing the condensation heat, the steam condenses and becomes water (condensed water). The water is discharged from the bottom of the main body 30 and passes through the third pipe 1c, and is returned to the first pipe 1a. In other words, the condensed water enters the flow path FP of the heat source HS. The above process is repeated thereafter. The heat medium contained in the thermosiphon 1 may be a liquid other than water (for example, alcohol).

[0017] In this way, the thermosiphon 1 receives heat from the heat source HS and exchanges heat with the heater 40. Such a thermosiphon 1 is also called a primary heat exchanger.

[0018] (1-2. Engine Configuration) The engine section 20 has a main body 30. The main body 30 is a cylinder that contains a working gas G. The working gas G is, for example, helium. Since helium has a large specific heat capacity, engine output per volume can be increased by increasing the density by applying high pressure to the helium. The working gas G may be a gas other than helium (for example, air, hydrogen, etc.). Within the main body 30, a heater 40, a cooler 50, and a regenerator 60 are arranged linearly in the horizontal direction.

[0019] The heater 40 is formed of, for example, a shell-and-tube type heat exchanger. The heater 40 is also referred to as a secondary heat exchanger in comparison with the thermosiphon 1 which is a primary heat exchanger. The heater 40 has a heater tube 41 through which the working gas G flows. The heater tube 41 is, for example, a metal tube. The metal constituting the heater tube 41 may be appropriately selected from metals with excellent thermal conductivity, such as aluminum, copper alloy, and stainless steel. In this embodiment, a plurality of heater tubes 41 are provided, but it is sufficient that at least one heater tube 41 is provided.

[0020] Steam introduced from thermosiphon 1 into main body 30 flows around each heater tube 41. This heats each heater tube 41, and the working gas G flowing inside each heater tube 41 is heated. In other words, heater 40 imparts heat transferred by the heat medium of thermosiphon 1 to working gas G.

[0021] One end of the heater 40 communicates with the expansion space ES, and the other end communicates with one end of the regenerator 60. That is, the heater 40 is located between the expansion space ES and the regenerator 60 within the main body 30. The expansion space ES is a space in which the working gas G expands when it is heated by the heater 40.

[0022] The cooler 50 is also configured with a shell-and-tube type heat exchanger similar to the heater 40. That is, the cooler 50 has a plurality of cooling pipes 51 through which the working gas G flows. The cooling pipes 51 are metal pipes similar to the heater pipe 41. In this embodiment, a plurality of cooling pipes 51 are provided, but it is sufficient that at least one cooling pipe is provided.

[0023] When a refrigerant is supplied to the cooler 50 from the cooling equipment 70 installed outside the main body 30 via the refrigerant piping 71, the refrigerant flows around each cooling tube 51. This cools each cooling tube 51, and the working gas G flowing through each cooling tube 51 is cooled. In other words, the cooler 50 cools the working gas G with the refrigerant. The above refrigerant is, for example, water, but a refrigerant other than water may also be used. The refrigerant flows through the refrigerant piping 71 and circulates between the cooler 50 and the cooling equipment 70.

[0024] One end of the cooler 50 communicates with the compression space CS, and the other end of the cooler 50 communicates with the other end of the regenerator 60. That is, the cooler 50 is located between the regenerator 60 and the compression space CS within the main body 30. The compression space CS is a space where the working gas G is compressed by a compression piston CP described later.

[0025] The regenerator 60 is disposed between the heater 40 and the cooler 50. The regenerator 60 is formed, for example, of a mesh-shaped flow path. This allows the working gas G in the main body 30 to circulate between the expansion space ES side and the compression space CS side via the regenerator 60. In other words, the regenerator 60 allows the working gas G to circulate between the expansion space ES and the compression space CS. Note that the regenerator 60 is not limited to a mesh-shaped flow path. For example, the regenerator 60 can also be formed of a heat storage material such as a laminated wire mesh, a thin plate aligned with the flow, or a porous body.

[0026] An expansion piston EP serving as a power piston PP is disposed in the main body 30 on the opposite side of the expansion space ES to the heater 40. Also, a compression piston CP serving as a power piston PP is disposed in the main body 30 on the opposite side of the compression space CS to the cooler 50. That is, in the main body 30, the expansion piston EP is disposed via the heater 40 and the expansion space ES of the working gas G, and the compression piston CP is disposed via the cooler 50 and the compression space CS of the working gas G. Thus, a two-piston type Stirling engine 100 having two pistons (expansion piston EP, compression piston CP) serving as a power piston PP is also called an α-type Stirling engine.

