JPH10103803A - Gas cycle equipment - Google Patents

Abstract

PROBLEM TO BE SOLVED: To shorten a gas communicating passage for a gas cycle for coupling cylinders to one another. SOLUTION: The gas cycle equipment comprises a phase control mechanism K for communicating cylinder chambers C2, C3 having pistons p2, p3 coupled to a first rotary shaft 8 with a cylinder chamber C1 having a piston p1 coupled to a second rotary shaft 9 via gas communicating passages 3a, 3b for a gas cycle so that a non-operating state for interlocking and synchronously rotating the shafts 8, 9 and an operating state for relatively rotating the shafts 8, 9 at a predetermined angle to alter a phase difference of both the shafts 8 and 9 in the case of interlocking and synchronously rotating are switchable. In this case, the shafts 8, 9 are disposed at the same side with respect to the mechanism K, and the pistons pi, p2, p3 coupled to the shafts 8, 9 are put together and disposed to one side of the mechanism K.

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 rotation shaft and a second rotation shaft. A cylinder chamber having a connected piston is communicated with the cylinder chamber through a gas communication passage for a gas cycle.
And a non-operating state in which the first and second rotating shafts are rotated relative to each other to change the phase difference between the two rotating shafts during the synchronized rotating operation. The present invention relates to a gas cycle device provided with a simple phase control mechanism.

[0002]

2. Description of the Related Art A gas cycle apparatus of this type has an inoperative state of the above-mentioned phase control mechanism and rotates the first and second rotating shafts synchronously with each other (that is, at the same speed so as to keep the phase difference constant). And 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.
The phase difference between the piston on the first rotating shaft and the piston on the second rotating shaft is changed by changing the phase difference between the two rotating shafts during the synchronized rotation by setting the phase control mechanism in the operating state. Then, the gas cycle characteristics are changed.

Conventionally, in this type of gas cycle equipment, a phase control mechanism is configured using a so-called differential mechanism, but this phase control mechanism is simply interposed between the butting ends of both rotating shafts. That is, the first and second rotating shafts are arranged in a straight line in a state where the ends are abutted with each other, and a phase control mechanism is interposed at a connecting portion between these rotating shafts (for example, Japanese Patent Application 8-73
No. 834).

[0004]

However, in the above-mentioned conventional type, a cylinder chamber having a piston on the first rotating shaft side and a piston on the second rotating shaft side are provided for interposing the phase control mechanism. The distance between the cylinder chamber and the cylinder chamber increases, and the gas communication path connecting these cylinder chambers becomes longer. For this reason, loss due to adiabatic change in the gas communication path increases, and the equipment efficiency decreases. There were problems such as an increase in piping space and equipment size.

[0005] In view of the above circumstances, a main object of the present invention is to solve the above problem by rationally disposing a phase control mechanism.

[0006]

[Means for Solving the Problems]

[1] According to the first aspect of the invention, the first and second rotating shafts are arranged on the same side with respect to the phase control mechanism, and the pistons connected to the first and second rotating shafts are connected to one side of the phase control mechanism. Because the phase control mechanism is interposed between the butting ends of the first and second rotary shafts arranged in a straight line, the phase control is performed in the center direction of the rotary shaft. A cylinder chamber having a piston on the first rotating shaft side and a cylinder chamber having a piston on the second rotating shaft side are different from a type in which a piston on the first rotating shaft side and a piston on the second rotating shaft side are divided on both sides of the mechanism. The separation distance from the cylinder chamber having the piston can be reduced, whereby the gas communication passage connecting these cylinder chambers can be shortened. From this, it is possible to suppress a loss due to a change in heat insulation in the gas communication passage and to improve the efficiency of the device, and to reduce a piping space to make the device compact.

[2] According to the second aspect of the present invention, the first and second rotating shafts have a double shaft structure in which one of the first and second rotating shafts is concentrically inserted into the other. In a form in which the second rotation shafts are arranged in parallel postures separated from each other, and a phase control mechanism is provided at one end of these rotation shafts,
Compared with the embodiment of the first aspect of the present invention, the arrangement of the shafts can be made more compact and the equipment can be made more compact.

