CN1140739C - Low-temperature refrigerator with reversed-phase gas circulation and without heat regenerator - Google Patents
Low-temperature refrigerator with reversed-phase gas circulation and without heat regenerator Download PDFInfo
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- CN1140739C CN1140739C CNB011090928A CN01109092A CN1140739C CN 1140739 C CN1140739 C CN 1140739C CN B011090928 A CNB011090928 A CN B011090928A CN 01109092 A CN01109092 A CN 01109092A CN 1140739 C CN1140739 C CN 1140739C
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- 238000005057 refrigeration Methods 0.000 claims description 46
- 238000000034 method Methods 0.000 claims description 32
- 238000007906 compression Methods 0.000 claims description 9
- 238000010521 absorption reaction Methods 0.000 claims description 6
- 239000002184 metal Substances 0.000 claims description 4
- 238000010438 heat treatment Methods 0.000 claims description 3
- 230000001172 regenerating effect Effects 0.000 abstract description 3
- 239000002245 particle Substances 0.000 description 35
- 239000011159 matrix material Substances 0.000 description 8
- 238000010586 diagram Methods 0.000 description 7
- 230000005540 biological transmission Effects 0.000 description 4
- 238000005192 partition Methods 0.000 description 3
- 230000007423 decrease Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- IXSZQYVWNJNRAL-UHFFFAOYSA-N etoxazole Chemical compound CCOC1=CC(C(C)(C)C)=CC=C1C1N=C(C=2C(=CC=CC=2F)F)OC1 IXSZQYVWNJNRAL-UHFFFAOYSA-N 0.000 description 2
- 229910052739 hydrogen Inorganic materials 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 229910000906 Bronze Inorganic materials 0.000 description 1
- 229910001111 Fine metal Inorganic materials 0.000 description 1
- 240000007594 Oryza sativa Species 0.000 description 1
- 235000007164 Oryza sativa Nutrition 0.000 description 1
- OAICVXFJPJFONN-UHFFFAOYSA-N Phosphorus Chemical compound [P] OAICVXFJPJFONN-UHFFFAOYSA-N 0.000 description 1
- 239000011805 ball Substances 0.000 description 1
- 239000010974 bronze Substances 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000010924 continuous production Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- KUNSUQLRTQLHQQ-UHFFFAOYSA-N copper tin Chemical compound [Cu].[Sn] KUNSUQLRTQLHQQ-UHFFFAOYSA-N 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000000945 filler Substances 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 239000000696 magnetic material Substances 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 238000012856 packing Methods 0.000 description 1
- 230000000737 periodic effect Effects 0.000 description 1
- 235000009566 rice Nutrition 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 229910001220 stainless steel Inorganic materials 0.000 description 1
- 239000010935 stainless steel Substances 0.000 description 1
- 238000012932 thermodynamic analysis Methods 0.000 description 1
- 239000002023 wood Substances 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/14—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle
- 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
- F25B2309/1418—Pulse-tube cycles with valves in gas supply and return lines
-
- 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
- F25B2309/1422—Pulse tubes with basic schematic including a counter flow heat exchanger instead of a regenerative heat exchanger
-
- 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
- F25B2309/1425—Pulse tubes with basic schematic including several pulse tubes
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The invention relates to a back-phase gas circulation low-temperature refrigerator without a heat regenerator, which comprises two sub-refrigerators without a heat regenerator and a high-efficiency counter-flow heat exchanger, wherein the two sub-refrigerators have the same structure, the cold ends of the two sub-refrigerators are connected in parallel with the cold end of the high-efficiency counter-flow heat exchanger, a main channel of the high-efficiency counter-flow heat exchanger consists of 2N groups of sub-channels, and N is a positive integer of 1-4; the sub-refrigerator is a conventional regenerative gas pulse tube refrigerator, a GM pulse tube or a Stirling refrigerator, and is provided with an air reservoir with small adjusting holes.