[0027] Piston rings PR are fitted around the outer periphery of the expansion piston EP and the compression piston CP. The piston rings PR act as a gas seal. In other words, the piston rings PR prevent leakage of the working gas G from the gap between the expansion piston EP and the main body 30 and the gap between the compression piston CP and the main body 30 (gas leakage).

[0028] An expansion-side piston rod 81 of the expansion piston EP is connected to an expansion-side crosshead piston 82. The expansion-side crosshead piston 82 is connected to an expansion-side crankshaft 84 via an expansion-side connecting rod 83. The expansion-side piston rod 81 is provided penetrating one end face 30a of the main body 30. Therefore, the expansion-side crosshead piston 82, the expansion-side connecting rod 83, and the expansion-side crankshaft 84 are located outside the main body 30.

[0029] The expansion-side crosshead piston 82, the expansion-side connecting rod 83, and the expansion-side crankshaft 84 constitute an expansion-piston-side crank mechanism 85. The expansion piston EP is connected to the expansion-piston-side crank mechanism 85 via the expansion-side piston rod 81. On one end surface 30a of the main body 30, an expansion-side gas seal portion 31a is provided around a through hole through which the expansion-side piston rod 81 passes.

[0030] A compression-side piston rod 86 of the compression piston CP is connected to a compression-side crosshead piston 87. The compression-side crosshead piston 87 is connected to a compression-side crankshaft 89 via a compression-side connecting rod 88. The compression-side piston rod 86 is provided penetrating the other end face 30b of the main body 30. Therefore, the compression-side crosshead piston 87, the compression-side connecting rod 88, and the compression-side crankshaft 89 are located outside the main body 30.

[0031] The compression side crosshead piston 87, the compression side connecting rod 88, and the compression side crankshaft 89 constitute a compression piston side crank mechanism 90. The compression piston CP is connected to the compression piston side crank mechanism 90 via a compression side piston rod 86. On the other end surface 30b of the main body 30, a compression side gas seal portion 31b is provided around a through hole through which the compression side piston rod 86 passes.

[0032] The expansion piston side crank mechanism 85 and the compression piston side crank mechanism 90 are connected to each other so as to be capable of transmitting power through a power transmission unit 91. More specifically, the expansion side crankshaft 84 of the expansion piston side crank mechanism 85 is connected to the output shaft SH through a first belt 92 so as to be capable of transmitting power. Furthermore, the compression side crankshaft 89 of the compression piston side crank mechanism 90 is connected to the output shaft SH through a second belt 93 so as to be capable of transmitting power. In other words, the first belt 92, the output shaft SH, and the second belt 93 constitute the above-mentioned power transmission unit 91. Note that the power transmission unit 91 may be configured to have a chain, gears, etc., other than or in addition to the belt.

[0033] The output shaft SH is, for example, a rotating shaft of a work machine M. The work machine M is composed of, for example, a generator and a motor. For example, the work machine M operates as a motor only at start-up, and operates as a generator after independent operation.

[0034] (1-3. Engine operation) In the above configuration, when steam flowing through the first pipe 1a and the second pipe 1b of the thermosiphon 1 is introduced into the main body 30 of the engine section 20, the heat of condensation of the steam is imparted to the heater 40, heating the heater 40. The heating of the heater 40 heats the working gas G in the heater tube 41. As a result, the working gas G expands, increasing the pressure in the expansion space ES and pressing against the expansion piston EP. Here, the pressure in the expansion space ES is defined as P E (Pa), and the volume of the expansion space ES is V E (m 3 ), the work load in the expansion process is W E (J) is W E =∫P E dV E It is expressed as:

[0035] As the expansion piston EP is pressed and moved, the expansion-side piston rod 81 and the expansion-side crosshead piston 82 rotate the expansion-side crankshaft 84 in the positive direction via the expansion-side connecting rod 83. The rotation of the expansion-side crankshaft 84 rotates the first belt 92, causing the output shaft SH to rotate in the positive direction. When the output shaft SH rotates, the second belt 93 rotates, causing the compression-side crankshaft 89 to rotate in the positive direction.

