CN204630137U - Ultra-low temperature refrigerating device - Google Patents
Ultra-low temperature refrigerating device Download PDFInfo
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- CN204630137U CN204630137U CN201520185786.9U CN201520185786U CN204630137U CN 204630137 U CN204630137 U CN 204630137U CN 201520185786 U CN201520185786 U CN 201520185786U CN 204630137 U CN204630137 U CN 204630137U
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Abstract
The utility model provides a kind of technology improving the efficiency of ultra-low temperature refrigerating device.Of the present utility model possess in the ultra-low temperature refrigerating device (100) of the 1st regenerator (18) and the 2nd regenerator (34), and the 2nd regenerator (34) possesses: container; Non magnetic cool storage material, is contained in the high temperature side region (32) of container; Magnetic cold-storage material, is contained in the low temperature side region (33) of container; And insertion parts (42), be contained in high temperature side region (32).At this, the thermal conductivity factor of insertion parts (42) at the temperature of ultra-low temperature refrigerating device (100) duration of work be 10 [W/ (mK)] below.Further, the sectional area of the insertion parts (42) in vertical with the axle of container plane be the sectional area of the container in this plane more than 1% and less than 25%.
Description
The application advocates the priority of No. 2014-083061st, the Japanese patent application based on application on April 14th, 2014.The full content of this Japanese publication is by reference to being applied in this description.
Technical field
The utility model relates to higher pressure refrigerant gas west that a kind of savings supplies from compression set and covers and expand and cold of producing, and the ultra-low temperature refrigerating device of cold of ultralow temperature desired by producing.
Background technology
As ultra-low temperature refrigerating device, such as, there is the refrigeration machine recorded in patent document 1.Displacer formula ultra-low temperature refrigerating device makes displacer move back and forth in cylinder interior, and makes the refrigerant gas in expansion space expand and produce cold.Further, pulse tube ultra-low temperature refrigerating device makes the gas piston in pulse tube move back and forth, and makes the refrigerant gas in expansion space expand and produce cold.Refrigerant gas expansion space produce cold put aside by regenerator while be passed to cooling bench and reach desired ultralow temperature, thus cool the cooling object be connected with cooling bench.
Patent document: Japanese Unexamined Patent Publication 2013-2217517 publication
Summary of the invention
The purpose of this utility model is to provide a kind of technology improving the efficiency of ultra-low temperature refrigerating device.
In order to solve above-mentioned problem, a kind of embodiment of the present utility model is a kind of ultra-low temperature refrigerating device possessing regenerator.This regenerator possesses: container; Non magnetic cool storage material, is contained in the 1st region of the high temperature side of container; Magnetic cold-storage material, is contained in the 2nd region of the low temperature side of container; And insertion parts, be contained in the 1st region.The thermal conductivity factor of insertion parts at the temperature of ultra-low temperature refrigerating device duration of work be 10 [W/ (mK)] below.
Another kind of embodiment of the present utility model is also a kind of ultra-low temperature refrigerating device.This ultra-low temperature refrigerating device possesses high temperature side regenerator and low temperature side regenerator.Low temperature side regenerator possesses: container; Non magnetic cool storage material, is contained in the 1st region of the high temperature side of container; And magnetic cold-storage material, be contained in the 2nd region of the low temperature side of container.Sectional area in the plane vertical with the axle of container in the region at least partially in the 1st region of container is less than the sectional area in the plane vertical with the axle of container in the 2nd region of container, the thermal conductivity factor of container at the temperature of ultra-low temperature refrigerating device duration of work be 10 [W/ (mK)] below.
According to ultra-low temperature refrigerating device of the present utility model, cool storage material can be reduced while maintenance refrigeration performance, thus the efficiency of refrigeration machine can be improved.
Accompanying drawing explanation
Fig. 1 is the integrally-built figure of the ultra-low temperature refrigerating device schematically represented involved by embodiment.
Fig. 2 is the figure of the internal structure schematically representing the expander that the ultra-low temperature refrigerating device involved by embodiment possesses.
Fig. 3 represents the helium of 2.2MPa and the helium density with temperature separately of 0.8MPa changes and both temperature variant figure of density contrast.
Fig. 4 is the figure of an example of the Temperature Distribution of the 2nd regenerator represented involved by embodiment.
Fig. 5 (a) and Fig. 5 (b) be represent the size of insertion parts and the temperature of the 1st cooling bench and the 2nd cooling bench temperature between the figure of relation.
Fig. 6 represents the temperature variant figure of cooling bench when being inserted with copper parts in the high temperature side region of the 2nd regenerator in the mode of the rectifier thermo-contact with upper end.
Fig. 7 is the figure of the thermal conductivity factor [W/ (mK)] of copper, stainless steel and the fluorocarbon resin represented under 40K.
Fig. 8 is the figure of the internal structure schematically representing the expander that the ultra-low temperature refrigerating device involved by variation of embodiment possesses.
In figure: 1-compressor, C1-the 1st gap, C2-the 2nd gap, 7-pipe arrangement, 7a-low-pressure fitting pipe, 7b-height press fit pipe, 8-feed cable, 9-cooling water pipe connecting portion, 10-expander, 11-the 1st cylinder body, 12-the 2nd cylinder body, 13-the 1st displacer, 14-the 2nd displacer, 15-sells, 16-connector, 17-sells, 18-the 1st regenerator, 19, 20-rectifier, 21-Room, 22-the 1st opening, 23-supply valve, 24-return valve, 25-seal, 26-the 1st expansion space, 27-the 2nd opening, 28-the 1st cooling bench, 29, 30-rectifier, 31-separator, 32-high temperature side region, 33-low temperature side region, 34-the 2nd regenerator, 35-the 2nd expansion space, 36-the 3rd opening, 37-the 2nd cooling bench, 38, 39-cap, 40, 41-pressure pin, 42-insertion parts, 100-ultra-low temperature refrigerating device.
