JP3394664B2 - Gas cycle equipment - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gas cycle device such as a reverse Stirling cycle heat pump or a Stirling cycle engine, and more particularly to a cylinder chamber having a piston connected to a first rotating shaft and a second rotating shaft. The cylinder chamber provided with the connected piston is communicated via a gas communication passage for a gas cycle, a prime mover for gas cycle operation is coupled to a first rotating shaft, and the first and second rotating shafts are interlocked and synchronously rotated. A phase that can be switched between a non-operating state and an operating state in which the first and second rotating shafts are relatively rotated by a required angle by the applied operating force to change the phase difference between the rotating shafts during the interlocked synchronous rotation. The present invention relates to a gas cycle device provided with a control mechanism.

[0002]

2. Description of the Related Art A gas cycle device of this type has the above-mentioned phase control mechanism in a non-operating state so that the first and second rotary shafts rotate in synchronization with each other (that is, speeds equal to each other so as to keep the phase difference constant). By interlocking rotation), the piston on the side of the first rotary shaft and the piston on the side of the second rotary shaft are operated with a constant phase difference to perform gas cycle operation, and
The phase difference between the piston on the side of the first rotary shaft and the piston on the side of the second rotary shaft is changed by changing the phase difference between both rotary shafts in the synchronized synchronous rotation with the phase control mechanism in the operating state. Then, the gas cycle characteristics are changed.

By the way, conventionally, in this type of gas cycle equipment, in the operating state of the phase control mechanism, in order to relatively rotate the first and second rotating shafts by a given angle by an applied operating force, a relative rotating operation is performed. A dedicated servo motor is provided, and the driving force of the servo motor is used as the above-mentioned applied operating force to relatively rotate both rotary shafts (see, for example, Japanese Patent Application No. 8-73834).

[0004]

However, in the above conventional equipment, in addition to the gas cycle driving prime mover such as the drive motor connected to the first rotary shaft, the dedicated servo motor for the relative rotary operation as described above is additionally provided. Therefore, there is a problem that the equipment cost is high.

In view of the above situation, the main object of the present invention is to eliminate the additional equipment of a dedicated servomotor for relative rotation operation by a rational improvement.

[0006]

[1] In the invention according to claim 1, the first and second rotary shafts are relatively rotated by a required angle by an applied operation force, and both rotary shafts at the time of interlocking synchronous rotation. When changing the phase difference between the first and second rotating shafts, the gas cycle driving prime mover connected to the first rotating shaft is also used for the relative rotation operation, and the driving force of the prime mover is applied to the first and second rotating shafts. The configuration is such that relative rotation is performed by the required angle.

Therefore, in the phase difference changing operation, the relative rotation operation of the first and second rotary shafts is performed by the driving operation force as before, but the additional equipment of the dedicated servo motor for the relative rotation operation is unnecessary. Therefore, the device cost can be reduced as compared with the conventional device described above.

Specifically (see FIG. 7), the non-circular member 13 is allowed to rotate and the rigid annular body 11 and the non-circular member 13 are integrally rotated in a switching state of the clutch 18a and the brake 18b. By setting the state, the differential portion 10 is set to the non-differential state, and the rigid annular body 11,
The elastic annular body 12 and the non-circular member 13 are integrally rotated, so that the first rotation shaft 8 and the second rotation shaft 9 have a constant phase difference with the phase control mechanism K in a non-operating state. It keeps at and obtains the state of synchronized rotation.

Further, the clutch 18a and the brake 18b
In this switching state, the non-circular member 13 is fixed to stop the rotation, and the rigid annular body 11 and the non-circular member 13 are
By allowing the relative rotation with respect to
In the above, with the rotation of the rigid annular body 11 and the elastic annular body 12, a difference due to the difference in the number of teeth is generated between the rigid annular body 11 and the elastic annular body 12, whereby
As the operating state of the phase control mechanism K, the first by the prime mover 1
With the rotational drive of the rotary shaft 8, the first rotary shaft 8 and the second rotary shaft 9 are relatively rotated to obtain a state in which the phase difference between the rotary shafts 8 and 9 is changed.

