CN2886449Y - Pulse tube refrigerator with cold end gas storage - Google Patents

Pulse tube refrigerator with cold end gas storage Download PDF

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Publication number
CN2886449Y
CN2886449Y CNU2006201031741U CN200620103174U CN2886449Y CN 2886449 Y CN2886449 Y CN 2886449Y CN U2006201031741 U CNU2006201031741 U CN U2006201031741U CN 200620103174 U CN200620103174 U CN 200620103174U CN 2886449 Y CN2886449 Y CN 2886449Y
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CN
China
Prior art keywords
cold
vascular
gas storage
end gas
cold end
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Expired - Fee Related
Application number
CNU2006201031741U
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Chinese (zh)
Inventor
张小斌
邱利民
甘智华
张学军
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Zhejiang University ZJU
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Zhejiang University ZJU
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Priority to CNU2006201031741U priority Critical patent/CN2886449Y/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/14—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle
    • F25B9/145—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle pulse-tube cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/14—Compression machines, plants or systems characterised by the cycle used 
    • F25B2309/1408—Pulse-tube cycles with pulse tube having U-turn or L-turn type geometrical arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/14—Compression machines, plants or systems characterised by the cycle used 
    • F25B2309/1415—Pulse-tube cycles characterised by regenerator details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/14—Compression machines, plants or systems characterised by the cycle used 
    • F25B2309/1418—Pulse-tube cycles with valves in gas supply and return lines
    • F25B2309/14181—Pulse-tube cycles with valves in gas supply and return lines the valves being of the rotary type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/14—Compression machines, plants or systems characterised by the cycle used 
    • F25B2309/1421—Pulse-tube cycles characterised by details not otherwise provided for
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/14—Compression machines, plants or systems characterised by the cycle used 
    • F25B2309/1424—Pulse tubes with basic schematic including an orifice and a reservoir
    • F25B2309/14241—Pulse tubes with basic schematic including an orifice reservoir multiple inlet pulse tube

Abstract

The utility model discloses a vessel refractor provided with a cold-end gas room comprising a regenerator, a lamellar flow element, a vessel, a heat exchanger and a gas room of the cold and hot end of the vessel, wherein the cold-end gas room is a head space communicated with the cold end of the vessel by a thin pipe tap or a capillary which provided with a laminar flow element nearby. The cold-end gas room produces a mass component compared the same phase with the pressure at the cold end of the vessel, regulates pressure wave and mass flow at the cold end directly to achieve more refrigerating capacity for the vessel. The cold-end gas room is applicable to not only vessel refractor for an eyelet gas room, but also two-way air-in vessel refractor for both GM-shaped and Stirling-shaped vessel refractors.