Detailed description of the invention
Ultra-low temperature refrigerating device possesses compressor and expander usually.As the refrigerant gas of ultra-low temperature refrigerating device, such as, use helium.The helium of compressor compresses low pressure (such as 0.8MPa), generates the helium of high pressure (such as 2.2MPa).Near ultralow temperature, the temperature dependency of the density contrast of the density of high-pressure helium and the density of low pressure helium is comparatively large, and especially when temperature is at about 8K, its density contrast becomes maximum.Therefore, in the regenerator that ultra-low temperature refrigerating device involved by embodiment possesses, in order to the density contrast in fact reducing the helium in regenerator becomes the volume in maximum region, the region becoming about 8K in the duration of work temperature of Cryo Refrigerator holds insertion parts.Further, in order to the heat of the regenerator or expansion space that suppress higher level passes over, the thermal conductivity factor of this insertion parts be set at the temperature of ultra-low temperature refrigerating device duration of work be 10 [W/ (mK)] below.
Below, with reference to accompanying drawing, embodiment of the present utility model is described.
First, the overall structure of the ultra-low temperature refrigerating device of embodiment is described.Fig. 1 is the integrally-built figure of the ultra-low temperature refrigerating device 100 schematically represented involved by embodiment.As shown in Figure 1, ultra-low temperature refrigerating device 100 possesses: compressor 1, expander 10, pipe arrangement 7, feed cable 8 and cooling water pipe connecting portion 9.
Compressor 1 compresses the low pressure refrigerant gas refluxed from expander 10, and is supplied to expander 10 by by the higher pressure refrigerant gas compressed.Expander 10 makes the higher pressure refrigerant gas supplied from compressor 1 expand and produce cold.The detailed content of expander 10 will be carried out aftermentioned.
Pipe arrangement 7 is connected with expander 10 and compressor 1, and refrigerant gas is circulated between expander 10 and compressor 1.Pipe arrangement 7 comprises low-pressure fitting pipe 7a and high press fit pipe 7b.The low pressure refrigerant gas from expander 10 towards compressor 1 is flow through in low-pressure fitting pipe 7a.On the other hand, the higher pressure refrigerant gas from compressor 1 towards expander 10 is flow through in high press fit pipe 7b.
Feed cable 8 is connected with compressor 1 and expander 10.Feed cable 8 is for becoming the electric power of the power of expander 10 from compressor 1 supply.Cooling water pipe connecting portion 9 connects the pipe arrangement (not shown) that Cooling Water flows through.Cooling water is used for cooling compressor 1 pair of refrigerant gas and compresses and the heat of compression that produces, and to the external heat rejection of compressor 1.
Fig. 2 is the figure of the internal structure schematically representing the expander 10 that the ultra-low temperature refrigerating device 100 involved by embodiment possesses.In embodiment, exemplify out Ji Fude-McMahon (Gifford-McMahon as ultra-low temperature refrigerating device 100; GM) refrigeration machine, and its expander 10 is illustrated.As shown in Figure 2, the ultra-low temperature refrigerating device 100 involved by embodiment possesses 2 grades of formula expanders 10.Therefore, this expander 10 possesses the 1st cylinder body 11 and these two cylinder bodies of the 2nd cylinder body 12.
1st cylinder body 11 and the 2nd cylinder body 12 form as one, and possess temperature end and low-temperature end respectively.The low-temperature end of the 1st cylinder body 11 is connected in the bottom of the 1st cylinder body 11 with the temperature end of the 2nd cylinder body 12.2nd cylinder body 12 is formed as along the axially extended form identical with the 1st cylinder body 11, is the cylinder part that diameter is less than the 1st cylinder body 11.1st cylinder body 11 is the container holding the 1st displacer 13 in the mode that can move back and forth along its length, and the 2nd cylinder body 12 is the container holding the 2nd displacer 14 in the mode that can move back and forth along its length.1st displacer 13 is such as connected via pin 15, connector 16 and pin 17 with the 2nd displacer 14.
The scotch yoke mechanism (not shown) that the 1st displacer 13 and the 2nd displacer 14 are moved back and forth is provided with in the temperature end of the 1st cylinder body 11.Consider intensity, thermal conductivity factor, helium isolating power etc., the 1st cylinder body 11, the 2nd cylinder body 12 such as use stainless steel.
Further, from viewpoints such as proportion, intensity, thermal conductivity factors, the 1st displacer 13 such as uses folder cloth phenolic resins etc.2nd displacer 14 is by metal cylinders such as stainless steels.The outer peripheral face of the 2nd displacer 14 can be formed polyfurolresin uniform wearability resin protection film.
1st displacer 13 has cylindric outer peripheral face, is filled with the 1st cool storage material be made up of woven wire etc. in the inside of the 1st displacer 13.The internal capacity of the 1st displacer 13 plays a role as the 1st regenerator 18.The top of the 1st regenerator 18 is provided with rectifier 19, is provided with rectifier 20 in bottom.Room 21 is the space formed by the temperature end of the 1st cylinder body 11 and the 1st displacer 13, and its volume changes along with the 1st moving back and forth of displacer 13.Being formed in the temperature end of the 1st displacer 13 makes refrigerant gas flow to the 1st opening 22 of the 1st displacer 13 from Room 21.
Be connected with in Room 21 and the exhaust that supplies in the interconnective pipe arrangement of suction and discharge system be made up of compressor 1, supply valve 23 and return valve 24 is shared pipe arrangement.Further, between the part and the 1st cylinder body 11 of the close temperature end of the 1st displacer 13, seal 25 is installed.
1st expansion space 26 is the space formed by the 1st cylinder body 11 and the 1st displacer 13, and its volume changes along with the 1st moving back and forth of displacer 13.Being formed in the low-temperature end of the 1st displacer 13 makes refrigerant gas import the 2nd opening 27 of the 1st expansion space 26 via the 1st clearance C 1.
