CN101128707A - Control system for refrigerating machine employing non-azeotropic refrigerant - Google Patents
Control system for refrigerating machine employing non-azeotropic refrigerant Download PDFInfo
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- CN101128707A CN101128707A CNA2006800061827A CN200680006182A CN101128707A CN 101128707 A CN101128707 A CN 101128707A CN A2006800061827 A CNA2006800061827 A CN A2006800061827A CN 200680006182 A CN200680006182 A CN 200680006182A CN 101128707 A CN101128707 A CN 101128707A
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- Prior art keywords
- refrigerant
- temperature
- evaporimeter
- pressure
- compressor
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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
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/006—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant containing more than one component
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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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator
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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
- F25B2500/00—Problems to be solved
- F25B2500/26—Problems to be solved characterised by the startup of the refrigeration cycle
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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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion valves
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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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2104—Temperatures of an indoor room or compartment
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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
- F25B40/00—Subcoolers, desuperheaters or superheaters
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Devices That Are Associated With Refrigeration Equipment (AREA)
Abstract
To improve the initial pulling-down performance of a refrigerating machine employing a non-azeotropic refrigerant immediately after starting when the chamber temperature is high. [MEANS FOR SOLVING PROBLEMS] A single-stage refrigerating machine which employs a non-azeotropic refrigerant and has a compressor (1), a condenser (2), and an evaporator (10), and in which heat exchange (3) is conducted between the refrigerant returned from the evaporator and the high-pressure refrigerant flowing from the condenser toward the evaporator is controlled in the following manner. When a high load is imposed as just after starting, capillary tubes (6-1) to (6-5) serving as expansion valves for the evaporator are made fully open with electromagnetic valves (5-1) to (5-5). As the internal temperature of the chamber declines, the tubes are successively closed. Thus, the pressure and flow amount of the refrigerant gas are regulated. When the internal temperature of the chamber is high and the condensation of a low-boiling ingredient does not proceed, the refrigerating ability of a high-boiling refrigerant can be exhibited in the highest degree.
Description
Technical field
The present invention is the relevant refrigeration system that has adopted non-vapor of mixture refrigerant, especially refer to the freezer class because larger, the normal operation that arrives till the freezer temperature of regulation usually needs bigger ability, or the discrepancy operation in collecting article in cold storage warehouse needs usually open the door greatly fan etc. and makes the big cataclysmal freezer refrigerator of storehouse temperature.
Background technology
The freezer of unlikely deterioration as for the freshness that still can keep meat or fish Jie class etc. through longer-term, though known have strong point that the freezer that can reach ultralow temperature below-50 ℃ is used to fishing port, grown place or item circulation etc., but these are as the refrigerator system that realizes ultralow temperature for a long time, to using boiling point to be made up with the refrigerator that uses the higher boiling refrigerant that under room temperature environment, moves at the refrigerator of the low boiling refrigerant in these fields, and the two-period form refrigerator system that forms by two compressors and condenser etc.
With respect to this, the inventor etc. once proposed by simple unistage type compressor realize by combination can realize the low boiling refrigerant of ultralow temperature and under room temperature environment condensable higher boiling refrigerant by non-azeotropic refrigerant the refrigerator system of ultralow temperature.(patent documentation 1)
In these ultralow temperature refrigerator systems, make in by the answer refrigerant gas that evaporimeter discharged in the low temperature and between the cold high pressure gas of evaporimeter, carry out heat exchange, carry out the condensation of the low boiling refrigerant in the cold high pressure gas by the heat of gasification of replying the higher boiling refrigerant in the refrigerant gas, establishment makes the condition that can finish in the circulation of the condensation of the non-azeotropic refrigerant of the front and back of evaporimeter and gasification, adopt the simple refrigeration system of the unistage type that the non-azeotropic refrigerant single compressed positive condenser identical with the situation that adopts single refrigerant or vapor of mixture refrigerant form, can realize ultralow temperature.
[patent documentation 1] TOHKEMY 11-99498 communique
The refrigerator system of the non-azeotropic refrigerant of this employing is applicable under the situation of so-called refrigerating box than low capacity etc., because thermal capacity is also less, textural general also with the form of switching above freezer of door leaf level, so when collecting article is being come in and gone out, make the ventilation of cold air in the storehouse also less, the change of storehouse temperature is also little, can keep more stable operating condition.
