JPH08219569A - Variable phase apparatus - Google Patents

Abstract

PURPOSE: To enhance functionality and versatility of a power input type Stirling cycle equipment and improve an achievement coefficient by providing a transmission system operating means to perform a phase difference relationship holding operation for holding a phase difference relationship of a plurality of pistons and a phase difference relationship altering operation for altering the phase difference relationship of the plurality of pistons. CONSTITUTION: A plurality of cranks 14a-14c are rotated in linkage at an angular velocity equal to one another in the respective prescribed directions of rotation to hold a phase difference relationship of the plurality of pistons 9a-9c by a phase difference relationship holding operation. Among the plurality of cranks 14a-14c, one crank 14c and other cranks 14a and 14b are operated to rotate relatively by a required angle of rotation at different angular velocities therebetween to alter the phase difference relationship of the plurality of pistons 9a-9c by a phase difference relationship altering operation. The phase difference relationship holding operation and the phase difference relationship altering operation are accomplished by a transmission system operating means 15.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a variable phase device for a power input type Stirling cycle machine which is operated by power input, and more specifically, a rotary transmission system provided with a plurality of cranks as a device configuration, and this rotary transmission system. Drive means for applying rotational power to the cylinders, a plurality of cylinder chambers for individually discharging and sucking working gas by the operation of a plurality of pistons respectively connected to the cranks, and a gas connection for communicating these cylinder chambers in the order of respective handling temperatures. Power provided with a passage, a regenerative heat exchanger provided in each of the cylinder chambers whose communication order in the gas communication passage is adjacent to each other, and an input / output heat exchanger that separately inputs and outputs heat to and from each of the cylinder chambers. The present invention relates to a variable phase device in an input type Stirling cycle device.

[0002]

2. Description of the Related Art Conventionally, in a power input type Stirling cycle machine, the rotary transmission system is configured such that a plurality of cranks are connected to these cranks by constantly rotating a plurality of cranks at equal angular velocities in accordance with a rotary power input from a driving means. The pistons are always operated with a constant phase difference relationship.In other words, the phase difference relationship between the plurality of pistons that individually discharge and suck the working gas into the plurality of cylinder chambers is fixed at a constant phase during the device manufacturing stage. It was

That is, the piston phase difference relationship that determines the discharge / intake operation relationship between the plurality of cylinder chambers is the device characteristic of this type of power input type Stirling cycle machine, that is, the heat input / output heat ratio of the plurality of cylinder chambers and the drive means. The ratio of power to the heat input / output of each cylinder chamber, the relationship between the ratio of the applied power / cylinder chamber heat input / output and the cylinder temperature ratio of multiple cylinder chambers, or whether each cylinder chamber heats or heats This is an important factor that determines the device characteristics such as the distinction between the two. Therefore, conventionally, the phase difference relationship between multiple pistons (in other words, the discharge / intake operation relationship between multiple cylinder chambers) is fixed at the device manufacturing stage as described above. By fixing it to the above, the desired constant device characteristics were obtained.

[0004]

However, in the conventional power input type Stirling cycle machine as described above, when it is necessary to change the machine characteristics, for example, the coupling portion interposed between the cranks in the rotary transmission system is used. Is disassembled once, and the phase difference relationship of the plurality of pistons is changed by changing the connection by changing the rotational phase relationship between the crank on one side and the crank on the other side in this coupling part.
Alternatively, the rotation transmission system needs to be recombined such that the entire rotation transmission system is replaced with one having a different crank phase relationship.

Therefore, the device characteristics should be appropriately changed according to the change / change of the power input condition from the driving means and the change / change of the thermal input / output condition with respect to the heat quantity or temperature in each of the plurality of cylinder chambers. In addition, because of this, the operation is in a state where the device characteristics do not match the input / output conditions and the coefficient of performance (efficiency) is reduced (that is, the power input value from the drive means or the thermal effect to the cylinder chamber). Energy loss occurs when the input value tends to be excessive with respect to the device characteristic value, and energy loss occurs when the device characteristic value with respect to the thermal output of the cylinder chamber tends toward the required value. ) Will be imposed, and in this respect functionality and
There was room for improvement in terms of versatility and coefficient of performance.

In view of the above circumstances, the present invention provides the following 1. Achievement of the above is the basic purpose, and with the achievement of this basic purpose, the following 2. ~ 4. To achieve the additional objective. 1. We will enhance the functionality and versatility of power input type Stirling cycle equipment and improve the coefficient of performance. 2. An engine-driven refrigerator or heat pump having high functionality and versatility and a high coefficient of performance. 3. To be able to accurately and easily change the device characteristics. 4. Improve the durability and reliability of equipment.

[0007]

[Means for Solving the Problems]

[First Characteristic Configuration] The present invention has, as a device configuration, a rotary transmission system provided with a plurality of cranks, a drive means for applying rotational power to the rotary transmission system, and a plurality of pistons respectively connected to the plurality of cranks. A plurality of cylinder chambers that individually discharge and inject working gas by operation, a gas communication passage that communicates these cylinder chambers in the order of their respective handling temperatures, and a cylinder chamber between which the communication order is adjacent in this gas communication passage. A variable phase device in a power input type Stirling cycle device provided with a mounted regenerative heat exchanger and a heat input / output device for separately inputting / extracting heat to / from each of the cylinder chambers. 1) is a phase difference relationship for maintaining the phase difference relationship between the plurality of pistons by rotating the plurality of cranks in the respective specified rotation directions at the same angular velocity. A holding operation and a phase difference relationship changing operation for changing a phase difference relationship between the plurality of pistons by relatively rotating some cranks of the plurality of cranks and other cranks by different rotation angles at different angular velocities. There is a transmission system operation means for performing.

[Second Characteristic Configuration] A second characteristic structure of the present invention (an invention according to claim 2) is to specify a specific structure suitable for carrying out the first characteristic structure, and is the power input type. Regarding the configuration of the Stirling cycle device, an engine is provided as the driving means, a high temperature cylinder chamber, an intermediate temperature cylinder chamber and a low temperature cylinder chamber are provided as the cylinder chambers, and the engine is provided in the high temperature cylinder chamber as the heat input / output device. A high temperature heater for giving exhaust heat of, a medium temperature radiator for radiating heat from the medium temperature cylinder chamber, and a low temperature heat absorber for absorbing heat in the low temperature cylinder chamber are provided. The transmission system operation means is configured to couple the crank for the piston of the high temperature cylinder chamber and the piston of another cylinder chamber to each other in the phase difference relation changing operation. In that a configuration in which only the relative rotation required of the rotating angle at different angular velocities to the crank that.