The position corresponding with the 1st expansion space 26 in the periphery of the 1st cylinder body 11 is configured with and cools hot linked 1st cooling bench 28 of object.1st cooling bench 28 is cooled by the refrigerant gas by the 1st clearance C 1.1st expansion space 26 is communicated with by the access around connector 16 with the temperature end of the 2nd displacer 14.Refrigerant gas flows to the 2nd displacer 14 via this access from the 1st expansion space 26.
2nd displacer 14 has cylindric outer peripheral face, and the inside of the 2nd displacer 14 is divided into two-stage vertically by the rectifier 29 of upper end, the rectifier 30 of lower end and the separator 31 be positioned at up and down.In the internal capacity of the 2nd displacer 14 than separator 31 more by the high temperature side region 32 of high temperature (higher level) side in be filled with the 2nd cool storage material be such as made up of nonmagnetic substances such as plumbous or bismuths.The cool storage material different from high temperature side region 32 is filled with, such as, by HoCu in the low temperature side region 33 of low temperature (subordinate) side of separator 31
2deng the 3rd cool storage material that magnetic material is formed.Lead or bismuth, HoCu
2etc. being formed as spherical, multiple spherical formation is assembled and forms cool storage material.Separator 31 prevents the cool storage material in high temperature side region 32 from mixing with the cool storage material in low temperature side region 33.The internal capacity (i.e. high temperature side region 32 and low temperature side region 33) of the 2nd displacer 14 plays a role as the 2nd regenerator 34.
The insertion parts 42 not making refrigerant gas pass through is accommodated in high temperature side region 32.The detailed content of this insertion parts 42 will be carried out aftermentioned.
2nd expansion space 35 is the space formed by the 2nd cylinder body 12 and the 2nd displacer 14, and its volume changes along with the 2nd moving back and forth of displacer 14.The 3rd opening 36 is formed in the low-temperature end of the 2nd displacer 14.3rd opening 36 makes refrigerant gas flow to the 2nd expansion space 35 via the 2nd clearance C 2.2nd clearance C 2 is formed by the low-temperature end of the 2nd cylinder body 12 and the 2nd displacer 14.
Position corresponding with the 2nd expansion space 35 in the periphery of the 2nd cylinder body 12 is configured with and cools hot linked 2nd cooling bench 37 of object.2nd cooling bench 37 is cooled by the refrigerant gas by the 2nd clearance C 2.
1st displacer 13 and the 2nd displacer 14 possess cap 38 and cap 39 in low-temperature end respectively.From the joint viewpoint with the 1st displacer 13 and the 2nd displacer 14, cap 38 and cap 39 have the cylinder form of two-stage shape respectively.Cap 38 is fixed on the 1st displacer 13 by pressure pin 40.Equally, cap 39 is fixed on the 2nd displacer 14 by pressure pin 41.
Then, the action of the ultra-low temperature refrigerating device 100 involved by embodiment is described.
In a certain moment of refrigerant gas supply step, the 1st displacer 13 and the 2nd displacer 14 are positioned at the lower dead center of the 1st cylinder body 11 and the 2nd cylinder body 12.If meanwhile or in the moment of staggering a little open supply valve 23, then higher pressure refrigerant gas is supplied in the 1st cylinder body 11 from sharing pipe arrangement for exhaust via supply valve 23.Its result, higher pressure refrigerant gas flows into the 1st regenerator 18 of the 1st displacer 13 inside from the 1st opening 22 on the top being arranged in the 1st displacer 13.The higher pressure refrigerant gas flowing into the 1st regenerator 18 is supplied to the 1st expansion space 26 by while the 1st cool storage material cooling via the 2nd opening 27 and the 1st clearance C 1 that are positioned at the 1st displacer 13 bottom.
The higher pressure refrigerant gas being supplied to the 1st expansion space 26 flows into the 2nd regenerator 34 of the 2nd displacer 14 inside via the access around connector 16.The higher pressure refrigerant gas flowing into the 2nd regenerator 34 is supplied to the 2nd expansion space 35 by while the 2nd cool storage material cooling via the 3rd opening 36 and the 2nd gap that are positioned at the 2nd displacer 14 bottom.
So, the 1st expansion space 26 and the 2nd expansion space 35 are full of by higher pressure refrigerant gas, and supply valve 23 is closed.Now, the 1st displacer 13 and the 2nd displacer 14 are positioned at the top dead centre of the 1st cylinder body 11 and the 2nd cylinder body 12.If meanwhile or in the moment of staggering a little open return valve 24, then the refrigerant gas in the 1st expansion space 26, the 2nd expansion space 35 is depressurized and expands.Absorbed the heat of the 1st cooling bench 28 via the 1st clearance C 1 by the refrigerant gas that is expanded into the 1st expansion space 26 of low temperature.Equally, the refrigerant gas of the 2nd expansion space 35 absorbs the heat of the 2nd cooling bench 37 via the 2nd clearance C 2.
1st displacer 13 and the 2nd displacer 14 move towards lower dead center, the volume reducing of the 1st expansion space 26 and the 2nd expansion space 35.Refrigerant gas in 2nd expansion space 35 turns back to the 1st expansion space 26 via the 2nd clearance C 2, the 3rd opening 36, the 2nd regenerator 34 and access.And the refrigerant gas in the 1st expansion space 26 turns back to the suction side of compressor 1 via the 2nd opening 27, the 1st regenerator 18 and the 1st opening 22.Now, the 1st cool storage material and cooled dose of gas cooling of the 2nd cool storage material.Using this operation as 1 circulation, ultra-low temperature refrigerating device 100 cools the 1st cooling bench 28 and the 2nd cooling bench 37 by repeatedly carrying out this cool cycles.
