JPH06185817A - Pulse tube refrigerator - Google Patents

Abstract

PURPOSE:To obtain a pulse tube refrigerator having a small size and high performance without necessity of a buffer tank. CONSTITUTION:A first communication tube 24 communicates a compressing chamber 5 with a pulse tube 1 via a heat accumulator 2 and a low temperature heat exchanger 8. Further, since second communication tubes 22, 23 communicate a buffer chamber 10 with the tube 1 via an ambient temperature heat exchanger 9, operation gas flows between the chamber 10 and the chamber 5 via the tube 1. Accordingly, a conventional buffer tank can be eliminated.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pulse tube refrigerator used for cryogenic production.

[0002]

2. Description of the Related Art FIG. 20 shows, for example, a document "Pulse Tube Refrigerator Using Linear Compressor (4) -Comprehensive Characteristic Evaluation-" (Author: Yoichi Matsubara, 7 others, Journal: 46th Society of Low Temperature Engineering Superconductivity Society). It is sectional drawing which shows the conventional pulse tube refrigerator shown in the lecture summary, 1991). In the figure, 1 is a pulse tube, 2 is a pulse tube 1
It is a heat storage device communicated with. Reference numeral 3 denotes a compressor cylinder communicating with the heat storage device 2, and a piston 4 is reciprocally supported in the compressor cylinder 3. Reference numeral 5 is a compression space formed by the upper surface of the piston 4 and the cylinder 3, and is in communication with the heat storage device 2. As a result, the compression space 5, the heat storage device 2 and the pulse tube 1 are communicated with each other to form a working space. A working gas is enclosed in the working space. Further, 6 is a heat storage device 2 of the pulse tube 1.
The buffer tank is connected to the opposite side via the orifice 7. The pulse tube 1 has a low temperature heat exchanger 8 at the end on the heat storage 2 side and a room temperature heat exchanger 9 at the end on the buffer tank 6 side. Further, the piston 4 is provided with a lightweight sleeve 11 made of a non-magnetic and non-magnetizable material such as aluminum in the buffer space 10 below the piston 4. A conductor is wound around the sleeve 11, and the wound conductor forms the coil 12. Coil 12
Is provided in the annular gap 13 so as to be vertically movable (axial direction). An armature magnetic field (permanent magnetic field) exists in the annular gap 13, and the force lines of the armature magnetic field extend in the direction (radial direction) transverse to the moving direction of the coil 12. In this case, the permanent magnetic field is obtained by the annular permanent magnet 14 and the yoke 15 which have magnetic poles on the outer and inner sides. Ring permanent magnet 1
4 and the yoke 15 integrally form a closed magnetic circuit (that is, a closed magnetic force line circuit). The sleeve 11, the coil 12, the annular gap 13, the annular permanent magnet 14, and the yoke 1 described above.
Reference numeral 5 constitutes a piston driving linear motor 16 as a whole. The piston 4 is reciprocally provided in the cylinder 3 via a spring 17, and the spring 17 serves as a piston 4.
Set the fixed position when the vehicle is stationary and the neutral position when driving.

Next, the operation of the conventional pulse tube refrigerator will be described. When an alternating current equal to the resonance frequency of the system is passed through the coil 12, the alternating current and the radial magnetic field produced by the annular permanent magnet 14 interact with each other to cause a periodic Lorentz force on the coil 12 in the axial direction. As a result, the system including the piston 4 and the spring 17 is brought into a resonance state, and the piston 4 vibrates in the axial direction. The vibration of the piston 4 causes a periodic pressure change in the working gas enclosed in the working space composed of the compression space 5, the heat storage device 2, and the pulse tube 1.

FIG. 21 is a diagram showing the cooling characteristics when the stroke and operating frequency of the piston 4 of the conventional pulse tube refrigerator shown in FIG. 20 are constant. In the figure, the vertical axis represents the temperature of the low temperature heat exchanger 8 when there is no load, and the horizontal axis represents the opening of the orifice 7. As is clear from this figure, the larger the opening of the orifice 7, the lower the temperature of the low temperature heat exchanger 8. Further, the larger the volume Vb of the buffer tank 6, the lower the temperature of the low temperature heat exchanger 8. Therefore,
When the vibration of the piston 4 causes a periodic pressure change in the working gas enclosed in the working space composed of the compression space 5, the heat storage device 2 and the pulse tube 1, when the opening degree of the orifice 7 is appropriately set, The low temperature heat exchanger 8 is cooled to an extremely low temperature.

The principle will be described below with reference to FIGS. 22 and 23. 22 (a) to 22 (d) are views for explaining the cooling operation of the conventional pulse tube refrigerator. In the figure, 18 is a boundary virtually set for the working gas in the pulse tube 1, and it is assumed that the working gas in the boundary 18 undergoes adiabatic change. This working gas forms the adiabatic gas piston 19 while being enclosed in the boundary 18. When the orifice 7 is appropriately opened, an appropriate phase difference is generated between the pressure fluctuation of the working gas in the pulse tube 1 and the movement of the working gas flowing in and out of the buffer tank 6 via the orifice 7.

In the process of FIG. 22 (a) to (b),
The piston 4 rises from the bottom dead center position. Therefore, the working gas in the compression space 5 is compressed and flows into the heat storage device 2. The working gas flowing into the heat storage device 2 is pre-cooled by the cold heat stored in the heat storage device 2 half a cycle before, and flows into the low temperature side space 20 in the pulse tube 1 via the low temperature heat exchanger 8. As a result, the pressure of the working gas that has flowed in rises, so that the adiabatic gas piston 19 rises and the pulse tube 1
The room temperature space 21 therein is smaller than that in FIG. 22A, and the low temperature space 20 is larger than that in FIG. 22A.

Next, in the strokes of FIGS. 22 (b) to 22 (c), the working gas in the room temperature space 21 in the pulse tube 1 remains in the position of the top dead center and the working gas in the room temperature space 21 has the room temperature heat exchanger 9 and the orifice. It flows into the buffer tank 6 via 7.
Therefore, the pressure of the working gas in the room temperature space 21 is lowered and the adiabatic gas piston 19 moves upward from FIG. 22 (b).
22 (b), the low temperature space 20 becomes larger than FIG. 22 (b).

Next, in the strokes of FIGS. 22 (c) to 22 (d), since the piston 4 descends from the position of the top dead center, part of the working gas in the low temperature space 20 in the pulse tube 1 is in the low temperature heat exchanger 8. And then flows into the heat storage device 2. The working gas flowing into the heat storage device 2 flows into the compression space 5 while applying cold heat to the heat storage device 2. Therefore, the room temperature space 21 in the pulse tube 1 is larger than that in FIG. 22C, and the low temperature space 20 is smaller than that in FIG. 22C.

Subsequently, in the strokes of FIGS. 22D to 22A, the working gas in the buffer tank 6 passes through the orifice 7 and the room temperature heat exchanger 9 while the piston 4 remains at the bottom dead center position. It flows into the room temperature space 21 in the pulse tube 1. Therefore, the pressure of the working gas in the room temperature space 21 rises, so that the room temperature space 21 in the pulse tube 1 is not heated.
It is larger than (d), and the low temperature space 20 is smaller than that in FIG. 22 (d).