Description
Invention field
The invention belongs to refrigeration and cryogenic technique field, particularly a kind of low-temp refrigerator with inverse gas circulation that does not have regenerator.
Background technology
For the conventional gas philip refrigerator (as pulse tube refrigerating machine, the G-M refrigeration machine, sterlin refrigerator), most important parts are regenerators, it is made up of the porous media solid packing with high specific heat capacity and lower resistance coefficient, and filler can be fine metal mesh (stainless steel, a phosphor bronze etc.), small metal ball or particle, compositions such as magnetic material.In the process of the one-period work of refrigeration machine, being stored in the regenerator of the cold part that gas working medium produces in exhaust expansion half period process is used for the high pressure-temperature gas working medium that precooling comes from compressor; In other half period, the heat that produces in the gas working medium inflation compression process also part is stored in this regenerator.Because the heat absorption and the exothermic process that circulate in the course of work of gas working medium are all finished in regenerator, so the height of conventional gas regenerative refrigerating engine efficiency depends on the thermal efficiency of regenerator, thereby require gas working medium various losses of motion process in regenerator as much as possible little: the resistance coefficient of (1) regenerator matrix is little, make that gas working medium flow process resistance therein is little, pressure drop is little, requires the regenerator matrix voidage big for this reason; (2) the ratio heat exchange area of regenerator matrix is big, and radially thermal conductivity factor is big, to strengthen the heat exchange amount between gas working medium and the regenerator matrix, requires the voidage of regenerator matrix little for this reason; (3) specific heat capacity of regenerator matrix wants big, makes that the cold-storage ability of regenerator matrix is big; (4) the axial thermal conductivity coefficient of regenerator matrix is little, to reduce the axial thermal conductivity loss.And these requirements are mutual contradiction, thereby very high to the actual design requirement of regenerator, cause the size of existing regenerator big, and complex structure involves great expense, the long-term work decrease in efficiency.
Summary of the invention
The objective of the invention is to, overcome the shortcoming that the conventional gas regenerating type low-temperature refrigerator adopts baroque regenerator, proposed a kind of low-temp refrigerator with inverse gas circulation that does not have regenerator.
Embodiment of the present invention are as follows:
The low-temp refrigerator with inverse gas circulation of no regenerator provided by the invention, it is characterized in that, comprise that two identical in structure do not have the sub-refrigeration machine and the high performance counter current heat exchanger of regenerator, the cold junction that these two identical in structure do not have the sub-refrigeration machine of regenerator is connected in parallel on the cold junction of high performance counter current heat exchanger, the main channel of high performance counter current heat exchanger is made up of 2N group subchannel, and N is the positive integer of 1-4; The sub-refrigeration machine that described two identical in structure do not have regenerator is conventional back-heating type gas pulses pipe refrigeration machine, GM pulse tube or sterlin refrigerator; The sub-refrigeration machine hot junction that described two identical in structure do not have regenerator has adjusting aperture and air reservoir.
During work, the gas working medium that these two identical in structure do not have in the sub-refrigeration machine of regenerator operates in antiphase (180 ° of phase differences) working condition constantly, in contra-flow heat exchanger, when on a direction, moving in the passage of the gas working medium in one of them sub-refrigeration machine at contra-flow heat exchanger and absorbing (emitting) heat, gas working medium in another sub-refrigeration machine moves in the opposite direction in another passage of contra-flow heat exchanger and emits (absorption) heat, otherwise still.The heat transmission is to be undertaken by the partition between contra-flow heat exchanger two passages, thereby has constituted the low-temp refrigerator with inverse gas circulation of no regenerator of the present invention.
The low-temp refrigerator with inverse gas circulation of no regenerator provided by the invention replaces baroque regenerator in two sub-refrigeration machines with a high performance counter current heat exchanger, and is simple in structure, compactness, reliability and refrigerating efficiency height.