As mentioned above, the cool cycles in ultra-low temperature refrigerating device 100 comprises refrigerant gas and repeatedly flows into and flow out the 2nd regenerator 34 and make the action of pressure oscillation.Below, to using helium to be described as the Temperature Distribution of helium existed in the 2nd regenerator 34 during refrigerant gas and mass change.
Fig. 3 represents the helium of 2.2MPa and the helium density with temperature separately of 0.8MPa changes and both temperature variant figure of density contrast.As shown in Figure 3, the density contrast of the helium of 2.2MPa and the helium of 0.8MPa becomes maximum when temperature is about 9K.When the temperature of helium is lower than 9K, the density contrast of the helium of 2.2MPa and the helium of 0.8MPa is relative to temperature monotonic increase, and when the temperature of helium is higher than 9K, density contrast is relative to temperature monotone decreasing.
At this, the quality of the helium existed in the 2nd regenerator 34 is set to M.Further, the quality of the unit interval of the helium of the temperature end (i.e. the rectifier 29 of upper end) of inflow the 2nd regenerator 34 is set to m
in, the quality of the unit interval of the helium flowed out by the rectifier 30 from lower end is set to m
out.If helium flow into the 2nd regenerator 34, then the mass M of the helium existed in the 2nd regenerator 34 can increase.On the other hand, if helium flows out from the 2nd regenerator 34, then the mass M of the helium existed in the 2nd regenerator 34 can reduce.Therefore, the quality m of the unit interval of the helium of the rectifier 29 of upper end is flowed into
inbecome the variable quantity dM/dt of the unit interval of the mass M of the helium existed in the 2nd regenerator 34 and the quality m of the unit interval of the helium flowed out from the rectifier 30 of lower end
outsum.Accordingly, following formula (1) is obtained.
m
in＝dM/dt+m
out(1)
As mentioned above, the 2nd regenerator 34 is the inside of the 2nd displacer 14, and the 2nd displacer 14 is such as formed with the 2nd cool storage material that lead gripper, bismuth etc. are spherical vertically such as felt and woven wire.Thereby, it is possible to be considered as constant by the volume of the 2nd regenerator 34, therefore its value is set to V.Further, if the averag density of the helium in the 2nd regenerator 34 is set to ρ, then the mass M of the refrigerant gas existed in the 2nd regenerator 34 represents by following formula (2).
M＝Vρ (2)
If formula (2) is substituted into formula (1), then can obtain following formula (3).
m
in＝Vdρ/dt+m
out(3)
Wherein, d ρ/dt represents the time diffusion of the density p of helium.
In formula (3), suppose that the density of the helium flowing into the 2nd regenerator 34 can not change along with the time (d ρ/dt=0), then become m
in=m
out.This illustrates and to flow out from the 2nd regenerator 34 and helium flows into the corresponding amount of the amount of the 2nd regenerator 34.That is, illustrate that the mass M of the helium existed in the 2nd regenerator 34 does not change.But, in systems in practice, if supply valve 23 is opened, then supply high-pressure helium via supply valve 23.Its result, also flows into high-pressure helium in the 2nd regenerator 34, and the low pressure helium being filled in the 2nd regenerator 34 is boosted, becomes high-pressure helium.
As shown in Figure 3, high-pressure helium and low pressure helium there are differences in its density.Therefore, if to flow into low pressure helium in the 2nd regenerator the 34,2nd regenerator 34 boosted and become high-pressure helium for high-pressure helium, then the right in formula (3) become on the occasion of.More specifically, the right in formula (3) becomes in Fig. 3 with the density contrast that solid line represents.Accordingly, following inequality (4) is obtained.
Vdρ/dt＝m
in-m
out＞0 (4)
As mentioned above, the high-pressure helium flowing into the 2nd regenerator 34 is cooled by the 2nd cool storage material, and is supplied to the 2nd expansion space 35 via the 3rd opening 36 and the 2nd gap being positioned at the 2nd displacer 14 bottom.But above-mentioned inequality (4) represents that the quality of the helium flowed out to the 2nd expansion space 35 from the 2nd regenerator 34 is less than the quality of the helium of inflow the 2nd regenerator.This means that the 2nd regenerator 34 plays the buffer effect of so-called helium.The helium flowed out to the 2nd expansion space 35 from the 2nd regenerator 34 reduces, and the pressure of its result the 2nd expansion space 35 also diminishes.
If return valve 24 is opened, then the high-pressure helium in the 2nd regenerator 34 is depressurized and becomes low pressure helium.Now, the right in formula (3) becomes the density contrast that represents using solid line in Fig. 3 negative value as absolute value.Therefore, following inequality (5) is obtained.
Vdρ/dt＝m
in-m
out＜0 (5)
This represents that the quality of the helium flowed out from the 2nd regenerator 34 is greater than the quality of the helium flowing into the 2nd regenerator 34 from the 2nd expansion space 35.This illustrates and to be depressurized and helium in the 2nd regenerator 34 that density diminishes flows out to the 1st expansion space 26 from the 2nd regenerator 34.
At this, the amount of the helium that compressor 1 reclaims is constant.Therefore, the yield of the helium expanded in the 2nd expansion space 35 reduces the corresponding amount of the amount that flows out from the 2nd regenerator 34 to the helium in the 2nd regenerator 34.Its result, is expanded in the 2nd expansion space 35 and is reduced by the helium of the 2nd clearance C 2, and therefore the cooling effectiveness of the 2nd cooling bench 37 reduces.
Fig. 4 is the figure of an example of the Temperature Distribution of the 2nd regenerator 34 represented involved by embodiment, and is represent the curve map by the Temperature Distribution of the 2nd regenerator 34 when being set to 1 from the temperature end of the 2nd regenerator 34 to the distance of low-temperature end.
