CN104729137A - Cryogenic refrigerator - Google Patents
Cryogenic refrigerator Download PDFInfo
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- CN104729137A CN104729137A CN201410733757.1A CN201410733757A CN104729137A CN 104729137 A CN104729137 A CN 104729137A CN 201410733757 A CN201410733757 A CN 201410733757A CN 104729137 A CN104729137 A CN 104729137A
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- refrigerant gas
- displacer
- expansion space
- gas stream
- low temperature
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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
- F25B9/10—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
- F25B2500/00—Problems to be solved
- F25B2500/09—Improving heat transfers
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
The invention relates to a cryogenic refrigerator, and provides a technology, which can be used to reduce the shuttle loss, improve the heat exchange efficiency between the refrigerant gas and the heat exchanger. In a cryogenic refrigerator 1, a displacer 2 includes a cover portion at a low temperature end of the displacer. A cylinder 4 accommodates the displacer 2 to be reciprocated in a longitudinal direction and forms an expansion space of a refrigerant gas between the cover portion and the cylinder. A refrigerant gas channel 16 through which the displacer 2 and the expansion space communicate with each other is formed in the cover portion. In the refrigerant gas channel, a flowing-out direction of the refrigerant gas flowing into the expansion space is inclined with respect to the longitudinal direction of the displacer 2.
Description
The application advocates the priority of No. 2013-261441st, the Japanese patent application based on application on December 18th, 2013.The full content of this Japanese publication is by reference to being applied in this description.
Technical field
The present invention relates to a kind of use produce west illiteracy expansion from the higher pressure refrigerant gas that compression set supplies and produce the ultra-low temperature refrigerating device of ultralow temperature cold, particularly relate to a kind of displacer used in ultra-low temperature refrigerating device.
Background technology
Routine as of the refrigeration machine producing ultralow temperature, there will be a known Ji Fude-McMahon (Gifford-McMahon; GM) refrigeration machine.GM refrigeration machine makes the volume of expansion space change by making displacer move back and forth in cylinder body.By with this Volume Changes accordingly, optionally connect the exhaust end of expansion space and compressor and expansion space and suction side, thus refrigerant gas is expanded in expansion space.By the cold now produced, cooling object is cooled.
Patent document 1: Japanese Unexamined Patent Publication 2013-142479 publication
What be representative with GM refrigeration machine possesses in the refrigeration machine of displacer, in order to make displacer move back and forth in cylinder body, between cylinder body and displacer, is provided with gap.Be provided with cooling bench in the low temperature side end of cylinder body, the part in this gap plays a role as the heat exchanger carrying out heat exchange between the refrigerant gas in gap and cooling bench.On the other hand, also the heat conduction and existing of the known refrigerant gas because existing in gap is referred to as the loss of loss of shuttling back and forth.
If lengthen heat exchanger and widen the heat exchange area with refrigerant gas, then the heat exchange efficiency between refrigerant gas and cooling bench is improved.But heat exchanger is longer, loss of shuttling back and forth is larger.So, the raising based on the heat exchange efficiency changing heat exchanger length is in shifting relation with the reduction of losing of shuttling back and forth.
Summary of the invention
The present invention completes in view of this problem, its object is to provide a kind of and reduces loss of shuttling back and forth, and improve the technology of the heat exchange efficiency between refrigerant gas and heat exchanger.
In order to solve above-mentioned problem, the ultra-low temperature refrigerating device of one embodiment of the present invention possesses displacer; Cap, is arranged on the low-temperature end of displacer; And cylinder body, displacer is held into and moves back and forth freely along long side direction, and between cap, form the expansion space of refrigerant gas.Be formed with the refrigerant gas stream be communicated with expansion space by displacer in cap, the outflow direction that refrigerant gas stream is arranged to the refrigerant gas flowed out in expansion space tilts relative to the long side direction of displacer.
According to the present invention, can provide a kind of and reduce loss of shuttling back and forth, and improve the technology of the heat exchange efficiency between refrigerant gas and heat exchanger.
Accompanying drawing explanation
Fig. 1 is the schematic diagram schematically representing ultra-low temperature refrigerating device involved by one embodiment of the present invention and displacer.
Fig. 2 (a)-Fig. 2 (b) is the figure of an example of the refrigerant gas stream represented in the ultra-low temperature refrigerating device involved by embodiments of the present invention.
Fig. 3 (a)-Fig. 3 (b) is the figure of another example of the refrigerant gas stream represented involved by embodiments of the present invention.
Fig. 4 is the schematic diagram of the structure of the 2 grades of formula ultra-low temperature refrigerating devices represented involved by embodiments of the present invention.
Fig. 5 (a)-Fig. 5 (b) is the schematic diagram of another structure of the 2 grades of formula ultra-low temperature refrigerating devices represented involved by embodiments of the present invention.
Fig. 6 represents the ultra-low temperature refrigerating device involved by a variation of embodiments of the present invention and the schematic diagram of displacer.