Description of drawings
Further describe the present invention below in conjunction with drawings and Examples:
Accompanying drawing 1 is a structural representation of the present invention;
Accompanying drawing 2 is the energy balance schematic diagram of contra-flow heat exchanger of the present invention;
Accompanying drawing 3 (A) is the variations in temperature schematic diagram in any infinitesimal particle course of work of contra-flow heat exchanger channel interior of the present invention;
Accompanying drawing 3 (B) is any infinitesimal particle actual motion track schematic diagram of contra-flow heat exchanger channel interior.
Wherein: compressor 1 connecting pipe 2 rotary valve systems 3
Metal hose 4 contra-flow heat exchangers 5 sub-refrigeration machines 61,62
Aperture 7 air reservoirs 8 contra-flow heat exchanger total length L
The temperature T of contra-flow heat exchanger hot junction gas working medium
H1, T
H2
The temperature T of contra-flow heat exchanger cold junction gas working medium
L1, T
L2
The enthalpy stream H of contra-flow heat exchanger hot junction gas working medium
H1, H
H2
The enthalpy stream H of contra-flow heat exchanger cold junction gas working medium
L1, H
L2
The entropy flow S of contra-flow heat exchanger hot junction gas working medium
H1, S
H2
The entropy flow S of contra-flow heat exchanger cold junction gas working medium
L1, S
L2
The heat conduction Q of contra-flow heat exchanger hot junction gas working medium
CH1, Q
CH2
The heat conduction Q of contra-flow heat exchanger cold junction gas working medium
CL1, Q
CL2
Heat exchange amount Qe between the contra-flow heat exchanger two main channel gas working mediums
The mean temperature T in contra-flow heat exchanger hot junction
H, T
L
Length coordinate L temperature T
The temperature T of arbitrary moment gas working medium
G1, T
G1
Temperature difference dT between arbitrary two gas infinitesimals
g
Contra-flow heat exchanger total moisture content gradient delta T
HL
Infinitesimal thermograde dT between arbitrary two gas infinitesimals
Adiabatic compression process a-b, a-b ' adiabatic expansion process c-d, c-d '
Isobaric exothermic process b-c, b '-c ' isobaric heat absorption process d-a
Gas infinitesimal one-period thermodynamic cycle process a-b-c-d, a-b '-c '-d
Solid line SX is the variations in temperature schematic diagram when two sub-refrigeration machines 61,62 operate in the same-phase course of work;
Dotted line XX is the variations in temperature schematic diagram when two sub-refrigeration machines 61,62 operate in the antiphase course of work.
The specific embodiment
As shown in Figure 1, provided by the invention a kind of low-temp refrigerator with inverse gas circulation that does not have regenerator, comprise that two identical in structure do not have the sub-refrigeration machine 61,61 and the high performance counter current heat exchanger 5 of regenerator, these two identical in structure do not have the sub-refrigeration machine 61 of regenerator and the cold junction that 62 cold junction is connected in parallel on high performance counter current heat exchanger 5, the main channel of high performance counter current heat exchanger 5 is made up of 2N group subchannel, and N is the positive integer of 1-4; The sub-refrigeration machine 61 and 62 that described two identical in structure do not have regenerator is conventional back-heating type gas pulses pipe refrigeration machine, GM pulse tube refrigerating machine or sterlin refrigerator; Described two identical in structure do not have the sub-refrigeration machine 61 of regenerator and 62 hot junction has adjusting aperture 7 and air reservoir 8.