[Third Characteristic Configuration] A third characteristic configuration of the present invention (an invention according to claim 3) is for specifying a specific configuration suitable for carrying out the first or second characteristic configuration. The transmission system operating means has a first gear that rotates together with one crank and a second gear that serves as a transmission structure between the cranks between the cranks that are to be relatively rotated at different angular velocities in the phase difference relation changing operation. Around the second gear, a second gear that rotates with the side crank, a first planetary gear that meshes with the first gear in a fixed position, a second planetary gear that meshes with the second gear, and a second gear. Despite the position change of the second planetary gear of
A gear position in which an intermediate gear that meshes with both the planetary gear and the second planetary gear is provided, and an operation of fixing and changing the position of the second planetary gear around the second gear is performed. It is configured as a planetary gear type differential structure provided with operating means.

[Fourth Characteristic Configuration] A fourth characteristic configuration of the present invention (an invention according to claim 4) is for specifying a specific configuration suitable for carrying out the above-mentioned third characteristic configuration. The means includes a clutch mechanism between the one-side crank and the other-side crank, which is in a transmission state when the position of the second planetary gear is fixed and is in a transmission interruption state when the position of the second planetary gear is changed. The planetary gear type differential structure is configured to be additionally equipped in parallel with the constituent gears.

[Fifth Characteristic Configuration] A fifth characteristic configuration of the present invention (an invention according to claim 5) is for specifying a specific configuration suitable for carrying out the first or second characteristic configuration, and The system operation means includes a first bevel gear that rotates together with one crank and another side as a transmission structure between the cranks that are to be relatively rotated at different angular velocities in the phase difference relation changing operation. A second bevel gear that rotates with the crank of, and an intermediate bevel gear that meshes with both the first bevel gear and the second bevel gear regardless of position changes around the first bevel gear and the second bevel gear,
In addition, the bevel gear type differential structure is provided with gear position operating means for performing an operation of fixing and changing the position of the intermediate bevel gear around the first bevel gear and the second bevel gear. is there.

[0012]

[Action]

[Operation of First Characteristic Configuration] In the first characteristic configuration (see FIG. 1), a plurality of cranks 14 a, 14 b, 14 c and the plurality of cranks are connected with the rotation power applied from the driving means 1 to the rotary transmission system 13. A plurality of pistons 9a, 9b,
9c is operated to cause the plurality of cylinder chambers 8a, 8b, 8c communicating with each other through the gas communication passage 10 to perform a working gas discharge / suction operation.
Compression and expansion of the working gas G over 8b and 8c, and
The movement of the working gas between the cylinder chambers is controlled by each regeneration heat exchanger 11
m, 11n and each of the heat input / output devices 12a, 12b, 12c, whereby a reverse Stirling cycle is performed between a plurality of cylinder chambers, or a Stirling cycle is performed in parallel with the reverse Stirling cycle. Make the power input type Stirling cycle device function.

And, in carrying out this cycle,
Holding the phase difference relationship between the plurality of pistons 9a, 9b, 9c by rotating the plurality of cranks 14a, 14b, 14c in the respective specified rotation directions at the same angular velocity by a phase difference holding operation by the transmission system operation means 15. As a result, along with the operation of the plurality of pistons 9a, 9b, 9c, the plurality of cylinder chambers 8a, 8b, 8c are caused to discharge and suck working gas in a constant discharge / suction operation relationship, whereby power input is performed with the cycle characteristics kept constant. Type Stirling cycle equipment to function with certain equipment characteristics.

If it is necessary to change the device characteristics,
By the phase difference relation changing operation by the transmission system operating means 15, some cranks 14c of the plurality of cranks 14a, 14b, 14c and other cranks 14a, 14b are relatively rotated by a required rotation angle at different angular velocities (one side). The relative rotation operation in a state where the crank on the side is stopped) to change the phase difference relationship between the plurality of pistons 9a, 9b, 9c, and then the above-mentioned phase difference relationship by the transmission system operating means 15 is changed. By holding operation, multiple pistons 9a, 9b,
By operating the plurality of pistons 9a, 9b, 9c in a state in which the phase difference relationship of 9c is maintained in the new relationship after the change, the plurality of cylinder chambers 8a, 8b, 8c correspond to the changed phase relationship of the pistons. With the new discharge suction operation relationship, the working gas is discharged and sucked in, and the power input type Stirling cycle device has different device characteristics from before the operation of changing the piston phase difference relationship while changing the cycle characteristics of the implementation cycle. To function.

[Operation of Second Characteristic Configuration] In the second characteristic configuration, as the power input type Stirling cycle device, an engine-driven refrigerator or an engine-driven heat pump of a mode in which a reverse Stirling cycle and a Stirling cycle are performed in parallel. To form.

That is, (see FIG. 1), the high temperature cylinder chamber 8
c piston 9c and medium temperature cylinder chamber 8b piston 9b
And the piston 9a of the low temperature cylinder chamber 8a are operated while maintaining a predetermined phase difference relationship, under the action of the high temperature heater 12c, the intermediate temperature radiator 12b, the low temperature heat absorber 12a, and the regenerative heat exchangers 11m and 11n. In the above, three cylinder chambers 8a, 8b, 8c for individually performing working gas discharge and suction under the communication by the gas communication passage 10 by applying rotational power from the engine 1 as the drive means to the rotary transmission system 13
Among them, with respect to the pair of the intermediate temperature cylinder chamber 8b and the low temperature cylinder chamber 8a, the low temperature cylinder chamber 8a is caused to absorb heat by the rotational power from the rotary transmission system 13 and the intermediate temperature cylinder chamber 8b is caused to radiate heat to pump up heat. It functions as a refrigerator or heat pump for the reverse Stirling cycle.

In parallel with this, the high temperature cylinder chamber 8
Regarding the pair of c and the medium temperature cylinder chamber 8b, the engine exhaust heat (for example, the retained heat of the engine exhaust gas or the retained heat of the engine cooling water after the cooling action) is applied from the high temperature heater 12c to the high temperature cylinder chamber 8c. The heat input of this form causes the engine to function as a Stirling cycle engine that generates rotational power while radiating heat in the intermediate temperature cylinder chamber 8b. The generated power is transmitted from the engine 1 to the rotary transmission system 13
It is applied to the rotary transmission system 13 in the form of adding power to the rotation transmission system 13.

That is, when the pair of the medium temperature cylinder chamber 8b and the low temperature cylinder chamber 8a is made to function as a refrigerator or a heat pump by the rotation power, the rotation power is enhanced by the above-mentioned power generation utilizing engine exhaust heat, Increases the functional capacity or heat pump capacity, or reduces the required input of engine power, which
Secure a high coefficient of performance for the entire device.

On the other hand, in order to function as an engine-driven refrigerator or heat pump as described above, the phase difference relationship between the pistons 9c, 9b, 9a is kept constant by the phase difference relationship holding operation by the transmission system operating means 15. Then, the reverse Stirling cycle and the Stirling cycle having a constant cycle characteristic are performed to keep the device characteristic constant. However, when the device characteristic needs to be changed, the high temperature is changed by the phase difference relation changing operation by the transmission system operating means 15. Crank 14c for cylinder chamber 8c and other cylinder chambers 8
The cranks 14a and 14b with respect to a and 8b are relatively rotated at different angular velocities by a required rotation angle,
High temperature cylinder chamber 8c piston 9c and other cylinder chamber 8
The phase difference relationship between the a and 8b and the pistons 9a and 9b is changed.

