JPH09264190A - Stirring equipment - Google Patents

Abstract

PROBLEM TO BE SOLVED: To significantly contract backlash by providing a phase difference changing means for changing the mutual phase difference relation of pistons to each cylinder chamber, and constituting this means in such a manner that the circumferential tooth train of an elastic rotating body is pressed onto the inside tooth train of a rigid rotating body by the elastic deformation of the elastic rotating body, and these tooth trains are mutually geared in a plurality of positions. SOLUTION: A phase changing means for changing mutual phase difference of a plurality of pistons in a gas cycle equipment has a rigid rotating body 20 having a number of teeth (a) formed on the inside, an elastic rotating body 21 having teeth (b) of the number different from the tooth number of the rotating body 20 formed on the circumference. It also has a non-circular member 22 for non-circularly elastically deforming the tooth train (b) of the elastic rotating body 21 so as to be geared with the tooth train (a) of the rigid rotating body 20 in a plurality of circumferential positions, and this non-circular member 22 is rotated according to the change instruction by an operating means 23. One of a plurality of pistons is interlocked with the elastic rotating body 21, and the other pistons to the rigid rotating body 20.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a Stirling engine that generates power by a Stirling cycle, a Stirling heat pump that outputs hot heat or cold heat by a reverse Stirling cycle, or a power / heat device that performs a Stirling cycle and a reverse Stirling cycle in parallel. For details on Stirling equipment for various applications such as
A plurality of cylinder chambers that individually discharge and inhale working gas with the operation of the pistons that interlock with the rotation transmission system, gas communication passages that communicate these cylinder chambers, and between the cylinder chambers that are adjacent to each other in this gas communication passage are provided. A regenerative heat exchanger provided in each case and a heat input / output heat exchanger for respectively inputting / extracting heat to / from each of the cylinder chambers are provided, and in the rotary transmission system, a mutual phase difference relationship between the pistons and the cylinder chambers. The present invention relates to a Stirling device provided with a phase difference changing unit that changes the number according to a change command.

[0002]

2. Description of the Related Art In this type of Stirling machine, the phase difference changing means changes the phase difference relationship of pistons.
According to the operating conditions of the equipment, the input / output relation and the expression of the engine function / heat pump function can be adjusted. Conventionally, as the phase difference changing means, as shown in FIG. A plurality of cylinder chambers C1 to C
Among the three pistons p1 to p3, a planetary gear type differential mechanism is provided between a rotary shaft portion 4a having cranks for some pistons p1 and a rotary shaft portion 4b having cranks for other pistons p2 and p3. A structure in which D1 is interposed or a structure in which a bevel gear type differential mechanism D2 is interposed as shown in FIG. 6 has been adopted.

That is, these planetary gear type differential mechanisms D
1 or bevel gear type differential mechanism D2,
The rotary shaft portions 4a and 4b are differentially operated and relatively rotated by a desired angle, thereby changing the phase difference relationship between the partial piston p1 and the other pistons p2 and p3. (See Japanese Patent Application No. 7-22449).

[0004]

However, in a differential mechanism using general gears such as a planetary gear type and a bevel gear type, there is a backlash necessary for smoothly interlocking rotation of rigid gears. Therefore, there is a limit to the improvement of the adjustment accuracy of the piston phase difference relationship.In this respect, in the operation of the Stirling machine, adjustment of the input / output relationship and adjustment of the expression state of the engine function / heat pump function are performed under various operating conditions. Therefore, there was still room for improvement in carrying out the method accurately and accurately.

In view of the above situation, the main object of the present invention is to make it possible to more accurately change and adjust the piston phase difference relationship by adopting a rational differential type for the phase difference changing means of the Stirling machine. There is a point to do.

[0006]

[Means for Solving the Problems]

[Invention of Claim 1] In the invention of Claim 1,
), With the operation of the pistons p1 to p3 in a predetermined phase difference relationship, under the communication by the gas communication passages 7a and 7b, the regenerative heat exchangers 8a and 8b, and the heat input and output devices 9 and 10,
Under the action of 11, the cylinder chambers C1 to C3 are individually discharged and sucked into the cylinder chambers C1 to C1.
A Stirling cycle or a reverse Stirling cycle is executed between C3 and C3.