That is, with this structure, since the teeth of the rigid annular body 11 and the teeth of the elastic annular body 12 are engaged with each other, a general differential structure of a planetary gear type or a bevel gear type for engaging rigid gears is used. The so-called backlash can be reduced as compared with the case where the differential portion of the phase control mechanism is constituted by this, and therefore, the phase difference of both rotary shafts can be changed and the gas cycle characteristics can be changed with high accuracy.

[ 2 ] In the invention according to claim 2 , the prime mover
The first and second rotating shafts are required as the driving force for applying the driving force.
In order to perform relative rotation operation by an angle (see FIG. 4), the second non-circular member 16 is allowed to rotate and the first and second rigid annular bodies 11 and 14 are connected by switching the clutch 18 a and the brake 18 b. By making the body and the second non-circular member 16 rotate integrally, the second differential portion 10
B is in a non-differential state, and the three members of the second rigid annular body 14, the second elastic annular body 15, and the second non-circular member 16 are integrally rotated, and along with this, the first differential portion 10A The first rigid annular body 11 and the first elastic annular body 1 as well.
2. The three members of the first non-circular member 13 are rotated integrally, so that the first rotation shaft 8 and the second rotation shaft 9 have a constant phase difference with the phase control mechanism K in the non-operating state. Keep it and get the state of synchronized rotation.

Further, the clutch 18a and the brake 18b
In the switching state, the second non-circular member 16 is fixed and the rotation is stopped, and the first and second rigid annular bodies 1 are
By setting the state in which the relative rotation between the connected body of Nos. 1 and 14 and the second non-circular member 16 is allowed, as the second rigid annular body 14 and the second elastic annular body 15 rotate in the second differential portion 10B. , These second rigid annular body 14 and second elastic annular body 1
5 causes a differential due to the difference in the number of teeth, and accordingly, also in the first differential portion 10A, with the rotation of the first rigid annular body 11 and the first elastic annular body 12, A difference due to the difference in the number of teeth is generated between the first rigid annular body 11 and the first elastic annular body 12, whereby
As the operating state of the phase control mechanism K, the first by the prime mover 1
With the rotational drive of the rotary shaft 8, the first differential unit 10A and the second differential unit 10B are overlapped with each other in the first differential state.
The rotary shaft 8 and the second rotary shaft 9 are relatively rotated to obtain a state in which the phase difference between the rotary shafts 8 and 9 is changed.

That is, with this configuration, as in the case of the invention described in claim 1 , as compared with the case where the differential portion of the phase control mechanism is configured by using a general differential structure that meshes rigid gears, Backlash can be reduced.

Further, in the state where the differential of the first differential section 10A and the differential of the second differential section 10B are superposed, both rotary shafts 8,
Since 9 is relatively rotated, the relative rotation angle θ of both rotation shafts 8 and 9 per one rotation of the first rotation shaft 8 can be further reduced as compared with the invention according to claim 1 described above.
From these facts, when changing the phase difference between both rotary shafts, and further when changing the gas cycle characteristics, it is possible to obtain a higher degree of change accuracy.

[ 3 ] According to the third aspect of the invention, the phase control mechanism is switched from the non-operating state to the operating state in response to the switching command, and after this switching, the rotational speed n detected by the rotational speed sensor is set to the rotational speed n. Based on this, the relative rotation angle θ between the first rotation axis and the second rotation axis is calculated, and when this relative rotation angle θ reaches the specified angle θs, control for returning the phase control mechanism from the operating state to the non-operating state Since a phase difference changing operation is performed using a gas cycle driving prime mover such as a dedicated servo motor, which is generally difficult to control the rotation angle, a switching command is given to this controller and the relative rotation angle θs By designating, the phase difference between both rotary shafts can be changed easily and accurately.

