CN208205604U - Use the cascade back-heating type natural gas liquefaction system of pulse type sterlin refrigerator - Google Patents
Use the cascade back-heating type natural gas liquefaction system of pulse type sterlin refrigerator Download PDFInfo
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- CN208205604U CN208205604U CN201820685644.2U CN201820685644U CN208205604U CN 208205604 U CN208205604 U CN 208205604U CN 201820685644 U CN201820685644 U CN 201820685644U CN 208205604 U CN208205604 U CN 208205604U
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Abstract
Cascade back-heating type natural gas liquefaction system according to the present utility model using pulse type sterlin refrigerator, including gas source, the first temperature reducing unit, the second temperature reducing unit and the LNG tank that are sequentially communicated by cooling liquefaction pipeline, wherein, first temperature reducing unit includes an at least high-temperature region pulse type sterlin refrigerator, and the second temperature reducing unit includes an at least middle warm area pulse type sterlin refrigerator.Because the utility model combines the new and effective pulse type sterlin refrigerator suitable for different operating warm area, the principle that refrigeration machine classification refrigeration is utilized cools down step by step, it is tentatively pre-chilled using high-temperature region pulse type sterlin refrigerator, deep cooling and supercooling are carried out using middle warm area pulse type sterlin refrigerator, the condensation liquefaction portion gas after the decompression of throttle valve isenthalpic throttling.So the cascade back-heating type natural gas liquefaction system of the utility model has the advantages of reduction system power dissipation, raising system effectiveness.
Description
Technical field
The utility model belongs to low-temperature gas liquefaction technical field, and in particular to a kind of combination pulse type sterlin refrigerator
Cascade back-heating type natural gas liquefaction system.
Background technique
Natural gas is the fastest-rising energy of 21 century consumption figure as clean energy resource, and the growth of natural gas consumption promotes
The rapid development of liquefied natural gas industry, nearly ten years, liquefied natural gas (LNG) exploitation in China are in great development period.LNG
All developed in each link of chain, wherein liquefaction technology is more complicated, and the professional face being related to is very wide, including natural gas is located in advance
Reason, pre-cooling, cryogenics and low-temperature (low temperature) vessel design and craft etc..It is total that the investment of natural gas liquefaction flow sheet equipment accounts for LNG factory
30% or so of investment, therefore, liquefaction flow path directly influences the economy of LNG factory construction and operation.It is natural in view of China
The characteristics of gas resource scattered distribution, Flow Sheet of Gas Liquefaction With Small Scale has very big advantage, can be applied to motor vehicle fuel and add
Note station, BOG liquefaction recycling, city gas peak shaving etc., compared with large and medium-sized liquefying plant, small liquid process small investment, equipment
Simple and compact, start and stop are convenient.Efficiently, the exploitation of economic small-scaled natural gas liquification device also helps outlying gas field, marine gas
The development and utilization of field gas source are conducive to push natural gas applications, improve energy resource structure, and application prospect is very wide.
With the continuous development of Refrigeration Technique, natural gas liquefaction process is more and more diversified, and the selection of liquefaction flow path is one
A vital technology, economic problems.The liquefaction flow path of natural gas mainly has tandem type circulation, mixed-refrigerant cycle
(MRC) and swell refrigeration recycles.Cascade refrigeration process flow is usually made of the independent refrigeration cycle of three-level, liquefaction flow path
Equipment is complex, and initial cost is higher and not easy to control and safeguards.The Main way of world's natural gas liquefaction process technical research,
First is that improving existing procedure technique and appliance arrangement efficiency, the power consumption of liquefaction process is reduced；Second is that research and development it is novel or
Follow-on natural gas liquefaction flow technologies.Novel pulse type sterlin refrigerator carries out swell refrigeration using pneumatics,
Warm area is wide, high-efficient.Wherein the pulse type sterlin refrigerator of three kinds of different structure forms can freeze at high, medium and low three kinds
Warm area realizes refrigeration and temperature control on a large scale, can be respectively intended to replace propane, ethylene, first in traditional Cascade
Alkane refrigeration cycle simplifies natural gas liquefaction process, realizes liquefaction flow path miniaturization.Exist in conjunction with pulse type sterlin refrigerator
Advantage on process simplification and miniaturization can also realize medium scale natural gas liquefaction using parallel system.In addition,
The utilization of cryogenic natural gas gas cold energy of not liquefying is also critical issue in liquefaction flow path, and reasonable utilization can not only reduce
Energy consumption improves system effectiveness, can also realize the compound action of liquefaction system.
Utility model content
One of the utility model aim is that the cascade back-heating type for providing novel combination pulse type sterlin refrigerator is natural
Gas liquefaction system.
