Source: https://patents.google.com/patent/WO2013168206A1/en
Timestamp: 2020-08-13 04:12:49
Document Index: 441158388

Matched Legal Cases: ['art 24', 'art 24', 'art 25', 'art 24', 'art 24', 'art 24', 'art 25', 'art 24', 'art 25', 'Application No. 2012', 'art 25', 'art 27']

WO2013168206A1 - Refrigeration machine and cooling trap - Google Patents
Refrigeration machine and cooling trap Download PDF
WO2013168206A1
WO2013168206A1 PCT/JP2012/007104 JP2012007104W WO2013168206A1 WO 2013168206 A1 WO2013168206 A1 WO 2013168206A1 JP 2012007104 W JP2012007104 W JP 2012007104W WO 2013168206 A1 WO2013168206 A1 WO 2013168206A1
PCT/JP2012/007104
淳宏 桑島
憲司 工藤
大策 鷹野
2012-05-11 Priority to JP2012-109660 priority Critical
2012-05-11 Priority to JP2012109660 priority
2012-11-06 Application filed by キヤノンアネルバ株式会社 filed Critical キヤノンアネルバ株式会社
2013-11-14 Publication of WO2013168206A1 publication Critical patent/WO2013168206A1/en
238000001816 cooling Methods 0.000 title claims abstract description 60
Provided is a cooling trap using a Stirling refrigeration machine. A refrigeration machine (14) is provided with: a drive piston (31) for driving a free piston (35) so as to move an operating gas to and fro between a heat release section (25) and a heat absorption section (24); a vibration sensor (41) for measuring the vibration of a housing (22); a dynamic damper (45) for reducing the vibration of the housing (22) when the drive piston (31) is driven; and a frequency adjustment device for adjusting, while the housing (22) is connected to a vacuum device, a drive frequency in order to reduce the vibration of the housing (22) when the drive piston (31) is driven.
Refrigerator, cooling trap
The present invention relates to a refrigerator and a cooling trap using the refrigerator, for example, a heat storage type refrigerator having a cylinder structure, and a cooling trap using the refrigerator.
The cooling trap is a vacuum exhaust device effective for exhausting the inside of the vacuum vessel, in particular, exhausting moisture, and includes a refrigerator that cools a cooling panel installed in the vacuum vessel. Conventionally, GM (Gifford-McMahon) type refrigerators are generally used as refrigerators for cooling traps (for example, Patent Documents 1 and 2).
JP-A-10-184541 JP 2009-19500 A
Demands for reducing the footprint of vacuum processing equipment have led to demands for smaller refrigerators. However, since the GM refrigerator is configured to supply refrigerant gas compressed by a compressor, there is a problem that downsizing is difficult.
Therefore, it is conceivable to use a regenerative refrigerator having a cylinder structure such as a free piston type Stirling refrigerator as a cooling trap refrigerator. This is because a refrigerator having such a structure can be used as a refrigerator for a cooling trap in terms of refrigeration capacity and size. For example, a free piston type Stirling refrigerator (hereinafter referred to as a Stirling refrigerator) is provided with a cooling stage at the tip of a thin cylindrical cylinder in which a piston reciprocates. A cooling panel is attached to the cooling stage via a heat transfer member.
When the piston is reciprocated by operating a linear motor drive mechanism, the pressure of the working gas filling the cylindrical cylinder changes (isothermal compression, isothermal expansion), and the displacer has a phase difference with the piston. Reciprocate. As a result, while the working gas moves through the compression space, the heat radiating part, the regenerating part, the heat absorbing part, and the expansion space, the Stirling cycle is formed by performing heat absorption by the heat absorbing part and heat radiating by the heat radiating part (equal volume change). . In this way, by interlocking the piston and the displacer, a reversible cycle consisting of isothermal compression and isothermal expansion due to working gas pressure change and heat absorption and heat dissipation due to isovolume change during working gas flow is performed, thereby endothermic. The periphery of the part is cooled to a low temperature, and the object to be cooled is cooled by bringing the heat absorption part into contact with the object to be cooled.