After the operation of changing the phase difference relationship of the pistons, the operation of maintaining the phase difference relationship by the transmission system operating means 15 causes the piston 9c of the high temperature cylinder chamber 8c and the pistons 9a and 9b of the other cylinder chambers 8a and 8b to be operated. By operating these pistons 9a, 9b, and 9c in a state where the phase difference relationship is maintained in the new relationship after the change, the high-temperature cylinder chamber 8c and the other cylinder chambers 8a and 8b are changed in the piston phase difference relationship. Corresponding to the new discharge suction operation relationship, the working gas is discharged and sucked, and the reverse Stirling cycle and the Stirling cycle with changed cycle characteristics are performed, and the engine-driven refrigerator or heat pump described above is used for the piston phase difference. Equipment characteristics that are different from those before the change operation, such as required input amount of engine power and engine exhaust heat Heat (i.e. the required heating quantity of the hot heater 12c), the heat radiation amount of the medium-temperature heat radiator 12b, and the characteristics and changing the ratio of the heat absorption amount of the low-temperature heat sink 12a,
Alternatively, the temperature required for exhaust heat from the engine, the intermediate temperature radiator 12b
The heat radiation temperature and the heat absorption temperature of the low temperature heat absorber 12a are changed in the ratio.

[Operation of Third Characteristic Configuration] In the third characteristic configuration (see FIGS. 2 to 4), the position of the second planetary gear 17a is fixed around the second gear 17 by the gear position operating means 20. , The first gear 16, the first planetary gear 16a, the intermediate gear 18, the second planetary gear 17a, and the second gear 17 are rotationally transmitted in a non-differential state, and the cranks 14a, 14b on one side and the cranks on the other side are transmitted. Crank 14c
And can be interlocked and rotated in the same direction at a constant angular velocity ratio. Therefore, if the gear ratio relationship of these gears is appropriately selected, the position of the second planetary gear 17a is fixed by the gear position operation means 20. By doing so, the cranks 14a, 14b on the one side and the crank 14c on the other side are interlockedly rotated in the same direction at mutually equal angular velocities, and the pistons 9a, 9b connected to the cranks 14a, 14b on the one side are rotated.
It is possible to operate the piston 9c connected to the crank 14c on the other side and the phase difference relation thereof.

Further, in the configuration in which the gear ratio relationship is selected such that the cranks 14a, 14b on one side and the crank 14c on the other side are interlockedly rotated at the same angular velocity by fixing the position of the second planetary gear 17a in this way, The position of the second planetary gear 17a is set to the second position by the gear position operation means 20.
By changing around the gear 17, in the changing process, the first gear 16, the first planetary gear 16a, the intermediate gear 1
8, the second planetary gear 17a, by causing a differential in rotational transmission over the second gear 17, only the rotation angle corresponding to the position change angle of the second planetary gear 17a around the second gear 17,
One crank 14a, 14b and the other crank 1
4c can be rotated relative to each other at different angular velocities.

After this position changing operation, the position of the second planetary gear 17a is fixed to the changed position by the gear position operating means 20, and the crank 1 on one side is fixed by this position fixing.
4a, 14b and the crank 14c on the other side are interlocked with each other at the same angular velocity to change the pistons 9a, 9b connected to the cranks 14a, 14b on the one side and the piston 9c connected to the crank 14c on the other side. It is possible to operate in a state in which the new phase difference relationship is maintained.

In other words, the third characteristic structure is for carrying out the phase difference relationship holding operation and the phase difference relationship changing operation by the structure using the planetary gear type differential structure, and the second operation by the gear position operating means 20 is performed. Fixing the position of the planet gear 17a is the holding operation of the phase difference relation, and changing the position of the second planet gear 17a by the gear position operating means 15 is the changing operation of the phase difference relation.

[Operation of Fourth Characteristic Configuration] In the fourth characteristic configuration (see FIG. 2), in the third characteristic configuration, when the position of the second planetary gear 17a is fixed, that is, the one-side crank 1
When the 4a, 14b and the crank 14c on the other side are interlockedly rotated in the same direction at the same angular velocity, the clutch mechanism 21 arranged in parallel with the constituent gears of the planetary gear type differential structure is set to the transmission state. Clutch mechanism 2
By performing transmission between the cranks via the first gear 16 and the first planetary gear 16 on the transmission between the cranks.
a, intermediate gear 18, second planetary gear 17a, second gear 17
(That is, the rotational torque that acts on the constituent gears of the planetary gear type differential structure) is reduced.

When the position of the second planetary gear 17a is changed,
That is, when the one-side cranks 14a and 14b and the other-side crank 14c are relatively rotated at different angular velocities, the clutch mechanism 21 is set to the transmission disengaged state so that the one-side cranks 14a and 14b and the other-side crank 14c. Allows relative rotational motions at different angular velocities from and.

[Operation of Fifth Characteristic Configuration] In the fifth characteristic configuration (see FIG. 5), the position of the intermediate bevel gear 24 is fixed around the first and second bevel gears 22 and 23 by the gear position operating means 25. , The first bevel gear 22, the intermediate bevel gear 24, and the second bevel gear 23 are rotationally transmitted in a non-differential state, so that the cranks 14a and 14b on one side and the crank 14c on the other side are opposite to each other at a constant angular velocity ratio. Therefore, if the gear ratio relationship of these bevel gears is appropriately selected, the position of the intermediate bevel gear 24 is fixed by the gear position operating means 25, so that the crank 14 on one side can be rotated.
a, 14b and the crank 14c on the other side are interlocked with each other at the same angular velocity in opposite directions to rotate the pistons 9a, 9b connected to the cranks 14a, 14b on one side and the piston 9c connected to the crank 14c on the other side. Can be operated while maintaining their phase difference relationship.

In addition, in the structure in which the gear ratio relationship is selected so that the cranks 14a, 14b on one side and the crank 14c on the other side are interlockedly rotated at the same angular velocity by fixing the position of the intermediate bevel gear 24 in this way, The position of the intermediate bevel gear 24 is set to the first position by the operating means 25.
By changing around the first and second bevel gears 22 and 23, in the changing process, a differential is generated in the rotation transmission across the first bevel gear 22, the intermediate bevel gear 24, and the second bevel gear 23, so that the first and second bevel gears are changed. The cranks 14a and 14b on the one side and the crank 14c on the other side can be relatively rotated at different angular velocities by a rotation angle corresponding to the position change angle of the intermediate bevel gear 24 around 22 and 23.

After this position changing operation, the position of the intermediate bevel gear 24 is fixed to the changing position by the gear position operating means 25, and the crank 1 on one side is fixed by this position fixing.
4a, 14b and the crank 14c on the other side are interlockedly rotated in the opposite directions at the same angular velocity,
Piston 9 connected to one side cranks 14a, 14b
a, 9b and the piston 9 connected to the crank 14c on the other side
It is possible to operate in a state where c and c are held in the new phase difference relationship after the change.

