CN102105758A - Symmetric refrigerant regulator for flooded multichannel evaporator - Google Patents
Symmetric refrigerant regulator for flooded multichannel evaporator Download PDFInfo
- Publication number
- CN102105758A CN102105758A CN2009801293825A CN200980129382A CN102105758A CN 102105758 A CN102105758 A CN 102105758A CN 2009801293825 A CN2009801293825 A CN 2009801293825A CN 200980129382 A CN200980129382 A CN 200980129382A CN 102105758 A CN102105758 A CN 102105758A
- Authority
- CN
- China
- Prior art keywords
- evaporator
- refrigerant
- heat exchanger
- evaporimeter
- regulator
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 239000003507 refrigerant Substances 0.000 title abstract description 11
- 238000001816 cooling Methods 0.000 abstract description 3
- 238000005057 refrigeration Methods 0.000 abstract description 3
- 238000010438 heat treatment Methods 0.000 abstract description 2
- 238000010257 thawing Methods 0.000 abstract description 2
- 238000004378 air conditioning Methods 0.000 abstract 1
- 238000012423 maintenance Methods 0.000 abstract 1
- 239000002937 thermal insulation foam Substances 0.000 abstract 1
- 239000007788 liquid Substances 0.000 description 9
- 238000000034 method Methods 0.000 description 7
- 238000009833 condensation Methods 0.000 description 5
- 230000005494 condensation Effects 0.000 description 5
- 239000007789 gas Substances 0.000 description 5
- 239000012530 fluid Substances 0.000 description 3
- 239000000203 mixture Substances 0.000 description 3
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000001704 evaporation Methods 0.000 description 2
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 1
- 102000004357 Transferases Human genes 0.000 description 1
- 108090000992 Transferases Proteins 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 229910052802 copper Inorganic materials 0.000 description 1
- 239000010949 copper Substances 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 239000006260 foam Substances 0.000 description 1
- 229910052757 nitrogen Inorganic materials 0.000 description 1
Images
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
- F25B13/00—Compression machines, plants or systems, with reversible 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
- F25B40/00—Subcoolers, desuperheaters or superheaters
-
- 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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
-
- 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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/05—Compression system with heat exchange between particular parts of the system
- F25B2400/052—Compression system with heat exchange between particular parts of the system between the capillary tube and another part of the refrigeration cycle
Abstract
A regulator of refrigerant for a refrigeration circuit with flooded evaporator. The refrigerant can be distributed to many separate evaporator channels. The flow of refrigerant can be changed so that the evaporator and condenser change functions. This provides the opportunity for a fast defrosting of the evaporator - or the evaporator can alternately be applied for cooling and heating. The regulator functions independently of the gravitational field and therefore it can be applied for air-conditioning systems in aeroplane and space crafts. The regulator is without movable parts. It has two throttling steps, e.g. two capillary tubes separated by a suction-gas heat exchanger. It requires neither adjustment nor maintenance and therefore it can be placed at inaccessible places or it can be embedded completely in insulation foam. The regulator keeps the evaporator flooded under all load conditions. The amount of circulating refrigerant is adapted to the load by an optional excess of refrigerant being bound in the evaporator. This happens by pulling heat energy out of the refrigerant whereby the density of the refrigerant is increased.
Description
Technical field
The present invention relates to a kind of refrigerating circuit with compressor (A), condenser (D), evaporimeter (C) and suction line heat exchanger (suction-gas heat exchanger), wherein cold-producing medium in two steps by capillary-compensated: at first from the condenser to the suction line heat exchanger (F) and from the suction line heat exchanger to the evaporimeter (E) then.
The purpose in such loop is the assignment system cryogen, makes evaporimeter be filled, and makes air-breathing (the suction gas) that locate in the suction port of compressor overheated.
Background technology
Learn such loop from DK 174179, wherein the suction line heat exchanger condensation arrives the steam of fluid container, makes and has only neat liquid further to be carried.Simultaneously, the pressure in the heat exchanger control container, thus and regulate amount to the stream of the cold-producing medium of evaporimeter.The degree of the amount of this stream of cold-producing medium air-breathing the pouring in of control (or overheated), the extent control suction line heat exchanger of air-breathing pouring in (or overheated) between two throttling steps with how strong degree cooling condensation thing.Process is self-regulating, and when reaching balance, evaporimeter is filled.