That is, in the execution of the Stirling cycle, the heat input causes the device to function as a Stirling engine, and the generated power is output to the rotary transmission system 4. In the execution of the reverse Stirling cycle, the rotation transmission system 4
It makes the equipment function as a Stirling heat pump by the power input from and outputs cold heat and hot heat as heat output.

In the operation of the device as described above, the phase difference changing means 15 changes and adjusts the mutual phase difference relationship between the pistons p1 to p3, thereby changing the execution Stirling cycle and the reverse Stirling cycle. The input / output relationship and the expression state of the engine function / heat pump function are adjusted. Regarding the change adjustment of the piston phase difference relationship (see FIGS. 2 to 4), the rigid rotating body 20, the elastic rotating body 21, and the non-circular member are adjusted. In the three-way relationship with 22, the non-circular member 22 fitted in the elastic rotating body 21 is relatively rotated with respect to the elastic rotating body 21 by the operating means 23, and by this relative rotation (see FIG. 4). (B) → (B)
The elastic rotation of the elastic rotating body 21 with respect to the inner peripheral tooth row a ... by changing the phase of the non-circular shape of the elastic rotating body 21 with respect to the rigid rotating body 20 with the elastic deformation of the elastic rotating body 21. A plurality of occlusal positions x of the outer peripheral tooth row b of the body 21 are moved, and by this movement of the occlusal positions x, the number of teeth and the elastic rotation of the rigid body rotating body 20 per one rotation operation of the non-circular member 22 by the operating means 23. Only the difference from the number of teeth on the body 21,
Rigid body rotating body 20 and elastic rotating body 21 are relatively rotated as a differential operation, whereby, in the rotation transmission system 4, a partial piston p1 of pistons p1 to p3 interlocking with elastic rotating body 21 and a rigid body The phase difference relationship with the other pistons p2, p3 that are interlocked with the rotating body 20 is changed.

After the operation of changing the relationship of the phase difference between the pistons, the rotation of the non-circular member 22 is stopped, and the phase of the non-circular shape of the elastic rotor 21 with respect to the rigid rotor 20 is maintained. The rigid body rotating body 20 and the elastic rotating body 21 are integrally rotated by the occlusion of the inner peripheral tooth row a ... Of the elastic rotating body 21 and the outer peripheral tooth row b of the elastic rotating body 21 at a plurality of points x. In the transmission system 4, the elastic rotating body 2
The partial piston p1 which is interlocked with 1 and the other pistons p2 and p3 which are interlocked with the rigid body 20 are interlocked while maintaining the changed phase difference relationship.

That is, according to the first aspect of the invention, due to the structure of the phase difference changing means, the outer peripheral tooth row of the elastic rotating body is changed to the inner peripheral tooth of the rigid rotating body by elastic deformation of the elastic rotating body into a non-circular shape. Since these tooth rows are occluded at multiple points by pressing against the row, the backlash is greatly reduced compared to the occlusal of general rigid gears (gear) used in differential mechanisms such as planetary gear type and bevel gear type. In addition, it is possible to obtain a large transmission force while increasing the number of teeth by making the teeth finer compared to a general rigid gear (gear) of the same size. Thus, it is possible to secure a high reduction ratio and a high rotation angle resolution.

From these facts, the adjustment accuracy of the piston phase difference relationship can be greatly improved as compared with the conventional one, and consequently, in the operation of the Stirling machine, the adjustment of the input / output relationship and the expression state of the engine function / heat pump function are adjusted. Can be performed more finely and more accurately according to various operating conditions, and the device performance can be greatly improved.