The utility model provides a kind of cascade back-heating type natural gas liquefaction system using pulse type sterlin refrigerator,
It has the feature that, including gas source, the first temperature reducing unit, the second cooling list that are sequentially communicated by cooling liquefaction pipeline
Member and LNG tank, wherein the first temperature reducing unit includes an at least high-temperature region pulse type sterlin refrigerator, the
Two temperature reducing units include an at least middle warm area pulse type sterlin refrigerator, and high-temperature region pulse type sterlin refrigerator includes the
One compressor frame, the first compression piston, the first expansion piston, the first pulse tube, the first second level hot end heat exchanger, the first level-one
Hot end heat exchanger, the first compressor frame have piston tube, and piston tube has for accommodating the first compression piston and the first expansion
The cylinder-piston chamber of piston, the first pulse tube is connected to plunger shaft and plunger shaft is coaxially disposed, the setting of the first second level hot end heat exchanger
In the first pulse tube, the outside of piston tube, the first compression piston, the first expansion piston is arranged in the first level-one hot end heat exchanger
And plunger shaft constitutes the first compression chamber, it is swollen that the first expansion piston, second level hot end heat exchanger and the first pulse tube constitute first
Swollen chamber, the first expansion chamber and the first compression chamber are coaxially arranged, and the internal diameter of the first pulse tube is identical as plunger shaft internal diameter, perpendicular to work
Cavity axis is filled in, multiple through-holes for penetrating piston tube wall are provided in plunger shaft, first through hole is connected to plunger shaft and the first level-one
Hot end heat exchanger, middle warm area pulse type sterlin refrigerator include the second compressor frame, the second compression piston, the second expansion work
Plug, the second pulse tube, the second second level hot end heat exchanger, the second level-one hot end heat exchanger, the second compressor frame, which has, coaxially to be set
The cylindrical compression piston chamber and expansion piston chamber set and be connected to, the second compression piston, the second expansion piston are separately positioned on pressure
In contracting plunger shaft and expansion piston chamber, the second pulse tube is connected to expansion piston chamber and is coaxially disposed with expansion piston chamber, the two or two
Grade hot end heat exchanger is arranged in the second pulse tube, and the outside of the second expansion piston chamber is arranged in the second level-one hot end heat exchanger,
Second compression piston, the second expansion piston, compression piston chamber and expansion piston chamber constitute the second compression chamber, and the second expansion is lived
Plug, the second second level hot end heat exchanger and the second expansion piston chamber constitute the second expansion chamber, the second expansion chamber and the second compression chamber
Coaxially arranged, the internal diameter of compression piston chamber is greater than the internal diameter of expansion piston chamber, the internal diameter of expansion piston chamber and the second pulse tube
Internal diameter be it is identical, be parallel to compression piston cavity axis, be provided in the second compressor frame multiple connection compression piston chambers with
The through-hole of second level-one hot end heat exchanger, the flowing for Working medium gas.
In the cascade back-heating type natural gas liquefaction system provided by the utility model using pulse type sterlin refrigerator,
It is characterized in that, further including the first pressure maintaining valve, it is arranged in the cooling liquefaction pipeline between gas source and the first temperature reducing unit.
In addition, in the cascade back-heating type natural gas liquefaction system provided by the utility model using pulse type sterlin refrigerator
In system, which is characterized in that further include throttle valve, the cooling liquefaction between the second temperature reducing unit and LNG tank is set
In pipeline.
In addition, in the cascade back-heating type natural gas liquefaction system provided by the utility model using pulse type sterlin refrigerator
In system, which is characterized in that further include tapping valve, be arranged and lead to the pipe of LNG (liquefied natural gas) storage tank in LNG tank
Lu Zhong.
In addition, in the cascade back-heating type natural gas liquefaction system provided by the utility model using pulse type sterlin refrigerator
In system, which is characterized in that further include the second pressure maintaining valve, the cold recovery pipeline that LNG tank leads to fuel gas is set
In.
The action and effect of utility model
The cascade back-heating type natural gas liquefaction system of pulse type sterlin refrigerator is used according to involved in the utility model
System utilizes because the utility model combines the new and effective pulse type sterlin refrigerator suitable for different operating warm area
The principle of refrigeration machine classification refrigeration cools down step by step, is tentatively pre-chilled using high-temperature region pulse type sterlin refrigerator, use
Middle warm area pulse type sterlin refrigerator carries out deep cooling and supercooling, the condensation liquefaction part gas after the decompression of throttle valve isenthalpic throttling
Body, process complexity is lower, and the cooling capacity for the cryogenic natural gas gas that do not liquefy has been recycled using backheat processing.So this reality
The advantages of having with novel cascade back-heating type natural gas liquefaction system reduces system power dissipation, improves system effectiveness, can be realized
Obtain the compound action of liquefied natural gas and normal temperature and pressure fuel gas.
In addition, pulse type sterlin refrigerator uses helium for working medium, it is higher in its optimal operation temperature area refrigerating efficiency, be
System high efficient and flexible, may be implemented to minimize, and can also realize medium scale day using parallel system in deep cooling and liquefaction link
Right gas liquefaction.
Detailed description of the invention
Fig. 1 is the cascade back-heating type natural gas liquefaction system that pulse type sterlin refrigerator is combined in the utility model embodiment
The flow chart of system；
Fig. 2 is the embodiments of the present invention high temperature area pulse type free-piston Stirling cooler diagrammatic cross-section；
Fig. 3 is that the solid of the embodiments of the present invention high temperature area pulse type free-piston Stirling cooler rack is shown
It is intended to；
Fig. 4 is A direction view in Fig. 3；
Fig. 5 is C-C cross-sectional view in Fig. 4；
Fig. 6 is that the solid of the embodiments of the present invention high temperature area pulse type free-piston Stirling cooler rack is cutd open
Depending on schematic diagram；
Fig. 7 is middle warm area pulse type free-piston Stirling cooler diagrammatic cross-section in the embodiments of the present invention；
Fig. 8 is that the solid of middle warm area pulse type free-piston Stirling cooler rack in the embodiments of the present invention is shown
It is intended to；
Fig. 9 is B direction view in Fig. 8；And
Figure 10 is D-D cross-sectional view in Fig. 9.