FIG. 23 shows the above process as a P-V diagram. 23A is a P-V diagram of the low temperature space 20 in the pulse tube 1, and FIG. 23B is a P-V diagram of the gas piston 19 in the pulse tube 1.
(C) is a P-V diagram of the room temperature space 21 in the pulse tube 1. 23A to 23C, states I and I
I, III and state IV are shown in FIG. 22 (a) and FIG. 22 respectively.
It corresponds to (b), FIG. 22 (c) and FIG. 22 (d). As is clear from these figures, the low temperature space 20 in the pulse tube 1 performs expansion work, the gas piston 19 in the pulse tube 1 performs reversible adiabatic work, and the room temperature space 21 in the pulse tube 1 performs compression work. Then, cold heat is generated by the expansion work in the low temperature space, and the low temperature heat exchanger 8
Is taken out as cold heat from.

FIG. 24 is shown in, for example, a document "Generation of 30K to 20K Region by Pulse Tube Refrigerator" (Author: Yoshihiro Ishizaki, Takayuki Matsui, Journal Name: 47th Annual Conference of Low Temperature Engineering Superconductivity Society, 1992). It is sectional drawing which shows the other Example of the conventional pulse tube refrigerator disclosed. In the figure, 29 is a connecting rod, and the connecting rod 29 connects the piston 4 and the pin 30 fixed to the crank arm 31. 32 is a crankshaft. Then, the connecting rod 29, the pin 30, the crank arm 31, the crank shaft 3
Reference numeral 2 constitutes a crank mechanism 33. Reference numeral 50 denotes an expander cylinder, and an expansion piston 51 is reciprocally supported in the expander cylinder 50. Reference numeral 52 is an expansion space, and the expansion space 52 is communicated with the pulse tube 1 via a communication pipe 22. 53 is a connecting rod, and the connecting rod 53 connects the expansion piston 51 and the pin 54 fixed to the crank arm 55. Reference numeral 56 is a crankshaft. Then, the connecting rod 53, the pin 54,
The crank arm 55 and the crank shaft 56 are the crank mechanism 5.
Make up 7.

Next, the operation of another embodiment of the conventional pulse tube refrigerator will be described. First, a rotation motor (not shown) is driven to rotate the crankshaft 32 and the crankshaft 56 with a constant phase difference. As a result, the piston 4 and the expansion piston 51 move with a constant phase difference, so that the working gas enclosed in the working space composed of the compression space 5, the heat storage device 2, the pulse tube 1, and the expansion space 52 is periodically pressurized. Change. In this case, in the pulse tube 1, the low temperature heat exchanger 8 is cooled to an extremely low temperature by the operation of the working gas similar to the conventional embodiment shown in FIG. And FIG.
In the case of the embodiment shown in FIG. 4, the phase difference and stroke of the adiabatic gas piston 19 and the piston 4 can be controlled arbitrarily. FIG. 25 is a diagram showing the relationship between the phase difference between the adiabatic gas piston 19 and the piston 4 and the cooling performance, and as is clear from the figure, there is an optimum phase difference. Therefore, the conventional pulse tube refrigerator shown in FIG. 24 has higher cooling performance than the conventional pulse tube refrigerator shown in FIG.

[0013]

Since the conventional pulse tube refrigerator is constructed as described above, the buffer tank 6 for the working gas is required, and the buffer tank 6 is required to obtain high cooling performance. It is necessary to increase the capacity. Therefore, there is a problem that the pulse tube refrigerator becomes large in size.

Further, in order to obtain higher cooling performance, as shown in FIG. 24, in addition to the compressor, an expansion piston 51 and a crank mechanism for driving the expansion piston 51 are required on the side of the pulse tube at the room temperature heat exchanger. . Therefore, there is a problem that the pulse tube refrigerator becomes large in size.

The present invention has been made to solve the above problems, and provides a compact and high performance pulse tube refrigerator without the need for a buffer tank or a crank mechanism for driving an expansion piston. Is intended.

[0016]

According to another aspect of the pulse tube refrigerator of the present invention, one end of the pulse tube is provided in the heat storage device via a low temperature heat exchanger that generates cold heat. The end is provided in the room temperature heat exchanger. The compressor includes a piston slidably supported in a cylinder and a compression chamber formed by the cylinder, and the compressor further includes drive means for reciprocating the piston. Further, the compressor is provided with a buffer chamber whose volume changes in inverse proportion to the volume change of the compression chamber. The first communication tube communicates the compression chamber with the pulse tube via the heat storage device and the low temperature heat exchanger. Then, the second communication pipe communicated the buffer chamber with the pulse tube through the room temperature heat exchanger. This allows the working gas to flow between the buffer chamber and the compression chamber via the pulse tube.

In the pulse tube refrigerator according to the second aspect of the invention, a linear motor is used as the driving means of the compressor, and the piston is slid by the linear motor. Furthermore, in the pulse tube refrigerator according to the invention of claim 3, a crank mechanism is used as a driving means of the compressor, and the piston is slid by the crank mechanism.

In the pulse tube refrigerator according to the invention of claim 4, the buffer chamber and the room temperature heat exchanger are provided with the orifice valve capable of adjusting the opening ratio through the second communicating pipe. Further, in the pulse tube refrigerator according to the invention of claim 5, a pair of pistons that reciprocate with a predetermined phase difference are provided on the compressor so as to be coaxially opposed to each other, and a compression chamber is formed between the pair of pistons. , Forming first and second buffer chambers whose volume change changes in inverse proportion to the volume change of the compression chamber, and further connecting the compression chamber to one end of the pulse tube via a heat storage device and a low temperature heat exchanger, Moreover, one of the first and second buffer chambers is connected to the other end of the pulse tube via the second communication tube.

Further, in the pulse tube refrigerator according to the invention of claim 6, the first and second buffer chambers of the invention of claim 5 are communicated with each other. The pulse tube refrigerator according to the invention of claim 7 uses a linear motor as the driving means for the pair of pistons of the invention of claim 5, and the pair of pistons are slid by the linear motor.

Further, the pulse tube refrigerator according to the invention of claim 8 uses a crank mechanism as a driving means for the pair of pistons according to the invention of claim 5, and slides the pair of pistons by the crank mechanism. Is. Further, in the pulse tube refrigerator according to the invention of claim 9, an expansion piston is formed coaxially with the piston of the invention of claim 1, and the expansion chamber formed by the expansion piston is pulsed through the second communication pipe. It is connected to the tube.

In the pulse tube refrigerator according to the invention of claim 10, the expansion piston of the invention of claim 9 is coaxially connected to the piston via an elastic member.
In the pulse tube refrigerator according to the invention of claim 11, the communication portion between the heat storage device and the pulse tube is bent, and the heat storage device and the pulse tube are arranged in parallel.

Further, in the pulse tube refrigerator according to the twelfth aspect of the invention, the pulse tube is coaxially arranged outside the heat accumulator. The pulse tube refrigerator according to the thirteenth aspect of the present invention has a heat accumulator coaxially arranged on the outer periphery of the pulse tube.

The pulse tube refrigerator according to the fourteenth aspect of the present invention is provided with a third communication pipe that connects the first communication pipe and the second communication pipe. Further, in the pulse tube refrigerator according to the invention of claim 15, the expansion piston connected to the elastic member is slidably supported in the expansion cylinder, and the volume change with a predetermined phase difference with respect to the volume change of the compression chamber. The buffer chamber is provided with a buffer means formed of an expansion cylinder and an expansion piston, and the buffer chamber and the pulse tube are communicated with each other by a second communication pipe via a room temperature heat exchanger.

