JP6913046B2 - Pulse tube refrigerator - Google Patents

Description

The present invention relates to a pulse tube refrigerator, for example, a sterling type pulse tube refrigerator.

Conventionally, a pulse tube refrigerator using a pressure vibration source such as a linear compressor has been known. Such a pulse tube refrigerator is also called a sterling type pulse tube refrigerator because it is common with the sterling refrigerator in that it utilizes the pressure vibration flow generated by the pressure vibration source. Vibration damping measures such as vibration damping rubber can be taken for the pressure vibration source.

Japanese Unexamined Patent Publication No. 2003-4322

As a result of intensive research on the pulse tube refrigerator, the present inventor has come to recognize the following problems. Not limited to the Sterling type pulse tube refrigerator, the pulse tube refrigerator is generally suitable for cooling objects to be cooled that dislike vibration, such as sensors. The cold head of the pulse tube refrigerator can be configured to have no moving parts, so that the cold head can be cooled by holding the object to be cooled at low vibration without taking any vibration damping measures. Because.

However, the present inventor, although only to the extent that it does not pose a problem in such known applications, is actually very much in the cold head due to the inertial force due to the movement of the refrigerant gas in and out of the cold head. I noticed that minute vibrations could occur. For example, in the case of a Stirling type pulse tube refrigerator, the pressure of the refrigerant gas to be filled is usually higher than that of the Stirling refrigerator. Therefore, the inertial force of the refrigerant gas also tends to be relatively large in the sterling type pulse tube refrigerator.

According to the inventor's assumption, existing cooling applications for cutting-edge academic research or advanced industrial use (for example, cryocooling of detection elements of new observation equipment mounted on spacecraft) Cooling under ultra-low vibration that exceeds the low vibration that can be achieved by a pulse tube refrigerator may be required in the future.

One of the exemplary objects of an aspect of the present invention is to provide a technique that contributes to ultra-low vibration of a pulse tube refrigerator.

According to an aspect of the present invention, the pulse tube refrigerating machine includes a pressure vibration source, a cold storage device including a cold storage device high temperature end connected to the pressure vibration source, a cold storage device low temperature end, and a cold storage device low temperature end. A pulse tube having a connected pulse tube low temperature end and a pulse tube high temperature end, an inertia tube connected to the pulse tube high temperature end, and fluidly connected to the pulse tube high temperature end via the inertia tube. A phase control unit including a buffer tank and a dynamic vibration absorber incorporated in the phase control unit, which can be displaced with respect to an elastic element attached to the high temperature end of the pulse tube and the high temperature end of the pulse tube. A dynamic vibration absorber including a mass element attached to the high temperature end of the pulse tube via an elastic element is provided.

It should be noted that any combination of the above components or components and expressions of the present invention that are mutually replaced between methods, devices, systems, and the like are also effective as aspects of the present invention.

According to the present invention, it is possible to provide a technique that contributes to ultra-low vibration of a pulse tube refrigerator.

It is a figure which shows schematicly the pulse tube refrigerator which concerns on 1st Embodiment. It is a figure which shows schematic the expansion machine of the pulse tube refrigerator which concerns on 2nd Embodiment. It is a figure which shows schematic the front view at the time of looking at the dynamic vibration absorber which can be applied to the expansion machine which concerns on 2nd Embodiment from the direction B shown in FIG. 4 (a) to 4 (c) schematically show the pulse tube refrigerator according to the third embodiment. It is a figure which shows schematicly the pulse tube refrigerator which concerns on 4th Embodiment.

Hereinafter, embodiments for carrying out the present invention will be described in detail with reference to the drawings. In the description and drawings, the same or equivalent components, members, and processes are designated by the same reference numerals, and duplicate description will be omitted as appropriate. The scales and shapes of the illustrated parts are set for convenience of explanation and are not to be interpreted in a limited manner unless otherwise specified. Embodiments are exemplary and do not limit the scope of the invention in any way. Not all features and combinations thereof described in the embodiments are essential to the invention.

(First Embodiment)
FIG. 1 schematically shows the pulse tube refrigerator 10 according to the first embodiment. The pulse tube refrigerator 10 is configured as a sterling type pulse tube refrigerator, and includes a pressure vibration source 12, a connecting pipe 14, and an expander 16 also called a cold head. The expander 16 includes a regenerator 18, a cooling stage 20, a pulse tube 22, and a phase control unit 24. The expander 16 has a so-called in-line type or linear type structure in which the cooler 18 and the pulse tube 22 are coaxially and in series connected to each other. For understanding, the axial direction of the inflator 16 is illustrated by arrow A.