[0016]

DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 shows a heat pump device using a Stirling machine, 1 is a drive motor as a prime mover for gas cycle operation, 2 is a gas cycle equipment section, and 2 is a gas cycle equipment section. , Pistons p1, p
A high temperature cylinder chamber C1, a medium temperature cylinder chamber C2, and a low temperature cylinder chamber C3 that repeatedly discharge and inhale the working gas G individually in accordance with the operations of 2 and p3 are provided, and the high temperature cylinder chamber C1
And the intermediate temperature cylinder chamber C2 are communicated with each other through the gas communication passage 3a, and the intermediate temperature cylinder chamber C2 and the low temperature cylinder chamber C3 are communicated with each other through the gas communication passage 3b. Regenerative heat exchangers 4a and 4b having a heat storage material inside are interposed.

Further, 5 is a heater for inputting heat to the high temperature cylinder chamber C1, 6 is a heat exchanger for extracting heat generated in the medium temperature cylinder chamber C2, and 7 is cold heat for extracting generated cold heat in the low temperature cylinder chamber C3. It is a heat exchanger for taking out.

That is, in this gas cycle equipment section 2,
Along with the operation of each piston p1 to p3, each cylinder chamber C
1 to C3 are connected to each other through the gas communication passages 3a and 3b, and the working gas is discharged and sucked under the action of the heater 5 and each of the heat exchangers 4a, 4b, 6 and 7, so that the high temperature cylinder chamber C1 is connected. For the combination with the medium temperature cylinder chamber C2, the heater 5
The Stirling cycle is executed under heat input to the high temperature cylinder chamber C1 to function as a Stirling engine, and the generated power is added to the applied power from the drive motor 1 to be used for the operation of the Stirling heat pump described later.

With respect to the combination of the medium temperature cylinder chamber C2 and the low temperature cylinder chamber C3, the reverse Stirling cycle is executed by the power supplied from the drive motor 1 and the power supplied by the above Stirling engine to function as a Stirling heat pump. As its heat output,
The cold heat generated in the low temperature cylinder chamber C3 is taken out from the heat exchanger 7 for taking out cold heat, and the hot heat generated in the intermediate temperature cylinder chamber C2 is taken out from the heat exchanger 6 for taking out heat.

Various gases such as helium gas, hydrogen gas, and air can be adopted as the working gas G in the gas cycle equipment section 2, and the heat input to the high temperature cylinder chamber C1 by the heater 5 is Various heats such as heat generated by the burner, exhaust heat generated by other devices / equipment, or engine exhaust heat when an engine is used as a prime mover can be adopted.

With respect to the transmission structure of the gas cycle equipment part 2, as shown in FIGS. 1 to 4, the base end of the first rotary shaft 8 is directly connected to the output shaft 1a of the drive motor 1, and the first rotary shaft 8 is connected. The piston p2 of the medium temperature cylinder chamber C2 and the piston p3 of the low temperature cylinder chamber C3 are connected to the crank portion 8a of the first rotary shaft 8 of the pistons p2 and p3 of the medium temperature and low temperature cylinder chambers C2 and C3. On the tip side (that is, on the side opposite to the side connected to the drive motor 1 in the present embodiment), the second rotary shaft 9 is fitted onto the first rotary shaft 8 so as to be rotatable relative to the first rotary shaft 8 by a double shaft structure. 2 The piston p of the high temperature cylinder chamber C1 is attached to the crank portion 9a of the rotary shaft 9.
1 are connected.

At the tip of the shaft in this double shaft structure, the first rotary shaft 8 and the second rotary shaft 9 are interlocked synchronously rotated (that is, interlocked rotary at equal speeds so as to keep the phase difference constant). ), And the action of changing the phase difference between the rotating shafts 8 and 9 during the interlocked synchronous rotation by relatively rotating the first and second rotating shafts 8 and 9 by a required angle by the applied operating force. A phase control mechanism K that can be switched between the state and the state is continuously provided.