[3] According to the third aspect of the invention, the eccentric shaft portion for connecting the piston of the outer rotating shaft in the double shaft structure is formed to have a diameter such that the rotating shaft center is located in a cross section thereof. Therefore, it is possible to realize a double shaft structure while adopting a form in which the piston is directly connected to the outer rotating shaft. For this reason, for example, the piston is indirectly connected to the outer rotating shaft via another appropriate intermediate interlocking mechanism. This makes it possible to further effectively reduce the size of the device, as compared with a case where a dual-shaft structure is realized by a form in which the components are connected to each other.

[4] According to the fourth aspect of the present invention (see FIG. 3), one of the first and second non-circular members 16, 17 is fixed and the other non-circular member is fixed. In the configuration in which the rotating operation of the other non-circular member 16 by the motor 19 is stopped, the first rigidity via the first elastic annular body 14 is stopped. A differential component generated in the interlocking rotation between the annular body 11 and the second rigid annular body 12 and in the interlocking rotation between the second rigid annular body 12 and the third rigid annular body 13 via the second elastic annular body 15. By offsetting the differential component, the first rigid annular body 11 and the third rigid annular body 13 are integrally rotated in conjunction with each other, whereby the phase control mechanism K is brought into an inoperative state and the first rotary shaft 8 Interlocked with the second rotating shaft 9 while maintaining a constant phase difference , A state of rotating.

When the other non-circular member 16 is rotated by a required angle by a relative rotation operation motor 19, the first rigid annular member 1 via the first elastic annular member 14 is rotated.
A differential component generated in the interlocking rotation of the first and second rigid annular members 12 and a differential component generated in the interlocking rotation of the second rigid annular member 12 and the third rigid annular member 13 via the second elastic annular member 15. A difference between the first rigid annular body 11 and the third rigid annular body 11
The rigid annular body 13 is relatively rotated, whereby the phase control mechanism K is operated so that the first rotating shaft 8 and the second rotating shaft 9 are relatively rotated so that the phase difference between the two rotating shafts 8, 9 is obtained. Get the state to change.

That is, according to this configuration, the differential structure using the three members of the rigid annular member of the inner peripheral teeth, the elastic annular member of the outer peripheral teeth, and the non-circular member is adopted. It is not necessary to rotate the body of the rotary operation motor itself together with the rotating shaft (see the above-mentioned Japanese Patent Application No. 8-73834), and the body of the relative rotation operation motor can be fixed. The connection structure of the signal lines can be simplified, and the power loss can be reduced without spending power for rotating the motor body.

[0012]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 shows a heat pump device using a Stirling device, 1 is a drive motor as a motor for driving a gas cycle, 2 is a gas cycle device portion, and 2 is a gas cycle device portion. , Piston p1, p
2, 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 in accordance with the operations of p3,
And the medium-temperature cylinder chamber C2 are communicated via a gas communication passage 3a, and the medium-temperature cylinder chamber C2 and the low-temperature cylinder chamber C3 are communicated via a gas communication passage 3b. Each of these gas communication passages 3a and 3b The regenerative heat exchangers 4a and 4b inside the heat storage material are interposed.

Reference numeral 5 denotes a heater for inputting heat into the high-temperature cylinder chamber C1, 6 denotes a heat exchanger for extracting hot heat generated in the medium-temperature cylinder chamber C2, and 7 denotes cold heat for extracting cold generated in the low-temperature cylinder chamber C3. It is a heat exchanger for removal.

That is, in the gas cycle equipment section 2,
With the operation of each piston p1 to p3, each cylinder chamber C
1 to C3 are communicated by 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 and For the set with the medium temperature cylinder chamber C2, the heater 5
A stirling cycle is executed under the heat input to the high-temperature cylinder chamber C1 by the above-described method to function as a Stirling engine, and the generated power is added to the applied power from the drive motor 1 and used for the operation of a Stirling heat pump described later.

