CN104697222A - Cloud server low-temperature test system with high heat productivity - Google Patents
Cloud server low-temperature test system with high heat productivity Download PDFInfo
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- CN104697222A CN104697222A CN201510099068.4A CN201510099068A CN104697222A CN 104697222 A CN104697222 A CN 104697222A CN 201510099068 A CN201510099068 A CN 201510099068A CN 104697222 A CN104697222 A CN 104697222A
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- 238000012360 testing method Methods 0.000 title claims abstract description 33
- 239000003507 refrigerant Substances 0.000 claims abstract description 4
- 238000005057 refrigeration Methods 0.000 claims description 25
- 238000004134 energy conservation Methods 0.000 abstract description 2
- 238000010438 heat treatment Methods 0.000 description 10
- 230000003068 static effect Effects 0.000 description 8
- 238000001816 cooling Methods 0.000 description 5
- 125000004122 cyclic group Chemical group 0.000 description 5
- 238000013461 design Methods 0.000 description 5
- 238000000034 method Methods 0.000 description 5
- 238000005516 engineering process Methods 0.000 description 4
- 238000001704 evaporation Methods 0.000 description 4
- 238000009833 condensation Methods 0.000 description 3
- 230000005494 condensation Effects 0.000 description 3
- 239000012774 insulation material Substances 0.000 description 3
- 238000012546 transfer Methods 0.000 description 3
- 238000013401 experimental design Methods 0.000 description 2
- 238000009413 insulation Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 238000004806 packaging method and process Methods 0.000 description 2
- 238000012856 packing Methods 0.000 description 2
- 230000005855 radiation Effects 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000007797 corrosion Effects 0.000 description 1
- 238000005260 corrosion Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 238000006116 polymerization reaction Methods 0.000 description 1
- 229920002635 polyurethane Polymers 0.000 description 1
- 239000004814 polyurethane Substances 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 238000010200 validation analysis Methods 0.000 description 1
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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Air Conditioning Control Device (AREA)
Abstract
The invention particularly relates to a cloud server low-temperature test system with high calorific value. The cloud server low-temperature test system with high calorific value adopts two semi-closed compressors, wherein one compressor is a 6-cylinder compressor, and the other compressor is a 4-cylinder compressor; when the temperature of the working chamber is above 0 ℃, only the 6-cylinder compressor works, and when the temperature of the working chamber is below 0 ℃, the two compressors work simultaneously; when the working chamber carries out the damp-heat test, only the 6-cylinder compressor is started to carry out the alternating or constant damp-heat test; when the working chamber is at constant temperature, the refrigerating capacity is adjusted by controlling the amount of refrigerant flowing through the heat exchanger and the unloading adjustment of the compressor. The cloud server low-temperature test system with high calorific value adopts the closed compressors of the two compressors with asymmetric refrigerating power to work in a cooperative manner, so that great energy conservation is realized during the test; in addition, the high and low temperature alternating damp and hot test requirement of the maximum 30KW heat productivity of the cloud server is met.
Description
Technical field
The present invention relates to computer testing technology field, particularly a kind of Cloud Server low-temperature test system of golf calorific value.
Background technology
Along with the fast development of cloud computing technology, Cloud Server arises at the historic moment.Cloud Server achieves the modularization of calculating, storage, network by hardware polymerization, the centralization of heat radiation, power supply, management.Based on the architecture of Cloud Server, rich and varied node and configuration can be designed.Therefore, Cloud Server has the feature that bulk density is high, storage density is high, volume is large, caloric value is large.In order to the heat dissipation design of scientific validation Cloud Server, design one is needed to meet the high/low temperature cyclic damp heat test room of the Cloud Server of golf calorific value.
Cloud Server is whole machine cabinet integrated design, and contain the rack of 42U height, redundancy AC power supply, radiator fan module, 32 server nodes, 3 48 mouthfuls of Ethernet switches etc., the appearance and size of Cloud Server is larger.