[Invention of Claim 2] In the invention of Claim 2 (see FIG. 2), when the non-circular member 22 is rotated by the motor 23 as the operating means, the above-mentioned operation is performed. Partial piston p1 and elastic rotor 2
1 is interlocked with the rotating shaft 4a, or the other pistons p2, p3 and the rigid rotating body 20 are interlocked with the rotating shaft 4b.
A motor case portion 24 is provided (in FIG. 2, the latter rotating shaft portion 4b), and the non-circular member 22 is relatively rotated with respect to the elastic rotating body 21 by the motor 23 internally supported in the motor case portion 24.

That is, according to the invention of claim 2,
In the configuration of the phase difference changing means, a motor as an operating means for rotating the non-circular member is provided with a rotating shaft part for interlocking a part of the piston and the elastic rotating body, and a rotating shaft part for interlocking the other piston and the rigid rotating body. Since it is arranged coaxially, the phase difference changing means can be made compact and small, and as a result, the entire Stirling machine can be made compact and small.

[Invention of Claim 3] In the invention of Claim 3 (see FIG. 1), in a configuration in which a high temperature cylinder chamber C1, an intermediate temperature cylinder chamber C2, and a low temperature cylinder chamber C3 are provided as cylinder chambers, these cylinders Along with the operation of the pistons p1 to p3 with respect to the chambers C1 to C3 in a predetermined phase difference relationship, under the communication by the gas communication passages 7a and 7b, the regenerative heat exchangers 8a and 8b, and the heater as the heat input / output device. 9,
Under the action of the heat exchanger 10 for extracting heat and the heat exchanger 11 for extracting cold, each of the cylinder chambers C1 to C3 is individually caused to discharge and inject working gas, so that among the cylinder chambers C1 to C3,
With respect to the combination of the high temperature cylinder chamber C1 and the medium temperature cylinder chamber C2, a Stirling cycle in which the applied heat from the heater 9 is input is executed to function as a Stirling engine, and the generated power is applied from the drive means 1. It is output to the rotary transmission system 4 in the form of being added to the power.

With respect to the combination of the medium temperature cylinder chamber C2 and the low temperature cylinder chamber C3, a reverse Stirling cycle with the power from the rotary transmission system 4 as an input is executed to function as a Stirling heat pump, and its heat output is The generated heat in the medium temperature cylinder chamber C2 is taken out from the heat exchanger 10 for extracting heat, and the cold heat generated in the low temperature cylinder chamber C3 is taken out from the heat exchanger 11 for extracting cold heat.

In this equipment operation, the piston p1 of the high temperature cylinder chamber C1 and the other cylinder chambers C2, C
One of the three pistons p2 and p3 is linked to the elastic rotating body 21, and the other is connected to the rigid rotating body 2
The Stirling cycle of the implementation is performed by changing and adjusting the phase difference relation of the piston p1 of the high temperature cylinder chamber C1 with respect to the piston p2 of the middle temperature cylinder chamber C2 and the piston p3 of the low temperature cylinder chamber C3 by the phase difference changing means 15 which is interlocked with 0. Is adjusted to adjust the expression state of the engine function by the heat input from the heater 9.

That is, in the operating mode in which the heat pump function is developed to obtain the heat output of cold heat or warm heat while power is applied to the rotary transmission system 4 by the drive means 1 and the engine function by the heat input from the heater 9, As described above, the piston phase difference relationship is adjusted by the phase difference changing means 15 and the engine function expression state by the heat input from the heater 9 is adjusted, whereby the power input by the driving means 1 and the heat input by the heater 9 are adjusted. It is possible to appropriately change the input ratio of and.

That is, according to the third aspect of the invention, as a heat pump device for obtaining hot heat or cold heat, the input ratio between the power input by the driving means and the heat input by the heater can be appropriately changed according to the operating conditions. A heat pump device having excellent functionality can be provided. Particularly, since the invention according to claim 1 can finely and accurately adjust the piston phase difference relationship, the input ratio can be finely adjusted according to the operating conditions. It can be performed properly and high device performance can be obtained.

[0019]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 shows an engine-driven heat pump using a Stirling machine, 1 is an engine as an example of driving means, 3 is a gas cycle equipment part, and these engine 1 and gas cycle equipment are shown. The part 3 is interlocked by a rotary shaft 4 as a rotary transmission system.

