US20240118007A1 - Method for operating cryocooler and cryocooler - Google Patents
Method for operating cryocooler and cryocooler Download PDFInfo
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- US20240118007A1 US20240118007A1 US18/475,195 US202318475195A US2024118007A1 US 20240118007 A1 US20240118007 A1 US 20240118007A1 US 202318475195 A US202318475195 A US 202318475195A US 2024118007 A1 US2024118007 A1 US 2024118007A1
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- cryocooler
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Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
- F25B49/022—Compressor control arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
- F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
- F17C1/00—Pressure vessels, e.g. gas cylinder, gas tank, replaceable cartridge
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/06—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/10—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point with several cooling stages
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/14—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/14—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle
- F25B9/145—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle pulse-tube cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/005—Gas cycle refrigeration machines using an expander of the rotary type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1933—Suction pressures
Definitions
- Certain embodiments of the present invention relate to a method for operating a cryocooler and a cryocooler.
- a cryocooler is used to cool various target objects such as superconducting equipment, measuring equipment, and samples used in a cryogenic environment.
- a cryocooler includes a first compressor, an expander, and a high pressure line and a low pressure line connecting the first compressor to the expander.
- the method includes: connecting a second compressor in series with a first compressor on a high pressure line or a low pressure line; connecting a buffer volume to the low pressure line via a supply valve; executing initial cooling for cooling an expander from an initial temperature to a cryogenic temperature in a state where the second compressor and the buffer volume are connected to the cryocooler; and executing a steady operation of maintaining the expander at the cryogenic temperature after the initial cooling.
- the execution of the initial cooling includes supplying a working gas to the expander by using the first compressor and the second compressor, and controlling the supply valve to keep a pressure of the high pressure line within a preset appropriate pressure range based on the measured pressure of the high pressure line.
- a cryocooler includes a first compressor, an expander, and a high pressure line and a low pressure line connecting the first compressor to the expander.
- the method includes: connecting a second compressor in series with a first compressor on a high pressure line or a low pressure line; executing initial cooling for cooling an expander from an initial temperature to a cryogenic temperature in a state where the second compressor is connected to the cryocooler; and executing a steady operation of maintaining the expander at the cryogenic temperature after the initial cooling.
- the first compressor or the second compressor has a compressor motor with a variable operating frequency.
- the execution of the initial cooling includes supplying a working gas to the expander by using the first compressor and the second compressor, and controlling the operating frequency of the compressor motor to keep a pressure of the high pressure line within a preset appropriate pressure range based on the measured pressure of the high pressure line.
- a cryocooler including: an expander capable of executing initial cooling for cooling from an initial temperature to a cryogenic temperature and a steady operation of maintaining the cryogenic temperature after the initial cooling; a high pressure line and a low pressure line connected to the expander; a first pressure sensor that measures a pressure of the high pressure line; a second pressure sensor that measures a pressure of the low pressure line; a buffer volume for storing a working gas; a supply valve that connects the buffer volume to the low pressure line; and a controller that controls the supply valve to keep the pressure of the high pressure line within a preset appropriate pressure range based on the pressure of the high pressure line measured by the first pressure sensor during the initial cooling.
- the controller discontinues control of the supply valve based on the pressure of the high pressure line when the pressure of the low pressure line measured by the second pressure sensor falls below a preset low pressure threshold, and controls the supply valve to restore the pressure of the low pressure line to the low pressure threshold based on the pressure of the low pressure line measured by the second pressure sensor.
- FIG. 1 is a view schematically illustrating a cryocooler according to one embodiment.
- FIG. 2 is a view schematically illustrating the cryocooler according to the embodiment.
- FIG. 3 is a flowchart for describing a method for controlling the cryocooler according to the embodiment.
- FIG. 4 is a flowchart for describing a method for controlling the cryocooler according to the embodiment.
- FIG. 5 is a graph illustrating an example of changes in temperature and pressure during an operation of the cryocooler according to the embodiment.
- FIGS. 6 A and 6 B are graphs illustrating an example of a change in pressure during the operation of the cryocooler according to the embodiment.
- FIG. 7 is a graph illustrating an example of changes in temperature and pressure during the operation of the cryocooler according to the embodiment.
- FIG. 8 is a view schematically illustrating the cryocooler according to the embodiment.
- FIG. 9 is a flowchart for describing a method for controlling the cryocooler according to the embodiment.
- FIG. 10 is a flowchart for describing the method for controlling the cryocooler according to the embodiment.
- FIG. 11 is a flowchart for describing the method for controlling the cryocooler according to the embodiment.
- FIG. 12 is a view schematically illustrating a cryocooler according to another embodiment.
- FIG. 13 is a view schematically illustrating the cryocooler according to the embodiment.
- FIG. 14 is a flowchart for describing a method for operating the cryocooler according to the embodiment.
- FIG. 15 is a view schematically illustrating a cryocooler according to still another embodiment.
- FIG. 16 is a flowchart for describing a method for operating the cryocooler according to the embodiment.
- FIG. 17 is a flowchart for describing a method for operating the cryocooler according to the embodiment.
- FIG. 18 is a view schematically illustrating the cryocooler according to the embodiment.
- FIG. 19 is a view schematically illustrating the cryocooler according to the embodiment.
- the cryocooler In order to cool a target object with a cryocooler, first, the cryocooler must be started and the cryocooler must be cooled from the initial temperature to the target cryogenic temperature.
- the initial cooling of such a cryocooler is also referred to as a cooldown. Since the initial cooling is merely a preparation for starting the cooling of the target object, it is desired that the required time is as short as possible.
- FIGS. 1 and 2 are views schematically illustrating a cryocooler 10 according to one embodiment.
- the cryocooler 10 is a two-stage Gifford-McMahon (GM) cryocooler.
- FIG. 1 schematically illustrates a compressor 12 and an expander 14 constituting the cryocooler together with a control device 100
- FIG. 2 illustrates the internal structure of the expander 14 of the cryocooler 10 .
- the compressor 12 is configured to collect the working gas of the cryocooler 10 from the expander 14 , pressurize the collected working gas, and supply the working gas to the expander 14 again.
- the compressor 12 and the expander 14 constitute a refrigeration cycle of the cryocooler 10 , whereby the cryocooler 10 can provide desired cryogenic cooling.
- the expander 14 is also referred to as a cold head.
- the working gas is also referred to as a refrigerant gas and is usually a helium gas, but other suitable gas may be used.
- the flow direction of the working gas is illustrated by an arrow in FIG. 1 .
- the pressure of the working gas supplied from the compressor 12 to the expander 14 and the pressure of the working gas collected from the expander 14 to the compressor 12 are both considerably higher than the atmospheric pressure, and are referred to as the first high pressure and the second high pressure, respectively.
- the first high pressure and the second high pressure are also simply referred to as high pressure and low pressure, respectively.
- the high pressure is, for example, 2 to 3 MPa.
- the low pressure is, for example, 0.5 to 1.5 MPa, for example, approximately 0.8 MPa.
- the flow direction of the working gas is indicated by an arrow.
- the expander 14 includes a cryocooler cylinder 16 and a displacer assembly 18 .
- the cryocooler cylinder 16 guides the linear reciprocating motion of the displacer assembly 18 , and forms expansion chambers ( 32 , 34 ) for the working gas with the displacer assembly 18 .
- the expander 14 includes a pressure switching valve 40 that determines an intake start timing of the working gas into the expansion chamber and an exhaust start timing of the working gas from the expansion chamber.
- the side close to the top dead center of the axial reciprocation of the displacer is “upper”, and the side close to the bottom dead center is “lower”.
- the top dead center is the position of the displacer where the volume of the expansion space is maximum
- the bottom dead center is the position of the displacer where the volume of the expansion space is the minimum. Since a temperature gradient is generated in which the temperature drops from the upper side to the lower side in the axial direction during the operation of the cryocooler 10 , the upper side can be referred to as a high temperature side and the lower side can be referred to as a low temperature side.
- the cryocooler cylinder 16 has a first cylinder 16 a and a second cylinder 16 b .
- the first cylinder 16 a and the second cylinder 16 b are members having a cylindrical shape, and the second cylinder 16 b has a diameter smaller than that of the first cylinder 16 a .
- the first cylinder 16 a and the second cylinder 16 b are coaxially disposed, and a lower end of the first cylinder 16 a is rigidly connected to an upper end of the second cylinder 16 b.
- the displacer assembly 18 includes a first displacer 18 a and a second displacer 18 b connected to each other, and these move integrally.
- the first displacer 18 a and the second displacer 18 b are members having a cylindrical shape, and the second displacer 18 b has a diameter smaller than that of the first displacer 18 a .
- the first displacer 18 a and the second displacer 18 b are disposed coaxially with each other.
- the first displacer 18 a is accommodated in the first cylinder 16 a
- the second displacer 18 b is accommodated in the second cylinder 16 b
- the first displacer 18 a can reciprocate in the axial direction along the first cylinder 16 a
- the second displacer 18 b can reciprocate in the axial direction along the second cylinder 16 b.
- the first displacer 18 a accommodates a first regenerator 26 .
- the first regenerator 26 is formed by filling a tubular main body portion of the first displacer 18 a with a wire mesh such as copper or other appropriate first regenerator material.
- the upper lid portion and the lower lid portion of the first displacer 18 a may be provided as members separate from the main body portion of the first displacer 18 a , the upper lid portion and the lower lid portion of the first displacer 18 a may be fixed to the main body by appropriate means such as fastening or welding, and accordingly, the first regenerator material may be accommodated in the first displacer 18 a.
- the second displacer 18 b accommodates a second regenerator 28 .
- the second regenerator 28 is formed by filling a tubular main body portion of the second displacer 18 b with a non-magnetic regenerator material such as bismuth, a magnetic regenerator material such as HoCu 2 , or other appropriate second regenerator material.
- the second regenerator material may be formed in a granular shape.
- the upper lid portion and the lower lid portion of the second displacer 18 b may be provided as members separate from the main body portion of the second displacer 18 b , the upper lid portion and the lower lid portion of the second displacer 18 b may be fixed to the main body by appropriate means such as fastening or welding, and accordingly, the second regenerator material may be accommodated in the second displacer 18 b.
- the displacer assembly 18 forms a room temperature chamber 30 , a first expansion chamber 32 , and a second expansion chamber 34 inside the cryocooler cylinder 16 .
- the expander 14 includes a first cooling stage 33 and a second cooling stage 35 for heat exchange with a desired object or medium to be cooled by the cryocooler 10 .
- the room temperature chamber 30 is formed between the upper lid portion of the first displacer 18 a and the upper portion of the first cylinder 16 a .
- the first expansion chamber 32 is formed between the lower lid portion of the first displacer 18 a and the first cooling stage 33 .
- the second expansion chamber 34 is formed between the lower lid portion of the second displacer 18 b and the second cooling stage 35 .
- the first cooling stage 33 is fixed to the lower portion of the first cylinder 16 a to surround the first expansion chamber 32
- the second cooling stage 35 is fixed to the lower portion of the second cylinder 16 b to surround the second expansion chamber 34 .
- the first regenerator 26 is connected to the room temperature chamber 30 through a working gas flow path 36 a formed in the upper lid portion of the first displacer 18 a , and is connected to the first expansion chamber 32 through a working gas flow path 36 b formed in the lower lid portion of the first displacer 18 a .
- the second regenerator 28 is connected to the first regenerator 26 through a working gas flow path 36 c formed from the lower lid portion of the first displacer 18 a to the upper lid portion of the second displacer 18 b .
- the second regenerator 28 is connected to the second expansion chamber 34 through a working gas flow path 36 d formed in the lower lid portion of the second displacer 18 b.
- the working gas flow between the first expansion chamber 32 , the second expansion chamber 34 , and the room temperature chamber 30 is not the clearance between the cryocooler cylinder 16 and the displacer assembly 18 , but a first seal 38 a and a second seal 38 b may be provided to be guided to the first regenerator 26 and the second regenerator 28 .
- the first seal 38 a may be mounted to the upper lid portion of the first displacer 18 a to be disposed between the first displacer 18 a and the first cylinder 16 a .
- the second seal 38 b may be mounted to the upper lid portion of the second displacer 18 b to be disposed between the second displacer 18 b and the second cylinder 16 b.
- the expander 14 includes a cryocooler housing 20 that accommodates the pressure switching valve 40 .
- the cryocooler housing 20 is coupled to the cryocooler cylinder 16 , thereby forming a hermetic container that accommodates the pressure switching valve 40 and the displacer assembly 18 .
- the pressure switching valve 40 includes a high pressure valve 40 a and a low pressure valve 40 b , and is configured to generate periodic pressure fluctuations in the cryocooler cylinder 16 .
- the working gas discharge port of the compressor 12 is connected to the room temperature chamber 30 via the high pressure valve 40 a
- the working gas suction port of the compressor 12 is connected to the room temperature chamber 30 via the low pressure valve 40 b .
- the high pressure valve 40 a and the low pressure valve 40 b are configured to selectively and alternately open and close (that is, when one is open, the other is closed).
- the pressure switching valve 40 may take the form of a rotary valve. That is, the pressure switching valve 40 may be configured such that the high pressure valve 40 a and the low pressure valve 40 b are alternately opened and closed by the rotational sliding of the valve disc with respect to the stationary valve body. In that case, an expander motor 42 may be connected to the pressure switching valve 40 to rotate the valve disc of the pressure switching valve 40 .
- the pressure switching valve 40 is disposed such that the valve rotation axis is coaxial with the rotation axis of the expander motor 42 .
- the high pressure valve 40 a and the low pressure valve 40 b may be valves that can be individually controlled. In this case, the pressure switching valve 40 may not be connected to the expander motor 42 .
- the expander motor 42 is connected to a displacer drive shaft 44 via a motion conversion mechanism 43 such as a Scotch yoke mechanism.
- the expander motor 42 is attached to the cryocooler housing 20 .
- the motion conversion mechanism 43 is accommodated in the cryocooler housing 20 similar to the pressure switching valve 40 .
- the motion conversion mechanism 43 converts the rotary motion output by the expander motor 42 into a linear reciprocating motion of the displacer drive shaft 44 .
- the displacer drive shaft 44 extends from the motion conversion mechanism 43 into the room temperature chamber 30 , and is fixed to the upper lid portion of the first displacer 18 a .
- the rotation of the expander motor 42 is converted into an axial reciprocation of the displacer drive shaft 44 by the motion conversion mechanism 43 , and the displacer assembly 18 reciprocates linearly in the cryocooler cylinder 16 in the axial direction.
- the expander 14 may include a temperature sensor 46 that measures the temperature of the second cooling stage 35 (and/or the first cooling stage 33 ) and outputs a measured temperature signal indicating the measured temperature.
- the compressor 12 includes a high pressure gas outlet 50 , a low pressure gas inlet 51 , a high pressure flow path 52 , a low pressure flow path 53 , a first pressure sensor 54 , a second pressure sensor 55 , a bypass line 56 , a compressor main body 57 , and a compressor housing 58 .
- the high pressure gas outlet 50 is installed in the compressor housing 58 as a working gas discharge port of the compressor 12
- the low pressure gas inlet 51 is installed in the compressor housing 58 as a working gas suction port of the compressor 12 .
- the high pressure flow path 52 connects the discharge port of the compressor main body 57 to the high pressure gas outlet 50
- the low pressure flow path 53 connects the low pressure gas inlet 51 to the suction port of the compressor main body 57 .
- the compressor housing 58 accommodates the high pressure flow path 52 , the low pressure flow path 53 , the first pressure sensor 54 , the second pressure sensor 55 , the bypass line 56 , and the compressor main body 57 .
- the compressor 12 is also referred to as a compressor unit.
- the compressor main body 57 is configured to internally compress the working gas sucked from the suction port and discharge the working gas from the discharge port.
- the compressor main body 57 may be a scroll type, a rotary type, or another pump for pressurizing the working gas.
- the compressor main body 57 is configured to discharge a fixed and constant working gas flow rate.
- the compressor main body 57 may be configured to have a variable flow rate of the working gas to be discharged.
- the compressor main body 57 may be referred to as a compression capsule.
- the first pressure sensor 54 is disposed in the high pressure flow path 52 to measure the pressure of the working gas flowing through the high pressure flow path 52 .
- the first pressure sensor 54 is configured to output a first measured pressure signal PH indicating the measured pressure.
- the second pressure sensor 55 is disposed in the low pressure flow path 53 to measure the pressure of the working gas flowing through the low pressure flow path 53 .
- the second pressure sensor 55 is configured to output a second measured pressure signal PL indicating the measured pressure. Therefore, the first pressure sensor 54 and the second pressure sensor 55 can also be referred to as a high pressure sensor and a low pressure sensor, respectively. Further, in this specification, any one of the first pressure sensor 54 and the second pressure sensor 55 , or both of them may be collectively referred to as a “pressure sensor”.
- the bypass line 56 connects the high pressure flow path 52 to the low pressure flow path 53 to bypass the expander 14 and return the working gas from the high pressure flow path 52 to the low pressure flow path 53 .
- the bypass line 56 is provided with a relief valve 60 for opening and closing the bypass line 56 or controlling the flow rate of the working gas flowing through the bypass line 56 .
- the relief valve 60 is configured to open when a differential pressure equal to or higher than a set pressure acts between the inlet and outlet of the relief valve 60 .
- the relief valve 60 may be an on/off valve or a flow control valve, and may be an electromagnetic valve, for example.
- the set pressure can be appropriately set based on the empirical knowledge of the designer, an experiment or simulation by the designer, or the like. In this manner, it is possible to prevent the differential pressure between the high pressure line 63 and the low pressure line 64 from exceeding the set pressure and becoming excessive. In addition, it is possible to prevent the pressure of the high pressure line 63 from becoming excessive.
- the relief valve 60 may be configured to work as a so-called safety valve, that is, may be mechanically opened when a differential pressure equal to or higher than a set pressure acts between the inlet and outlet. Alternatively, the relief valve 60 may be opened and closed under the control of the control device 100 .
- the control device 100 compares the differential pressure between the high pressure line 63 and the low pressure line 64 to be measured with the set pressure, the relief valve 60 may be controlled to open the relief valve 60 when the measured differential pressure is equal to or higher than the set pressure, and to close the relief valve 60 when the measured differential pressure is less than the set pressure.
- the control device 100 may acquire the measured differential pressures of the high pressure line 63 and the low pressure line 64 based on the first measured pressure signal PH from the first pressure sensor 54 and the second measured pressure signal PL from the second pressure sensor 55 . As another example, the control device 100 compares the measured pressure of the high pressure line 63 with the upper limit pressure based on the first measured pressure signal PH, and the relief valve 60 may be controlled to open the relief valve 60 when the measured pressure is equal to or higher than the upper limit pressure, and to close the relief valve 60 when the measured pressure is less than the upper limit pressure.
- the compressor 12 may have various other components.
- the high pressure flow path 52 may be provided with an oil separator, an adsorber, or the like.
- the low pressure flow path 53 may be provided with a storage tank or other components.
- the compressor 12 may be provided with an oil circulation system that cools the compressor main body 57 with oil, a cooling system that cools the oil, or the like.
- the cryocooler 10 includes a gas line 62 that circulates a working gas between the compressor 12 and the expander 14 .
- the gas line 62 includes the high pressure line 63 connecting the compressor 12 to the expander 14 to supply the working gas from the compressor 12 to the expander 14 , and the low pressure line 64 connecting the compressor 12 to the expander 14 to collect the working gas from the expander 14 to the compressor 12 .
- the cryocooler housing 20 of the expander 14 is provided with a high pressure gas inlet 22 and a low pressure gas outlet 24 .
- the high pressure gas inlet 22 is connected to the high pressure gas outlet 50 by a high-pressure pipe 65
- the low pressure gas outlet 24 is connected to the low pressure gas inlet 51 by a low-pressure pipe 66 .
- the high pressure line 63 includes the high-pressure pipe 65 and the high pressure flow path 52
- the low pressure line 64 includes the low-pressure pipe 66 and the low pressure flow path 53
- the bypass line 56 may be considered to be a part of the gas line 62 .