Although shown as a single-stage pulse tube refrigerator 10 in the figure for simplicity, in certain embodiments, the pulse tube refrigerator 10 can also be configured as a two-stage pulse tube refrigerator. ..

Helium gas is typically used as the refrigerant gas of the pulse tube refrigerator 10. However, the present invention is not limited to this, and other appropriate gases can be used as the refrigerant gas. The refrigerant gas is filled and sealed in the pulse tube refrigerator 10.

In the pulse tube refrigerator 10, the pressure vibration of the refrigerant gas is induced in the pulse tube 22 by the operation of the pressure vibration source 12, and the pulse tube 22 has an appropriate phase delay in synchronization with the pressure vibration by the action of the phase control unit 24. It is designed so that the displacement vibration of the refrigerant gas, that is, the reciprocating movement of the gas piston occurs inside. The movement of the refrigerant gas that periodically reciprocates up and down in the pulse tube 22 while holding a certain pressure is often referred to as a "gas piston" and is often used to explain the behavior of the pulse tube refrigerator 10. When the gas piston is at or near the high temperature end of the pulse tube 22, the refrigerant gas expands at the low temperature end of the pulse tube 22, and cold is generated.

By repeating such a refrigeration cycle (for example, specifically, a reverse Stirling cycle), the pulse tube refrigerator 10 can cool the cooling stage 20 to a desired extremely low temperature. Therefore, the pulse tube refrigerator 10 can cool the object to be cooled, which is installed in the cooling stage 20 or thermally coupled to the cooling stage 20 via an appropriate heat transfer member, to an extremely low temperature.

As an example, the object to be cooled may be a detection element that detects infrared rays, submillimeter waves, X-rays, or other electromagnetic waves. Such a detection element may be a component of an observation device used for astronomical observation. The pulse tube refrigerator 10 may be mounted on a spacecraft such as an artificial satellite together with an observation device having such an electromagnetic wave detecting element. Alternatively, the pulse tube refrigerator 10 may be mounted on a ground facility equipped with such an observation device. Alternatively, the pulse tube refrigerator 10 may be mounted on a spacecraft or ground equipment together with, for example, a superconducting device or other device in which an extremely low temperature environment is desired.

The pressure vibration source 12 is configured as a so-called two-cylinder opposed linear compressor having two cylinders 12a arranged coaxially with each other facing each other. Each cylinder 12a houses a piston 12b and a linear actuator 12c that vibrates the piston 12b in the axial direction. The vibration direction of the piston 12b is different from the axial direction of the expander 16. The piston 12b is elastically supported by the cylinder 12a via a leaf spring or an elastic support member, which is also called a flexure bearing 12d, so that the piston 12b can be displaced in the axial direction while the displacement in the radial and circumferential directions is restricted. Further, the cylinder 12a fixedly supports the linear actuator 12c. A compression chamber 12e is formed between the cylinder 12a and the piston 12b. One end of the connecting pipe 14 is connected to the compression chamber 12e.

The drive of the linear actuator 12c causes the piston 12b to vibrate in the axial direction. As a result, the volume of the compression chamber 12e vibrates and increases, and pressure vibration of the refrigerant gas in the compression chamber 12e is generated. As an example, the average pressure of pressure vibration is, for example, in the order of megapascals, for example, in the range of about 1 to 3 MPa, the pressure amplitude is, for example, in the range of about 0.5 to 1 MPa, and the frequency is in the range of, for example, about 50 to 60 Hz. May be.

The connecting pipe 14 fluidly connects the pressure vibration source 12 to the expander 16. That is, the connecting pipe 14 connects the pressure vibration source 12 and the expander 16 so that the refrigerant gas can flow in both directions between the pressure vibration source 12 and the expander 16. Therefore, the pressure vibration of the refrigerant gas generated by the pressure vibration source 12 is transmitted to the expander 16 via the connecting pipe 14, whereby the pressure vibration can be induced in the expander 16. The connecting pipe 14 may be a flexible pipe or a rigid pipe.

The cold storage device 18 usually includes a container having a cylindrical or other cylindrical shape, and a cold storage material filled in the container. The cold storage device 18 has a cold storage device high temperature end 18a and a cold storage device low temperature end 18b. The cold storage high temperature end 18a is connected to the other end of the connecting pipe 14, and is connected to the compression chamber 12e of the pressure vibration source 12 via the connecting pipe 14. The cold storage high temperature end 18a may be provided with a heat exchanger or other heat radiating member, which is also called an aftercooler.