According to the sixteenth aspect of the pulse tube refrigerator, a pair of the piston and the expansion piston of the ninth or tenth aspect are provided in the compressor, respectively. In the pulse tube refrigerator according to the invention of claim 17, a pair of pistons according to claim 15 is provided in the compressor.

[0025]

In the pulse tube refrigerator according to the first aspect of the present invention, one end of the pulse tube is provided in the regenerator via the low temperature heat exchanger that generates cold heat, and the other end of the pulse tube is in the room temperature heat exchanger. It is provided. The compressor includes a piston slidably supported in a cylinder and a compression chamber formed by the cylinder, and the compressor further includes drive means for reciprocating the piston. Further, the compressor is provided with a buffer chamber whose volume changes in inverse proportion to the volume change of the compression chamber. The first communication tube communicates the compression chamber with the pulse tube via the heat storage device and the low temperature heat exchanger. The second communication pipe communicates the buffer chamber with the pulse tube via the room temperature heat exchanger so that the working gas flows between the buffer chamber and the compression chamber via the pulse tube. Therefore, since the buffer chamber corresponds to the conventional buffer tank, the buffer tank can be removed.

Further, in the pulse tube refrigerator according to the second aspect of the present invention, since the linear motor is used as the driving means of the compressor and the piston is reciprocated by this linear motor, the piston is smoothly moved in a straight line. be able to.

Further, in the pulse tube refrigerator according to the invention of claim 3, a crank mechanism is used as a driving means of the compressor, and the piston is slid by the crank mechanism. As a result, the phase difference and stroke between the adiabatic gas piston and the piston can be set arbitrarily.

In the pulse tube refrigerator according to the invention of claim 4, an orifice valve capable of adjusting the opening ratio is provided between the room temperature heat exchanger and the second communicating pipe. Therefore, the flow rate of the working gas can be easily adjusted.

Further, in the pulse tube refrigerator according to the invention of claim 5, a pair of pistons that reciprocate with a predetermined phase difference are provided in the compressor so as to coaxially face each other, and a compression chamber is formed between the pair of pistons. In addition, the first and second buffer chambers whose volume change changes in inverse proportion to the volume change of the compression chamber are formed, and the compression chamber communicates with one end of the pulse tube through the heat storage device and the low temperature heat exchanger. In addition, one of the first and second buffer chambers was communicated with the other end of the pulse tube via the second communication tube. In this way, the vibration of the compressor can be reduced by making the piston of the compressor two cylinders.

Further, in the pulse tube refrigerator according to the invention of claim 6, the first and second buffer chambers are communicated with each other. Also in this case, it is possible to reduce the vibration as in the fifth aspect. In the pulse tube refrigerator according to the invention of claim 7, a linear motor is used as a driving means for the pair of pistons, and the pair of pistons are reciprocally moved by the linear motor. Therefore, the pair of pistons can be smoothly linearly moved. be able to.

Further, in the pulse tube refrigerator according to the invention of claim 8, a crank mechanism is used as a driving means for the pair of pistons, and the pair of pistons are slid by this crank mechanism. The phase difference and stroke of the piston can be set arbitrarily.

Further, in the pulse tube refrigerator according to the invention of claim 9, an expansion piston is formed coaxially with the piston, and the expansion chamber formed by the expansion piston is connected to the other end of the pulse tube via the second communicating pipe. Communicated with. Therefore, it is possible to obtain a high cooling effect by removing the crank mechanism for the expansion piston, which has been conventionally required.

In the pulse tube refrigerator according to the invention of claim 10, the expansion piston is coaxially connected to the piston via a spring. Therefore, in addition to the operation of claim 9, the stroke of the expansion piston and the piston The phase difference with respect to can be controlled arbitrarily.

In the pulse tube refrigerator according to the invention of claim 11, the communication portion between the regenerator and the pulse tube is bent, and the regenerator and the pulse tube are arranged in parallel. Therefore, the height of the pulse tube refrigerator can be reduced.

Furthermore, in the pulse tube refrigerator according to the twelfth aspect of the invention, the pulse tube is coaxially arranged outside the heat accumulator. Therefore, the height of the pulse tube refrigerator can be reduced. In the pulse tube refrigerator according to the thirteenth aspect of the invention, the heat accumulator is coaxially arranged on the outer circumference of the pulse tube. Therefore, the height of the pulse tube refrigerator can be reduced.

Further, in the pulse tube refrigerator according to the fourteenth aspect of the invention, since the third communication pipe that connects the first communication pipe and the second communication pipe is arranged, a high cooling capacity can be obtained. . Further, in the pulse tube refrigerator according to the invention of claim 15, the expansion piston connected to the elastic member is slidably supported in the expansion cylinder, and the buffer chamber whose volume changes in inverse proportion to the volume change of the compression chamber is expanded. A buffer means formed of a cylinder and an expansion piston was provided, and the buffer chamber and the pulse tube were communicated with each other by a second communication pipe. Therefore, in addition to the effect of the ninth aspect, the stroke of the expansion piston and the phase difference with respect to the piston can be arbitrarily controlled.

In the pulse tube refrigerator according to the sixteenth aspect of the present invention, a pair of the piston and the expansion piston according to the ninth or tenth aspect are provided in the compressor. Therefore, the crank mechanism for the expansion piston can be removed to obtain a high cooling effect, and further the vibration can be reduced.

In the pulse tube refrigerator according to the invention of claim 17, a pair of pistons according to claim 15 is provided in the compressor. Therefore, the crank mechanism for the expansion piston can be removed to obtain a high cooling effect, and further the vibration can be reduced.

[0039]

【Example】

Example 1. An embodiment of the present invention will be described below with reference to the drawings. In Fig. 1, the same members as those of the conventional pulse tube refrigerator shown in Fig. 20 are designated by the same reference numerals and the description thereof will be omitted. In FIG. 1, 22 is a communication pipe that connects the room temperature heat exchanger 9 and the orifice 7, 23 is a communication pipe that connects the orifice 7 and the buffer space 10, and 24 is a communication pipe that connects the heat storage device 2 and the compression space 5. .

The operation of this embodiment will be described below.
When an alternating current equal to the resonance frequency of the system is passed through the coil 12, the alternating current and the radial magnetic field produced by the annular permanent magnet 14 interact with each other to cause a periodic Lorentz force on the coil 12 in the axial direction. Thereby, the piston 4 and the spring 1
The system composed of 7 is brought into resonance, and the piston 4 vibrates in the axial direction. The vibration of the piston 4 causes a periodic pressure change in the working gas enclosed in the working space composed of the compression space 5, the heat storage device 2, and the pulse tube 1.

In this state, when the opening degree of the orifice 7 is appropriately set, the working gas in the pulse tube 1 passes through the room temperature heat exchanger 9, the communicating pipe 22, the orifice 7 and the communicating pipe 23 to the inside of the pulse tube 1 and the buffer. It reciprocates between the spaces 10. In this case, since the volume of the buffer space 10 changes due to the vibration of the piston 4, the buffer space 10 includes the room temperature heat exchanger 9, the pulse tube 1, the low temperature heat exchanger 8, the heat storage device 2,
The same volume changes in the opposite phase with respect to the working space including the communication pipe 24 and the compression space 5. Therefore, the working gas in the working space can reciprocate through the orifice 7 between the working space and the buffer space 10 until the pressure fluctuation of the working gas in the working space is almost eliminated. By thus connecting the buffer space 10 and the pulse tube 1 to each other, it is possible to remove the buffer tank that has been conventionally required. Then, by appropriately opening the orifice 7, it is possible to generate cold heat in the low temperature heat exchanger 8 by the same operation as in the conventional pulse tube refrigerator.