- the bypass line 56 connects the high pressure line 63 to the low pressure line 64 to bypass the expander 14 and return the working gas from the high pressure line 63 to the low pressure line 64 .
- the working gas collected from the expander 14 to the compressor 12 enters the low pressure gas inlet 51 of the compressor 12 from the low pressure gas outlet 24 of the expander 14 through the low-pressure pipe 66 , and further returns to the compressor main body 57 through the low pressure flow path 53 , is compressed by the compressor main body 57 , and is pressurized.
- the working gas supplied from the compressor 12 to the expander 14 exits from the high pressure gas outlet 50 of the compressor 12 through the high pressure flow path 52 from the compressor main body 57 , and further supplied to the expander 14 via the high-pressure pipe 65 and the high pressure gas inlet 22 of the expander 14 .
- the cryocooler 10 includes a buffer volume 70 , a supply valve 72 , and a collection valve 74 .
- the buffer volume 70 is a volume for storing the working gas, and may be, for example, a buffer tank.
- the supply valve 72 connects the buffer volume 70 to the low pressure line 64
- the collection valve 74 connects the buffer volume 70 to the high pressure line 63 .
- the supply valve 72 and the collection valve 74 may be an on/off valve or a flow control valve, and may be an electromagnetic valve, for example.
- the pressure of the buffer volume 70 is a filling pressure of the working gas in the cryocooler 10 when the operation of the cryocooler 10 is stopped.
- the pressure of the buffer volume 70 is a pressure intermediate between the pressure of the high pressure line 63 and the pressure of the low pressure line 64 (for example, average pressure of high pressure and low pressure).
- the supply valve 72 when the supply valve 72 is opened during the operation of the cryocooler 10 , the working gas is supplied from the buffer volume 70 to the low pressure line 64 through the supply valve 72 .
- the supply valve 72 When the supply valve 72 is closed, the supply of the working gas from the buffer volume 70 to the low pressure line 64 is stopped.
- the collection valve 74 When the collection valve 74 is opened, the working gas is collected from the high pressure line 63 to the buffer volume 70 through the collection valve 74 .
- the collection valve 74 When the collection valve 74 is closed, collection of the working gas from the high pressure line 63 to the buffer volume 70 is stopped.
- the control device 100 that controls the cryocooler 10 includes a controller 110 that controls the supply valve 72 and the collection valve 74 .
- the controller 110 is electrically connected to the first pressure sensor 54 and the second pressure sensor 55 to acquire the first measured pressure signal PH and the second measured pressure signal PL.
- the controller 110 receives the first measured pressure signal PH from the first pressure sensor 54 , and opens and closes the supply valve 72 and the collection valve 74 based on the measured pressure of the high pressure line 63 indicated by the first measured pressure signal PH. Further, the controller 110 is electrically connected to the temperature sensor 46 to acquire the measured temperature signal from the temperature sensor 46 .
- control device 100 is provided separately from the compressor 12 and the expander 14 , and is connected to these, but the present invention is not limited thereto.
- the control device 100 may be mounted on the compressor 12 .
- the control device 100 may be provided in the expander 14 , such as being mounted on the expander motor 42 .
- the controller 110 may be provided in the supply valve 72 , in the collection valve 74 , or in each of the supply valve 72 and the collection valve 74 .
- the control device 100 is realized as a hardware configuration by elements or circuits such as a CPU or memory of a computer, and is realized by a computer program or the like as a software configuration.
- FIG. 1 these are drawn as functional blocks realized by their cooperation as appropriate. It is understood by those skilled in the art that the functional blocks can be realized in various forms by combining hardware and software.
- the cryocooler 10 When the compressor 12 and the expander motor 42 are operated, the cryocooler 10 generates periodic volume fluctuations and pressure fluctuations of the working gas synchronized with the periodic volume fluctuations in the first expansion chamber 32 and the second expansion chamber 34 .
- the low pressure valve 40 b is closed and the high pressure valve 40 a is opened, whereby the high pressure working gas flows from the compressor 12 into the room temperature chamber 30 through the high pressure valve 40 a , is supplied to first expansion chamber 32 through the first regenerator 26 , and is supplied to the second expansion chamber 34 through the second regenerator 28 .
- the first expansion chamber 32 and the second expansion chamber 34 are pressurized from the low pressure to the high pressure.
- the displacer assembly 18 is moved upward from the bottom dead center to the top dead center, and the volumes of the first expansion chamber 32 and the second expansion chamber 34 are increased.
- the high pressure valve 40 a is closed, the intake process ends.
- the high pressure valve 40 a is closed and the low pressure valve 40 b is opened, whereby the high pressure first expansion chamber 32 and the second expansion chamber 34 are opened to the low pressure working gas suction port of the compressor 12 , and thus the working gas expands in the first expansion chamber 32 and the second expansion chamber 34 .
- the low pressure working gas is discharged from the first expansion chamber 32 and the second expansion chamber 34 to the room temperature chamber 30 through the first regenerator 26 and the second regenerator 28 .
- the displacer assembly 18 is moved downward from the top dead center to the bottom dead center, and the volumes of the first expansion chamber 32 and the second expansion chamber 34 are reduced.
- the working gas is collected from the expander 14 to the compressor 12 through the low pressure valve 40 b .
- the low pressure valve 40 b is closed, the exhaust process ends.
- a refrigeration cycle such as a GM cycle is configured, and the first cooling stage 33 and the second cooling stage 35 are cooled to a desired cryogenic temperature.
- the first cooling stage 33 can be cooled to a first cooling temperature in the range of, for example, approximately 20K to approximately 40K.
- the second cooling stage 35 can be cooled to a second cooling temperature (for example, approximately 1K to approximately 4K) lower than the first cooling temperature.
- the cryocooler 10 can execute initial cooling and steady operation following the initial cooling.
- the initial cooling is an operation mode of the expander 14 that rapidly cools from the initial temperature to the cryogenic temperature when the cryocooler 10 is started, and the steady operation is an operation mode of the expander 14 that maintains a cryogenically cooled state by initial cooling.
- the initial temperature may be an ambient temperature (for example, room temperature).
- the initial cooling can also be performed when the cryocooler 10 is restarted after maintenance of a cryogenic device (for example, superconducting equipment such as a magnetic resonance imaging (MRI) system).
- MRI magnetic resonance imaging
- the object to be cooled in the cryogenic device may be kept at a relatively low temperature (for example, 20 to 80 K) without being raised to an ambient temperature. In this case, the initial temperature may be such a low temperature.
- the expander 14 is cooled to a standard cooling temperature by initial cooling, and is maintained within an allowable temperature range of cryogenic temperature including the standard cooling temperature in steady operation.
- the standard cooling temperature varies depending on the application and setting of the cryocooler 10 , but is typically approximately 4.2 K or lower in, for example, an application for cooling a superconducting device. In some other cooling applications, the standard cooling temperature may be, for example, approximately 10K to 20K, or 10K or less.
- the initial cooling can also be referred to as a cooldown.
- the density of the working gas increases in the expander 14 as the temperature is lowered from the initial temperature to the cryogenic temperature.
- the amount of the working gas accumulated in the expander 14 increases, that is, the working gas is absorbed by the expander 14 from the gas line 62 .
- the pressure of the working gas circulating in the gas line 62 gradually decreases. Since a decrease in the pressure of the working gas causes a decrease in the cooling capacity of the cryocooler 10 , there is a concern that this may become a factor that lengthens the time required for the initial cooling. Since the initial cooling is merely a preparation because the cooling of the target object is started by the cryocooler, it is desired that the required time is as short as possible.
- the controller 110 controls the supply valve 72 to keep the pressure of the high pressure line 63 within a preset appropriate pressure range based on the pressure of the high pressure line 63 measured by the first pressure sensor 54 during the initial cooling. More specifically, the controller 110 may compare the measured pressure of the high pressure line 63 with the lower limit value Pc of the appropriate pressure range during the initial cooling, and operate the supply valve 72 to repeatedly open and close the supply valve 72 such that the pressure of the high pressure line 63 does not fall below the lower limit value Pc.
- the controller 110 controls the collection valve 74 to keep the pressure of the high pressure line 63 within an appropriate pressure range based on the pressure of the high pressure line 63 measured by the first pressure sensor 54 during the initial cooling. More specifically, the controller 110 may compare the measured pressure of the high pressure line 63 with an upper limit value Pd of the appropriate pressure range during the initial cooling, and operate the collection valve 74 to repeatedly open and close the collection valve 74 such that the pressure of the high pressure line 63 does not exceed the upper limit value Pd.
- FIG. 3 is a flowchart for describing a method for controlling the cryocooler 10 according to one embodiment. This method is repeatedly executed by the controller 110 in a predetermined cycle in the initial cooling of the cryocooler 10 . This method may be continuously executed not only during the initial cooling but also during the steady operation of the cryocooler 10 .
- the pressure of the high pressure line 63 is measured (S 10 ).
- the first pressure sensor 54 measures the pressure of the high pressure line 63 , and outputs the first measured pressure signal PH indicating the measured pressure of the high pressure line 63 .
- the controller 110 receives the first measured pressure signal PH and acquires the measured pressure of the high pressure line 63 .
- the measured pressure of the high pressure line 63 is compared with an appropriate pressure range (S 12 ).
- the lower limit value Pc of the appropriate pressure range is set such that the cryocooler 10 provides a sufficient cooling capacity.
- the upper limit value Pd of the appropriate pressure range is set not to generate excessive pressure in the high pressure line 63 .
- the upper limit value Pd of the appropriate pressure range may be set to a pressure value smaller than the above-described set pressure at which the relief valve 60 is opened.
- the appropriate pressure range can be appropriately set based on the empirical knowledge of the designer, an experiment or simulation by the designer, or the like.
- the appropriate pressure range may be stored in advance in the controller 110 as an initial setting of the cryocooler 10 , or may be set in the controller 110 by the user before the cryocooler 10 is operated.
- the upper limit value Pd and the lower limit value Pc of the appropriate pressure range may be selected from, for example, a range of 2 MPa to 3 MPa or a range of 2.1 MPa to 2.7 MPa.
- the width of the appropriate pressure range that is, the difference between the upper limit value Pd and the lower limit value Pc of the appropriate pressure range may be set to a certain value within 0.5 MPa, 0.3 MPa, or 0.1 MPa, for example.
- the appropriate pressure range may be set to 2.45 ⁇ 0.05 MPa. In this case, the width of the appropriate pressure range is 0.1 MPa, the upper limit value Pd is 2.5 MPa, and the lower limit value Pc is 2.4 MPa.
- the controller 110 compares the measured pressure of the high pressure line 63 with the lower limit value Pc of the appropriate pressure range, and opens the supply valve 72 when the measured pressure of the high pressure line 63 falls below the lower limit value Pc (PH ⁇ Pc) (S 14 ). In this manner, the working gas is supplied from the buffer volume 70 to the low pressure line 64 through the supply valve 72 . Since the amount of the working gas circulating in the gas line 62 increases, the pressure in the high pressure line 63 is restored.
- the controller 110 closes the supply valve 72 when the measured pressure of the high pressure line 63 is restored to an appropriate pressure range (S 16 ). For example, the controller 110 may compare the measured pressure of the high pressure line 63 with the lower limit value Pc of the appropriate pressure range, and close the supply valve 72 when the measured pressure of the high pressure line 63 exceeds the lower limit value Pc (PH>Pc or PH ⁇ Pc).
- Pc lower limit value
- the pressure threshold for closing the supply valve 72 may be different from the lower limit value Pc of the appropriate pressure range, and may be larger than the lower limit value Pc, for example.
- the pressure threshold may be set not to exceed the upper limit value Pd of the appropriate pressure range.
- the pressure threshold may be a value obtained by adding a predetermined ratio of a width of an appropriate pressure range (upper limit value Pd ⁇ lower limit value Pc) to the lower limit value Pc.
- the predetermined ratio may be 50% or less, 30% or less, or 10% or less.
- FIG. 4 is a flowchart for describing a method for controlling the cryocooler 10 according to one embodiment. This method is repeatedly executed by the controller 110 in a predetermined cycle in the initial cooling of the cryocooler 10 . This method may be executed in parallel with the method illustrated in FIG. 3 . This method may be continuously executed not only during the initial cooling but also during the steady operation of the cryocooler 10 .
- the pressure of the high pressure line 63 is measured using the first pressure sensor 54 (S 20 ).
- the controller 110 receives the first measured pressure signal PH from the first pressure sensor 54 , and acquires the measured pressure of the high pressure line 63 .
- the measured pressure of the high pressure line 63 is compared with an appropriate pressure range (S 22 ).
- the controller 110 compares the measured pressure of the high pressure line 63 with the upper limit value Pd of the appropriate pressure range, and opens the collection valve 74 when the measured pressure of the high pressure line 63 exceeds the upper limit value Pd (PH>Pd) (S 24 ).
- Pd the upper limit value
- the working gas is collected from the high pressure line 63 to the buffer volume 70 through the collection valve 74 , and the pressure of the high pressure line 63 decreases.
- the controller 110 closes the collection valve 74 when the measured pressure of the high pressure line 63 is restored to an appropriate pressure range (S 26 ). For example, the controller 110 may compare the measured pressure of the high pressure line 63 with the upper limit value Pd of the appropriate pressure range, and close the collection valve 74 when the measured pressure of the high pressure line 63 falls below the upper limit value Pd (PH ⁇ Pd or PH Pd).
- Pd Pd
- the collection valve 74 is closed, collection of the working gas from the high pressure line 63 to the buffer volume 70 is stopped. In this manner, the present method ends, and is executed again in the next control cycle.
- the pressure threshold for closing the collection valve 74 may be different from the upper limit value Pd of the appropriate pressure range, and may be smaller than, for example, the upper limit value Pd.
- This pressure threshold may be selected from an appropriate pressure range, that is, may be larger than the lower limit value Pc of an appropriate pressure range.
- the appropriate pressure range may be changed during the operation of the cryocooler 10 .
- the appropriate pressure range in the initial cooling may be different from the appropriate pressure range in the steady operation, and may be higher than the appropriate pressure range in the steady operation, for example.
- the lower limit value Pc in the initial cooling may be higher than the lower limit value Pc in the steady operation
- the upper limit value Pd in the initial cooling may be higher than the upper limit value Pd in the steady operation.
- the switching from the initial cooling to the steady operation and the change of the appropriate pressure range may be controlled by the control device 100 .
- the control device 100 may compare the measured temperature of the second cooling stage 35 (and/or the first cooling stage 33 ) with the above-described standard cooling temperature based on the measured temperature signal from the temperature sensor 46 , execute the initial cooling when the measured temperature is higher than the standard cooling temperature, and shift from the initial cooling to the steady operation when the measured temperature is equal to or lower than the standard cooling temperature.
- the controller 110 may change the appropriate pressure range with the shift from the initial cooling to the steady operation.
- the switching from the initial cooling to the steady operation and the change of the appropriate pressure range may be performed based on the pressure of the buffer volume 70 or based on the differential pressure of the high pressure line 63 and the low pressure line 64 . In this manner, the control device 100 can complete the initial cooling of the cryocooler 10 without depending on the temperature sensor 46 .
- PI MPa
- VH L
- VL L
- VB L
- n mol
- R the gas constant.
- PH (MPa) indicates the pressure of the high pressure line 63 in the steady operation at the temperature T
- PL (MPa) indicates the pressure of the low pressure line 64 in the steady operation at the temperature T
- PB (MPa) indicates the pressure of the buffer volume 70 in the steady operation at the temperature T.
- Equation (3) is solved for PB and substituted into Equation (4), the following relationship is obtained.
- the buffer volume 70 satisfies Equation (5) for any temperature in the temperature range from the initial temperature to the cryogenic temperature.
- a condition desired for the buffer volume 70 is considered.
- a condition desired for the buffer volume 70 is considered.
- in order to supply the working gas from the buffer volume 70 to the high pressure line 63 at any timing during the operation of the cryocooler 10 for any temperature T in a temperature range from the initial temperature of the cryocooler 10 to the cryogenic temperature, for any temperature T in a temperature range from the initial temperature of the cryocooler 10 to the cryogenic temperature,
- Equation (3) is solved for PB and substituted into Equation (6), the following relationship is obtained.
- the buffer volume 70 satisfies Equation (7) for any temperature in the temperature range from the initial temperature to the cryogenic temperature.
- FIG. 5 is a graph illustrating an example of time-dependent changes in temperature and pressure during the operation of the cryocooler 10 according to one embodiment.
- the illustrated pressure change is acquired by an experiment, and in the upper part of FIG. 5 , the pressure PH of the high pressure line 63 measured by the first pressure sensor 54 and the pressure PL of the low pressure line 64 measured by the second pressure sensor 55 are illustrated.
- a temperature T 1 of the first cooling stage 33 and a temperature T 2 of the second cooling stage 35 are illustrated in the lower part of FIG. 5 .
- the horizontal axis represents time.
- both the pressure PH of the high pressure line 63 and the pressure PL of the low pressure line 64 are the filling pressures PI, and the temperature T 1 of the first cooling stage 33 and the temperature T 2 of the second cooling stage 35 are room temperature (approximately 300K).
- the compressor 12 and the expander 14 work, the pressure PH of the high pressure line 63 is increased from the filling pressure PI, and the pressure PL of the low pressure line 64 decreases from the filling pressure PI. Due to the initial cooling, the temperature T 1 of the first cooling stage 33 and the temperature T 2 of the second cooling stage 35 decrease.
- the first cooling stage 33 and the second cooling stage 35 are each cooled to the above-described standard cooling temperature (for example, T 1 ⁇ 30K, T 2 ⁇ 4K), the initial cooling is completed and shifted to the steady operation.
- FIG. 6 A schematically illustrates an enlarged portion A illustrated in FIG. 5
- FIG. 6 B schematically illustrates an enlarged portion B illustrated in FIG. 5
- FIG. 6 A illustrates the pressure PH of the high pressure line 63 immediately after the start of the initial cooling together with the open/closed state of the collection valve 74
- FIG. 6 B illustrates the pressure PH of the high pressure line 63 after the portion A together with the open/closed state of the supply valve 72 .
- the collection valve 74 is opened. Since the working gas is collected from the high pressure line 63 to the buffer volume 70 through the collection valve 74 , the pressure PH of the high pressure line 63 decreases. When the pressure PH of the high pressure line 63 falls below the upper limit pressure Pd, the collection valve 74 is closed. In this manner, excessive pressurization of the high pressure line 63 can be avoided. The risk of an emergency stop of the compressor 12 due to excessive pressurization is reduced. Further, since the buffer volume 70 is pressurized by collecting the working gas, which leads to effective utilization for supplying the working gas from the buffer volume 70 to the low pressure line 64 .
- the supply valve 72 is opened.
- the working gas is supplied from the buffer volume 70 to the low pressure line 64 through the supply valve 72 . Since the amount of the working gas circulating in the gas line 62 increases, the pressure in the high pressure line 63 is restored. In this manner, when the pressure PH of the high pressure line 63 exceeds the lower limit value Pc, the supply valve 72 is closed.
- the density of the working gas increases in the expander 14 due to the temperature decrease of the expander 14 during the initial cooling, which has the effect of lowering the pressure PH of the high pressure line 63 . Therefore, even when the pressure PH of the high pressure line 63 is restored once, the pressure PH falls below the lower limit value Pc again.
- the supply valve 72 is opened again, the pressure in the high pressure line 63 is restored, and the supply valve 72 is closed. In this manner, the supply valve 72 operates to repeatedly open and close to maintain the pressure PH of the high pressure line 63 within an appropriate pressure range.
- the pressure PH of the high pressure line 63 may significantly decrease due to the temperature decrease of the expander 14 . Since the cooling capacity of the cryocooler 10 correlates with the pressure PH of the high pressure line 63 , the cooling capacity of the cryocooler 10 may decrease as the initial cooling progresses. This can be a factor that increases the time required for the initial cooling.
- the pressure PH of the high pressure line 63 can be maintained within an appropriate pressure range by controlling the supply valve 72 during the initial cooling. Therefore, the cooling capacity of the cryocooler 10 can be appropriately maintained, and an increase in the initial cooling time can be suppressed. Further, by keeping the pressure PH of the high pressure line 63 substantially constant, the cryocooler 10 can provide a stable cooling capacity.