The accompanying drawing summary
Fig. 1: compressor (A), cross valve (B) can change the direction of the stream of cold-producing medium in cross valve (B).Evaporator/condenser (C, D) is symmetrical, and two identical capillaries (E, F) that the heat exchanger by having suction line (G) and two nozzles for example converge in suction line heat exchanger (H) connect.
Fig. 2 illustrates the adjuster that is used for the multichannel evaporator/condenser.3 shown in the drawings are used to be connected to the capillary (E) of evaporimeter and the capillary (F) that 2 are used to be connected to condenser.Suction line (G) be conducted through show be used for passage capillaceous outer cover (external jacket) (H).
Fig. 3 illustrates the temperature in the suction line heat exchanger.Te is the air-breathing temperature in the porch of heat exchanger, and Tx is " almost " stationary temperature in the hydraulic fluid side.Tc illustrates the relation of the temperature relatively hot interchanger of condenser.
Figure 4 and 5 illustrate with the loop of enthalpy-log (pressure) figure and calculate.Cold-producing medium is R290, and evaporating temperature is-25 ℃, and condensation temperature is 45 ℃.Loop among Fig. 4 has the cold-producing medium load bigger than the loop among Fig. 5, and it pulls to the left side further with evaporimeter (EF).Line segment CD is the enthalpy that is shifted by heat exchanger, and line segment (FG) is the corresponding skew of evaporimeter towards lower enthalpy.In Fig. 4, evaporimeter contains about 3 times cold-producing medium of the evaporimeter that is equivalent among Fig. 5.
Summary of the invention
The present invention is different from DK 174179, because lack liquid container.The amount of the cold-producing medium that instead, is recycled is adjusted to loading condition by excessive cold-producing medium is bound by in the evaporimeter.This takes place when cold-producing medium excessive, by suction line heat exchanger, is reduced in the enthalpy of the porch of evaporimeter, and the ratio between steam and the liquid is changed whereby---and make the density of cold-producing medium be increased.
Structure is symmetrical, and can change the stream of cold-producing medium, makes evaporimeter and condenser exchange their function.This defrosting for evaporimeter provides chance---and perhaps evaporimeter is applicable to cooling off and heating the two.This method is independent of gravitational field, and it is therein in the aircraft that reversed of system and do not have fully to work in the spaceship of gravitational field.
This method is self-regulating, and does not have movably part, and so it can be placed on inaccessible position or it can be embedded in the insulating foams fully.
Even the present invention can use the system of all sizes and use most of cold-producing mediums to use---not zeotrope,, will comprise the great fluctuation process of the temperature of evaporimeter for the adjusting of the enthalpy of evaporimeter because in the case with big thermograde.
New technical means (claim 1):
The throttling means comprise two throttling steps of being separated by suction line heat exchanger, and wherein the flow velocity by suction line heat exchanger is very high, so that liquids and gases are not separated.
Two throttling steps can be by two nozzles, and for example two capillaries are set up, and suction line heat exchanger can be made by two concentric tubes that satisfy following two requirements:
Heat shifts character must be enough to remove all fluid refrigeration agent from sucking gas under all operations condition.
Flow velocity at condenser side must be very high, so that liquids and gases are not separated.This is being realized by the turbulent flow place that limits greater than 3000 Reynolds number.
Technique effect (claim 1):
Condensate passes through suction line heat exchanger as liquid and steam mixture, wherein has thermodynamical equilibrium between pressure and temperature.When air-breathing when condensate is removed enthalpy, some condensations in the steam---but the marked change of pressure does not appear, and therefore do not have the change of temperature yet.Air-breathing with adverse current by condensate, and be heated to temperature near the temperature of condensate.
This process is self-regulating.
Test:
When refrigerating circuit has excessive cold-producing medium, can cause decline at the enthalpy in the exit of evaporimeter.Therefore the variation of enthalpy can not be passed through heat exchanger, because the suction temperature after interchanger is that " almost " is constant, and the following general who has surrendered of enthalpy is transferred to condenser side, and wherein the enthalpy in the porch of evaporimeter correspondingly descends.