As shown in Figure 4, in the 2nd regenerator 34 of 2 grades of formula refrigeration machines, become the shape be inversely proportional to the distance apart from temperature end towards the Temperature Distribution of low-temperature end from temperature end, in the shape as hyperbola.In Fig. 4, thermograde becomes the high temperature side region 32 that maximum phenomenon is present in the 2nd regenerator 34.The duration of work that high temperature side region 32 is included in ultra-low temperature refrigerating device 100 becomes the region of about 9K temperature.This temperature is consistent with the temperature when density contrast of helium is maximum in Fig. 3.
According to more than, the 2nd regenerator 34 involved by embodiment accommodate in the high temperature side region 32 of the 2nd regenerator 34 hinder helium circulation insertion parts 42.Insertion parts 42 is fixed to become coaxial mode with the 2nd regenerator 34 and is configured at separator 31.
If hold insertion parts 42 in the high temperature side region 32 of the 2nd regenerator 34, then the region that in the 2nd regenerator 34, helium can exist reduces the volume V with insertion parts 42
1suitable amount.Because helium cannot pass through insertion parts 42, therefore the volume V of the 2nd regenerator 34 is actually the volume V deducting insertion parts 42 from the volume V of the 2nd regenerator 34
1residual volume V
2(=V-V
1).Now, above-mentioned formula (3) becomes following formula (6).
m
in＝V
2dρ/dt+m
out(6)
Wherein, V
2< V (7).
Suppose the unit interval quality m of the helium flowing into the 2nd regenerator 34 from the 1st expansion space 26 via rectifier 29
inconstant, then according to formula (6) and formula (7), the quality m of the unit interval of the helium flowed out to the 2nd expansion space 35 from rectifier 30
outincrease.But, in fact, the quality m of the unit interval of the helium flowed into the 2nd regenerator 34 from the 1st expansion space 26
inreduce.If the quality of the unit interval of the helium flowed into from the 1st expansion space 26 to the 2nd regenerator 34 when accommodating insertion parts 42 in the high temperature side region 32 of the 2nd regenerator 34 is set to m '
in, then above-mentioned formula (6) becomes following formula (8).
m’
in＝V
2dρ/dt+m
out(8)
Wherein, m '
in< m
in(9).
Because the helium flowing into the 2nd regenerator 34 from the 1st expansion space 26 reduces, thus the helium of respective amount is stranded in the 1st expansion space 26.The helium being trapped in the 1st expansion space 26 expands and contributes to producing cold in the 1st expansion space 26.Therefore, it is possible to make the temperature of the 1st cooling bench 28 decline further.
By formula (8) and formula (9), if the left side m ' of formula (8)
inbe less than the left side m of formula (3)
in, then the right V of formula (8)
2d ρ/dt+m
outalso the right Vd ρ/dt+m of formula (3) is less than
out.On the other hand, according to formula (7) V
2< V, therefore the 1st, the right V of formula (8)
2d ρ/dt is less than the 1st, the right Vd ρ/dt of formula (3).Therefore, it is possible to suppress the 2nd, the right m of formula (8)
outreduce.
By more than, can be following 3 points by clear and definite summary of benefits when holding insertion parts 42 in the high temperature side region 32 of the 2nd regenerator 34.
1. the helium flowing into the 2nd regenerator 34 from the 1st expansion space 26 reduces the amount corresponding to the volume of insertion parts 42, and the helium expanded in the 1st expansion space 26 increases.The helium increased expands and produces cold in the 1st expansion space 26, and the temperature therefore contributing to the 1st cooling bench 28 declines.
2., at ultra-low temperature refrigerating device 100 duration of work, the density contrast that the temperature in the high temperature side region 32 of the 2nd regenerator 34 becomes high-pressure helium and low pressure helium becomes large temperature range.The above-mentioned volume playing the region of the effect of buffering helium reduces the amount corresponding to the volume of insertion parts 42, and thus between the 2nd regenerator 34 and the 2nd expansion space 35, the helium gas flow of movement increases.
3. the cool storage material being contained in the high temperature side region 32 of the 2nd regenerator 34 reduces the amount corresponding to the volume of insertion parts 42.
Above, clear and definite effect when holding insertion parts 42 in the high temperature side region 32 of the 2nd regenerator 34 is illustrated.Then, the concrete size of insertion parts 42 in the high temperature side region 32 being inserted into the 2nd regenerator 34 is described.
Fig. 5 (a) and Fig. 5 (b) be represent the size of insertion parts 42 and the temperature of the 1st cooling bench 28 and the 2nd cooling bench 37 temperature between the figure of relation.More specifically, Fig. 5 (a) is the curve map of the variations in temperature of each cooling bench when representing that insertion parts 42 is fluorocarbon resin, and Fig. 5 (b) is the curve map of the variations in temperature of each cooling bench when representing that insertion parts 42 is stainless steel.
As mentioned above, the 2nd regenerator 34 is the internal capacity of the 2nd displacer 14, cylindrical shape.Further, the shape of insertion parts 42 is such as cylindrical or square column type.Insertion parts 42 is configured at the high temperature side region 32 of the 2nd regenerator 34 in the mode coaxial with the 2nd regenerator 34, therefore with the constant cross section of the insertion parts 42 during the plane cutting vertical with the axle of the 2nd regenerator 34, and has nothing to do with the position on its axle.
Now, S is set to by with the sectional area of the 2nd regenerator 34 during the plane cutting vertical with the axle of the 2nd regenerator 34
1, the sectional area of the insertion parts 42 in this plane is set to S
2.Transverse axis in the curve map of Fig. 5 (a) and Fig. 5 (b) is the sectional area S of the 2nd regenerator 34
1with the sectional area S of insertion parts 42
2difference S
1-S
2relative to the sectional area S of the 2nd regenerator 34
1ratio.That is, the sectional area S of insertion parts 42
2become larger, the sectional area S of the 2nd regenerator 34
1with the sectional area S of insertion parts 42
2difference S
1-S
2become less.Below, sometimes by the sectional area S of the 2nd regenerator 34
1with the sectional area S of insertion parts 42
2difference S
1-S
2relative to the sectional area S of the 2nd regenerator 34
1ratio referred to as " ratio of sectional area ".Further, on the longitudinal axis of the curve map of Fig. 5 (a) and Fig. 5 (b), " 1 grade of temperature " represents the temperature of the 1st cooling bench 28, and " 2 grades of temperature " represents the temperature of the 2nd cooling bench 37.