That is, the fifth characteristic structure is to perform the phase difference relation holding operation and the phase difference relation changing operation by the structure utilizing the bevel gear type differential structure, and the intermediate bevel gear 24 by the gear position operating means 25. The above-mentioned phase difference relation holding operation is performed by fixing the position, and the phase difference relation changing operation is performed by changing the position of the intermediate bevel gear 24 by the gear position operating means 25.

[0031]

【The invention's effect】

[Effects of First Characteristic Configuration] According to the first characteristic configuration of the present invention, the change / change of the power input condition from the driving means and the thermal input / output condition of the heat quantity or temperature in each of the plurality of cylinder chambers can be changed. In response to changes and changes, the device characteristics can be easily changed to characteristics that meet new input / output conditions by changing the piston phase difference relationship by the transmission system operation means and holding operation after the change. It is possible to enhance the functionality and versatility of the Stirling cycle device, and prevent the coefficient of performance from decreasing due to nonconformity of characteristics, and maintain a high coefficient of performance regardless of changes or changes in input / output conditions.

Incidentally, in order to change the phase difference relationship of the plurality of pistons and the discharge suction operation relationship of the plurality of cylinder chambers without disassembling the rotary transmission system, as an alternative method, the plurality of cylinder chambers may be arranged with the rotation axis core. It is also possible to change the phase difference relationship between a plurality of pistons by individually changing the attitude around the circumference, and by changing the reciprocating operation direction of the corresponding pistons by changing the attitude of each cylinder chamber. .

However, in this alternative form, it is necessary to adopt a special structure for allowing the attitude of the cylinder chamber to be changed for each of the gas communication passage, each heat input / output device, and each regenerative heat exchanger, which are incidental structures. Although the device structure is complicated from this, according to the first characteristic configuration of the present invention, the phase difference relationship between the plurality of pistons is changed by relatively rotating the plurality of cranks at the required rotation angles at different angular velocities. Therefore, it is not necessary to adopt the special structure as described above for each of the gas communication passage, each heat input / output heat exchanger, and each regenerative heat exchanger, and in this respect, the device structure can be simplified as compared with the above-mentioned other type. The manufacturing cost can be reduced and the manufacturing cost can be reduced.

[Effect of Second Characteristic Configuration] According to the second characteristic configuration of the present invention, it is possible to obtain an engine-driven refrigerator or heat pump that effectively utilizes engine exhaust heat and has a high coefficient of performance.

Further, in response to changes / changes in the heat load conditions of the refrigerator or heat pump, or changes / changes in the engine-side operating conditions such as engine power and engine exhaust heat, a high temperature cylinder by the transmission system operation means is provided. By the changing operation of the piston phase difference relationship between the piston of the chamber and the piston of the other cylinder chamber and the holding operation after the change, the required input amount of engine power, the required heat input amount of engine exhaust heat, the heat radiation amount of the medium temperature radiator, And, by changing the ratio of the heat absorption amount of the low temperature heat absorber, or by changing the ratio of the required temperature of engine exhaust heat, the heat radiation temperature of the medium temperature radiator, and the heat absorption temperature of the low temperature heat absorber, The characteristics of the refrigerator or heat pump can be easily changed to meet the new heat load conditions and engine side operating conditions. Together with it is possible to increase the combined functionality and versatility as a heat pump, more effectively achieve improvement in the coefficient of performance by preventing deterioration of the coefficient of performance by characteristics incompatible.

Incidentally, as an example of changing the engine-side operating condition, when the engine output is changed, the ratio between the engine power and the engine exhaust heat (for example, the heat retained by the engine exhaust gas) changes accordingly. Then, this ratio largely deviates from the ratio between the required input amount of engine power and the required heat input amount of engine exhaust heat as a device characteristic value.
Although the effective utilization rate of engine exhaust heat may decrease and the coefficient of performance may also decrease, in such a case, the necessary input of engine power as a device characteristic value is changed by changing the piston phase difference relationship as described above. By changing the ratio between the amount of heat and the required heat input of engine exhaust heat to match the ratio of actual engine power and engine exhaust heat, the effective utilization ratio of engine exhaust heat is maintained high and the coefficient of performance The decline can be suppressed.

[Effect of Third Characteristic Configuration] According to the third characteristic configuration of the present invention, in the phase difference relation changing operation, the cranks that are to be relatively rotated at different angular velocities have the planetary gear type differential structure. While using the differential function,
By the position changing operation of the second planetary gear, the relative rotation operation can be accurately and easily performed only by the rotation angle corresponding to the position changing angle of the second planetary gear. Therefore, the piston phase difference relationship can be changed to the desired relationship. It can be changed accurately and easily.

[Effect of Fourth Characteristic Configuration] According to the fourth characteristic configuration of the present invention, since the rotational torque acting on the constituent gears of the planetary gear type differential structure can be reduced, the early stage of the planetary gear type differential structure can be reduced. Gear wear and damage can be prevented to improve the durability and reliability of the device, and the required strength of the planetary gear type differential structure can be reduced, so that the device cost can be reduced.

[Effect of Fifth Characteristic Configuration] According to the fifth characteristic configuration of the present invention, in the phase difference relation changing operation, the cranks that are to be relatively rotated at different angular velocities are different from each other in the difference of the bevel gear type differential structure. By using the dynamic function, by performing the position change operation of the intermediate bevel gear, the relative rotation operation can be accurately and easily performed by the rotation angle corresponding to the position change angle of the intermediate bevel gear. The desired relationship can be changed accurately and easily.

[0040]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 shows an engine-driven refrigerator or heat pump as an example of a power input type Stirling cycle device, 1 is an engine as a driving means, and 2 is a heat equipment part driven by an engine 1. , Engine 1
In FIG. 3, 3 is an engine output shaft, 4 is a fuel passage, 5 is an intake passage, 6 is an exhaust passage for the engine exhaust gas E, and 7 is a circulation passage for the engine cooling water W.

On the other hand, in the heat equipment section 2, 8a is a low temperature cylinder chamber, 8b is a medium temperature cylinder chamber, and 8c is a high temperature cylinder chamber. These cylinder chambers 8a, 8b, 8c are respectively equipped with pistons 9a, 9b, The working gas G (for example, helium gas or hydrogen gas) is periodically discharged and sucked by the reciprocating motion of 9c.

Reference numeral 10 denotes a gas communication passage that connects the cylinder chambers 8a, 8b, 8c to each other in the order of handling temperatures. In this gas communication passage 10, one of the cylinder chambers adjacent to each other in communication order has a heat storage function. A regenerative heat exchanger 11m that thermally separates the cylinder chamber side from the other cylinder chamber side,
11n is interposed.

