• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    A cryogenic refrigeration device comprising a working circuit for cooling a working fluid circulating in said circuit, the working circuit comprising, arranged in series within a loop: a compression portion (3), a portion (5, 6, 22, 23, 24, 26, 27), a valve portion (s) (9), an expansion portion (10, 25, 28) and a heating portion, for subjecting the working fluid to a recuperative-type work cycle comprising compression and then cooling and then expansion and reheating for a new cycle, wherein the compression portion comprises at least one driven linear piston compressor (3, 20, 21) by a linear motor (1), the detent portion comprises at least one linear piston holder (10, 25, 28), the valve portion (s) comprises at least one linear actuating valve (9) actuated by a linear and piloted motor to power or extracting the working fluid from the at least one piston expander.
    公开号:FR3047551A1
    申请号:FR1650962
    申请日:2016-02-08
    公开日:2017-08-11
    发明作者:Fabien Durand
    申请人:Air Liquide SA；LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude；
    IPC主号:
    专利说明:

    The invention relates to a cryogenic refrigeration device. The invention more particularly relates to a cryogenic refrigeration device comprising a working circuit for cooling a working fluid circulating in said circuit, the working circuit comprising, arranged in series within a loop: a compression portion, a cooling portion, a valve portion (s), a detent portion, and a warming portion, for subjecting the working fluid to a recuperative-type work cycle comprising compressing and then cooling and then relaxing and warming in order to of a new cycle. The invention also relates to a cryogenic gas liquefier comprising such a refrigeration device.
    A concern for the constant improvement of existing cryogenic refrigerators or liquefiers is to increase their service life, reduce the minimum operating temperature, increase their reliability. In particular, it is particularly advantageous to eliminate maintenance operations and to eliminate the use of oils.
    A first known solution consists in using a regenerative thermodynamic cycle of the Stirling or Pulse-Tube type. The disadvantages of these regenerative solutions are as follows: These devices have poor performance at temperatures below 30K. This is related to the low heat capacity of the materials constituting the regenerator at this temperature level. In addition, in these solutions, it is relatively difficult to thermally bond the refrigerator to the system to be cooled and the heat removal system.
    Another solution is to use an inverted Brayton type thermodynamic recuperative cycle based on a screw-lubricated compressor, a plate counter-current exchanger and a centripetal expansion turbine. This solution however has the disadvantage of using oil to cool and lubricate the compressor. This imposes a de-oiling operation of the cycle gas after compression. In addition, the life of this type of system is relatively short because of the compressor technology used as well as because of the compressor leaks. This technology also has difficulties to relax a two-phase fluid and the energy efficiency is not optimal.
    Yet another solution is to use a recuperative thermodynamic cycle of the inverted Turbo-Brayton type based on dry centrifugal compressors, a countercurrent plate heat exchanger and a centripetal expansion turbine (see FR2924205A1). This solution is, however, poorly suited to low thermal powers due to the difficulty of miniaturizing the turbomachines used.
    In addition, the compression ratio achievable per centrifugal compression stage is relatively low because of the low molecular weight of the gases that can be used at cryogenic temperature. The manufacturing cost of such turbomachines is also relatively high and centripetal machines used are poorly adapted to relax a two-phase fluid.
    An object of the present invention is to overcome all or part of the disadvantages of the prior art noted above. To this end, the device according to the invention, moreover in accordance with the generic definition given in the preamble above, is essentially characterized in that the compression portion comprises at least one linear piston compressor driven by an engine. linear, the trigger portion comprises at least one linear piston holder, the valve portion (s) comprises at least one linear type control valve actuated by a linear motor and driven to supply or extract the working fluid of at least a piston regulator.