Example 2. In the first embodiment, the case where the compressor has a single cylinder has been described, but the compressor may have two cylinders as in the second embodiment shown in FIG. The second embodiment will be described below with reference to FIG. 2, the same members as those of the pulse tube refrigerator of FIG. 1 are designated by the same reference numerals and the description thereof will be omitted. In FIG. 2, 3a and 4a are a first compressor cylinder and a first piston, respectively.
The first piston and the first piston are configured similarly to the compressor 3 and the piston 4 of the first embodiment. Further, 16a is a first linear motor, and the first linear motor 16a includes the first sleeve 11a, the first coil 12a, and the first annular gap 1
3a, the first annular permanent magnet 14a, the first yoke 15a
And is configured similarly to the linear motor 16 of the first embodiment. Further, 10a and 17a are the first buffer space and the first spring, respectively, which are the first embodiment.
Corresponding to the buffer space 10 and the spring 17.

Further, the pulse tube refrigerator of the second embodiment is equipped with the second compressor cylinder 36, the second piston 4a and the second linear motor 16b. These second
The compressor cylinder 3b, the piston 4b and the linear motor 16b are configured similarly to the first compressor cylinder 3a, the piston 4a and the linear motor 16a. Also, 1
Reference numerals 0b and 17b denote a second buffer space and a second spring, respectively, which are configured similarly to the first buffer space 10a and the first spring 17a. However, it differs from the first buffer space 10a in that the communication pipe 23 is not communicated with the second buffer space 10b.

Next, the operation will be described. In addition, the volume change of the compression space 5 and the first buffer space 10a based on the vibration of the first piston 4a is determined by the buffer space 1 of the first embodiment.
0 and the volume change of the buffer space 10 are set to be the same. Therefore, the operation of generating cold heat in the low-temperature heat exchanger 8 is the same as that in the first embodiment, and therefore the description thereof is omitted, and the volume change of the compression space 5 based on the movement of the first and second pistons 4a and 4b will be described.

First, assuming that the motion of the first piston 4a and the second piston 4b is a sine wave and the phase difference between them is α, the change in the volume Vc of the compression space 5 is expressed by the following equation.

Vc = V1 {1-sin (θ)} / 2 + V2 {1-sin (θ−α)} / 2 (1) Vc: Volume of the compression space 5 V1: Compression by the first piston 4a Volume change of space 5 V2: Volume change of compression space 5 by the second piston 4b θ: Crank angle α: Phase difference

Equation (1) can be rewritten as follows.

Vc = (V1 + V2) / 2−Asin (θ + β) (2) A: Constant β: Phase difference of volume change of the compression space 5 with respect to the movement of the first piston 4a.

A and β are respectively expressed by the following equations.

A = {[V1 + V2cos (α)] ² + [V2sin (α)] ² } ^0.5 / 2 (3)

Β = −tan ⁻¹ [(V2sin (α)) / (V1 + V2cos (α))] (4)

On the other hand, the pulse tube 1 is connected to the first
The volume change of the buffer space 10a is expressed by the following equation.

Vb = Vb0 + V1 {1 + sin (θ)} / 2 (5) Vb: Volume of the first buffer space 10a Vb0: Dead volume of the first buffer space 10a

From the equations (1) to (5), the first piston 4
Volume change V1 of compression space 5 due to a and second piston 4
volume change V2 of the compression space 5 due to b and their phase difference α
By appropriately changing, the phase difference β of the volume change between the compression space 5 and the first buffer space 10a can be controlled arbitrarily. As a result, the volume changes of the compression space 5 and the first buffer space 10a become similar to those in the first embodiment, and cold heat is generated in the low temperature heat exchanger 8 as in the first embodiment. In addition, by using a pair of pistons 4a and 4b to form two cylinders,
The vibration of the pulse tube refrigerator can be reduced.

Example 3. Although the first buffer space 10a and the second buffer space 10b are shielded in the second embodiment, the first buffer space 10a and the second buffer space 10b communicate with each other as in the third embodiment shown in FIG. Tube 43
May be communicated with each other via.

Example 4. Next, a fourth embodiment of the present invention will be described with reference to FIG. 4, the same members as those of the pulse tube refrigerator of FIG. 1 are designated by the same reference numerals and the description thereof will be omitted. In FIG. 4, 34a and 34b are shown in FIG.
Is a spring having the same function as the spring 17 in FIG. 1, 58 is an expander cylinder, and 59 is an expansion piston. The expansion piston 59 is formed coaxially with the piston 4 and is supported in the expander cylinder 58 so as to be reciprocally movable. Reference numeral 60 is an expansion chamber, and 61 is a communication pipe that connects the orifice 7 and the expansion chamber 60.

Next, the operation will be described. The expansion piston 59 moves in unison with the piston 4 of the compressor. Therefore, the pulse tube refrigerator of the fourth embodiment corresponds to the case where the phase difference between the two pistons 4, 51 of the other embodiment of the conventional pulse tube refrigerator shown in FIG. 24 is 180 °. Thereby, in the pulse tube refrigerator of the fourth embodiment, cold heat is generated in the low temperature heat exchanger 8 by the same operation as the other conventional embodiments. The pulse tube refrigerator of the fourth embodiment is the same as that of the first embodiment.
It has higher cooling performance than that of the pulse tube refrigerator.

Example 5. A fifth embodiment of the present invention will be described based on FIG. 5, the same members as those of the pulse tube refrigerator of FIG. 4 are designated by the same reference numerals and the description thereof will be omitted. In FIG. 5, 62 is the expansion piston 5
9 is a spring connected to the piston 4, and the expansion piston 59 and the piston 4 are coaxially supported.

Next, the operation will be described. In the fifth embodiment, if the operations of the piston 4 and the expansion piston 59 are similar to those of the fourth embodiment of FIG. 4, the operation of generating cold heat in the low temperature heat exchanger 8 is also the same as that of the fourth embodiment, and therefore the description thereof is omitted. Two
The operation of the two pistons 4, 59 will be described.

It is now assumed that the piston 4 is forcibly moved by the linear motor 16 in a sinusoidal motion represented by the following equation.

X _c = X _c0 sin (ωt) (6) X _c : Position of piston 4 X _c0 : Motion amplitude of piston 4 t: Time ω: Operating frequency

On the other hand, FIG. 6 is an explanatory diagram for explaining the movement of the expansion piston 59. In the figure, 64 is the piston 4, 65 is the expansion piston 59, 66 is the compressor cylinder 3, and 67 is the spring. Reference numerals 62 and 68 correspond to damping acting on the expansion piston. At this time, the equation of motion of the expansion piston 59 is expressed by the following equation.