The greater density in the decline hint evaporimeter of the enthalpy at evaporator inlet place and the constraint---this has alleviated cause---of cold-producing medium therefore are the excessive of circulating refrigerant.
Similarly, when the loop lacks cold-producing medium:
This causes the increase at the enthalpy in the exit of evaporimeter.The variation of enthalpy can not be passed through heat exchanger, because the suction temperature after heat exchanger is constant for " almost "---and therefore the increase of enthalpy will be transferred to condenser side, and wherein the enthalpy in the porch of evaporimeter correspondingly increases.
---and cold-producing medium is released whereby, and---this has alleviated cause---is the deficiency of circulating refrigerant to less density in the increase hint evaporimeter of the enthalpy of the porch of evaporimeter.
Structure is symmetrical, and can change the stream of cold-producing medium, makes evaporimeter and condenser function of exchange.
New technical means (claim 2):
The present invention can easily be expanded to regulate evaporimeter wherein and/or condenser is divided into the system of a plurality of parts.
Advance with the nozzle that goes out suction line heat exchanger and can be replaced, make each part in evaporator/condenser all have nozzle separately by how parallel nozzle.
Technique effect (claim 2):
Be divided into many parallel nozzles and can aspect the gathering of the cold-producing medium of many condenser portion, any problem do not occurring, but cold-producing medium may be a problem to the distribution of many evaporator sections, therefore some nozzles are supplied a lot of liquid, and other are supplied many steam.This problem is solved by the turbulent flow demand in the heat exchanger, and turbulent flow has been guaranteed the uniform homogeneous blend of liquid and steam, and this uniform homogeneous blend can be assigned to many nozzles subsequently, and can not go wrong.
Embodiment:
Compressor S C21CNX2 is used for R290, and has 750 watts power in the condensation temperature of-25 degrees centigrade evaporating temperature and 45 degrees centigrade, is equivalent to the mass flow of 3 Grams Per Seconds.Two capillaries all have the length of diameter and the 1000mm of 1mm, are equivalent to the capacity of 27.4 liters of nitrogen of per minute.
Fig. 3 shows the refrigeration work consumption of heat exchanger at most necessary transferase 45 0% under 30 temperature differences of opening, and is 400W herein, and this needs 90cm
2Area.The diameter of suction line is 10mm, so 90cm
2The surface that is equivalent to about 30cm of suction line.
Heat exchanger comprises the concentric copper pipe of two length 300mm.Interior pipe is the suction line with external diameter of 10mm, and the selected internal diameter with 10.4mm of outer tube, makes that the distance between the pipe becomes 0.2mm.Opening between the pipe becomes 6mm
2, and can calculate Reynolds number in 3200 to 6000 scope according to this, this has guaranteed turbulent flow.
The general introduction of advantage of the present invention
It is the simple and high performance adjuster be used to the cold-producing medium of the system with flooded evaporator (flooded evaporator) (comprising the multichannel evaporimeter with a plurality of parallel parts).
Can change the direction of the stream of cold-producing medium, so that evaporimeter and condenser change function.
It does not need to regulate or safeguard, and it can be placed on inaccessible position.
It is independent of gravitational field and works, and it can be used in aircraft and the spaceship.
Claims (3)
1. refrigerating circuit, comprise compressor (A), evaporimeter (C), condenser (D), suction line heat exchanger (H) and throttling arrangement (E, H, F), described throttling arrangement (E, H, F) comprises that the bottom with described condenser is connected to the nozzle that reduces pressure (F) of described suction line heat exchanger and described suction line heat exchanger is connected to the nozzle that reduces pressure (E) of described evaporimeter, and described refrigerating circuit is characterised in that: the stream of the cold-producing medium by described suction line heat exchanger is turbulent flow in the condensate side.
2. refrigerating circuit according to claim 1, wherein, described evaporimeter and/or described condenser are divided into a plurality of parts, and wherein, each part is connected to described heat exchanger by the nozzle that reduces pressure that separates.