Specific embodiment
In order to be easy to understand the technical means, creative features, achievement of purpose, and effectiveness of the utility model, with
Lower embodiment combination attached drawing uses the utility model the cascade back-heating type natural gas liquefaction system of pulse type sterlin refrigerator
It is specifically addressed.
Embodiment
As shown in Figure 1, a kind of process of the cascade back-heating type natural gas liquefaction system of combination pulse type sterlin refrigerator
Figure, this kind combine the natural gas liquefaction system of two kinds of different warm area pulse type sterlin refrigerators and backheat pipeline to specifically include that
Gas source 1L, pressure maintaining valve I 2, cooling liquefaction pipeline 3, LNG tank 4L, tapping valve 5, pressure maintaining valve II 6, cold recovery pipeline
7, wherein the cooling liquefaction classification refrigeration of pipeline 3 includes: two high-temperature region pulse type sterlin refrigerators, 301, two middle warm areas
Pulse type sterlin refrigerator 302, throttle valve 303.
Gas source 1L is sequentially communicated two high-temperature region pulse type sterlin refrigerators 301, two by cooling liquefaction pipeline 3
Platform middle warm area pulse type sterlin refrigerator 302 reach LNG tank 4L, pressure maintaining valve I 2 setting gas source 1L with
In cooling liquefaction pipeline 3 between high-temperature region pulse type sterlin refrigerator 301.Throttle valve 303 is arranged in middle warm area pulse type
In cooling liquefaction pipeline 3 between sterlin refrigerator 302 and LNG tank 4L.The setting of tapping valve 5 is natural in liquefaction
Gas storage tank 4L leads in the pipeline of LNG (liquefied natural gas) storage tank.The setting of pressure maintaining valve II 6 leads to combustion in LNG tank 4L
In the cold recovery pipeline 7 for expecting gas.
As shown in Fig. 2, Fig. 7, respectively high-temperature region pulse type sterlin refrigerator 301 and middle warm area pulse type sterlin system
The structure sectional view of cold 302.The optimal operation temperature area of high-temperature region pulse type sterlin refrigerator 301 is 220K (- 53 DEG C)
The above refrigeration section, can provide the refrigerating capacity of 50W~200W in its optimal operation temperature area, suitable for the pre- of natural gas liquefaction process
Cold link；The optimal operation temperature area of middle warm area pulse type sterlin refrigerator 302 is 120K~220K (- 153 DEG C~-53 DEG C)
Refrigeration section, can provide the refrigerating capacity of 20W~50W in its optimal operation temperature area, suitable for natural gas liquefaction process further
Cooling deep cooling link.Relative carnot efficiency of the pulse type sterlin refrigerator of two kinds of warm areas in its optimal operation temperature area is reachable
30%.
As shown in Fig. 2, high-temperature region pulse type free-piston Stirling cooler includes linear motor 1, compression unit, expansion
Machine unit, undamped dynamic absorber unit 4, rack 50 and shell 60.
As shown in Fig. 3,4,5,6, rack 50 includes flange 52, the piston tube 51 being arranged in flange 52 and pedestal 53,
Wherein, the shape in disk form of flange 52, the side of the flange are additionally provided with concentric roundel 521, on flange 52
It is even to be provided with multiple connection through-holes.
Pedestal 53 is cylindrical in shape, and one end is connected with the side of flange 52, and the other end is free end, the center line and method of pedestal 53
The center line of orchid 52 is overlapped, and is provided with multiple connecting screw holes on the free end of pedestal 53, and in embodiment, pedestal 53 is around flange
Four supporting legs of 52 center line.
Piston tube 51 be straight pipe, be arranged in flange 52 and with 52 coaxial line of flange, lateral ends opening be located at roundlet
The outside of disk 521, inner opposite end opening are located in pedestal 53, have cylinder-piston chamber in piston tube 51, are provided in plunger shaft
Multiple perpendicular to piston tube axis and to penetrate the through-hole 511 of piston tube wall, in embodiment, the section of through-hole 511 is arc groove,
Quantity is 3.
Linear motor 1 includes outer yoke 11, interior yoke 14 and mover, and outer yoke 11, interior yoke 14 are separately positioned on machine
There is gap, mover is arranged in gap, and mover includes permanent magnet 13 and permanent magnetism body support frame on frame and between outer yoke, interior yoke
15。
As shown in Fig. 2, linear motor 1 mainly includes outer yoke 11, coil 12, permanent magnet 13, interior yoke 14, permanent magnet branch
Frame 15, mover include permanent magnet 13, permanent magnetism body support frame 15, connector 16, fixture nut 18, compression piston 19 and compression piston
Flat spring 17 (only takes the 1/3 of flat spring quality when calculating mover quality), and permanent magnetism body support frame 15 is connected with permanent magnet 13, and with
Compression piston 19 and connector 16 are connected through a screw thread.Outer yoke 11 is soft magnetic materials with interior yoke 14, commonly uses electric work pure iron, silicon
The production of the materials such as steel disc, permanent magnet 13 are permanent-magnet material, commonly use Ru-Fe-Mn, alnico permanent magnetic material to make.Outer yoke 11, line
Circle 12, permanent magnet 13, interior yoke 14 are annular, and using coaxially arranged.Outer yoke 11, interior yoke 14 are separately positioned on machine
There is gap, mover is arranged in gap on frame 50 and between outer yoke, interior yoke.