Description

The vascular refrigerator of band cold end gas storage
Technical field
The utility model relates to the Cryo Refrigerator in a kind of low-temperature refrigeration technology field, particularly a kind of vascular refrigerator with cold end gas storage.
Background technology
Vascular refrigerator utilizes high-low pressure gas that the gas process that charges and discharge of vascular cavity is obtained refrigeration effect.It has eliminated traditional regenerating type low-temperature refrigerator, as the low temperature movement parts of Sriling and G-M refrigeration machine, and the phase place that vascular cold junction mass flow and pressure wave are regulated in the reciprocating motion of dependence vascular internal gas piston.Yet gas piston motion and vascular pressure quadrature in phase are according to the phase potential theory, when vascular cold junction pressure and the same phase time of speed, refrigerating capacity maximum; When spending, refrigerating capacity equals zero when both quadratures (phase difference 90).The basic model vascular mainly by and the heat exchange of tube wall with heat from cold junction " pump " to the hot junction, produce cold thus.But the pump hot merit of tube wall can be limited, limited the raising of basic model vascular refrigerator performance.1986, former Soviet Union Micoud woods has been introduced aperture and air reservoir in the hot junction of basic model vascular, makes the two plume amounts that produced in the vascular respectively with pressure homophase and quadrature.In one-period gas piston is done positive work after wherein synchronous flow and the pressure effect, according to the conservation of energy, this equals refrigerating capacity hard during dynamic stability, thereby has improved refrigeration mechanism cold and refrigerating efficiency.Yet another quadrature component and pressure acting equal zero in one-period, so this component consumption external compression merit, but do not produce cold, have reduced the refrigeration machine overall efficiency.As seen, improve the vascular refrigerator performance, must improve in the vascular and the mass component of pressure in-phase component, reduce the mass component of quadrature component simultaneously.In recent years, on the basis of pinhole type vascular refrigerator, some new phase modulation structures have appearred in succession, its effect is to increase and the synchronous mass component of pressure: bidirectional air intake structure on the one hand bypass partly pass through the gas of regenerator, make a part of gas directly enter the vascular hot junction without regenerator, reduced flow, improved THERMAL REGENERATOR EFFICIENCIES through regenerator; The effect of similar on the other hand aperture and air reservoir can further produce and pressure homophase volume flow in vascular.But, make by the mass component of by-passing valve and pressure homophase very little, therefore little to the phase modulation effect of cold junction because regenerator pressure at two ends phase difference is less.The multi-channel shunt structure has similar effect to bidirectional air intake structure, but be subjected to the restriction of resistance element one aperture or valve pressure at two ends phase difference equally, continuation regulating action to the cold junction phase place limited (but since both improved pressure amplitude, so overall performance improves than pinhole type).But the pressure phase difference active adjustment at interior phase modulation structure aperture valve two ends, thereby quality of regulation component, so refrigerating capacity also improves a lot than pinhole type.Generally, several phase modulation structures belong to indirect pm mode, i.e. the phase place of phase modulation effect by gas piston indirect regulation vascular cold junction more than.
Summary of the invention
The purpose of this utility model provides a kind of vascular refrigerator with cold junction phase modulation structure one cold end gas storage.
It comprises compressor, rotary valve, regenerator hot end heat exchanger, regenerator, cool end heat exchanger, vascular, hot end heat exchanger, little ports valve, the air reservoir that is connected, be connected by the bidirection air intake valve between hot end heat exchanger and the regenerator hot end heat exchanger, it is characterized in that being provided with the cold junction phase modulating mechanism at the vascular cold junction.
Said cold junction phase modulating mechanism has cold end gas storage, and the cold end gas storage vascular is communicated with by the tube wall aperture, both coaxial arrangement, and adjacent aperture is provided with deflector in the vascular.The cold junction phase modulating mechanism has cold end gas storage, and cold end gas storage is communicated with by capillary with vascular, and both arrange that independently adjacent aperture is provided with deflector in the vascular.Cold end gas storage is an empty, is put in the vacuum insulation environment.
The utility model increases cold end gas storage at the vascular cold junction, and it is communicated with the vascular cold junction or by the tube wall pore, both coaxial arrangement; Or by the capillary connection, both are arranged apart.Cold end gas storage can further produce the mass component with the pressure homophase in vascular, directly regulate vascular cold junction pressure and flow phase place, thereby improve the refrigeration mechanism cold.Show that through calculating pinhole type and dual-way air-intake vascular refrigeator refrigerating capacity after increasing cold end gas storage all can improve with linear model analysis, if the volume ratio of cold end gas storage and vascular greater than certain value, then refrigerating efficiency will improve.This structure both had been applicable to GM type vascular refrigerator, also was applicable to Stirling type vascular refrigerator.In addition, the cold end gas storage requisite space is much smaller than the room temperature air reservoir, and shape is unrestricted, so the not significantly increase of vascular refrigerator volume, and compact conformation, and is simple to operate.
Description of drawings
Fig. 1 is the pulse pipe refrigeration machine system schematic diagram of the utility model cold end gas storage and vascular cold junction coaxial arrangement.
Fig. 2 is a utility model cold end gas storage and vascular cold junction pulse pipe refrigeration machine system schematic diagram arranged apart.
Fig. 3 compares OV for the utility model aperture air reservoir type vascular refrigerator dimensionless refrigerating capacity with cold end gas storage and vessel volume 2Variation.Dimensionless frequency F=ω V among the figure p/ κ P 0C r=0.5, wherein ω is an angular speed, V pBe vessel volume, κ is the working medium specific heat ratio, P 0Be average pressure, C rBe the regenerator flow resistance coefficient.Little ports valve compares OC with the flow resistance of regenerator 1=0.2, the volume ratio OV of hot junction air reservoir and vascular 1=8, vascular low temperature T c=40K, high temperature T h=300K.In addition, the ratio OC of cold end gas storage aperture or capillary flow resistance and regenerator flow resistance among the figure 2=0, the cold end gas storage volume compares OV with vessel volume 2=0 expression does not have cold end gas storage, is pinhole type vascular refrigerator refrigerating capacity.
