EP3071903B1 - Tête froide pour refroidisseur cryogénique - Google Patents

Tête froide pour refroidisseur cryogénique Download PDF

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Publication number
EP3071903B1
EP3071903B1 EP14798872.9A EP14798872A EP3071903B1 EP 3071903 B1 EP3071903 B1 EP 3071903B1 EP 14798872 A EP14798872 A EP 14798872A EP 3071903 B1 EP3071903 B1 EP 3071903B1
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EP
European Patent Office
Prior art keywords
cold head
pressure connection
cryogenic refrigeration
refrigeration machines
low
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP14798872.9A
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German (de)
English (en)
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EP3071903A1 (fr
Inventor
Gerhard Wilhelm Walter
Holger Dietz
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Leybold GmbH
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Leybold GmbH
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Publication of EP3071903A1 publication Critical patent/EP3071903A1/fr
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Classifications

    • 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
    • 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
    • F25B2309/006—Gas cycle refrigeration machines using a distributing valve of the rotary type

Definitions

  • the invention relates to a cold head for a low-temperature refrigerator.
  • WO 94/29653 describes a cold head for a low-temperature refrigerator, which is operated with helium as the working gas and is connected to a high pressure source and a low pressure source.
  • the cold head contains a multi-channel control valve, which controls the connection of a high-pressure inlet and a low-pressure inlet, each with a piston-cylinder unit and with a warm-side working area of the cold finger.
  • the displacer which can contain a regenerator, delimits a warm-side working space at one end and a cold-side working space at the opposite end. As the displacer is periodically moved back and forth by the piston-cylinder unit, heat is constantly extracted from the housing of the cold head.
  • thermodynamic cycle (Stirling process or Gifford-McMahon process) is carried out in the cold head with the process gas, usually helium, the process gas being conducted in a closed cycle. The result is that heat is extracted from one end region of the housing enclosing the displacer.
  • the cold head is connected to a compressor. Since it is a closed circuit, both the high pressure connection and the low pressure connection of the cold head are connected to the compressor.
  • Such compressors usually have an overflow valve. This is arranged in a return flow channel arranged between the high pressure side and the low pressure side.
  • overflow valves are spring-loaded check valves, which are usually designed for a differential pressure between high and low pressure of the compressor of, for example, 18 bar. If a cold head with a very high resistance is connected to the compressor, the working pressure on the high-pressure side of the compressor is increased. To discharge this excess energy, the overflow valve opens so that the refrigerant, in particular helium, flows via the return line to the low-pressure side of the compressor.
  • a cold head for low-temperature chillers with the features of the preamble of claim 1 is from WO 03/036191 known.
  • the object of the invention is to reduce the load on the overflow valve.
  • this object is achieved by a cold head according to claim 1.
  • the cold head according to the invention for a low-temperature refrigeration machine has a working space in an optionally multi-part housing.
  • a single or multi-stage displacer is arranged in the work space.
  • the cold head has a high-pressure connection for supplying highly compressed cooling medium to the work space and a low-pressure connection for removing relaxed or low-pressure cooling medium.
  • a control valve device is also provided.
  • the control valve device is used to control the supply and discharge of refrigerant into or out of the work space.
  • the control device can have a plurality of valves, such as, for example, an inlet and an outlet valve. It is preferred that the control valve device has a multi-channel control valve through which the connection between the high-pressure connection, the low-pressure connection and the work space is controlled.
  • the cold head has a distribution body in which at least one first connecting channel is provided.
  • the first connection channel is used to connect the high pressure connection to the work area. This connection is preferably made via the control valve device, so that the first connection channel is arranged between the control valve device and the work space.
  • the distributor body preferably additionally has a second connecting channel, which is arranged between the control valve device and the low-pressure connection.
  • the distribution body is designed such that it also has a control channel.
  • the control channel serves to supply and discharge control medium to the movement device, ie in particular to the piston-cylinder unit.
  • the control medium is preferably the cooling medium.
  • a bypass channel arranged between the high-pressure connection and the low-pressure connection or connecting the two connections, which is provided in the distribution body. If necessary, excess refrigerant can flow directly from the high-pressure connection to the low-pressure connection without it flowing through the cold head. Such excess energy can thus be derived via the bypass.
  • the overflow valve integrated in the compressor is relieved. If necessary, the overflow valve in the compressor can even be completely omitted or can only be provided as a safety device. This means that at least one significantly cheaper overflow valve can be used.
  • a flow regulation device is arranged in the bypass channel.
  • This is, for example, a nozzle and / or a valve.
  • the flow regulation device can be adjustable. It is possible that a fixed setting is carried out before operation, so that the valve opens, for example, when a pressure difference is exceeded. Furthermore, it is possible to adjust the flow regulating device from the outside, i. H. from outside the cold head. In this respect, it may be possible to make appropriate settings even during operation.
  • the cold head has a movement device for moving the displacer.
  • the movement device can be a motor.