Cloud Server is not with size during external packing:
600 mm W(are wide) × 1200 mm D(are dark) × 2500mm H(is high)
The size during external packing of Cloud Server band:
1000 mm W(are wide) × 1400 mm D(are dark) × 2550mm H(is high)
Single server maximum load power is 15KW, places two-server simultaneously, amounts to 30KW.30KW is for electric loading, and 100% for heating, i.e. the caloric value of 30KW.
Server node in rack takes horizontal positioned, and cold wind is from anterior air intake, and through the CPU, internal memory, hard disk, mainboard etc. of heating, hot blast is from rear portion air-out.In order to meet the heat radiation needs of Cloud Server node, Cloud Server is configured with fan and carries out air-cooled.Often overlap the fan of Cloud Server maximum configured 33 140mm x 140mm x 38mm specifications, air circulation be greater than 20400CMH(cubic meter per time).
Cloud Server volume is large, and caloric value is large, and wind flow is large, in order to carry out high/low temperature cyclic damp heat test to Cloud Server, need the operating room that design one is large-scale, 2500mm W(is wide) × 3000mm D(is dark) × 3000mm H(is high), two Cloud Servers can be put into simultaneously and test.
Based on this, the caloric value of the present invention to Cloud Server is analyzed and calculates, propose a kind of method for designing of the high/low temperature cyclic damp heat test room for golf calorific value Cloud Server product, can promote the use of in the experimental design of similar golf calorific value server product.
Summary of the invention
The present invention, in order to make up the defect of prior art, provides a kind of Cloud Server low-temperature test system of rationally effective golf calorific value.
The present invention is achieved through the following technical solutions:
A Cloud Server low-temperature test system for golf calorific value, is characterized in that: adopt two semi-closed compressors, and wherein one is 6 cylinder compressors, and another is 4 cylinder compressors; When operating room's temperature is more than 0 DEG C, only 6 cylinder compressor work, when operating room's temperature is below 0 DEG C, two compressors work simultaneously; Operating room only starts 6 cylinder compressors when carrying out damp heat test and carries out alternation or steady-state damp heat test; During operating room's constant temperature, the adjustment of refrigerating capacity adopts and controls amount and the compressor unloading adjustment that refrigerant flows through heat exchanger.
Described compressor is respectively HGX7/1620-4S, a R404A level, and power is about 6 cylinder compressors and HGX6/1240-4, a R23 level of 40P, and power is about 4 cylinder compressors of 25P.
Described 6 cylinder compressors, by increasing capacity adjusting valve, automatically regulate the air intake passage of close compressor cylinder, reduce the working quantity of compresser cylinder, reduce 2, can with the power match of 4 cylinder compressor cascade refrigeration relations.
The invention has the beneficial effects as follows: the Cloud Server low-temperature test system of this golf calorific value, adopt small one and large one two refrigeration work consumption asymmetrical compressor hermetic compressor collaborative work, achieve significantly energy-conservation at the trial; In addition, the high/low temperature cyclic damp heat test requirement of the maximum 30KW caloric value of Cloud Server is met.
Detailed description of the invention
In order to meet the thermocycling of Cloud Server, carrying out thermal technology's estimation according to experimental technique index request, then selecting corresponding compressor scheme to be solved.
The Cloud Server low-temperature test system of described golf calorific value, technical requirement is as follows:
1, operating room's size: 2.5m × 3m × 3m (W × D × H)=22.5m3;
2, temperature range :-50 ~ 80 DEG C;
3, humidity range: 10 ~ 98%;
4, load characteristic: 3200kg time static; During duty, 3000kg, 30kw heating exports;
5, heating and cooling require:
1) static: 3200kg(is divided into two kinds of situations: 1. do not start shooting, without packaging; 2. do not start shooting, have complete cardboard pallet packaging).
Temperature fall time requires:
From 25 DEG C ~-40 DEG C about 65min;
From 70 DEG C ~-40 DEG C about 110min.