But, under the state that keeps whole piece yaito tuna class not dismember, collected, during keeping, as business with often having the storehouse content become big and the people enters the necessity of working in the storehouse, just become the freezer of thousands of liters of storehouse internal volumes, owing to these operations or keeping had carry out needing etc. of space distribution, open and close pattern so form the door leaf of erect type, performance boost when amplifying the activation that causes along with volume not only is being required, open and close or open these door leaf and carry out the discrepancy operation of collecting article when and the ventilation between outer gas also big, so the storage temperature that returns back to rapidly of the temperature that therefore needs to keep storehouse temperature and risen is being required, promote because of this reduction performance necessity.
But, if when wanting capacity with indivedual key elements of the refrigerator of compressor, condenser etc. to increase to give corresponding these performance boost, then be accompanied by the cost increase that the capacity of these equipment increases and not only become bigger burden, if when giving the condition when making frequent running, excessive capacity of equipment.
In addition, for the increase of these temporary transient loads, though can promote the output of compressor and give correspondence, relatively poor to these variations in temperature correspondence or retinue property, make can't bring into play corresponding to the cooling capacity of output.
Especially more frequent in the discrepancy of the collecting article of freezer, situation that the change of storehouse temperature is showing or the like can't return back to the temperature of stationary state rapidly, and the stable storehouse temperature that is hard to keep.
The inventor etc. adopt multiple discussion at its reason, find out it is caused by the intrinsic characteristic of following non-azeotropic refrigerant.
That is to say, ventilation is bigger when starting refrigerator or in the storehouse, and the situation that storehouse temperature significantly rises etc., though necessity of the cooling capacity of giving full play to refrigerator is arranged, but the state that the storehouse temperature till becoming the steady running state is higher, temperature in the answer refrigerant of heat exchanger is also higher, even make in the non-azeotropic refrigerant higher boiling refrigerant composition of condensation gasification and cooling high-pressure side refrigerant, also can't reduce temperature fully, and the low boiling refrigerant composition still is circulated in the refrigerator under uncooled state.Because of though this pressure that spues from compressor rises, and the condensation of no show low boiling point component, on the other hand, because the resistance of the pressure reducer of capillary etc. makes flow limited, so also limited from the heat release of condenser.
Though do not give condensation as the low boiling point component in this non-azeotropic refrigerant, but when being circulated in the refrigerator system to make under the original state that keeps gaseous state, also can till evaporimeter, make these low boiling point components remain on gaseous state by condenser even then be compressed to high pressure through heat exchanger with compressor, the load of compressor is bigger, though and because the overload running of compressor is risen pressure, as above-mentioned, because the thermal discharge from condensing gas does not increase, cooling capacity does not on the whole increase yet, and storehouse temperature does not reduce yet.That is to say, in these the cooling effect of transitional state, mainly be by due to the condensation/gasification of higher boiling composition, thus the internal circulating load of these refrigerants can't guarantee, by these and cooling capacity can't keep performance.
In these transitional state, low boiling point component remains on the state that is cooled to enough temperature that do not give, can't bring into play its ultralow temperature cooling capacity, even or the pressure that causes by the compressor also not condensation of rising, and all circulations of obstruction refrigerant, so that the increase of cooling capacity, the fixedly answer of operating condition.
Summary of the invention
The problem that solves is wanted in invention
In the unistage type refrigeration system that adopts non-azeotropic refrigerant, make when starting, low boiling point component when storehouse temperature rises etc. does not carry out the flow increase of the state refrigerant down of condensation, improving cooling capacity and storehouse temperature being reduced and suppress makes stable running become possibility to the load change between becoming till the fixing operating condition.
The means that solve problem and adopt
The present invention is a kind of refrigeration system that adopts non-vapor of mixture refrigerant, it is characterized in that by compressor, condenser, evaporimeter and come the answer refrigerant of self-evaporating steam and between the high pressure refrigerant of evaporimeter, carry out the unistage type refrigerator of the non-vapor of mixture refrigerant of employing of heat exchange by condenser, open degree by evaporator expansion valve makes pressure and the flow that can adjust cold media gas, when activating, or storehouse temperature is higher and the state that do not carry out the condensation of low boiling point component, the expansion valve of open evaporimeter and maintenance have cooperated the pressure of the condensing condition of higher boiling composition, promote the cooling capacity that the higher boiling composition causes, along with storehouse temperature is reduced, low boiling point component carries out condensation, by the expansion valve of tight lock evaporimeter and make the pressure of the condensing condition that satisfies low boiling point component in regular turn, make into fixedly operating condition.
Especially, it is characterized in that the expansion valve system plural number of aforementioned evaporation device in parallel capillary is set, carry out the control of above-mentioned flow by these switching number.