[0036] By the rotation of the compression side crankshaft 89, the compression side connecting rod 88 presses the compression side crosshead piston 87 and the compression side piston rod 86, and pushes the compression piston CP into the main body 30. As a result, the compression space CS is compressed, and the working gas G in the compression space CS flows into the cooler 50, and the working gas G is cooled by the cooler 50. Here, the pressure in the compression space CS is expressed as P C (Pa), and the volume of the compression space CS is V C (m 3 ), the work load in the compression process is W C (J) is W C =-∫P C dV C It is expressed as:

[0037] Therefore, when the amount of work required to rotate the output shaft SH (for example, the amount of work required to generate electricity) is W (J), the amount of work W is the amount of work W during the expansion process. E and the work load in the compression process W C and a predetermined mechanical efficiency η of the engine unit 20, the following equation is used: W = (W E +W C ) η=(∫P E dV E -∫P C dV C )·η

[0038] The expansion and compression steps are repeated by the reciprocating movements of the expansion piston EP and the compression piston CP. At this time, the pressure P E and volume V E In the compression space CS, the pressure PC and volume V C This changes as shown in FIG.

[0039] (1-4. Timing) As described above, the power imparted to the expansion piston side crank mechanism 85 by the movement of the expansion piston EP shown in FIG. 1 is transmitted to the compression piston side crank mechanism 90 via the first belt 92, the output shaft SH, and the second belt 93.

[0040] Here, the expansion piston EP and the compression piston CP reciprocate within the main body 30 with a predetermined phase difference. The phase difference corresponds to the difference between the crank angle of the expansion piston-side crank mechanism 85 and the crank angle of the compression piston-side crank mechanism 90. Therefore, for example, when the rotation angle (crank angle) of the expansion-side crankshaft 84 from a reference position is θ (°), the rotation angle (crank angle) of the compression-side crankshaft 89 from a reference position is expressed as (θ-β), where β (°) is a phase lag. The phase lag β is, for example, 90°, but is not limited to 90°.

[0041] The expansion piston side crank mechanism 85 and the compression piston side crank mechanism 90 are pre-timed to realize the above-mentioned phase difference. Such timing can be achieved, for example, by connecting the expansion side crankshaft 84 to the output shaft SH via a first belt 92 at a predetermined rotational position, and connecting the compression side crankshaft 89 to the output shaft SH via a second belt 93 at a predetermined rotational position.

[0042] Specifically, the expansion side crankshaft 84 and the first belt 92 are provided with marks for alignment. The compression side crankshaft 89 and the second belt 93 are provided with marks for alignment. Therefore, by aligning the marks of the expansion side crankshaft 84 and the first belt 92 and connecting them, and aligning the marks of the compression side crankshaft 89 and the second belt 93 and connecting them, the expansion side crankshaft 84 can be connected to the output shaft SH via the first belt 92 at a predetermined rotational position, and the compression side crankshaft 89 can be connected to the output shaft SH via the second belt 93 at a predetermined rotational position. The first belt 92 and the second belt 93 used at this time are preferably toothed belts, i.e., timing belts. In this manner, timing is performed. That is, the expansion piston side crank mechanism 85 and the compression piston side crank mechanism 90 are connected to each other via the power transmission unit 91 so as to be capable of timing.

[0043] In this embodiment, the expansion piston side crank mechanism 85 and the compression piston side crank mechanism 90 are connected via a power transmission unit 91 so as to be capable of transmitting power and adjusting timing, but it is sufficient that they are connected so as to enable at least one of power transmission and timing.

[0044] <2. Details of placement inside the main unit> As shown in FIG. 1, the expansion piston EP and the heater 40 are arranged in a straight line in the direction of movement of the expansion piston EP in the main body 30. The cooler 50 and the compression piston CP are arranged in a straight line in the direction of movement of the compression piston CP in the main body 30. Here, "arranged in a straight line" means that two members are arranged (side by side) along one direction. The direction of movement of the expansion piston EP refers to the direction in which the expansion piston EP reciprocates within the main body 30 due to the expansion of the working gas G in the main body 30 and the rotation of the expansion-side crankshaft 84. On the other hand, the direction of movement of the compression piston CP refers to the direction in which the compression piston CP reciprocates within the main body 30 due to the compression of the working gas G in the main body 30 and the rotation of the compression-side crankshaft 89.

[0045] Such a linear arrangement allows the entire expansion space ES between the expansion piston EP and the heater 40 to contribute to the pressing of the expansion piston EP. Also, the entire compression space CS between the cooler 50 and the compression piston CP to contribute to the retraction of the compression piston CP. Therefore, there is no void space in the expansion space ES that does not contribute to the pressing of the expansion piston EP. Also, there is no void space in the compression space CS that does not contribute to the retraction of the compression piston CP. As a result, the heating of the working gas G by the heater 40 and the cooling of the working gas G by the cooler 50 can efficiently drive the Stirling engine 100 (particularly the engine section 20) and increase the output of the engine section 20 (specifically the rotation speed of the output shaft SH).