In figure: 1-ultra-low temperature refrigerating device, 2-displacer, 2a-main part, 2b-cap, 3-expansion space, 4-cylinder body, 5-cooling bench, 7-regenerator, 8-Room, 11-upper opening, 12-compressor, 13-supply valve, 14-return valve, 15-seal, 16-refrigerant gas stream, 17-the 1st opening portion, 18-the 2nd opening portion, 19-interior surface, 20-outer surface, 31-ultra-low temperature refrigerating device, 32-the 1st displacer, 32b-cap, 33-sells, 34-connector, 35-sells, 36-the 2nd displacer, 37-the 1st cylinder body, 38-the 2nd cylinder body, 39-Room, 41-the 1st regenerator, 42-upper opening, 43-compressor, 44-supply valve, 45-return valve, 46-seal, 47-the 1st expansion space, 48-refrigerant gas stream, 49-the 1st cooling bench, 50-the 2nd regenerator, 51-the 2nd expansion space, 52b-cap, 53-helicla flute, 54-the 2nd cooling bench, 56-refrigerant gas stream.
Detailed description of the invention
By reference to the accompanying drawings embodiments of the present invention are described.
Ultra-low temperature refrigerating device 1 involved by embodiment is such as the refrigeration machine of Ji Fude-McMahon (GM) formula helium being used as refrigerant gas.Ultra-low temperature refrigerating device 1 possesses displacer 2, between displacer 2, form the cooling bench 5 of the bottomed cylindrical that the cylinder body 4 of expansion space 3 and mode that is adjacent with expansion space 3 and that surround this expansion space 3 in addition exist.Cooling bench 5 plays a role as the heat exchanger carrying out heat exchange between cooling object and refrigerant gas.Displacer 2 comprises main part 2a and the cap 2b in low-temperature end.Cap 2b can be made up of the parts identical with main part 2a.Further, cap 2b also can be made up of the material of thermal conductivity factor higher than main part 2a.Thus, cap 2b is also as playing a role flowing through the heat-conducting part carrying out heat exchange between the refrigerant gas in cap 2b.Cap 2b such as uses the thermal conductivity factors such as copper, aluminium, stainless steel to be at least greater than the material of main part 2a.Cooling bench 5 is such as made up of copper, aluminium, stainless steel etc.
Compressor 12 reclaims low pressure refrigerant gas from suction side, and the backward ultra-low temperature refrigerating device 1 compressed supplies higher pressure refrigerant gas.As refrigerant gas, such as, can use helium etc., but be not limited thereto.
Displacer 2 holds into and can move back and forth along long side direction by cylinder body 4.Consider from viewpoints such as intensity, thermal conductivity factor, helium isolating powers, cylinder body 4 such as uses stainless steel.
Be provided with the not shown scotch yoke mechanism back and forth driving displacer 2 in the temperature end of displacer 2, displacer 2 moves along the axial reciprocating of cylinder body 4.
Displacer 2 has cylindric outer peripheral face, is filled with cool storage material in the inside of displacer 2.The internal capacity of this displacer 2 forms regenerator 7.The rectifier (not shown) flowing of helium being carried out to rectification can be provided with in the upper end side of regenerator 7 and lower end side.
The upper opening 11 that refrigerant gas is circulated from this Room 8 to displacer 2 is formed in the temperature end of displacer 2.Room 8 is the space formed by the temperature end of cylinder body 4 and displacer 2, and its volume changes along with moving back and forth of displacer 2.
Room 8 is connected with by the common pipe arrangement of supply and discharge in the interconnective pipe arrangement of suction and discharge system that is made up of compressor 12, supply valve 13, return valve 14.Further, partially leaning between the part of temperature end and cylinder body 4 of displacer 2, seal 15 is installed.
The refrigerant gas stream 16 importing refrigerant gas to expansion space 3 is formed in the low-temperature end of displacer 2.Expansion space 3 is the space formed by cylinder body 4 and displacer 2, and its volume changes along with moving back and forth of displacer 2.Be configured with in the position corresponding with expansion space 3 of the periphery of cylinder body 4 and bottom and cool the hot linked cooling bench 5 of object, cooling bench 5 is cooled by the refrigerant gas being flowed into expansion space 3 by refrigerant gas stream 16.
Consider from viewpoints such as proportion, intensity, thermal conductivity factors, the main part 2a of displacer 2 such as uses phenolic resins etc.Cool storage material is such as made up of woven wire etc.In addition, the operating state of ultra-low temperature refrigerating device 1 shown in Fig. 1.Therefore, along with main part 2a shrinks a little because of low temperature, main part 2a and cap 2b are in the identical state of external diameter, but at normal temperatures, the external diameter of cap 2b is slightly less than the external diameter of main part 2a.
Then, the action of ultra-low temperature refrigerating device 1 is described.At the point sometime of refrigerant gas supply step, displacer 2 is positioned at the lower dead center LP of cylinder body 4.If the moment of meanwhile or a little staggering opens supply valve 13, then higher pressure refrigerant gas is supplied in cylinder body 4 from the common pipe arrangement of supply and discharge via supply valve 13.Its result, higher pressure refrigerant gas flows into the regenerator 7 of displacer 2 inside from the upper opening 11 being arranged in displacer 2 top.While the higher pressure refrigerant gas flow in regenerator 7 is cooled by cool storage material, be supplied to expansion space 3 via the refrigerant gas stream 16 being positioned at displacer 2 bottom.