- a method for controlling the supply valve 72 and the collection valve 74 based on the pressure of the low pressure line 64 is also conceivable.
- the pressure of the low pressure line 64 is affected by the cooling temperature of the expander 14 (varies depending on the cooling temperature). Therefore, it is practically indispensable to set an appropriate pressure range of the low pressure line 64 , that is, a pressure threshold of the low pressure line 64 for opening and closing the supply valve 72 and the collection valve 74 to a different value depending on the cooling temperature, and the design of the control becomes complicated. Further, even when the low pressure line 64 is within an appropriate pressure range, there may be a case where the pressure of the high pressure line 63 is excessively high depending on the cooling temperature. Therefore, a method based on the pressure of the high pressure line 63 as in the embodiment is advantageous in that such inconvenience is alleviated or prevented.
- FIG. 7 is a graph illustrating an example of changes in temperature and pressure during the operation of the cryocooler 10 according to one embodiment.
- FIG. 8 is a view schematically illustrating the cryocooler 10 according to one embodiment.
- the cryocooler 10 includes the compressor 12 , the expander 14 , the buffer volume 70 , and the control device 100 .
- the controller 110 controls the supply valve 72 to keep the pressure of the high pressure line 63 within a preset appropriate pressure range based on the pressure of the high pressure line 63 measured by the first pressure sensor 54 during the initial cooling. Further, the controller 110 controls the collection valve 74 to keep the pressure of the high pressure line 63 within an appropriate pressure range based on the pressure of the high pressure line 63 measured by the first pressure sensor 54 during the initial cooling.
- the cryocooler 10 includes a buffer pressure sensor 76 connected to the buffer volume 70 to measure the pressure of the buffer volume 70 .
- the buffer pressure sensor 76 is electrically connected to the control device 100 , and is configured to output a measured buffer pressure signal PB representing the measured pressure to the control device 100 .
- the pressure PB of the buffer volume 70 measured by the buffer pressure sensor 76 is illustrated in the upper part of FIG. 7 .
- the temperature T 1 of the first cooling stage 33 and the temperature T 2 of the second cooling stage 35 are illustrated in the lower part of FIG. 7 .
- the pressure PH of the high pressure line 63 and the pressure PL of the low pressure line 64 are also stabilized.
- both the supply valve 72 and the collection valve 74 are closed, and the buffer volume 70 is disconnected from the gas line 62 . Therefore, the pressure PB of the buffer volume 70 is also constant (final buffer pressure PF illustrated in FIG. 7 ).
- the completion of the initial cooling can be determined by detecting the stabilization of the pressure PB having the buffer volume 70 .
- the working gas filling pressure PI of the cryocooler 10 and operating conditions for example, high pressure PH, low pressure PL, temperatures T 1 , T 2 , and the like
- the controller 110 may compare the predicted value of the final buffer pressure with the measured pressure PB of the buffer volume 70 , and based on the comparison result, the controller 110 may determine whether or not the measured pressure PB of the buffer volume 70 is equal to the predicted value of the final buffer pressure.
- the controller 110 may complete the initial cooling when a state where the measured pressure PB of the buffer volume 70 is equal to the predicted value of the final buffer pressure continues for a predetermined time (for example, several minutes).
- the controller 110 may calculate a difference between the measured pressure PB of the buffer volume 70 and a reference pressure during the initial cooling, and detect the stabilization of the calculated pressure difference, to determine the completion of the initial cooling.
- the reference pressure may be the pressure of the previously measured buffer volume 70 , and may be, for example, the maximum value PM of the pressure of the buffer volume 70 measured during the initial cooling. It is understood from FIG. 7 that the pressure of the buffer volume 70 increases from the filling pressure PI and takes the maximum value PM immediately after the start of the initial cooling.
- the controller 110 may compare the calculated pressure difference (that is, the difference between the measured pressure PB of the buffer volume 70 and the reference pressure) with the pressure difference target value, and based on the comparison result, the controller 110 may determine whether or not the calculated pressure difference is equal to the pressure difference target value.
- the controller 110 may complete the initial cooling when a state where the calculated pressure difference is equal to the pressure difference target value continues for a predetermined time.
- the predetermined time may be selected from a range of 1 minute or more and 10 minutes or less.
- a predetermined value for example, 0.05 MPa
- the pressure PH of the high pressure line 63 (or the pressure PL of the low pressure line 64 ) measured at the same timing as the measured pressure PB of the buffer volume 70 may be used.
- the controller 110 may calculate a difference between the measured pressure PB of the buffer volume 70 and the measured pressure PH of the high pressure line 63 (or the measured pressure PL of the low pressure line 64 ), and detect the stabilization of the calculated pressure difference, to determine the completion of the initial cooling. Similar to the above example, the controller 110 may compare the calculated pressure difference with the pressure difference target value, and when the calculated pressure difference is equal to the pressure difference target value over a predetermined time, the controller 110 may complete the initial cooling.
- the controller 110 may calculate the difference between the measured pressure PH of the high pressure line 63 and the measured pressure PL of the low pressure line 64 , and detect the stabilization of the calculated pressure difference, to determine the completion of the initial cooling.
- the supply valve 72 is controlled (hereinafter, also referred to as high pressure priority control) based on the measured pressure of the high pressure line 63 during the initial cooling, and the pressure of the high pressure line 63 is kept within an appropriate pressure range.
- high pressure priority control also referred to as high pressure priority control
- the controller 110 may be configured to discontinue the control (that is, high pressure priority control) of the supply valve 72 based on the pressure of the high pressure line 63 when the pressure of the low pressure line 64 measured by the second pressure sensor 55 falls below a preset low pressure threshold.
- the controller 110 may be configured to control the supply valve 72 to restore the pressure of the low pressure line 64 to the low pressure threshold based on the pressure of the low pressure line 64 measured by the second pressure sensor 55 .
- the control of the supply valve 72 based on the pressure of the low pressure line 64 will also be referred to as low pressure priority control. An example of the switching processing from the high pressure priority control to the low pressure priority control will be described later with reference to FIG. 9 .
- FIG. 9 is a flowchart for describing a method for controlling the cryocooler 10 according to one embodiment. This method is repeatedly executed by the controller 110 in a predetermined cycle in the initial cooling of the cryocooler 10 . This method may be continuously executed not only during the initial cooling but also during the steady operation of the cryocooler 10 .
- the pressure of the low pressure line 64 is measured (S 30 ).
- the second pressure sensor 55 measures the pressure of the low pressure line 64 , and outputs the second measured pressure signal PL indicating the measured pressure of the low pressure line 64 .
- the controller 110 receives the second measured pressure signal PL and acquires the measured pressure of the low pressure line 64 .
- the measured pressure PL of the low pressure line 64 is compared with a low pressure threshold Pe (S 32 ).
- the low pressure threshold Pe may be set as a lower limit value of the pressure of the low pressure line 64 from the viewpoint of guaranteeing stable operation of the compressor 12 .
- the low pressure threshold Pe may be selected from a range of 0.2 MPa to 0.4 MPa.
- the low pressure threshold Pe can be appropriately set based on the empirical knowledge of the designer, an experiment or simulation by the designer, or the like.
- the low pressure threshold Pe may be stored in advance in the controller 110 as an initial setting of the cryocooler 10 , or may be set in the controller 110 by the user before the cryocooler 10 is operated.
- the controller 110 compares the measured pressure of the low pressure line 64 with the low pressure threshold Pe, and when the measured pressure of the low pressure line 64 exceeds the low pressure threshold Pe (PL>Pe or PL ⁇ Pe), the high pressure priority control is selected (S 34 ). In this case, as described with reference to FIG. 3 , the controller 110 compares the measured pressure of the high pressure line 63 with the lower limit value Pc of the appropriate pressure range, and operate the supply valve 72 to repeatedly open and close the supply valve 72 such that the pressure of the high pressure line 63 does not fall below the lower limit value Pc. In this manner, the high pressure priority control is continuously executed.
- the controller 110 selects the low pressure priority control (S 36 ).
- the high pressure priority control is discontinued, and the low pressure priority control is started.
- An example of the low pressure priority control will be described later with reference to FIG. 10 . In this manner, the switching processing from the high pressure priority control to the low pressure priority control ends.
- the pressure of the low pressure line 64 is measured (S 40 ).
- the measured pressure of the low pressure line 64 is compared with the low pressure threshold Pe (S 42 ).
- the controller 110 opens the supply valve 72 (S 44 ). In this manner, the working gas is supplied from the buffer volume 70 to the low pressure line 64 through the supply valve 72 , and the pressure of the low pressure line 64 is restored.
- the controller 110 closes the supply valve 72 (S 46 ).
- the supply of the working gas from the buffer volume 70 to the low pressure line 64 is stopped.
- the pressure threshold for closing the supply valve 72 may be different from the low pressure threshold Pe, and may be somewhat larger than, for example, the low pressure threshold Pe. In this manner, the present method ends, and is executed again in the next control cycle.
- the supply valve 72 is opened and closed based on the pressure of the low pressure line 64 , and the pressure of the low pressure line 64 can be restored to the low pressure threshold Pe.
- the pressure of the high pressure line 63 is not managed. Therefore, during the low pressure priority control, there is a possibility that an undesired phenomenon such that the pressure of the high pressure line 63 becomes extremely low may occur.
- controller 110 may be configured
- the controller 110 may be configured to control the supply valve 72 to restore the pressure of the high pressure line 63 to the high pressure threshold based on the pressure of the high pressure line 63 measured by the first pressure sensor 54 .
- An example of the return processing from the low pressure priority control to the high pressure priority control will be described later with reference to FIG. 11 .
- FIG. 11 is a flowchart for describing a method for controlling the cryocooler 10 according to one embodiment. During the execution of the low pressure priority control described above, this method is repeatedly executed by the controller 110 at a predetermined cycle.
- the pressure of the high pressure line 63 is measured (S 50 ).
- the measured pressure of the high pressure line 63 is compared with a high pressure threshold Pf (S 52 ).
- the high pressure threshold Pf may be the lower limit value Pc within an appropriate pressure range.
- the high pressure threshold Pf can be appropriately set based on the empirical knowledge of the designer, an experiment or simulation by the designer, or the like.
- the high pressure threshold Pf may be stored in advance in the controller 110 as an initial setting of the cryocooler 10 , or may be set in the controller 110 by the user before the cryocooler 10 is operated.
- the controller 110 compares the measured pressure of the high pressure line 63 with the high pressure threshold Pf, and when the measured pressure of the high pressure line 63 exceeds the high pressure threshold Pf (PH>Pf or PH ⁇ Pf), the low pressure priority control is selected (S 54 ). In this case, the low pressure priority control is continuously executed.
- the controller 110 selects the high pressure priority control (S 56 ). In this manner, the switching processing from the high pressure priority control to the low pressure priority control ends.
- the supply valve 72 is controlled based on the measured pressure of the high pressure line 63 , and the pressure of the high pressure line 63 is maintained within an appropriate pressure range.
- the time required for initial cooling can also be shortened.
- the relief valve 60 bypassing the high pressure line 63 and the low pressure line 64 may be an obstacle.
- the relief valve 60 is of a type that is mechanically opened when a differential pressure equal to or higher than a set pressure acts between the inlet and outlet of the relief valve 60 , the operating differential pressure of the cryocooler 10 may be limited to this set pressure.
- cryocooler 10 In order to cope with this, additional compressors may be temporarily installed in the cryocooler 10 for initial cooling, as described below.
- the main compressor 12 of the cryocooler 10 will be referred to as a first compressor 12
- the sub-compressor to be added will be referred to as a second compressor 80 .
- FIGS. 12 and 13 are views schematically illustrating the cryocooler 10 according to another embodiment.
- FIG. 12 illustrates the settings of the cryocooler 10 in the initial cooling
- FIG. 13 illustrates the basic settings of the cryocooler 10 in steady operation before or after the initial cooling.
- FIG. 14 is a flowchart for describing a method for operating the cryocooler 10 according to another embodiment.
- the cryocooler 10 and the method for operating the same according to another embodiment can be the same as the cryocooler 10 and the method for operating method the same according to one embodiment, except for the second compressor 80 . Therefore, in FIGS. 12 and 13 , the same reference numerals will be assigned to the configurations common to one embodiment, and detailed description thereof will be appropriately omitted in order to avoid redundancy.
- the cryocooler 10 takes a basic setting including the first compressor 12 and the expander 14 as illustrated in FIG. 13 before the initial cooling is performed.
- the first compressor 12 and the expander 14 are connected by the high pressure line 63 and the low pressure line 64 .
- the second compressor 80 and the buffer volume 70 are not connected to the cryocooler 10 .
- the second compressor 80 and the buffer volume 70 are connected to the cryocooler 10 as pretreatment for initial cooling (S 60 , S 61 ).
- the attachment order of the second compressor 80 and the buffer volume 70 is not limited.
- the second compressor 80 is connected in series with the first compressor 12 on the high pressure line 63 . More specifically, as illustrated in FIG. 12 , the high pressure gas outlet 50 of the first compressor 12 is connected to the suction port of the second compressor 80 , and the discharge port of the second compressor 80 is connected to the high pressure gas inlet 22 of the expander 14 . Therefore, the cryocooler 10 has a two-stage compressor configuration including the first compressor 12 and the second compressor 80 .
- the buffer volume 70 is connected to the low pressure line 64 via the supply valve 72 and is connected to the high pressure line 63 via the collection valve 74 .
- the supply valve 72 and the collection valve 74 may be accommodated in one housing together with the buffer volume 70 to form a buffer volume unit.
- the buffer volume unit and the second compressor 80 may be brought to the site where the cryocooler 10 is operated, for example, by a serviceman and connected to the cryocooler 10 .
- the cryocooler 10 is started and initial cooling is started (S 62 ).
- the initial cooling is a process of cooling the cryocooler 10 from the initial temperature to the target cryogenic temperature in preparation for steady operation of the cryocooler 10 .
- the initial temperature may be an ambient temperature (for example, room temperature), or may be a temperature lower than the ambient temperature and higher than a target cryogenic temperature (for example, a temperature selected from a range of 20K to 80K).
- the first cooling stage 33 of the expander 14 is cooled to the first cooling temperature
- the second cooling stage 35 is cooled to the second cooling temperature.
- the initial cooling is executed in a state where the second compressor 80 and the buffer volume 70 are connected to the cryocooler 10 . Therefore, in the initial cooling, the working gas is supplied to the expander 14 by using the first compressor 12 and the second compressor 80 .
- the first compressor 12 pressurizes the working gas of the cryocooler 10 collected from the expander 14 through the low pressure line 64 , and supplies the pressurized working gas to the second compressor 80 .
- the second compressor 80 further pressurizes the working gas from the first compressor 12 , and supplies this to the expander 14 again.
- the buffer volume 70 is used to keep the pressure of the high pressure line 63 within an appropriate pressure range, as in one embodiment. That is, the supply valve 72 performs control to keep the pressure of the high pressure line 63 within an appropriate pressure range based on the pressure of the high pressure line 63 measured by the first pressure sensor 54 during the initial cooling.
- the second compressor 80 and the buffer volume 70 are removed from the cryocooler 10 (S 63 , S 64 ).
- the order of removal of the second compressor 80 and the buffer volume 70 is not limited.
- the cryocooler 10 is returned to the basic setting illustrated in FIG. 14 . Then, a steady operation of the cryocooler 10 is performed (S 65 ).
- the operating differential pressure of the cryocooler 10 can be increased by adding the second compressor 80 .
- the operating differential pressure of the cryocooler 10 can be increased exceeding the limitation caused by the set pressure of the relief valve 60 of the first compressor 12 described above.
- An increase in the operating differential pressure causes an increase in the cooling capacity of the cryocooler 10 , and can shorten the time required for initial cooling.
- the cryocooler 10 As another method for increasing the operating differential pressure of the cryocooler 10 , it is conceivable to bring a large-sized compressor having a higher output than the first compressor 12 to the site from the outside and replace the first compressor 12 with the large-sized compressor. However, such a large-sized compressor is generally unsuitable for carrying because the large-sized compressor is large in size and weight. On the other hand, since the second compressor 80 is used in combination with the first compressor 12 , the second compressor 80 may be relatively small in size and is easy to carry.
- the second compressor 80 is connected to the discharge side (outlet side) of the first compressor 12 in order to form a two-stage compressor configuration.
- the second compressor 80 may be connected to the suction side (inlet side) of the first compressor 12 . That is, the second compressor 80 may be connected in series with the first compressor 12 on the low pressure line 64 .
- the buffer volume 70 is removed. Also in another embodiment, similar to one embodiment, as illustrated in FIG. 1 , a steady operation of the cryocooler 10 may be performed in a state where the buffer volume 70 is connected to the cryocooler 10 . Alternatively, also in one embodiment, similar to another embodiment, the buffer volume 70 may be removed from the cryocooler 10 after the initial cooling.
- FIG. 15 is a view schematically illustrating the cryocooler 10 according to still another embodiment.
- FIGS. 16 and 17 are flowcharts for describing a method for operating the cryocooler 10 according to still another embodiment.
- the cryocooler 10 and the method for operating the same according to still another embodiment can be the same as the cryocooler 10 and the method for operating method the same according to one embodiment, except for the second compressor 80 . Therefore, in FIG. 15 , the same reference numerals will be assigned to the configurations common to one embodiment, and detailed description thereof will be appropriately omitted in order to avoid redundancy.
- the cryocooler 10 takes a basic setting including the first compressor 12 and the expander 14 as illustrated in FIG. 13 before the initial cooling is performed.
- the first compressor 12 and the expander 14 are connected by the high pressure line 63 and the low pressure line 64 .
- the second compressor 80 is not connected to the cryocooler 10 .
- the second compressor 80 is connected to the cryocooler as pretreatment for initial cooling (S 70 ).
- the second compressor 80 is connected in series with the first compressor 12 on the high pressure line 63 .
- the high pressure gas outlet 50 of the first compressor 12 is connected to the suction port of the second compressor 80
- the discharge port of the second compressor 80 is connected to the high pressure gas inlet 22 of the expander 14 . Therefore, the cryocooler 10 has a two-stage compressor configuration including the first compressor 12 and the second compressor 80 .
- the second compressor 80 may be brought to the site where the cryocooler 10 is operated by a serviceman, for example, and may be connected to the cryocooler 10 .
- the second compressor 80 includes the compressor main body 57 similar to the first compressor 12 .
- the second compressor 80 includes a compressor motor 82 in which an operating frequency (that is, a rotation speed) is variable, and the compressor main body 57 is driven by the compressor motor 82 .
- the compressor motor 82 may be, for example, an electric motor, or may be any other suitable type of motor.
- the control device 100 includes an inverter 90 that controls the operating frequency of the compressor motor 82 .
- the compressor motor 82 and the inverter 90 are supplied with power from an external power source 92 such as a commercial power source (three-phase AC power source).
- the inverter 90 is configured to adjust the frequency of the power input from the external power source 92 under the control of the controller 110 and output the frequency to the compressor motor 82 at any frequency.
- the operating frequency of the compressor motor 82 corresponds to the output frequency of the inverter 90 , and can be adjusted in the range of 30 Hz to 100 Hz or 40 Hz to 70 Hz, for example.
- the cryocooler 10 is started and initial cooling is performed (S 72 ).
- the working gas is supplied to the expander 14 by using the first compressor 12 and the second compressor 80 .
- the first compressor 12 pressurizes the working gas of the cryocooler 10 collected from the expander 14 through the low pressure line 64 , and supplies the pressurized working gas to the second compressor 80 .
- the second compressor 80 further pressurizes the working gas from the first compressor 12 , and supplies this to the expander 14 again.
- the operating frequency of the compressor motor 82 of the second compressor 80 is controlled to keep the pressure of the high pressure line 63 within an appropriate pressure range based on the measured pressure of the high pressure line 63 .
- the second compressor 80 is removed from the cryocooler 10 (S 73 ).
- the cryocooler 10 is returned to the basic setting illustrated in FIG. 13 . Then, a steady operation of the cryocooler 10 is performed (S 75 ).
