CN101031763A - Cooling systems - Google Patents
Cooling systems Download PDFInfo
- Publication number
- CN101031763A CN101031763A CNA2005800331253A CN200580033125A CN101031763A CN 101031763 A CN101031763 A CN 101031763A CN A2005800331253 A CNA2005800331253 A CN A2005800331253A CN 200580033125 A CN200580033125 A CN 200580033125A CN 101031763 A CN101031763 A CN 101031763A
- Authority
- CN
- China
- Prior art keywords
- evaporimeter
- main flow
- heat exchanger
- expansion gear
- compressor
- 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
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
- F25B2400/13—Economisers
Abstract
An apparatus has a compressor having suction and discharge ports. One or more conduits form a main flowpath from the discharge port through a condenser, a heat exchanger first leg, a first expansion device, and an evaporator to return to the suction port. The conduits also form a bypass flowpath bypassing the heat exchanger first leg, the first expansion device, and the evaporator but passing through a second leg of the heat exchanger in heat exchange relation with the first leg.
Description
Technical field
The present invention relates to cooling system, relate in particular to for the cold-producing medium control mutually in the evaporimeter of air-conditioning and refrigeration system.
Background technology
Consideration on many engineerings focuses on the structure and the operation of the air-conditioning system and the refrigeration system of sealing.Wherein, for evaporator operation, exist various efficient to consider and other Consideration.Suitable evaporimeter operation is important for obtaining the operation of efficient and reliable system.Consideration comprises that cold-producing medium is regulated and the control of conducting heat.Because excessively frosting meeting interference is conducted heat, therefore excessively frosting is one of the problem that must control.So structure and engineering configuration for evaporimeter need be made more effort.
The special dimension that requires emphasis is the engineering configuration of distribution system.Distributor is accepted from the two phase refrigerant of expansion gear and is provided balanced liquid phase refrigerant and vapor phase refrigerant to carry for each coil pipe of evaporimeter, thereby prevents uneven performance.Developed polytype distributor.These comprise the distributor and the impingement/turbulence distributors of capillary type.At US 2,148,414, US 2,461,876, US 3,795,259, US 4,543,802, US5,832,744, distributor has been carried out exemplary description among US 5,842,351, EP 0 160 542 and JP 5-322378, the JP10-185363.
Yet, for this area, still need to provide further improvement.
Summary of the invention
According to an aspect of of the present present invention, a kind of like this device is provided, it comprises: the compressor with suction port and exhaust port; Condenser; First expansion gear; Second expansion gear; Evaporimeter; And heat exchanger, this heat exchanger has first and the second portion that is heat exchange relationship each other.One or more pipelines form: main flow path and bypass flow path.This main flow path from this exhaust port through this condenser, this heat exchanger first, this first expansion gear and this evaporimeter so that turn back to this suction port.This bypass flow path bypass is walked around this heat exchanger first, this first expansion gear and this evaporimeter, but through this second expansion gear and this heat exchanger second portion.
In different embodiments, this evaporimeter does not have distributor.This second expansion gear can be TXV, and it has the thermometer bulb that roughly is heat exchange relationship with suction port condition.This second expansion gear can be EXV.Controller can be connected with EXV, and this controller is programmed in response to the degree of superheat that obtains and controls this EXV.This heat exchanger first can be positioned at the downstream of condenser, the upstream of evaporimeter along main flow path.This heat exchanger second portion can be positioned at the downstream of condenser along bypass flow path.This heat exchanger first can be positioned at the upstream of first expansion gear along main flow path.This evaporimeter can be the heat exchanger of cold-producing medium and air heat exchange.At least in bypass mode, bypass flow enters the heat exchanger second portion and leaves the heat exchanger second portion with single-phase overheated gaseous state along bypass flow path with two-phase gaseous state/liquid state.In this bypass mode, main flow keeps single-phase liquid along main flow path basically in described heat exchanger second portion.Compressor can be to select from the group that comprises screw compressor and scroll compressor.
According to another aspect of the present invention, a kind of method that is used to handle described device is provided, it comprises: detect at least one running parameter; With in response to described detection, handle this second expansion gear at least so that the cold-producing medium that keeps entering this evaporimeter along this main flow path is essentially single-phase liquid.Described at least one running parameter comprise following at least one: saturated suction temperature; With actual suction temperature.