In other words, the heat input from the heater 5 causes the gas cycle equipment section 2 to function as an engine and the power supplied from the drive motor 1 to cause the gas cycle equipment section 2 to function as a heat pump to generate cold heat and warm heat. Although the heat output is obtained, in this operation, the phase control mechanism K described above
The phase difference at the time of the interlocking synchronous rotation of the first rotating shaft 8 and the second rotating shaft 9 is changed so that the piston p1 of the high temperature cylinder chamber C1 is changed.
And the pistons p2 of the other two cylinder chambers C2, C3
By changing the phase difference relationship of piston movement with p3,
The gas cycle characteristics are changed so that the input ratio between the power input from the drive motor 1 and the heat input from the heater 5 can be changed appropriately.

As shown in FIGS. 3 and 4, the phase control mechanism K has a differential section 10 and a clutch / brake mechanism 18 as an operating section for the differential section 10, and the The moving unit 10 includes a first differential unit 10A and a second differential unit 10A.
B is provided, and as a specific structure, the first differential unit 10
In A, a first rigid annular body 11 having a large number of spline-shaped teeth (for example, hundreds to several hundreds of teeth) formed on the inner circumference thereof, and teeth of an inner circumferential tooth row of the first rigid annular body 11 are provided. The first elastic ring-shaped body 12 arranged inside the first rigid ring-shaped body 11 is formed with a large number of spline-shaped teeth on the outer circumference, the number of which is slightly different (for example, about two or three). And the inner circumference of the first elastic annular body 12 is rotatably fitted to the first elastic annular body 12, and the outer peripheral tooth row of the first elastic annular body 12 is inserted into the first rigid annular body 11 at two circumferential positions. A first elliptical member 13 that elastically deforms the first elastic annular body 12 into an elliptical shape is provided so as to be occluded in the circumferential tooth row.

Similarly, in the second differential portion 10B, a second rigid annular body 14 having a large number of spline-shaped teeth (hundreds to hundreds of teeth) formed on the inner circumference, and the second rigid annular body 14 are also provided. Rigid ring 1
A large number of spline-shaped teeth, which are slightly different from the number of teeth of the inner peripheral tooth row of No. 4 (about two or three teeth), are formed on the outer periphery and are arranged inside the second rigid annular body 14. The second elastic annular body 15 and the second elastic annular body 15 are fitted into the second elastic annular body 15 so as to be rotatable relative to each other, and by this fitting, the outer peripheral tooth row of the second elastic annular body 15 is located at two positions in the circumferential direction. A second elliptical member 16 that elastically deforms the second elastic annular body 15 into an elliptical shape is provided so as to occlude the inner peripheral tooth row of the two-rigid annular body 14.

The first rigid annular body 11 and the second rigid annular body 14 are connected to the first and second case-combined connecting members 17 respectively.
a and 17b, the tip of the second rotating shaft 9 at the tip of the double shaft structure and the first disc member 19 on the side of the clutch / brake mechanism 18 in the state of being integrally connected to each other.
And the first elastic annular body 12 is connected to the tip of the first rotating shaft 8 in the tip portion of the double shaft structure, and the first elliptical member 13 is further connected via the central connecting member 20. The second elliptical member 16 is connected to the second elastic annular member 15, and the second elliptical member 16 is connected to the relay rotary shaft 21 on the clutch / brake mechanism 18 side.

On the other hand, the clutch / brake mechanism 18 has a phase control mechanism K when the differential portion 10 is switched.
Is switched between the non-acting state and the actuating state. Specifically, the second disc member 22 integrally connected to the relay rotary shaft 21 and the movable portion 19a (first A clutch 18a for engaging and disengaging frictional joining with a movable portion which is elastically biased toward the separating side with respect to the disc surface of the two-disc member 22, and a coil holding portion fixed to the case of the gas cycle equipment unit 2 via stays s. The brake pad 23a of the movable disk 24a of the third disc member 24 integrally connected to the relay rotary shaft 21 (the brake pad 2a).
Brake 18 for bringing relay rotary shaft 21 into a rotation stopped state by pressing a movable portion which is elastically urged to the separating side with respect to 3a.
As a mode of operation, the controller 25, which will be described later, performs a switching operation performed on the electromagnetic coils 23b and 23c of the coil holding portion 23 by a switching operation to release the braking by the brake 18b, and the clutch 18a is in the engaged state. The non-relay relay state in which the clutch 18a is disengaged and, conversely, the non-relay relay state in which the brake 18b is in the braking state with the clutch 18a disengaged are selectively operated.