    Furthermore, embodiments of the invention may include one or more of the following features: the device comprises at least one linear piston holder coupled to the linear motor which drives at least one linear piston compressor, this is that is, at least one linear motor couples both a linear piston holder and a linear piston compressor; the device comprises at least one linear type control valve coupled to the linear motor which drives at least one compressor. with linear piston, that is to say that at least one linear motor couples both a linear piston compressor and a linear type control valve, - the device comprises at least one linear piston holder coupled to a linear piston linear alternator separate from the motor of the at least one compressor, that is to say that at least one linear alternator couples a linear piston holder led alternator, - the working fluid is cooled to a temperature between 4K and 200 K, - the compression portion of the working circuit comprises a plurality of linear piston compressors, - the expansion portion of the work circuit comprises several holders with linear piston each associated with a respective linear type regulating valve (9), - the working circuit comprises a high pressure line connecting a high-pressure outlet of a compressor to the inlet of a pressure regulator, high pressure system comprising a check valve system, at least one compressed gas cooling heat exchanger, and a linear type control valve; - the working circuit comprises a low pressure line connecting an outlet of a pressure regulator to the inlet of a compressor, said low-pressure pipe comprising, a linear type control valve, at least one heat exchanger The at least one heat exchanger comprises a countercurrent heat exchanger and comprises a countercurrent heat exchanger setting the working fluid circulating in the high and low pressure lines in heat exchange. at least one heat exchanger puts the working fluid in heat exchange with at least one of: water, air, nitrogen, helium, hydrogen, methane, neon , the oxygen or argon, the at least one linear type control valve is actuated by its linear motor at the same frequency as the operating frequency of the linear piston regulator for which the valve controls the supply or removal of working fluid but out of phase with the actuation of the piston expander, - the device comprises two linear piston compressors arranged in series, the working circuit comprising a first high pipe pressure connecting a high pressure outlet of a first compressor to the inlet of a second compressor via a check valve system and a second high pressure line connecting a high pressure outlet of the second compressor to the inlet of the first compressor via at least one heat exchanger in heat exchange with the working fluid, a check valve system (s), at least one and preferably two linear type control valves and at least one and preferably two regulators with linear piston, the at least one control valve being controlled to transfer fluid from the compressors and having exchanged thermally with the at least one heat exchanger to the at least one expander and then to transfer the expanded fluid from the at least one expander in compressors with an intermediate heat exchange with at least one heat exchanger, - the working circuit comprises a ph separator disposed downstream of at least one control valve for liquefying at least a portion of the working fluid at the outlet of an expander and separating the liquid phase from the gaseous phase of the latter, - the working circuit comprises a pipe method of drawing liquefied working fluid and a working fluid supply line to the gaseous circuit, - the working circuit subjects the working fluid to a thermodynamic cycle selected from: a Brayton cycle, a Joule-Thomson cycle, a cycle Claude, - the working circuit is closed (or respectively open), that is to say that the working fluid is not (or, respectively is), withdrawn from the circuit, - the working fluid always flows in the same direction in the working circuit, that is to say that the working fluid does not go back and forth in the same circuit of the circuit between two work circuit elements, - the refrigerator transfers from the heat of the user organ (cold source) to a hot source (organ at a higher temperature than the cold source), - the at least one linear motor is of the flexible bearing type or gas bearing or magnetic bearings, - the at least one compressor with linear piston is of the "dry" type, that is to say not bringing the working fluid into contact with lubricating oil, - the at least one linear piston expansion valve is of the "dry" type; ie not bringing the working fluid into contact with lubricating oil, - the at least one valve is of the "dry" type, that is to say not bringing the working fluid into contact with of the lubricating oil, the working fluid comprises at least one of: helium, hydrogen, nitrogen, methane, neon, oxygen or argon the at least one regulating valve forms a piston expander, in particular for a gaseous working fluid, a liquid or a diph asics, - the at least one linear piston holder coupled to the linear motor of a linear piston compressor is configured to transfer mechanical work of expansion of the working fluid of the pressure reducer to the compressor via a motor shaft of said motor, - at least a bypass is provided in the working circuit to relax a part of the working fluid in one of several expansion valves, - all or part of the working fluid expanded in one of the regulators can be returned to the compressor or compressors via a pipe of return connected to a determined intermediate