If expansion space 3 is filled up by higher pressure refrigerant gas, then supply valve 13 is closed.Now, displacer 2 is positioned at the top dead centre UP of cylinder body 4.If the moment of meanwhile or a little staggering opens return valve 14, then the refrigerant gas of expansion space 3 is depressurized and expands.The heat of cooling bench 5 is absorbed by the helium being expanded into the expansion space 3 of low temperature.
Displacer 2 moves towards lower dead center LP, thus the volume of expansion space 3 reduces.Refrigerant gas in expansion space 3 turns back to the suction side of compressor 12 via refrigerant gas stream 16, regenerator 7, upper opening 11.Now, cool storage material cooled dose of gas cooling.Using this operation as 1 circulation, ultra-low temperature refrigerating device 1 repeats this cool cycles, cools thus to cooling bench 5.
In the ultra-low temperature refrigerating device 1 involved by embodiment and displacer 2, the heat entered from cooling bench 5 enters to cap 2b via the refrigerant gas existed expansion space 3.That is, when the low temperature refrigerant gas produced in expansion space 3 is by refrigerant gas stream 16, between refrigerant gas and cap 2b, heat exchange is carried out.
Further, the heat entering into cap 2b transmits towards expansion space 3 in cap 2b inside further.As mentioned above, cap 2b is possessed in the low-temperature end of displacer 2.Therefore, cap 2b contacts with the low temperature refrigerant gas in expansion space 3, thus can improve the heat exchange efficiency between cooling bench 5 and refrigerant gas further.
In addition, the cap 2b of displacer 2 is sometimes also made up of such as phenolic resins etc.But compared with the ultra-low temperature refrigerating device 1 involved by the present embodiment being made up cap 2b of thermal conductivity factor higher than the material of main part 2a, the heat exchange between refrigerant gas and lid reduces, and does not substantially carry out heat exchange.Therefore, carry out heat exchange between the low temperature refrigerant gas only produced in expansion space 3 and cooling bench 5, cooling effectiveness declines.Therefore, with regard to the Gai Eryan of displacer 2, preferably make cap 2b by thermal conductivity factor higher than the material of main part 2a.
As described above, in the ultra-low temperature refrigerating device 1 involved by embodiment, displacer 2 moves back and forth in cylinder body 4, thus makes the refrigerant gas in expansion space 3 expand and produce cold.As shown in Figure 1, in order to moving back and forth of displacer 2, between cylinder body 4 and displacer 2, be provided with clearance C.Part adjacent with cooling bench 5 in clearance C plays a role as the heat exchanger carrying out heat exchange between the refrigerant gas in cooling bench 5 and clearance C.
At this, be also known as and made the refrigerant gas in displacer 2 be made by heat exchanger refrigerant gas stream 16 towards the technology of the radial direction (direction towards the side of cylinder body 4) of cylinder body 4.According to the method, although the advantage having heat exchange area to increase, there is the trend that the bending and flow path area of refrigerant gas stream 16 narrows.Its result, flow path resistance increases, thus produces the pressure loss.Further, when displacer 2 moves back and forth in cylinder body 4, because of the heat conduction of refrigerant gas that exists in clearance C and the loss produced and so-called " loss of shuttling back and forth " also increase.
Loss of shuttling back and forth is reduced, refrigerant gas stream 16 is axially set and makes the technology that refrigerant gas to flow out to the bottom surface of cylinder body 4 at cylinder body 4 in contrast, be also known as.The method owing to actively not carrying out heat exchange in clearance C, therefore, it is possible to the flow path resistance of reduction refrigerant gas stream 16.Therefore, with by refrigerant gas stream 16 towards the radial direction of cylinder body 4 method compared with, the pressure loss and shuttle back and forth loss reduce.On the other hand, the heat exchange area between the refrigerant gas expanded in expansion space 3 and cooling object narrows, and heat exchange efficiency declines.
Therefore, the refrigerant gas stream 16 that displacer 2 is communicated with expansion space 3 is arranged to when the refrigerant gas flowed into from displacer 2 flows out in expansion space 3 involved by embodiment, makes it tilt towards the long side direction relative to displacer 2.Below, the refrigerant gas stream 16 involved by embodiment is more specifically illustrated.
One example of the refrigerant gas stream 16 shown in Fig. 1 involved by embodiment.As shown in Figure 1, be provided with the 1st opening portion 17 on the surface (hereinafter referred to as " interior surface 19 ") of the private side of the displacer 2 of the cap 2b of displacer 2, and the surface (hereinafter referred to as " outer surface 20 ") of outer side at displacer 2 is provided with the 2nd opening portion 18.Refrigerant gas stream 16 to be arranged to the 1st opening portion 17 as one end, using the 2nd opening portion 18, as the other end, the interior surface 19 in cap 2b be communicated with outer surface 20.