The effect of invention
If when of the present invention, in the unistage type refrigeration system that adopts non-azeotropic refrigerant, the operating temperature of the refrigeration system during activation or when storehouse temperature is rising etc. is higher, when the state entry into service by the condensation deficiency in the non-azeotropic refrigerant, can bring into play cooling capacity to greatest extent, make that to reduce storehouse temperature smoothly be possible till stationary state, and can reduce the load of the compressor of refrigeration system.
Description of drawings
Fig. 1 is the concept map of refrigeration system of the present invention.
Fig. 2 is the cooling velocity curve of the relation of expression number of capillaries and cooling velocity.
The primary clustering symbol description:
1 compressor
2 condensers
3 heat exchangers
5-1～5-5 magnetic valve
6-1～6-5 choke valve (capillary)
7 freezers
10 evaporimeters
11 temperature sensors
12 control device
The specific embodiment
The refrigerant that is used in refrigerator of the present invention is non-vapor of mixture refrigerant, especially the ultralow temperature below-50 ℃ for to reach, with low boiling refrigerant composition with the normal boiling point below-50 ℃ and environment condensation under room temperature, make heat release from condensing gas become combining of the lower higher boiling refrigerant of possible higher boiling and vapour pressure, in between the refrigerant of the low-temp low-pressure of compressor, carrying out heat exchange towards the refrigerant of the high-temperature high-pressure state of evaporimeter and by evaporimeter by condenser, cooling towards the high pressure refrigerant of boil-off gas to below the boiling point under this pressure, the gas running that compressor is sucked with the condition that more than the dew point of this pressure, heats.
Formation aspect in refrigerator, for reaching above-mentioned condition, form by compressor, condenser, throttling (decompression) valve, evaporimeter, compressor, between compressor and throttling (decompression) valve and evaporimeter and compressor, heat exchanger is set, though can reach above-mentioned heat exchange condition, but make the open degree that to adjust choke valve, the sensor of measuring storehouse temperature and the controlling organization of being adjusted the open degree of choke valve by the temperature of its detection are set.
When activating refrigerator, or because the discrepancy of freezer content makes storehouse temperature rise to certain value when above, open degree with this choke valve is a maximum, reduce corresponding to storehouse temperature, and lock the open degree of choke valve in regular turn and cold medium flux is reduced, storehouse temperature becomes assigned temperature when following, is minimum with the open degree of choke valve.
As for the choke valve of the cold coal of non-vapor of mixture, being suitable for the capillary that plural number is set in parallel is by the capillary that opens and closes these with magnetic valve in regular turn in response to storehouse temperature, the control cold medium flux.
[embodiment]
Below enumerate the refrigeration system summary and the various yardstick of the embodiment of the invention.
Fig. 1 is that the system of refrigerator of the present invention constitutes concept map, the cold media gas that is compressed for compressor 1 be with condenser 2 heat releases to atmosphere, via heat exchanger 3 and give difference and become 5, import capillary 6-1～6-5 and expansion by magnetic valve 5-1～5-5 through giving, gasification in the evaporimeter 10 that is disposed along the freezer inwall, cooling freezer 7.
In evaporimeter, in response to storehouse temperature, pressure, the higher boiling refrigerant composition of part is sent to heat exchanger at condensing state along with replying gas, mainly utilizes its gasification, and the refrigerant of cooling down high-temperature high pressure carries out the condensation of low boiling refrigerant composition.
Freezing storehouse temperature is to utilize temperature sensor 11 can give detection to go out, and in response to the temperature of utilizing control device 12 to set in advance, opens and closes the magnetic valve of 5-1～5-5, the number of capillaries of the conducting of control refrigerant.
When activating and the higher state of storehouse temperature more than certain, each magnetic valve all gives unlatching, makes the refrigerant conducting to all capillaries.
If storehouse temperature becomes fixing design temperature when above, then close magnetic valve in regular turn, be controlled in response to the refrigerant circulation of storehouse temperature and the compressor pressure that spues,, then only can give running with 1 in capillary if reach storehouse temperature in advance when giving the stationary state of setting.
The various yardsticks of actual machine, as follows.
Freezer structure: have the prefabricated structure of opening from the mediad left and right sides
Freezer internal volume: 4275 liters
Temperature commonly used: below-50 ℃, maximum-60 ℃
Refrigerant: enclose 4400 g of EP-53P and give use.The various characteristics that mixes the composition gas of refrigerant is as shown in table 1.The composition of non-azeotropic refrigerant EP-53P is to use HFC-23:40 weight %, HFC-134a:60 weight %.