The pulse tube 22 is, for example, a cylinder or other tubular member having a suitable shape and has an internal space capable of accommodating a refrigerant gas. The regenerator 18 and the phase control unit 24 are fluidly connected via a pulse tube 22. The pulse tube refrigerator 10 is not provided with a flow path for the refrigerant gas that bypasses the refrigerator 18 and the pulse tube 22. Therefore, all gas flow between the pressure vibration source 12 and the phase control unit 24 goes through the regenerator 18 and the pulse tube 22.

The pulse tube 22 has a pulse tube high temperature end 22a and a pulse tube low temperature end 22b. The low temperature end 22b of the pulse tube is connected to the low temperature end 18b of the cooler. The low temperature end 22b of the pulse tube and the low temperature end 18b of the cold storage device communicate with each other, whereby the pulse tube 22 and the cold storage device 18 are fluidly connected. Further, the low temperature end 22b of the pulse tube is structurally tightly coupled to the low temperature end 18b of the cooler.

A cooling stage 20 is installed at a joint portion between the low temperature end 22b of the pulse tube and the low temperature end 18b of the cooler so as to surround the joint portion. The cooling stage 20 is made of a high thermal conductive material such as copper. The cooling stage 20 is thermally coupled to the low temperature end 22b of the pulse tube and the low temperature end 18b of the regenerator. As described above, the cooling stage 20 can be provided with a desired object to be cooled by the pulse tube refrigerator 10.

A phase control unit 24 is provided at the high temperature end 22a of the pulse tube. The phase control unit 24 has an inertia pipe 26 connected to the high temperature end 22a of the pulse pipe and a buffer tank 28 fluidly connected to the high temperature end 22a of the pulse pipe via the inertia pipe 26.

The inertia pipe 26 is housed in the buffer tank 28. Therefore, one end of the inertia pipe 26 is fluidly connected to the high temperature end 22a of the pulse pipe, and the other end of the inertia pipe 26 is open to the buffer volume, that is, the internal space of the buffer tank 28. The inertia tube 26 is significantly longer than, for example, the axial length of the cooler 18 and / or the pulse tube 22 (eg, it can extend to at least about 1 m, or even a few meters), so it can be properly accommodated in the buffer tank 28. It is molded into a coiled, meandering or other curved shape so that it can be formed. The inertia pipe 26 may be a flexible pipe or a rigid pipe.

The buffer tank 28 is structurally tightly coupled to the high temperature end 22a of the pulse tube. A flange portion 30 extending in the radial direction may be provided at the high temperature end 22a of the pulse tube, and the flange portion 30 defines a part of the wall of the buffer tank 28 (for example, the upper surface or the bottom surface of the buffer tank 28). May be good. The buffer tank 28 may also be arranged coaxially with the cooler 18 and the pulse tube 22.

The inflator 16 includes a vibration suppression mechanism configured to suppress the vibration of the inflator 16, for example, axial vibration, for example, a dynamic vibration absorber 32. The dynamic vibration absorber 32 is incorporated in the phase control unit 24. More specifically, the dynamic vibration absorber 32 is incorporated in the phase control unit 24 by being included in the buffer tank 28. The Tuned Mass Damper 32 is configured to suppress axial vibration of the pulse tube 22.

The Tuned Mass Damper 32 has an elastic element 32a attached to the high temperature end 22a of the pulse tube and a mass element attached to the high temperature end 22a of the pulse tube via the elastic element 32a so as to be displaceable with respect to the high temperature end 22a of the pulse tube. 32b and the like. The elastic element 32a elastically supports the mass element 32b so as to allow axial displacement of the mass element 32b while limiting or prohibiting displacement in other directions (eg, radial and circumferential). The elastic element 32a comprises, for example, a flexure bearing or a spring mechanism that includes one or more leaf springs or other springs. The mass element 32b may be anything as long as it acts as a weight. The mass element 32b may have an opening in the center thereof for passing the inertia tube 26.

The elastic element 32a is attached between the mass element 32b and the high temperature end 22a of the pulse tube so that an elastic restoring force acts on the mass element 32b when the mass element 32b is displaced in the axial direction from the neutral position. For example, the elastic element 32a may be mounted between the flange portion 30 and the mass element 32b, and may be attached to the pulse tube high temperature end 22a via the flange portion 30. Alternatively, the elastic element 32a may be attached between the other wall portion of the buffer tank 28 and the mass element 32b, and may be attached to the high temperature end 22a of the pulse tube via the buffer tank 28.