At this, refrigerant gas stream 16 is arranged to as follows: when the 1st opening portion 17 in interior surface 19 is projected to outer surface 20 along the long side direction of displacer 2, the position of the 1st opening portion 17 after projection is different from the position of the 2nd opening portion 18.Thus, when the refrigerant gas flowed into from the 1st opening portion 17 flows out in expansion space 3 from the 2nd opening portion 18, refrigerant gas flows out to the direction different from the long side direction of displacer 2.Its result, with axially arrange compared with the situation of refrigerant gas stream 16 towards the below in Fig. 1 along cylinder body 4, ultra-low temperature refrigerating device 1 involved by embodiment passes through the effect of the refrigerant gas flowed out in expansion space 3 from the 2nd opening portion 18, easily produces the eddy current of refrigerant gas in expansion space 3.Therefore, the heat exchange efficiency between refrigerant gas and cooling bench 5 is improved.
Further, with make refrigerant gas stream 16 towards the radial direction of cylinder body 4 situation compared with, the ultra-low temperature refrigerating device 1 involved by embodiment due to the flow path area of refrigerant gas stream 16 can be widened, therefore, it is possible to reduce shuttle back and forth loss and the pressure loss.
At this, the refrigerant gas that refrigerant gas stream 16 is preferably arranged to flow out from the 2nd opening portion 18 is towards the side of cylinder body 4.Thus, the side collision of the refrigerant gas and the cylinder body 4 that flow out from the 2nd opening portion 18 and change moving direction, the flowing of the refrigerant gas therefore in expansion space 3 becomes complexity.Therefore, in expansion space 3, more easily produce the eddy current of refrigerant gas, thus the heat exchange efficiency between refrigerant gas and cooling bench 5 is further enhanced.
In addition, preferably multiple refrigerant gas stream 16 be communicated with the 2nd opening portion 18 1st opening portion 17 is set at the cap 2b of displacer 2.Thereby, it is possible to widen the flow path area of refrigerant gas stream 16 entirety, thus the pressure loss can be reduced further.Further, because refrigerant gas flows out in expansion space 3 from multiple position, the flowing of the refrigerant gas therefore in expansion space 3 becomes complicated.Therefore, in expansion space 3, easily produce the turbulent flow of refrigerant gas, the heat exchange efficiency between refrigerant gas and cooling bench 5 is further enhanced.
Fig. 2 (a)-Fig. 2 (b) is the figure of another example of the refrigerant gas stream 16 represented in the ultra-low temperature refrigerating device 1 involved by embodiments of the present invention.Identical with the example shown in Fig. 1, the refrigerant gas stream 16 of the example shown in Fig. 2 (a) and Fig. 2 (b) be also arranged to using the 1st opening portion 17 as one end, using the 2nd opening portion 18 as the other end, the interior surface 19 in cap 2b is communicated with outer surface 20.Further, be arranged to when the 1st opening portion 17 in interior surface 19 is projected to outer surface 20 along the long side direction of displacer 2, the position of the 1st opening portion 17 after projection is different from the position of the 2nd opening portion 18.
On the other hand, example shown in Fig. 2 (a) and Fig. 2 (b) is different from the example shown in Fig. 1, and the direction of being flowed out in expansion space 3 by the refrigerant gas of a refrigerant gas stream 16 is identical with the direction that the refrigerant gas by other refrigerant gas streams 16 flows out in expansion space 3.Thus, the active force of the refrigerant gas flowed out to expansion space 3 works to the direction making the refrigerant gas of expansion space 3 rotate, thus the refrigerant gas of expansion space 3 easily produces eddy current.In addition, in the example shown in Fig. 2 (a), refrigerant gas stream 16 is configured to linearity, in contrast, in the example shown in Fig. 2 (b), refrigerant gas stream 16 is configured to spiral-shaped.Compared with the example shown in Fig. 2 (b), the example shown in Fig. 2 (a) is easily processing this one side of refrigerant gas stream 16 effectively.On the other hand, compared with the example shown in Fig. 2 (a), in the example shown in Fig. 2 (b), refrigerant gas stream 16 is elongated.Therefore, there is the effect that the heat exchange efficiency between the refrigerant gas flowing through refrigerant gas stream 16 and cap 2b is improved.
Fig. 3 (a)-Fig. 3 (b) is the figure of the another example of the refrigerant gas stream 16 represented involved by embodiments of the present invention, is the stereogram representing cap 2b and refrigerant gas stream 16.More specifically, Fig. 3 (a)-Fig. 3 (b) is the figure arranging the situation of 4 refrigerant gas streams 16 (refrigerant gas stream 16a, 16b, 16c and 16d) at cap 2b respectively.In addition, compared with the example shown in Fig. 1, Fig. 2 (a) and Fig. 2 (b), in Fig. 3 (a)-Fig. 3 (b), omit a part for cap 2b shape.
At this, 4 articles of refrigerant gas streams 16 shown in Fig. 3 (a) are configured to the example of linearity respectively to the 2nd opening portion 18 from the 1st opening portion 17.Further, shown in Fig. 3 (b), 4 articles of refrigerant gas streams 16 are configured to spiral-shaped example from the 1st opening portion 17 respectively to the 2nd opening portion 18.In Fig. 3 (a)-Fig. 3 (b), the direction of being flowed out in expansion space 3 by the refrigerant gas of a refrigerant gas stream 16 in 4 refrigerant gas streams 16 is different from the direction that the refrigerant gas by other refrigerant gas streams 16 flows out in expansion space 3.