The Stirling refrigerator has the disadvantage that vibration occurs because the piston and displacer continuously reciprocate inside. When the vibration of the Stirling refrigerator is transmitted to the vacuum vessel, it may resonate with the transfer device in the vacuum vessel and cause the substrate to be displaced.
An object of the present invention has been made in view of the above problems, and is to provide a refrigerator that can reduce vibration of a regenerative refrigerator having a cylinder structure such as a Stirling refrigerator. Another object of the present invention is to provide a cooling trap using a refrigerator with reduced vibration.
The refrigerator of the present invention includes a housing, a piston capable of reciprocating in the housing to compress and expand the working gas, and vibration reducing means for reducing vibration of the housing when the piston is driven. Driving frequency adjusting means for adjusting a driving frequency of the piston to reduce vibration of the casing when the piston is driven in a state where the casing is connected to a vacuum device. Features. Or the cooling trap of this invention cools the cooling panel which captures gas molecules using the above-mentioned refrigerator.
It is possible to provide a refrigerator that can reduce the vibration of a regenerative refrigerator having a cylinder structure such as a Stirling refrigerator. In addition, a cooling trap using a refrigerator that suppresses vibrations can be provided.
It is the schematic of the vacuum processing apparatus which concerns on one Embodiment of this invention. It is the schematic of the cooling trap which concerns on one Embodiment of this invention. It is the schematic of the internal structure of the refrigerator which concerns on one Embodiment of this invention. It is a system configuration figure of the refrigerator concerning one embodiment of the present invention. It is a related figure of the drive frequency and vibration value of the refrigerator which concerns on one Embodiment of this invention.
Embodiments of the present invention will be described with reference to the drawings. The members, arrangements, and the like described below are examples embodying the invention and do not limit the present invention, and it is needless to say that various modifications can be made in accordance with the spirit of the present invention. The configurations of the described embodiments can be applied in combination as appropriate. In the drawings described below, components having the same function are denoted by the same reference numerals, and repeated description thereof is omitted.
In this embodiment, a free piston type Stirling refrigerator is described as an example, but the present invention can be applied to a refrigerator having a piston that reciprocates in a cylinder. In this specification, when it is described as a Stirling refrigerator without particular notice, it refers to all regenerative refrigerators having a cylinder structure.
1 is a schematic diagram of a vacuum processing apparatus having a cooling trap according to an embodiment of the present invention, FIG. 2 is a schematic diagram of a cooling trap, FIG. 3 is a schematic diagram of the internal structure of a refrigerator, and FIG. 4 is a system of the refrigerator. FIG. 5 is a diagram showing the relationship between the drive frequency and vibration value of the refrigerator. In order to prevent complication of the drawing, the illustration is omitted except for a part.
A vacuum processing apparatus including a cooling trap will be described with reference to FIG. The vacuum processing apparatus 1 includes a cooling trap 10 and a turbo molecular pump (TMP) 7 as an evacuation apparatus 5 connected to the vacuum vessel 3. Inside the vacuum vessel 3, a predetermined vacuum process is performed on a material to be processed such as a substrate. The vacuum process performed in the vacuum vessel 3 is not limited to a specific process, but may be, for example, a film formation process by sputtering or CVD, or an etching process. Although the cooling trap 10 of this embodiment is attached between the vacuum vessel 3 and the TMP 7, a cooling trap may be attached inside the vacuum vessel 3, and the cooling trap 10 and the TMP 7 are connected to a pipe connected to the vacuum vessel 3. May be attached. Furthermore, the refrigerator according to the present invention is also applicable as a refrigerator for cooling the substrate holder.
The cooling trap will be described with reference to FIG. The cold trap 10 is attached to the refrigerator 14, the trap container 12 connected to the refrigerator 14, and the refrigerator 14 via the heat transfer member 27 and traps the gas from the vacuum container 3. It has a cooling panel 18 (trap section). The trap container 12 is connected to the vacuum container 3 and the TMP 7. The heat transfer member 27 is arranged in a cantilever structure in which one end is connected to the cooling stage 23 of the refrigerator 14 and the other end is connected to the cooling panel 18.