Heating-up time requires:
From 25 DEG C ~ 70 DEG C about 40min;
From-40 DEG C ~ 70 DEG C about 70min.
Duty: 3000kg; Maximum 30kw caloric value is had to export.
Temperature fall time requires:
From 25 DEG C ~ 0 DEG C about 30min;
From 55 DEG C ~ 0 DEG C about 60min.
Heating-up time requires:
From 25 DEG C ~ 55 DEG C about 20min;
From 0 DEG C ~ 55 DEG C about 40min.
Refrigeration work consumption needed for laboratory mainly should be able to meet following requirement, that is:
Under 3200Kg static load, be down to-40 DEG C from 70 DEG C, average rate of temperature fall about 1 DEG C/min;
3000Kg load, under 30kw caloric value condition, is down to 0 DEG C from 55 DEG C, average rate of temperature fall about 1 DEG C/min;
Selected compressor is if meet above refrigeration work consumption situation, then run be less than the experimental condition of above condition at other severity under, press selected by it all can meet, and temperature fall time also can shorten.
Below refrigeration work consumption needed for above-mentioned technical requirement:
(1) 3200kg static load, is down to-40 DEG C from 70 DEG C, average rate of temperature fall about 1 DEG C/min.
1, heat power:
1), heat transfer is gone along with sb. to guard him: with hard polyurethane foamed board (the inner surface corrosion resistant plate δ 1 of δ 100; Outer surface plate δ 1) Coefficient K gets 0.03W/m2 DEG C:
q1＝k1 F1(T1－T2)*η1＝0.03×54×(70＋40)×1.1≈196w
In formula: 1.1 is coefficient, consider leakage heat and the other factors of building enclosure;
K1--heat transfer coefficient, when wallboard is thick be 100mm thick time, K ≈ 0.03W/m2 DEG C, and approximate to get each K value identical.
The heat transfer area of F1--building enclosure is about 54m2
T1=70℃
T2=-40℃
1), observation window: observation window area F2=0.4 × 0.5=0.2m2, k2 gets 3W/m2 DEG C; 2 fan observation windows:
q2＝2×k2 F2(T1－T2)＝2×3×0.2×(70＋40)＝132w
2), observation window frost prevention heater:
Get q3=300W
2), blower fan heating: consider 6 centrifugal blowers, general power is 9000w
q4＝η·N＝ 9000×0.75＝6750w
3), doorframe heater:
Get q5=1500W
Total heat power Σ q1=q1+q2+q3+q4+q5=11128w
2, heat load:
1), room air Q1 is tested:
Q1＝G1 C1(T1－T2)＝26.76×1.29×1.005×(70＋40)＝3816kj
In formula, G1 is air weight (kg), C1 is that air specific heat equals 1.005KJ/Kg DEG C
The density of air is approximately 1.29 kilograms every cubic metre
2), heat-insulation layer Q2:
Q2＝G 2·C2(T1－T2)/2
＝5.72×0.837×39×(70＋40)/2＝10270kj
In formula, G2 is insulation material weight (heavy 39kg/m3, Ku Ban producer of trying to please provides).C2 is the specific heat of insulation material, and its value equals 0.837 KJ/Kg DEG C, considers that insulation material temperature is interior low, outer height, and its variations in temperature is approximate presses Δ T/2 and calculate.
3), inner bag, aerofoil Q3:
Q3＝G 3·c3 ·(T1－T2) ＝84×1×7.85×0.5×(70＋40)＝36267kj
In formula, G3 is laboratory's inner bag and aerofoil weight sum, and C3 is specific heat, gets 0.5 KJ/Kg DEG C.
4), evaporimeter, blower fan Q4:
Q4＝G 4·C4(T1－T2) ＝300×0.6×110＝19800kj
In formula, G4 is evaporimeter, blower fan weight sum, and C4 is avergae specific heat, gets 0.6 KJ/Kg DEG C.