As shown in Fig. 5 (a), when insertion parts 42 is not inserted in the high temperature side region 32 of the 2nd regenerator 34, when namely sectional area ratio is 1.0,1 grade of temperature is about 36.2K, and 2 grades of temperature are about 3.82K.As the sectional area S of insertion parts 42
2be the sectional area S of the 2nd regenerator 34
1about 5% time, when namely sectional area ratio is about 0.95,1 grade of temperature is about 34.6K, and 2 grades of temperature are about 3.83K.
The sectional area S of further increasing insertion parts 42
2, by the sectional area S of insertion parts 42
2be set to the sectional area S of the 2nd regenerator 34
1about 10% time, 1 grade of temperature is about 35.8K, and 2 grades of temperature are about 3.85K.If strengthen the sectional area S of insertion parts 42 further
2, then 1 grade of temperature and 2 grades of temperature together rise.The sectional area S of insertion parts 42
2be about the sectional area S of the 2nd regenerator 34
125% time, 1 grade of temperature and 2 grades of temperature all become the degree identical with when not inserting insertion parts 42.
As shown in Fig. 5 (b), insertion parts 42 is in stainless situation, as the sectional area S of insertion parts 42
2be about the sectional area S of the 2nd regenerator 34
15% time, while maintenance 2 grades of temperature, 1 grade of temperature becomes minimum.The sectional area S of insertion parts 42
2be about the sectional area S of the 2nd regenerator 34
125% time, 1 grade of temperature becomes the degree identical with when not inserting insertion parts 42.
So, if be contained in the sectional area S of the insertion parts 42 in the high temperature side region 32 of the 2nd regenerator 34
2be the sectional area S of the 2nd regenerator 34
1less than 25%, then can reduce the cool storage material being contained in high temperature side region 32 while maintenance 1 grade of temperature.Especially, when insertion parts 42 is fluorocarbon resin, as the sectional area S of insertion parts 42
2be the sectional area S of the 2nd regenerator 34
1less than 25% time, 1 grade of temperature and 2 grades of temperature are identical with when not inserting insertion parts 42 or below it.As the sectional area S of insertion parts 42
2be the sectional area S of the 2nd regenerator 34
15% time, 1 grade of temperature fall is maximum.Therefore, the sectional area S of preferred insertion parts 42
2be set to the sectional area S of the 2nd regenerator 34
1about 5%.
But, in the example shown in Fig. 2, be inserted into the insertion parts 42 in the high temperature side region 32 of the 2nd regenerator 34 and rectifier 29 thermo-contact of upper end.The temperature of the rectifier 29 of upper end is identical with the temperature of the 1st expansion space 26, as shown in Figure 4, is the temperature close to the maximum temperature in the Temperature Distribution of the 2nd regenerator 34.Therefore, when supposing insertion parts 42 such as transcalent materials of appearance such as copper, the internal temperature of the 2nd regenerator 34 can rise.Now, the rising of 1 grade of temperature and 2 grades of temperature is likely caused.
Fig. 6 represents the temperature variant figure of cooling bench when being inserted with copper parts in the mode of rectifier 29 thermo-contact with upper end in the high temperature side region 32 of the 2nd regenerator 34.As shown in Figure 6, when being inserted with the copper parts of diameter 2mm, 1 grade of temperature and 2 grades of temperature together rise.Wherein, the sectional area of the copper parts of diameter 2mm is less than the sectional area S of the 2nd regenerator 34
11%.
Fig. 7 is the figure of the thermal conductivity factor [W/ (mK)] of copper, stainless steel and the fluorocarbon resin represented under 40K.As shown in Figure 4, at ultra-low temperature refrigerating device 100 duration of work, the temperature of the rectifier 29 of upper end is about 40K.Therefore, Fig. 7 represents ultra-low temperature refrigerating device 100 duration of work, the thermal conductivity factor of each parts when inserting copper, stainless steel and fluorocarbon resin in the high temperature side region 32 of the 2nd regenerator 34.As shown in Figure 7, the thermal conductivity factor of the copper under 40K is 1850 [W/ (mK)].Compared with this and the stainless thermal conductivity factor under 40K i.e. 5 [W/ (mK)], many 3 of its figure place, and compared with thermal conductivity factor i.e. 0.2 [W/ (mK)] of fluorocarbon resin, many 4 of figure place.
Clear and definite advantage when holding insertion parts 42 in the high temperature side region 32 of above-mentioned 2nd regenerator 34 and the material category of insertion parts 42 have nothing to do.But when the thermal conductivity factor of insertion parts 42 is larger, the heat being passed to the rectifier 29 of the upper end of the 2nd regenerator 34 inside can offset above-mentioned advantage.Its result, 1 grade of temperature and 2 grades of temperature rise on the contrary.This is because the thermal conductivity factor of copper under 40K and the thermal conductivity factor of stainless steel or fluorocarbon resin differ greatly, even if the sectional area being therefore inserted into the copper parts in the high temperature side region 32 of the 2nd regenerator 34 is less than the sectional area S of the 2nd regenerator 34
11%, 1 grade of temperature and 2 grades of temperature also can be caused to rise.
By more than, the thermal conductivity factor of insertion parts 42 is preferably degree identical with the thermal conductivity factor of stainless steel or fluorocarbon resin at the temperature of ultra-low temperature refrigerating device 100 duration of work, is specially 10 [W/ (mK)] below.If the thermal conductivity factor of insertion parts 42 is the degree identical with the thermal conductivity factor of stainless steel or fluorocarbon resin, then by holding insertion parts 42 in the high temperature side region 32 of the 2nd regenerator 34, above-mentioned effect can be obtained.Therefore, the sectional area S of such as insertion parts 42
2be the sectional area S of the 2nd regenerator 34
1more than 1% and less than 25%, be more preferably more than 1% and less than 15%, more preferably more than 1% and less than 10%.