The Tuned Mass Damper 32 is designed so that the natural frequency of the vibration system formed by the elastic element 32a and the mass element 32b matches the frequency of the vibration that can be excited by the expander 16. As an example of vibration that can be excited by the inflator 16, the inflator 16 or the pulse tube 22 is excited by the inertial force due to the motion of the refrigerant gas entering and exiting the pulse tube 22 as the pulse tube refrigerator 10 operates. A small amount of axial vibration is assumed, but it is not limited to this. The design of such a Tuned Mass Damper 32 can be appropriately performed by, for example, theoretical analysis and / or numerical analysis and / or experimental method.

Therefore, according to the pulse tube refrigerator 10 according to the first embodiment, since the inflator 16 is provided with the dynamic vibration absorber 32, the vibration of the inflator 16 can be suppressed. In particular, since the dynamic vibration absorber 32 can suppress minute vibrations of the expander 16 due to the inertial force of the refrigerant gas, the pulse tube refrigerator super-vibrates beyond the low vibration that can be realized by the existing pulse tube refrigerators. It is possible to reduce vibration.

Further, since the dynamic vibration absorber 32 is incorporated in the phase control unit 24, it is possible to suppress the increase in size of the expander 16 due to the addition of the dynamic vibration absorber 32. In particular, accommodating the Tuned Mass Damper 32 in the buffer tank 28 is advantageous in that it does not require a new space for installing the Tuned Mass Damper 32.

Passive vibration countermeasures such as the Tuned Mass Damper 32 have a simpler configuration and are advantageous in terms of manufacturing cost as compared to active vibration countermeasures using an actuator and / or a controller. In particular, when the pulse tube refrigerator 10 is mounted on a spacecraft, active vibration countermeasures require an extremely expensive controller having special specifications such as resistance to radiation. On the other hand, according to the pulse tube refrigerator 10 according to the first embodiment, since such an expensive controller is not required, it is considerably advantageous in terms of cost.

(Second Embodiment)
FIG. 2 schematically shows an expander 16 of the pulse tube refrigerator according to the second embodiment. The expander 16 according to the second embodiment is different from the first embodiment in terms of arrangement in the regenerator 18 and the pulse tube 22, and the rest is generally common. In the following, different configurations will be mainly described, and common configurations will be briefly described or omitted.

The expander 16 includes a regenerator 18, a cooling stage 20, a pulse tube 22, and a phase control unit 24. The expander 16 has a so-called coaxial type configuration in which the regenerator 18 and the pulse tube 22 are coaxially arranged so that the regenerator 18 surrounds the pulse tube 22. Inside the cooling stage 20, the flow path of the refrigerant gas is folded back in the opposite direction in the axial direction. The cold storage high temperature end 18a and the pulse tube high temperature end 22a are located at substantially the same location, and both are fixed to the flange portion 30. The connecting pipe 14 penetrates the flange portion 30 in the radial direction and is connected to the cold storage high temperature end 18a.

In the second embodiment as well, as in the first embodiment, the phase control unit 24 fluidly connects the inertia tube 26 connected to the pulse tube high temperature end 22a and the pulse tube high temperature end 22a via the inertia tube 26. It has a connected buffer tank 28. The buffer tank 28 accommodates the inertia tube 26 and the tuned mass damper 32.

First, the inertia pipe 26 extends axially from the high temperature end 22a of the pulse pipe to the inside of the buffer tank 28. Then, the inertia pipe 26 is curved to the side wall of the buffer tank 28 along the dome-shaped wall surface of the buffer tank 28 on the side opposite to the flange portion 30 in the axial direction, and further along the side wall of the buffer tank 28. It is curved like a coil. The open end of the inertia pipe 26 is located in the vicinity of the flange portion 30, and fluid connection between the buffer tank 28 and the inertia pipe 26 is possible through this open end (illustrated by the arrow 34).

The dynamic vibration absorber 32 is incorporated in the phase control unit 24. The Tuned Mass Damper 32 is configured to suppress axial vibration of the expander 16 or the pulse tube 22. The Tuned Mass Damper 32 is attached to the high temperature end 22a of the pulse tube. As an example, the Tuned Mass Damper 32 is attached to the flange portion 30 via a plurality of support rods 36. The support rods 36 are arranged at equal angle intervals on the outer peripheral portion of the dynamic vibration absorber 32.