According to another aspect of the present invention, a kind of method that is used to handle cooling system is provided, it comprises: make main flow of refrigerant move the evaporimeter of flowing through; Make with upstream and this main flow precooling to enter this evaporimeter so that keep described main flow to be essentially liquid state at this evaporimeter.This precooling can comprise that making bypass flow be controlled to this main flow is heat exchange relationship.This method also comprises: do not having under the situation of described precooling, determining whether this main flow is shown two phase flow greatly and entered this evaporimeter.
According to another aspect of the present invention, a kind of like this system is provided, it comprises: compressor; Condenser; Gas exhaust piping, this gas exhaust piping are connected to this condenser with this compressor so that be transported to this condenser from this compressor to the main flow of major general's cold-producing medium; Expansion gear; Evaporimeter; Suction line, this suction line are connected to this compressor with this evaporimeter so that cold-producing medium is transported to this compressor and comprises first and second parts in parallel from this condenser; With being used for the cold-producing medium that enters this expansion gear is carried out precooling so that keep described main flow to be roughly device liquid and the flow-path-length scope from this expansion gear to this evaporimeter of flowing through simultaneously.
In various embodiments, this evaporimeter can not have distributor.In this evaporimeter, main flow can change two-phase liquid state/gaseous flow into and change single-phase overheated gaseous flow subsequently into.This bypass flow is counted the 10-35% of the cold-producing medium total amount that accounts for the compressor of flowing through by weight.
Description of drawings
Following with reference to accompanying drawing with describe in detail and to set forth one or more embodiment of the present invention.In conjunction with following accompanying drawing and detailed description and claim, can understand other feature, purpose and advantage of the present invention better, in the accompanying drawings:
Fig. 1 is the schematic diagram that adopts refrigeration system of the present invention or air-conditioning system;
Fig. 2 is the phasor of prior art system; With
Fig. 3 is the phasor of system shown in Figure 1.
Identical Reference numeral and same or analogous parts of symbolic representation in each figure.
The specific embodiment
Fig. 1 shows exemplary enclosed refrigeration system or air-conditioning system 10.This system 10 has hermetic compressor 12, and compressor exhaust pipe or gas exhaust piping 14 extend to condenser 16 downstream from compressor.Intermediate duct 18 extends to expansion gear 20 and evaporimeter 22 downstream from condenser 16.Suction line 24 extends to compressor 12 downstream from evaporimeter 22, so that finish main circuit/flowpath 26.
In order to form bypass circuit/flowpath 28, bypass line 30 comes out and comprises auxiliary expansion device 32 from middle pipeline 18 branches, and bypass line 30 is connected with suction line 24.Heat exchanger 34 is positioned to be convenient to make and is heat exchange relationship in the bypass line 30 in this auxiliary expansion device 32 downstreams and intermediate duct 18 in main expansion gear 20 upstreams.
Exemplary evaporimeter 22 is the cold-producing medium of intersection streaming and the heat exchanger of air heat exchange, it has the cold-producing medium coil pipe 36 of a plurality of parallel connections, and cold-producing medium coil pipe 36 extends to the port of export that is positioned at air-breathing gatherer or collector 40 places from the arrival end that is positioned at liquid header or collector 38.Fan 42 drives air stream 44 coil pipe 36 of flowing through, so that make the flow through cold-producing medium of this coil pipe absorb heat from air stream.
Except electric expansion valve (EEV), also can use the expansion gear of any kind, (for example having the heating power expansion valve (TXV) 32 of the thermometer bulb 70 of far-end, fixing opening arrangement or capillary type device).