The non-azeotropic refrigerant that table 1 has used is formed and its physical characteristic
| Chemical formula | Boiling point (℃, 1atm) | Critical-temperature (℃) | Critical pressure (abs) (MPa) | |
| HFC-23 | CHF 3 | -82.03 | 25.9 | 4.83 |
| HFC-134a | CH 2FCF 3 | -26.18 | 101.5 | 4.065 |
System in Fig. 1 constitutes, and the storehouse temperature variation when activating with 1 in capillary is shown in table 2.Storehouse temperature is to measure and get in the freezer epimere.The required time of the temperature till 34 ℃ of room temperatures arrive design temperature-50 ℃ is about 5 hours.
Operating condition (room temperature during 1 in table 2 capillary; 31～34 ℃)
| The duration of runs | Storehouse temperature (℃) | The compressor pressure (MPa) that spues | Compressor suction pressure (MPa) | Compressor spue temperature (℃) | The compressor inlet temperature (℃) | The heat exchanger entrance temperature (℃) | The heat exchanger outlet temperature (℃) |
| 0:00 | - | - | - | - | - | - | |
| 0:30 | 5.7 | 2.35 | 0.025 | 122.8 | 33.3 | 108.0 | |
| 1:00 | -8.4 | 2.42 | 0.050 | 134.2 | 32.8 | 116.0 | |
| 1:30 | -27.0 | 2.30 | 0.070 | 136.0 | 24.9 | 114.4 | -30.7 |
| 2:00 | -35.5 | 2.25 | 0.070 | 133.0 | 24.9 | 111.9 | -37.9 |
| 2:30 | 2.23 | 0.070 | - | ||||
| 3:00 | -44.6 | 2.20 | 0.060 | 120.0 | 9.6 | 107.0 | -42.0 |
| 3:30 | -47.2 | 1.95 | 0.050 | 118.0 | 5.8 | 107.0 | -43.6 |
| 4:00 | -48.5 | 1.95 | 0.040 | 119.0 | 5.1 | 103.0 | -44.4 |
| 4:30 | -49.1 | 1.90 | 0.040 | 118.0 | 5.0 | 104.0 | -44.1 |
| 5:00 | -50.2 | 1.95 | 0.040 | 118.0 | 5.1 | 104.0 | -44.4 |
Secondly, adopt the storehouse temperature variation of the embodiment of 4 in capillary to be shown in table 3.
Storehouse temperature lies in the freezer epimere and measures, in 4 capillary inversion temperatures: close magnetic valve in regular turn for 0 ℃ ,-10 ℃ ,-25 ℃, in respectively should below temperature province, 1 frequent ON of conduct of capillary is turned round.The results are shown in table 3.The required time that arrives the temperature till the design temperature-50 ℃ is about 4 hours.
Operating condition (room temperature when table 3 uses 4 in capillary; 31～33 ℃)
| The duration of runs | Storehouse temperature (℃) | The compressor pressure (MPa) that spues | Compressor suction pressure (MPa) | Compressor spue temperature (℃) | The compressor inlet temperature (℃) | The heat exchanger entrance temperature (℃) | The heat exchanger outlet temperature (℃) |
| 0:00 | |||||||
| 0:30 | -15.3 | 2.20 | 0.25 | 101.0 | -3.8 | 78.4 | -21.0 |
| 1:00 | -30.6 | 2.40 | 0.070 | 114.0 | 15.6 | 98.0 | -33.8 |
| 1:30 | -38.2 | 2.20 | 0.060 | 122.1 | 10.9 | 105.0 | -38.6 |
| 2:00 | -41.8 | 2.20 | 0.060 | 122.0 | 10.5 | 10.4 | -39.5 |
| 2:30 | -45.1 | 20.5 | 0.060 | 122.0 | 10.0 | 104.0 | -41.4 |
| 3:00 | -47.9 | 20.0 | 0.050 | 125.0 | 10.7 | 104.0 | -42.0 |
| 3:30 | -48.5 | 19.0 | 0.050 | 123.0 | 10.2 | 105.0 | -43.3 |
| 4:00 | -50.2 | 19.0 | 0.050 | 119.0 | 10.6 | 105.0 | -43.2 |
| 4:30 | -50.0 | 19.0 | 0.040 | 125.0 | 9.0 | 111.0 | -44.0 |
| 5:00 | -50.2 | 19.0 | 0.040 | 120.0 | 6.2 | 101.0 | -45.1 |
With above result for the storehouse temperature of the duration of runs being changed and being shown in Fig. 2.As shown in Figure 2, close capillary in regular turn in response to storehouse temperature and control the flow of refrigerant and during pressure with 4 in capillary, can regard as from room temperature rapid be cooled to storehouse temperature, the speed that comes into operation is very big.The very big thing of this speed that comes into operation is represented along with required time less till the fixedly operating temperature of-50 ℃ of arrival, and is extremely rapid to the response of temperature.