- the pressure of the high pressure line 63 is measured (S 80 ).
- the measured pressure of the high pressure line 63 is compared with a high pressure target value Pg (S 82 ).
- the high pressure target value Pg may be the lower limit value Pc of an appropriate pressure range.
- the high pressure target value Pg can be appropriately set based on the empirical knowledge of the designer, an experiment or simulation by the designer, or the like.
- the high pressure target value Pg may be stored in advance in the controller 110 as an initial setting of the cryocooler 10 , or may be set in the controller 110 by the user before the cryocooler 10 is operated.
- the controller 110 compares the measured pressure PH of the high pressure line 63 with the high pressure target value Pg, and outputs a magnitude relationship between the two as a comparison result. That is, the comparison results obtained by the controller 110 are any of the following three states: (i) the measured pressure PH is smaller than the high pressure target value Pg, (ii) the measured pressure PH is larger than the high pressure target value Pg, and (iii) the measured pressure PH is equal to the high pressure target value Pg.
- the inverter 90 is controlled based on the comparison result of the controller 110 , and the operating frequency of the compressor motor 82 is controlled according to the output frequency of the inverter 90 . Specifically, (i) when the measured pressure PH is smaller than the high pressure target value Pg, the controller 110 controls the inverter 90 to increase the operating frequency of the compressor motor 82 (S 84 ). Accordingly, the pressure of the high pressure line 63 can be increased.
- the controller 110 controls the inverter 90 to reduce the operating frequency of the compressor motor 82 (S 18 ). Accordingly, the pressure of the high pressure line 63 can be reduced.
- the controller 110 may increase or decrease the operating frequency by a predetermined amount from the value of the current operating frequency of the compressor motor 82 .
- the controller 110 may maintain the upper limit value without increasing the operating frequency. For example, in a case where the operating frequency of the compressor motor 82 is within a range of 30 Hz to 100 Hz and the current value is already the upper limit value of 100 Hz, the controller 110 does not further increase the operating frequency from 100 Hz, and 100 Hz is maintained.
- the controller 110 may maintain the lower limit value without reducing the operating frequency.
- the controller 110 may control the inverter 90 to adjust the operating frequency of the compressor motor 82 to minimize the deviation of the measured pressure PH from the high pressure target value Pg (for example, by feedback control such as PID control). In this manner, the controller 110 may compare the pressure of the high pressure line 63 with the target pressure, and control the inverter 90 to reduce the operating frequency of the compressor motor 82 when the pressure of the high pressure line 63 exceeds the target pressure and increase the operating frequency of the compressor motor 82 when the pressure of the high pressure line 63 falls below the target pressure.
- the operating differential pressure of the cryocooler 10 can be increased by adding the second compressor 80 .
- the operating differential pressure of the cryocooler 10 can be increased exceeding the limitation caused by the set pressure of the relief valve 60 of the first compressor 12 described above.
- An increase in the operating differential pressure causes an increase in the cooling capacity of the cryocooler 10 , and can shorten the time required for initial cooling.
- the second compressor 80 since the second compressor 80 is used in combination with the first compressor 12 , the second compressor 80 may be relatively small in size and is easy to carry.
- the buffer volume 70 may be connected to the cryocooler 10 for initial cooling together with the supply valve 72 and the collection valve 74 .
- the buffer volume 70 is connected to the low pressure line 64 via the supply valve 72 and is connected to the high pressure line 63 via the collection valve 74 .
- the buffer volume 70 is used to keep the pressure of the high pressure line 63 within an appropriate pressure range, as in one embodiment. That is, the supply valve 72 performs control to keep the pressure of the high pressure line 63 within an appropriate pressure range based on the pressure of the high pressure line 63 measured by the first pressure sensor 54 during the initial cooling.
- the buffer volume 70 may be removed from the cryocooler 10 together with the supply valve 72 and the collection valve 74 . In this manner, by using the buffer volume 70 for the initial cooling, the time required for the initial cooling can be shortened similar to the above-described embodiment.
- the second compressor 80 may be connected to the suction side (inlet side) of the first compressor 12 . That is, the second compressor 80 may be connected in series with the first compressor 12 on the low pressure line 64 .
- the operating frequency of the compressor motor 82 that drives the compressor main body 57 of the first compressor 12 may be variable.
- the operating frequency of the compressor motor 82 may be controlled by the controller 110 and the inverter 90 to keep the pressure of the high pressure line 63 within an appropriate pressure range based on the measured pressure of the high pressure line 63 .
- the operating frequency of the compressor motor 82 of the second compressor 80 may be controlled by the controller 110 and the inverter 90 , similar to the embodiment illustrated in FIG. 15 .
- control processing described with respect to one embodiment may be applied to other embodiment and still another embodiment.
- the cryocooler 10 may include the expander motor 42 having a variable operating frequency, and during initial cooling, so-called accelerated cooling in which the expander motor 42 works at a higher operating frequency than in steady operation may be executed.
- the switching from the initial cooling (accelerated cooling) to the steady operation and the change of the operating frequency may be performed based on the pressure of the buffer volume 70 or based on the differential pressure of the high pressure line 63 and the low pressure line 64 as described above with reference to FIGS. 7 and 8 .
- the initial cooling time can be further shortened.
- the pressure sensors such as the first pressure sensor 54 and the second pressure sensor 55 are not essential to be provided in the compressor 12 , and may be provided at any place where the pressure of the gas line 62 and the expander 14 can be measured.
- the first pressure sensor 54 may be provided at any place on the high pressure line 63
- the second pressure sensor 55 may be provided at any place on the low pressure line 64 .
- the supply valve 72 and the collection valve 74 are prepared as separate valves, and each of the supply valve 72 and the collection valve 74 are connected to the buffer volume 70 .
- the present invention is not limited thereto.
- the supply valve 72 and the collection valve 74 may be integrated, or may be, for example, a three-way valve connected to the buffer volume 70 . By switching the three-way valve, a supply state where the buffer volume 70 is connected to the low pressure line 64 and a collection state where the buffer volume 70 is connected to the high pressure line 63 may be switched.
- the buffer volume 70 is a single buffer tank.
- the buffer volume 70 may be a plurality of buffer tanks.
- One buffer tank may be connected to the low pressure line 64 by the supply valve 72
- another buffer tank may be connected to the high pressure line 63 by the collection valve 74 .
- the buffer volume 70 is disposed outside the compressor 12 and the expander 14 , but the present invention is not limited thereto.
- the buffer volume 70 may be disposed inside the compressor 12 .
- cryocooler 10 is a two-stage GM cryocooler
- the cryocooler 10 may be a single-stage or multi-stage GM cryocooler, and may be another type of cryocooler such as a pulse tube cryocooler.
- Embodiments of the present invention can also be expressed as follows.
- a cryocooler including: an expander capable of executing initial cooling for cooling from an initial temperature to a cryogenic temperature and a steady operation of maintaining the cryogenic temperature after the initial cooling; a high pressure line which is connected to the expander and through which a working gas taken into the expander flows; a low pressure line which is connected to the expander and through which a working gas exhausted from the expander flows; a first pressure sensor that measures a pressure of the high pressure line; a buffer volume for storing a working gas; a supply valve that connects the buffer volume to the low pressure line; and a controller that controls the supply valve to keep the pressure of the high pressure line within a preset appropriate pressure range based on the pressure of the high pressure line measured by the first pressure sensor during the initial cooling. 2.
- the cryocooler according to item 1, in which the controller compares the measured pressure of the high pressure line with the lower limit value of the appropriate pressure range during the initial cooling, and operate the supply valve to repeatedly open and close the supply valve such that the pressure of the high pressure line does not fall below the lower limit value.
- the cryocooler according to item 1 or 2 in which, when the buffer volume is VB, the volume of the high pressure line is VH, the volume of the low pressure line is VL, the working gas filling pressure at a certain temperature is PI, and the pressure of the high pressure line in the steady operation at the temperature is PH, and the pressure of the low pressure line in the steady operation at a temperature is PL, the buffer volume satisfies VB VH(PH ⁇ PI)/(PI ⁇ PL) ⁇ VL for any temperature in a temperature range from the initial temperature to the cryogenic temperature. 4.
- the cryocooler according to any one of items 1 to 3, further including the collection valve for connecting the buffer volume to the high pressure line, in which the controller controls the collection valve to keep the pressure of the high pressure line in an appropriate pressure range.
- the cryocooler according to item 4 in which, when the buffer volume is VB, the volume of the high pressure line is VH, the volume of the low pressure line is VL, the working gas filling pressure at a certain temperature is PI, and the pressure of the high pressure line in the steady operation at the temperature is PH, and the pressure of the low pressure line in the steady operation at a temperature is PL, the buffer volume satisfies VB ⁇ VH+VL(PI ⁇ PL)/(PH ⁇ PI) for any temperature in a temperature range from the initial temperature to the cryogenic temperature.
- the cryocooler according to item 9 in which the first compressor or the second compressor includes a compressor motor having a variable operating frequency, and is driven by the compressor motor, and the controller controls the operating frequency of the compressor motor to keep the pressure of the high pressure line within an appropriate pressure range based on the pressure of the high pressure line measured by the first pressure sensor during the initial cooling. 11.
- a method for operating a cryocooler in which the cryocooler includes a first compressor, an expander, and a high pressure line and a low pressure line connecting the first compressor to the expander including: connecting a second compressor in series with the first compressor on the high pressure line or the low pressure line; connecting a buffer volume to the low pressure line via a supply valve; executing initial cooling for cooling the expander from an initial temperature to a cryogenic temperature in a state where the second compressor and the buffer volume are connected to the cryocooler; and executing a steady operation of maintaining the expander at the cryogenic temperature after the initial cooling, in which the execution of the initial cooling includes supplying a working gas to the expander by using the first compressor and the second compressor, and controlling the supply valve to keep a pressure of the high pressure line within a preset appropriate pressure range based on the measured pressure of the high pressure line.
- the execution of the initial cooling includes discontinuing control of the supply valve based on the pressure of the high pressure line when the measured pressure of the low pressure line falls below a preset low pressure threshold, and controlling the supply valve to restore the pressure of the low pressure line to the low pressure threshold based on the measured pressure of the low pressure line. 15.
- the first compressor or the second compressor includes a compressor motor having a variable operating frequency, and is driven by the compressor motor, and the execution of the initial cooling includes controlling the operating frequency of the compressor motor to keep the pressure of the high pressure line within the preset appropriate pressure range based on the measured pressure of the high pressure line. 17.
- a method for operating a cryocooler in which the cryocooler includes a first compressor, an expander, and a high pressure line and a low pressure line connecting the first compressor to the expander the method including: connecting a second compressor in series with the first compressor on the high pressure line or the low pressure line; executing initial cooling for cooling the expander from an initial temperature to a cryogenic temperature in a state where the second compressor is connected to the cryocooler; and executing a steady operation of maintaining the expander at the cryogenic temperature after the initial cooling, in which the first compressor or the second compressor has a compressor motor with a variable operating frequency, and is driven by the compressor motor, and the execution of the initial cooling includes supplying a working gas to the expander by using the first compressor and the second compressor, and controlling the operating frequency of the compressor motor to keep a pressure of the
Abstract
A method for operating a cryocooler includes: connecting a second compressor in series with a first compressor on a high pressure line or a low pressure line; connecting a buffer volume to the low pressure line via a supply valve; executing initial cooling for cooling an expander from an initial temperature to a cryogenic temperature in a state where the second compressor and the buffer volume are connected to the cryocooler; and executing a steady operation of maintaining the expander at the cryogenic temperature after the initial cooling. The execution of the initial cooling includes supplying a working gas to the expander by using the first compressor and the second compressor, and controlling the supply valve to keep a pressure of the high pressure line within a preset appropriate pressure range based on the measured pressure of the high pressure line.
Description
- This application claims priority to Japanese Patent Application No. 2022-161835, filed on Oct. 6, 2022, which is incorporated by reference herein in its entirety.
- Certain embodiments of the present invention relate to a method for operating a cryocooler and a cryocooler.
- A cryocooler is used to cool various target objects such as superconducting equipment, measuring equipment, and samples used in a cryogenic environment.
- According to an aspect of the present invention, there is provided a method for operating a cryocooler. A cryocooler includes a first compressor, an expander, and a high pressure line and a low pressure line connecting the first compressor to the expander. The method includes: connecting a second compressor in series with a first compressor on a high pressure line or a low pressure line; connecting a buffer volume to the low pressure line via a supply valve; executing initial cooling for cooling an expander from an initial temperature to a cryogenic temperature in a state where the second compressor and the buffer volume are connected to the cryocooler; and executing a steady operation of maintaining the expander at the cryogenic temperature after the initial cooling. The execution of the initial cooling includes supplying a working gas to the expander by using the first compressor and the second compressor, and controlling the supply valve to keep a pressure of the high pressure line within a preset appropriate pressure range based on the measured pressure of the high pressure line.
- According to another aspect of the present invention, there is provided a method for operating a cryocooler. A cryocooler includes a first compressor, an expander, and a high pressure line and a low pressure line connecting the first compressor to the expander. The method includes: connecting a second compressor in series with a first compressor on a high pressure line or a low pressure line; executing initial cooling for cooling an expander from an initial temperature to a cryogenic temperature in a state where the second compressor is connected to the cryocooler; and executing a steady operation of maintaining the expander at the cryogenic temperature after the initial cooling. The first compressor or the second compressor has a compressor motor with a variable operating frequency. The execution of the initial cooling includes supplying a working gas to the expander by using the first compressor and the second compressor, and controlling the operating frequency of the compressor motor to keep a pressure of the high pressure line within a preset appropriate pressure range based on the measured pressure of the high pressure line.
- According to still another aspect of the present invention, there is provided a cryocooler including: an expander capable of executing initial cooling for cooling from an initial temperature to a cryogenic temperature and a steady operation of maintaining the cryogenic temperature after the initial cooling; a high pressure line and a low pressure line connected to the expander; a first pressure sensor that measures a pressure of the high pressure line; a second pressure sensor that measures a pressure of the low pressure line; a buffer volume for storing a working gas; a supply valve that connects the buffer volume to the low pressure line; and a controller that controls the supply valve to keep the pressure of the high pressure line within a preset appropriate pressure range based on the pressure of the high pressure line measured by the first pressure sensor during the initial cooling. The controller discontinues control of the supply valve based on the pressure of the high pressure line when the pressure of the low pressure line measured by the second pressure sensor falls below a preset low pressure threshold, and controls the supply valve to restore the pressure of the low pressure line to the low pressure threshold based on the pressure of the low pressure line measured by the second pressure sensor.
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FIG. 1 is a view schematically illustrating a cryocooler according to one embodiment. -
FIG. 2 is a view schematically illustrating the cryocooler according to the embodiment. -
FIG. 3 is a flowchart for describing a method for controlling the cryocooler according to the embodiment. -
FIG. 4 is a flowchart for describing a method for controlling the cryocooler according to the embodiment. -
FIG. 5 is a graph illustrating an example of changes in temperature and pressure during an operation of the cryocooler according to the embodiment. -
FIGS. 6A and 6B are graphs illustrating an example of a change in pressure during the operation of the cryocooler according to the embodiment. -
FIG. 7 is a graph illustrating an example of changes in temperature and pressure during the operation of the cryocooler according to the embodiment. -
FIG. 8 is a view schematically illustrating the cryocooler according to the embodiment. -
FIG. 9 is a flowchart for describing a method for controlling the cryocooler according to the embodiment. -
FIG. 10 is a flowchart for describing the method for controlling the cryocooler according to the embodiment. -
FIG. 11 is a flowchart for describing the method for controlling the cryocooler according to the embodiment. -
FIG. 12 is a view schematically illustrating a cryocooler according to another embodiment. -
FIG. 13 is a view schematically illustrating the cryocooler according to the embodiment. -
FIG. 14 is a flowchart for describing a method for operating the cryocooler according to the embodiment. -
FIG. 15 is a view schematically illustrating a cryocooler according to still another embodiment. -
FIG. 16 is a flowchart for describing a method for operating the cryocooler according to the embodiment. -
FIG. 17 is a flowchart for describing a method for operating the cryocooler according to the embodiment. -
FIG. 18 is a view schematically illustrating the cryocooler according to the embodiment. -
FIG. 19 is a view schematically illustrating the cryocooler according to the embodiment. - In order to cool a target object with a cryocooler, first, the cryocooler must be started and the cryocooler must be cooled from the initial temperature to the target cryogenic temperature. The initial cooling of such a cryocooler is also referred to as a cooldown. Since the initial cooling is merely a preparation for starting the cooling of the target object, it is desired that the required time is as short as possible.
- It is desirable to shorten the initial cooling time of the cryocooler.
- Any combination of the components described above and any replacement of the components and expressions of the present invention between methods, devices, systems, and the like are also effective as aspects of the present invention.
- 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 will be assigned with the same reference symbols, and redundant description thereof will be omitted as appropriate. The scales and shapes of each illustrated part are set for convenience in order to make the description easy to understand, and are not to be understood as limiting unless stated otherwise. The embodiments are merely examples and do not limit the scope of the present invention. All characteristics and combinations to be described in the embodiment are not necessarily essential to the invention.