Further, 12a is a low-temperature heat absorber for absorbing heat in the low-temperature cylinder chamber 8a with respect to the cold heat medium C circulated with the cold heat demand device X, and 12b is a warm heat medium H circulated with the heat heat demand device Y. On the other hand, a medium temperature radiator for radiating the medium temperature cylinder chamber 8b, and a high temperature heater 12c for imparting the retained heat of the engine exhaust gas E guided by the exhaust passage 6 to the high temperature cylinder chamber 8c.

It is to be noted that, in addition to applying the heat release heat of the intermediate temperature cylinder chamber 8b to the heat requesting device Y via the heat transfer medium H, the engine cooling water W after the cooling action introduced through the cooling water circulation path 7 is provided. Apply the retained heat.

Reference numeral 13 denotes a rotary shaft connected to the engine output shaft 3 as a rotary transmission system for interlocking the pistons 9a, 9b, 9c.
The first crank 14a connecting the piston 9a of the low temperature cylinder chamber 8a and the second crank 14b connecting the piston 9b of the intermediate temperature cylinder chamber 8b in order from the connection side with the engine output shaft 3 in accordance with the arrangement of a, 8b, 8c. , The third crank 14c connecting the piston 9c of the high temperature cylinder chamber 8c
Is provided.

The respective cylinder chambers 8a, 8b, 8c are arranged such that their mutual posture relations around the rotation axis (in other words, the mutual angular relations of the piston reciprocating motion directions around the rotation axis) are fixed to a predetermined relation. And the low temperature cylinder chamber 8a
The first crank 14a and the second crank 14b with respect to the intermediate temperature cylinder chamber 8b are formed on the rotary shaft 13 while fixing the mutual rotational phase difference at a predetermined angle, and the attitude relationship of these cylinder chambers is set, and By setting the rotational phase difference between the first crank 14a and the second crank 14b, the piston 9b of the intermediate temperature cylinder chamber 8b always reciprocates with a constant phase delay with respect to the piston 9a of the low temperature cylinder chamber 8a. In other words, the medium temperature cylinder chamber 8b is configured to discharge and inhale the working gas G with a constant phase delay (for example, a phase delay of about 1/4 cycle) with respect to the low temperature cylinder chamber 8a.

On the other hand, the rotating shaft 13 is divided into an engine connecting side rotating shaft portion 13m provided with the first crank 14a and the second crank 14b and an end side rotating shaft portion 13n provided with the third crank 14c. The transmission system operating means 15 as described below is interposed in this dividing portion, thereby forming a variable phase device capable of changing the piston phase difference relationship.

The transmission system operating means 15 changes the phase difference relationship between the piston 9c of the high temperature cylinder chamber 8c and the pistons 9a and 9b of the other cylinder chambers 8a and 8b to change the high temperature cylinder chamber 8c and the other cylinder chambers. The discharge suction operation relationship with 8a and 8b is changed. As a specific function, the third crank 14c with respect to the high temperature cylinder chamber 8c and the crank with respect to the other cylinder chambers 8a and 8b (that is, the rotational phase difference between Fixed first and second cranks 14a,
14b) are interlocked with each other in the same direction at the same angular velocity to hold the phase difference relationship holding operation for maintaining the phase difference relationship between the piston 9c of the high temperature cylinder chamber 8c and the pistons 9a, 9b with respect to the other cylinder chambers 8a, 8b. , High temperature cylinder chamber 8
3rd crank 14c for c and other cylinder chamber 8a,
The cranks 14a and 14b with respect to 8b are relatively rotated at different angular velocities by a required rotation angle, so that the piston 9c of the high temperature cylinder chamber 8c and the other cylinder chambers 8a and 8b.
A phase difference relation changing operation for changing the phase difference relation between the pistons 9a and 9b with respect to b is performed.

That is, the piston 9c of the high temperature cylinder chamber 8c and the other cylinder chamber 8 are retained by the above-mentioned phase difference maintaining operation.
By maintaining the phase difference relationship between the pistons 9a, 9b with respect to a, 8b, the high temperature cylinder chamber 8c and the other cylinder chambers 8a, 8c
8b and the working gas are sucked and sucked in a constant discharge and suction operation relationship, whereby operation is performed with the device characteristics kept constant.

When it is necessary to change the device characteristics,
By the phase difference relation changing operation, the phase difference relation between the piston 9c of the high temperature cylinder chamber 8c and the pistons 9a, 9b with respect to the other cylinder chambers 8a, 8b is changed, and then the phase difference relation maintaining operation is performed to increase the high temperature. By operating these pistons 9a, 9b, 9c in a state where the phase difference relationship between the piston 9c of the cylinder chamber 8c and the pistons 9a, 9b with respect to the other cylinder chambers 8a, 8b is maintained in the new relationship after the change, The high temperature cylinder chamber 8c and the other cylinder chambers 8a and 8b are kept in a new discharge / intake operation relationship corresponding to the changed piston phase difference relationship to allow the working gas to be sucked and sucked, thereby making it possible to perform machine operation in which the device characteristics are changed. To do.

Regarding the concrete structure of the transmission system operating means 15, as shown in FIGS. 2 to 4, the transmission structure between the rotating shaft portion 13m on the engine connecting side and the rotating shaft portion 13n on the end side is the engine. Rotate integrally with the rotating shaft portion 13m on the connecting side (that is, the first and second cranks 14a, 14b).
A first gear 16 that rotates integrally with the second gear 17 that rotates integrally with the end-side rotation shaft portion 13n (that is, a single rotation with the third crank 14c), and the first gear 16 in a position-fixed state. A plurality of first planetary gears 16a that mesh with
A plurality of second planetary gears 17a that mesh with the second gear 17
And an internal gear type intermediate gear 18 that meshes with both the first planetary gear 16a and the second planetary gear 17a regardless of the position change of the second planetary gear 17a around the second gear 17, and As a gear position operating means for the second planetary gear 17a, a worm gear having a function of rotating the movable carrier 19 supporting the second planetary gear 17a around the rotation axis and fixing the movable carrier 19 in the rotational operation position. A planetary gear type differential structure provided with a manual operation mechanism 20 is adopted.

The first gear 16 and the first planetary gear 16a
And a gear ratio between the second planetary gear 17a and the second planetary gear 17a, and a gear ratio between the first planetary gear 16a and the intermediate gear 18 is equal to that of the second planetary gear 17a and the intermediate gear 1.
8 and the gear ratio.

Also, the rotary shaft portion 13m on the engine connecting side
In addition to the planetary gear type differential structure described above, the second planetary gear 17a is in a transmission state when the position of the second planetary gear 17a is fixed, and
Clutch mechanism 21 that is in a transmission cutoff state when the position of a is changed
The planetary gear type differential structure gears 16, 16a, 18,
17a and 17 are provided in a parallel relationship.