The variations in temperature of the design temperature that the discrepancy of the collecting article that undertaken by fixing operating condition is caused, storehouse temperature or in advance in the collecting article of freezing state in design temperature, gas encloses and the collecting article newly taken in promptly becomes the cooling object in the storehouse of the rising greatly by opening the ventilation effect that door leaf causes.Because of this, though the load for the cooling of being observed by thermal capacity is less, but the chilling temperature amplitude has bigger relation, make the fixing response utmost point refrigerator of the present invention rapidly system of operating temperature, to along with the variations in temperature of the collecting article discrepancy in this freezer etc. the fixing recovery rapidly (reset) of operating temperature is become possibility, also more suitable to the real attitude of the use of freezer.
Claims (2)
1. refrigerator system that has adopted non-vapor of mixture refrigerant, it is characterized in that by compressor, condenser, evaporimeter and come the answer refrigerant of flash-pot and between the high pressure refrigerant of evaporimeter, carry out the unistage type refrigerator of the non-vapor of mixture refrigerant of employing of heat exchange by condenser, open degree by the expansion valve of evaporimeter makes pressure and the flow that can adjust cold gas body, when activating, or storehouse temperature is higher and the state that do not carry out the condensation of low boiling point component, the expansion valve of open evaporimeter and maintenance have cooperated the pressure of the condensing condition of higher boiling composition, promote the cooling capacity that the higher boiling composition causes, along with storehouse temperature is reduced, low boiling point component carries out condensation, by the expansion valve of tight lock evaporimeter and make the pressure of the condensing condition that satisfies low boiling point component in regular turn, make into fixedly operating condition.
2. the refrigerator system that has adopted non-vapor of mixture refrigerant as claimed in claim 1, wherein the expansion valve of aforementioned evaporation device be plural number in parallel capillary is set, carry out the control of above-mentioned flow by these switching number.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP260151/2005 | 2005-09-08 | ||
| JP2005260151A JP2007071468A (en) | 2005-09-08 | 2005-09-08 | Refrigerating machine control system using zeotropic refrigerant |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101128707A true CN101128707A (en) | 2008-02-20 |
Family
ID=37835521
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2006800061827A Pending CN101128707A (en) | 2005-09-08 | 2006-06-14 | Control system for refrigerating machine employing non-azeotropic refrigerant |
Country Status (7)
| Country | Link |
|---|---|
| US (1) | US20080302116A1 (en) |
| EP (1) | EP1923645A4 (en) |
| JP (1) | JP2007071468A (en) |
| KR (1) | KR20080042035A (en) |
| CN (1) | CN101128707A (en) |
| TW (1) | TWI310827B (en) |
| WO (1) | WO2007029390A1 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105371546A (en) * | 2014-08-25 | 2016-03-02 | 谢德音 | Method capable of changing refrigerant evaporation flow and controlling refrigerant channels |
| CN113614467A (en) * | 2019-01-15 | 2021-11-05 | 马士基集装箱工业公司 | Method for calibrating saturation temperature of refrigerant in refrigeration system, controller and cooler applying same |
| CN114719471A (en) * | 2022-03-08 | 2022-07-08 | 澳柯玛股份有限公司 | Mixed refrigerant refrigerating system and refrigerating method |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2008035A4 (en) * | 2006-03-30 | 2013-01-23 | Carrier Corp | Transport refrigeration unit |
| IT1392820B1 (en) * | 2008-08-06 | 2012-03-23 | Dominici | DEVICE FOR CELL CULTURE |
| JP2010043758A (en) * | 2008-08-08 | 2010-02-25 | Fuji Electric Retail Systems Co Ltd | Cooling device |