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FIGS. 1 and 2 are views schematically illustrating acryocooler 10 according to one embodiment. As an example, thecryocooler 10 is a two-stage Gifford-McMahon (GM) cryocooler.FIG. 1 schematically illustrates acompressor 12 and anexpander 14 constituting the cryocooler together with acontrol device 100, andFIG. 2 illustrates the internal structure of theexpander 14 of thecryocooler 10. - The
compressor 12 is configured to collect the working gas of thecryocooler 10 from theexpander 14, pressurize the collected working gas, and supply the working gas to theexpander 14 again. Thecompressor 12 and theexpander 14 constitute a refrigeration cycle of thecryocooler 10, whereby thecryocooler 10 can provide desired cryogenic cooling. Theexpander 14 is also referred to as a cold head. The working gas is also referred to as a refrigerant gas and is usually a helium gas, but other suitable gas may be used. For the sake of understanding, the flow direction of the working gas is illustrated by an arrow inFIG. 1 . - In general, the pressure of the working gas supplied from the
compressor 12 to theexpander 14 and the pressure of the working gas collected from theexpander 14 to thecompressor 12 are both considerably higher than the atmospheric pressure, and are referred to as the first high pressure and the second high pressure, respectively. For convenience of description, the first high pressure and the second high pressure are also simply referred to as high pressure and low pressure, respectively. Typically, the high pressure is, for example, 2 to 3 MPa. The low pressure is, for example, 0.5 to 1.5 MPa, for example, approximately 0.8 MPa. For the sake of understanding, the flow direction of the working gas is indicated by an arrow. - The
expander 14 includes acryocooler cylinder 16 and adisplacer assembly 18. Thecryocooler cylinder 16 guides the linear reciprocating motion of thedisplacer assembly 18, and forms expansion chambers (32, 34) for the working gas with thedisplacer assembly 18. In addition, theexpander 14 includes apressure switching valve 40 that determines an intake start timing of the working gas into the expansion chamber and an exhaust start timing of the working gas from the expansion chamber. - In this specification, in order to describe the positional relationship between the components of the
cryocooler 10, for convenience, the side close to the top dead center of the axial reciprocation of the displacer is “upper”, and the side close to the bottom dead center is “lower”. The top dead center is the position of the displacer where the volume of the expansion space is maximum, and the bottom dead center is the position of the displacer where the volume of the expansion space is the minimum. Since a temperature gradient is generated in which the temperature drops from the upper side to the lower side in the axial direction during the operation of thecryocooler 10, the upper side can be referred to as a high temperature side and the lower side can be referred to as a low temperature side. - The
cryocooler cylinder 16 has afirst cylinder 16 a and asecond cylinder 16 b. As an example, thefirst cylinder 16 a and thesecond cylinder 16 b are members having a cylindrical shape, and thesecond cylinder 16 b has a diameter smaller than that of thefirst cylinder 16 a. Thefirst cylinder 16 a and thesecond cylinder 16 b are coaxially disposed, and a lower end of thefirst cylinder 16 a is rigidly connected to an upper end of thesecond cylinder 16 b. - The
displacer assembly 18 includes afirst displacer 18 a and asecond displacer 18 b connected to each other, and these move integrally. As an example, thefirst displacer 18 a and thesecond displacer 18 b are members having a cylindrical shape, and thesecond displacer 18 b has a diameter smaller than that of thefirst displacer 18 a. Thefirst displacer 18 a and thesecond displacer 18 b are disposed coaxially with each other. - The
first displacer 18 a is accommodated in thefirst cylinder 16 a, and thesecond displacer 18 b is accommodated in thesecond cylinder 16 b. Thefirst displacer 18 a can reciprocate in the axial direction along thefirst cylinder 16 a, and thesecond displacer 18 b can reciprocate in the axial direction along thesecond cylinder 16 b. - As illustrated in
FIG. 2 , thefirst displacer 18 a accommodates afirst regenerator 26. Thefirst regenerator 26 is formed by filling a tubular main body portion of thefirst displacer 18 a with a wire mesh such as copper or other appropriate first regenerator material. The upper lid portion and the lower lid portion of thefirst displacer 18 a may be provided as members separate from the main body portion of thefirst displacer 18 a, the upper lid portion and the lower lid portion of thefirst displacer 18 a may be fixed to the main body by appropriate means such as fastening or welding, and accordingly, the first regenerator material may be accommodated in thefirst displacer 18 a. - Similarly, the
second displacer 18 b accommodates asecond regenerator 28. Thesecond regenerator 28 is formed by filling a tubular main body portion of thesecond displacer 18 b with a non-magnetic regenerator material such as bismuth, a magnetic regenerator material such as HoCu2, or other appropriate second regenerator material. The second regenerator material may be formed in a granular shape. The upper lid portion and the lower lid portion of thesecond displacer 18 b may be provided as members separate from the main body portion of thesecond displacer 18 b, the upper lid portion and the lower lid portion of thesecond displacer 18 b may be fixed to the main body by appropriate means such as fastening or welding, and accordingly, the second regenerator material may be accommodated in thesecond displacer 18 b. - The
displacer assembly 18 forms aroom temperature chamber 30, afirst expansion chamber 32, and asecond expansion chamber 34 inside thecryocooler cylinder 16. Theexpander 14 includes afirst cooling stage 33 and asecond cooling stage 35 for heat exchange with a desired object or medium to be cooled by thecryocooler 10. Theroom temperature chamber 30 is formed between the upper lid portion of thefirst displacer 18 a and the upper portion of thefirst cylinder 16 a. Thefirst expansion chamber 32 is formed between the lower lid portion of thefirst displacer 18 a and thefirst cooling stage 33. Thesecond expansion chamber 34 is formed between the lower lid portion of thesecond displacer 18 b and thesecond cooling stage 35. Thefirst cooling stage 33 is fixed to the lower portion of thefirst cylinder 16 a to surround thefirst expansion chamber 32, and thesecond cooling stage 35 is fixed to the lower portion of thesecond cylinder 16 b to surround thesecond expansion chamber 34. - The
first regenerator 26 is connected to theroom temperature chamber 30 through a workinggas flow path 36 a formed in the upper lid portion of thefirst displacer 18 a, and is connected to thefirst expansion chamber 32 through a workinggas flow path 36 b formed in the lower lid portion of thefirst displacer 18 a. Thesecond regenerator 28 is connected to thefirst regenerator 26 through a workinggas flow path 36 c formed from the lower lid portion of thefirst displacer 18 a to the upper lid portion of thesecond displacer 18 b. In addition, thesecond regenerator 28 is connected to thesecond expansion chamber 34 through a workinggas flow path 36 d formed in the lower lid portion of thesecond displacer 18 b. - The working gas flow between the
first expansion chamber 32, thesecond expansion chamber 34, and theroom temperature chamber 30 is not the clearance between thecryocooler cylinder 16 and thedisplacer assembly 18, but afirst seal 38 a and asecond seal 38 b may be provided to be guided to thefirst regenerator 26 and thesecond regenerator 28. Thefirst seal 38 a may be mounted to the upper lid portion of thefirst displacer 18 a to be disposed between thefirst displacer 18 a and thefirst cylinder 16 a. Thesecond seal 38 b may be mounted to the upper lid portion of thesecond displacer 18 b to be disposed between thesecond displacer 18 b and thesecond cylinder 16 b. - As illustrated in
FIG. 1 , theexpander 14 includes acryocooler housing 20 that accommodates thepressure switching valve 40. Thecryocooler housing 20 is coupled to thecryocooler cylinder 16, thereby forming a hermetic container that accommodates thepressure switching valve 40 and thedisplacer assembly 18. - As illustrated in
FIG. 2 , thepressure switching valve 40 includes a high pressure valve 40 a and a low pressure valve 40 b, and is configured to generate periodic pressure fluctuations in thecryocooler cylinder 16. The working gas discharge port of thecompressor 12 is connected to theroom temperature chamber 30 via the high pressure valve 40 a, and the working gas suction port of thecompressor 12 is connected to theroom temperature chamber 30 via the low pressure valve 40 b. The high pressure valve 40 a and the low pressure valve 40 b are configured to selectively and alternately open and close (that is, when one is open, the other is closed). - The
pressure switching valve 40 may take the form of a rotary valve. That is, thepressure switching valve 40 may be configured such that the high pressure valve 40 a and the low pressure valve 40 b are alternately opened and closed by the rotational sliding of the valve disc with respect to the stationary valve body. In that case, anexpander motor 42 may be connected to thepressure switching valve 40 to rotate the valve disc of thepressure switching valve 40. For example, thepressure switching valve 40 is disposed such that the valve rotation axis is coaxial with the rotation axis of theexpander motor 42. - Alternatively, the high pressure valve 40 a and the low pressure valve 40 b may be valves that can be individually controlled. In this case, the
pressure switching valve 40 may not be connected to theexpander motor 42. - The
expander motor 42 is connected to adisplacer drive shaft 44 via amotion conversion mechanism 43 such as a Scotch yoke mechanism. Theexpander motor 42 is attached to thecryocooler housing 20. Themotion conversion mechanism 43 is accommodated in thecryocooler housing 20 similar to thepressure switching valve 40. Themotion conversion mechanism 43 converts the rotary motion output by theexpander motor 42 into a linear reciprocating motion of thedisplacer drive shaft 44. Thedisplacer drive shaft 44 extends from themotion conversion mechanism 43 into theroom temperature chamber 30, and is fixed to the upper lid portion of thefirst displacer 18 a. The rotation of theexpander motor 42 is converted into an axial reciprocation of thedisplacer drive shaft 44 by themotion conversion mechanism 43, and thedisplacer assembly 18 reciprocates linearly in thecryocooler cylinder 16 in the axial direction. - In addition, the
expander 14 may include atemperature sensor 46 that measures the temperature of the second cooling stage 35 (and/or the first cooling stage 33) and outputs a measured temperature signal indicating the measured temperature. - The
compressor 12 includes a highpressure gas outlet 50, a lowpressure gas inlet 51, a highpressure flow path 52, a lowpressure flow path 53, afirst pressure sensor 54, asecond pressure sensor 55, abypass line 56, a compressormain body 57, and acompressor housing 58. The highpressure gas outlet 50 is installed in thecompressor housing 58 as a working gas discharge port of thecompressor 12, and the lowpressure gas inlet 51 is installed in thecompressor housing 58 as a working gas suction port of thecompressor 12. The highpressure flow path 52 connects the discharge port of the compressormain body 57 to the highpressure gas outlet 50, and the lowpressure flow path 53 connects the lowpressure gas inlet 51 to the suction port of the compressormain body 57. Thecompressor housing 58 accommodates the highpressure flow path 52, the lowpressure flow path 53, thefirst pressure sensor 54, thesecond pressure sensor 55, thebypass line 56, and the compressormain body 57. Thecompressor 12 is also referred to as a compressor unit. - The compressor
main body 57 is configured to internally compress the working gas sucked from the suction port and discharge the working gas from the discharge port. For example, the compressormain body 57 may be a scroll type, a rotary type, or another pump for pressurizing the working gas. In this embodiment, the compressormain body 57 is configured to discharge a fixed and constant working gas flow rate. Alternatively, the compressormain body 57 may be configured to have a variable flow rate of the working gas to be discharged. The compressormain body 57 may be referred to as a compression capsule. - The
first pressure sensor 54 is disposed in the highpressure flow path 52 to measure the pressure of the working gas flowing through the highpressure flow path 52. Thefirst pressure sensor 54 is configured to output a first measured pressure signal PH indicating the measured pressure. Thesecond pressure sensor 55 is disposed in the lowpressure flow path 53 to measure the pressure of the working gas flowing through the lowpressure flow path 53. Thesecond pressure sensor 55 is configured to output a second measured pressure signal PL indicating the measured pressure. Therefore, thefirst pressure sensor 54 and thesecond pressure sensor 55 can also be referred to as a high pressure sensor and a low pressure sensor, respectively. Further, in this specification, any one of thefirst pressure sensor 54 and thesecond pressure sensor 55, or both of them may be collectively referred to as a “pressure sensor”. - The
bypass line 56 connects the highpressure flow path 52 to the lowpressure flow path 53 to bypass theexpander 14 and return the working gas from the highpressure flow path 52 to the lowpressure flow path 53. Thebypass line 56 is provided with arelief valve 60 for opening and closing thebypass line 56 or controlling the flow rate of the working gas flowing through thebypass line 56. Therelief valve 60 is configured to open when a differential pressure equal to or higher than a set pressure acts between the inlet and outlet of therelief valve 60. Therelief valve 60 may be an on/off valve or a flow control valve, and may be an electromagnetic valve, for example. The set pressure can be appropriately set based on the empirical knowledge of the designer, an experiment or simulation by the designer, or the like. In this manner, it is possible to prevent the differential pressure between thehigh pressure line 63 and thelow pressure line 64 from exceeding the set pressure and becoming excessive. In addition, it is possible to prevent the pressure of thehigh pressure line 63 from becoming excessive. - The
relief valve 60 may be configured to work as a so-called safety valve, that is, may be mechanically opened when a differential pressure equal to or higher than a set pressure acts between the inlet and outlet. Alternatively, therelief valve 60 may be opened and closed under the control of thecontrol device 100. Thecontrol device 100 compares the differential pressure between thehigh pressure line 63 and thelow pressure line 64 to be measured with the set pressure, therelief valve 60 may be controlled to open therelief valve 60 when the measured differential pressure is equal to or higher than the set pressure, and to close therelief valve 60 when the measured differential pressure is less than the set pressure. Thecontrol device 100 may acquire the measured differential pressures of thehigh pressure line 63 and thelow pressure line 64 based on the first measured pressure signal PH from thefirst pressure sensor 54 and the second measured pressure signal PL from thesecond pressure sensor 55. As another example, thecontrol device 100 compares the measured pressure of thehigh pressure line 63 with the upper limit pressure based on the first measured pressure signal PH, and therelief valve 60 may be controlled to open therelief valve 60 when the measured pressure is equal to or higher than the upper limit pressure, and to close therelief valve 60 when the measured pressure is less than the upper limit pressure. - The
compressor 12 may have various other components. For example, the highpressure flow path 52 may be provided with an oil separator, an adsorber, or the like. The lowpressure flow path 53 may be provided with a storage tank or other components. Further, thecompressor 12 may be provided with an oil circulation system that cools the compressormain body 57 with oil, a cooling system that cools the oil, or the like. - In addition, the
cryocooler 10 includes agas line 62 that circulates a working gas between thecompressor 12 and theexpander 14. Thegas line 62 includes thehigh pressure line 63 connecting thecompressor 12 to theexpander 14 to supply the working gas from thecompressor 12 to theexpander 14, and thelow pressure line 64 connecting thecompressor 12 to theexpander 14 to collect the working gas from theexpander 14 to thecompressor 12. Thecryocooler housing 20 of theexpander 14 is provided with a highpressure gas inlet 22 and a lowpressure gas outlet 24. The highpressure gas inlet 22 is connected to the highpressure gas outlet 50 by a high-pressure pipe 65, and the lowpressure gas outlet 24 is connected to the lowpressure gas inlet 51 by a low-pressure pipe 66. Thehigh pressure line 63 includes the high-pressure pipe 65 and the highpressure flow path 52, and thelow pressure line 64 includes the low-pressure pipe 66 and the lowpressure flow path 53. Thebypass line 56 may be considered to be a part of thegas line 62. Thebypass line 56 connects thehigh pressure line 63 to thelow pressure line 64 to bypass theexpander 14 and return the working gas from thehigh pressure line 63 to thelow pressure line 64. - Therefore, the working gas collected from the
expander 14 to thecompressor 12 enters the lowpressure gas inlet 51 of thecompressor 12 from the lowpressure gas outlet 24 of theexpander 14 through the low-pressure pipe 66, and further returns to the compressormain body 57 through the lowpressure flow path 53, is compressed by the compressormain body 57, and is pressurized. The working gas supplied from thecompressor 12 to theexpander 14 exits from the highpressure gas outlet 50 of thecompressor 12 through the highpressure flow path 52 from the compressormain body 57, and further supplied to theexpander 14 via the high-pressure pipe 65 and the highpressure gas inlet 22 of theexpander 14. - Furthermore, the
cryocooler 10 includes abuffer volume 70, asupply valve 72, and acollection valve 74. Thebuffer volume 70 is a volume for storing the working gas, and may be, for example, a buffer tank. Thesupply valve 72 connects thebuffer volume 70 to thelow pressure line 64, and thecollection valve 74 connects thebuffer volume 70 to thehigh pressure line 63. Thesupply valve 72 and thecollection valve 74 may be an on/off valve or a flow control valve, and may be an electromagnetic valve, for example. - The pressure of the
buffer volume 70 is a filling pressure of the working gas in thecryocooler 10 when the operation of thecryocooler 10 is stopped. When thecryocooler 10 is operating (for example, during initial cooling or steady operation), the pressure of thebuffer volume 70 is a pressure intermediate between the pressure of thehigh pressure line 63 and the pressure of the low pressure line 64 (for example, average pressure of high pressure and low pressure). - Therefore, when the
supply valve 72 is opened during the operation of thecryocooler 10, the working gas is supplied from thebuffer volume 70 to thelow pressure line 64 through thesupply valve 72. When thesupply valve 72 is closed, the supply of the working gas from thebuffer volume 70 to thelow pressure line 64 is stopped. Further, when thecollection valve 74 is opened, the working gas is collected from thehigh pressure line 63 to thebuffer volume 70 through thecollection valve 74. When thecollection valve 74 is closed, collection of the working gas from thehigh pressure line 63 to thebuffer volume 70 is stopped. By opening and closing thesupply valve 72 and thecollection valve 74 in this manner, the amount of the working gas circulating in thegas line 62 can be adjusted, and as a result, the pressures of thehigh pressure line 63 and thelow pressure line 64 can also be controlled. - As illustrated in
FIG. 1 , thecontrol device 100 that controls thecryocooler 10 includes acontroller 110 that controls thesupply valve 72 and thecollection valve 74. Thecontroller 110 is electrically connected to thefirst pressure sensor 54 and thesecond pressure sensor 55 to acquire the first measured pressure signal PH and the second measured pressure signal PL. As will be described later, thecontroller 110 receives the first measured pressure signal PH from thefirst pressure sensor 54, and opens and closes thesupply valve 72 and thecollection valve 74 based on the measured pressure of thehigh pressure line 63 indicated by the first measured pressure signal PH. Further, thecontroller 110 is electrically connected to thetemperature sensor 46 to acquire the measured temperature signal from thetemperature sensor 46. - In the illustrated example, the
control device 100 is provided separately from thecompressor 12 and theexpander 14, and is connected to these, but the present invention is not limited thereto. Thecontrol device 100 may be mounted on thecompressor 12. Thecontrol device 100 may be provided in theexpander 14, such as being mounted on theexpander motor 42. Thecontroller 110 may be provided in thesupply valve 72, in thecollection valve 74, or in each of thesupply valve 72 and thecollection valve 74. - The
control device 100 is realized as a hardware configuration by elements or circuits such as a CPU or memory of a computer, and is realized by a computer program or the like as a software configuration. InFIG. 1 , these are drawn as functional blocks realized by their cooperation as appropriate. It is understood by those skilled in the art that the functional blocks can be realized in various forms by combining hardware and software. - When the
compressor 12 and theexpander motor 42 are operated, thecryocooler 10 generates periodic volume fluctuations and pressure fluctuations of the working gas synchronized with the periodic volume fluctuations in thefirst expansion chamber 32 and thesecond expansion chamber 34. Typically, in the intake process, the low pressure valve 40 b is closed and the high pressure valve 40 a is opened, whereby the high pressure working gas flows from thecompressor 12 into theroom temperature chamber 30 through the high pressure valve 40 a, is supplied tofirst expansion chamber 32 through thefirst regenerator 26, and is supplied to thesecond expansion chamber 34 through thesecond regenerator 28. In this manner, thefirst expansion chamber 32 and thesecond expansion chamber 34 are pressurized from the low pressure to the high pressure. At this time, thedisplacer assembly 18 is moved upward from the bottom dead center to the top dead center, and the volumes of thefirst expansion chamber 32 and thesecond expansion chamber 34 are increased. When the high pressure valve 40 a is closed, the intake process ends. - In the exhaust process, the high pressure valve 40 a is closed and the low pressure valve 40 b is opened, whereby the high pressure
first expansion chamber 32 and thesecond expansion chamber 34 are opened to the low pressure working gas suction port of thecompressor 12, and thus the working gas expands in thefirst expansion chamber 32 and thesecond expansion chamber 34. As a result, the low pressure working gas is discharged from thefirst expansion chamber 32 and thesecond expansion chamber 34 to theroom temperature chamber 30 through thefirst regenerator 26 and thesecond regenerator 28. At this time, thedisplacer assembly 18 is moved downward from the top dead center to the bottom dead center, and the volumes of thefirst expansion chamber 32 and thesecond expansion chamber 34 are reduced. The working gas is collected from theexpander 14 to thecompressor 12 through the low pressure valve 40 b. When the low pressure valve 40 b is closed, the exhaust process ends. - In this manner, for example, a refrigeration cycle such as a GM cycle is configured, and the
first cooling stage 33 and thesecond cooling stage 35 are cooled to a desired cryogenic temperature. Thefirst cooling stage 33 can be cooled to a first cooling temperature in the range of, for example, approximately 20K to approximately 40K. Thesecond cooling stage 35 can be cooled to a second cooling temperature (for example, approximately 1K to approximately 4K) lower than the first cooling temperature. - The
cryocooler 10 can execute initial cooling and steady operation following the initial cooling. The initial cooling is an operation mode of theexpander 14 that rapidly cools from the initial temperature to the cryogenic temperature when thecryocooler 10 is started, and the steady operation is an operation mode of theexpander 14 that maintains a cryogenically cooled state by initial cooling. The initial temperature may be an ambient temperature (for example, room temperature). In addition, the initial cooling can also be performed when thecryocooler 10 is restarted after maintenance of a cryogenic device (for example, superconducting equipment such as a magnetic resonance imaging (MRI) system). During the maintenance, the object to be cooled in the cryogenic device may be kept at a relatively low temperature (for example, 20 to 80 K) without being raised to an ambient temperature. In this case, the initial temperature may be such a low temperature. - The
expander 14 is cooled to a standard cooling temperature by initial cooling, and is maintained within an allowable temperature range of cryogenic temperature including the standard cooling temperature in steady operation. The standard cooling temperature varies depending on the application and setting of thecryocooler 10, but is typically approximately 4.2 K or lower in, for example, an application for cooling a superconducting device. In some other cooling applications, the standard cooling temperature may be, for example, approximately 10K to 20K, or 10K or less. As described above, the initial cooling can also be referred to as a cooldown. - Incidentally, during the initial cooling, the density of the working gas increases in the
expander 14 as the temperature is lowered from the initial temperature to the cryogenic temperature. Along with this, the amount of the working gas accumulated in theexpander 14 increases, that is, the working gas is absorbed by theexpander 14 from thegas line 62. As a result, as the cooling of theexpander 14 progresses, the pressure of the working gas circulating in thegas line 62 gradually decreases. Since a decrease in the pressure of the working gas causes a decrease in the cooling capacity of thecryocooler 10, there is a concern that this may become a factor that lengthens the time required for the initial cooling. Since the initial cooling is merely a preparation because the cooling of the target object is started by the cryocooler, it is desired that the required time is as short as possible. - In order to cope with such a problem, in this embodiment, the
controller 110 controls thesupply valve 72 to keep the pressure of thehigh pressure line 63 within a preset appropriate pressure range based on the pressure of thehigh pressure line 63 measured by thefirst pressure sensor 54 during the initial cooling. More specifically, thecontroller 110 may compare the measured pressure of thehigh pressure line 63 with the lower limit value Pc of the appropriate pressure range during the initial cooling, and operate thesupply valve 72 to repeatedly open and close thesupply valve 72 such that the pressure of thehigh pressure line 63 does not fall below the lower limit value Pc. - Further, in this embodiment, the
controller 110 controls thecollection valve 74 to keep the pressure of thehigh pressure line 63 within an appropriate pressure range based on the pressure of thehigh pressure line 63 measured by thefirst pressure sensor 54 during the initial cooling. More specifically, thecontroller 110 may compare the measured pressure of thehigh pressure line 63 with an upper limit value Pd of the appropriate pressure range during the initial cooling, and operate thecollection valve 74 to repeatedly open and close thecollection valve 74 such that the pressure of thehigh pressure line 63 does not exceed the upper limit value Pd. -
FIG. 3 is a flowchart for describing a method for controlling thecryocooler 10 according to one embodiment. This method is repeatedly executed by thecontroller 110 in a predetermined cycle in the initial cooling of thecryocooler 10. This method may be continuously executed not only during the initial cooling but also during the steady operation of thecryocooler 10. - First, the pressure of the
high pressure line 63 is measured (S10). Thefirst pressure sensor 54 measures the pressure of thehigh pressure line 63, and outputs the first measured pressure signal PH indicating the measured pressure of thehigh pressure line 63. Thecontroller 110 receives the first measured pressure signal PH and acquires the measured pressure of thehigh pressure line 63. - Next, the measured pressure of the
high pressure line 63 is compared with an appropriate pressure range (S12). The lower limit value Pc of the appropriate pressure range is set such that thecryocooler 10 provides a sufficient cooling capacity. The upper limit value Pd of the appropriate pressure range is set not to generate excessive pressure in thehigh pressure line 63. The upper limit value Pd of the appropriate pressure range may be set to a pressure value smaller than the above-described set pressure at which therelief valve 60 is opened. The appropriate pressure range can be appropriately set based on the empirical knowledge of the designer, an experiment or simulation by the designer, or the like. The appropriate pressure range may be stored in advance in thecontroller 110 as an initial setting of thecryocooler 10, or may be set in thecontroller 110 by the user before thecryocooler 10 is operated. - As an example, the upper limit value Pd and the lower limit value Pc of the appropriate pressure range may be selected from, for example, a range of 2 MPa to 3 MPa or a range of 2.1 MPa to 2.7 MPa. The width of the appropriate pressure range, that is, the difference between the upper limit value Pd and the lower limit value Pc of the appropriate pressure range may be set to a certain value within 0.5 MPa, 0.3 MPa, or 0.1 MPa, for example. For example, the appropriate pressure range may be set to 2.45±0.05 MPa. In this case, the width of the appropriate pressure range is 0.1 MPa, the upper limit value Pd is 2.5 MPa, and the lower limit value Pc is 2.4 MPa.