Further, for the set of the medium-temperature cylinder chamber C2 and the low-temperature cylinder chamber C3, a reverse Stirling cycle is executed by using the applied power from the drive motor 1 and the above-mentioned applied power from the Stirling engine to function as a Stirling heat pump. Due to its heat output,
The cold generated in the low-temperature cylinder chamber C3 is taken out of the heat exchanger 7 for taking out cold heat, and the heat generated in the medium-temperature cylinder chamber C2 is taken out of the heat exchanger 6 for taking out hot heat.

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

As shown in FIGS. 1 to 3, the transmission structure of the gas cycle equipment section 2 is such that the output shaft 1a of the drive motor 1 is directly connected to the base end of the first rotation shaft 8, and the first rotation shaft 8 is connected to the output shaft 1a. 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 medium-temperature cylinder chamber C2. On the distal end side (that is, on the opposite side to the connection side to the drive motor 1 in the present embodiment), the second rotating shaft 9 is externally fitted to the first rotating shaft 8 in a double-shaft structure so as to be relatively rotatable. The piston p of the high-temperature cylinder chamber C1 is
1 is connected.

At the tip of the shaft in this double shaft structure, the first rotating shaft 8 and the second rotating shaft 9 are interlocked synchronously (that is, interlockingly rotated at the same speed so as to keep the phase difference constant). And the operation state in which the first and second rotating shafts 8 and 9 are relatively rotated by a required angle to change the phase difference between the two rotating shafts 8 and 9 during the synchronized rotation. A switchable phase control mechanism K is provided in series.

That is, the power obtained by causing the gas cycle device section 2 to function as an engine by the heat input from the heater 5 and the applied power from the drive motor 1 cause the gas cycle device section 2 to function as a heat pump to generate cold and hot heat. A heat output is obtained. In this operation, the phase control mechanism K
The phase difference at the time of the synchronous rotation of the first rotary shaft 8 and the second rotary shaft 9 is changed, and the piston p1 of the high-temperature cylinder chamber C1 is changed.
And pistons p2 of the other two cylinder chambers C2 and C3.
By adjusting the phase difference relationship of piston operation with p3,
By changing the gas cycle characteristics, the input ratio between the power input from the drive motor 1 and the heat input from the heater 5 can be appropriately changed and adjusted.

Further, when the phase control mechanism K is equipped, a double-shaft structure is employed as described above, and all three pistons p1 to p3 are collectively arranged on the phase control mechanism K on one side in the rotation axis center direction. The cylinder chamber C
The gas communication passages 3a and 3b (particularly, the gas communication passage 3a for the high-temperature cylinder chamber C1) for communicating between 1 to C3 can be shortened, thereby reducing loss due to adiabatic change in the gas communication passages 3a and 3b. Suppression and downsizing of the entire device are achieved.

In the adoption of the double shaft structure, the eccentric shaft portion for connecting the piston in the crank portion 9a of the second rotary shaft 9 located on the outside is formed in the cross section of the rotary shaft. It is formed to have a diameter d where the core Q is located, thereby realizing a double-shaft structure while adopting a structure in which the piston p1 is directly connected to the outer second rotation shaft 9.

The above-described phase control mechanism K includes a differential section 10,
A servo motor 19 for relative rotation operation as an operation means for this is provided. As a specific structure, as shown in FIG. 3, in the differential portion 10, a large number of spline-shaped teeth (for example, The first to third rigid annular bodies 11 to 13 forming several hundred teeth) are juxtaposed concentrically, and a plurality of spline-shaped teeth are formed on the outer periphery.
The elastic annular body 14 is divided into first and second rigid annular bodies 11 and 12.
And a second elastic annular body 15 having a large number of spline-shaped teeth formed on the outer periphery thereof is arranged inside the second and third rigid annular bodies 12 and 13.

The first elastic annular body 14 is fitted inside the first elastic annular body 14 so as to be relatively rotatable.
4 so as to engage the inner peripheral teeth of the first and second rigid annular bodies 11 and 12 at two locations in the circumferential direction.
A first elliptical member 16 for elastically deforming the elastic annular body 14 into an elliptical shape, and a second elastic annular body 15 are internally fitted so as to be rotatable relative to each other. At two places in the circumferential direction, the second and third rigid annular bodies 12, 1
A second elliptical member 17 for elastically deforming the second elastic annular body 15 into an elliptical shape is provided so as to engage with each of the three inner peripheral teeth.