That is, in the above structure, the fixing function of the worm gear type operating mechanism 20 causes the second planetary gear 17 to move.
The position of a is fixed around the second gear 17, so that the rotation transmission in the form of no differential is transmitted to the first gear 16, the first planetary gear 16a, the intermediate gear 18, the second planetary gear 17a, and the second planetary gear 17a.
The third crank 14c and other cylinder chambers with respect to the high temperature cylinder chamber 8c are made to operate over the gear 17, and at the same time, the clutch mechanism 21 is set to the transmission state so that rotation transmission is also performed via the clutch mechanism 21. The cranks 14a and 14b with respect to 8a and 8b are interlockedly rotated at the same angular velocity in the same direction, and with this, the phase difference relationship between the piston 9c of the high temperature cylinder chamber 8c and the pistons 9a and 9b of the other cylinder chambers 8a and 8b. The phase difference relation holding operation for holding

Further, with the clutch mechanism 21 in the transmission disengaged state and the rotation transmission via the clutch mechanism 21 disengaged, the second planetary gear 1 is operated by the worm gear type operation mechanism 20.
The position of 7a is changed around the second gear 17, and with this position change, the first gear 16, the first planetary gear 16a,
By causing a differential in rotational transmission over the intermediate gear 18, the second planetary gear 17a, and the second gear 17, only a rotation angle corresponding to a position change angle of the second planetary gear 17a around the second gear 17, Third for high temperature cylinder chamber 8c
The crank 14c and the cranks 14a and 14b with respect to the other cylinder chambers 8a and 8b are rotated relative to each other at different angular velocities, whereby the piston 9c of the high temperature cylinder chamber 8c and the pistons 9a of the other cylinder chambers 8a and 8b,
The phase difference relation changing operation is performed to change the phase difference relation with 9b.

Next, regarding equipment operation, the piston 9c in the high temperature cylinder chamber 8c and the piston 9 in the medium temperature cylinder chamber 8b
b and the piston 9a of the low temperature cylinder chamber 8a are operated by holding the phase difference relationship holding operation in the predetermined phase difference relationship and operating the high temperature heater 12c, the intermediate temperature radiator 12b, the low temperature heat absorber 12a, and Regeneration heat exchanger 11m, 11
By applying rotational power from the engine 1 to the rotary shaft 13 under the action of n, the three cylinder chambers 8 for individually performing working gas discharge and suction under the communication by the gas communication passages 10 are provided.
Among the a, 8b, and 8c, for the pair of the medium temperature cylinder chamber 8b and the low temperature cylinder chamber 8a, the rotation power of the rotary shaft 13 causes the low temperature cylinder chamber 8a to absorb heat and the medium temperature cylinder chamber 8b to dissipate heat. It functions as a refrigerator or heat pump of the reverse Stirling cycle for pumping.

In parallel with this, the high temperature cylinder chamber 8
For the pair of c and the medium temperature cylinder chamber 8b, a Stirling cycle engine that generates rotational power while heat is dissipated in the medium temperature cylinder chamber 8b by inputting engine exhaust gas holding heat from the high temperature heater 12c to the high temperature cylinder chamber 8c The generated power is applied to the rotary shaft 13 in the form of being added to the power applied from the engine 1 to the rotary shaft 13.

That is, each cylinder chamber 8a, 8b, 8c
The cylinder chambers 8a, 8b,
In producing compression and expansion of the working gas G over 8c and movement of the working gas between the cylinder chambers, the working gas G compressed between the high temperature cylinder chamber 8c and the intermediate temperature cylinder chamber 8b is basically the same. Is introduced into the high-temperature cylinder chamber 8c by being heated by the stored heat of the regenerative heat exchanger 11n through the regenerative heat exchanger 11n on the high-temperature cylinder chamber side, and thereafter, the working gas G undergoes an expansion process to undergo high-temperature heater 12c. Then, the working gas G is again passed through the regenerative heat exchanger 11n on the high temperature cylinder chamber side, and the heat of heat is stored in the regenerative heat exchanger 11n and the temperature of the working gas G is lowered, and the working gas G is heated from the high temperature cylinder chamber 8c to the medium temperature cylinder chamber. The working gas G, which is led to 8b and whose temperature has dropped, undergoes a compression process and is discharged at an intermediate temperature lower than the temperature level of the high temperature cylinder chamber 8c. Radiating to vessel 12b (i.e., the heat medium H warming) is, to execute the Stirling cycle such, thereby to generate power.

Regarding the pair of the medium temperature cylinder chamber 8b and the low temperature cylinder chamber 8a, basically, the compressed working gas G passes through the regenerative heat exchanger 11m on the low temperature cylinder chamber side, and the heat of the regenerative heat exchanger 11m is accumulated. After being cooled by cold heat, it is introduced into the low temperature cylinder chamber 8a, and thereafter the working gas G
Absorbs heat (that is, cools the cold heat transfer medium C) to the low temperature heat absorber 12a through the expansion process, and then the working gas G passes through the regenerative heat exchanger 11m on the low temperature cylinder chamber side again to regenerate the heat exchanger 11m. The cold working temperature G is discharged from the low temperature cylinder chamber 8a to the middle temperature cylinder chamber 8b with the accumulation of cold heat to the middle temperature cylinder chamber 8b, and the working gas G whose temperature has increased is higher than the temperature level of the low temperature cylinder chamber 8a through the compression process. A reverse Stirling cycle is performed such that heat is dissipated (that is, the heating medium H is heated) to the middle-temperature radiator 12b at a level, thereby obtaining a refrigerator function or heat pump function for pumping heat.

In the above operation, there is a change / change in the heat load condition as a refrigerator or a heat pump, or a change / change in the engine side operation condition with respect to the engine power or the engine exhaust heat amount, which requires a change in the device characteristics. In this case, as described above, the clutch mechanism 21 is set to the transmission cutoff state as the phase difference relation changing operation, and then the position of the second planetary gear 17a is changed by the worm gear type operation mechanism 20 to change the piston of the high temperature cylinder chamber 8c. 9c and the pistons 9a and 9b of the other cylinder chambers 8a and 8b are changed, and then the second planetary gear 17a is changed by the fixing function of the worm gear type operation mechanism 20 as a phase difference holding operation. Fixed to the clutch mechanism 2
By setting 1 for transmission, the high temperature cylinder chamber 8
The piston 9c of c and the pistons 9a and 9b of the other cylinder chambers 8a and 8b are operated while maintaining the new phase difference relationship after the change, and the high temperature cylinder chamber 8c and the other cylinder chambers 8a and 8b are operated. The working gas is discharged and sucked in a new discharge suction operation relationship that corresponds to the changed piston phase difference relationship, thereby changing the equipment characteristics to meet the new heat load conditions and new engine side operating conditions. Operation, for example, required input amount of engine power, required input amount of engine exhaust heat (that is, required heating amount of high temperature heater 12c), heat radiation amount of medium temperature radiator 12b, and low temperature heat absorber 1
Operation in which the ratio of the heat absorption amount of 2a is changed to a new heat load condition or a new engine side operation condition,
Alternatively, the required temperature of the engine exhaust gas, the intermediate temperature radiator 12
An operation is performed in which the ratio of the heat radiation temperature of b and the heat absorption temperature of the low temperature heat absorber 12a is changed to one that meets new heat load conditions and new engine side operating conditions.