[0063] ^{_{m e (d 2 X e /}} dt 2) + C e (dx e / dt) + k e (X e -X c) = 0 ‥‥‥ (7) C e: attenuation k acting on the expansion piston 59 _e: spring constant m _e of the spring 62: the mass of the expansion piston 59 X _e: position Thus, movement of the expansion piston 59 of the expansion piston 59 is represented by the following formula,

X _e = X _e0 sin (ωt−α) (8) X _e0 : amplitude of expansion piston 59 α: phase difference Here, X _e0 and α are represented by the following equations, respectively.

X _e0 = [k _e / (-m _e ω ² cos α-C _e sin α + k _e cos α)] X _c0 (9)

[0066] _{tanα = C e / (m e} ω 2 -k e) ‥‥‥ (10)

From equations (8), (9) and (10), the piston 4 is driven by the linear motor 16 and the mass m _e of the expansion piston 59 and the spring constant k _e of the spring 62 are set appropriately. Stroke of expansion piston 59 and piston 4
The phase difference with respect to can be controlled arbitrarily. Therefore, cold heat is generated in the low temperature heat exchanger 8 as in the fourth embodiment.

Example 6. Next, a sixth embodiment of the present invention will be described with reference to FIG. 7, the same members as those of the pulse tube refrigerator of FIG. 1 are designated by the same reference numerals and the description thereof will be omitted. In FIG. 7, 64 is a reaction chamber, and 69 is a spring connected to the expansion cylinder 58 and the expansion piston 59.

Next, the operation will be described. If the operations of the piston 4 and the expansion piston 59 in the sixth embodiment are the same as those in the fourth embodiment, the operation of generating cold heat in the low temperature heat exchanger 8 is the same, and therefore the description thereof is omitted and the two pistons 4, The operation of 59 will be described.

First, in the pulse tube refrigerator of the sixth embodiment, it is assumed that the piston 4 is forcibly moved by the linear motor 16 in the sinusoidal motion represented by the equation (6), as in the fourth embodiment.

FIG. 8 is an explanatory view for explaining the movement of the expansion piston 59. In the figure, 70 is the expansion piston 59, 71 is the expander cylinder 58, and 72 is the spring 69.
Further, reference numeral 73 corresponds to the damping acting on the expansion piston, and 74 is the exciting force F acting on the expansion piston 59 due to the fluctuation of the working gas pressure. At this time, the equation of motion of the expansion piston 59 is expressed by the following equation.

M _e (d ² X _e / dt ² ) + C _e (dX _e / dt) + k _e X _e = F (11) F: Exciting force acting on the expansion piston 59

The motion of the expansion piston 59 is thus represented by simple forced vibration with one degree of freedom. The working gas pressure fluctuation is generated by the movement of the piston 4, so that the working gas pressure fluctuation also becomes a sine wave, and the exciting force F is assumed to be a sine wave and is expressed by the following equation.

F = F ₀ sin ωt (12) F ₀ : Amplitude of Excitation Force F The amplitude X _e0 and the phase difference α with respect to the excitation force F are respectively expressed by the following equations.

X _e0 = (F ₀ / k _e ) / ([{1- (ω / ω _n ) ² } ² + (2ζω / ω _n ) ² ] ^0.5 ) (13)

Tan α = (2ζω / ω _n ) / [1- (ω / ω _n ) ² ] ... (14)

Ω _n = (k / m _e ) ^0.5 (15)

Ζ = C _e / [2 (m _e k _e ) ^0.5 ] (16)

Here, ω _n is the natural frequency of the motion of the expansion piston 59, and ζ is the damping ratio. Expansion piston 5
The amplitude X _e0 and the phase difference α of 9 are shown in FIGS. 9A and 9B, respectively. Here, the phase difference α (excitation force F, that is, the phase difference with respect to the pressure fluctuation of the working gas) is shown in FIG.
As is clear from (b), the mass m of the expansion piston 59
The spring constant k _e of _e and the spring 72 by appropriately adjusting,
The strokes and phase differences of the piston 4 and the expansion piston 59 can be controlled arbitrarily. Therefore, cold heat can be generated in the low-temperature heat exchanger 8 as in the fourth embodiment.

Example 7. In Example 1 shown in FIG. 1, the heat storage device 2 is coaxially arranged at the lower end of the pulse tube 1 via the low temperature heat exchanger 8, but the present invention is not limited to this, and as in Example 7 shown in FIG. The pulse tube 1 may be provided in a state of being bent from the low temperature heat exchanger 8. In this case, the seventh embodiment has the same effect as the first embodiment.

Example 8. Further, as shown in FIG. 11, the low temperature heat exchanger 8 may be provided on the upper end of the pulse tube 1, and the heat accumulator 2 may be provided on the outer periphery of the pulse tube 1. In this case, the same effect as that of the first embodiment is achieved by connecting the lower end of the pulse tube 1 to the buffer space 10 via the room temperature heat exchanger 9 and the orifice 7.

Example 9. Furthermore, as shown in FIG. 12, the heat storage device 2 is disposed inside the pulse tube 1, and
By connecting the lower end of the pulse tube 1 to the buffer space 10 via the room temperature heat exchanger 9 and the orifice 7, the same effect as that of the first embodiment is achieved.

Example 10. In addition, FIG. 1, FIG.
1, the compression space 5 in the embodiments 1, 7, 8, and 9 shown in FIG.
And the volume of the buffer space 10 are correspondingly changed, and the pulse tube 1 is further connected to the buffer space 10 through the room temperature heat exchanger 9, the orifice 7 and the communication pipe 23. 13 to 16, the working gas space between the room temperature heat exchanger 9 and the orifice 26 and the working gas space between the heat accumulator 2 and the compression space 5 are connected by the communication pipes 25 and 27 and the orifice 26. A double inlet type pulse tube refrigerator may be connected to communicate with each other.

Next, the operation will be described. In the tenth embodiment, the operation of generating cold heat in the low temperature heat exchanger 8 is the same as in the first embodiment.
This is basically the same as in the case of the above, and the document "Pulse tube refrigerator using linear compressor (2) -Pulse tube performance-" (Author: Hiroshi Yata et al., Journal name: The 46th Society of Low Temperature Engineering Superconductivity Society Lecture Summary Shu, 1991)
The double inlet type has the effect of further increasing the cooling performance.

Example 11. Although the linear motor 16 is used for the drive mechanism of the piston 4 in the first embodiment shown in FIG. 1, a crank mechanism 33 may be used instead of the linear motor 16 as shown in FIG. Also in this case, the same effect as that of the first embodiment is obtained. In the figure, 28 is a pin fixed to the piston 4, 29 is a connecting rod connecting the pin 28 and a pin 30 fixed to a crank arm 31, and 32 is a crankshaft. The pin 28, connecting rod 29, pin 30, crank arm 31, and crank shaft 32 form a crank mechanism 33. Crank mechanism 3
When the crankshaft 32 is rotationally driven by a rotary motor (not shown), the piston 3 reciprocates in the cylinder 3 to achieve the same effect as that of the first embodiment.