When coil is passed through direct current, outer yoke 11 and interior yoke 14 will form magnetic force loop line, thus in outer 11 He of yoke
Magnetic pole is generated on interior yoke 14.When being passed through alternating current in coil, permanent magnet 13 just will receive alternating electromagnetic force and do reciprocal
Linear motion.When permanent magnet 13 does linear reciprocating motion, it will drive compression piston 19 and do linear reciprocating motion, compression piston plate
Spring 17 provides axial reciprocating elastic power and radial support.
Compression unit includes connector 16, compression piston flat spring 17, fixture nut 18, compression piston 19.Compression piston
Flat spring 17 is connected by fixture nut 18 with connector 16, and compression piston flat spring 17 is fixed with rack 50 by connector
Connection, compression piston 19 are arranged in plunger shaft, and one end is connected with mover and is connected with compression piston spring 17, and the other end is certainly
By holding.
Expanding machine unit include expansion piston 21, expansion piston flat spring 22, piston rod 23, level-one hot end heat exchanger 26,
Second level hot end heat exchanger 33, regenerator 25, pulse tube 31, cool end heat exchanger 24, cold finger shell 35,
Level-one hot end heat exchanger 26 is cylindrical, covers on the outer wall of piston tube 51 and be arranged in the end face of roundel 521
On, level-one hot end heat exchanger 26 and rack 50 are separate structure, and level-one hot end heat exchanger 26 and the outer wall interference of piston tube 51 are matched
It closes.
One end of pulse tube 31 is connected with 51 lateral ends of piston tube, and the other end is connected with cool end heat exchanger 24,
Regenerator 25 is in the cylindrical shape of ring-shaped section and ring-shaped, and the outside of pulse tube 31, one end and cool end heat exchanger 24 is arranged in
It is connected, the other end is connected with level-one hot end heat exchanger 26.Regenerator 25 is using polyester film, nylon and polytetrafluoroethylene (PTFE) material
Any one in material is made, in embodiment regenerator 25 using being made of polyester film, polyester film with a thickness of
20-50μm。
Second level hot end heat exchanger 33 is arranged in pulse tube 31, positioned at the junction of pulse tube 31 and piston tube 51, second level
Hot end heat exchanger 33 and rack 50 are separate structure, the inner wall interference fit of second level hot end heat exchanger 33 and piston tube 51.
Expansion piston 21 is arranged in piston tube 51, and expansion piston flat spring 22 connects by the way that connector and rack 50 are fixed
Connect, one end of piston rod 23 is connected with expansion piston 21, the other end pass through compression piston 19, after compression piston flat spring 17 with it is swollen
Swollen piston flat spring 22 is connected,
Compression piston 19, expansion piston 21 and plunger shaft constitute compression chamber, compression piston 19, second level hot end heat exchanger 33
And plunger shaft constitutes expansion chamber, expansion chamber is coaxially arranged with compression chamber.
The outside of level-one hot end heat exchanger 26, regenerator 25, cool end heat exchanger 24 is arranged in cold finger shell 35, and shell 60 is arranged
In rack 50 and the outside of expanding machine unit 30, shell 60, cold finger shell 35 and rack 50 are linked into an integrated entity by connector.
Undamped dynamic absorber unit 4 is connected with shell 60 and is arranged in the outside of shell 60, for carrying out to refrigeration machine
Damping.
The motion process and gas flow of expansion piston and compression piston:
Expansion piston flat spring 22 and piston rod 23 are fixed, and expansion piston 21 is connected with piston rod 23.
Expansion piston 21 is pure pneumatic actuation, is generated using the displacement phase difference between expansion piston 21 and compression piston 19
Refrigeration effect, 70 °~100 ° of displacement of the leading compression piston 19 of displacement of usual expansion piston 21, in low-temperature space (cold head temperature
At -100 DEG C or less) when, displacement phase difference can be decreased to 50~60 °.Since linear motor is sinusoidal ac excitation, so swollen
The movement of swollen piston 21 and compression piston 19 is also in sinusoidal continuous movement, but in order to illustrate its working principle, it is assumed that
Expansion piston 21 and compression piston 19 do intermittent touchdown formula according to circulation law and move.