Reference numeral 5 is a fuel supply passage for supplying the fuel F to the engine 1, and 6 is an exhaust passage for engine exhaust gas.

The gas cycle equipment section 3 has, as its equipment structure, a high temperature cylinder chamber C1 and a medium temperature cylinder chamber C2 which individually discharge and inhale the working gas G with the operation of the pistons p1, p2, p3 interlocked with the rotary shaft 4. A low temperature cylinder chamber C3 is provided, and a high temperature cylinder chamber C1 and a medium temperature cylinder chamber C are provided.
2 through the gas communication passage 7a, the medium temperature cylinder chamber C2 and the low temperature cylinder chamber C3 through the gas communication passage 7b, each of the gas communication passages 7a, 7b 8a and 8b are interposed.

Further, 9 is a heater for inputting heat into the high temperature cylinder chamber C1, 10 is a heat exchanger for extracting heat generated in the medium temperature cylinder chamber C2, and 11 is a low temperature cylinder chamber C.
It is a heat exchanger for cold heat extraction that takes out the cold heat generated in No. 3.

In other words, in the gas cycle equipment section 3, the high temperature cylinder chamber C1, the medium temperature cylinder chamber C2, and the low temperature cylinder chamber C3 are respectively operated by the gas communication passages 7a and 7b as the pistons p1 to p3 operate. Under communication, the above-mentioned heater 9 and each heat exchanger 8a, 8b, 1
Among the cylinder chambers C1 to C3, the set of the high temperature cylinder C1 and the intermediate temperature cylinder chamber C2 is heated by the discharge of the working gas under the action of 0 and 11, and the heater 9
The Stirling cycle is executed under the heat input to the high temperature cylinder chamber C1 to function as the Stirling engine, and the generated power is output to the rotary shaft 4 in a form of being added to the applied power from the engine 1.

Further, of the cylinder chambers C1 to C3, the set of the medium temperature cylinder chamber C2 and the low temperature cylinder chamber C3 performs a reverse Stirling cycle using the power from the rotary shaft 4 as an input to function as a Stirling heat pump. As a result, as the heat output, the cold generated in the low temperature cylinder chamber C3 is taken out from the heat exchanger 11 for taking out cold heat, and the hot generated heat in the intermediate temperature cylinder chamber C2 is taken out from the heat exchanger 10 for taking out hot heat. .

The heater 9 has a high temperature cylinder chamber C1.
As a heat input to the high temperature cylinder chamber C1, the retained heat of the engine exhaust gas E guided by the exhaust passage 6 is applied to the high temperature cylinder chamber C1. Further, the working gas G of the gas cycle equipment unit 3 includes helium gas, hydrogen gas, air, etc.
Various gases can be adopted.

Reference numeral 15 is a phase difference changing means for changing the mutual phase difference relationship between the pistons p1 to p3 in conjunction with the rotary shaft 4 in response to a change command from the command device 16, and specifically, high temperature. In the connection of the rotary shaft portion 4a having a crank for the piston p1 of the cylinder chamber C1 and the rotary shaft portion 4b having a crank for the pistons p1, p2 of the other two cylinder chambers C2, C3, these rotary shaft portions 4a, 4b are connected. Is relatively rotated by a required rotation angle to change the phase difference relationship between the piston p1 of the high temperature cylinder chamber C1 and the pistons p1 and p2 of the other two cylinder chambers C2 and C3.

That is, the gas cycle equipment section 3 is made to function as a heat pump by the motive power obtained by causing the gas cycle equipment section 3 to function as an engine by the heat input from the heater 9 and the applied power from the engine 1, and cold heat and warm heat. In this operation mode, the phase difference changing means 15 changes and adjusts the phase difference relationship between the pistons p1 to p3 to adjust the expression state of the engine function of the gas cycle equipment part 3. The input ratio between the power input from the engine 1 and the heat input from the heater 9 can be appropriately changed according to various operating conditions.