- The
controller 110 compares the measured pressure of thehigh pressure line 63 with the lower limit value Pc of the appropriate pressure range, and opens thesupply valve 72 when the measured pressure of thehigh pressure line 63 falls below the lower limit value Pc (PH<Pc) (S14). In this manner, the working gas is supplied from thebuffer volume 70 to thelow pressure line 64 through thesupply valve 72. Since the amount of the working gas circulating in thegas line 62 increases, the pressure in thehigh pressure line 63 is restored. - The
controller 110 closes thesupply valve 72 when the measured pressure of thehigh pressure line 63 is restored to an appropriate pressure range (S16). For example, thecontroller 110 may compare the measured pressure of thehigh pressure line 63 with the lower limit value Pc of the appropriate pressure range, and close thesupply valve 72 when the measured pressure of thehigh pressure line 63 exceeds the lower limit value Pc (PH>Pc or PH≥Pc). When thesupply valve 72 is closed, the supply of the working gas from thebuffer volume 70 to thelow pressure line 64 is stopped. In this manner, the present method ends, and is executed again in the next control cycle. - The pressure threshold for closing the
supply valve 72 may be different from the lower limit value Pc of the appropriate pressure range, and may be larger than the lower limit value Pc, for example. The pressure threshold may be set not to exceed the upper limit value Pd of the appropriate pressure range. For example, the pressure threshold may be a value obtained by adding a predetermined ratio of a width of an appropriate pressure range (upper limit value Pd−lower limit value Pc) to the lower limit value Pc. For example, the predetermined ratio may be 50% or less, 30% or less, or 10% or less. -
FIG. 4 is a flowchart for describing a method for controlling thecryocooler 10 according to one embodiment. This method is repeatedly executed by thecontroller 110 in a predetermined cycle in the initial cooling of thecryocooler 10. This method may be executed in parallel with the method illustrated inFIG. 3 . This method may be continuously executed not only during the initial cooling but also during the steady operation of thecryocooler 10. - First, the pressure of the
high pressure line 63 is measured using the first pressure sensor 54 (S20). Thecontroller 110 receives the first measured pressure signal PH from thefirst pressure sensor 54, and acquires the measured pressure of thehigh pressure line 63. - Next, the measured pressure of the
high pressure line 63 is compared with an appropriate pressure range (S22). Thecontroller 110 compares the measured pressure of thehigh pressure line 63 with the upper limit value Pd of the appropriate pressure range, and opens thecollection valve 74 when the measured pressure of thehigh pressure line 63 exceeds the upper limit value Pd (PH>Pd) (S24). As a result, the working gas is collected from thehigh pressure line 63 to thebuffer volume 70 through thecollection valve 74, and the pressure of thehigh pressure line 63 decreases. - The
controller 110 closes thecollection valve 74 when the measured pressure of thehigh pressure line 63 is restored to an appropriate pressure range (S26). For example, thecontroller 110 may compare the measured pressure of thehigh pressure line 63 with the upper limit value Pd of the appropriate pressure range, and close thecollection valve 74 when the measured pressure of thehigh pressure line 63 falls below the upper limit value Pd (PH<Pd or PH Pd). When thecollection valve 74 is closed, collection of the working gas from thehigh pressure line 63 to thebuffer volume 70 is stopped. In this manner, the present method ends, and is executed again in the next control cycle. - The pressure threshold for closing the
collection valve 74 may be different from the upper limit value Pd of the appropriate pressure range, and may be smaller than, for example, the upper limit value Pd. This pressure threshold may be selected from an appropriate pressure range, that is, may be larger than the lower limit value Pc of an appropriate pressure range. - The appropriate pressure range may be changed during the operation of the
cryocooler 10. For example, the appropriate pressure range in the initial cooling may be different from the appropriate pressure range in the steady operation, and may be higher than the appropriate pressure range in the steady operation, for example. For example, the lower limit value Pc in the initial cooling may be higher than the lower limit value Pc in the steady operation, and/or the upper limit value Pd in the initial cooling may be higher than the upper limit value Pd in the steady operation. - In this case, the switching from the initial cooling to the steady operation and the change of the appropriate pressure range may be controlled by the
control device 100. For example, thecontrol device 100 may compare the measured temperature of the second cooling stage 35 (and/or the first cooling stage 33) with the above-described standard cooling temperature based on the measured temperature signal from thetemperature sensor 46, execute the initial cooling when the measured temperature is higher than the standard cooling temperature, and shift from the initial cooling to the steady operation when the measured temperature is equal to or lower than the standard cooling temperature. Thecontroller 110 may change the appropriate pressure range with the shift from the initial cooling to the steady operation. - Further, as will be described later with reference to
FIGS. 7 and 8 , the switching from the initial cooling to the steady operation and the change of the appropriate pressure range may be performed based on the pressure of thebuffer volume 70 or based on the differential pressure of thehigh pressure line 63 and thelow pressure line 64. In this manner, thecontrol device 100 can complete the initial cooling of thecryocooler 10 without depending on thetemperature sensor 46. - Here, in order to ensure the supply of the working gas from the
buffer volume 70, a condition desired for thebuffer volume 70 is considered. From the state equation of the ideal gas, while the operation of thecryocooler 10 is stopped (that is, before the initial cooling), -
PI(VH+VL+VB)=nRT (1) - is established. Here, PI (MPa) indicates the working gas filling pressure of the
cryocooler 10 at the temperature T (K), VH (L) indicates the volume of thehigh pressure line 63, VL (L) indicates the volume of thelow pressure line 64, VB (L) indicates the volume of thebuffer volume 70, n (mol) indicates the amount of the working gas in thecryocooler 10, and R represents the gas constant. - Similarly, during the steady operation of the
cryocooler 10, -
PHVH+PLVL+PBVB=nRT (2) - is established. Here, PH (MPa) indicates the pressure of the
high pressure line 63 in the steady operation at the temperature T, PL (MPa) indicates the pressure of thelow pressure line 64 in the steady operation at the temperature T, and PB (MPa) indicates the pressure of thebuffer volume 70 in the steady operation at the temperature T. - From Equations (1) and (2),
-
PI(VH+VL+VB)=PHVH+PLVL+PBVB (3) - is established.
- In order to supply the working gas from the
buffer volume 70 to thelow pressure line 64 at any timing during the operation of thecryocooler 10, for any temperature T in a temperature range from the initial temperature of thecryocooler 10 to the cryogenic temperature, -
PL≤PB (4) - is supposed to be satisfied.
- When Equation (3) is solved for PB and substituted into Equation (4), the following relationship is obtained.
-
VB≥VH(PH−PI)/(PI−PL)−VL (5) - Therefore, in order to ensure the supply of the working gas from the
buffer volume 70 to thelow pressure line 64, it is preferable that thebuffer volume 70 satisfies Equation (5) for any temperature in the temperature range from the initial temperature to the cryogenic temperature. - Similarly, in order to ensure gas collection to the
buffer volume 70, a condition desired for thebuffer volume 70 is considered. In this case, in order to supply the working gas from thebuffer volume 70 to thehigh pressure line 63 at any timing during the operation of thecryocooler 10, for any temperature T in a temperature range from the initial temperature of thecryocooler 10 to the cryogenic temperature, -
PB≤PH (6) - is supposed to be satisfied.
- When Equation (3) is solved for PB and substituted into Equation (6), the following relationship is obtained.
-
VB≥−VH+VL(PI−PL)/(PH−PI) (7) - Therefore, in order to ensure the collection of the working gas from the
high pressure line 63 to thebuffer volume 70, it is preferable that thebuffer volume 70 satisfies Equation (7) for any temperature in the temperature range from the initial temperature to the cryogenic temperature. -
FIG. 5 is a graph illustrating an example of time-dependent changes in temperature and pressure during the operation of thecryocooler 10 according to one embodiment. The illustrated pressure change is acquired by an experiment, and in the upper part ofFIG. 5 , the pressure PH of thehigh pressure line 63 measured by thefirst pressure sensor 54 and the pressure PL of thelow pressure line 64 measured by thesecond pressure sensor 55 are illustrated. A temperature T1 of thefirst cooling stage 33 and a temperature T2 of thesecond cooling stage 35 are illustrated in the lower part ofFIG. 5 . The horizontal axis represents time. - Before the
cryocooler 10 starts (time 0), both the pressure PH of thehigh pressure line 63 and the pressure PL of thelow pressure line 64 are the filling pressures PI, and the temperature T1 of thefirst cooling stage 33 and the temperature T2 of thesecond cooling stage 35 are room temperature (approximately 300K). When thecryocooler 10 is started and the initial cooling is started, thecompressor 12 and theexpander 14 work, the pressure PH of thehigh pressure line 63 is increased from the filling pressure PI, and the pressure PL of thelow pressure line 64 decreases from the filling pressure PI. Due to the initial cooling, the temperature T1 of thefirst cooling stage 33 and the temperature T2 of thesecond cooling stage 35 decrease. When thefirst cooling stage 33 and thesecond cooling stage 35 are each cooled to the above-described standard cooling temperature (for example, T1≤30K, T2≤4K), the initial cooling is completed and shifted to the steady operation. -
FIG. 6A schematically illustrates an enlarged portion A illustrated inFIG. 5 , andFIG. 6B schematically illustrates an enlarged portion B illustrated inFIG. 5 .FIG. 6A illustrates the pressure PH of thehigh pressure line 63 immediately after the start of the initial cooling together with the open/closed state of thecollection valve 74, andFIG. 6B illustrates the pressure PH of thehigh pressure line 63 after the portion A together with the open/closed state of thesupply valve 72. - As illustrated in
FIG. 6A , when the pressure PH of thehigh pressure line 63 exceeds the upper limit value Pd of the appropriate pressure range, thecollection valve 74 is opened. Since the working gas is collected from thehigh pressure line 63 to thebuffer volume 70 through thecollection valve 74, the pressure PH of thehigh pressure line 63 decreases. When the pressure PH of thehigh pressure line 63 falls below the upper limit pressure Pd, thecollection valve 74 is closed. In this manner, excessive pressurization of thehigh pressure line 63 can be avoided. The risk of an emergency stop of thecompressor 12 due to excessive pressurization is reduced. Further, since thebuffer volume 70 is pressurized by collecting the working gas, which leads to effective utilization for supplying the working gas from thebuffer volume 70 to thelow pressure line 64. - As illustrated in
FIG. 6B , when the pressure PH of thehigh pressure line 63 falls below the lower limit value Pc of the appropriate pressure range, thesupply valve 72 is opened. The working gas is supplied from thebuffer volume 70 to thelow pressure line 64 through thesupply valve 72. Since the amount of the working gas circulating in thegas line 62 increases, the pressure in thehigh pressure line 63 is restored. In this manner, when the pressure PH of thehigh pressure line 63 exceeds the lower limit value Pc, thesupply valve 72 is closed. - As described above, the density of the working gas increases in the
expander 14 due to the temperature decrease of theexpander 14 during the initial cooling, which has the effect of lowering the pressure PH of thehigh pressure line 63. Therefore, even when the pressure PH of thehigh pressure line 63 is restored once, the pressure PH falls below the lower limit value Pc again. Thesupply valve 72 is opened again, the pressure in thehigh pressure line 63 is restored, and thesupply valve 72 is closed. In this manner, thesupply valve 72 operates to repeatedly open and close to maintain the pressure PH of thehigh pressure line 63 within an appropriate pressure range. - When the working gas is not supplied to the
gas line 62 during the initial cooling, the pressure PH of thehigh pressure line 63 may significantly decrease due to the temperature decrease of theexpander 14. Since the cooling capacity of thecryocooler 10 correlates with the pressure PH of thehigh pressure line 63, the cooling capacity of thecryocooler 10 may decrease as the initial cooling progresses. This can be a factor that increases the time required for the initial cooling. - On the other hand, according to the embodiment, the pressure PH of the
high pressure line 63 can be maintained within an appropriate pressure range by controlling thesupply valve 72 during the initial cooling. Therefore, the cooling capacity of thecryocooler 10 can be appropriately maintained, and an increase in the initial cooling time can be suppressed. Further, by keeping the pressure PH of thehigh pressure line 63 substantially constant, thecryocooler 10 can provide a stable cooling capacity. - In order to maintain the pressure PH of the
high pressure line 63 within an appropriate pressure range, a method for controlling thesupply valve 72 and thecollection valve 74 based on the pressure of thelow pressure line 64 is also conceivable. The pressure of thelow pressure line 64 is affected by the cooling temperature of the expander 14 (varies depending on the cooling temperature). Therefore, it is practically indispensable to set an appropriate pressure range of thelow pressure line 64, that is, a pressure threshold of thelow pressure line 64 for opening and closing thesupply valve 72 and thecollection valve 74 to a different value depending on the cooling temperature, and the design of the control becomes complicated. Further, even when thelow pressure line 64 is within an appropriate pressure range, there may be a case where the pressure of thehigh pressure line 63 is excessively high depending on the cooling temperature. Therefore, a method based on the pressure of thehigh pressure line 63 as in the embodiment is advantageous in that such inconvenience is alleviated or prevented. -
FIG. 7 is a graph illustrating an example of changes in temperature and pressure during the operation of thecryocooler 10 according to one embodiment.FIG. 8 is a view schematically illustrating thecryocooler 10 according to one embodiment. - Similar to the above-described embodiment, the
cryocooler 10 includes thecompressor 12, theexpander 14, thebuffer volume 70, and thecontrol device 100. Thecontroller 110 controls thesupply valve 72 to keep the pressure of thehigh pressure line 63 within a preset appropriate pressure range based on the pressure of thehigh pressure line 63 measured by thefirst pressure sensor 54 during the initial cooling. Further, thecontroller 110 controls thecollection valve 74 to keep the pressure of thehigh pressure line 63 within an appropriate pressure range based on the pressure of thehigh pressure line 63 measured by thefirst pressure sensor 54 during the initial cooling. - The
cryocooler 10 includes abuffer pressure sensor 76 connected to thebuffer volume 70 to measure the pressure of thebuffer volume 70. Thebuffer pressure sensor 76 is electrically connected to thecontrol device 100, and is configured to output a measured buffer pressure signal PB representing the measured pressure to thecontrol device 100. - In the upper part of
FIG. 7 , in addition to the pressure PH of thehigh pressure line 63 and the pressure PL of thelow pressure line 64 illustrated inFIG. 5 , the pressure PB of thebuffer volume 70 measured by thebuffer pressure sensor 76 is illustrated. The temperature T1 of thefirst cooling stage 33 and the temperature T2 of thesecond cooling stage 35 are illustrated in the lower part ofFIG. 7 . As will be understood fromFIG. 7 , when thecryocooler 10 is sufficiently cooled by the completion of the initial cooling and the temperatures of thefirst cooling stage 33 and thesecond cooling stage 35 are stabilized, the pressure PH of thehigh pressure line 63 and the pressure PL of thelow pressure line 64 are also stabilized. At this time, both thesupply valve 72 and thecollection valve 74 are closed, and thebuffer volume 70 is disconnected from thegas line 62. Therefore, the pressure PB of thebuffer volume 70 is also constant (final buffer pressure PF illustrated inFIG. 7 ). - Therefore, the completion of the initial cooling can be determined by detecting the stabilization of the pressure PB having the
buffer volume 70. When the working gas filling pressure PI of thecryocooler 10 and operating conditions (for example, high pressure PH, low pressure PL, temperatures T1, T2, and the like) are known, the final pressure of thebuffer volume 70 when the initial cooling is completed can be predicted. In this case, thecontroller 110 may compare the predicted value of the final buffer pressure with the measured pressure PB of thebuffer volume 70, and based on the comparison result, thecontroller 110 may determine whether or not the measured pressure PB of thebuffer volume 70 is equal to the predicted value of the final buffer pressure. Thecontroller 110 may complete the initial cooling when a state where the measured pressure PB of thebuffer volume 70 is equal to the predicted value of the final buffer pressure continues for a predetermined time (for example, several minutes). - Alternatively, the
controller 110 may calculate a difference between the measured pressure PB of thebuffer volume 70 and a reference pressure during the initial cooling, and detect the stabilization of the calculated pressure difference, to determine the completion of the initial cooling. The reference pressure may be the pressure of the previously measuredbuffer volume 70, and may be, for example, the maximum value PM of the pressure of thebuffer volume 70 measured during the initial cooling. It is understood fromFIG. 7 that the pressure of thebuffer volume 70 increases from the filling pressure PI and takes the maximum value PM immediately after the start of the initial cooling. - The
controller 110 may compare the calculated pressure difference (that is, the difference between the measured pressure PB of thebuffer volume 70 and the reference pressure) with the pressure difference target value, and based on the comparison result, thecontroller 110 may determine whether or not the calculated pressure difference is equal to the pressure difference target value. Thecontroller 110 may complete the initial cooling when a state where the calculated pressure difference is equal to the pressure difference target value continues for a predetermined time. For example, the predetermined time may be selected from a range of 1 minute or more and 10 minutes or less. When the difference between the calculated pressure difference and the pressure difference target value is within a predetermined value (for example, 0.05 MPa), it can be considered that the calculated pressure difference is equal to the pressure difference target value. Since this pressure difference target value does not depend on the filling pressure PI, it is possible to determine the completion of the initial cooling even when the filling pressure PI is unknown. - As another example of the reference pressure, the pressure PH of the high pressure line 63 (or the pressure PL of the low pressure line 64) measured at the same timing as the measured pressure PB of the
buffer volume 70 may be used. Thecontroller 110 may calculate a difference between the measured pressure PB of thebuffer volume 70 and the measured pressure PH of the high pressure line 63 (or the measured pressure PL of the low pressure line 64), and detect the stabilization of the calculated pressure difference, to determine the completion of the initial cooling. Similar to the above example, thecontroller 110 may compare the calculated pressure difference with the pressure difference target value, and when the calculated pressure difference is equal to the pressure difference target value over a predetermined time, thecontroller 110 may complete the initial cooling. - As a further alternative example, the
controller 110 may calculate the difference between the measured pressure PH of thehigh pressure line 63 and the measured pressure PL of thelow pressure line 64, and detect the stabilization of the calculated pressure difference, to determine the completion of the initial cooling. - In the above-described embodiment, the
supply valve 72 is controlled (hereinafter, also referred to as high pressure priority control) based on the measured pressure of thehigh pressure line 63 during the initial cooling, and the pressure of thehigh pressure line 63 is kept within an appropriate pressure range. At this time, since the pressure of thelow pressure line 64 is not managed, there is a possibility that an undesired phenomenon such that the pressure of thelow pressure line 64 becomes extremely low may occur in some cases. - In order to cope with such a problem, the
controller 110 may be configured to discontinue the control (that is, high pressure priority control) of thesupply valve 72 based on the pressure of thehigh pressure line 63 when the pressure of thelow pressure line 64 measured by thesecond pressure sensor 55 falls below a preset low pressure threshold. Thecontroller 110 may be configured to control thesupply valve 72 to restore the pressure of thelow pressure line 64 to the low pressure threshold based on the pressure of thelow pressure line 64 measured by thesecond pressure sensor 55. In the following, the control of thesupply valve 72 based on the pressure of thelow pressure line 64 will also be referred to as low pressure priority control. An example of the switching processing from the high pressure priority control to the low pressure priority control will be described later with reference toFIG. 9 . -
FIG. 9 is a flowchart for describing a method for controlling thecryocooler 10 according to one embodiment. This method is repeatedly executed by thecontroller 110 in a predetermined cycle in the initial cooling of thecryocooler 10. This method may be continuously executed not only during the initial cooling but also during the steady operation of thecryocooler 10. - First, the pressure of the
low pressure line 64 is measured (S30). Thesecond pressure sensor 55 measures the pressure of thelow pressure line 64, and outputs the second measured pressure signal PL indicating the measured pressure of thelow pressure line 64. Thecontroller 110 receives the second measured pressure signal PL and acquires the measured pressure of thelow pressure line 64. - Next, the measured pressure PL of the
low pressure line 64 is compared with a low pressure threshold Pe (S32). For example, the low pressure threshold Pe may be set as a lower limit value of the pressure of thelow pressure line 64 from the viewpoint of guaranteeing stable operation of thecompressor 12. For example, the low pressure threshold Pe may be selected from a range of 0.2 MPa to 0.4 MPa. The low pressure threshold Pe can be appropriately set based on the empirical knowledge of the designer, an experiment or simulation by the designer, or the like. The low pressure threshold Pe may be stored in advance in thecontroller 110 as an initial setting of thecryocooler 10, or may be set in thecontroller 110 by the user before thecryocooler 10 is operated. - The
controller 110 compares the measured pressure of thelow pressure line 64 with the low pressure threshold Pe, and when the measured pressure of thelow pressure line 64 exceeds the low pressure threshold Pe (PL>Pe or PL≥Pe), the high pressure priority control is selected (S34). In this case, as described with reference toFIG. 3 , thecontroller 110 compares the measured pressure of thehigh pressure line 63 with the lower limit value Pc of the appropriate pressure range, and operate thesupply valve 72 to repeatedly open and close thesupply valve 72 such that the pressure of thehigh pressure line 63 does not fall below the lower limit value Pc. In this manner, the high pressure priority control is continuously executed. - On the other hand, when the measured pressure of the