FIG. 3 schematically shows a front view of a tuned mass damper 32 that can be applied to the expander 16 according to the second embodiment when viewed from the direction B shown in FIG. The Tuned Mass Damper 32 has an elastic element 32a and a mass element 32b. Further, the Tuned Mass Damper 32 has a regular triangular or regular polygonal inner peripheral support 32c and a circular ring-shaped outer peripheral support 32d arranged so as to surround the inner peripheral support 32c. The Tuned Mass Damper 32 is formed in a substantially disk shape as a whole.

The outer peripheral support 32d is fastened to the plurality of support rods 36 by each of the plurality of fastening members 38. The fastening member 38 and the support rod 36 are arranged on the outer peripheral support 32d at equal angular intervals. Therefore, as shown in FIG. 2, the outer peripheral support 32d is fixed to the flange portion 30 and the high temperature end 22a of the pulse tube via the support rod 36.

The inner peripheral support 32c is arranged inside the outer peripheral support 32d, and both are connected by a plurality of elongated leaf spring members as elastic elements 32a. These leaf spring members are arranged between the inner peripheral support 32c and the outer peripheral support 32d. Each leaf spring member is arranged along each side of the inner peripheral support 32c, and the apex portion of the inner peripheral support 32c is connected to the outer peripheral support 32d. A first slit 42 is formed between each leaf spring member and the side of the corresponding inner peripheral support 32c, and a second slit 44 is formed between each leaf spring member and the outer peripheral support 32d. .. A circular mass element 32b is fixed to the center of the inner peripheral support 32c. At the center of the mass element 32b, an inertia pipe insertion hole 40 for passing the inertia pipe 26 is formed.

According to such an exemplary configuration, an axial vibration system having an elastic element 32a and a mass element 32b is formed. The mass element 32b is elastically supported by the elastic element 32a so that axial displacement of the mass element 32b is allowed while displacement in other directions (eg, radial and circumferential) is restricted or prohibited.

Similarly to the first embodiment, the inflator 16 according to the second embodiment can also suppress the vibration of the inflator 16 by the dynamic vibration absorber 32. The dynamic vibration absorber 32 contributes to ultra-low vibration of the pulse tube refrigerator by suppressing minute vibrations of the expander 16 caused by the inertial force of the refrigerant gas. Further, since the dynamic vibration absorber 32 is housed in the buffer tank 28, it is possible to suppress the increase in size of the expander 16 due to the addition of the dynamic vibration absorber 32.

(Third Embodiment)
4 (a) to 4 (c) schematically show the pulse tube refrigerator 10 according to the third embodiment. The pulse tube refrigerator 10 according to the third embodiment is different from the above-described embodiment in terms of the configuration of the dynamic vibration absorber 32, and the rest is generally common. In the following, different configurations will be mainly described, and common configurations will be briefly described or omitted.

The expander 16 includes a dynamic vibration absorber 32 that is incorporated in the phase control unit 24 and is configured to suppress vibration in the axial direction. The Tuned Mass Damper 32 is configured such that the inertial tube 26 functions as an elastic element 32a and / or the buffer tank 28 functions as a mass element 32b.

As shown in FIG. 4A, the inertia pipe 26 may function as the elastic element 32a of the tuned mass damper 32, and the buffer tank 28 may function as the mass element 32b of the tuned mass damper 32. The inertia pipe 26 is arranged outside the buffer tank 28, one end of which is connected to the high temperature end 22a of the pulse pipe, and the other end of which is connected to the buffer tank 28. The inertia tube 26 has an elastically deformable section 46 formed into an elastically deformable shape as an elastic element 32a. The elastically deformable section 46 has, for example, a coiled shape, a meandering shape, or another suitable repetitive curved shape.

As shown in FIG. 4B, the inertia pipe 26 functions as an elastic element 32a of the tuned mass damper 32, and a weight 48 separate from the buffer tank 28 functions as a mass element 32b of the tuned mass damper 32. May be good. One end of the inertia pipe 26 is connected to the high temperature end 22a of the pulse pipe, and the other end is opened to the buffer tank 28 inside the buffer tank 28. A weight 48 is attached to this open end. Since the inertia pipe 26 is housed in the buffer tank 28, the elastically deformable section 46 is also arranged in the buffer tank 28.