[Other Embodiments] Next, other embodiments will be listed.

In the above-described embodiment, the clutch mechanism 21 is omitted, and when the piston phase difference relationship is maintained, the constituent gears 16, 16a, 1 of the planetary gear type differential structure are provided.
The rotation transmission between the cranks may be performed only by 8, 17a and 17.

When the clutch mechanism 21 is additionally provided in parallel with the constituent gears of the planetary gear type differential structure as in the above-described embodiment, the operation for switching the clutch mechanism 21 between the transmission operation state and the transmission cutoff state. Is a mode in which the clutch mechanism 21 is switched in synchronism with the position changing operation and the fixing operation of the second planetary gear 17a by the gear position operating means 20, or the clutch mechanism is independently operated by a dedicated operating means other than the gear position operating means 20. Any of the modes for switching and operating 21 may be adopted.

Further, the clutch mechanism 21 employs a centrifugal clutch that automatically switches to a transmission operation state with rotation and automatically switches to a transmission interruption state with rotation stop. The phase difference relationship changing operation by the position changing operation of the second planetary gear 17a may be performed when the rotation is stopped.

Instead of constructing the transmission system operating means 15 using the planetary gear type differential structure as in the above-described embodiment, as shown in FIG. 5, the transmission system operating means 15 is formed using a bevel gear type differential structure. You may comprise.

That is, in the phase difference relation changing operation, the crank to be relatively rotated at different angular velocities (in the above embodiment, the crank 14c for the high temperature cylinder chamber 8c and the crank 1 for the other cylinder chambers 8a, 8b).
4a, 14b) as a transmission structure between the cranks, the first bevel gear 22 rotating together with the cranks 14a, 14b on one side and the crank 14 on the other side.
A second bevel gear 23 that rotates together with c, and an intermediate bevel gear 24 that meshes with both the first bevel gear 22 and the second bevel gear 23 regardless of position changes around the first and second bevel gears 22 and 23, And the first
Also, a bevel gear type differential structure is provided which is provided with a gear position operating means 25 for performing an operation of fixing the position of the intermediate bevel gear 24 around the second bevel gears 22 and 23 and an operation of changing the position.

In this bevel gear type differential structure,
The position of the intermediate bevel gear 24 is fixed around the first and second bevel gears 22 and 23 by the gear position operation means 25, so that the rotation transmission in the form of no differential is transmitted to the first bevel gear 2.
2, the intermediate bevel gear 24, and the second bevel gear 23, so that the one side cranks 14a, 14b
And the crank 14c on the other side are interlocked with each other at the same angular velocity in opposite directions, and with this, the pistons 9a, 9b connected to the cranks 14a, 14b on the one side and the piston 9c connected to the crank 14c on the other side are rotated. The above-mentioned phase difference relationship holding operation for holding the phase difference relationship is performed.

Further, the position of the intermediate bevel gear 24 is changed by the gear position operation means 25 to the first and second bevel gears 22, 2.
The change operation is performed around 3, and with this position change, the first bevel gear 22, the intermediate bevel gear 24, the second bevel gear 2
By causing a differential in rotation transmission over 3, the crankshafts 14a, 14b on one side and the crankshafts on the other side by a rotation angle corresponding to the position change angle of the intermediate bevel gear 24 around the first and second bevel gears 22, 23. Crank 14c
Are rotated relative to each other at different angular velocities to change the phase difference between the pistons 9a and 9b connected to the cranks 14a and 14b on one side and the piston 9c connected to the crank 14c on the other side. The operation is to change the phase difference relationship.

When the planetary gear type differential structure is used, the gear position operating means 20 for changing and fixing the position of the second planetary gear 17a, and the intermediate bevel gear when the bevel gear type differential structure is used. 24
Each of the gear position operating means 25 for performing the position changing operation and the position fixing operation is not limited to the worm gear type operation mechanism, and various types of operation structures can be adopted.

The transmission system operating means 15 is constituted by using a planetary gear type, a bevel gear type, or other type of differential structure. Instead of, for example, a sliding movement of a key causes a shaft portion on one side and a shaft portion on the other side. Change the connection phase in the direction of rotation with and, using a so-called slide key mechanism,
Alternatively, as described below, various configuration changes are possible, such as a configuration using a clutch mechanism and rotation operating means, a configuration using a gear shift mechanism, and the like.

That is, in the configuration example using the clutch mechanism and the rotation operating means, the clutch mechanism is interposed between the cranks which are to be relatively rotated at the angular velocities different from each other in the phase difference relation changing operation, and
The phase difference relationship holding operation is performed by interlocking the one side crank and the other side crank at the same angular velocity by setting the clutch mechanism for transmission, while the phase difference relationship changing operation is performed by the clutch mechanism. Is switched to the transmission cutoff state, and then the crank on one side and the crank on the other side are relatively rotated at different angular velocities by appropriate rotation operation means.

Further, regarding the configuration example using the gear transmission mechanism, the gear transmission mechanism is interposed between the cranks that are to be relatively rotated at different angular velocities in the phase difference relation changing operation, and the phase difference is set. As a relationship holding operation, by switching this gear transmission mechanism to a one-to-one gear shifting state, the crank on one side and the crank on the other side are interlockedly rotated in the respective prescribed rotation directions at the same angular velocity, and the phase difference As the relationship changing operation, the one speed side crank and the other speed side crank are relatively rotated at different angular velocities by switching the gear speed change mechanism to a speed change state other than 1: 1.

The drive means 1 for giving the rotary power to the rotary transmission system 13 is not limited to the engine, but may be a motor, a turbine, or other rotary power generating means.

When an engine is used as the driving means 1, various types of engines can be adopted as this engine, and a Stirling cycle engine may be adopted.

The present invention is not limited to a power input type Stirling cycle device having three cylinder chambers, but can be applied to one having two cylinder chambers and one having four or more cylinder chambers.
Further, the present invention is not limited to the type in which one piston corresponds to one cylinder chamber, but can be applied to what is called a displacer type.

In the above-mentioned embodiment, the reverse Stirling cycle and the Stirling cycle are carried out in parallel, but only the reverse Stirling cycle may be carried out by inputting the rotational power by the driving means 1.

Further, when the reverse Stirling cycle and the Stirling cycle are performed in parallel by performing heat input to a part of the cylinder chambers together with the rotational power input by the driving means 1, this heat input is equivalent to engine exhaust heat. Not limited to this, various heats such as heat generated by the burner and heat retained by high-temperature steam can be adopted.

According to the present invention, as in the above-described embodiment, the phase difference relations of some pistons are fixed during the manufacture of the equipment, and the mutual phase difference relations only between these pistons having the fixed phase difference relations and the other pistons. The transmission system operation means 15
However, the phase difference relation between each of the plurality of pistons and the other pistons may be changed by the transmission system operating means 15.