As to the concrete structure of the phase difference changing means 15, as shown in FIGS. 2, 3 and 4, the main component thereof is a large number of spline-shaped teeth a (for example, from 100 to several). An annular rigid body 20 having 100 teeth),
The number of teeth of the rigid body 20 is extremely small (for example,
(A few sheets), a cylindrical elastic rotating body 21 having a large number of spline-shaped teeth b formed on the outer circumference thereof, and the elastic rotating body 21 is relatively rotatably fitted into the elastic rotating body 21 by this inner fitting. A non-circular shape that elastically deforms the elastic rotary body 21 into a non-circular shape so that the outer peripheral tooth row b of the elastic rotary body 21 is engaged with the inner peripheral tooth row a of the rigid rotary body 20 at a plurality of locations x in the circumferential direction. A member 22 (ellipsoidal shape is adopted in the present embodiment), and a servomotor 23 for rotating the non-circular member 22 in response to a command from the command device 16 is provided as an operation means for the non-circular member 22.

The pair of the rigid rotary body 20 and the elastic rotary body 21 is connected between the rotary shaft portion 4a on the one side and the rotary shaft portion 4b on the other side by the rotary shaft portion 4a,
4b, the rotary shaft portion 4a on one side is connected to the elastic rotary body 21, and the rotary shaft portion 4b on the other side is arranged.
Is connected to the rigid rotating body 20.

That is, in the phase difference changing means 15, the non-circular member 22 is relatively rotated by the servo motor 23 with respect to the elastic rotating body 21, so that the elastic member is elastically moved as shown in (a) to (b) of FIG. The elastic rotating body with respect to the inner peripheral tooth row a of the rigid rotating body 20 is changed by changing the phase of the non-circular shape (ellipse) of the elastic rotating body 21 with respect to the rigid rotating body 20 with the elastic deformation of the rotating body 21. The plural occlusal positions x of the outer peripheral tooth row b of 21 are moved.

Due to the movement of the occlusal position x, a single rotation operation of the non-circular member 22 by the servo motor 23 is performed by the difference between the number of teeth of the rigid body 20 and the number of teeth of the elastic body 21. 20 and the elastic rotating body 21 are relatively rotated as a differential operation, so that the rotating shaft portion 4 on one side is rotated.
The phase difference relationship between the piston p1 of the high temperature cylinder chamber C1 that is linked to a and the pistons p2 and p3 of the other two cylinder chambers C2 and C3 that are linked to the rotary shaft portion 4b on the other side is changed.

After the operation of changing the relationship of the piston phase difference, the rigid rotating body 20 is kept in a state in which the non-circular shape phase of the elastic rotating body 21 with respect to the rigid rotating body 20 is maintained by stopping the rotation operation of the non-circular member 22. .. and the outer peripheral tooth row b of the elastic rotating body 21 are engaged with each other at a plurality of positions x to integrally rotate the rigid body rotating body 20 and the elastic rotating body 21. The piston p1 of the high temperature cylinder chamber C1 and the pistons p2 and p3 of the other two cylinder chambers C2 and C3
And are operated in synchronism with the changed phase difference relationship maintained.

The servomotor 23 is arranged coaxially with the rigid rotary body 20 and the elastic rotary body 21 on the rotary shaft portions 4a and 4b on the one side and the other side. A cylindrical motor case portion 24 is provided on the rotating shaft portion 4b on the other side to be connected.
4, the servo motor 23 is internally supported.

Reference numeral 25 is a commander 1 for transmitting an operation signal.
6, the signal line 26a on the fixed side and the signal line 2 on the side of the servo motor 23 that rotates together with the rotating shaft portion 4b on the other side.
6b and the other side rotary shaft portion 4b and the servo motor 23
It is a universal connector that always keeps the connected state while allowing the integral rotation of the.

Further, 27 is a non-circular bearing that is interposed between the elastic rotating body 21 and the non-circular member 22 to facilitate relative rotation between them, 28 is a fixed case, and 29a, 2a.
Reference numeral 9b is a bearing for supporting the rotating shaft portion 4b on the other side and the rigid rotating body 20 connected thereto bilaterally.