5), test product Q5:
Q5＝G 5·C5(T1－T2) ·η5 ＝2×1600×0.55×(70＋40)×0.7＝135524kj
In formula: G 5 is test product weight 3200Kg; C5 is specific heat, and because of the compositing characteristic of support materials, wherein steel are main component, therefore to get this coefficient be 0.55KJ/Kg DEG C.η 5 is coefficient, when considering that in case, air themperature is down to-40 DEG C, load temperature change by show and in lag behind air themperature, therefore-40 DEG C of calculating are down to by the approximate material having 70% by load.
Band heat-carrying load Σ Q1=Q1+Q2+Q3+Q4+Q5=205677kj
3, refrigeration work consumption is needed:
3.2 tons of static load temperature are down to-40 DEG C (the average 1 DEG C/min of rate of temperature fall) required refrigeration work consumption from 70 DEG C and are: W1=N1+ Σ q1.
N1＝ΣQ1/T＝(205677×1000)/｛3600×（70＋40）/60｝≈31kw
W1=N1＋Σq1=31kw＋11kw≈42kw
By obtaining above: 3.2T static load temperature is down to-40 DEG C (the average 1 DEG C/min of rate of temperature fall) from 70 DEG C, compressor should be selected provide when evaporating temperature-50 DEG C, condensation temperature 0 DEG C the refrigeration work consumption being greater than 42kw.
(2) 3000kg load, heating power outputs 30kw, be down to 0 DEG C from 55 DEG C, average rate of temperature fall about 1 DEG C/min.
1, heat power Σ q2=11128w+30000w=41128w
2, heat load:
A, room air Q1 '=26.76 × 1.29 × 1.005 × 55=1908kj
B, heat-insulation layer Q2 '=5.72 × 39 × 0.837 × 55/2=5135kj
C, inner bag and aerofoil Q3 '=84 × 1 × 7.85 × 0.5 × 55=18134kj
D, evaporimeter Q4 '=300 × 0.6 × 55=9900kj
E, load Q5 '=3000 × 0.55 × 55 × 0.7=63525kj
ΣQ2=Q1′＋Q2′＋Q3′＋Q4′＋Q5′=98602kj
3, required refrigeration work consumption:
3000Kg load, heating power outputs 30kw, be down to 0 DEG C from 55 DEG C, and average rate of temperature fall about 1 DEG C/min is W2=N2+ Σ q2.
N2＝ΣQ2/T＝(98602×1000)/｛3600×（55）/60｝≈30kw
W2=N2＋Σq2=30kw＋41128w≈71kw
By obtaining above: 3000Kg load, heating power outputs 30kw, be down to 0 DEG C (the average 1 DEG C/min of rate of temperature fall) from 55 DEG C, compressor should be selected provide when evaporating temperature-10 DEG C, condensation temperature 35 DEG C the refrigeration work consumption being greater than 71kw.
(3) refrigeration modes is selected.
1, because the most low energy of laboratory work temperature requirement is to-50 DEG C, namely the evaporating temperature of refrigeration system at-60 ~-57 DEG C, therefore should adopt cascade refrigeration mode.
1), the choosing (consideration is loaded into-40 DEG C) of cooling condition:
Getting R404A level operating mode is 35 DEG C/-10 DEG C;
Getting R23 level operating mode is 0 DEG C/-50 DEG C.
2), compressor is chosen according to above refrigeration work consumption:
Select R23 level V1=W1/391=42000/391=107.4m3/h
Look into BOCK and select handbook
HGX6/1240-4 model, 25P, 4 cylinder compressors meet the demands (capacity V1 '=107.6m3/h).
W1 '=391V1 '=391 × 107.6 ≈ 42.1kw(can select)
Condenser/evaporator heat load power (being set to W3)
W3=450V1=107.4×450=48150w≈48.3kw
Select R404A stage compressor
V2=W2/502 makes V2=V1 obtain
W2 '=107.6 × 502 ≈ 54kw>W3=48.2kw(and R404A stage compressor can be identical with R23 stage compressor).