Such as, in Fig. 3 (a), flowed out to lower right in Fig. 3 (a) in expansion space 3 by the refrigerant gas of refrigerant gas stream 16a.In contrast, by the refrigerant gas of the refrigerant gas stream 16c opposition side to the outflow direction of the refrigerant gas by refrigerant gas stream 16a expansion space 3 in, i.e. lower left outflow in Fig. 3 (a).Thus, the active force of the refrigerant gas flowed out to expansion space 3 works to the direction making the refrigerant gas of expansion space 3 rotate, thus the refrigerant gas of expansion space 3 easily produces eddy current.
More specifically, in Fig. 3 (a), 4 refrigerant gas streams 16 are arranged to the central shaft Rotational Symmetry of the long side direction relative to displacer 2.At this, the central shaft of the long side direction of displacer 2 is consistent with central shaft when cap 2b being regarded as cylinder.Therefore, in Fig. 3 (a), can also say that 4 refrigerant gas streams 16 are arranged to the central shaft Rotational Symmetry relative to cap 2b.
Such as, if by the 90-degree rotation clockwise centered by central shaft of the cap 2b shown in Fig. 3 (a), then the position of postrotational refrigerant gas stream 16a, 16b, 16c and 16d respectively with rotate before refrigerant gas stream 16b, 16c, 16d and 16a consistent.Also identical when revolving turnback or 270 degree, the position of postrotational refrigerant gas stream 16a, 16b, 16c and 16d respectively with rotate before refrigerant gas stream 16a, 16b, 16c and 16d in any one is consistent.
Thus, the refrigerant gas flowed out to expansion space 3 by refrigerant gas stream 16a, 16b, 16c and 16d all plays the effect that the refrigerant gas of expansion space 3 is rotated to same direction of rotation.As a result, the refrigerant gas of expansion space 3 easily produces eddy current, thus the heat exchange efficiency between the refrigerant gas that can improve further in expansion space 3 and cap 2b.
In addition, identical with the example shown in Fig. 3 (a), in the example shown in Fig. 3 (b), 4 refrigerant gas streams 16 are also arranged to the central shaft Rotational Symmetry of the long side direction relative to displacer 2.Therefore, its action effect is also identical with the example shown in Fig. 3 (a), and the refrigerant gas of expansion space 3 easily produces eddy current, thus the heat exchange efficiency between the refrigerant gas that can improve further in expansion space 3 and cap 2b.
Above, as the ultra-low temperature refrigerating device 1 involved by embodiment, one-level formula ultra-low temperature refrigerating device is illustrated as an example.But ultra-low temperature refrigerating device 1 is not limited to one-level formula, also can be multi-stag, such as, can be applicable to 2 grades of following formula ultra-low temperature refrigerating devices.
Fig. 4 is the schematic diagram of the 2 grades of formula ultra-low temperature refrigerating devices 31 represented involved by embodiments of the present invention.Ultra-low temperature refrigerating device 31 and above-mentioned one-level formula ultra-low temperature refrigerating device 1 are similarly the refrigeration machine of Ji Fude-McMahon (GM) formula helium being used as refrigerant gas.As shown in Figure 4, ultra-low temperature refrigerating device 31 the 2nd displacer 36 that possesses the 1st displacer 32 and link on long side direction with the 1st displacer 32.Such as, as shown in Figure 5, the 1st displacer 32 is connected via pin 33, connector 34, pin 35 with the 2nd displacer 36.
1st cylinder body 37 and the 2nd cylinder body 38 form as one, and the low-temperature end of the 1st cylinder body 37 is connected in the bottom of the 1st cylinder body 37 with the temperature end of the 2nd cylinder body 38.2nd cylinder body 38 is coaxially to be formed with the 1st cylinder body 37 and diameter is less than the cylinder part of the 1st cylinder body 37.1st displacer 32 holds into and can move back and forth along long side direction by the 1st cylinder body 37, and the 2nd displacer 36 holds into and can move back and forth along long side direction by the 2nd cylinder body 38.
Consider intensity, thermal conductivity factor, helium isolating power etc., the 1st cylinder body 37, the 2nd cylinder body 38 such as use stainless steel.2nd displacer 36 is consisted of the outer peripheral face of the metal cylinders such as the coated stainless steel of diaphragm with fluororesin uniform wearability resin.
1st displacer 32 has cylindric outer peripheral face, is filled with the 1st cool storage material (not shown) in the inside of the 1st displacer 32.The internal capacity of the 1st displacer 32 plays a role as the 1st regenerator 41.Although not shown, but also on the top of the 1st regenerator 41 and bottom, rectifier can be set respectively.The upper opening 42 that refrigerant gas is circulated from Room 39 to the 1st displacer 32 is formed in the temperature end of the 1st displacer 32.Room 39 is the space formed by the temperature end of the 1st cylinder body 37 and the 1st displacer 32, and its volume changes along with the 1st moving back and forth of displacer 32.Room 39 is connected with by the common pipe arrangement of supply and discharge in the interconnective pipe arrangement of suction and discharge system that is made up of compressor 43, supply valve 44, return valve 45.Further, partially leaning between the part of temperature end and the 1st cylinder body 37 of the 1st displacer 32, seal 46 is installed.