Fig. 4 has provided the utility model pinhole type vascular refrigerator refrigerating efficiency (COP) and has compared OV with cold end gas storage and vessel volume 2Variation.F=0.5 among the figure, OC 1=0.2, OV 1=8, T c=40, T h=300.
Fig. 5 has provided the utility model dual-way air-intake vascular refrigeator dimensionless refrigerating capacity and compared OV with cold end gas storage and vessel volume when different cold junction aperture aperture 2Variation, F=0.5 among the figure, OC 1=0.2, OV 1=8, the ratio DC=0.1 of by-passing valve and regenerator flow resistance.
Fig. 6 has provided the utility model dual-way air-intake vascular refrigeator efficient (COP) and has compared OV with cold end gas storage and vessel volume 2Variation, the COP curve that has provided pinhole type vascular refrigerator (DC=0) among the figure simultaneously is to contrast.
The specific embodiment
As shown in Figure 1, 2, the vascular refrigerator of band cold end gas storage comprises compressor 1, rotary valve 2, regenerator hot end heat exchanger 3, regenerator 4, cool end heat exchanger 5, vascular 9, hot end heat exchanger 10, aperture valve 12, the air reservoir 13 that is connected, be connected by bidirection air intake valve 11 between hot end heat exchanger 10 and the regenerator hot end heat exchanger 3, it is characterized in that being provided with the cold junction phase modulating mechanism at vascular 9 cold junctions.
The cold junction phase modulating mechanism has cold end gas storage 6, and cold end gas storage 6 is communicated with by tube wall aperture 7 with vascular 9, both coaxial arrangement, and adjacent aperture 7 is provided with deflector 8 in the vascular 9.The cold junction phase modulating mechanism has cold end gas storage 6, and cold end gas storage 6 is communicated with by capillary 14 with vascular 9, and both arrange that independently adjacent aperture 7 is provided with deflector 8 in the vascular 9.Cold end gas storage 6 one emptys are put in the vacuum insulation environment.
Laminarization element 8 can be that silk nettings fillings such as stainless steel, red copper form or other porous media materials.
Shown in Fig. 3,5, the acting in conjunction of cold end gas storage and pore (or capillary), produced mass component with pressure homophase and quadrature at the vascular cold junction, produce cold at one-period after in-phase component and the pressure acting in conjunction, therefore the refrigerating capacity of vascular refrigerator must increase, and increases with the volume ratio of cold end gas storage and vascular.But in fact the cold end gas storage volume is limited by the vacuum insulation system bulk, can not be excessive.During with the vascular coaxial arrangement, notice that axial direction length can not be oversize, because the blood vessel wall surface temperature rises to room temperature from cold junction temperature vertically, and the cold end gas storage temperature equates with the vascular cold junction temperature all the time, therefore, both long axial contacts will cause the heat conduction from the tube wall to the cold end gas storage, thereby reduce the refrigeration mechanism cold.The aperture aperture is also very big to the refrigerating capacity influence, and generally getting tube wall aperture aperture is 0.1～0.3 of vascular hot junction aperture valve opening.Shown in Fig. 3,5, than less than about 0.4 o'clock, during aperture aperture less (0.1 of aperture valve opening, state A), the increase of refrigerating capacity is more remarkable when big (0.3 of aperture valve opening, state B) than aperture aperture in cold end gas storage and vessel volume; Yet, when air reservoir and vessel volume than greater than about 0.4 the time, state B presents more superior refrigerating capacity performance than state A.And more about 0.4 the time than surpassing when air reservoir and vessel volume, state A refrigerating capacity increases small, and that state B refrigerating capacity increases is still remarkable.
Yet, owing in the one-period of vascular, do not produce refrigerating capacity with the mass component of pressure quadrature, but consume simultaneously the compressor compresses merit, therefore, though the introduction of cold end gas storage can increase refrigerating capacity, when also having increased simultaneously extra compressor horsepower, cold end gas storage is relevant with the relative size that cold increases and work done during compression increases to the influence of refrigeration machine efficient.Shown in Fig. 4,6, when the volume ratio of cold end gas storage and vascular hour, what cold end gas storage caused is less than quadrature component with the pressure in-phase component, so refrigeration machine efficient reduces during than no cold end gas storage.But when increasing to certain value along with the volume ratio of cold end gas storage and vascular, what cold end gas storage caused surpasses quadrature component with the pressure in-phase component, and therefore, refrigeration machine efficient increases during than no cold end gas storage, and increases with the continuation of volume ratio, and efficient also continues increase.The analysis showed that when state A, this definite value is about 0.2; When state B, this definite value is about 0.75, and when tube wall aperture aperture was 0.2 (state C) of aperture valve opening, this definite value was about 0.45.
It should be noted that the introduction of cold end gas storage has increased the flow of refrigeration machine working medium, this has negative effect to THERMAL REGENERATOR EFFICIENCIES, and the reduction of THERMAL REGENERATOR EFFICIENCIES will reduce the overall efficiency of refrigeration machine simultaneously.Yet, if the cold end gas storage volume is relative less with tube wall aperture aperture, can think that the increase of flow is limited, thus less to the influence of THERMAL REGENERATOR EFFICIENCIES.
In addition, cold end gas storage and tube wall aperture make the vascular cold junction produce radially disturbance, have destroyed the working medium laminar flow, impel working medium to present turbulent condition at the vascular cold junction, have strengthened the heat convection of heat, have reduced the refrigerating capacity of refrigeration machine.Therefore, the laminarization element must be set behind aperture.The effect of laminarization element is that turbulent flow is limited in small equality of temperature volume of vascular cold junction, and the heat convection of blocking-up working medium guarantees the laminar flow of working medium in vascular.The laminarization element is filled for the stainless steel cloth sheet and is formed or other porous media structure, certain axial length must be arranged to guarantee the vascular laminarization.