A vibration sensor 41 is attached to the trap container 12. The control unit 43 is attached to the casing of the refrigerator 14. The frequency adjusting device that controls the frequency of the linear motor 32 includes a control unit 43 and a vibration sensor 41. The vibration absorber 45 is configured to include the dynamic vibration absorber 45 and the frequency adjusting device. The dynamic vibration absorber 45, the frequency adjusting device, and the vibration absorption unit will be described later. In this embodiment, the vibration sensor 41 is attached to the trap container 12 via a flange 55 (attachment portion). However, the casing 22 of the refrigerator 14, the vacuum container 3, the cooling panel 18, the substrate holder, and the substrate transport You may attach to the member which is easy to vibrate in the vacuum vessel 3, such as an arm for. A member to which the refrigerator 14 can be attached is an external vacuum device. At this time, it is connected to the vacuum device via the mounting portion. Here, the attaching portion indicates a member for attaching to the vacuum apparatus in addition to the flange 55.
The trap container 12 is an aluminum container that separates the atmosphere from the vacuum, and can accommodate the heat transfer member 27 and the cooling panel 18 therein. Inside the trap container 12, the exhaust port of the vacuum container 3, the intake port of the TMP 7, and the cooling unit of the refrigerator 14 can be communicated with each other. In this embodiment, the refrigerator 14 attached to the trap container 12 is a free-piston Stirling refrigeration having the ability to cool a thin cylindrical cooling panel 18 to a cryogenic temperature capable of capturing gas molecules such as moisture in a vacuum. Machine. The cooling part refers to a range composed of a cooled part on the tip side of the cylinder 21 and the cooling stage 23. The other end side of the cylinder 21 refers to a portion of the cylinder 21 on the cooling stage 23 side.
The structure of the refrigerator according to this embodiment will be described with reference to FIG. In this embodiment, a free piston type Stirling refrigerator (hereinafter referred to as refrigerator 14) is used. The refrigerator 14 includes a housing 22 in which a cylinder 21 (cylinder part) is formed, and a flange 55 (attachment part) connected to the trap container 12. A cooling stage 23 is provided at the tip of the cylinder 21.
The refrigerator 14 further includes a radiator 56 made of an annular metal as a heat exhaust mechanism for discharging heat generated from the heat radiating unit 25 to the outside of the refrigerator main body. Although the heat radiating body 56 of the present embodiment is a structure having metal fins, a structure in which a refrigerant such as water is introduced into the inside and exhausted through the fluidized refrigerant may be employed.
The housing 22 has a shape in which a thin cylindrical member (cylinder 21) is provided on one end side of the cylindrical member. In the housing, a drive piston 31 (piston) driven so as to reciprocate in the longitudinal direction (axial direction) of the cylinder 21 by a linear motor 32, and a free piston provided so as to be able to reciprocate in the same direction as the drive piston 31. 35 (second piston), a phase adjustment spring 36 that adjusts the phase of the movement of the free piston 35, and a connecting shaft 33 that connects the free piston 35 and the phase adjustment spring 36. Among these, the free piston 35 is disposed inside the cylinder 21.
The space between the drive piston 31 and the free piston 35 is filled with working gas. As the working gas, for example, helium gas can be used, but other gases may be used. The outer peripheral surface of the free piston 35 is movable with a slight gap with the internal member of the cylinder 21. The drive piston 31 has a slight gap with the internal member of the housing 22 filled with the working gas. Can drive. Therefore, the working gas can be moved by the movement of the drive piston 31 and the free piston 35.
By driving the drive piston 31 with a predetermined phase difference from the free piston 35 and linking the operation of the free piston 35 in the axial direction, isothermal compression and isothermal expansion due to changes in the pressure of the working gas and operation are performed. A reversible cycle consisting of heat absorption and exhaust heat due to an equal volume change at the time of gas flow is performed, whereby the peripheral members of the heat absorption part 24 are cooled.