That is, the clutch / brake mechanism 18
To the non-braking relay state, and the second rotating shaft 9 and the first and second
By integrally rotating the first disk member 19 connected to the rigid annular bodies 11 and 14 and the relay rotary shaft 21 connected to the second elliptical member 16 in a non-braking state, the second differential portion 10B is non-differential. In this state, the second rigid annular body 14 and the second elastic annular body 1
5, the three members of the second elliptical member 16 are integrally rotated, and the first differential portion 10A is also brought into a non-differential state accordingly, and the first rigid annular body 11, the first elastic annular body 12, The three members of the first elliptical member 13 are integrally rotated, whereby the first rotating shaft 8 and the second rotating shaft 9 are interlocked with each other while keeping the constant phase difference in the non-operating state of the phase control mechanism K. Get the state of synchronous rotation.

While the clutch / brake mechanism 18 is set in the non-relay braking state, the rotation of the first disk member 19 connected to the second rotating shaft 9 and the first and second rigid annular bodies 11 and 14 is allowed. By setting the relay rotation shaft 21 to stop rotating together with the second elliptical member 16 connected thereto, in the second differential portion 10B, as the second rigid annular body 14 and the second elastic annular body 15 rotate, A differential is generated between the second rigid annular body 14 and the second elastic annular body 15 due to the difference in the number of teeth, and accordingly, the first rigid annular body 11 is also formed in the first differential portion 10A. With the rotation of the first elastic annular body 12, a difference due to the difference in the number of teeth is generated between the first rigid annular body 11 and the first elastic annular body 12, whereby the phase control mechanism K is operated. As a working state, drive motor Along with by the rotational driving of the first rotary shaft 8, a first rotary shaft 8 and a second rotary shaft 9 by relative rotation operation, and the state for changing the phase difference between the two rotating shafts 8,9.

That is, the phase control mechanism K is operated by the applied operating force in the operating state.
In the relative rotation operation of the drive motor 1 by a required angle, the drive motor 1 for gas cycle operation connected to the first rotary shaft 8 is also used for the relative rotation operation.
Drive force of the first and second rotary shafts 8 and 9 as applied operating force
Is configured to perform relative rotation operation, and thereby, the additional equipment of the dedicated servo motor for relative rotation operation is not required, and the device cost is reduced.

When the switching command is given, the controller 25 automatically changes the phase difference between the first rotary shaft 8 and the second rotary shaft 9 by the angle θs designated together with the command. The clutch / brake mechanism 18 is automatically operated. Specifically, when a switching command is given, the clutch / brake mechanism 18 is switched from the non-braking relay state to the non-relay braking state by operating the electromagnetic coil. Then, the phase control mechanism K is switched from the non-operating state to the operating state, and after the switching, the rotation speed sensor 26
The relative rotation angle θ between the first rotation shaft 8 and the second rotation shaft 9 is calculated on the basis of the rotation speed n of the first rotation shaft 8 detected by, and the relative rotation angle θ reaches the designated angle θs. At this time, the clutch / brake mechanism 18 is returned from the non-relay braking state to the non-relay relay state, and the phase control mechanism K is returned from the operating state to the non-operating state.

Another Embodiment Next, another embodiment will be listed. To configure the phase control mechanism K, as shown in FIG. 5, the piston p1 of the high temperature cylinder chamber C1 is provided between the first differential portion 10A and the second differential portion 10B.
You may make it arrange | position the connection part with respect to.