3. according to claim 1 or the described refrigerating circuit of claim 2, has the device (B) of the direction of the described stream that is used to change the cold-producing medium by described evaporimeter and described condenser.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DKPA200801298 | 2008-09-16 | ||
| DKPA200801298A DK176868B1 (en) | 2008-09-16 | 2008-09-16 | Symmetrical refrigerant regulator for flooded multi-channel evaporator |
| PCT/DK2009/050238 WO2010031402A1 (en) | 2008-09-16 | 2009-09-13 | Symmetric refrigerant regulator for flooded multichannel evaporator |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN102105758A true CN102105758A (en) | 2011-06-22 |
Family
ID=41600761
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009801293825A Pending CN102105758A (en) | 2008-09-16 | 2009-09-13 | Symmetric refrigerant regulator for flooded multichannel evaporator |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20110154849A1 (en) |
| CN (1) | CN102105758A (en) |
| DK (1) | DK176868B1 (en) |
| WO (1) | WO2010031402A1 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107279448B (en) * | 2017-06-28 | 2022-12-27 | 中绅科技(广东)有限公司 | Cold control device and method for double-throttling precooling fresh-keeping ice cream machine and ice cream machine |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1389677A (en) * | 2002-07-10 | 2003-01-08 | 邹自才 | Improved air conditioner |
| US20030097856A1 (en) * | 2000-03-13 | 2003-05-29 | Stokes Warwick James | Regulator with receiver for refrigerators and heatpumps |
| CN1506647A (en) * | 2002-12-10 | 2004-06-23 | ���µ�����ҵ��ʽ���� | Double-layer tube type heat exchanger |
| CN1752610A (en) * | 2004-09-24 | 2006-03-29 | 乐金电子(天津)电器有限公司 | Overcooling structure for air conditioner |
| JP2007085647A (en) * | 2005-09-22 | 2007-04-05 | Daikin Ind Ltd | Air conditioning device |
| CN101144656A (en) * | 2006-09-14 | 2008-03-19 | 三星电子株式会社 | Air conditioner |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2785540A (en) * | 1953-09-30 | 1957-03-19 | Westinghouse Electric Corp | Heat pumps |
| US4106308A (en) * | 1977-05-19 | 1978-08-15 | The Singer Company | Heating and cooling system with capillary control means |
| US5167275A (en) * | 1989-12-06 | 1992-12-01 | Stokes Bennie J | Heat exchanger tube with turbulator |
| NZ304969A (en) * | 1995-03-14 | 1998-07-28 | Hussmann Corp | Refrigerated merchandiser having modular evaporator coils |
| JP3322292B2 (en) * | 1995-10-23 | 2002-09-09 | 日立電線株式会社 | Heat transfer tube |
-
2008
- 2008-09-16 DK DKPA200801298A patent/DK176868B1/en not_active IP Right Cessation
-
2009
- 2009-09-13 WO PCT/DK2009/050238 patent/WO2010031402A1/en active Application Filing
- 2009-09-13 CN CN2009801293825A patent/CN102105758A/en active Pending
- 2009-09-13 US US13/061,631 patent/US20110154849A1/en not_active Abandoned
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20030097856A1 (en) * | 2000-03-13 | 2003-05-29 | Stokes Warwick James | Regulator with receiver for refrigerators and heatpumps |
| CN1389677A (en) * | 2002-07-10 | 2003-01-08 | 邹自才 | Improved air conditioner |
| CN1506647A (en) * | 2002-12-10 | 2004-06-23 | ���µ�����ҵ��ʽ���� | Double-layer tube type heat exchanger |
| CN1752610A (en) * | 2004-09-24 | 2006-03-29 | 乐金电子(天津)电器有限公司 | Overcooling structure for air conditioner |
| JP2007085647A (en) * | 2005-09-22 | 2007-04-05 | Daikin Ind Ltd | Air conditioning device |
| CN101144656A (en) * | 2006-09-14 | 2008-03-19 | 三星电子株式会社 | Air conditioner |
Also Published As
| Publication number | Publication date |
|---|---|
| US20110154849A1 (en) | 2011-06-30 |
| DK176868B1 (en) | 2010-02-01 |
| WO2010031402A1 (en) | 2010-03-25 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C02 | Deemed withdrawal of patent application after publication (patent law 2001) | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20110622 |