A heat absorption part 24 (expansion space) in which the working gas expands is formed at the front end side of the cylinder 21, and a heat radiation part 25 (compression space) in which the working gas is compressed is defined in a space between the free piston 35 and the drive piston 31. A heat exchanger 37 is provided in the working gas flow path between the heat dissipating unit 25 and the heat absorbing unit 24. In the heat radiating portion 25, heat is radiated from the working gas compressed by the free piston 35 and the drive piston 31. Therefore, a heat radiating body 56 as a heat radiating portion is provided at the lower end outside the cylinder 21 in contact with the heat radiating portion 25. In the heat absorption part 24, heat is absorbed from the working gas expanded by the movement of the free piston 35 and the drive piston 31, and therefore a cooling stage 23 is provided at a position in contact with the heat absorption part 24. The heat absorbing portion 24 and the heat radiating portion 25 are partitioned by a free piston 35.
The driving piston 31 and the free piston 35 are members that push or attract the working gas to reciprocate between the heat absorbing portion 24 and the heat radiating portion 25 by their movements. Therefore, it is desirable that the drive piston 31 and the free piston 35 have a cross-sectional shape that matches the inner surface shape of the portion in which they move. The shape of the drive piston 31 and the free piston 35 may be a plate shape (valve body) in addition to the columnar shape. The flange 55 is provided at a position between the heat absorbing part 24 and the heat radiating part 25. By disposing the heat absorbing part 24 on the vacuum side and the heat dissipating part 25 on the atmosphere side, heat dissipation becomes easy.
When the refrigerator 14 is operated and the cooling stage 23 at the top of the refrigerator 14 is cooled, cold heat is transmitted from the cooling stage 23 to the heat transfer member 27, and the cooling panel 18 connected to the heat transfer member 27 is cooled. . The heat transfer member 27 is a copper member arranged directly on the cooling stage 23, and transfers the cold heat of the cooling stage 23 to the cooling panel 18.
The water that jumps in from the inside of the vacuum vessel 3 and the water that returns from the turbo molecular pump 7 side are captured on the surface of the cooled cooling panel 18. The cooling stage 23, the heat transfer member 27, and the cooling panel 18 are each fixed with screws, and the contact surfaces of the components are attached with an indium sheet (not shown) sandwiched between the connection surfaces in order to improve heat transfer. sell.
説明 Explain the vibration absorption unit. The vibration absorbing unit includes a dynamic vibration absorber 45 (vibration reducing means) and a frequency adjusting device (driving frequency adjusting means). Further, the frequency adjusting device has at least a control unit 43.
The dynamic vibration absorber 45 includes a spring 51 (elastic member) attached to the housing 22 and a vibrating body 52 (weight) attached to the spring 51. The vibrating body 52 is composed of a metal member or the like. The spring 51 is constituted by a coil spring or a leaf spring, and one end is connected to the housing 22 side and the other end is connected to the vibrating body 52 (weight). By adjusting the natural frequency f of the dynamic vibration absorber 45, the vibrating body 52 vibrates at a phase angle that cancels the vibration of the refrigerator 14. The drive frequency of the drive piston 31 that absorbs vibrations best by the dynamic vibration absorber 45 is referred to as a set frequency (a preset drive frequency). The set frequency is set so as to coincide with the drive frequency at which the performance of the refrigerator 14 can be sufficiently exerted.
The natural frequency f of the dynamic vibration absorber 45 is determined from the spring constant of the spring 51 and the weight of the vibrating body 52. The dynamic vibration absorber 45 of this embodiment is provided at the bottom of the housing 22 so that the operation axis driven by the drive piston 31 and the operation axis where the vibration body 52 of the dynamic vibration absorber 45 vibrates are coaxial. With such an arrangement, vibration can be efficiently reduced.
The dynamic vibration absorber 45 is initially set so that the vibration of the refrigerator 14 is minimized when the drive piston 31 is driven at a set frequency in a state where the housing 22 (the refrigerator 14) is not connected to a vacuum vessel or the like. Yes. When the installation environment of the refrigerator 14 changes, such as fixing to a vacuum vessel, the drive frequency at which the dynamic vibration absorber 45 can effectively suppress vibration may change. That is, when the refrigerator 14 is driven at a set frequency while the refrigerator 14 is attached to the vacuum apparatus, the dynamic vibration absorber 45 may not be able to sufficiently reduce vibration. In such a case, the drive frequency is adjusted by the frequency adjusting device in order to reduce the vibration of the housing 22. That is, the vibration of the refrigerator 14 is reduced by adjusting the drive frequency of the refrigerator 14 to the drive frequency at which the dynamic vibration absorber 45 can best reduce the vibration while the housing 22 (the refrigerator 14) is attached to the vacuum apparatus. can do.