Among the embodiment of the low-temp refrigerator with inverse gas circulation of no regenerator shown in Figure 1, its structure is: compressor 1 is formed high pressure and low pressure air supply system through two connecting pipes 2 and a rotary valve 3, this system links to each other with contra-flow heat exchanger 5 by the metal hose 4 of two long 1-4 rice, the main channel of contra-flow heat exchanger 5 is made up of 2N group subchannel, N is the positive integer of 1-4, in the present embodiment, its main channel is made of 2 groups of passages; The sub-refrigeration machine 61 of two identical no regenerators and 62 two main channels by contra-flow heat exchanger 5 are connected with the high pressure and the low-pressure admission hole of rotary valve 3 respectively.In the course of work of one-period, compressor 1 is connected with the high pressure and the low-pressure admission hole of rotary valve 3 respectively, so the gas working medium in two sub-refrigeration machines 61 and 62 operates in antiphase (180 ° of phase differences) working condition at any time, promptly working as one of them sub-refrigeration machine is operated in the exhaust expansion process, another sub-refrigeration machine then is operated in the inflation compression process, otherwise still.Provided gas working medium direction of motion arrow in two passages of this contra-flow heat exchanger 5 in half period among Fig. 1, gas working medium direction of motion arrow is opposite in other half period.When two sub-refrigeration machines 61 and 62 were conventional pulse tube refrigerating machine, can also there be the aperture 7 and the air reservoir 8 of control phase in their hot junction.Equally, gas working medium in two main channels of the contra-flow heat exchanger 5 that links to each other with 62 with two sub-refrigeration machines 61 respectively, at any time also operate in antiphase (180 ° of phase differences) working condition, promptly when motion and when absorbing (emitting) heat on a direction in wherein one group of passage of the gas working medium in one of them refrigeration machine at contra-flow heat exchanger 5, gas working medium in another refrigeration machine moves in the opposite direction in another passage of contra-flow heat exchanger and emits heat (absorption), otherwise still.The heat transmission is to be undertaken by the partition between these contra-flow heat exchanger two passages.
Fig. 2 is the energy balance schematic diagram of the contra-flow heat exchanger 5 among the present invention.Here, we illustrate that by the energy balance of analyzing contra-flow heat exchanger 5 inside it can produce refrigeration effect, promptly produces thermograde.If the contra-flow heat exchanger total length is L, axially get coordinate along this contra-flow heat exchanger, the end that contra-flow heat exchanger 5 links to each other with rotary valve 3 is defined as: l=0, the other end, promptly an end that links to each other with sub-refrigeration machine is: l=L, as shown in Figure 2.By thermodynamic analysis, we obtain axially can producing Δ T along contra-flow heat exchanger 5
HL=T
H-T
LTemperature echelon:
T wherein
H, T
LBe respectively the mean temperature of contra-flow heat exchanger 5 two ends (l=0 and l=L), t is the time, t
cBe the cycle, F is a heat exchange area, α
hBe the coefficient of heat transfer between gas and the countercurrent flow modulator material, k
ReAxial thermal conductivity coefficient for the countercurrent flow modulator material.Therefore, in order to obtain the big Δ T of temperature echelon
HL, promptly obtaining lower cryogenic temperature, the contra-flow heat exchanger that is adopted should have bigger ratio heat exchange area, bigger radially thermal conductivity factor, less axial thermal conductivity coefficient, this contra-flow heat exchanger should have less empty volume and pressure drop simultaneously.
Fig. 3 is the variations in temperature schematic diagram in any gas infinitesimal particle of contra-flow heat exchanger channel interior (the claiming the first gas infinitesimal particle) course of work in the wood invention.Solid line is represented the variations in temperature of the first gas infinitesimal particle when two sub-refrigeration machines 61 and 62 operate in the same-phase working condition among the figure: dotted line is represented the variations in temperature of the first gas infinitesimal particle when operating in antiphase (180 ° of phase differences) working condition in two sub-refrigeration machines 61 and 62.