As described above, the ultra-low temperature refrigerating device 100 involved by embodiment of the present utility model, can improve the efficiency of ultra-low temperature refrigerating device 100.
Especially, the helium flowing into the 2nd regenerator 34 from the 1st expansion space 26 reduces the amount corresponding to the volume of the insertion parts 42 in the high temperature side region 32 being inserted into the 2nd regenerator 34.Therefore, the helium expanded in the 1st expansion space 26 increases.Its result, can produce more cold, thus the temperature of the 1st cooling bench 28 is declined in the 1st expansion space 26.Further, the helium that the density contrast being present in helium becomes at large temperature reduces the amount corresponding to the volume of the insertion parts 42 in the high temperature side region 32 being inserted into the 2nd regenerator 34.Its result, can be increased in the helium gas flow of movement between the 2nd regenerator 34 and the 2nd expansion space 35.And, the cool storage material being contained in the high temperature side region 32 of the 2nd regenerator 34 can be reduced the amount corresponding to the volume of the insertion parts 42 in the high temperature side region 32 being inserted into the 2nd regenerator 34.Its result, can reduce the manufacturing cost of ultra-low temperature refrigerating device 100.
Above, preferred embodiment of the present utility model has been described in detail, but the utility model is not limited to above-described embodiment, can is not departing within the scope of the utility model, to above-described embodiment various distortion and displacement in addition.
In above-mentioned, the high temperature side region 32 at the 2nd regenerator 34 is inserted to the insertion parts 42 be made up of the parts that thermal conductivity factor is less, thus the situation reducing the actual volume in the high temperature side region 32 of the 2nd regenerator 34 is illustrated.But the method reducing the volume in the high temperature side region 32 of the 2nd regenerator 34 is not limited to the method inserting insertion parts 42.The method can be replaced or the volume of the part corresponding with high temperature side region 32 of the 2nd displacer 14 can also be reduced on this basis.
Fig. 8 is the figure of the internal structure schematically representing the expander 10 that the ultra-low temperature refrigerating device 100 involved by variation of embodiment possesses.In Fig. 8, identical symbol is marked for the parts identical with the ultra-low temperature refrigerating device 100 involved by above-mentioned embodiment.Below, in the ultra-low temperature refrigerating device 100 involved by variation, for the part repeated with the ultra-low temperature refrigerating device 100 involved by embodiment, suitably omit or simplify its explanation.
As shown in Figure 8, in the ultra-low temperature refrigerating device 100 involved by variation, do not accommodate insertion parts 42 in the high temperature side region 32 of the 2nd regenerator 34.In the 2nd displacer 14 involved by variation, compared with the 2nd displacer 14 involved by the embodiment shown in Fig. 2, the part corresponding with high temperature side region 32 is the container that wall is thicker.Therefore, compared with the sectional area in low temperature side region 33, the sectional area in the high temperature side region 32 of the 2nd regenerator 34 involved by variation diminishes.Wherein, " sectional area in high temperature side region 32 " is with the sectional area in the high temperature side region 32 during the plane cutting vertical with the axle of the 2nd regenerator 34." sectional area in low temperature side region 33 " is also identical.
More specifically, the sectional area in preferred high temperature side region 32 is set to 75% ~ 99% of the sectional area in low temperature side region 33.And as mentioned above, the peripheral part of the 2nd displacer 14 is the metal cylinders such as stainless steel.Therefore, under namely the temperature of ultra-low temperature refrigerating device 100 duration of work is about 40K, the thermal conductivity factor of the wall portion in high temperature side region 32 be 10 [W/ (mK)] below.
Ultra-low temperature refrigerating device 100 involved by the variation of said structure, due to the smaller volume in the high temperature side region 32 of the 2nd regenerator 34, the helium therefore flowing into the 2nd regenerator 34 from the 1st expansion space 26 reduces.Thus, the helium expanded in the 1st expansion space 26 increases.Its result, can produce more cold, thus the temperature of the 1st cooling bench 28 is declined in the 1st expansion space 26.Further, because the volume in the high temperature side region 32 of the 2nd regenerator 34 reduces, the helium that the density contrast being therefore present in helium becomes at large temperature reduces.Its result, can be increased in the helium gas flow of movement between the 2nd regenerator 34 and the 2nd expansion space 35.And, because the volume in the high temperature side region 32 of the 2nd regenerator 34 reduces, therefore, it is possible to reduce the cool storage material being contained in the high temperature side region 32 of the 2nd regenerator 34.
In addition, the sectional area that Fig. 8 shows all parts in high temperature side region 32 is less than the situation of the sectional area in low temperature side region 33.The sectional area of all parts in high temperature side region 32 also can be not less than the sectional area in low temperature side region 33, as long as the sectional area in the region at least partially in high temperature side region 32 is less than the sectional area in low temperature side region 33.
Further, Fig. 8 shows the situation of the constant cross section of all parts in high temperature side region 32, but this sectional area not must be constant.Such as, sectional area also can increase from the upper end side in high temperature side region 32 (high temperature side) to lower end side (low temperature side) continuously.
In above-mentioned, the situation that the progression of ultra-low temperature refrigerating device 100 is secondary is illustrated, but this progression can suitably be chosen as more than three grades.Further, in embodiment, the example that ultra-low temperature refrigerating device is displacer formula GM refrigeration machine is illustrated, but is not limited to this.Such as, the utility model can also be applicable to pulse tube refrigerating machine, sterlin refrigerator, Suhl prestige refrigeration machine etc.