  • the motor which can be an electric motor, for example, the displacer can be moved with the aid of a link guide. This can take place, for example, via an eccentric, so that the rotary movement of the motor is converted into a linear movement of the displacer in a simple manner.
  • a piston-cylinder unit can be provided for moving the displacer.
  • the piston-cylinder unit can be operated, for example, via a separate hydraulic system.
  • a low-temperature chiller according to the state of the art ( Figure 1 ) has a compressor 10, by which refrigerant, such as helium, is compressed.
  • the compressor 10 On the high pressure side, the compressor 10 is connected via a line 12 to a high pressure connection 14 of a cold head 16. A low pressure connection 18 of the cold head 16 is connected to the low pressure side of the compressor 10 via a line 20. In order to avoid overloading the compressor 10, a check valve 24 is arranged in a return flow line 22, which connects the high pressure side of the compressor 10 to the low pressure side of the compressor 10.
  • a work space 26 is provided, in which an in Figure 1 Displacement piston, not shown, is arranged.
  • An inlet valve 28 is connected to the high-pressure connection 14, so that compressed refrigerant flows into the working space 26 when the inlet valve 28 is open. Expanded refrigerant can be led to the low pressure connection 18 via an outlet valve 30.
  • a bypass channel 32 is provided in a schematic representation between the inlet valve 28 of the cold head 16 and the outlet valve 30 of the cold head 16, in which a flow regulating device is optionally arranged.
  • a flow regulating device is optionally arranged.
  • the bypass channel 32 by providing the bypass channel 32 according to the invention, the backflow line 22 and the overflow valve 24 can be omitted.
  • a preferred embodiment of the cold head 16 is shown in a schematic sectional view in FIG Figure 3 shown.
  • the cold head 16 has a housing which consists of the two housing parts 34 and 36.
  • the housing part 34 two cylindrical cold-side working spaces 38 and 40 for the two displacement stages 42 and 44 are accommodated.
  • the upper displacement stage 42 delimits a warm-side work space 46 and it is equipped with a drive piston 48, which is accommodated in a cylinder 50 of a distribution body 52.
  • the displacer 42, 44 is thus arranged in a work space 38, 40, 46 consisting of several subspaces.
  • the distribution body 52 delimits the working chamber 46 on the warm side. It is equipped with bores which form a control channel 54, a first connecting channel 56 and a second connecting channel 57.
  • the first connecting channel 56 opens into the working space 46 and serves to supply this space with the working gas. All three channels are controlled by the control valve 58.
  • the first connecting channel 56 connects the control valve 58 to the warm-side working space 46
  • the control channel 54 connects the valve 58 to the cylinder 50
  • the second 57 connects the valve 58 to a low-pressure connection 60.
  • the control valve 58 is also connected to a space 62 which communicates with a high pressure connection 64.
  • the high-pressure connection 64 supplies helium gas at a pressure of approximately 20 bar, while helium is present at the low-pressure connection 18 at a pressure of approximately 5 bar.
  • both pressures are supplied to corresponding connections (not shown) of the control valve 58. All lines lead into the top of the distribution body 52 and from there to the valve 58.
  • a motor 66 is housed in the housing part 36 and drives the control valve 58 via a shaft 68. This is under the action of a compression spring 70.
  • the process gas which is subjected to the thermodynamic cycle and the drive gas for the piston-cylinder unit 48, 50 are identical. Helium is expediently used. A gas other than the process gas can also be used as the drive gas.
  • a motor movement of the displacers 72, 76 can also take place, for example with the aid of an electric motor.
  • the electric motor can be provided with an eccentric and a link guide, so that the rotation of the eccentric is converted into a linear movement.
  • the displacer stage 42 has a tubular displacer 72 in the cylindrical working space 46, which is filled with a thermal regenerator 74 which is gas-permeable.
  • the regenerator 74 is used to store cold and to release stored cold to the inflowing warm gas.
  • the displacer stage 44 which has a smaller diameter than the displacer stage 42, contains a tubular displacer 76 which is axially displaceable in the cylindrical working space 40, which is connected to the displacer 72 and is also filled with a gas-permeable regenerator 78.
  • the warm-side working space 46 is first connected to the high-pressure connection 64 via the first connecting duct 56 and the control valve 58.
  • the high pressure is let into the cylinder 50 via the control channel 54.
  • the displacers 72 and 76 are shifted to the cold side (downwards).
  • the high pressure gas also flows through the regenerators 74 and 78 to the cold side. It relaxes with cooling, with further relaxation through heat exchange with the regenerators.
  • control channel 54 is connected to the low pressure connection.
  • the displacers 72 and 76 are shifted towards the warm side, so that the warm-side working space 46 is located reduced and gas flows through the regenerators 74 and 78 into the cold-side working space 40.
  • control valve 58 causes the working space 46 to be connected to the low-pressure connection 60 via the line 56.
  • the gas relaxes in all work rooms of the cold head while cooling.
  • the displacers 72 and 76 are then moved to the cold side, as a result of which the volume of the cold-side working space 40 is reduced in order to be prepared for the next cycle.
  • the cold gas flows from the working space 40 into the regenerators 74 and 78, which are thereby further cooled.
  • the frequency of the described working cycle is approximately 2 Hz.
  • a bypass duct 80 according to the invention is provided in the distribution body 52.
  • the bypass duct 80 connects the second connecting duct 57 to the space 62.
  • the bypass duct 80 thus connects the high-pressure connection 64 to the low-pressure connection 60.
  • a flow regulating device, such as a valve 82, is shown schematically within the bypass duct 80. In the event of an undesirably high pressure rise in the space 62, part of the refrigerant thus flows directly through the bypass duct 80 back into the duct 57 connected to the low-pressure connection 60.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Claims (12)