Sound wave compression process: expansion piston 21 rests on that top dead centre is motionless, and compression piston 19 is moved upwards by lower dead center, this
When main compression chamber 29 in sound wave compressed, and flow into the level-one hot end heat exchanger 26 on the outside of cylinder, compression process generated
Heat be released to level-one hot end heat exchanger 26, heat is passed to dissipating for outside by outer housing again by level-one hot end heat exchanger 26
Hot device 27, is finally released to environment.Ideally think cylinder and outer housing is completely thermally conductive, while level-one hot end exchanges heat
The heat exchange area of device 26 and radiator 27 is infinitely great, therefore the temperature of working medium remains unchanged.But in the actual process, isotherm compression
It is impossible, and expansion piston 21 is it is not possible that intermittent movement, the expansion piston 21 when compression piston 19 moves upwards
It has begun and moves downward.
Regenerator exothermic process: compression piston 19 moves to motionless after top dead centre, and expansion piston 21 moves downward, at this time sound
Wave comes into full contact with heat exchange by the filler in regenerator 25, with regenerator 25, heat is discharged to regenerator 25, at this time backheat
The temperature of device 25 increases, acoustic wave temperature and pressure reduction.But in practical heat transfer process, 25 heat transfer process of regenerator is not fixed
Hold, it is also not possible to the complete heat exchange of 25 filler of real sound wave and regenerator.
Sound wave Laminar Flow process: gas passes through air deflector 32 after flowing through cool end heat exchanger 24, enters as a laminar flow
Gas in pulse tube 31 is pushed to expansion chamber 28 by pulse tube 31.After gas is squeezed, pressure and temperature rises.The heat of generation
It is radially transferred to level-one hot end heat exchanger 26 by second level hot end heat exchanger 33, be finally transmitted to radiator 27 and is released to ring
Border.Gas expansion for doing work in expansion chamber 28, auxiliary pushing expansion piston become smaller, rise to lower dead center, function recycling compression chamber 34B
The effect of recycling sound function is arrived.In practical work process, compression piston 19 can't rest on always top dead centre, but can be with
Expansion piston 21 moves downwardly together, but it need to be pointed out that the two is not movement in the same direction but the leading compression piston of expansion piston
Certain phase angle.
Sound wave process of refrigerastion: expansion piston 21 moves up to top dead centre since lower dead center, and compression piston 19 moves to
Lower dead center, expansion piston 21 push back to the sound wave in expansion chamber 28 in pulse tube 31, gas swelling heat absorption in pulse tube, produce
Raw refrigeration effect reaches lowest refrigerating temperature at air deflector 32 at 31 top of pulse tube.The cooling capacity of generation is changed by cold end
Hot device 24 is exported to cold environment.Sound wave working medium returns in regenerator 25 along original route again and comes into full contact with heat exchange with filler, inhales
After receiving the heat in regenerator 25, returns to main compression chamber 29 and wait next second compression.The temperature and pressure of the process sound wave
Rise, the decline of 25 temperature of regenerator.In the actual process, when compression piston 19 reaches lower dead center expansion piston 21 and not up on
Stop, but during returning to top dead centre, but its still advanced compression piston 19 on displacement wave phase.
The present embodiment is suitable for the cryogenic temperature of 220K (- 53 DEG C) or more, can provide the refrigerating capacity of 50W-200W.
As shown in fig. 7, coaxial pulse-tube type free-piston Stirling cooler includes linear motor 1, compression unit, expanding machine
Unit, undamped dynamic absorber unit 4, rack 50B and shell 60.
As shown in Figure 8,9, 10, rack 50B includes flange 52B, expansion piston pipe 51B, compression piston pipe 54B and pedestal
53B,
Wherein, flange 52B shape in disk form, the one side of flange 52B are provided with concentric disk 521B, another side
It is connected with pedestal 53B, multiple connection through-holes is evenly arranged on flange 52B.
Pedestal 53B is cylindrical in shape, one end be connected with flange 52B and with disk 521B coaxial line, the other end is free end, pedestal
The center line of 53B is overlapped with the center line of flange 52B, and multiple connecting screw holes, embodiment are provided on the free end of pedestal 53B
In, pedestal 53B is four supporting legs of the center line around pedestal 53B.
Expansion piston pipe 51B is straight pipe, and one end is connected with disk 521B, and the other end is free end, for connecting refrigeration
The pulse tube of machine, expansion piston pipe 51B is interior to have cylindrical expansion plunger shaft 511B,
Compression piston pipe 54B is straight pipe, is arranged in pedestal 53B, and one end is connected and same with flange 52B with flange 52B
Axis, the other end are free end, have compression cylinder plunger shaft 541B in compression piston pipe 54B, compression piston chamber 541B with it is swollen
Swollen plunger shaft 511B coaxial line and it is connected.
It is parallel to compression piston chamber 541B axis, multiple connection compression piston chamber 541B and outside are provided on disk 521B
Through-hole 522B, the quantity of through-hole 522B is between 3-9.In embodiment, the section of through-hole 522B is arc groove, quantity 4
It is a.
The internal diameter of compression piston chamber 541B is greater than the internal diameter of expansion piston chamber 511B, the internal diameter and arteries and veins of expansion piston chamber 511B
The internal diameter of washing pipe is identical.