The refrigerant gas stream 48 refrigerant gas being imported to the 1st expansion space 47 is formed in the low-temperature end of the 1st displacer 32.1st expansion space 47 is the space formed by the 1st cylinder body 37 and the 1st displacer 32, and its volume changes along with the 1st moving back and forth of displacer 32.In the 1st cylinder body 37 periphery, the position corresponding with the 1st expansion space 47 is configured with hot linked 1st cooling bench the 49,1st cooling bench 49 with not shown cooled object and is cooled by the refrigerant gas of the 1st expansion space 47.
2nd displacer 36 has cylindric outer peripheral face, is filled with the 2nd cool storage material (not shown) in the inside of the 2nd displacer 36.The internal capacity of the 2nd displacer 36 forms the 2nd regenerator 50.1st expansion space 47 is communicated with by not shown access with the temperature end of the 2nd displacer 36.Refrigerant gas circulates to the 2nd regenerator 50 from the 1st expansion space 47 via this access.
The refrigerant gas stream 56 for making refrigerant gas circulate to the 2nd expansion space 51 is formed in the low-temperature end of the 2nd displacer 36.2nd expansion space 51 is the space formed by the 2nd cylinder body 38 and the 2nd displacer 36, and its volume changes along with the 2nd moving back and forth of displacer 36.
In the 2nd cylinder body 38 periphery, the position corresponding with the 2nd expansion space 51 is configured with and cools hot linked 2nd cooling bench the 54,2nd cooling bench 54 of object and cooled by the refrigerant gas in the 2nd expansion space 51.
Consider from viewpoints such as proportion, intensity, thermal conductivity factors, the 1st displacer 32 such as uses folder cloth phenolic aldehyde etc.1st cool storage material is such as made up of woven wire etc.Further, the 2nd cool storage material is by clamping the cool storage materials such as such as shot in the axial direction with felt and woven wire and form.In addition, be formed spirally to the helicla flute 53 that the 1st side, expansion space 47 extends at the outer peripheral face of the 2nd displacer 36.
In the example shown in Figure 4, refrigerant gas stream 48 is configured to run through the cap 32b of the low-temperature end being positioned at the 1st displacer 32.Refrigerant gas stream 56 is configured to run through the cap 52b of the low-temperature end being positioned at the 2nd displacer 36.In the same manner as the refrigerant gas stream 16 shown in Fig. 1, refrigerant gas stream 48 and refrigerant gas stream 56 are arranged to tilt relative to the long side direction of the 1st displacer 32 and the 2nd displacer 36.Thus, in the 1st expansion space 47, the eddy current of refrigerant gas is produced by the refrigerant gas of refrigerant gas stream 48.Similarly, in the 2nd expansion space 51, the eddy current of refrigerant gas is produced by the refrigerant gas of refrigerant gas stream 56.
As a result, the heat exchange efficiency between refrigerant gas in the 1st expansion space 47 and the 1st cooling bench 49 and the refrigerant gas in the 2nd expansion space 51 and the heat exchange efficiency between the 2nd cooling bench 54 can be improved.Further, shuttling back and forth between the 1st cylinder body 37 and the 1st displacer 32 can also be reduced to lose and shuttling back and forth between the 2nd cylinder body 38 and the 2nd displacer 36 is lost.
Fig. 5 (a)-Fig. 5 (b) is the schematic diagram of another structure of the 2 grades of formula ultra-low temperature refrigerating devices 31 represented involved by embodiments of the present invention.The difference of the example shown in the example shown in Fig. 5 (a)-Fig. 5 (b) and Fig. 4 is, the shape running through the refrigerant gas stream 56 of the cap 52b of the low-temperature end being positioned at the 2nd displacer 36 is different, and other parts are common.Therefore, suitably omit or simplify common ground and be described.
The shape of the refrigerant gas stream 56 in the example shown in Fig. 5 (a) is identical with the shape of the refrigerant gas stream 16 shown in Fig. 2 (a).Further, the shape of the refrigerant gas stream 56 in Fig. 5 (b) is identical with the shape of the refrigerant gas stream 16 shown in Fig. 2 (b).Therefore, its action effect is also identical, can improve the heat exchange efficiency between refrigerant gas in the 2nd expansion space 51 and the 2nd cooling bench 54.Further, shuttling back and forth between the 1st cylinder body 37 and the 1st displacer 32 can also be reduced to lose and shuttling back and forth between the 2nd cylinder body 38 and the 2nd displacer 36 is lost.
As described above, the ultra-low temperature refrigerating device 1 involved by embodiment and ultra-low temperature refrigerating device 31 can reduce loss of shuttling back and forth, and can improve the heat exchange efficiency between refrigerant gas and heat exchanger.
Above, describe the present invention according to embodiment, but embodiment only illustrates principle of the present invention, application.Further, for embodiment, do not depart from the scope of the inventive concept specified in claim can have various deformation example or configuration change.