| DE102011006174B4 (en) * | 2011-03-25 | 2014-07-24 | Bruker Biospin Ag | Refrigeration device with controllable evaporation temperature |
| EP2645018A3 (en) * | 2012-04-01 | 2017-08-23 | Liebherr-Hausgeräte Ochsenhausen GmbH | Refrigeration and/or freezer device |
| US8739567B2 (en) | 2012-06-08 | 2014-06-03 | General Electric Company | Dual evaporator refrigeration system using zeotropic refrigerant mixture |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5924161A (en) * | 1982-07-30 | 1984-02-07 | 三菱電機株式会社 | Freezing-refrigerator |
| JPS5984052A (en) * | 1982-11-05 | 1984-05-15 | 三菱重工業株式会社 | Method of controlling capability of refrigerator |
| US4580415A (en) * | 1983-04-22 | 1986-04-08 | Mitsubishi Denki Kabushiki Kaisha | Dual refrigerant cooling system |
| US4771610A (en) * | 1986-06-06 | 1988-09-20 | Mitsubishi Denki Kabushiki Kaisha | Multiroom air conditioner |
| JPH01200155A (en) * | 1988-02-03 | 1989-08-11 | Yazaki Corp | Method of controlling quantity of coolant and device used therefor |
| JPH0650646A (en) * | 1992-07-31 | 1994-02-25 | Sanyo Electric Co Ltd | Refrigerator |
| JPH11118202A (en) * | 1997-08-13 | 1999-04-30 | Toshiba Corp | Split air conditioner |
| JP2002039637A (en) * | 2000-07-25 | 2002-02-06 | Shin Meiwa Ind Co Ltd | Freezer and freezing method |
| JP2002062020A (en) * | 2000-08-17 | 2002-02-28 | Toshiba Corp | Refrigerator |
| US6631621B2 (en) * | 2001-07-03 | 2003-10-14 | Thermo King Corporation | Cryogenic temperature control apparatus and method |
| JP2003021473A (en) * | 2001-07-03 | 2003-01-24 | Nihon Freezer Kk | Heat exchanger for circulating refrigerater system having non-azeotropic refrigerant |
| AU2002349758A1 (en) * | 2002-12-03 | 2004-06-23 | Nihon Freezer Co., Ltd. | Refrigerator system using non-azeotropic refrigerant, and non-azeotropic refrigerant for very low temperature used for the system |
| JP2004198063A (en) * | 2002-12-20 | 2004-07-15 | Sanyo Electric Co Ltd | Non-azeotropic refrigerant mixture, refrigerating cycle and refrigerating device |
| JP4307878B2 (en) * | 2003-03-24 | 2009-08-05 | 三洋電機株式会社 | Refrigerant cycle equipment |
-
2005
- 2005-09-08 JP JP2005260151A patent/JP2007071468A/en active Pending
-
2006
- 2006-06-14 KR KR1020077018676A patent/KR20080042035A/en not_active Application Discontinuation
- 2006-06-14 WO PCT/JP2006/311961 patent/WO2007029390A1/en active Application Filing
- 2006-06-14 US US11/658,182 patent/US20080302116A1/en not_active Abandoned
- 2006-06-14 CN CNA2006800061827A patent/CN101128707A/en active Pending
- 2006-06-14 EP EP06766729A patent/EP1923645A4/en not_active Withdrawn
- 2006-08-01 TW TW095128054A patent/TWI310827B/en not_active IP Right Cessation
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105371546A (en) * | 2014-08-25 | 2016-03-02 | 谢德音 | Method capable of changing refrigerant evaporation flow and controlling refrigerant channels |
| CN113614467A (en) * | 2019-01-15 | 2021-11-05 | 马士基集装箱工业公司 | Method for calibrating saturation temperature of refrigerant in refrigeration system, controller and cooler applying same |
| CN113614467B (en) * | 2019-01-15 | 2024-02-13 | 马士基集装箱工业公司 | Method for determining refrigerant or its composition, controller and cooling machine |
| US12038212B2 (en) | 2019-01-15 | 2024-07-16 | Maersk Container Industry A/S | Calibration method of refrigerant saturation temperature in a refrigeration system, a controller for applying such a method and a cooling machine |
| CN114719471A (en) * | 2022-03-08 | 2022-07-08 | 澳柯玛股份有限公司 | Mixed refrigerant refrigerating system and refrigerating method |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2007029390A1 (en) | 2007-03-15 |
| EP1923645A1 (en) | 2008-05-21 |
| TWI310827B (en) | 2009-06-11 |
| EP1923645A4 (en) | 2009-02-18 |
| JP2007071468A (en) | 2007-03-22 |
| TW200710355A (en) | 2007-03-16 |
| US20080302116A1 (en) | 2008-12-11 |
| KR20080042035A (en) | 2008-05-14 |
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