Claims (4)

1, a kind of vascular refrigerator with cold end gas storage, it is characterized in that it comprises compressor (1), rotary valve (2), regenerator hot end heat exchanger (3), regenerator (4), cool end heat exchanger (5), vascular (9), hot end heat exchanger (10), little ports valve (12), the air reservoir (13) that is connected, be connected by bidirection air intake valve (11) between hot end heat exchanger (10) and the regenerator hot end heat exchanger (3), it is characterized in that being provided with the cold junction phase modulating mechanism at vascular (9) cold junction.
2, a kind of vascular refrigerator according to claim 1 with cold end gas storage, it is characterized in that, said cold junction phase modulating mechanism has cold end gas storage (6), cold end gas storage (6) is communicated with by tube wall aperture (7) with vascular (9), adjacent aperture (7) is provided with deflector (8) in both coaxial arrangement, vascular (9).
3, a kind of vascular refrigerator according to claim 1 with cold end gas storage, it is characterized in that, said cold junction phase modulating mechanism has cold end gas storage (6), cold end gas storage (6) is communicated with by capillary (14) with vascular (9), both arrange that independently adjacent aperture (7) is provided with deflector (8) in the vascular (9).
4, a kind of vascular refrigerator with cold end gas storage according to claim 1 is characterized in that, said cold end gas storage (6) is an empty, is put in the vacuum insulation environment.
CNU2006201031741U 2006-04-28 2006-04-28 Pulse tube refrigerator with cold end gas storage Expired - Fee Related CN2886449Y (en)

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CNU2006201031741U CN2886449Y (en) 2006-04-28 2006-04-28 Pulse tube refrigerator with cold end gas storage

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100386578C (en) * 2006-04-28 2008-05-07 浙江大学 Pulse tube refrigerator with cold end gas storage
CN101603743B (en) * 2009-06-29 2012-07-11 浙江大学 Acoustic power amplifier used in inertia tube phase adjustment and pulse tube refrigerator thereof
CN105042922A (en) * 2015-07-07 2015-11-11 中国科学院理化技术研究所 Pulse tube refrigerator and flow guide structure thereof

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100386578C (en) * 2006-04-28 2008-05-07 浙江大学 Pulse tube refrigerator with cold end gas storage
CN101603743B (en) * 2009-06-29 2012-07-11 浙江大学 Acoustic power amplifier used in inertia tube phase adjustment and pulse tube refrigerator thereof
CN105042922A (en) * 2015-07-07 2015-11-11 中国科学院理化技术研究所 Pulse tube refrigerator and flow guide structure thereof
CN105042922B (en) * 2015-07-07 2017-05-24 中国科学院理化技术研究所 Pulse tube refrigerator and flow guide structure thereof

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GR01 Patent grant
C19 Lapse of patent right due to non-payment of the annual fee
CF01 Termination of patent right due to non-payment of annual fee