low pressure line 64 falls below the low pressure threshold Pe (PL<Pe), thecontroller 110 selects the low pressure priority control (S36). The high pressure priority control is discontinued, and the low pressure priority control is started. An example of the low pressure priority control will be described later with reference toFIG. 10 . In this manner, the switching processing from the high pressure priority control to the low pressure priority control ends. - In the low pressure priority control, first, as illustrated in
FIG. 10 , the pressure of thelow pressure line 64 is measured (S40). Next, the measured pressure of thelow pressure line 64 is compared with the low pressure threshold Pe (S42). When the measured pressure of thelow pressure line 64 falls below the low pressure threshold Pe (PL<Pe), thecontroller 110 opens the supply valve 72 (S44). In this manner, the working gas is supplied from thebuffer volume 70 to thelow pressure line 64 through thesupply valve 72, and the pressure of thelow pressure line 64 is restored. On the other hand, when the measured pressure of - the
low pressure line 64 exceeds the low pressure threshold Pe (PL>Pe or PL≥Pe), thecontroller 110 closes the supply valve 72 (S46). The supply of the working gas from thebuffer volume 70 to thelow pressure line 64 is stopped. The pressure threshold for closing thesupply valve 72 may be different from the low pressure threshold Pe, and may be somewhat larger than, for example, the low pressure threshold Pe. In this manner, the present method ends, and is executed again in the next control cycle. - According to the low pressure priority control described above, the
supply valve 72 is opened and closed based on the pressure of thelow pressure line 64, and the pressure of thelow pressure line 64 can be restored to the low pressure threshold Pe. However, in the low pressure priority control, the pressure of thehigh pressure line 63 is not managed. Therefore, during the low pressure priority control, there is a possibility that an undesired phenomenon such that the pressure of thehigh pressure line 63 becomes extremely low may occur. - Therefore, the
controller 110 may be configured - to discontinue the control of the
supply valve 72 based on the pressure of thelow pressure line 64 when the pressure of thehigh pressure line 63 measured by thefirst pressure sensor 54 falls below the high pressure threshold. Thecontroller 110 may be configured to control thesupply valve 72 to restore the pressure of thehigh pressure line 63 to the high pressure threshold based on the pressure of thehigh pressure line 63 measured by thefirst pressure sensor 54. An example of the return processing from the low pressure priority control to the high pressure priority control will be described later with reference toFIG. 11 . -
FIG. 11 is a flowchart for describing a method for controlling thecryocooler 10 according to one embodiment. During the execution of the low pressure priority control described above, this method is repeatedly executed by thecontroller 110 at a predetermined cycle. - First, the pressure of the
high pressure line 63 is measured (S50). Next, the measured pressure of thehigh pressure line 63 is compared with a high pressure threshold Pf (S52). For example, the high pressure threshold Pf may be the lower limit value Pc within an appropriate pressure range. The high pressure threshold Pf can be appropriately set based on the empirical knowledge of the designer, an experiment or simulation by the designer, or the like. The high pressure threshold Pf may be stored in advance in thecontroller 110 as an initial setting of thecryocooler 10, or may be set in thecontroller 110 by the user before thecryocooler 10 is operated. - The
controller 110 compares the measured pressure of thehigh pressure line 63 with the high pressure threshold Pf, and when the measured pressure of thehigh pressure line 63 exceeds the high pressure threshold Pf (PH>Pf or PH≥Pf), the low pressure priority control is selected (S54). In this case, the low pressure priority control is continuously executed. - On the other hand, when the measured pressure of the
high pressure line 63 falls below the high pressure threshold Pf (PH<Pf), thecontroller 110 selects the high pressure priority control (S56). In this manner, the switching processing from the high pressure priority control to the low pressure priority control ends. By switching to the high pressure priority control again, thesupply valve 72 is controlled based on the measured pressure of thehigh pressure line 63, and the pressure of thehigh pressure line 63 is maintained within an appropriate pressure range. - Incidentally, by increasing the operating differential pressure of the cryocooler 10 (the pressure difference between the
high pressure line 63 and the low pressure line 64), and by increasing the cooling capacity of thecryocooler 10, the time required for initial cooling can also be shortened. However, in the above-described embodiment, therelief valve 60 bypassing thehigh pressure line 63 and thelow pressure line 64 may be an obstacle. When therelief valve 60 is of a type that is mechanically opened when a differential pressure equal to or higher than a set pressure acts between the inlet and outlet of therelief valve 60, the operating differential pressure of thecryocooler 10 may be limited to this set pressure. This is because, when the pressure difference between thehigh pressure line 63 and thelow pressure line 64 exceeds the set pressure of therelief valve 60, therelief valve 60 is mechanically opened, the working gas flows out from thehigh pressure line 63 to thelow pressure line 64 through therelief valve 60, and as a result, an increase in the operating differential pressure of thecryocooler 10 may be impeded. - In order to cope with this, additional compressors may be temporarily installed in the
cryocooler 10 for initial cooling, as described below. In the following, for convenience of description, themain compressor 12 of thecryocooler 10 will be referred to as afirst compressor 12, and the sub-compressor to be added will be referred to as asecond compressor 80. -
FIGS. 12 and 13 are views schematically illustrating thecryocooler 10 according to another embodiment.FIG. 12 illustrates the settings of thecryocooler 10 in the initial cooling, andFIG. 13 illustrates the basic settings of thecryocooler 10 in steady operation before or after the initial cooling.FIG. 14 is a flowchart for describing a method for operating thecryocooler 10 according to another embodiment. - The
cryocooler 10 and the method for operating the same according to another embodiment can be the same as thecryocooler 10 and the method for operating method the same according to one embodiment, except for thesecond compressor 80. Therefore, inFIGS. 12 and 13 , the same reference numerals will be assigned to the configurations common to one embodiment, and detailed description thereof will be appropriately omitted in order to avoid redundancy. - The
cryocooler 10 takes a basic setting including thefirst compressor 12 and theexpander 14 as illustrated inFIG. 13 before the initial cooling is performed. Thefirst compressor 12 and theexpander 14 are connected by thehigh pressure line 63 and thelow pressure line 64. Thesecond compressor 80 and thebuffer volume 70 are not connected to thecryocooler 10. - In the method for operating the
cryocooler 10 according to another embodiment, as illustrated inFIG. 14 , thesecond compressor 80 and thebuffer volume 70 are connected to thecryocooler 10 as pretreatment for initial cooling (S60, S61). The attachment order of thesecond compressor 80 and thebuffer volume 70 is not limited. - The
second compressor 80 is connected in series with thefirst compressor 12 on thehigh pressure line 63. More specifically, as illustrated inFIG. 12 , the highpressure gas outlet 50 of thefirst compressor 12 is connected to the suction port of thesecond compressor 80, and the discharge port of thesecond compressor 80 is connected to the highpressure gas inlet 22 of theexpander 14. Therefore, thecryocooler 10 has a two-stage compressor configuration including thefirst compressor 12 and thesecond compressor 80. - The
buffer volume 70 is connected to thelow pressure line 64 via thesupply valve 72 and is connected to thehigh pressure line 63 via thecollection valve 74. Thesupply valve 72 and thecollection valve 74 may be accommodated in one housing together with thebuffer volume 70 to form a buffer volume unit. The buffer volume unit and thesecond compressor 80 may be brought to the site where thecryocooler 10 is operated, for example, by a serviceman and connected to thecryocooler 10. - When the
second compressor 80 and thebuffer volume 70 are connected to thecryocooler 10 in this manner, thecryocooler 10 is started and initial cooling is started (S62). As described above, the initial cooling is a process of cooling thecryocooler 10 from the initial temperature to the target cryogenic temperature in preparation for steady operation of thecryocooler 10. The initial temperature may be an ambient temperature (for example, room temperature), or may be a temperature lower than the ambient temperature and higher than a target cryogenic temperature (for example, a temperature selected from a range of 20K to 80K). By the initial cooling, thefirst cooling stage 33 of theexpander 14 is cooled to the first cooling temperature, and thesecond cooling stage 35 is cooled to the second cooling temperature. - The initial cooling is executed in a state where the
second compressor 80 and thebuffer volume 70 are connected to thecryocooler 10. Therefore, in the initial cooling, the working gas is supplied to theexpander 14 by using thefirst compressor 12 and thesecond compressor 80. Thefirst compressor 12 pressurizes the working gas of thecryocooler 10 collected from theexpander 14 through thelow pressure line 64, and supplies the pressurized working gas to thesecond compressor 80. Thesecond compressor 80 further pressurizes the working gas from thefirst compressor 12, and supplies this to theexpander 14 again. - Further, in the initial cooling, the
buffer volume 70 is used to keep the pressure of thehigh pressure line 63 within an appropriate pressure range, as in one embodiment. That is, thesupply valve 72 performs control to keep the pressure of thehigh pressure line 63 within an appropriate pressure range based on the pressure of thehigh pressure line 63 measured by thefirst pressure sensor 54 during the initial cooling. - When the initial cooling is completed, the
second compressor 80 and thebuffer volume 70 are removed from the cryocooler 10 (S63, S64). The order of removal of thesecond compressor 80 and thebuffer volume 70 is not limited. Thecryocooler 10 is returned to the basic setting illustrated inFIG. 14 . Then, a steady operation of thecryocooler 10 is performed (S65). - According to another embodiment, the operating differential pressure of the
cryocooler 10 can be increased by adding thesecond compressor 80. In particular, the operating differential pressure of thecryocooler 10 can be increased exceeding the limitation caused by the set pressure of therelief valve 60 of thefirst compressor 12 described above. An increase in the operating differential pressure causes an increase in the cooling capacity of thecryocooler 10, and can shorten the time required for initial cooling. - As another method for increasing the operating differential pressure of the
cryocooler 10, it is conceivable to bring a large-sized compressor having a higher output than thefirst compressor 12 to the site from the outside and replace thefirst compressor 12 with the large-sized compressor. However, such a large-sized compressor is generally unsuitable for carrying because the large-sized compressor is large in size and weight. On the other hand, since thesecond compressor 80 is used in combination with thefirst compressor 12, thesecond compressor 80 may be relatively small in size and is easy to carry. - In the above-described embodiment, the
second compressor 80 is connected to the discharge side (outlet side) of thefirst compressor 12 in order to form a two-stage compressor configuration. However, other configurations are possible. For example, in principle, thesecond compressor 80 may be connected to the suction side (inlet side) of thefirst compressor 12. That is, thesecond compressor 80 may be connected in series with thefirst compressor 12 on thelow pressure line 64. - It is not essential that the
buffer volume 70 is removed. Also in another embodiment, similar to one embodiment, as illustrated inFIG. 1 , a steady operation of thecryocooler 10 may be performed in a state where thebuffer volume 70 is connected to thecryocooler 10. Alternatively, also in one embodiment, similar to another embodiment, thebuffer volume 70 may be removed from thecryocooler 10 after the initial cooling. -
FIG. 15 is a view schematically illustrating thecryocooler 10 according to still another embodiment.FIGS. 16 and 17 are flowcharts for describing a method for operating thecryocooler 10 according to still another embodiment. - The
cryocooler 10 and the method for operating the same according to still another embodiment can be the same as thecryocooler 10 and the method for operating method the same according to one embodiment, except for thesecond compressor 80. Therefore, inFIG. 15 , the same reference numerals will be assigned to the configurations common to one embodiment, and detailed description thereof will be appropriately omitted in order to avoid redundancy. - Also in still another embodiment, similar to another embodiment, the
cryocooler 10 takes a basic setting including thefirst compressor 12 and theexpander 14 as illustrated inFIG. 13 before the initial cooling is performed. Thefirst compressor 12 and theexpander 14 are connected by thehigh pressure line 63 and thelow pressure line 64. Thesecond compressor 80 is not connected to thecryocooler 10. - In the method for operating the
cryocooler 10 according to still another embodiment, as illustrated inFIG. 16 , thesecond compressor 80 is connected to the cryocooler as pretreatment for initial cooling (S70). Thesecond compressor 80 is connected in series with thefirst compressor 12 on thehigh pressure line 63. As illustrated inFIG. 15 , the highpressure gas outlet 50 of thefirst compressor 12 is connected to the suction port of thesecond compressor 80, and the discharge port of thesecond compressor 80 is connected to the highpressure gas inlet 22 of theexpander 14. Therefore, thecryocooler 10 has a two-stage compressor configuration including thefirst compressor 12 and thesecond compressor 80. Thesecond compressor 80 may be brought to the site where thecryocooler 10 is operated by a serviceman, for example, and may be connected to thecryocooler 10. - The
second compressor 80 includes the compressormain body 57 similar to thefirst compressor 12. In addition, thesecond compressor 80 includes acompressor motor 82 in which an operating frequency (that is, a rotation speed) is variable, and the compressormain body 57 is driven by thecompressor motor 82. Thecompressor motor 82 may be, for example, an electric motor, or may be any other suitable type of motor. By increasing the operating frequency of thecompressor motor 82, the discharge flow rate of the compressormain body 57 is increased, and as a result, the pressure of thehigh pressure line 63 can be increased. On the contrary, by reducing the operating frequency of thecompressor motor 82, the discharge flow rate of the compressormain body 57 is reduced, and as a result, the pressure of thehigh pressure line 63 can be reduced. - The
control device 100 includes aninverter 90 that controls the operating frequency of thecompressor motor 82. Thecompressor motor 82 and theinverter 90 are supplied with power from anexternal power source 92 such as a commercial power source (three-phase AC power source). As will be described later, theinverter 90 is configured to adjust the frequency of the power input from theexternal power source 92 under the control of thecontroller 110 and output the frequency to thecompressor motor 82 at any frequency. The operating frequency of thecompressor motor 82 corresponds to the output frequency of theinverter 90, and can be adjusted in the range of 30 Hz to 100 Hz or 40 Hz to 70 Hz, for example. - In a state where the
second compressor 80 is connected to thecryocooler 10, thecryocooler 10 is started and initial cooling is performed (S72). The working gas is supplied to theexpander 14 by using thefirst compressor 12 and thesecond compressor 80. Thefirst compressor 12 pressurizes the working gas of thecryocooler 10 collected from theexpander 14 through thelow pressure line 64, and supplies the pressurized working gas to thesecond compressor 80. Thesecond compressor 80 further pressurizes the working gas from thefirst compressor 12, and supplies this to theexpander 14 again. As will be described later, the operating frequency of thecompressor motor 82 of thesecond compressor 80 is controlled to keep the pressure of thehigh pressure line 63 within an appropriate pressure range based on the measured pressure of thehigh pressure line 63. - When the initial cooling is completed, the
second compressor 80 is removed from the cryocooler 10 (S73). Thecryocooler 10 is returned to the basic setting illustrated inFIG. 13 . Then, a steady operation of thecryocooler 10 is performed (S75). - An example of the control processing of the operating frequency of the
compressor motor 82 based on the measured pressure of thehigh pressure line 63 will be described with reference toFIG. 17 . This processing is repeatedly executed by thecontroller 110 in a predetermined cycle in the initial cooling of thecryocooler 10. - First, the pressure of the
high pressure line 63 is measured (S80). Next, the measured pressure of thehigh pressure line 63 is compared with a high pressure target value Pg (S82). For example, the high pressure target value Pg may be the lower limit value Pc of an appropriate pressure range. The high pressure target value Pg can be appropriately set based on the empirical knowledge of the designer, an experiment or simulation by the designer, or the like. The high pressure target value Pg may be stored in advance in thecontroller 110 as an initial setting of thecryocooler 10, or may be set in thecontroller 110 by the user before thecryocooler 10 is operated. - The
controller 110 compares the measured pressure PH of thehigh pressure line 63 with the high pressure target value Pg, and outputs a magnitude relationship between the two as a comparison result. That is, the comparison results obtained by thecontroller 110 are any of the following three states: (i) the measured pressure PH is smaller than the high pressure target value Pg, (ii) the measured pressure PH is larger than the high pressure target value Pg, and (iii) the measured pressure PH is equal to the high pressure target value Pg. - The
inverter 90 is controlled based on the comparison result of thecontroller 110, and the operating frequency of thecompressor motor 82 is controlled according to the output frequency of theinverter 90. Specifically, (i) when the measured pressure PH is smaller than the high pressure target value Pg, thecontroller 110 controls theinverter 90 to increase the operating frequency of the compressor motor 82 (S84). Accordingly, the pressure of thehigh pressure line 63 can be increased. - (ii) When the measured pressure PH is larger than the high pressure target value Pg, the
controller 110 controls theinverter 90 to reduce the operating frequency of the compressor motor 82 (S18). Accordingly, the pressure of thehigh pressure line 63 can be reduced. - (iii) When the measured pressure PH is equal to the high pressure target value Pg, it is not necessary to increase or decrease the operating frequency of the
compressor motor 82. Therefore, thecontroller 110 controls theinverter 90 to maintain the current operating frequency. The case of (iii) may be included in either (i) or (ii). - When the operating frequency of the
compressor motor 82 is increased or decreased, thecontroller 110 may increase or decrease the operating frequency by a predetermined amount from the value of the current operating frequency of thecompressor motor 82. When the current operating frequency value has already reached the upper limit value when the operating frequency is to be increased, thecontroller 110 may maintain the upper limit value without increasing the operating frequency. For example, in a case where the operating frequency of thecompressor motor 82 is within a range of 30 Hz to 100 Hz and the current value is already the upper limit value of 100 Hz, thecontroller 110 does not further increase the operating frequency from 100 Hz, and 100 Hz is maintained. Similarly, when the current operating frequency value has already reached the lower limit value when the operating frequency is to be reduced, thecontroller 110 may maintain the lower limit value without reducing the operating frequency. - Alternatively, the
controller 110 may control theinverter 90 to adjust the operating frequency of thecompressor motor 82 to minimize the deviation of the measured pressure PH from the high pressure target value Pg (for example, by feedback control such as PID control). In this manner, thecontroller 110 may compare the pressure of thehigh pressure line 63 with the target pressure, and control theinverter 90 to reduce the operating frequency of thecompressor motor 82 when the pressure of thehigh pressure line 63 exceeds the target pressure and increase the operating frequency of thecompressor motor 82 when the pressure of thehigh pressure line 63 falls below the target pressure. - According to still another embodiment, the operating differential pressure of the
cryocooler 10 can be increased by adding thesecond compressor 80. In particular, the operating differential pressure of thecryocooler 10 can be increased exceeding the limitation caused by the set pressure of therelief valve 60 of thefirst compressor 12 described above. An increase in the operating differential pressure causes an increase in the cooling capacity of thecryocooler 10, and can shorten the time required for initial cooling. In addition, since thesecond compressor 80 is used in combination with thefirst compressor 12, thesecond compressor 80 may be relatively small in size and is easy to carry. - Similar to another embodiment, also in still another embodiment, as illustrated in
FIG. 18 , thebuffer volume 70 may be connected to thecryocooler 10 for initial cooling together with thesupply valve 72 and thecollection valve 74. As pretreatment of the initial cooling, thebuffer volume 70 is connected to thelow pressure line 64 via thesupply valve 72 and is connected to thehigh pressure line 63 via thecollection valve 74. During the execution of the initial cooling, thebuffer volume 70 is used to keep the pressure of thehigh pressure line 63 within an appropriate pressure range, as in one embodiment. That is, thesupply valve 72 performs control to keep the pressure of thehigh pressure line 63 within an appropriate pressure range based on the pressure of thehigh pressure line 63 measured by thefirst pressure sensor 54 during the initial cooling. After the initial cooling, thebuffer volume 70 may be removed from thecryocooler 10 together with thesupply valve 72 and thecollection valve 74. In this manner, by using thebuffer volume 70 for the initial cooling, the time required for the initial cooling can be shortened similar to the above-described embodiment. - Further, as illustrated in
FIG. 19 , in order to form the two-stage compressor configuration, thesecond compressor 80 may be connected to the suction side (inlet side) of thefirst compressor 12. That is, thesecond compressor 80 may be connected in series with thefirst compressor 12 on thelow pressure line 64. In this case, the operating frequency of thecompressor motor 82 that drives the compressormain body 57 of thefirst compressor 12 may be variable. The operating frequency of thecompressor motor 82 may be controlled by thecontroller 110 and theinverter 90 to keep the pressure of thehigh pressure line 63 within an appropriate pressure range based on the measured pressure of thehigh pressure line 63. Along with or instead of this, the operating frequency of thecompressor motor 82 of thesecond compressor 80 may be controlled by thecontroller 110 and theinverter 90, similar to the embodiment illustrated inFIG. 15 . - Above, the present invention was described based on examples. It will be understood by those skilled in the art that the present invention is not limited to the above-described embodiment, various design changes are possible, various modification examples are possible, and such modification examples are also within the scope of the present invention. Various characteristics described in relation to one embodiment are also applicable to other embodiments. A new embodiment generated through combination also has the effects of each of the combined embodiments.