Such as, in above-mentioned ultra-low temperature refrigerating device, show the situation that progression is 1 grade and 2 grades, but this progression suitably can be chosen to be 3 grades etc.Further, in embodiments, the example that ultra-low temperature refrigerating device is GM refrigeration machine is illustrated, but is not limited to this.Such as, the present invention also can be applicable to any refrigeration machine that sterlin refrigerator, Suhl prestige refrigeration machine etc. possess displacer.
In Fig. 4 and Fig. 5 (a)-Fig. 5 (b), for refrigerant gas stream 48, the shape of refrigerant gas stream 48 of the cap 32b running through the low-temperature end being positioned at the 1st displacer 32 is illustrated with the identical situation of the shape of the refrigerant gas stream 16 shown in Fig. 1.But, the shape of the refrigerant gas stream 48 in 2 grades of formula ultra-low temperature refrigerating devices 31 is not limited to this, such as can be the shape shown in Fig. 2 (a)-Fig. 2 (b) or Fig. 3 (a)-Fig. 3 (b), the action effect based on this is also identical with the situation shown in Fig. 2 (a)-Fig. 2 (b) or Fig. 3 (a)-Fig. 3 (b).
Above, the interior surface 19 in the lid of the low temperature side of displacer 2 is arranged to one end i.e. the 1st opening portion 17 of refrigerant gas stream 16 and the situation that the other end i.e. the 2nd opening portion 18 is arranged at outer surface 20 is illustrated.At this, in refrigerant gas stream 16, as long as be arranged to the tilting towards the long side direction relative to displacer 2 of refrigerant gas of flowing out from the 2nd opening portion 18, be not limited to the 1st opening portion 17 and the 2nd opening portion 18 and be arranged on situation on the lid of the low temperature side of displacer 2.
Fig. 6 represents the ultra-low temperature refrigerating device 1 involved by a variation of embodiments of the present invention and the schematic diagram of displacer 2.As shown in Figure 6, in the ultra-low temperature refrigerating device 1 involved by variation, two ends i.e. the 1st opening portion 17 of refrigerant gas stream 16 and the 2nd opening portion 18 are arranged at the main part 2a of displacer 2.At this, on the long side direction of displacer 2, the 1st opening portion 17 is different with the 2nd opening portion 18, and refrigerant gas stream 16 is oblique below in figure.
2nd opening portion 18 is positioned at clearance C, is flowed out after the 1st opening portion 17 flows into by the gas of refrigerant gas stream 16 from the 2nd opening portion 18 towards the side of cylinder body 4.Thus, the side collision of the refrigerant gas and the cylinder body 4 that flow out from the 2nd opening portion 18 and change moving direction, the flowing of the refrigerant gas therefore in expansion space 3 becomes complexity.Therefore, in expansion space 3, more easily produce the eddy current of refrigerant gas, thus the heat exchange efficiency between refrigerant gas and cooling bench 5 can be improved.Further, loss of shuttling back and forth can also be reduced.
Above, as shown in Figure 1, the interior surface 19 in the lid of the low temperature side of displacer 2 is arranged to one end i.e. the 1st opening portion 17 of refrigerant gas stream 16 and the situation that the other end i.e. the 2nd opening portion 18 is arranged at outer surface 20 is illustrated.On this basis, such as, the refrigerant gas stream being provided with stream two ends at the main part 2a of displacer 2 as shown in Figure 6 can also be possessed.Now, can be set to so-called " lateral spray type stream ", that is, make the refrigerant gas stream being arranged at main part 2a orthogonal with the axis of displacer 2.
In addition, the ultra-low temperature refrigerating device 1 involved by above-mentioned variation shows the situation that progression is 1 grade, but also goes for more than 2 grades.In at different levels, be arranged to side refrigerant gas stream 16 being arranged at cylinder body, and from the tilting towards the long side direction relative to displacer 2 of refrigerant gas that the 2nd opening portion 18 is flowed out.In addition, also can be set to the interior surface 19 the 1st opening portion 17 being arranged at lid, and the 2nd opening portion 18 is arranged at the side of cylinder body.
Claims (5)
1. a ultra-low temperature refrigerating device, is characterized in that, possesses:
Displacer;
Cap, is arranged on the low-temperature end of described displacer; And
Cylinder body, holds into described displacer and moves back and forth freely along long side direction, and form the expansion space of refrigerant gas between described cap,
The refrigerant gas stream be communicated with described expansion space by described displacer is formed in described cap,
The outflow direction that described refrigerant gas stream is arranged to the refrigerant gas flowed out in described expansion space tilts relative to the long side direction of described displacer.
2. ultra-low temperature refrigerating device according to claim 1, is characterized in that,
Described refrigerant gas stream is arranged to the refrigerant gas that flows out in the described expansion space side towards described cylinder body.
3. ultra-low temperature refrigerating device according to claim 1 and 2, is characterized in that,
Described cap possesses multiple refrigerant gas stream.
4. ultra-low temperature refrigerating device according to claim 3, is characterized in that,
The direction of being flowed out in described expansion space by the refrigerant gas of a stream in described multiple refrigerant gas stream is different from the direction that the refrigerant gas by other streams flows out in described expansion space.