The fundamental system of prior art lacks bypass flow path 28 and heat exchanger 34.Fig. 2 shows pressure 100 and the enthalpy 102 for cold-producing medium stream in this fundamental system (existing system that does not perhaps have bypass flow).Boundary line 104 has separated the gaseous state/liquefied mixture district 106 of two-phase, single-phase supercooled liquid district 108, single-phase superheated gas domain 110.Point or the state 120 of shown suction condition as being in enthalpy 122 and pressure 124.These states are present in basically from suction manifold 40 following to be swum over to the flow path of compressor suction port.Cold-producing medium is compressed to compressed point 126 (compression section 125 of curve) in compressor 12, it has the enthalpy 128 and the elevated pressure 130 of rising.In compression process 125, cold-producing medium remains on superheated gas domain 110 usually, perhaps changes superheated gas domain 110 into from two-phase section 106.Cold-producing medium is condensed (condensation segment 131) to condensed point 132 in condenser 16, it has the enthalpy 134 of reduction, but has the pressure identical with compressed/exhaust condition.In condensation process 131, refrigerant condition can change two-phase section 106 into from superheated gas domain 110, and even changes supercooled liquid district 108 into.This cold-producing medium (expansion arc 135) point 136 after become expanding that expands in expansion gear 34, it has the pressure 138 of reduction.In expansion process 135, enthalpy may keep constant, is in 134.Cold-producing medium can enter or remain on two-phase section 106 once more in expansion process.Described two phase refrigerant through expanding must enter evaporimeter.This cold-producing medium evaporates in evaporimeter, so that turn back to the point 120 of the pressure that has the enthalpy of obvious rising and descend a little for the point 136 after expanding.
There is significant problem in the point 136 that is in after the expansion of two-phase section 106.When the cold-producing medium of two-phase enters evaporimeter, be difficult to make cold-producing medium balanced between evaporator coil.That is, similar coil pipe may have different cold-producing medium total amounts and/or have two different phase ratios.This causes producing visibly different coil pipe state in each coil pipe.Coil pipe with higher amounts of refrigerant and higher amount of liquid towards mutually may sub-cooled, therefore produces too much frosting and gathers.Gross efficiency may also descend.Therefore, thus be known that and use complicated dispensing arrangement so that replace liquid collectors 38 balanced described ratio between different coil pipes.Distributor is expensive often.Advantageously, may cause a little 136 to be under the situation of ambient conditions of two-phase section 106, desirable is to make invocation point 136 move to single-phase liquid district 108, thereby can save distributor.In this case, the single-phase liquid stream that enters evaporimeter is convenient to be divided into the similar stream for each coil pipe.Coil pipe can be designed/be configured to be convenient to work under the situation of this inlet flow.
How the bypass flow of the present invention that shows Fig. 3 realizes entering the favourable refrigerant condition of evaporimeter 22.Suction condition/point 220 is roughly the same with point 120 shown in Figure 2.After compression process 225, compressed/exhaust/226 are similar to point 126 shown in Figure 2.That condensation process 231 makes that the main flows of combination and bypass flow flow to is condensed/232, and it is with to put 132 similar.
From this condensed state, bypass flow branch from main flow comes out.The cold-producing medium of this bypass flow expands (referring to line segment 233) to point 234, and this point is in pressure of inspiration(Pi) 124 and enthalpy 134 basically.Like this, heat exchange in heat exchanger 34 between main flow and the bypass flow (be 235 and be 236 for main flow for bypass flow) makes the state of bypass flow turn back to a little 220 and main flow is cooled to precooling/238, and it has the enthalpy 240 of the main flow of further reduction.The main flow of cold-producing medium expands (line segment 241) to putting 242 in expansion gear 20, it has the pressure 244 (roughly the same with point 138) of decline.Main flow of refrigerant is evaporated (line segment 245) so that make main flow turn back to initial inspiratory point 220 in evaporimeter 22.Heat exchange meeting between main flow and the bypass flow makes invocation point 242 move to the lower state of enthalpy.The amount of required heat exchange depends on the state of surrounding environment.
The groundwork of expansion gear 32 can leave the degree of superheat of evaporimeter 22 in response to the cold-producing medium that senses.This degree of superheat (actual temperature deducts saturation temperature) can be based on determining (for example in control system 44 known refrigerant property being programmed) for the temperature sensor 50 of actual temperature with for the output of the pressure sensor 52 of saturation temperature.Expansion gear 32 can be by dibit mode or progressive mode in response to the overheated existence or the degree of superheat or cross thermal parameter (being higher than the overheated of thresholding) and open.By heating power expansion valve (TXV), realize control by its thermometer bulb 70 being arranged to be heat exchange relationship with the cold-producing medium that is in suction condition as expansion gear 32.
Other parts of expansion gear 32 and/or bypass flow path can be determined size with reference to main flow flow path parts, so that make the suitable equilibrium of acquisition between bypass flow and non-bypass flow.In exemplary dibit structure (dibit that promptly only has open and closed flows), the design of exemplary flow equalization make flow through that compressor total flow about 30% as bypass flow, percentage for by weight/quality calculates (being that non-bypass flow is 3/7).Exemplary parameter for the broad of dibit operation is 25-33% and 10-35%.Progressive or cloth advances operation can make these scopes maximize and optionally feasible flowing less than the lower limit of these scopes.