In formula: V1, V2 be capacity (being respectively R23, R404A level) needed for compressor; The refrigeration work consumption (being respectively R23, R404A level) that W1 ', W2 ' are selected press; 391,450,502 is that the multiple-factor of low form press under operating mode determination condition derives coefficient, and described coefficient comprises bulk coefficient λ, specific volume υ and enthalpy h.
Conclusion: select HGX6/1240-4 model, 25P, 4 cylinder compressor 2 composition folding type cooling system can meet 3.2T static load temperature and be down to-40 DEG C from+70 DEG C, rate of temperature fall average 1 DEG C/min requirement.
2, as adopted folding type cooling system to provide refrigeration to above operating mode (0 DEG C of operating mode), the first order (R404A level) load will be very large, and compressor operating, at pole badness, has serious impact to performance and used life.
2), 3000Kg load, heating power outputs 30kw, 0 DEG C is down to from 55 DEG C, average rate of temperature fall about 1 DEG C/min, the actual refrigeration work consumption of needs is 71kw, and HGX6/1240-4 model, 25P, 4 cylinder compressors are actual can only provide 391V1 '=107.6 × 391=42kw.
2) if provide refrigeration with folding type cooling system to above operating mode (0 DEG C of operating mode), the first order (R404A level) load will be very large, and compressor operating, at pole badness, has serious impact to performance and used life.
(4) explanation is realized.
3.2 tons of static load temperature are down to-40 DEG C from 70 DEG C, and the average 1 DEG C/min of rate of temperature fall adopts cascade refrigeration; 3000Kg load, heating power outputs 30kw, be down to 0 DEG C from 55 DEG C, and average rate of temperature fall about 1 DEG C/min and damp and hot pattern adopt single-stage work.Namely less than 0 DEG C is 2 compressor cascade refrigeration working methods, and more than 0 DEG C temperature and damp and hot pattern be 1 compressor single-stage working method only, by the working method of program according to operating temperature automatic switchover compressor.
71kw refrigeration work consumption can be needed to reselect R404A stage compressor according to 0 DEG C of operating mode, and make it work independently, namely adopt multi-evaporator system, first evaporator, second level evaporimeter, dehumidifying evaporimeter are independent of one another.
Look into BOCK and select handbook, HGX7/1620-4S model, 40P, 6 cylinder compressors are condensation temperature 40 DEG C, and can provide 73.7kw refrigeration work consumption during evaporating temperature-10 DEG C, that is: W2 ' >W2(can select).
For energy-saving consumption-reducing, the employing of R404A stage compressor is installed capacity adjusting valve additional and is automatically regulated the power match with R23 stage compressor according to loading condition.By the air intake passage of automatic close compressor cylinder, reduce by 2 cylinder operation, thus reduce refrigerating capacity, reduce operation power consumption, meet the power match of R404A stage compressor and R23 stage compressor cascade refrigeration relation.
The present invention is by analyzing the caloric value of Cloud Server and calculating, propose a kind of method for designing of the thermocycling room for golf calorific value Cloud Server product, the high/low temperature cyclic damp heat test requirement of the maximum 30KW caloric value of Cloud Server can be met, can also promote the use of in the experimental design of similar golf calorific value server product.Specific design conclusion sees below.
The Cloud Server low-temperature test system of this golf calorific value, adopts two semi-closed compressors, and wherein one is 6 cylinder compressors, and another is 4 cylinder compressors; When operating room's temperature is more than 0 DEG C, only 6 cylinder compressor work, when operating room's temperature is below 0 DEG C, two compressors work simultaneously; Operating room only starts 6 cylinder compressors when carrying out damp heat test and carries out alternation or steady-state damp heat test; During operating room's constant temperature, the adjustment of refrigerating capacity adopts and controls amount and the compressor unloading adjustment that refrigerant flows through heat exchanger.
Described compressor is respectively HGX7/1620-4S, a R404A level, and power is about 6 cylinder compressors and HGX6/1240-4, a R23 level of 40P, and power is about 4 cylinder compressors of 25P.