level of the low pressure line. The invention has many advantages over the prior art in particular: in comparison with a regenerative cycle (of the pulse-tube type in which the working fluid goes back and forth between a compressor and a regenerator), the device according to the invention which uses a recuperative cycle (the working circuit forms a loop of different structure in which the working fluid always circulates in the same direction) makes it possible to reach very low temperatures, typically 4 K, the use of a piston compressor (s) can achieve significant compression rates including up to ten per compression stage. Compared with a cycle using centrifugal compressors, this feature reduces cycle throughput and increases cycle efficiency, given the low number of moving parts and the simplicity of the system, the refrigerator has high reliability . The compressor does not require mechanical power transmission: speed multiplier, cardan joints, the device requires little or no maintenance, the life of such a device is typically several decades, the recovery cycle according to the invention makes it possible to easily connect the refrigerator to the system to be cooled, for example via a plate heat exchanger as well as to the heat evacuation system, for example via a tube / shell heat exchanger, the recuperative cycle according to the invention makes it possible to to deport the system to cool compression / expansion machines and the heat dissipation system of the compression / expansion machines via tubes, the modularity of the device makes it adaptable to a multitude of different needs. It is for example possible to extract heat at several temperature levels, the absence of oil in the device allows to connect directly with a cooling system that would not tolerate this type of pollution, advantageously the refrigerator does not does not use oil for lubrication or cooling. This eliminates the de-oiling plant downstream of the compressor, as well as the treatment and recycling operations of used oils, the expansion work of the piston expander can be upgraded and used by the compressor, the device can be devoid of rotating joints or slippery, the system is then completely airtight with respect to the outside. This prevents any loss or pollution of the cycle gas, the device makes it possible to relax a two-phase fluid and to replace for example on a Joules Thomson or Claude cycle, the regulator Joules Thomson by a regulator with recovery of work, contrary to the existing piston regulators using complex mechanical systems and requiring lubrication and maintenance to operate the valves of the expander, the device uses a simpler mechanism and whose lifetime is typically several tens of years, the invention also relates to a method refrigerating a user organ by means of such a cryogenic refrigeration device wherein the cooled working fluid is in heat exchange with said user member. The invention also relates to a liquefier or liquefaction process comprising or using such a refrigeration device. The invention may also relate to any alternative device or method comprising any combination of the above or below features. Other features and advantages will appear on reading the description below, with reference to the figures in which: - Figure 1 shows a schematic and partial view illustrating an example of structure and operation of a refrigeration device according to FIG. 2 represents a schematic and partial view illustrating another example of the structure and operation of a liquefaction device according to the invention. The nonlimiting exemplary embodiment illustrated in FIG. 1 is a cryogenic refrigerator, for example having a cold temperature of 77 k, capable of liquefying nitrogen at saturation.
    The cooling device 100 is preferably intended to transfer heat from a cold source 13 at low temperature (via a heat exchange with a member or user 7 to be cooled) to a hot source 15 at a higher temperature (for example via a heat exchange with a cooling member 5).
    As illustrated in FIG. 1, the device comprises a working circuit for a working fluid (for example helium). The working circuit forms a loop in which the working fluid circulates in one direction while being subjected to a thermodynamic cycle of the recuperative type.
    The device may comprise all or part of the components described below.
    The device comprises one or more linear motors 1 preferably using flexible bearings 2 (or gas or low friction or magnetic). The bearings shown by way of example in FIG. 1 are of the flexible bearing type.
    The circuit comprises one or more compressors 3 with pistons arranged in series preferably operating at ambient temperature and driven by the linear motor (s) 1. The piston compressor is in particular a piston compressor linear displacement driven by a motor 1. The piston is coupled to a shaft moved in translation in a reciprocating movement via a motor, for example an electromagnetic motor whose reciprocating translation movement of the shaft integral piston is driven by a system of magnetic coils (cooperating with magnets integral with the shaft or secured to a stator).
    These piston compressors 3 use, for example, non-return valves 4 and 14 to communicate with high-pressure (for discharging compressed fluid) and low-pressure (high pressure) pipes 11 (to accommodate relaxed fluid for the purpose of repressing it). . Several technologies of check valves are possible, for example leaf valves. Of course any other type of member for preventing the return of the compressed fluid in the opposite direction in the circuit may be considered.