5. the ultra-low temperature refrigerating device according to claim 3 or 4, is characterized in that,
Described multiple refrigerant gas stream is arranged to the central shaft Rotational Symmetry of the long side direction relative to described displacer.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013261441A JP2015117885A (en) | 2013-12-18 | 2013-12-18 | Cryogenic refrigerating machine |
| JP2013-261441 | 2013-12-18 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN104729137A true CN104729137A (en) | 2015-06-24 |
Family
ID=53367972
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410733757.1A Pending CN104729137A (en) | 2013-12-18 | 2014-12-04 | Cryogenic refrigerator |
Country Status (3)
| Country | Link |
|---|---|
| US (1) | US20150168028A1 (en) |
| JP (1) | JP2015117885A (en) |
| CN (1) | CN104729137A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107449172A (en) * | 2016-05-31 | 2017-12-08 | 住友重机械工业株式会社 | Ultra-low temperature refrigerating device |
| CN111936802A (en) * | 2018-04-06 | 2020-11-13 | 住友(Shi)美国低温研究有限公司 | Heat station for cooling circulating refrigerant |
| US11649989B2 (en) | 2018-04-06 | 2023-05-16 | Sumitomo (Shi) Cryogenics Of America, Inc. | Heat station for cooling a circulating cryogen |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP7277166B2 (en) * | 2019-02-19 | 2023-05-18 | 住友重機械工業株式会社 | Displacer assembly and cryogenic refrigerator |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010077447A (en) * | 2009-12-24 | 2010-04-08 | Toshiba Corp | Cold accumulating material and method for manufacturing the same |
| JP2011017457A (en) * | 2009-07-07 | 2011-01-27 | Toshiba Corp | Cold storage type refrigerator |
| CN102679608A (en) * | 2011-03-17 | 2012-09-19 | 住友重机械工业株式会社 | Cryogenic refrigerator |
| CN103017393A (en) * | 2011-09-21 | 2013-04-03 | 住友重机械工业株式会社 | Cryogenic refrigerator |
| CN103196254A (en) * | 2012-01-06 | 2013-07-10 | 住友重机械工业株式会社 | Cryogenic refrigerator and displacer |
| CN103363706A (en) * | 2012-04-04 | 2013-10-23 | 住友重机械工业株式会社 | Regenerative refrigerator |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0356860Y2 (en) * | 1985-12-19 | 1991-12-24 | ||
| US5398511A (en) * | 1992-03-30 | 1995-03-21 | Mitsubishi Denki Kabushiki Kaisha | Regenerative refrigerator |
| DE10229311A1 (en) * | 2002-06-29 | 2004-01-29 | Leybold Vakuum Gmbh | Refrigerator with regenerator |
| JP2004183919A (en) * | 2002-11-29 | 2004-07-02 | Sumitomo Heavy Ind Ltd | Cryogenic refrigerator |
| CN104990297B (en) * | 2011-09-26 | 2017-08-22 | 住友重机械工业株式会社 | Ultra-low temperature refrigerating device |
-
2013
- 2013-12-18 JP JP2013261441A patent/JP2015117885A/en active Pending
-
2014
- 2014-12-04 CN CN201410733757.1A patent/CN104729137A/en active Pending
- 2014-12-11 US US14/567,576 patent/US20150168028A1/en not_active Abandoned
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2011017457A (en) * | 2009-07-07 | 2011-01-27 | Toshiba Corp | Cold storage type refrigerator |
| JP2010077447A (en) * | 2009-12-24 | 2010-04-08 | Toshiba Corp | Cold accumulating material and method for manufacturing the same |
| CN102679608A (en) * | 2011-03-17 | 2012-09-19 | 住友重机械工业株式会社 | Cryogenic refrigerator |
| CN103017393A (en) * | 2011-09-21 | 2013-04-03 | 住友重机械工业株式会社 | Cryogenic refrigerator |
| CN103196254A (en) * | 2012-01-06 | 2013-07-10 | 住友重机械工业株式会社 | Cryogenic refrigerator and displacer |
| CN103363706A (en) * | 2012-04-04 | 2013-10-23 | 住友重机械工业株式会社 | Regenerative refrigerator |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107449172A (en) * | 2016-05-31 | 2017-12-08 | 住友重机械工业株式会社 | Ultra-low temperature refrigerating device |
| CN107449172B (en) * | 2016-05-31 | 2020-03-10 | 住友重机械工业株式会社 | Cryogenic refrigerator |
| CN111936802A (en) * | 2018-04-06 | 2020-11-13 | 住友(Shi)美国低温研究有限公司 | Heat station for cooling circulating refrigerant |
| US11649989B2 (en) | 2018-04-06 | 2023-05-16 | Sumitomo (Shi) Cryogenics Of America, Inc. | Heat station for cooling a circulating cryogen |
Also Published As
| Publication number | Publication date |
|---|---|
| US20150168028A1 (en) | 2015-06-18 |
| JP2015117885A (en) | 2015-06-25 |
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Application publication date: 20150624 |