[0046] However, when considering another configuration in which the working gas contained in the main body is drawn out of the main body and used for heat exchange with a heat source, for example, the working gas that does not contribute at all to the operation of the expansion piston or compression piston exists outside the main body in the above configuration. In other words, the entire space outside the main body through which the working gas flows becomes a wasted space (ineffective space) that does not contribute to the operation of the expansion piston, etc.

[0047] In this embodiment, the thermosiphon 1 transfers heat received from the heat source HS to the heater 40 by the heat medium. In this configuration, heat is transferred from the heat source HS to the heater 40 by the heat medium of the thermosiphon 1, so that the working gas G is contained (confined) within the main body 30, and the entire working gas G within the main body 30 can contribute to the operation of the expansion piston EP or the compression piston CP. Therefore, a configuration in which heat is transferred using the thermosiphon 1, as in this embodiment, is extremely effective in that it provides an effect common to the linear arrangement of the heater 40, such as reducing dead space.

[0048] As shown in Fig. 1, in this embodiment, the expansion piston EP, the heater 40, the cooler 50, and the compression piston CP are arranged in a straight line in the main body 30. In this configuration, there are no bends in the flow path in the main body 30, so there is no pressure loss caused by the bends. Therefore, in this case, it is expected that a decrease in output of the engine unit 20 caused by the pressure loss can be avoided. In this respect, the straight line arrangement shown in Fig. 1 is desirable.

[0049] In particular, in a configuration in which the regenerator 60 is disposed between the heater 40 and the cooler 50 as shown in Fig. 1, the heater 40, the regenerator 60, and the cooler 50 are aligned in a straight line, and no bending of the flow path occurs in the regenerator 60. This is effective in reducing pressure loss in the regenerator 60.

[0050] When it is more important to configure the main body 30 compactly than to reduce pressure loss caused by bending the flow path, the main body 30 may be bent. The configuration in which the main body 30 is bent will be described below.

[0051] Fig. 4 is an explanatory diagram showing another configuration of the Stirling engine 100. For convenience, the power transmission mechanism from the expansion side connecting rod 83 to the compression side connecting rod 88 shown in Fig. 1 is omitted in Fig. 4. As shown in Fig. 4, the main body 30 may be bent in an inverted U-shape. As a result, the heater 40 and other members are arranged in the main body 30 as follows.

[0052] In the main body 30, the regenerator 60 is arranged to extend in one direction. Here, the one direction is conveniently referred to as the A direction. Meanwhile, the expansion piston EP and the heater 40 are arranged in a straight line in the B direction. Here, the B direction is a direction intersecting the A direction, for example, a direction perpendicular to the A direction. The heater 40 is connected to the lower part of the regenerator 60 on one side of the center C0 of the regenerator 60 in the A direction. The cooler 50 and the compression piston CP are also arranged in a straight line in the B direction. The cooler 50 is connected to the lower part of the regenerator 60 on the other side of the center C0 of the regenerator 60 in the A direction. The B direction corresponds to the movement direction of the expansion piston EP and the compression piston CP.

[0053] In the configuration in which the heater 40, the regenerator 60, and the cooler 50 are arranged as described above in the main body 30, the expansion piston EP and the heater 40, and the cooler 50 and the compression piston CP are arranged in parallel. In this case, the flow path of the working gas G between the expansion space ES and the compression space CS is bent by 180° at the regenerator 60.

[0054] By arbitrarily setting the intersection angle between the directions A and B, it is also possible to realize a flow path bent at an arbitrary angle other than 180° as the flow path of the working gas G. Therefore, from the viewpoint of increasing the degree of freedom in the arrangement of the expansion piston EP and the heater 40, the cooler 50 and the compression piston CP, the expansion piston EP and the heater 40, the cooler 50 and the compression piston CP may be arranged so as to intersect with the extension direction of the regenerator 60.

[0055] In particular, from the viewpoint of realizing a compact layout by bending the flow passages, it is desirable to arrange the expansion piston EP and the heater 40, and the cooler 50 and the compression piston CP in parallel.

[0056] <3. Notes> The Stirling engine described in this embodiment can also be expressed as follows.