The intended use of the power input type Stirling cycle device may be any one such as cooling or heating, or heating or cooling of articles.

The device characteristics to be changed are the characteristics of the heat input / output heat ratios of a plurality of cylinder chambers, the characteristics of the ratio of the power applied by the driving means to the heat input / output heat of each cylinder chamber, and the applied power / heat input / output of the cylinder chambers. Ratio and the cylinder temperature ratio of multiple cylinder chambers, and the heat input / output characteristics of whether to heat out or heat in each cylinder chamber, as long as they can be changed by changing the piston phase difference relationship. The characteristics of various device functions can be changed.

It should be noted that reference numerals are given in 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 perspective view showing the overall configuration of a device.

FIG. 2 is a side view structural diagram of a transmission system operating means.

FIG. 3 is a structural view of the transmission system operating means as viewed in the axial direction.

FIG. 4 is a structural view of the thermal equipment section as viewed from the axial direction.

FIG. 5 is a structural diagram of a transmission system operating means showing another embodiment.

[Explanation of symbols]

13 rotation transmission system 1 drive means (engine) 14a, 14b, 14c crank 9a, 9b, 9c piston G working gas 8a cylinder chamber (low temperature cylinder chamber) 8b cylinder chamber (medium temperature cylinder chamber) 8c cylinder chamber (high temperature cylinder chamber) 10 Gas communication passage 11m, 11n Regeneration heat exchanger 12a Heat input / output device (low temperature heat absorber) 12b Heat input / output device (medium temperature radiator) 12c Heat input / output device (high temperature heater) 15 Transmission system operating means 16 First gear 17 Second gear 16a 1st planetary gear 17a 2nd planetary gear 18 Intermediate gear 20 Gear position operating means 21 Clutch mechanism 22 1st bevel gear 23 2nd bevel gear 24 Intermediate bevel gear 25 Gear position operating means

Front Page Continuation (72) Inventor Kazuyuki Morikawa 1-1-1, Hama, Amagasaki City, Hyogo Prefecture Kubota Technology Development Laboratory Co., Ltd. (72) Inventor Satoshi Fukui 64 Ishizukitamachi, Sakai City, Osaka Prefecture Kubota Sakai Manufacturing Co., Ltd. In-house

Claims (5)

[Claims] 1. A rotation transmission system (13) having a plurality of cranks (14a), (14b), (14c) as a device structure, and a drive means (applying a rotation power to the rotation transmission system (13)). 1) and the plurality of cranks (14a), (14b), (14c)
A plurality of pistons (9a), (9b), which are individually connected to
A plurality of cylinder chambers (8a), (8b), (8c) that individually discharge and suck the working gas (G) by the operation of (9c).
And a gas communication passage (10) for communicating these cylinder chambers (8a), (8b), (8c) in the order of respective handling temperatures, and between the cylinder chambers whose communication order is adjacent in this gas communication passage (10). Regeneration heat exchanger (11m) installed in each,
(11n) and a heat input / output device (12a) for inputting / outputting heat to / from each of the cylinder chambers (8a), (8b), (8c),
A variable phase shifter for a power input type Stirling cycle device, comprising: (12b), (12c), wherein the plurality of cranks (14a), (14b), (14c)
Of the plurality of pistons (9a), (9b), (9)
c) phase difference holding operation for holding the phase difference relationship, and the plurality of cranks (14a), (14b), (14c)
Part of the crank (14c) and the other crank (1
4a) and (14b) are rotated relative to each other by a required rotation angle at different angular velocities, and the plurality of pistons (9
a), (9b), (9c) a variable phase device provided with a transmission system operating means (15) for performing a phase difference relationship changing operation for changing the phase difference relationship. 2. A power input type Stirling cycle device comprising: an engine (1) as the driving means, and a high temperature cylinder chamber (8c), an intermediate temperature cylinder chamber (8b) and a low temperature cylinder as the cylinder chamber. A chamber (8a) is provided, and as the heat input / output device, a high temperature heater (12) that applies exhaust heat of the engine (1) to the high temperature cylinder chamber (8c).
c), a medium temperature radiator (12b) for radiating heat from the medium temperature cylinder chamber (8b), and a low temperature heat absorber (12a) for absorbing heat in the low temperature cylinder chamber (8a). With respect to the configuration, the transmission system operation means (15) is configured such that the crank (14c) with respect to the piston (9c) of the high temperature cylinder chamber (8c) and the other cylinder chambers (8a), (8b) in the phase difference relation changing operation. 2. The variable phase shifter according to claim 1, wherein the cranks (14a), (14b) with respect to the pistons (9a), (9b) of (1) are rotationally moved relative to each other at a required rotation angle at different angular velocities. 3. The cranks (14a, 14) to be rotationally operated at different angular velocities in the phase difference relation changing operation in the transmission system operating means (15).
b) and (14c), a first gear (16) that rotates with the cranks (14a, 14b) on one side and a first gear (16c) that rotates with the crank (14c) on the other side as a transmission structure between the cranks. Two gears (17) and a first gear (16) that engages with the first gear (16) in a fixed position
A planetary gear (16a), a second planetary gear (17a) that meshes with the second gear (17), and a position change of the second planetary gear (17a) around the second gear (17). First, an intermediate gear (18) that meshes with both the first planetary gear (16a) and the second planetary gear (17a).
And a gear position operating means (20) for fixing the position of the second planetary gear (17a) around the second gear (17) and changing the position of the second planetary gear (17a). 3. The variable phase shifter according to claim 1, wherein the variable phase shifter has a differential structure. 4. The transmission system operating means (15) transmits between the one side cranks (14a, 14b) and the other side crank (14c) when the position of the second planetary gear (17a) is fixed. A clutch mechanism (21) that is in an operating state and that is in a transmission cutoff state when the position of the second planetary gear (17a) is changed is used as a component gear (16, 16a, 18, 17a, 17) of the planetary gear type differential structure. 4.) The variable phase shifter according to claim 3, wherein the variable phase shifter and the variable phase shifter are additionally installed in parallel. 5. The cranks (14a, 14) to be relatively rotated at angular velocities different from each other in the phase difference relation changing operation in the transmission system operation means (15).
b) and (14c), the first bevel gear (22) that rotates with the crank (14a, 14b) on one side and the first bevel gear (22c) that rotates with the crank (14c) on the other side as a transmission structure between the cranks. 2 bevel gear (2
3) and the first bevel gear (22) and the second bevel gear (23) regardless of the position change around the first bevel gear (22) and the second bevel gear (23).
An intermediate bevel gear (24) that meshes with both of the first and second bevel gears (22) and (23), and the intermediate bevel gear (2) around the first bevel gear (22) and the second bevel gear (23).
3. The variable phase shifter according to claim 1, wherein the variable phase shifter has a bevel gear type differential structure provided with gear position operating means (25) for performing a position fixing operation and a position changing operation.