Described 6 cylinder compressors, by increasing capacity adjusting valve, automatically regulate the air intake passage of close compressor cylinder, reduce the working quantity of compresser cylinder, reduce 2, can with the power match of 4 cylinder compressor cascade refrigeration relations.
Claims (3)
1. a Cloud Server low-temperature test system for golf calorific value, is characterized in that: adopt two semi-closed compressors, and wherein one is 6 cylinder compressors, and another is 4 cylinder compressors; When operating room's temperature is more than 0 DEG C, only 6 cylinder compressor work, when operating room's temperature is below 0 DEG C, two compressors work simultaneously; Operating room only starts 6 cylinder compressors when carrying out damp heat test and carries out alternation or steady-state damp heat test; During operating room's constant temperature, the adjustment of refrigerating capacity adopts and controls amount and the compressor unloading adjustment that refrigerant flows through heat exchanger.
2. the Cloud Server low-temperature test system of golf calorific value according to claim 1, it is characterized in that: described compressor is respectively HGX7/1620-4S, a R404A level, power is about 6 cylinder compressors and a HGX6/1240-4 of 40P, R23 level, power is about 4 cylinder compressors of 25P.
3. the Cloud Server low-temperature test system of golf calorific value according to claim 1 and 2, it is characterized in that: described 6 cylinder compressors are by increasing capacity adjusting valve, the air intake passage of automatic adjustment close compressor cylinder, reduce the working quantity of compresser cylinder, reduce 2, can with the power match of 4 cylinder compressor cascade refrigeration relations.
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Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4550574A (en) * | 1983-06-02 | 1985-11-05 | Sexton-Espec, Inc. | Refrigeration system with liquid bypass line |
| CN1188219A (en) * | 1996-12-02 | 1998-07-22 | 运载器有限公司 | Refrigeration system employing compressor for single or multi-stage operation with capacity control |
| CN1828185A (en) * | 2006-03-28 | 2006-09-06 | 王全龄 | Heat pump type air conditioner especially suitable for highly effective heating operation under low temperature |
| US7603871B2 (en) * | 2006-06-29 | 2009-10-20 | Test Enterprises, Inc. | High-flow cold air chiller |
| CN202420018U (en) * | 2012-01-13 | 2012-09-05 | 重庆市威尔试验仪器有限公司 | Energy-saving mixed cascade refrigeration system |
| CN103486754A (en) * | 2013-08-26 | 2014-01-01 | 安徽亿瑞深冷能源科技有限公司 | Energy-saving middle temperature refrigerant/middle temperature refrigerant cascade refrigeration system |
-
2015
- 2015-03-06 CN CN201510099068.4A patent/CN104697222A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4550574A (en) * | 1983-06-02 | 1985-11-05 | Sexton-Espec, Inc. | Refrigeration system with liquid bypass line |
| CN1188219A (en) * | 1996-12-02 | 1998-07-22 | 运载器有限公司 | Refrigeration system employing compressor for single or multi-stage operation with capacity control |
| CN1828185A (en) * | 2006-03-28 | 2006-09-06 | 王全龄 | Heat pump type air conditioner especially suitable for highly effective heating operation under low temperature |
| US7603871B2 (en) * | 2006-06-29 | 2009-10-20 | Test Enterprises, Inc. | High-flow cold air chiller |
| CN202420018U (en) * | 2012-01-13 | 2012-09-05 | 重庆市威尔试验仪器有限公司 | Energy-saving mixed cascade refrigeration system |
| CN103486754A (en) * | 2013-08-26 | 2014-01-01 | 安徽亿瑞深冷能源科技有限公司 | Energy-saving middle temperature refrigerant/middle temperature refrigerant cascade refrigeration system |
Non-Patent Citations (1)
| Title |
|---|
| 薄祥余: "大型环境试验箱制冷系统设计", 《装备制造技术》 * |
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Application publication date: 20150610 |