Linear motor 1 includes outer yoke 11, interior yoke 14 and mover, and outer yoke 11, interior yoke 14 are separately positioned on machine
There is gap, mover is arranged in gap, and mover includes permanent magnet 13 and permanent magnetism body support frame on frame and between outer yoke, interior yoke
15。
As shown in fig. 7, linear motor 1 mainly includes outer yoke 11, coil 12, permanent magnet 13, interior yoke 14, permanent magnet branch
Frame 15, mover include permanent magnet 13, permanent magnetism body support frame 15, connector 16, fixture nut 18, compression piston 19 and compression piston
Flat spring 17 (only takes the 1/3 of flat spring quality when calculating mover quality), and permanent magnetism body support frame 15 is connected with permanent magnet 13, and with
Compression piston 19 and connector 16 are connected through a screw thread.Outer yoke 11 is soft magnetic materials with interior yoke 14, commonly uses electric work pure iron, silicon
The production of the materials such as steel disc, permanent magnet 13 are permanent-magnet material, commonly use Ru-Fe-Mn, alnico permanent magnetic material to make.Outer yoke 11, line
Circle 12, permanent magnet 13, interior yoke 14 are annular, and using coaxially arranged.Outer yoke 11, interior yoke 14 are separately positioned on machine
There is gap, mover is arranged in gap on frame 50B and between outer yoke, interior yoke.
When coil is passed through direct current, outer yoke 11 and interior yoke 14 will form magnetic force loop line, thus in outer 11 He of yoke
Magnetic pole is generated on interior yoke 14.When being passed through alternating current in coil, permanent magnet 13 just will receive alternating electromagnetic force and do reciprocal
Linear motion.When permanent magnet 13 does linear reciprocating motion, it will drive compression piston 19 and do linear reciprocating motion, compression piston plate
Spring 17 provides axial reciprocating elastic power and radial support.
Compression unit includes connector 16, compression piston flat spring 17, fixture nut 18, compression piston 19.Compression piston
Flat spring 17 is connected by fixture nut 18 with connector 16, and compression piston flat spring 17 and rack 50B are solid by connector
Fixed connection, compression piston 19 are arranged in compression piston chamber 541B, and one end is connected with mover and is connected with compression piston spring 17,
The other end is free end.
Expanding machine unit includes expansion piston 21B, expansion piston flat spring 22B, piston rod 23B, level-one hot end heat exchanger
26B, second level hot end heat exchanger 33B, regenerator 25B, pulse tube 31B, cool end heat exchanger 24B, cold finger shell 35B.
Level-one hot end heat exchanger 26B is cylindrical, covers on the outer wall of expansion piston pipe 51B and is arranged in roundel 521B
End face on, level-one hot end heat exchanger 26B and rack 50B are separate structure, level-one hot end heat exchanger 26B and piston tube 51B's
Outer wall interference fit.
One end of pulse tube 31B is connected with one end of expansion piston pipe 51B, and the other end is connected with cool end heat exchanger 24B.
Regenerator 25B is in the cylindrical shape of ring-shaped section and ring-shaped, and the outside of pulse tube 31B, one end and cool end heat exchanger is arranged in
24B is connected, and the other end is connected with level-one hot end heat exchanger 26B.
Second level hot end heat exchanger 33B is arranged in pulse tube 31B, positioned at the connection of pulse tube 31B and expansion piston pipe 51B
Place, second level hot end heat exchanger 33B and rack 50B are separate structure, and second level hot end heat exchanger 33B is interior with expansion piston pipe 51B's
Wall interference fit.
Expansion piston 21B is arranged in expansion piston pipe 51B, and expansion piston flat spring 22B passes through connector and rack 50B
It is fixedly connected, one end of piston rod 23B is connected with expansion piston 21B, and the other end passes through compression piston 19, compression piston flat spring
It is connected after 17 with expansion piston flat spring 22B,
Compression piston 19, expansion piston 21B, compression piston chamber 541B and expansion piston chamber 511B constitute compression chamber.
Expansion piston 21B, second level hot end heat exchanger 33B and expansion piston chamber 511B constitute expansion chamber.Expansion chamber and pressure
Contracting chamber is coaxially arranged.
The outside of level-one hot end heat exchanger 26B, regenerator 25B, cool end heat exchanger 24B, shell 60 is arranged in cold finger shell 35B
The outside of rack 50B and expanding machine unit are set, and shell 60, cold finger shell 35B and rack 50B connect into one by connector
Body.
Radiator 27 is located at the outside of level-one hot end heat exchanger 26B and is arranged on cold finger shell 35B, level-one hot end heat exchanger
Heat is passed to the radiator 27 in outside by 26B by cold finger shell 35B, is finally released to environment.
Undamped dynamic absorber unit 4 is connected with shell 60 and is arranged in the outside of shell 60, for carrying out to refrigeration machine
Damping.
Sound wave Laminar Flow process: gas is flowed through by air deflector 32B after cool end heat exchanger 24B, as a laminar flow into
Enter pulse tube 31B, gas in pulse tube 31B is pushed to expansion chamber 28B.After gas is squeezed, pressure and temperature rises.It generates
Heat is radially transferred to level-one hot end heat exchanger 26B by second level hot end heat exchanger 33B, is finally transmitted to radiator 27 and releases
It puts to environment.Gas expansion for doing work in expansion chamber 28B, auxiliary pushing expansion piston recycle compression chamber 34B to lower dead center, function
Become smaller, plays the role of recycling sound function.In practical work process, compression piston 19 can't rest on always top dead centre,
But it can be moved downwardly together with expansion piston 21B, but it need to be pointed out that the two is not movement in the same direction but expansion piston neck
The certain phase angle of first compression piston.