Example 12 In the second embodiment, the case where the linear motors 16a and 16b are used for the drive mechanism of the first piston 4a and the second piston 4b is shown. However, as shown in FIG. 18, instead of the linear motors 16a and 16b, cranks are used. A mechanism may be used. In this case, the same effect as that of the second embodiment is obtained. In the figure, 33a and 33b are respectively first and second crank mechanisms, and the first and second crank mechanisms 33a and 33b are the crank mechanisms 33 shown in FIG.
Is configured similarly to. The first crank mechanism 33a includes a pin 28a, a connecting rod 29a, a pin 30a, a crank arm 31a, and a crank shaft 32a. When the crank shaft 32a is rotated by a rotary motor (not shown), the first piston 4a moves to the first piston 4a. 1 compressor cylinder 3
Reciprocate in a. In addition, the second crank mechanism 33b
Is composed of a pin 28b, a connecting rod 29b, a pin 30b, a crank arm 31b and a crank shaft 32b. When the crank shaft 32b is rotated by a rotary motor (not shown), the second piston 4b causes the second compressor cylinder 3 to rotate.
Reciprocate in b. As a result, the second embodiment shown in FIG.
Has the same effect as.

Example 13 Although the first buffer space 10a and the second buffer space 10b are shielded in the twelfth embodiment, the first buffer space 10a and the second buffer space 10b communicate with each other as in the thirteenth embodiment shown in FIG. They may be communicated with each other via the pipe 43. Also in this case, the same effect as that of the twelfth embodiment can be obtained.

Example 14 In addition, in Examples 1 to 13,
The case where an orifice valve with a variable opening is used for the orifice 7 has been shown, but an orifice with a constant opening or a capillary tube may be used, and the same effect can be obtained without the orifice.

Example 15. Further, in the fourth and fifth embodiments, the case where each of the pistons 4 and 59 is one short cylinder has been shown, but a pair of pistons 4 and 59 may be provided so as to oppose the two cylinders as shown in the second embodiment. In this case, high cooling capacity can be obtained as in the case of Examples 4 and 5, and further low vibration can be obtained.

Example 16. Further, in the sixth embodiment, the case where the number of pistons is one is shown as a short cylinder, but a two-cylinder opposed type piston as shown in the second embodiment may be provided. In this case, as in the case of the sixth embodiment, a high cooling capacity can be obtained, and the vibration can be further reduced.

[0091]

As described above, according to the invention of claim 1, the compressor is provided with the piston slidably supported in the cylinder and the compression chamber formed by the cylinder,
The compressor is provided with a buffer chamber whose volume changes in inverse proportion to the volume change of the compression chamber. The first communication pipe communicates the compression chamber with the pulse tube via the heat storage device and the low temperature heat exchanger, and the second communication pipe communicates the buffer chamber with the pulse tube via the room temperature heat exchanger. Since the working gas is configured to flow between the buffer chamber and the compression chamber via the pulse tube, it is possible to remove the buffer tank that has been conventionally required. Therefore, the pulse tube refrigerator can be downsized.

Further, according to the invention of claim 2, since the linear motor is used as the driving means of the compressor, the piston is reciprocated by the linear motor to smoothly move the piston on a straight line. Vibration due to piston movement can be reduced.

Further, according to the third aspect of the present invention, since the crank mechanism is used as the drive means of the compressor, the phase difference and stroke of the adiabatic gas piston and the piston can be set arbitrarily. Therefore, a desired cooling capacity can be obtained.

Further, according to the invention of claim 4, since the orifice valve capable of adjusting the opening ratio is provided between the room temperature heat exchanger and the second communication pipe, the flow rate of the working gas can be easily adjusted. It can be carried out. Therefore, the orifice valve can be adjusted to obtain the optimum cooling capacity.

According to the invention of claim 5, a pair of pistons which reciprocate with a predetermined phase difference are provided on the compressor so as to coaxially face each other to form a compression chamber between the pair of pistons, and The first and second buffer chambers whose volume change changes in inverse proportion to the volume change of the compression chamber were formed. Further, the compression chamber is connected to one end of the pulse tube via the heat storage device and the low temperature heat exchanger, and one of the first and second buffer chambers is connected to the other end of the pulse tube via the second communication pipe. Connected to the end. Since the piston of the compressor has two cylinders in this way, low vibration can be achieved.

Furthermore, according to the invention of claim 6,
Since the second buffer chambers are configured to communicate with each other, low vibration can be achieved.

According to the invention of claim 7, since the linear motor is used as the driving means for the pair of pistons, the linear motor reciprocates the pair of pistons to smoothly move the pair of pistons linearly. It can be moved to reduce vibration.

Further, according to the invention of claim 8, since the crank mechanism is used for the driving means of the pair of pistons, the phase difference and stroke of the adiabatic gas piston and the pair of pistons can be arbitrarily set. You can Therefore,
Optimal cooling capacity can be obtained.

Further, according to the invention of claim 9, an expansion piston is formed coaxially with the piston, and the expansion chamber formed by the expansion piston is communicated with the other end of the pulse tube through the second communication tube. With this configuration, the crank mechanism for the expansion piston can be removed and a high cooling effect can be obtained. Therefore, a high-performance and compact pulse tube refrigerator can be obtained.

According to the invention of claim 10, since the expansion piston is configured to be coaxially connected to the piston via the elastic member, in addition to the effect of claim 9, the stroke of the expansion piston and the piston The phase difference can be controlled arbitrarily. Therefore, the optimum cooling capacity can be obtained.

According to the eleventh aspect of the invention, since the communication portion between the heat storage device and the pulse tube is bent and the heat storage device and the pulse tube are arranged in parallel, the pulse tube refrigerator The height of can be lowered. Therefore, the pulse tube refrigerator can be made compact.

Further, according to the twelfth aspect of the invention, since the pulse tube is arranged coaxially outside the heat accumulator, the height of the pulse tube refrigerator can be reduced. Therefore, the pulse tube refrigerator can be made compact.

According to the thirteenth aspect of the invention, since the heat accumulator is coaxially arranged on the outer circumference of the pulse tube, the height of the pulse tube refrigerator can be reduced. Therefore, the pulse tube refrigerator can be made compact.

According to the fourteenth aspect of the invention, since the third communication pipe that connects the first communication pipe and the second communication pipe is arranged, the cooling performance can be improved. . Therefore, a compact and high-performance pulse tube refrigerator can be obtained.

Further, according to the fifteenth aspect of the invention, the expansion piston connected to the elastic member is slidably supported in the expansion cylinder, and the buffer chamber whose volume changes in inverse proportion to the volume change of the compression chamber is expanded. Since the buffer means formed by the cylinder and the expansion piston is provided, and the buffer chamber and the pulse tube are connected by the second communication pipe, the crank mechanism for the expansion piston is removed, and a high cooling effect is obtained. Obtainable. Further, the stroke of the expansion piston and the phase difference with respect to the piston can be controlled arbitrarily. Therefore, a high-performance and compact pulse tube refrigerator can be obtained.

According to the sixteenth aspect of the present invention, since the piston and the expansion piston of the ninth or tenth aspect are provided in the compressor respectively, a crank mechanism for the expansion piston, which is conventionally required. Can be removed to obtain a high cooling effect, and further low vibration can be achieved.

Further, according to the seventeenth aspect of the invention, since the pair of pistons of the fifteenth aspect is provided in the compressor, the crank mechanism for the expansion piston, which has been conventionally required, is eliminated to achieve a high cooling effect. In addition, it is possible to obtain low vibration.

[Brief description of drawings]

FIG. 1 is a first embodiment of a pulse tube refrigerator according to the present invention.
FIG.

FIG. 2 is a second embodiment of the pulse tube refrigerator according to the present invention.
FIG.

FIG. 3 is a third embodiment of the pulse tube refrigerator according to the present invention.
FIG.