One or more embodiment of the present invention has below been described.Yet, should be understood that, under the situation that does not break away from the spirit and scope of the present invention, can make various modification.For example when implementing as the modification of existing system or redesign, the details of existing system can influence the details of enforcement significantly.Although the present invention is described with reference to the state of fundamental system and simplification, principle of the present invention can be applicable to many more complicated system forms, and no matter this system is existing or does not also develop.Therefore, other embodiment also drops in the scope of following claim.
Claims (20)
1. device, it comprises:
Compressor with suction port and exhaust port;
Condenser;
First expansion gear;
Second expansion gear;
Evaporimeter;
Heat exchanger, this heat exchanger have first and the second portion that is heat exchange relationship each other; With
One or more pipelines, so that form:
Main flow path, this main flow path from this exhaust port through this condenser, this heat exchanger first, this first expansion gear and this evaporimeter so that turn back to this suction port; With
Bypass flow path, this bypass flow path bypass is walked around this heat exchanger first, this first expansion gear and this evaporimeter, but through this second expansion gear and this heat exchanger second portion.
2. device as claimed in claim 1 is characterized in that,
This evaporimeter does not have distributor.
3. device as claimed in claim 1 is characterized in that,
This second expansion gear is TXV, and it has the thermometer bulb that roughly is heat exchange relationship with suction port condition.
4. device as claimed in claim 1 is characterized in that,
This second expansion gear is EXV.
5. device as claimed in claim 4 is characterized in that, also comprises:
The controller that is connected with EXV, this controller are programmed in response to the degree of superheat that obtains and control this EXV.
6. device as claimed in claim 1 is characterized in that,
This heat exchanger first is positioned at the downstream of condenser, the upstream of evaporimeter along main flow path; With
This heat exchanger second portion is positioned at the downstream of condenser along bypass flow path.
7. device as claimed in claim 6 is characterized in that,
This heat exchanger first is positioned at the upstream of first expansion gear along main flow path.
8. device as claimed in claim 1 is characterized in that,
This evaporimeter is the heat exchanger of cold-producing medium and air heat exchange.
9. device as claimed in claim 1 is characterized in that,
At least in bypass mode, bypass flow enters the heat exchanger second portion and leaves the heat exchanger second portion with single-phase overheated gaseous state along bypass flow path with two-phase gaseous state/liquid state; With
In this bypass mode, main flow keeps single-phase liquid along main flow path basically in described heat exchanger second portion.
10. device as claimed in claim 1 is characterized in that,
Compressor is to select from the group that comprises screw compressor and scroll compressor.
11. a method that is used to handle the described device of claim 1, it comprises:
Detect at least one running parameter; With
In response to described detection, handle this second expansion gear at least so that the cold-producing medium that keeps entering this evaporimeter along this main flow path is essentially single-phase liquid.
12. method as claimed in claim 11 is characterized in that,
Described at least one running parameter comprise following at least one:
Saturated suction temperature; With
Actual suction temperature.
13. a method that is used to handle cooling system, it comprises:
Make main flow of refrigerant move the evaporimeter of flowing through; With
Make in the upstream of this evaporimeter and this main flow precooling enter this evaporimeter so that keep described main flow to be essentially liquid state.
14. method as claimed in claim 13 is characterized in that,
This precooling comprises that making bypass flow be controlled to this main flow is heat exchange relationship.
15. method as claimed in claim 13 is characterized in that, also comprises:
Do not having under the situation of described precooling, determining whether this main flow is shown two phase flow greatly and entered this evaporimeter.
16. method as claimed in claim 15 is characterized in that,
Describedly determine to comprise that the refrigerant superheat of determining to leave evaporimeter surpasses thresholding.
17. a system, it comprises:
Compressor;
Condenser;
Gas exhaust piping, this gas exhaust piping are connected to this condenser with this compressor so that be transported to this condenser from this compressor to the main flow of major general's cold-producing medium;
Expansion gear;
Evaporimeter;
Suction line, this suction line are connected to this compressor with this evaporimeter so that cold-producing medium is transported to this compressor and comprises first and second parts in parallel from this condenser; With
Be used for the cold-producing medium that enters this expansion gear is carried out precooling so that keep described main flow to be roughly device liquid and the flow-path-length scope from this expansion gear to this evaporimeter of flowing through simultaneously.