As described above, the vibration sensor 41 is provided in the trap container 12, and the control unit 43 is provided in the casing 22 of the refrigerator. The frequency adjusting device is a device for adjusting the piston driving frequency (driving frequency) of the refrigerator, and is a device that adjusts the driving frequency of the driving piston 31 so as to minimize vibration while referring to the measurement value from the vibration sensor 41. It is.
The system configuration of the frequency adjustment device will be described with reference to FIG. The frequency adjusting device of the refrigerator 14 includes a control unit 43 that controls the drive frequency of the drive piston 31 based on the measurement value of the vibration sensor 41. The control unit 43 is connected to a vibration sensor 41 that detects the vibration of the trap container 12. The control unit 43 also includes a band-pass filter 49 that filters a signal from the vibration sensor 41, an arithmetic unit 47 that processes a signal sent from the vibration sensor 41 via the band-pass filter 49, and a control signal from the arithmetic unit 47. And an inverter 48 for controlling the AC power at the drive frequency of the linear motor 32 as a main component. The computing unit 47 includes components (for example, an arithmetic circuit and a memory circuit) necessary for calculation for calculating the drive frequency. The control signal output from the calculator 47 is a value corresponding to the drive frequency output from the inverter 48.
The vibration sensor 41 of this embodiment may be mounted on a control board to which the computing unit 47 is attached, and the control board itself may be mounted on the refrigerator 14 or other vacuum apparatus. In the present embodiment, an acceleration sensor is used as the vibration sensor 41 that measures the vibration of the refrigerator 14, but a speedometer and a displacement meter can be substituted.
The signal output from the vibration sensor 41 is sent to the computing unit 47 through a center frequency variable bandpass filter (hereinafter referred to as a bandpass filter 49). The band pass filter 49 can adjust the center value of the pass frequency band based on the input control signal. As a control signal to be input to the band pass filter 49, a control signal (inverter control signal) corresponding to the drive frequency for driving the drive piston 31 is divided and input. As a result, the center frequency of the pass frequency band of the bandpass filter is automatically adjusted to the driving frequency for driving the driving piston 31, and the vibration signal from the vibration sensor 41 can be detected with a constant filter strength independent of the driving frequency. . With such a configuration, it is possible to correlate the vibration signal value for each drive frequency during the search. The band pass filter 49 uses a high-order filter with respect to the center frequency. This is to input a vibration signal to the computing unit 47 in a state where vibration signals and noise other than the vibration of the refrigerator 14 are cut.
As the band-pass filter 49, a switched capacitor filter (switched capacitor) or the like can be used. The bandpass filter 49 can be replaced by a software filter. At that time, the signal from the vibration sensor 41 is directly taken into the computing unit 47. The computing unit 47 calculates a control signal corresponding to the drive frequency that minimizes vibration based on the signal from the vibration sensor 41 and outputs the control signal to the inverter 48. The inverter 48 supplies AC power having a driving frequency corresponding to the control signal from the computing unit 47 to the linear motor 32 of the refrigerator 14 and drives the driving piston 31 at the driving frequency.
As described above, even when the band-pass filter 49 is replaced with a software filter, the software configuration is such that the vibration signal around the drive frequency is extracted. The computing unit 47 records the signal value from the vibration sensor 41 while changing the drive frequency within a range where the capacity of the refrigerator 14 is not reduced. The drive frequency (optimum drive frequency) that minimizes the signal value from the recorded vibration sensor 41 is searched, and the drive piston 31 is driven at that frequency. That is, in the computing unit 47, an operation for searching for a driving frequency at which the vibration value measured by the vibration sensor 41 is minimized while controlling the inverter 48 and changing the driving frequency of the refrigerator 14 is performed.