FIG. 4 is a fourth embodiment of the pulse tube refrigerator according to the present invention.
FIG.

FIG. 5 is a fifth embodiment of the pulse tube refrigerator according to the present invention.
FIG.

FIG. 6 is a fifth embodiment of the pulse tube refrigerator according to the present invention.
It is an explanatory view for explaining the operation of.

FIG. 7 is a sixth embodiment of the pulse tube refrigerator according to the present invention.
FIG.

FIG. 8 is a sixth embodiment of the pulse tube refrigerator according to the present invention.
It is explanatory drawing explaining the operation | movement of.

9 (a) is an explanatory diagram illustrating the amplitude (X _e0 ) of the expansion piston of the sixth embodiment, and FIG. 9 (b) illustrates the phase difference (α) of the expansion piston of the sixth embodiment. FIG.

FIG. 10 is a sectional view of a pulse tube refrigerator according to a seventh embodiment of the present invention.

FIG. 11 is a sectional view of an eighth embodiment of the pulse tube refrigerator according to the present invention.

FIG. 12 is a sectional view of a pulse tube refrigerator according to a ninth embodiment of the present invention.

FIG. 13 is a sectional view of a pulse tube refrigerator according to a tenth embodiment of the present invention.

FIG. 14 is a sectional view of a pulse tube refrigerator according to a tenth embodiment of the present invention.

FIG. 15 is a sectional view of a pulse tube refrigerator according to a tenth embodiment of the present invention.

FIG. 16 is a sectional view of a pulse tube refrigerator according to a tenth embodiment of the present invention.

FIG. 17 is a sectional view of an eleventh embodiment of a pulse tube refrigerator according to the present invention.

FIG. 18 is a sectional view of a twelfth embodiment of the pulse tube refrigerator according to the present invention.

FIG. 19 is a sectional view of a pulse tube refrigerator according to a thirteenth embodiment of the present invention.

FIG. 20 is a sectional view of a conventional pulse tube refrigerator.

FIG. 21 is a graph illustrating the relationship between the temperature of a low temperature heat exchanger of a conventional pulse tube refrigerator when there is no load and the opening of the orifice.

22 (a) to 22 (d) are explanatory views for explaining the operation of the conventional pulse tube refrigerator.

23 (a) to 23 (c) are views for explaining the relationship between pressure and volume of a conventional pulse tube refrigerator, respectively.
It is a V diagram.

FIG. 24 is a cross-sectional view of another embodiment of the conventional pulse tube refrigerator.

FIG. 25 is an explanatory diagram illustrating the relationship between the phase difference and the cooling performance of another example of the conventional pulse tube refrigerator.

[Explanation of symbols]

 1 pulse tube 2 heat accumulator 3 compressor cylinder 3a first compressor cylinder 3b second compressor cylinder 4 piston 4a first piston 4b second piston 5 compression space (compression chamber) 7 orifice 8 low temperature heat exchanger 9 Room temperature heat exchanger 10 Buffer space (buffer chamber) 10a 1st buffer space (1st buffer chamber) 10b 2nd buffer space (2nd buffer chamber) 16 Linear motor 16a 1st linear motor 16b 2nd Linear motors 22 to 24, 25, 27, 43, 61 communication pipe 33 crank mechanism 33a first crank mechanism 33b second crank mechanism 59 expansion piston 60 expansion chamber 61 communication pipe

Claims (17)