18. system as claimed in claim 17 is characterized in that,
This evaporimeter does not have distributor.
19. system as claimed in claim 17 is characterized in that,
In this evaporimeter, main flow changes two-phase liquid state/gaseous flow into and changes single-phase overheated gaseous flow subsequently into.
20. system as claimed in claim 17 is characterized in that,
This bypass flow is counted the 10-35% of the cold-producing medium total amount that accounts for the compressor of flowing through by weight.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US10/954,499 | 2004-09-29 | ||
| US10/954,499 US20060064997A1 (en) | 2004-09-29 | 2004-09-29 | Cooling systems |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101031763A true CN101031763A (en) | 2007-09-05 |
Family
ID=36097475
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2005800331253A Pending CN101031763A (en) | 2004-09-29 | 2005-09-07 | Cooling systems |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20060064997A1 (en) |
| EP (1) | EP1800071A2 (en) |
| CN (1) | CN101031763A (en) |
| WO (1) | WO2006039042A2 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103836732A (en) * | 2012-11-20 | 2014-06-04 | 三星电子株式会社 | Air conditioner |
| CN107709894A (en) * | 2015-06-08 | 2018-02-16 | 丹佛斯有限公司 | Method for running the vapor compression system with heat recovery |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20080307805A1 (en) * | 2005-11-04 | 2008-12-18 | Gupte Neelkanth S | Dual Temperature Refrigeration Circuit |
| JP2008032336A (en) * | 2006-07-31 | 2008-02-14 | Sanyo Electric Co Ltd | Two-stage expansion refrigeration apparatus |
| KR101552618B1 (en) * | 2009-02-25 | 2015-09-11 | 엘지전자 주식회사 | air conditioner |
| US9644905B2 (en) | 2012-09-27 | 2017-05-09 | Hamilton Sundstrand Corporation | Valve with flow modulation device for heat exchanger |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2148414A (en) * | 1934-09-06 | 1939-02-21 | Westinghouse Electric & Mfg Co | Cooling apparatus |
| LU27859A1 (en) * | 1944-02-14 | |||
| US3795250A (en) * | 1969-07-24 | 1974-03-05 | Amf Inc | Process for making a reconstituted tobacco composition |
| DE3327179A1 (en) * | 1983-07-28 | 1985-02-07 | Süddeutsche Kühlerfabrik Julius Fr. Behr GmbH & Co KG, 7000 Stuttgart | EVAPORATOR |
| US5390507A (en) * | 1992-09-17 | 1995-02-21 | Nippondenso Co., Ltd. | Refrigerant evaporator |
| US5832744A (en) * | 1996-09-16 | 1998-11-10 | Sporlan Valve Company | Distributor for refrigeration system |
| US5842351A (en) * | 1997-10-24 | 1998-12-01 | American Standard Inc. | Mixing device for improved distribution of refrigerant to evaporator |
| US6474087B1 (en) * | 2001-10-03 | 2002-11-05 | Carrier Corporation | Method and apparatus for the control of economizer circuit flow for optimum performance |
-
2004
- 2004-09-29 US US10/954,499 patent/US20060064997A1/en not_active Abandoned
-
2005
- 2005-09-07 WO PCT/US2005/031179 patent/WO2006039042A2/en not_active Application Discontinuation
- 2005-09-07 CN CNA2005800331253A patent/CN101031763A/en active Pending
- 2005-09-07 EP EP05794299A patent/EP1800071A2/en not_active Withdrawn
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103836732A (en) * | 2012-11-20 | 2014-06-04 | 三星电子株式会社 | Air conditioner |
| CN103836732B (en) * | 2012-11-20 | 2018-05-01 | 三星电子株式会社 | Air conditioner |
| US9982929B2 (en) | 2012-11-20 | 2018-05-29 | Samsung Electronics Co., Ltd. | Air conditioner |
| CN107709894A (en) * | 2015-06-08 | 2018-02-16 | 丹佛斯有限公司 | Method for running the vapor compression system with heat recovery |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2006039042A2 (en) | 2006-04-13 |
| EP1800071A2 (en) | 2007-06-27 |
| US20060064997A1 (en) | 2006-03-30 |
| WO2006039042A3 (en) | 2006-11-23 |
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