The present embodiment is suitable for the cryogenic temperature section of 120K~220K (- 153 DEG C~53 DEG C), can provide 20W~50W
Refrigerating capacity.
In conjunction with shown in Fig. 1, Fig. 2, Fig. 7, a kind of cascade back-heating type natural gas liquefaction of combination pulse type sterlin refrigerator
The workflow of system are as follows: by the high-pressure gaseous natural gas of the operation processings such as clean dehumidifying, exported from gas source 1L, through pressure maintaining valve
I 2 pressure stabilizings flow into cooling liquefaction pipeline 3, first flow through first order high temperature in cooling liquefaction pipeline 3 to certain operating pressure
The cold end of area's pulse type sterlin refrigerator 301 is tentatively pre-chilled, First high-temperature region pulse type sterlin refrigerator 301
Cold junction temperature setting exists in 253K (- 20 DEG C), the cold junction temperature setting of second high-temperature region pulse type sterlin refrigerator 301
220K (- 53 DEG C), the gaseous natural gas after preliminary pre-cooling are flowed out from first order high-temperature region pulse type sterlin refrigerator 301
Afterwards, into the further cooling down of second level middle warm area pulse type sterlin refrigerator 302, this spy of First middle warm area pulse type
The cold junction temperature setting of woods refrigeration machine 302 at 180K (- 93 DEG C), second middle warm area pulse type sterlin refrigerator 302 it is cold
End temperature can be set according to liquefied fraction demand, and gaseous natural gas is subcooled, and the gaseous state after further deep cooling and supercooling is natural
Gas flows through 303 isenthalpic throttling of throttle valve and is depressurized to a mark after the outflow of second level middle warm area pulse type sterlin refrigerator 302
Quasi- atmospheric pressure, gaseous natural gas, with certain liquefied fraction condensation liquefaction, it is natural to flow into liquefaction according to the supercooling situation after its deep cooling
Gas storage tank 4L, opening tapping valve 5, the liquefied natural gas in LNG tank 4L can be discharged, and be sent into LNG storage tank.It opens steady
Pressure valve II 6, control cold recovery pipeline 7 in certain pressure, the not liquefied cryogenic natural gas gas in part through pressure maintaining valve II 6 into
Enter cold recovery pipeline 7, cold recovery pipeline 7 and cooling liquefaction pipeline 3, which are inversely arranged and do insulation isothermal holding, carries out pipeline
Between exchange heat, by the cold recovery of cryogenic natural gas gas to cooling liquefaction pipeline 3, reduce system power dissipation, from cold recovery pipeline 7
The normal temperature and pressure natural gas gas of middle outflow, which can directly transport away, makees fuel gas use.Entire cascade back-heating type natural gas liquefaction
Each pipeline, each equipment cold end, valve member and natural gas storage tank in system flow make adiabatic heat-insulation processing.
The action and effect of embodiment
The characteristics of the present embodiment, is combined with the new and effective pulse type sterlin refrigeration suitable for different operating warm area
Machine, the principle that Cryo Refrigerator classification refrigeration is utilized are cooled down step by step, are carried out just using high-temperature region pulse type sterlin refrigerator
Step pre-cooling carries out deep cooling and supercooling using middle warm area pulse type sterlin refrigerator, condenses after the decompression of throttle valve isenthalpic throttling
Liquefaction portion gas, process complexity is lower, and the cooling capacity for the cryogenic natural gas gas that do not liquefy has been recycled using backheat processing,
System power dissipation is reduced, system effectiveness is improved, realizes the compound action for obtaining liquefied natural gas and normal temperature and pressure fuel gas.
Pulse type sterlin refrigerator uses helium for working medium, and higher in its optimal operation temperature area refrigerating efficiency, system high efficiency is flexible, can
To realize miniaturization, medium scale natural gas liquefaction can also be realized using parallel system in deep cooling and liquefaction link.
In addition, the pulse type free-piston Stirling cooler of the present embodiment eliminates traditional free piston stirling refrigeration
The longer low-temperature expansion piston of machine is replaced with shorter room-temperature zone work work recycling expansion piston.Free piston stirling refrigeration
The expansion cylinder of machine becomes the pulse tube of vascular cold finger, and pulse tube cold end is disposed with the air deflector of laminarization, and hot end is equipped with two
Grade hot end heat exchanger.The advantages of this change combines free-piston Stirling cooler and vascular refrigerator, by cancelling
The expansion piston of hot and cold side high frequency motion eliminates low-temperature expansion piston bring pumping loss, shuttles and lose and axially lead
Heat loss.Shorter swell at room temperature piston is set by hot end and solves the problems, such as the acoustic power recovery of vascular refrigerator, therefore, when complete
When full recycling cold end sound function, which is Carnot's cycle efficiency.Meanwhile
Cancelling low-temperature expansion piston reduces refrigeration machine manufacture difficulty, reduces overall mass.
Above embodiment is the preferred case of the utility model, is not intended to limit the protection scope of the utility model.