To describe in detail in the present invention below, the motion process of contra-flow heat exchanger channel interior gas working medium reaches how to produce axial-temperature gradient Δ T
HL=T
H-T
L.(we are called passage TD1 in a main channel of consideration contra-flow heat exchanger 5, then another passage is TD2) the inner first gas infinitesimal particle is with the periodic swinging process of pressure, two adiabatic compression of its experience and expansion process (curve a-b, c-d), two isobaric heat transfer process (curve b-c, d-a), for the sake of simplicity, we consider the square type digital process (curve a-b-c-d) shown in Fig. 3 (A), rather than actual continuous process [as Fig. 3 (B)].In the inflation compression process, this first gas infinitesimal particle along passage TD1 axially from initial position towards the L end motion, its temperature raise (curve a-b); In the exhaust expansion process, this first gas infinitesimal particle moves towards initial position, its temperature decline (curve c-d).The variation of the mean temperature of this first gas infinitesimal particle can be used curve (curve a-c) expression in one-period.If operate in the same-phase working condition at any time in two sub-refrigeration machines 61 and 62, then (curve b-c) process liberated heat should equal the heat that (curve d-a) process absorbs, then the mean temperature of this first gas infinitesimal particle is changed to zero in one-period, gas working medium is temperature-resistant, remains on original state (shown in the solid line SX among Fig. 3).
When operating in antiphase (180 ° of phase differences) working condition in two sub-refrigeration machines 61 and 62, in the inflation compression process, this first gas infinitesimal particle along passage TD1 axially from initial position towards the L end motion, its temperature raise (curve a-b); Because the Working medium gas of passage TD1 and passage TD2 inside operates in the antiphase duty constantly, so passage TD2 inside corresponds to another gas infinitesimal particle (the second gas infinitesimal particle) of this first gas infinitesimal particle and just is being operated in the exhaust expansion process, its temperature is lower than the temperature of this first gas infinitesimal particle.That is to say between the first gas infinitesimal particle and the second gas infinitesimal particle d is arranged
Tg=T
G1-T
G2Temperature difference.According to principle of energy balance, the first gas infinitesimal particle in the passage TD1 will be by the cooling of the second gas infinitesimal particle among the passage TD2, and its temperature can reduce (curve b-b ').The heat transmission is to be undertaken by the partition between these contra-flow heat exchanger two main channels, and transmission capacity equals to operate in two passages enthalpy difference of working gas under the different pressures.So in the inflation compression process, the thermodynamic process that the first gas infinitesimal particle is experienced is curve a-b ', rather than curve a-b.Should be with two sub-refrigerator operations identical during in the same-phase duty at heat that isobaric heat transfer process discharged, because the merit that compressor is done is identical.So press heat transfer process waiting, the thermodynamic process of the first gas infinitesimal particle is curve b '-c ', rather than curve b-c.
In the exhaust expansion process, the first gas infinitesimal particle axially moves towards initial position along passage TD1's, its temperature (curve c '-d) that further descends; Because it is duty that the Working medium gas of passage TD1 and passage TD2 inside operates in anti-phase constantly,, passage TD2 inside just is being operated in the inflation compression process so corresponding to the second gas infinitesimal particle of the first gas infinitesimal particle.According to principle of energy balance, the first gas infinitesimal particle in the passage TD1 absorbs heat with the second gas infinitesimal particle from passage TD2, the heat that absorbs is identical with curve b-b ' process liberated heat, and then the temperature of the first gas infinitesimal particle can arrive poised state.
At last, in the isobaric heat absorption process, according to the energy conservation principle, the heat that is absorbed heat should equal curve b '-c ', the heat that process discharged, thus get back to initial position.This just means that the thermodynamic process that the first gas infinitesimal particle is experienced is curve a-b '-c '-d '-a, rather than curve a-b-c-d-a when operating in the antiphase working condition in two sub-refrigeration machines 61 and 62.Promptly the variation of the mean temperature of this first gas infinitesimal particle is curve curve a-c ' in one-period, rather than curve a-c, thereby produces a small thermograde dT vertically.The gas infinitesimal particle that in the passage of contra-flow heat exchanger 5, has the countless first gas infinitesimal particles equally to move, the similar motion process of they experience, each gas infinitesimal particle all transmits an infinitesimal energy in one-period, produce a small thermograde dT, total effect of all gas infinitesimal particles will obtain the bigger Δ T of temperature echelon
HL=T
H-T
L, shown in the dotted line XX of Fig. 3 (A).