Since the change in the optimum drive frequency caused by attaching the refrigerator to the vacuum device such as the vacuum vessel 3 or the trap vessel 12 is small, the optimum drive frequency can be specified by searching for frequencies around the set frequency. The change in the optimum driving frequency caused by the secular change of the structural member such as the spring 51 is also a small value like the optimum frequency change when the refrigerator 14 is attached to the vacuum apparatus, and can be handled in the same manner.
Since the change in the optimum drive frequency due to the above is small, even if the drive frequency is corrected and the drive piston 31 is driven at the optimum drive frequency after the change, the performance of the refrigerator is not affected. In addition, even when the optimum drive frequency changes significantly due to other causes, the drive frequency range to be searched is set within a range in which the performance of the refrigerator 14 is not deteriorated. Therefore, the drive frequency is not changed as the performance of the refrigerator 14 decreases. That is, the frequency adjusting device according to the embodiment of the present invention does not deteriorate the performance of the refrigerator 14 when the set frequency of the dynamic vibration absorber 45 deviates from the optimum drive frequency due to a subsequent cause, and the state In this device, the vibration absorber 45 in FIG. 4 reduces the vibration of the refrigerator 14 by driving the drive piston 31 at the drive frequency (the optimum drive frequency after the change) that can best reduce the vibration.
In this embodiment, the drive frequency of the drive piston 31 is adjusted when the drive frequency (optimum drive frequency) at which the dynamic vibration absorber 45 can reduce the vibration is changed due to the fact that the cooling trap 10 is attached to the vacuum vessel 3. Described about what to do. However, even when the drive frequency changes due to the secular change of the spring of the dynamic vibration absorber 45, the vibration of the refrigerator 14 or the cooling trap 10 can be reduced by adjusting the drive frequency of the drive piston 31.
The relationship between the drive frequency of the refrigerator and the vibration value will be described based on FIG.
In the present embodiment, the drive frequency is 74.95 ± 0.01 Hz due to the effect that the refrigerator initially set so that the vibration is minimized when the refrigerator drive frequency is 75.00 Hz (set frequency) is attached to the vacuum vessel 3. The case where it changes so that the vibration of a refrigerator may become the minimum is demonstrated.
FIG. 5 also shows the acceleration sensor signal (vibration value) measured by the search method described above when the drive frequency was changed from 74.7 to 75.3 Hz. When the drive frequency (optimum drive frequency) that minimizes the vibration of the refrigerator is searched according to the search method described above, 74.95 ± 0.01 Hz is obtained. That is, the refrigerator is driven at 74.95 ± 0.01 Hz where the vibration of the refrigerator is minimized. By this operation, the drive frequency of the drive piston 31 of the refrigerator is changed from 75.00 Hz to 74.95 ± 0.01 Hz, but with such a change, the performance of the refrigerator is hardly deteriorated.
According to the present invention, a refrigerator with reduced vibration can be provided. Moreover, according to this invention, the cooling trap using the refrigerator which reduced the vibration can be provided. The vibration of the refrigerator or the cooling trap can be further reduced by providing the vibration absorption unit including the refrigerator or the dynamic vibration absorber and the drive frequency adjustment device (frequency adjustment device).
Even if the refrigerator does not include a frequency adjusting device, a refrigerator or a cooling trap that can reduce vibration to some extent can be provided. However, the dynamic vibration absorber is initially set so that vibration is minimized when the Stirling refrigerator is operated at the set frequency. Therefore, in the conventional refrigerator, when the drive frequency at which the dynamic vibration absorber can effectively suppress vibration changes, screws or magnets are added to or removed from the vibration body of the dynamic vibration absorber to physically reduce its mass. Adjustment work was required. In addition, when the conventional refrigerator is mounted in a vacuum vessel, the above-mentioned difficulty is caused by the deviation of the natural frequency of the dynamic vibration absorber, the resonance with the members in the vacuum vessel, the environmental temperature and the deterioration of the dynamic vibration spring over time. It may be necessary to perform the adjustment work again.