    The working circuit comprises one or more exchangers 5 designed to evacuate heat from the compressed gas to a hot source and arranged at the outlet of the compressor or compressors 3. This cooling exchanger for example puts the working fluid in heat exchange with a coolant coolant.
    Then, (downstream in the direction of circulation of the working fluid in the circuit on the high pressure line 12) at least one countercurrent heat changer 6 is provided. This heat exchanger 6 can separate the relatively high temperature elements from the relatively low temperature elements 6 of the circuit.
    The circuit further comprises at least one valve 9 operating at low temperature (that is to say between 4 and 200K). This valve 9 is provided for supplying and extracting gas from a downstream piston expander 10.
    This valve 9 can be actuated by a linear motor 8 of technology equivalent to the technology of the motor 1 of the compressor.
    This valve 9 can be coupled indifferently to the motor 1 of the compressor 3 or to a separate motor. Similarly, the pressure reducer 10 can be coupled indifferently to the engine 1 of the compressor or to the motor 8 of the valve 9 or to a separate alternator (this linear alternator can be equivalent in technology to the engine 1 technology described above This alternator has for example a structure of the same type as the compressor or engines but used in an alternator mode: that is to say that the piston is moved by the fluid and produces energy).
    This valve 9 is actuated preferably at the same frequency as the expander 10, however, its movement is out of phase with the expander 10 so as to maximize the efficiency of the expander 10.
    The piston regulator (s) 10 operate at low temperature and may or may not be mechanically linked to the engine 1 of the compressor.
    The gas expanded by the expander 10 is returned to the compressor 3 via a low pressure line 11 (through the valve 9). One or more heat exchangers 7 are provided for heating the working fluid and thus extracting heat from the cold source 13. The expanded fluid passes in particular in the countercurrent exchanger 6 before returning to the compressor 3 (FIG. via the corresponding flap 4).
    The function of this refrigerator 100 can be the following. The working gas (helium in this example) in the gas phase (for example at 20 ° C.) is compressed through the piston compressor 3 from a low pressure (for example 10 bar) to a high pressure (for example of 18 bar).
    The non-return valves 4, 14 are used to alternately communicate the compression chamber of the compressor with the low pressure line 11 and the high pressure line 12. The helium is heated at the outlet of the compressor (for example at 110 ° C. ). The helium is then cooled through a first exchanger 5 using a flow of water (or any other suitable cooling agent). The temperature of the helium is reduced to 25 ° C. The helium then passes through the countercurrent exchanger 6, its temperature is lowered, for example to 79K. Downstream, the control valve 9 is used to alternately communicate the expansion chamber of the expander 10 with the low pressure line 11 and the high pressure line 12. The helium passes through the piston expander 10, its temperature drops ( for example at 67 K). This piston expander 10 is especially configured to operate with a two-phase fluid or liquid.
    When the expander is coupled to the compressor motor, the expansion work of the expander 10 can be transferred via the common shaft of the linear motor 1 to the compressor 3. The helium then passes through the heat exchanger 7 where it cools the user member 13 cold (nitrogen in this example). The cooled nitrogen gas 13 is, for example, liquefied to saturation by extracting heat from it.
    The temperature of the helium is, for example, brought to 76 K. The helium then passes again through the countercurrent exchanger 6 where it is reheated (for example at 20 ° C.). The helium then returns to the compressor 3 to perform a new identical cycle via the valve 4.
    Figure 2 illustrates another embodiment of the invention. This example represents a gas liquefier, in particular hydrogen. This liquefier uses the same main elements as those described above.
    The working gas (hydrogen) for example at 20 ° C (gas phase) is compressed in two piston compressors 20 and 21 arranged in series. At the outlet of each compressor 20, 21, (via a high-pressure pipe and a valve 14), the gas is cooled by a heat exchanger 22, 23. This hydrogen is then cooled through a first heat exchanger 24. against a current.
    Part of the cooled gas flow may be passed through a bypass 15 including a first linear valve 9 through a first piston expander 25 to extract heat from hydrogen.