  1. Tête froide pour machine frigorifique basse température, dotée
    d'un boîtier (34, 36),
    d'un élément de déplacement (72, 76) agencé dans un espace de travail (38, 40, 46) du boîtier (34, 36),
    d'un raccord à haute pression (64) destiné à acheminer du fluide frigorigène hautement comprimé dans l'espace de travail (38, 40, 46),
    d'un raccord à basse pression (60) destiné à évacuer le fluide frigorigène détendu hors de l'espace de travail (38, 40, 46),
    d'un dispositif de vanne de commande (28, 30 ; 58) destiné à commander l'acheminement et l'évacuation de fluide frigorigène respectivement dans et hors de l'espace de travail (38, 40, 46), et
    d'un corps de distribution (52), au moins un premier canal de liaison (56) étant prévu dans celui-ci afin de relier le raccord à haute pression (64) à l'espace de travail (38, 40, 46),
    caractérisée par
    un canal de pontage (80) prévu dans le corps de distribution (52), reliant le raccord à haute pression (64) au raccord à basse pression (60).
  2. Tête froide pour machine frigorifique basse température selon la revendication 1, caractérisée en ce que le premier canal de liaison (56) est agencé entre la vanne de commande (58) et l'espace de travail (38, 40, 46) .
  3. Tête froide pour machine frigorifique basse température selon la revendication 1 ou 2, caractérisée en ce que le corps de distribution (52) comporte un deuxième canal de liaison (57) entre la vanne de commande (58) et le raccord à basse pression (60).
  4. Tête froide pour machine frigorifique basse température selon l'une des revendications 1-3, caractérisée en ce que le corps de distribution (52) comporte un canal de commande (54) pour l'acheminement et/ou l'évacuation de fluide de commande, en particulier de fluide frigorigène, à l'unité piston-cylindre (48, 50) .
  5. Tête froide pour machine frigorifique basse température selon l'une des revendications 1 à 4, caractérisée en ce qu'un dispositif de régulation de débit (82) est agencé dans le canal de pontage (80).
  6. Tête froide pour machine frigorifique basse température selon la revendication 5, caractérisée en ce que le dispositif de régulation de débit (82) est en particulier réglable pendant le fonctionnement.
  7. Tête froide pour machine frigorifique basse température selon l'une des revendications 1-6, caractérisée par un dispositif de mouvement (48, 50) destiné à mouvoir l'élément de déplacement (72, 76).
  8. Tête froide pour machine frigorifique basse température selon la revendication 7, caractérisée en ce que le dispositif de mouvement est réalisé comme unité piston-cylindre (48, 50), laquelle est reliée de préférence au raccord à haute pression (64) et au raccord à basse pression (60) pour l'actionnement.
  9. Tête froide pour machine frigorifique basse température selon la revendication 7, caractérisée en ce que le dispositif de mouvement comporte un moteur, en particulier un moteur électrique.
  10. Tête froide pour machine frigorifique basse température selon la revendication 9, caractérisée en ce que le moteur électrique entraîne un excentrique, lequel opère sur un guidage à coulisse afin de fournir un mouvement linéaire de l'élément de déplacement (72, 76).
  11. Tête froide pour machine frigorifique basse température selon l'une des revendications 1-9, caractérisée en ce que le dispositif de vanne de commande (28, 30 ; 58) comporte une vanne de commande (58) multicanaux fonctionnant de façon cyclique, laquelle commande le raccordement d'un espace de travail (38, 40, 46) à un raccord à haute pression (64) et à un raccord à basse pression (60).
  12. Tête froide pour machine frigorifique basse température selon la revendication 11, caractérisée en ce que la vanne de commande (58) commande le raccordement de l'unité piston-cylindre (48, 50).
EP14798872.9A 2013-11-18 2014-11-14 Tête froide pour refroidisseur cryogénique Active EP3071903B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202013010352.3U DE202013010352U1 (de) 2013-11-18 2013-11-18 Kaltkopf für Tieftemperatur-Kältemaschine
PCT/EP2014/074623 WO2015071418A1 (fr) 2013-11-18 2014-11-14 Tête froide pour refroidisseur cryogénique