[Other Embodiments] Next, other embodiments will be listed. In the above-described embodiment, the high temperature cylinder chamber C1, the medium temperature cylinder chamber C2, and the low temperature cylinder chamber C are used as the cylinder chambers.
Although the three chambers 3 and 3 are provided to execute the Stirling cycle and the reverse Stirling cycle, the number of the cylinder chambers is not limited to three, and any number of chambers of two or more can be used. But it's okay.

As for the gas cycle to be executed, either one of the Stirling cycle and the reverse Stirling cycle is executed, or both the cycles are executed in parallel, or the Stirling cycle or the reverse Stirling cycle and another gas cycle are executed. It may be performed in parallel.

The heat input / output devices 9, 10, 11 for inputting / outputting heat to / from each of the cylinder chambers C1 to C3 are the cylinder chamber C1.
~ Instead of directly equipping C3, the gas communication passage 7
It is also possible to adopt a form of equipment that is interposed between a and 7b.

In the above embodiment, the high temperature cylinder chamber C1
Of the piston p1 and the pistons p2 and p3 of the other two cylinder chambers C2 and C3, one of which is linked to the rigid body 20 and the other of which is the elastic body 21.
Although the number of pistons interlocked with the rigid rotary body 20 and the number of pistons interlocked with the elastic rotary body 21 may be one or more, respectively.

Further, in the above-described embodiment, the phase difference changing means 15 which has the rigid rotating body 20, the elastic rotating body 21, and the non-circular member 22 as main constituent members is provided with the piston p1 of the high temperature cylinder chamber C1 and the medium temperature cylinder chamber C2. In the rotary transmission system 4 such as by interposing them in the transmission system portion between the piston p2 of the intermediate temperature cylinder chamber C2 and the piston p3 of the low temperature cylinder chamber C3 in the intermediate temperature cylinder chamber C2. The phase difference changing means 15 may be interposed.

Elastic rotating body 2 in the phase difference changing means 15
1 and a part of the piston p1, and a rigid rotating body 20
The interlocking with the other pistons p2, p3 is not limited to the direct coupling type by the shaft coupling as in the above-described embodiment, but various interlocking types can be adopted.

In the above-described embodiment, the rotation operation of the non-circular member 22 is performed by the motor 23. However, in some cases, an operation tool interlocked with the non-circular member 22 is provided as an operation means, and this operation tool is provided with this operation tool. On the other hand, the rotation operation of the non-circular member 22 may be performed by an artificial operation force given as a change command.

The deformed shape of the elastic rotating body 21 elastically deformed by the non-circular member 22 is not limited to the elliptical shape, and may be a triangular shape, a quadrangular shape, or a polygonal shape.

Although the engine 1 is provided as the drive means in the above-mentioned embodiment, when the drive means 1 for applying power to the rotation transmission system 4 is provided, the drive means 1 is not limited to the engine, but may be a motor or a turbine. Other rotary power generation means may be used.

In the case of a device configuration in which heat is input to the high temperature cylinder chamber C1 by the heater 9, the heat input is the heat retained by the engine exhaust gas, the heat retained by the engine cooling water after the cooling action, or these engine exhausts. In addition to heat, various kinds of heat such as heat generated by a burner and retained heat of high-temperature steam can be adopted.

Incidentally, reference numerals are written in the claims for convenience of comparison with the drawings, but the present invention is not limited to the configuration of the attached drawings by the entry.

[Brief description of drawings]

FIG. 1 is a block diagram of an engine-driven heat pump using a Stirling machine.

FIG. 2 is a vertical sectional view of a phase difference changing unit.

FIG. 3 is an exploded perspective view of a phase difference changing unit.

FIG. 4 is a sectional view showing the operation of the phase difference changing means.

FIG. 5 is a structural diagram of a phase difference changing unit showing a conventional example.

FIG. 6 is a structural diagram of a phase difference changing unit showing another conventional example.