Further, in constructing the phase control mechanism K, as shown in FIGS. 6 and 7, for the purpose of downsizing and weight reduction,
A structure in which the second differential portion B is omitted and the first rigid annular body 11 is connected to the first disc member 19 and the first elliptical member 13 is connected to the relay rotary shaft 21 may be adopted. .

The prime mover 1 for gas cycle operation, which is also used for relative rotation operation, is not limited to a motor and may be an engine.

The present invention can be applied not only to the Stirling machine for carrying out the Stirling cycle and the reverse Stirling cycle but also to various gas cycle machines, and the number of cylinders is not limited to three cylinders, and the first rotary shaft is not limited. The number of cylinders provided on each of the 8 side and the second rotating shaft 9 side may be either a single number or a plurality.

In the claims and the means for solving the problem, reference numerals are given for convenience of comparison with the drawings. The configuration is not limited to the above.

[Brief description of drawings]

FIG. 1 is a perspective view showing the overall configuration of a device.

[Fig.2] Enlarged view of transmission structure

FIG. 3 is an enlarged view of a phase control mechanism.

FIG. 4 is a schematic diagram of a transmission structure and a phase control mechanism.

FIG. 5 is a schematic view of a transmission structure and a phase control mechanism showing another embodiment.

FIG. 6 is an enlarged view of a phase control mechanism showing another embodiment.

7 is a schematic diagram of a transmission structure and a phase control mechanism corresponding to the phase control mechanism of FIG.

[Explanation of symbols]

8 First rotating shaft 9 Second rotating shaft p1 to p3 pistons C1 to C3 cylinder chamber 3a, 3b gas communication passage 1 prime mover K phase control mechanism 10 Differential part 11 Rigid annular body (first rigid annular body) 12 Elastic annular body (first elastic annular body) 13 Non-circular member (first non-circular member) 18 Operation part 18a clutch 18b brake 10A first differential section 10B Second differential section 14 Second rigid annular body 15 Second elastic annular body 16 Second non-circular member n rpm 26 Revolution sensor θ Relative rotation angle θs specified angle 25 controller

Continuation of the front page (56) Reference JP-A-8-219569 (JP, A) JP-A-7-279632 (JP, A) JP-A-8-177993 (JP, A) JP-A-5-26305 (JP , A) (58) Fields investigated (Int.Cl. ⁷ , DB name) F25B 9/14 520 F25B 9/14 510 F02G 1/045 F16D 1/12 F16H 1/28

Claims (3)