In above-mentioned, be that situation that is cylindrical or square column type is illustrated to the shape of insertion parts 42.The shape of insertion parts 42 is not limited to cylindrical or square column type, such as, also can be conical or pyramid.
In above-mentioned, the situation of rectifier 29 thermo-contact of insertion parts 42 and upper end is illustrated, but insertion parts 42 also can not with rectifier 29 thermo-contact.Now, the heat of rectifier 29 can be suppressed further to enter the inside of the 2nd regenerator 34 via insertion parts 42.
Claims (8)
1. a ultra-low temperature refrigerating device, possesses regenerator, it is characterized in that,
Described regenerator possesses:
Container;
Non magnetic cool storage material, is contained in the 1st region of the high temperature side of described container;
Magnetic cold-storage material, is contained in the 2nd region of the low temperature side of described container; And
Insertion parts, is contained in described 1st region,
The thermal conductivity factor of described insertion parts at the temperature of described ultra-low temperature refrigerating device duration of work be 10 [W/ (mK)] below.
2. ultra-low temperature refrigerating device according to claim 1, is characterized in that,
The sectional area of the described insertion parts in the plane vertical with the axle of described container be the sectional area of the described container in described plane more than 1% and less than 25%.
3. ultra-low temperature refrigerating device according to claim 1, is characterized in that,
Described container also possesses the separator separating described non magnetic cool storage material and described magnetic cold-storage material,
Described insertion parts is fixed on described separator.
4. ultra-low temperature refrigerating device according to claim 2, is characterized in that,
Described container also possesses the separator separating described non magnetic cool storage material and described magnetic cold-storage material,
Described insertion parts is fixed on described separator.
5. ultra-low temperature refrigerating device according to any one of claim 1 to 4, is characterized in that,
Described container configures with coaxial manner and holds described insertion parts.
6. ultra-low temperature refrigerating device according to any one of claim 1 to 4, is characterized in that,
Described insertion parts is formed from a resin.
7. ultra-low temperature refrigerating device according to claim 5, is characterized in that,
Described insertion parts is formed from a resin.
8. a ultra-low temperature refrigerating device, possesses high temperature side regenerator and low temperature side regenerator, it is characterized in that,
Described low temperature side regenerator possesses:
Container;
Non magnetic cool storage material, is contained in the 1st region of the high temperature side of described container; And
Magnetic cold-storage material, is contained in the 2nd region of the low temperature side of described container,
Sectional area in the plane vertical with the axle of described container in the region at least partially in described 1st region of described container is less than the sectional area in the plane vertical with the axle of described container in described 2nd region of described container,
The thermal conductivity factor of described container at the temperature of described ultra-low temperature refrigerating device duration of work be 10 [W/ (mK)] below.
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| JP2014083061A JP6320142B2 (en) | 2014-04-14 | 2014-04-14 | Cryogenic refrigerator |
| JP2014-083061 | 2014-04-14 |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105627610A (en) * | 2016-03-15 | 2016-06-01 | 北京美尔斯通科技发展股份有限公司 | High-temperature superconductor refrigerating equipment based on fixed nitrogen |
| CN108954891A (en) * | 2018-08-27 | 2018-12-07 | 浙江大学 | Stirling based on eddy-current damping phase modulation/vascular composite refrigerator |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0240452Y2 (en) * | 1985-03-26 | 1990-10-29 | ||
| JP2980461B2 (en) * | 1992-09-18 | 1999-11-22 | 株式会社東芝 | Cryogenic refrigerator |
| JP3751646B2 (en) * | 1993-09-17 | 2006-03-01 | 株式会社東芝 | Cold storage material and refrigerator using the same |
| JP2659684B2 (en) * | 1994-05-31 | 1997-09-30 | 住友重機械工業株式会社 | Regenerator refrigerator |
| US6256997B1 (en) * | 2000-02-15 | 2001-07-10 | Intermagnetics General Corporation | Reduced vibration cooling device having pneumatically-driven GM type displacer |
| JP2004278877A (en) * | 2003-03-14 | 2004-10-07 | Sumitomo Heavy Ind Ltd | Cold storage unit for refrigerating machine |
| JP4323400B2 (en) * | 2004-09-24 | 2009-09-02 | アイシン精機株式会社 | Regenerator and regenerator type refrigerator |
| JP2008096040A (en) * | 2006-10-13 | 2008-04-24 | Iwatani Industrial Gases Corp | Cold storage for cryogenic refrigerating machine |
| US8978400B2 (en) * | 2009-11-09 | 2015-03-17 | Sumitomo (Shi) Cryogenics Of America Inc. | Air cooled helium compressor |
| CN102812311B (en) * | 2010-03-19 | 2015-05-20 | 住友重机械工业株式会社 | Cold storage apparatus, gifford-mcmahon cooler, and pulse tube refrigerator |
| JP5790989B2 (en) * | 2011-05-10 | 2015-10-07 | 独立行政法人国立高等専門学校機構 | Regenerator |
| JP5882110B2 (en) * | 2012-04-04 | 2016-03-09 | 住友重機械工業株式会社 | Regenerator type refrigerator, regenerator |
-
2014
- 2014-04-14 JP JP2014083061A patent/JP6320142B2/en active Active
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105627610A (en) * | 2016-03-15 | 2016-06-01 | 北京美尔斯通科技发展股份有限公司 | High-temperature superconductor refrigerating equipment based on fixed nitrogen |
| CN105627610B (en) * | 2016-03-15 | 2018-02-06 | 北京美尔斯通科技发展股份有限公司 | A kind of high-temperature superconductor refrigeration plant based on fixed nitrogen |
| CN108954891A (en) * | 2018-08-27 | 2018-12-07 | 浙江大学 | Stirling based on eddy-current damping phase modulation/vascular composite refrigerator |
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|---|---|
| JP6320142B2 (en) | 2018-05-09 |
| JP2015203530A (en) | 2015-11-16 |
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