The first rigid annular body 11 is connected to the distal end of the first rotary shaft 8 at the distal end of the double shaft structure,
The rigid annular body 13 is connected to the distal end of the second rotating shaft 9 at the distal end of the dual-shaft structure via a connecting member 18 also serving as a case, and the first elliptical member 16 is connected to the servomotor 19.
Is connected to the rotating shaft 19a. The second elliptical member 1
7 is fixedly supported, and the body of the servo motor 19 is fixedly supported on the case of the gas cycle equipment unit 2.

Further, the number of teeth of the inner peripheral teeth of the second rigid annular body 12, the number of teeth of the outer peripheral teeth of the first elastic annular body 14,
The number of teeth of the outer peripheral teeth of the elastic annular body 15 is equal to the number of teeth. On the other hand, the number of teeth of the inner peripheral teeth of the first rigid annular body 11 connected to the first rotating shaft 8 and the number of teeth of the second rotational The number of teeth of the inner peripheral tooth row of the third rigid annular body 13 connected to the shaft 9 is extremely small (both the number of teeth of the second rigid annular body 12, the first and second elastic annular bodies 14 and 15). (For example, about two or three teeth), the number of teeth being different from each other.

That is, in the phase control mechanism K,
In a state where the rotation operation of the first elliptical member 16 by the servo motor 19 is stopped, the first
A differential component (i.e., a differential component due to a difference in the number of teeth between the first elastic annular member 14 and the first rigid annular member 11) generated in the interlocking rotation between the rigid annular member 11 and the second rigid annular member 12; The second rigid annular body 12 and the third
The differential component (ie, the differential component due to the difference in the number of teeth between the second elastic annular member 15 and the third rigid annular member 13) generated in the interlocking rotation with the rigid annular member 13 is canceled, and the first rigid annular member is canceled. The body 11 and the third rigid annular body 13 are integrally rotated in association with each other, thereby setting the phase control mechanism K in an inoperative state.
A state is obtained in which the first rotation shaft 8 and the second rotation shaft 9 are synchronously rotated while maintaining a constant phase difference.

By rotating the first elliptical member 16 by a required angle by the servo motor 19, the first rigid annular body 11 and the second rigid annular body 12 are interlocked via the first elastic annular body 14. A difference is generated between a differential component generated in the rotation and a differential component generated in the interlocking rotation of the second rigid annular member 12 and the third rigid annular member 13 via the second elastic annular member 15, and the first The rigid annular body 11 and the third rigid annular body 13 are relatively rotated, and as a result, the first rotation shaft 8 and the second rotation shaft 9 are relatively rotated by operating the phase control mechanism K. A state in which the phase difference between the axes 8 and 9 is changed is obtained.

In the phase control mechanism K having the above structure, it is not necessary to rotate the body of the servomotor 19 together with the rotating shafts 8 and 9, and the body of the servomotor 19 can be fixed. Can be simplified, and the power loss can be reduced without spending power for rotating the motor body.

[Another Embodiment] Next, another embodiment will be described. In the above-described embodiment, the differential portion 10 of the phase control mechanism K may be a rigid annular body of the inner peripheral teeth, an elastic annular body of the outer peripheral teeth, and an elliptical shape (a polygonal shape such as a triangle or a quadrangle). )), The non-circular member is shown.
In some cases, the differential section 10 of the phase control mechanism K may be formed by a differential mechanism of a planetary gear type, a bevel gear type, or the like in the embodiments of the present invention.

In the above embodiment, the first and second rotating shafts 8 and 9 have a double shaft structure, and the pistons p1 to p3 are arranged on one side of the phase control mechanism K.
In some cases, in carrying out the invention of claim 1,
The first and second rotating shafts 8 and 9 are arranged on the same side with respect to the phase control mechanism K in a parallel posture or a posture having an intersection angle apart from each other, and are connected to the first and second rotating shafts 8 and 9. A configuration in which the pistons p1 to p3 are collectively arranged on one side of the phase control mechanism K may be adopted.