(57) [Claims] 1. A cylinder chamber (C2, C3) provided with a piston (p2, p3) connected to a first rotating shaft (8),
The cylinder chamber (C1) provided with the piston (p1) connected to the second rotating shaft (9) is made to communicate with each other via the gas communication passages (3a, 3b) for gas cycle, and the prime mover (1) for gas cycle operation is provided. ) Is connected to the first rotary shaft (8) and the first and second rotary shafts (8, 9) are interlocked and synchronously rotated, and the first and second rotary shafts ( (8) and (9) are rotated relative to each other by a required angle, and a phase control mechanism (K) is switchable to an operating state in which the phase difference between both rotary shafts (8, 9) at the time of the interlocked synchronous rotation is changed.
The phase control mechanism (K) uses the driving force of the prime mover (1) as the applied operating force in the operating state,
In order to relatively rotate the second rotary shafts (8, 9) by a required angle, a rigid annular body (11) having a large number of teeth formed on its inner periphery is provided as a differential portion (10).
A large number of teeth with a different number of teeth from the rigid annular body (11)
Formed on the outer circumference and placed inside the rigid annular body (11)
And the elastic annular body (12) and the elastic annular body (12)
Then, it is relatively rotatably fitted inside, and by this fitting,
The outer peripheral tooth row of the flexible annular body (12) has the rigidity in a part in the circumferential direction.
The bullet is inserted so as to occlude the inner dentition of the annular body (11).
Non-circular member (13) for elastically deforming the flexible annular body (12)
Of the elastic annular body (12) and the rigid annular body (11)
Of which, one is on the first rotary shaft (8) and the other is on the front
The rigid annular body (11) and the non-circular member (13) are connected to the second rotating shaft (9) and serve as an operating portion (18).
To a state in which it rotates integrally and a state in which relative rotation is allowed.
The clutch (18a) to be replaced and the non-circular member (13) are fixed to stop rotation.
Gas cylinder having a configuration including a brake (18b)
Kuru equipment . 2. A piston connected to a first rotating shaft (8)
A cylinder chamber (C2, C3) having (p2, p3),
Provided with a piston (p1) connected to the second rotating shaft (9)
The cylinder chamber (C1) and the gas communication passage for the gas cycle
(3a, 3b), the prime mover (1) for gas cycle operation is connected to the first rotary shaft.
(8) to rotate the first and second rotary shafts (8, 9) in synchronization with each other.
The non-acting state and the applied operation force
Move the rolling shafts (8, 9) relative to each other by the required angle,
Change the phase difference between both rotating shafts (8, 9) during synchronized rotation.
Phase control mechanism (K) that can be switched to a further operating state
And a phase control mechanism (K) for operating the prime mover in an operating state.
Using the driving force of the machine (1) as the applied operating force, the first
And the relative rotation of the second rotation axis (8, 9) by the required angle
To do so, a first rigid annular body (11) having a large number of teeth formed on the inner periphery is provided as a differential portion (10),
A first elastic annular body (12) having a number of teeth different in the number of teeth of the first rigid annular body (11) formed on the outer periphery and arranged inside the first rigid annular body (11); , The first elastic annular body (12) is rotatably fitted in the first elastic annular body (12), and by this inner fitting, the outer peripheral tooth row of the first elastic annular body (12) is circumferentially partially covered with the first rigidity. A first non-circular member (13) for elastically deforming the first elastic annular body (12) so as to occlude the inner circumferential tooth row of the annular body (11);
The differential portion (10A) and the second rigid annular body (1 having a large number of teeth formed on the inner periphery thereof)
4) and a second elastic annular body in which a large number of teeth having a number of teeth different from the number of teeth of the second rigid annular body (14) are formed on the outer periphery and arranged inside the second rigid annular body (14). (15),
The second elastic annular body (15) is fitted into the second elastic annular body (15) so as to be rotatable relative thereto, and the second elastic annular body (15) is fitted by the inner fitting.
Of the outer peripheral tooth row of the second rigid annular body (1
4) A second differential portion (10B) having a second non-circular member (16) that elastically deforms the second elastic annular body (15) so as to occlude the inner peripheral tooth row, The first rigid annular body (11) and the second rigid annular body (1
4) and the first non-circular member (1
3) and the second elastic annular member (15) in a connected state, of the connected body of the first and second rigid annular bodies (11, 14) and the first elastic annular body (12), One of them is connected to the second rotating shaft (9) and the other is connected to the first rotating shaft (8), and as an operation part (18), the first and second rigid annular bodies (11, 14) are connected. A clutch (18) for switching the connecting body and the second non-circular member (16) between a state of integrally rotating and a state of allowing relative rotation.
and a), it is constituted with a brake (18b) for the rotation stop state by fixing the second non-circular member (16) Gas
Cycle equipment . 3. A rotation speed sensor (26) for detecting the rotation speed (n) of the first rotation shaft (8) is provided, and the phase control mechanism (K) is changed from a non-operating state to an operating state in response to a switching command. After switching, the relative rotation angle (θ) between the first rotating shaft (8) and the second rotating shaft (9) is changed based on the detected rotation speed (n) of the rotation speed sensor (26). operation to claim this when the relative rotation angle (theta) reaches the specified angle ([theta] s), wherein are controller to return the phase control mechanism (K) from the working state to the inoperative state (25) provided The gas cycle device according to 1 or 2 .