[Explanation of symbols]

 4 Rotation transmission system p1 to p3 Piston G Working gas C1 Cylinder chamber (high temperature cylinder chamber) C2 Cylinder chamber (medium temperature cylinder chamber) C3 Cylinder chamber (low temperature cylinder chamber) 7a, 7b Gas communication passage 8a, 8b Regenerative heat exchanger 9 Input / output Heater (heater) 10 Heat input / output device (heat exchanger for extracting heat / heat) 11 Heat input / output device (heat exchanger for extracting cold / heat) 15 Phase difference changing means a, b teeth 20 Rigid rotating body 21 Elastic rotating body x Occlusal part 22 Non-circular member 23 Operating means (motor) 4a, 4b Rotating shaft part 24 Motor case part 1 Driving means

Claims (3)

[Claims] 1. A plurality of cylinder chambers (C1 to C3) for individually discharging and sucking working gas (G) with the operation of pistons (p1 to p3) interlocking with a rotary transmission system (4), and these cylinder chambers. The gas communication passages (7a) and (7b) for communicating (C1 to C3) and the cylinder chambers (C1 to C3) adjacent to each other in the gas communication passages (7a) and (7b) are respectively interposed. Heat input / output devices (9), (10), (11) for inputting / extracting heat to / from each of the regenerative heat exchangers (8a) and (8b) and the cylinder chambers (C1 to C3).
Are provided, and in the rotation transmission system (4), the cylinder chamber (C1
To C3), the phase difference changing means (1) for changing the mutual phase difference relationship of the pistons (p1 to p3) with respect to the change command.
5) A Stirling machine provided with the phase difference changing means (15), wherein the rigid rotating body (20) has a large number of teeth (a) formed on its inner circumference.
And an elastic rotating body (21) having teeth (b) with a number of teeth different from the number of teeth of the rigid rotating body (20) formed on the outer periphery, and an elastic rotating body (21) internally fitted so as to be rotatable relative to the elastic rotating body (21). By this internal fitting, the tooth row (b ...) Of the elastic rotating body (21) is engaged with the tooth row (a ..) of the rigid rotating body (20) at a plurality of circumferential positions (x). As described above, the non-circular member (22) elastically deforms the elastic rotating body (21) into a non-circular shape, and the operating means (23) for rotating the non-circular member (22) in response to the change command. In the rotation transmission system (4), the pistons (p1 to
Some pistons (p1) of p3) are interlocked with the elastic rotating body (21), and other pistons (p2),
A Stirling machine configured to interlock (p3) with the rigid rotating body (20). 2. A rotary shaft portion (4a) for interlocking the partial piston (p1) and the elastic rotary body (21), or the other pistons (p2), (p3) and the rigid rotary body. A motor case portion (24) is provided on a rotating shaft portion (4b) that works in conjunction with (20), and a motor (23) as the operating means for rotating the non-circular member (22) is provided in the motor case portion (24). 24)
The Stirling machine according to claim 1, wherein the Stirling machine is supported in the interior. 3. A drive means (1) for imparting rotational power to the rotary transmission system (4) is provided, and as the cylinder chambers, a high temperature cylinder chamber (C1), an intermediate temperature cylinder chamber (C2) and a low temperature cylinder chamber (C3). ) Are provided, and as the heat input / output device, a heater (9) for applying heat to the high temperature cylinder chamber (C1) and the intermediate temperature cylinder chamber (C
Heat exchanger (1) for extracting heat generated in 2)
0) and a heat exchanger (11) for extracting cold heat generated in the low temperature cylinder chamber (C3), wherein the phase difference changing means (15) is a piston of the high temperature cylinder chamber (C1). (P1) and other cylinder chambers (C
2) and (C3) of the pistons (p2) and (p3), one of them is the partial piston that is interlocked with the elastic rotating body (21), and the other is the rigid rotating body (20). ), The piston (p1) of the high temperature cylinder chamber (C1) and the pistons (p2), (p) of the other cylinder chambers (C2), (C3)
3. The constitution is such that the phase difference relationship with 3) is changed.
Or the Stirling machine according to 2.