As shown in FIG. 4 (c), the buffer tank 28 functions as the mass element 32b of the dynamic vibration absorber 32, and the elastic member 50 different from the inertia pipe 26 functions as the elastic element 32a of the dynamic vibration absorber 32. You may. The buffer tank 28 is attached to the high temperature end 22a of the pulse tube via the elastic member 50. The inertia pipe 26 extends from the high temperature end 22a of the pulse pipe along the elastic member 50 and is inserted into the buffer tank 28. The insertion portion of the inertia pipe 26 into the buffer tank 28 is configured to prevent or minimize the leakage of the refrigerant gas from the buffer tank 28 while allowing the axial displacement of the buffer tank 28 with respect to the inertia pipe 26. A sealed seal portion 52 is provided.

Since the dynamic vibration absorber 32 is also provided in the pulse tube refrigerator 10 according to the third embodiment, the vibration of the expander 16 can be suppressed.

(Fourth Embodiment)
FIG. 5 schematically shows the pulse tube refrigerator 10 according to the fourth embodiment. The pulse tube refrigerator 10 according to the fourth embodiment is different from the above-described embodiment in terms of the configuration of the pressure vibration source 12, and the rest is generally common. In the following, different configurations will be mainly described, and common configurations will be briefly described or omitted.

In each of the above-described embodiments, the pressure vibration source 12 has an opposed two-cylinder configuration, but in the fourth embodiment, the pressure vibration source 12 has a single-cylinder configuration. Further, in each of the above-described embodiments, the pressure vibration source 12 is connected to the expander 16 by the connecting pipe 14, that is, the pressure vibration source 12 is arranged away from the expander 16, but in the fourth embodiment, , The pressure vibration source 12 is integrated adjacent to the expander 16.

The pressure vibration source 12 includes a piston 12b that reciprocates in the axial direction, and the regenerator 18 and the pulse tube 22 of the expander 16 are coaxially arranged with the piston 12b. Further, the mass element 32b of the dynamic vibration absorber 32 is also coaxially arranged with the piston 12b and can be displaced in the axial direction. Similar to the embodiment shown in FIG. 4A, the buffer tank 28 functions as the mass element 32b of the tuned mass damper 32, and the inertia pipe 26 has an elastically deformable section 46, and the elasticity of the tuned mass damper 32. It functions as an element 32a.

Also in the fourth embodiment, the configuration exemplified in FIG. 4 (b) or FIG. 4 (c) can be adopted as the dynamic vibration absorber 32.

Since the dynamic vibration absorber 32 is also provided in the pulse tube refrigerator 10 according to the fourth embodiment, the vibration of the pulse tube refrigerator 10 can be suppressed. Further, since the configuration of the pressure vibration source 12 is simplified, the pulse tube refrigerator 10 can be configured in a small size and at low cost.

The present invention has been described above based on examples. It will be understood by those skilled in the art that the present invention is not limited to the above embodiment, various design changes are possible, various modifications are possible, and such modifications are also within the scope of the present invention. By the way.

The various features described in relation to one embodiment are also applicable to other embodiments. The new embodiments resulting from the combination have the effects of each of the combined embodiments.

10 Pulse tube refrigerator, 12 pressure vibration source, 12b piston, 18 cold storage, 18a cold storage high temperature end, 18b cold storage low temperature end, 22 pulse tube, 22a pulse tube high temperature end, 22b pulse tube low temperature end, 24 phase control unit , 26 Inertance pipe, 28 Buffer tank, 32 Tuned mass damper, 32a Elastic element, 32b Mass element.

Claims (4)

Pressure vibration source and
A cold storage device including a cold storage device high temperature end connected to the pressure vibration source and a cold storage device low temperature end.
A pulse tube including a pulse tube low temperature end connected to the cold storage cold end and a pulse tube high temperature end.
A phase control unit including an inertia tube connected to the high temperature end of the pulse tube and a buffer tank fluidly connected to the high temperature end of the pulse tube via the inertia tube.
A dynamic vibration absorber incorporated in the phase control unit, the pulse tube high temperature is provided via an elastic element attached to the pulse tube high temperature end and an elastic element so as to be displaceable with respect to the pulse tube high temperature end. A pulse tube refrigerating machine, characterized in that it comprises a dynamic vibration absorber with a mass element attached to the end. The pulse tube refrigerator according to claim 1, wherein the dynamic vibration absorber is housed in the buffer tank. The pulse tube refrigerator according to claim 1 or 2, wherein the inertia tube functions as the elastic element and / or the buffer tank functions as the mass element. The pressure vibration source includes a piston that reciprocates in the axial direction.
The cold storage and the pulse tube are coaxially arranged with the piston.
The pulse tube refrigerator according to any one of claims 1 to 3, wherein the mass element is coaxially arranged with the piston and is displaceable in the axial direction.

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