The present invention can be applied not only to a Stirling machine for performing a Stirling cycle or a reverse Stirling cycle but also to various gas cycle machines. Also, the number of cylinders is not limited to three. The number of cylinders provided on each of the side 8 and the side of the second rotating shaft 9 may be any one or more.

It should be noted that, in the claims,
In the section of [Means for Solving the Problems], reference numerals are written for convenience of comparison with the drawings, but the present invention is not limited to the configuration of the attached drawings by the entry.

[Brief description of the drawings]

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

FIG. 2 is an enlarged view of a transmission structure.

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

[Explanation of symbols]

 8 First rotating shaft 9 Second rotating shaft p1 to p3 Piston C1 to C3 Cylinder chamber 3a, 3b Gas communication passage K Phase control mechanism Q Rotating shaft core d Diameter of eccentric shaft portion for piston connection 11 to 13 First to first 3 Rigid annular body 14, 15 First and second elastic annular body 16, 17 First and second non-circular member 19 Motor for relative rotation operation 19a Output shaft

Claims (4)

[Claims] Cylinder chambers (C2, C3) each having a piston (p2, p3) connected to a first rotating shaft (8);
The first and second rotating shafts are communicated with a cylinder chamber (C1) having a piston (p1) connected to the second rotating shaft (9) through gas communication passages (3a, 3b) for a gas cycle. (8, 9) in a non-operating state in which the first and second rotating shafts (8, 9) are rotated relative to each other by a required angle, and the two rotating shafts (8, 9) in the interlocking synchronous rotation are rotated. , 9) provided with a phase control mechanism (K) that can be switched to an operation state of changing the phase difference, wherein the first and second rotating shafts (8, 9) are connected to the phase control mechanism (K). K), and the pistons (p1, p2, p) connected to the first and second rotating shafts (8, 9).
(3) A gas cycle device wherein the phase control mechanism (K) is collectively arranged on one side. 2. The first and second rotating shafts (8, 9) are:
2. The gas cycle device according to claim 1, wherein the gas cycle device has a double-shaft structure in which one of the components is concentrically inserted into the other. 3. The eccentric shaft portion for connecting a piston of the outer rotating shaft (9) in the double shaft structure is formed to have a diameter (d) where the rotating shaft core (Q) is located in a cross section thereof. Item 2
Gas cycle equipment as described. 4. The first to third rigid annular bodies (1) each having a plurality of teeth formed on an inner periphery thereof.
1, 12 and 13), and a first elastic annular body (1) having a number of teeth formed on the outer periphery and arranged inside the first and second rigid annular bodies (11, 12).
4) and a second elastic annular body (1) having a number of teeth formed on the outer periphery and arranged inside the second and third rigid annular bodies (12, 13).
5) and the first elastic annular body (14) is fitted inside the first elastic annular body (14) so as to be rotatable relative to the first elastic annular body (14).
The first elastic annular body (14) is elastically deformed so that the outer peripheral teeth of the first elastic annular body (14) are engaged with the inner peripheral teeth of the first and second rigid annular bodies (11, 12) at a part in the circumferential direction. A non-circular member (16) and the second elastic annular body (15) are fitted inside the second elastic annular body (15) so as to be relatively rotatable.
The second elastic annular body (15) is elastically deformed so that the outer peripheral teeth of the second elastic annular body (15) are engaged with the inner peripheral teeth of the second and third rigid annular bodies (12, 13) at a part in the circumferential direction. A non-circular member (17), wherein the second rigid annular body (12) and the first elastic annular body (1) are provided.
4) and the second elastic annular body (15) have the same number of teeth, and the first rigid annular body (11) and the third rigid annular body (13) with the number of teeth different from the number of teeth. And the number of teeth is equal, and the first rigid annular body (11) is connected to the first rotating shaft (8).
And the third rigid annular body (13) is connected to the second rotating shaft (9), and one of the first and second non-circular members (16, 17) is fixed and the other is relatively fixed. 4. The motor according to claim 1, wherein the output shaft is connected to an output shaft of the rotation operation motor.
Gas cycle equipment according to the item.