Publications (2)

Publication Number Publication Date
EP3071903A1 EP3071903A1 (fr) 2016-09-28
EP3071903B1 true EP3071903B1 (fr) 2020-07-22

Family

ID=51900440

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Application Number Title Priority Date Filing Date
EP14798872.9A Active EP3071903B1 (fr) 2013-11-18 2014-11-14 Tête froide pour refroidisseur cryogénique

Country Status (7)

Country Link
US (1) US20160273809A1 (fr)
EP (1) EP3071903B1 (fr)
JP (1) JP6525998B2 (fr)
KR (1) KR102248108B1 (fr)
CN (1) CN105814375B (fr)
DE (1) DE202013010352U1 (fr)
WO (1) WO2015071418A1 (fr)

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FR2127166A5 (fr) * 1971-02-26 1972-10-13 Air Liquide
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DE3836884C2 (de) * 1988-10-29 1997-10-02 Leybold Ag Verfahren zur Untersuchung einer auf dem Kaltkopf eines Kryostaten befindlichen Probe und Refrigerator-Kryostat
JPH0384368A (ja) * 1989-08-25 1991-04-09 Toshiba Corp 冷凍機
DE4318406A1 (de) * 1993-06-03 1994-12-08 Leybold Ag Verfahren zum Betrieb eines Refrigerators und für die Durchführung dieses Verfahrens geeigneter Refrigerator
US5878580A (en) * 1993-06-03 1999-03-09 Leybold Aktiengesellschaft Method of operating a cryogenic cooling device, and a cryogenic cooling device suitable for operation by this method
JP2663247B2 (ja) * 1994-10-21 1997-10-15 岩谷産業株式会社 パルス管冷凍機
GB2301426B (en) * 1995-05-16 1999-05-19 Toshiba Kk A refrigerator having a plurality of cooling stages
JP3806185B2 (ja) * 1995-10-31 2006-08-09 アイシン精機株式会社 流体制御機構付蓄熱型冷凍機及び流体制御機構付パルス管型冷凍機
JP3729684B2 (ja) 1999-06-28 2005-12-21 東海旅客鉄道株式会社 極低温冷凍機
DE10152262A1 (de) * 2001-10-20 2003-04-30 Leybold Vakuum Gmbh Kaltkopf für eine Tieftempratur-Kältemaschine
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US20070261416A1 (en) * 2006-05-11 2007-11-15 Raytheon Company Hybrid cryocooler with multiple passive stages
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JP2009121786A (ja) * 2007-11-19 2009-06-04 Ihi Corp 極低温冷凍装置とその制御方法
JP5378050B2 (ja) * 2009-04-23 2013-12-25 住友重機械工業株式会社 蓄冷器式冷凍機用圧縮機
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JP5738174B2 (ja) * 2011-12-27 2015-06-17 住友重機械工業株式会社 クライオポンプシステム、極低温システム、圧縮機ユニットの制御装置及びその制御方法

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Also Published As

Publication number Publication date
CN105814375B (zh) 2017-11-24
JP2016537604A (ja) 2016-12-01
WO2015071418A1 (fr) 2015-05-21
EP3071903A1 (fr) 2016-09-28
KR20160086841A (ko) 2016-07-20
US20160273809A1 (en) 2016-09-22
KR102248108B1 (ko) 2021-05-03
DE202013010352U1 (de) 2015-02-19
CN105814375A (zh) 2016-07-27
JP6525998B2 (ja) 2019-06-05

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