Claims (5)
1. a kind of cascade back-heating type natural gas liquefaction system using pulse type sterlin refrigerator characterized by comprising
The first temperature reducing unit, the second temperature reducing unit and the liquefaction that gas source, the pipeline that liquefied by cooling are sequentially communicated are natural
Gas storage tank,
Wherein, first temperature reducing unit includes an at least high-temperature region pulse type sterlin refrigerator, and second cooling is single
Member includes an at least middle warm area pulse type sterlin refrigerator,
The high-temperature region pulse type sterlin refrigerator include the first compressor frame, the first compression piston, the first expansion piston,
First pulse tube, the first second level hot end heat exchanger, the first level-one hot end heat exchanger,
First compressor frame has piston tube, and the piston tube has for accommodating first compression piston and described
The cylinder-piston chamber of first expansion piston, first pulse tube is connected to the plunger shaft and the plunger shaft is coaxially disposed, institute
It states the first second level hot end heat exchanger to be arranged in first pulse tube, the first level-one hot end heat exchanger is arranged in the work
The outside of pipe is filled in,
First compression piston, first expansion piston and the plunger shaft constitute the first compression chamber,
First expansion piston, the second level hot end heat exchanger and first pulse tube constitute the first expansion chamber, described
First expansion chamber and first compression chamber are coaxially arranged,
The internal diameter of first pulse tube is identical as the plunger shaft internal diameter,
Perpendicular to the piston cavity axis, multiple first through hole for penetrating the piston tube wall are provided in the plunger shaft,
The first through hole is connected to the plunger shaft and the first level-one hot end heat exchanger,
The middle warm area pulse type sterlin refrigerator include the second compressor frame, the second compression piston, the second expansion piston,
Second pulse tube, the second second level hot end heat exchanger, the second level-one hot end heat exchanger,
Second compressor frame has a cylindrical compression piston chamber and expansion piston chamber of coaxial arrangement and connection, and described the
Two compression pistons, second expansion piston are separately positioned in the compression piston chamber and the expansion piston chamber, and described
Two pulse tubes are connected to the expansion piston chamber and are coaxially disposed with the expansion piston chamber, and the second second level hot end heat exchanger is set
It sets in second pulse tube, the outside of expansion piston chamber is arranged in the second level-one hot end heat exchanger,
Second compression piston, second expansion piston, the compression piston chamber and the expansion piston chamber constitute the
Two compression chambers,
Second expansion piston, the second second level hot end heat exchanger and the expansion piston chamber constitute the second expansion chamber,
Second expansion chamber and second compression chamber are coaxially arranged,
The internal diameter of the compression piston chamber is greater than the internal diameter of the expansion piston chamber, the internal diameter of the expansion piston chamber and described the
The internal diameter of two pulse tubes be it is identical,
It is parallel to the compression piston cavity axis, multiple connection compression piston chambers are provided in second compressor frame
With the second through-hole of the second level-one hot end heat exchanger, flowing for Working medium gas.
2. the cascade back-heating type natural gas liquefaction system according to claim 1 using pulse type sterlin refrigerator,
It is characterized in that, further includes:
First pressure maintaining valve is arranged in the cooling liquefaction pipeline between the gas source and first temperature reducing unit.
3. the cascade back-heating type natural gas liquefaction system according to claim 1 using pulse type sterlin refrigerator,
It is characterized in that, further includes:
The cooling liquefaction pipeline between second temperature reducing unit and the LNG tank is arranged in throttle valve
In.
4. the cascade back-heating type natural gas liquefaction system according to claim 1 using pulse type sterlin refrigerator,
It is characterized in that, further includes:
Tapping valve is arranged in the pipeline that the LNG tank leads to LNG (liquefied natural gas) storage tank.
5. the cascade back-heating type natural gas liquefaction system according to claim 1 using pulse type sterlin refrigerator,
It is characterized in that:
Second pressure maintaining valve is arranged in the LNG tank and leads in the cold recovery pipeline of fuel gas.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201820685644.2U CN208205604U (en) | 2018-05-09 | 2018-05-09 | Use the cascade back-heating type natural gas liquefaction system of pulse type sterlin refrigerator |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201820685644.2U CN208205604U (en) | 2018-05-09 | 2018-05-09 | Use the cascade back-heating type natural gas liquefaction system of pulse type sterlin refrigerator |
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| CN201820685644.2U Expired - Fee Related CN208205604U (en) | 2018-05-09 | 2018-05-09 | Use the cascade back-heating type natural gas liquefaction system of pulse type sterlin refrigerator |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108413705A (en) * | 2018-05-09 | 2018-08-17 | 上海理工大学 | Use the cascade back-heating type natural gas liquefaction system of pulse type sterlin refrigerator |
| CN117663680A (en) * | 2023-12-16 | 2024-03-08 | 江苏永诚装备科技有限公司 | Ship natural gas liquefying device with precooling structure |
-
2018
- 2018-05-09 CN CN201820685644.2U patent/CN208205604U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108413705A (en) * | 2018-05-09 | 2018-08-17 | 上海理工大学 | Use the cascade back-heating type natural gas liquefaction system of pulse type sterlin refrigerator |
| CN117663680A (en) * | 2023-12-16 | 2024-03-08 | 江苏永诚装备科技有限公司 | Ship natural gas liquefying device with precooling structure |
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