    As before, this first piston expander 25 may be connected to the first compressor 20 via a linear motor (not shown for simplification purposes but may be of the same type as that described above). Similarly, the first regulator can be coupled to a separate engine (alternator).
    The first control valve 9 upstream of the first expander 25 is preferably operated via a linear motor (not shown for the sake of simplification but may be of the same type as that described above). The hydrogen (expanded or not) can then be cooled through a second countercurrent exchanger 26, and possibly through a third countercurrent exchanger 27. This hydrogen expanded in the first expander 25 can be returned directly to the first compressor 20 (via the countercurrent heat exchanger (s) 24, 26. That is, the hydrogen expanded in the first expander 25 can be returned to the compressors without being subjected to a second relaxation or cooling.
    Downstream of the branch 15, the remaining hydrogen is then expanded in a second linear expander 28 (via a linear control valve 9). The second expander 28 is preferably of the two-phase piston type for extracting heat from hydrogen with a view to partially liquefying it. This second piston expander 28 can be mechanically linked (coupled) to the second compressor 21 (via a linear motor not shown for simplification purposes as previously) or to a separate alternator.
    The second control valve 9 located upstream of the second expander 28 can also be actuated by a linear motor (not shown for the sake of simplification).
    The control valves 9 controlling the circulation of the fluid between the regulators 25, 28 and the compressors 20 may, if necessary, be actuated by one and the same common actuator.
    The two-phase mixture obtained after passing through the second expander 28 can then be sent to a cryogenic separator 29. The gaseous phase of the hydrogen is returned to the first compressor 20 through the exchangers 27, 26, 24 against the current.
    The liquid phase produced can be sent to an end user through a conduit 30 provided for this purpose. The circuit may comprise an inlet 31 for supplying working fluid (for example upstream of the first compressor 20) to compensate for the liquid withdrawal.
    Of course, the working fluid used may be any other fluid than helium or hydrogen, for example nitrogen, methane, neon, oxygen or argon.
    The working circuit can thus be of open or closed type.
    Of course, the invention is not limited to the examples of cycles and circuits illustrated in FIGS. 1 and 2. Thus, it is possible to envisage a multitude of different architectures based for example on the Brayton, Joules Thomson or Claude in particular.
    权利要求:
    Claims (15)
    [1" id="c-fr-0001]
    A cryogenic refrigeration device comprising a working circuit for cooling a working fluid circulating in said circuit, the working circuit comprising, arranged in series within a loop: a compression portion (3), a portion ( 5, 6, 22, 23, 24, 26, 27), a valve portion (9), an expansion portion (10, 25, 28) and a heating portion, for working at a work cycle of the recuperative type comprising compression then cooling and then expansion and heating for a new cycle, in which the compression portion comprises at least one piston compressor (3, 20, 21) linear driven by a linear motor (1), the trigger portion comprises at least one holder (10, 25, 28) linear piston, the valve portion (s) comprises at least one valve (9) linear type control driven by a linear motor and driven for conveying or extracting the working fluid from the at least one piston expander.
    [2" id="c-fr-0002]
    2. Refrigeration device according to claim 1, characterized in that it comprises at least one linear piston holder (10, 25, 28) coupled to the linear motor (1) which drives at least one compressor (3, 20, 21). ) linear piston, that is to say that at least one linear motor (1) couples both a linear piston holder (10, 25, 28) and a piston compressor (3, 20, 21). linear.
    [3" id="c-fr-0003]
    3. Refrigeration device according to claim 1 or 2, characterized in that it comprises at least one linear control valve (9) coupled to the linear motor (1) which drives at least one compressor (3, 20, 21). ) linear piston, that is to say that at least one linear motor (1) couples both a linear piston compressor (3, 20, 21) and a linear type control valve (9).
    [4" id="c-fr-0004]
    4. Refrigeration device according to any one of claims 1 to 3, characterized in that it comprises at least one linear piston holder (10, 25, 28) coupled to a linear alternator separate from the motor of the at least one compressor, that is to say that at least one linear alternator couples a linear piston holder (10, 25, 28) to said alternator.