Claims (3)
1. low-temp refrigerator with inverse gas circulation that does not have regenerator, it is characterized in that, comprise that two identical in structure do not have the sub-refrigeration machine and the high performance counter current heat exchanger of regenerator, the cold junction that these two identical in structure do not have the sub-refrigeration machine of regenerator is connected in parallel on the cold junction of high performance counter current heat exchanger, the main channel of high performance counter current heat exchanger is made up of 2N group subchannel, and N is the positive integer of 1-4; One compressor is connected with the high pressure of a rotary valve and low-pressure admission hole respectively and forms high pressure and low pressure air supply system, this high pressure links to each other with the hot junction of high performance counter current heat exchanger by two metal hoses with the low pressure air supply system, in a work period process, gas working medium in two sub-refrigeration machines operates in the antiphase working condition: a sub-refrigeration machine is operated in the exhaust expansion process, and another sub-refrigeration machine then is operated in the inflation compression process; Equally, gas working medium in two main channels of the contra-flow heat exchanger that links to each other with two sub-refrigeration machines operates in the antiphase working condition respectively: the motion and absorbing on a direction in wherein one group of passage of contra-flow heat exchanger (5) of the gas working medium in refrigeration machine/when emitting heat, gas working medium in another refrigeration machine moves in the opposite direction in another passage of contra-flow heat exchanger and emits heat/absorption, otherwise still.
2. the low-temp refrigerator with inverse gas circulation of claims 1 described no regenerator, it is characterized in that the sub-refrigeration machine that described two identical in structure do not have regenerator is conventional back-heating type gas pulses pipe refrigeration machine, GM pulse tube refrigerating machine or sterlin refrigerator.
3. the low-temp refrigerator with inverse gas circulation of claims 1 described no regenerator is characterized in that, the sub-refrigeration machine that described two identical in structure do not have regenerator has regulates aperture and air reservoir.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB011090928A CN1140739C (en) | 2001-02-28 | 2001-02-28 | Low-temperature refrigerator with reversed-phase gas circulation and without heat regenerator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB011090928A CN1140739C (en) | 2001-02-28 | 2001-02-28 | Low-temperature refrigerator with reversed-phase gas circulation and without heat regenerator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1373335A CN1373335A (en) | 2002-10-09 |
| CN1140739C true CN1140739C (en) | 2004-03-03 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB011090928A Expired - Fee Related CN1140739C (en) | 2001-02-28 | 2001-02-28 | Low-temperature refrigerator with reversed-phase gas circulation and without heat regenerator |
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Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101749882B (en) * | 2009-12-25 | 2012-05-30 | 河北农业大学 | Sleeve motion type stirling refrigerating device |
| CN106595140B (en) * | 2017-01-19 | 2018-05-22 | 中国科学院理化技术研究所 | Two-way phase adjustable valve, pulse tube expander |
| CN110726265B (en) * | 2019-10-17 | 2021-11-19 | 上海理工大学 | Pulse tube refrigerator and hydrogen supply refrigerating system of fuel cell automobile |
| CN114427982A (en) * | 2021-12-08 | 2022-05-03 | 兰州空间技术物理研究所 | Performance testing device for single-stage G-M refrigerator heat regenerator |
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| CN1373335A (en) | 2002-10-09 |
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According to article 9 of the patent law and article 13 of the detailed rules for the implementation of the patent law: 1109092.8 of the invention patents in this issue as a notice of authorization, and at the same time corresponding to the 1204596.9 utility model patent to be given up, and in the 20 volume of the 9 issue of the new type of communique on the patent right to abandon the announcement. |
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