[Claims] 1. A pulse tube having a heat accumulator at one end and a room temperature heat exchanger at the other end via a low-temperature heat exchanger for generating cold heat, and a piston slidably supported in a cylinder. And a compressor having a compression chamber formed by the cylinder, a drive unit for reciprocating the piston, and a buffer chamber that changes in volume in inverse proportion to a change in volume of the compression chamber; And a first communication pipe that communicates the compression chamber with the pulse tube via the low temperature heat exchanger, and the normal temperature heat exchanger so that the working gas flows between the buffer chamber and the compression chamber via the pulse tube. A pulse tube refrigerator, comprising: a second communication pipe that connects the buffer chamber and the pulse tube via the. 2. A pulse tube having a heat accumulator at one end and a room temperature heat exchanger at the other end via a low temperature heat exchanger for generating cold heat, and a piston slidably supported in the cylinder. And a compressor having a compression chamber formed of the cylinder and having a linear motor that reciprocates the piston, and a buffer chamber that changes in volume in inverse proportion to a change in volume of the compression chamber; A first communication pipe that communicates the compression chamber and the pulse tube via a container and a low-temperature heat exchanger, so that the working gas flows between the buffer chamber and the compression chamber via the pulse tube,
A pulse tube refrigerator, comprising: a second communication tube that connects the buffer chamber and the pulse tube via the room temperature heat exchanger. 3. A pulse tube having a heat accumulator at one end and a room temperature heat exchanger at the other end via a low temperature heat exchanger for generating cold heat, and a piston slidably supported in the cylinder. And a compressor having a compression chamber formed by the cylinder and having a crank mechanism that reciprocates the piston, and a buffer chamber that changes in volume in inverse proportion to a change in volume of the compression chamber, and the heat storage unit. And a first communication pipe that communicates the compression chamber with the pulse tube via the low temperature heat exchanger, and the normal temperature heat exchanger so that the working gas flows between the buffer chamber and the compression chamber via the pulse tube. A pulse tube refrigerator, comprising: a second communication pipe that connects the buffer chamber and the pulse tube via the. 4. A pulse tube having a heat accumulator at one end and a room temperature heat exchanger at the other end via a low temperature heat exchanger for generating cold heat, and a piston slidably supported in the cylinder. And a compressor having a compression chamber formed by the cylinder, a drive unit for reciprocating the piston, and a buffer chamber that changes in volume in inverse proportion to a change in volume of the compression chamber; And a first communication pipe that communicates the compression chamber with the pulse tube via the low temperature heat exchanger, and the normal temperature heat exchanger so that the working gas flows between the buffer chamber and the compression chamber via the pulse tube. A second communication pipe that communicates the buffer chamber with the pulse tube via a valve, and an orifice valve that is provided between the buffer chamber and the room temperature heat exchanger via the second communication pipe and has an adjustable opening ratio. A pulse tube refrigerator, which is equipped with a tube. 5. A pulse tube having a heat accumulator provided at one end and a room temperature heat exchanger provided at the other end via a low temperature heat exchanger for generating cold heat, and slidably opposed to and supported in a cylinder. A compression chamber formed between the pair of pistons, and a drive means for reciprocating the pair of pistons with a predetermined phase difference; and a volume change in inverse proportion to a volume change of the compression chamber. , A compressor provided with a second buffer chamber, a first communication pipe for communicating the compression chamber with a pulse tube via the heat accumulator and a low temperature heat exchanger, and a working gas with the pulse tube connected via a pulse tube. First and second
A second communication pipe for communicating the one buffer chamber with the pulse tube via the room temperature heat exchanger so as to flow between any one of the buffer chambers and the compression chamber. Pulse tube refrigerator. 6. A pulse tube having a heat accumulator provided at one end and a room temperature heat exchanger provided at the other end via a low temperature heat exchanger for generating cold heat, and slidably opposed to and supported in a cylinder. A compression chamber formed between the pair of pistons, and a drive means for reciprocating the pair of pistons with a predetermined phase difference; and a volume change in inverse proportion to a volume change of the compression chamber. , A compressor provided with a second buffer chamber, a first communication pipe for communicating the compression chamber with a pulse tube via the heat accumulator and a low temperature heat exchanger, and a working gas with the pulse tube connected via a pulse tube. First and second
Second buffer pipe for communicating the one buffer chamber with the pulse tube via the room temperature heat exchanger so as to flow between any one of the buffer chambers and the compression chamber, and the first and second buffers. A pulse tube refrigerator comprising: a third communication pipe that communicates with the chamber. 7. The pulse tube refrigerator according to claim 5, wherein the driving means is a linear motor. 8. The pulse tube refrigerator according to claim 5, wherein the driving means is a crank mechanism. 9. A pulse tube having a heat accumulator at one end and a room temperature heat exchanger at the other end via a low temperature heat exchanger for generating cold heat, and a piston slidably supported in the cylinder. A compression chamber formed by the cylinder and the cylinder, and driving means for reciprocating the piston, and an expansion piston formed coaxially with the piston to form the expansion piston and the compression chamber A compressor provided with an expansion chamber whose volume changes in inverse proportion to the volume change, a first communication pipe for connecting the compression chamber and the pulse tube through the heat storage device and the low temperature heat exchanger, and a working gas pulsed. A pulse tube provided with a second communication tube that connects the expansion chamber and the pulse tube through the normal temperature heat exchanger so that the expansion tube and the compression chamber flow through the tube. Move refrigerator. 10. A pulse tube in which a heat accumulator is connected to one end and a room temperature heat exchanger is connected to the other end via a low temperature heat exchanger that generates cold heat, and slidably supported in a cylinder. A compression chamber formed by a piston and the cylinder; a drive means for reciprocating the piston; and an expansion piston coaxially connected to the piston via an elastic member A compressor provided with an expansion chamber whose volume changes with a predetermined phase difference with respect to the volume change of the chamber, and a first communication pipe that connects the compression chamber and the pulse tube via the heat storage device and the low temperature heat exchanger. And a second communication pipe that communicates the expansion chamber and the pulse tube through the room temperature heat exchanger so that the working gas flows between the expansion chamber and the compression chamber through the pulse tube. Features and Pulse tube refrigerator. 11. A pulse tube having a low temperature heat exchanger for generating cold heat at one end and a room temperature heat exchanger at the other end; and a pulse tube provided at one end of the pulse tube via the low temperature heat exchanger. A heat storage device arranged in parallel with the pulse tube, a piston slidably supported in a cylinder, and a compression chamber formed by the cylinder, and a driving means for reciprocating the piston,
A first communication pipe for communicating the compression chamber with the pulse tube via the heat storage device and the low temperature heat exchanger, and a compressor having a buffer chamber whose volume changes in inverse proportion to the volume change of the compression chamber. And a second communication pipe that communicates the buffer chamber and the pulse tube through the normal temperature heat exchanger so that the working gas flows between the buffer chamber and the compression chamber through the pulse tube. Characteristic pulse tube refrigerator. 12. A pulse tube having a low temperature heat exchanger for generating cold heat at one end and a room temperature heat exchanger at the other end; and a pulse tube provided at one end of the pulse tube via the low temperature heat exchanger. A heat storage unit arranged coaxially inside the pulse tube, a piston slidably supported in a cylinder, and a compression chamber formed by the cylinder, and a driving means for reciprocating the piston. And a first communication that connects the compression chamber and the pulse tube via the heat storage device and the low-temperature heat exchanger, and a compressor that includes a buffer chamber that changes in volume in inverse proportion to the change in volume of the compression chamber. A second communication for communicating the buffer chamber with the pulse tube through the room temperature heat exchanger so that the working gas flows between the tube and the compression chamber through the pulse tube. A pulse tube refrigerator having a tube. 13. A pulse tube having a low temperature heat exchanger for generating cold heat at one end and a room temperature heat exchanger at the other end, and a pulse tube provided at one end of the pulse tube via the low temperature heat exchanger. A heat accumulator arranged coaxially on the outer circumference of the pulse tube, a piston slidably supported in a cylinder, a compression chamber formed by the cylinder, and a driving means for reciprocating the piston. And a first communication that connects the compression chamber and the pulse tube via the heat storage device and the low-temperature heat exchanger, and a compressor that includes a buffer chamber that changes in volume in inverse proportion to the change in volume of the compression chamber. A second communication for communicating the buffer chamber with the pulse tube through the room temperature heat exchanger so that the working gas flows between the tube and the compression chamber through the pulse tube. A pulse tube refrigerator having a tube. 14. A pulse tube having a heat accumulator at one end and a room temperature heat exchanger at the other end via a low temperature heat exchanger for generating cold heat, and a piston slidably supported in a cylinder. And a compressor having a compression chamber formed by the cylinder, a drive unit for reciprocating the piston, and a buffer chamber that changes in volume in inverse proportion to a change in volume of the compression chamber; And a first communication pipe that communicates the compression chamber with the pulse tube via the low temperature heat exchanger, and the normal temperature heat exchanger so that the working gas flows between the buffer chamber and the compression chamber via the pulse tube. Pulse tube refrigeration characterized by comprising a second communication pipe that communicates the buffer chamber with the pulse tube via the second communication pipe, and a third communication pipe that communicates the first communication pipe and the second communication pipe. Machine. 15. A pulse tube having a heat accumulator at one end and a room temperature heat exchanger at the other end via a low temperature heat exchanger for generating cold heat, and a piston slidably supported in the cylinder. A compressor having a compression chamber formed by a cylinder and the cylinder, and a drive means for reciprocating the piston, and an expansion piston connected to an elastic member slidably supported in the expansion cylinder, and the expansion A buffer means formed of a cylinder and an expansion piston and having a buffer chamber whose volume changes with a predetermined phase difference with respect to the volume change of the compression chamber; and a pulse with the compression chamber via the heat accumulator and a low temperature heat exchanger. A first communication pipe communicating with the tube and a buffer chamber and a valve via the room temperature heat exchanger so that the working gas flows between the buffer chamber and the compression chamber via a pulse tube. A pulse tube refrigerator, comprising: a second communication tube that communicates with the tube. 16. A drive means for providing a pair of the pistons in a cylinder of the compressor so as to face each other, forming the compression chamber between the pair of pistons, and reciprocating the pair of pistons with a predetermined phase difference. The pulse tube refrigerator according to claim 9, wherein the pulse tube refrigerator is provided. 17. A pulse tube having a heat accumulator at one end and a room temperature heat exchanger at the other end via a low temperature heat exchanger for generating cold heat, and slidably opposed to and supported in a cylinder. A compressor provided with a compression chamber formed between a pair of pistons and a drive means for reciprocating the pair of pistons with a predetermined phase difference; and an expansion piston connected to an elastic member in an expansion cylinder. Buffer means slidably supported and formed by the expansion cylinder and the expansion piston and having a volume change with a predetermined phase difference with respect to the volume change of the compression chamber, the heat storage device and the low temperature heat exchange A first communication pipe that communicates the compression chamber with the pulse tube via a pressure vessel, and the normal temperature heat exchanger so that the working gas flows between the buffer chamber and the compression chamber via the pulse tube. Then, the pulse tube refrigerator is provided with a second communication tube for communicating the buffer chamber with the pulse tube.