    [5" id="c-fr-0005]
    5. Refrigeration device according to any one of claims 1 to 4, characterized in that the working fluid is cooled to a temperature between 4K and 200 K.
    [6" id="c-fr-0006]
    6. Refrigeration device according to any one of claims 1 to 5, characterized in that the compression portion (3) of the working circuit comprises a plurality of compressors (3, 20, 21) linear piston.
    [7" id="c-fr-0007]
    7. Refrigeration device according to any one of claims 1 to 6, characterized in that the expansion portion (10, 25, 28) of the working circuit comprises a plurality of linear piston holders (10, 25, 28) each associated with to a respective linear type control valve (9).
    [8" id="c-fr-0008]
    8. Refrigeration device according to any one of claims 1 to 7, characterized in that the working circuit comprises a pipe (11) high pressure connecting a high pressure outlet of a compressor (3) to the inlet of an expander (10), said high-pressure line (11) comprising a non-return valve system (4), at least one compressed gas cooling heat exchanger (5, 6), and a valve (9) Linear type control.
    [9" id="c-fr-0009]
    9. Refrigeration device according to any one of claims 1 to 8, characterized in that the working circuit comprises a pipe (12) low pressure connecting an output of a pressure reducer (10) to the inlet of a compressor (3), said low pressure line (12) comprising, a linear type regulating valve (9), at least one expanded gas heating heat exchanger (7, 6) and a nonreturn valve system (14) .
    [10" id="c-fr-0010]
    10. Refrigeration device according to claims 8 and 9 taken in combination, characterized in that the at least one heat exchanger comprises a countercurrent heat exchanger (7) putting in heat exchange the working fluid circulating in the pipes. (11, 12) high and low pressure.
    [11" id="c-fr-0011]
    11 .Delivery device according to any one of claims 8 to 10, characterized in that the at least one heat exchanger (5, 7) puts in heat exchange the working fluid with at least one of: water, air, nitrogen, helium, hydrogen, methane, neon, oxygen or argon.
    [12" id="c-fr-0012]
    12. Refrigeration device according to any one of claims 1 to 11, characterized in that the at least one linear type control valve (9) is actuated by its linear motor at the same frequency as the operating frequency of the expander (10) linear piston for which the valve (9) controls the supply or withdrawal of working fluid but out of phase with the actuation of the piston expander (10).
    [13" id="c-fr-0013]
    13. Refrigeration device according to any one of claims 1 to 12, characterized in that it comprises two compressors (20, 21) linear piston arranged in series, the working circuit comprising a first pipe (111) high pressure connecting a high pressure outlet of a first compressor (20) to the inlet of a second compressor (21) via a non-return valve system (14) and a second high pressure line (11) connecting an outlet to high pressure of the second compressor (21) at the inlet of the first compressor (20) via at least one exchanger (24, 26, 27) heat in heat exchange with the working fluid, a valve system (s) (14) , 4) nonreturn, at least one and preferably two linear control valves (9) and at least one and preferably two linear piston expander (25, 28), the at least one valve (9) of control being controlled to transfer fluid from the compressors (20, 21) and having heat exchanged with the at least one heat exchanger (24, 26, 27) to the at least one expander (25, 28) and then to transfer the expanded fluid from the at least one expander (25, 28) into the compressors (20, 21) with an intermediate heat exchange with at least one heat exchanger (24, 26, 27).
    [14" id="c-fr-0014]
    Cooling device according to claim 13, characterized in that the working circuit comprises a phase separator (29) arranged downstream of at least one control valve (9) for liquefying at least a portion of the working fluid. at the outlet of an expander (25, 28) and separating the liquid phase from the gaseous phase of the latter.
    [15" id="c-fr-0015]
    15. Refrigeration device according to claim 14, characterized in that the working circuit comprises a line (30) for sampling liquefied working fluid and a line (31) for supplying working fluid to the circuit in gaseous form.