Like the refrigerator 14 of the embodiment of the present invention, the refrigerator includes the dynamic vibration absorber and the frequency adjustment device, so that even when the drive frequency (optimum drive frequency) at which the dynamic vibration absorber can reduce vibration most changes, The refrigerator can change the drive frequency to an optimum drive frequency simply and reliably. Therefore, the refrigerator or the cooling trap can effectively reduce vibration. At this time, it is not necessary to adjust the mass of the vibrating body of the dynamic vibration absorber, such as adding or removing screws or magnets, and the maintenance time can be greatly shortened. Further, the same effect as described above can be obtained by using the cooling trap vibration reducing method of the embodiment of the present invention.
This application claims priority based on Japanese Patent Application No. 2012-109660 filed on May 11, 2012, the entire contents of which are incorporated herein by reference.
DESCRIPTION OF SYMBOLS 1 Vacuum processing apparatus 3 Vacuum container 5 Vacuum exhaust apparatus 7 Turbo molecular pump (TMP)
DESCRIPTION OF SYMBOLS 10 Cooling trap 12 Trap container 14 Refrigerator 18 Cooling panel 21 Cylinder 22 Case 23 Cooling stage 24 Heat absorption part 25 Heat radiation part 27 Heat transfer member 31 Drive piston 32 Linear motor 35 Free piston 36 Phase adjustment spring 37 Heat exchanger 41 Vibration sensor 43 Control unit 45 Dynamic vibration absorber 47 Operation unit 48 Inverter 49 Band pass filter 51 Spring 52 Vibrating body (weight)
55 Flange 56 Radiator
A piston capable of reciprocating within the housing to compress and expand the working gas;
Vibration reducing means for reducing vibration of the housing when the piston is driven;
Drive frequency adjusting means for adjusting the drive frequency of the piston to reduce vibration of the housing when the piston is driven in a state where the housing is connected to a vacuum device. Refrigerator.
The refrigerator according to claim 1, further comprising a measuring unit that measures vibration of the casing.
The vibration reducing means includes an elastic member having one end connected to the housing and the other end connected to a weight,
2. The refrigerator according to claim 1, wherein the drive frequency adjusting unit searches the drive frequency of the piston that minimizes vibration of the housing while changing the drive frequency.
A second piston is provided that reciprocates within the housing with a predetermined phase difference from the piston, and is disposed between a space where the working gas is compressed and a space where the working gas is expanded. Item 4. The refrigerator according to any one of items 1 to 3.
The refrigerator according to any one of claims 1 to 4, further comprising an attachment portion that connects the casing to the vacuum device.
A cooling trap that cools a cooling panel that captures gas molecules using the refrigerator according to any one of claims 1 to 5.
PCT/JP2012/007104 2012-05-11 2012-11-06 Refrigeration machine and cooling trap WO2013168206A1 (en)
JP2012-109660 2012-05-11
JP2012109660 2012-05-11
KR1020147015472A KR101573647B1 (en) 2012-05-11 2012-11-06 Cold trap
CN201280064197.4A CN104011484B (en) 2012-05-11 2012-11-06 Cold-trap device
JP2014514238A JP5711424B2 (en) 2012-05-11 2012-11-06 Refrigerator, cooling trap
US14/279,382 US9421478B2 (en) 2012-05-11 2014-05-16 Refrigerator and cold trap
US14/279,382 Continuation US9421478B2 (en) 2012-05-11 2014-05-16 Refrigerator and cold trap
WO2013168206A1 true WO2013168206A1 (en) 2013-11-14
ID=49550292
PCT/JP2012/007104 WO2013168206A1 (en) 2012-05-11 2012-11-06 Refrigeration machine and cooling trap
US (1) US9421478B2 (en)
JP (1) JP5711424B2 (en)
KR (1) KR101573647B1 (en)
CN (1) CN104011484B (en)
WO (1) WO2013168206A1 (en)
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2012-11-06 WO PCT/JP2012/007104 patent/WO2013168206A1/en active Application Filing
2012-11-06 CN CN201280064197.4A patent/CN104011484B/en active IP Right Grant
2012-11-06 JP JP2014514238A patent/JP5711424B2/en active Active
2012-11-06 KR KR1020147015472A patent/KR101573647B1/en active IP Right Grant
2014-05-16 US US14/279,382 patent/US9421478B2/en active Active
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