[0057] The Stirling engine in Appendix (1) is A body that contains a working gas; a heater disposed within the body and configured to apply heat from a heat source to the working gas, a cooler disposed within the body and configured to cool the working gas; an expansion piston disposed within the body via an expansion space for the working gas and the heater; The compressor further includes a compression piston disposed within the main body via the cooler and a compression space for the working gas, the expansion piston and the heater are aligned in a direction of movement of the expansion piston within the body; The cooler and the compression piston are aligned within the body in a direction of movement of the compression piston.

[0058] The Stirling engine of appendix (2) is the Stirling engine of appendix (1), a thermosiphon containing a heat medium that receives the heat from the heat source; The thermosiphon transfers the heat to the heater via the heat medium.

[0059] The Stirling engine of appendix (3) is the Stirling engine of appendix (1) or (2), The expansion piston, the heater, the cooler, and the compression piston are aligned within the body.

[0060] The Stirling engine of appendix (4) is the Stirling engine of appendix (3), The compressor further includes a regenerator that circulates the working gas between the expansion space and the compression space, The regenerator is disposed between the heater and the cooler.

[0061] The Stirling engine of appendix (5) is the Stirling engine of appendix (3) or (4), an expansion piston side crank mechanism connected to the expansion piston; a compression piston-side crank mechanism connected to the compression piston, The expansion piston side crank mechanism and the compression piston side crank mechanism are connected to each other so as to be capable of transmitting power and / or being timed via a power transmission part.

[0062] The Stirling engine of appendix (6) is the Stirling engine of appendix (1) or (2), The compressor further includes a regenerator that circulates the working gas between the expansion space and the compression space, The regenerator is disposed to extend in one direction, the expansion piston and the heater are arranged in a straight line in a direction intersecting the one direction, The cooler and the compression piston are arranged in a straight line in a direction intersecting the one direction.

[0063] The Stirling engine of appendix (7) is the Stirling engine of appendix (6), The expansion piston and the heater, and the cooler and the compression piston are arranged in parallel.

[0064] Although the embodiment of the present invention has been described above, the scope of the present invention is not limited to this, and the invention can be expanded or modified without departing from the spirit of the invention. [Industrial Applicability]

[0065] The present invention can be used in a Stirling engine that utilizes heat from a heat source, such as exhaust heat, and drives an engine section by performing heat exchange. [Explanation of symbols]

[0066] 1 Thermosyphon 30 Main unit 40 Heater 50 Cooler 60 Regenerator 85 Expansion piston side crank mechanism 90 Compression piston side crank mechanism 91 Power transmission section 100 Stirling Engine CP Compression Piston CS Compressed Space EP Expansion Piston ES Expansion Space G Working gas HS heat source

Claims

1. A body that contains a working gas; a heater disposed within the body and configured to apply heat from a heat source to the working gas, a cooler disposed within the body and configured to cool the working gas; an expansion piston disposed within the body via an expansion space for the working gas and the heater; The compressor further includes a compression piston disposed within the main body via the cooler and a compression space for the working gas, the expansion piston and the heater are aligned in a direction of movement of the expansion piston within the body; A Stirling engine, wherein the cooler and the compression piston are aligned in a direction of motion of the compression piston within the body.

2. a thermosiphon containing a heat medium that receives the heat from the heat source; 2. The Stirling engine of claim 1, wherein the thermosiphon transfers the heat to the heater by the heat transfer medium.

3. 2. The Stirling engine of claim 1, wherein the expansion piston, the heater, the cooler, and the compression piston are aligned within the body.

4. The compressor further includes a regenerator that circulates the working gas between the expansion space and the compression space, 4. The Stirling engine of claim 3, wherein the regenerator is disposed between the heater and the cooler.

5. an expansion piston side crank mechanism connected to the expansion piston; a compression piston-side crank mechanism connected to the compression piston, 4. The Stirling engine according to claim 3, wherein the expansion piston side crank mechanism and the compression piston side crank mechanism are connected to each other so as to be capable of transmitting power and / or being timed via a power transmission section.

6. The compressor further includes a regenerator that circulates the working gas between the expansion space and the compression space, The regenerator is disposed to extend in one direction, the expansion piston and the heater are arranged in a straight line in a direction intersecting the one direction, 2. The Stirling engine according to claim 1, wherein the cooler and the compression piston are arranged in a straight line in a direction intersecting the one direction.

7. 7. The Stirling engine of claim 6, wherein the expansion piston and the heater, and the cooler and the compression piston are arranged in parallel.

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