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    WO2017137674A1|2017-08-17|
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    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    FR2084109A5|1970-03-02|1971-12-17|Knoeoes Stellan|Gas expansion plant - external combustion engine or heat pump on practically reversible operating cycle|
    SU1305506A1|1985-12-09|1987-04-23|Московский Институт Химического Машиностроения|Free-piston gas expansion machine-compressor|
    US20150052887A1|2012-01-12|2015-02-26|Isis Innovation Limited|Stirling cycle machines|
    US4267701A|1979-11-09|1981-05-19|Helix Technology Corporation|Helium liquefaction plant|
    FR2510181B1|1981-07-21|1984-04-27|Bertin & Cie|
    FR2668583B1|1990-10-26|1997-06-20|Air Liquide|PROCESS FOR LIQUEFACTION OF A GAS AND REFRIGERATION PLANT.|
    JPH0849943A|1994-08-08|1996-02-20|Yamaha Motor Co Ltd|Engine driven heat pump equipment|
    US6965444B1|2000-09-19|2005-11-15|Kabushiki Kaisha Toshiba|Image output method and system for distributing image output|
    JP4129126B2|2001-06-26|2008-08-06|松下電器産業株式会社|Linear compressor drive control method and vehicle linear compressor drive control method|
    FR2924205B1|2007-11-23|2013-08-16|Air Liquide|CRYOGENIC REFRIGERATION DEVICE AND METHOD|
    CN100575703C|2007-11-30|2009-12-30|西安交通大学|A kind of double-action free-piston type expansion-compressor bank|
    US9353975B2|2009-09-24|2016-05-31|Mitsubishi Electric Corporation|Refrigeration cycle apparatus with an expander to recover power from refrigerant|
    US20120117984A1|2010-11-11|2012-05-17|Quantum Design, Inc.|Valve assembly adapted for dynamic control of gas-flow about a cryogenic region|
    US9140478B2|2012-05-21|2015-09-22|Whirlpool Corporation|Synchronous temperature rate control for refrigeration with reduced energy consumption|
    KR102257508B1|2014-06-24|2021-05-31|엘지전자 주식회사|A linear compressor and a refrigerator including the same|FR3100319B1|2019-09-04|2021-08-20|Absolut System|Regenerative cryogenic machine|
    CN110986408A|2019-12-13|2020-04-10|中国科学院合肥物质科学研究院|Integrated neon refrigerator and refrigeration method|
    FR3107103A1|2020-02-12|2021-08-13|L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude|Compression device, installation, filling station and method using such a device|
    WO2022046468A1|2020-08-28|2022-03-03|SumitomoCryogenics Of America, Inc.|Reversible pneumatic drive expander|
    CN112460825A|2020-11-12|2021-03-09|新疆维吾尔自治区寒旱区水资源与生态水利工程研究中心|Single-piston compressed air refrigeration cycle device|
    法律状态:
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    2017-08-11| PLSC| Publication of the preliminary search report|Effective date: 20170811 |
    2018-02-23| PLFP| Fee payment|Year of fee payment: 3 |
    2020-02-19| PLFP| Fee payment|Year of fee payment: 5 |
    2021-11-12| ST| Notification of lapse|Effective date: 20211005 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1650962|2016-02-08|
    FR1650962A|FR3047551B1|2016-02-08|2016-02-08|CRYOGENIC REFRIGERATION DEVICE|FR1650962A| FR3047551B1|2016-02-08|2016-02-08|CRYOGENIC REFRIGERATION DEVICE|
    RU2018130607A| RU2018130607A|2016-02-08|2017-01-17|CRYOGENIC REFRIGERATOR|
    KR1020187023550A| KR20180108666A|2016-02-08|2017-01-17|Cryogenic freezer|
    CN201780008099.1A| CN108603701B|2016-02-08|2017-01-17|Low-temperature refrigerating device|
    PCT/FR2017/050098| WO2017137674A1|2016-02-08|2017-01-17|Cryogenic refrigeration device|
    JP2018538871A| JP6847966B2|2016-02-08|2017-01-17|Very low temperature freezer|
    EP17706538.0A| EP3414498B1|2016-02-08|2017-01-17|Cryogenic refrigeration device|
    US16/075,792| US11156388B2|2016-02-08|2017-01-17|Cryogenic refrigeration device|
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