- For example, the control processing described with respect to one embodiment (for example, the completion processing of the initial cooling based on the buffer pressure, the switching processing from the high pressure priority control to the low pressure priority control, and the switching processing from the low pressure priority control to the high pressure priority control) may be applied to other embodiment and still another embodiment.
- In the above-described embodiment, as an example, a case where the
expander motor 42 works at a constant operating frequency (motor rotation speed) (that is, a case where theexpander motor 42 works at the same operating frequency in initial cooling and steady operation) is described, but the present invention is not limited thereto. - The
cryocooler 10 may include theexpander motor 42 having a variable operating frequency, and during initial cooling, so-called accelerated cooling in which theexpander motor 42 works at a higher operating frequency than in steady operation may be executed. In this case, the switching from the initial cooling (accelerated cooling) to the steady operation and the change of the operating frequency may be performed based on the pressure of thebuffer volume 70 or based on the differential pressure of thehigh pressure line 63 and thelow pressure line 64 as described above with reference toFIGS. 7 and 8 . By executing the accelerated cooling, the initial cooling time can be further shortened. - The pressure sensors such as the
first pressure sensor 54 and thesecond pressure sensor 55 are not essential to be provided in thecompressor 12, and may be provided at any place where the pressure of thegas line 62 and theexpander 14 can be measured. For example, thefirst pressure sensor 54 may be provided at any place on thehigh pressure line 63, and thesecond pressure sensor 55 may be provided at any place on thelow pressure line 64. - In the above-described embodiment, the
supply valve 72 and thecollection valve 74 are prepared as separate valves, and each of thesupply valve 72 and thecollection valve 74 are connected to thebuffer volume 70. However, the present invention is not limited thereto. For example, thesupply valve 72 and thecollection valve 74 may be integrated, or may be, for example, a three-way valve connected to thebuffer volume 70. By switching the three-way valve, a supply state where thebuffer volume 70 is connected to thelow pressure line 64 and a collection state where thebuffer volume 70 is connected to thehigh pressure line 63 may be switched. - In the embodiment described above, the
buffer volume 70 is a single buffer tank. However, in a certain embodiment, thebuffer volume 70 may be a plurality of buffer tanks. One buffer tank may be connected to thelow pressure line 64 by thesupply valve 72, and another buffer tank may be connected to thehigh pressure line 63 by thecollection valve 74. Further, in the above-described embodiment, thebuffer volume 70 is disposed outside thecompressor 12 and theexpander 14, but the present invention is not limited thereto. For example, thebuffer volume 70 may be disposed inside thecompressor 12. - In the above-described embodiment, a case where the
cryocooler 10 is a two-stage GM cryocooler was described as an example, but the present invention is not limited thereto. Thecryocooler 10 may be a single-stage or multi-stage GM cryocooler, and may be another type of cryocooler such as a pulse tube cryocooler. - Embodiments of the present invention can also be expressed as follows.
- 1. A cryocooler including: an expander capable of executing initial cooling for cooling from an initial temperature to a cryogenic temperature and a steady operation of maintaining the cryogenic temperature after the initial cooling; a high pressure line which is connected to the expander and through which a working gas taken into the expander flows; a low pressure line which is connected to the expander and through which a working gas exhausted from the expander flows; a first pressure sensor that measures a pressure of the high pressure line; a buffer volume for storing a working gas; a supply valve that connects the buffer volume to the low pressure line; and a controller that controls the supply valve to keep the pressure of the high pressure line within a preset appropriate pressure range based on the pressure of the high pressure line measured by the first pressure sensor during the initial cooling.
2. The cryocooler according to item 1, in which the controller compares the measured pressure of the high pressure line with the lower limit value of the appropriate pressure range during the initial cooling, and operate the supply valve to repeatedly open and close the supply valve such that the pressure of the high pressure line does not fall below the lower limit value.
3. The cryocooler according to item 1 or 2, in which, when the buffer volume is VB, the volume of the high pressure line is VH, the volume of the low pressure line is VL, the working gas filling pressure at a certain temperature is PI, and the pressure of the high pressure line in the steady operation at the temperature is PH, and the pressure of the low pressure line in the steady operation at a temperature is PL, the buffer volume satisfies VB VH(PH−PI)/(PI−PL)−VL for any temperature in a temperature range from the initial temperature to the cryogenic temperature.
4. The cryocooler according to any one of items 1 to 3, further including the collection valve for connecting the buffer volume to the high pressure line, in which the controller controls the collection valve to keep the pressure of the high pressure line in an appropriate pressure range.
5. The cryocooler according to item 4, in which, when the buffer volume is VB, the volume of the high pressure line is VH, the volume of the low pressure line is VL, the working gas filling pressure at a certain temperature is PI, and the pressure of the high pressure line in the steady operation at the temperature is PH, and the pressure of the low pressure line in the steady operation at a temperature is PL, the buffer volume satisfies VB≥−VH+VL(PI−PL)/(PH−PI) for any temperature in a temperature range from the initial temperature to the cryogenic temperature.
6. The cryocooler according to any one of items 1 to 5, further including: a buffer pressure sensor that measures a pressure of the buffer volume, in which the controller completes the initial cooling based on a pressure of the buffer volume measured by the buffer pressure sensor.
7. The cryocooler according to any one of items 1 to 6, further including: a second pressure sensor that measures a pressure of the low pressure line, in which the controller discontinues control of the supply valve based on the pressure of the high pressure line when the pressure of the low pressure line measured by the second pressure sensor falls below a preset low pressure threshold, and controls the supply valve to restore the pressure of the low pressure line to the low pressure threshold based on the pressure of the low pressure line measured by the second pressure sensor.
8. The cryocooler according toitem 7, in which the controller discontinues control of an operating frequency of the compressor motor based on the pressure of the low pressure line when the pressure of the high pressure line measured by the first pressure sensor falls below the first appropriate pressure range, and controls the operating frequency of the compressor motor to return the pressure of the high pressure line to the first appropriate pressure range based on the pressure of the high pressure line measured by the first pressure sensor.
9. The cryocooler according to any one of items 1 to 8, further including: a first compressor connected to the expander through the high pressure line and the low pressure line; and a second compressor connected in series with the first compressor on the high pressure line or the low pressure line.
10. The cryocooler according to item 9, in which the first compressor or the second compressor includes a compressor motor having a variable operating frequency, and is driven by the compressor motor, and the controller controls the operating frequency of the compressor motor to keep the pressure of the high pressure line within an appropriate pressure range based on the pressure of the high pressure line measured by the first pressure sensor during the initial cooling.
11. A method for operating a cryocooler in which the cryocooler includes a first compressor, an expander, and a high pressure line and a low pressure line connecting the first compressor to the expander, the method including: connecting a second compressor in series with the first compressor on the high pressure line or the low pressure line; connecting a buffer volume to the low pressure line via a supply valve; executing initial cooling for cooling the expander from an initial temperature to a cryogenic temperature in a state where the second compressor and the buffer volume are connected to the cryocooler; and executing a steady operation of maintaining the expander at the cryogenic temperature after the initial cooling, in which the execution of the initial cooling includes supplying a working gas to the expander by using the first compressor and the second compressor, and controlling the supply valve to keep a pressure of the high pressure line within a preset appropriate pressure range based on the measured pressure of the high pressure line.
12. The method according to item 11, further including: removing the second compressor after the initial cooling.
13. The method according toitem 11 or 12, further including: removing the buffer volume after the initial cooling.
14. The method according to any one of items 11 to 13, in which the execution of the initial cooling includes discontinuing control of the supply valve based on the pressure of the high pressure line when the measured pressure of the low pressure line falls below a preset low pressure threshold, and controlling the supply valve to restore the pressure of the low pressure line to the low pressure threshold based on the measured pressure of the low pressure line.
15. The method according toitem 14, in which the execution of the initial cooling includes discontinuing control of the supply valve based on the pressure of the low pressure line when the measured pressure of the high pressure line falls below a high pressure threshold, and controlling the supply valve to restore the pressure of the high pressure line to the high pressure threshold based on the measured pressure of the high pressure line.
16. The method according to any one of items 11 to 15, in which the first compressor or the second compressor includes a compressor motor having a variable operating frequency, and is driven by the compressor motor, and the execution of the initial cooling includes controlling the operating frequency of the compressor motor to keep the pressure of the high pressure line within the preset appropriate pressure range based on the measured pressure of the high pressure line.
17. The method according to any one of items 11 to 16, in which the execution of the initial cooling includes measuring the pressure of the buffer volume during the initial cooling, and completing the initial cooling based on the measured pressure of the buffer volume.
18. A method for operating a cryocooler in which the cryocooler includes a first compressor, an expander, and a high pressure line and a low pressure line connecting the first compressor to the expander, the method including: connecting a second compressor in series with the first compressor on the high pressure line or the low pressure line; executing initial cooling for cooling the expander from an initial temperature to a cryogenic temperature in a state where the second compressor is connected to the cryocooler; and executing a steady operation of maintaining the expander at the cryogenic temperature after the initial cooling, in which the first compressor or the second compressor has a compressor motor with a variable operating frequency, and is driven by the compressor motor, and the execution of the initial cooling includes supplying a working gas to the expander by using the first compressor and the second compressor, and controlling the operating frequency of the compressor motor to keep a pressure of the high pressure line within a preset appropriate pressure range based on the measured pressure of the high pressure line.
19. The method according toitem 18, further including: removing the second compressor after the initial cooling.
20. The method according toitem 18 or 19, further including: connecting a buffer volume to the low pressure line via a supply valve, in which the execution of the initial cooling includes controlling the supply valve to keep the pressure of the high pressure line within the preset appropriate pressure range based on the measured pressure of the high pressure line.
21. The method according toitem 20, further including: removing the buffer volume after the initial cooling.
22. The method according toitem 20 or 21, in which the execution of the initial cooling includes measuring the pressure of the buffer volume during the initial cooling, and completing the initial cooling based on the measured pressure of the buffer volume. - Above, the present invention was described based on examples. It will be understood by those skilled in the art that the present invention is not limited to the above-described embodiment, various design changes are possible, various modification examples are possible, and such modification examples are also within the scope of the present invention.
- It should be understood that the invention is not limited to the above-described embodiment, but may be modified into various forms on the basis of the spirit of the invention. Additionally, the modifications are included in the scope of the invention.
Claims (12)
1. A method for operating a cryocooler in which the cryocooler includes a first compressor, an expander, and a high pressure line and a low pressure line connecting the first compressor to the expander, the method comprising:
connecting a second compressor in series with the first compressor on the high pressure line or the low pressure line;
connecting a buffer volume to the low pressure line via a supply valve;
executing initial cooling for cooling the expander from an initial temperature to a cryogenic temperature in a state where the second compressor and the buffer volume are connected to the cryocooler; and
executing a steady operation of maintaining the expander at the cryogenic temperature after the initial cooling, wherein
the execution of the initial cooling includes:
supplying a working gas to the expander by using the first compressor and the second compressor, and
controlling the supply valve to keep a pressure of the high pressure line within a preset appropriate pressure range based on a measured pressure of the high pressure line.
2. The method according to claim 1 , further comprising:
removing the second compressor after the initial cooling.
3. The method according to claim 1 , further comprising:
removing the buffer volume after the initial cooling.
4. The method according to claim 1 , wherein
the execution of the initial cooling includes
discontinuing control of the supply valve based on the measured pressure of the high pressure line when a measured pressure of the low pressure line falls below a preset low pressure threshold, and
controlling the supply valve to restore a pressure of the low pressure line to the low pressure threshold based on the measured pressure of the low pressure line.
5. The method according to claim 4 , wherein
the execution of the initial cooling includes
discontinuing control of the supply valve based on the measured pressure of the low pressure line when the measured pressure of the high pressure line falls below a high pressure threshold, and
controlling the supply valve to restore the pressure of the high pressure line to the high pressure threshold based on the measured pressure of the high pressure line.
6. A method for operating a cryocooler in which the cryocooler includes a first compressor, an expander, and a high pressure line and a low pressure line connecting the first compressor to the expander, the method comprising:
connecting a second compressor in series with the first compressor on the high pressure line or the low pressure line;
executing initial cooling for cooling the expander from an initial temperature to a cryogenic temperature in a state where the second compressor is connected to the cryocooler; and
executing a steady operation of maintaining the expander at the cryogenic temperature after the initial cooling, wherein
the first compressor or the second compressor includes a compressor motor with a variable operating frequency, and
the execution of the initial cooling includes:
supplying a working gas to the expander by using the first compressor and the second compressor, and
controlling the operating frequency of the compressor motor to keep a pressure of the high pressure line within a preset appropriate pressure range based on a measured pressure of the high pressure line.
7. The method according to claim 6 , further comprising:
removing the second compressor after the initial cooling.
8. The method according to claim 6 , further comprising:
connecting a buffer volume to the low pressure line via a supply valve, wherein
the execution of the initial cooling includes
controlling the supply valve to keep the pressure of the high pressure line within the preset appropriate pressure range based on the measured pressure of the high pressure line.
9. The method according to claim 8 , further comprising:
removing the buffer volume after the initial cooling.
10. A cryocooler comprising:
an expander capable of executing initial cooling for cooling from an initial temperature to a cryogenic temperature and a steady operation of maintaining the cryogenic temperature after the initial cooling;
a high pressure line and a low pressure line connected to the expander;
a first pressure sensor that measures a pressure of the high pressure line;
a second pressure sensor that measures a pressure of the low pressure line;
a buffer volume for storing a working gas;
a supply valve that connects the buffer volume to the low pressure line; and
a controller configured to control the supply valve to keep the pressure of the high pressure line within a preset appropriate pressure range based on the pressure of the high pressure line measured by the first pressure sensor during the initial cooling, wherein
the controller is further configured to:
discontinue control of the supply valve based on the pressure of the high pressure line when the pressure of the low pressure line measured by the second pressure sensor falls below a preset low pressure threshold, and
control the supply valve to restore the pressure of the low pressure line to the low pressure threshold based on the pressure of the low pressure line measured by the second pressure sensor.
11. The cryocooler according to claim 10 , wherein
the controller is further configured to:
discontinue control of the supply valve based on the pressure of the low pressure line when the pressure of the high pressure line measured by the first pressure sensor falls below a high pressure threshold, and
control the supply valve to restore the pressure of the high pressure line to the high pressure threshold based on the pressure of the high pressure line measured by the first pressure sensor.
12. The cryocooler according to claim 10 , further comprising:
a first compressor connected to the expander through the high pressure line and the low pressure line; and
a second compressor connected in series with the first compressor on the high pressure line or the low pressure line.
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JP2022161835A JP2024055145A (en) | 2022-10-06 | 2022-10-06 | Method for operating cryogenic refrigerator and cryogenic refrigerator |
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