EP2153139A1 - Refrigerant injection above critical point in a transcritical refrigerant system - Google Patents
Refrigerant injection above critical point in a transcritical refrigerant systemInfo
- Publication number
- EP2153139A1 EP2153139A1 EP07797666A EP07797666A EP2153139A1 EP 2153139 A1 EP2153139 A1 EP 2153139A1 EP 07797666 A EP07797666 A EP 07797666A EP 07797666 A EP07797666 A EP 07797666A EP 2153139 A1 EP2153139 A1 EP 2153139A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- refrigerant
- economizer
- set forth
- compressor
- point
- 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.)
- Withdrawn
Links
- 239000003507 refrigerant Substances 0.000 title claims abstract description 202
- 238000002347 injection Methods 0.000 title claims abstract description 75
- 239000007924 injection Substances 0.000 title claims abstract description 75
- 238000007906 compression Methods 0.000 claims description 35
- 238000000034 method Methods 0.000 claims description 23
- 230000006835 compression Effects 0.000 claims description 22
- 238000011144 upstream manufacturing Methods 0.000 claims description 19
- 238000010079 rubber tapping Methods 0.000 claims 2
- 238000001816 cooling Methods 0.000 description 11
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 10
- 239000013256 coordination polymer Substances 0.000 description 7
- 229910002092 carbon dioxide Inorganic materials 0.000 description 6
- 239000001569 carbon dioxide Substances 0.000 description 6
- 230000007613 environmental effect Effects 0.000 description 4
- 239000012530 fluid Substances 0.000 description 4
- 238000010438 heat treatment Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 238000001704 evaporation Methods 0.000 description 2
- 230000008020 evaporation Effects 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 229920006395 saturated elastomer Polymers 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000003467 diminishing effect Effects 0.000 description 1
- 230000002708 enhancing effect Effects 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 230000007704 transition Effects 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
- 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
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
-
- 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
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
-
- 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
- F25B2400/04—Refrigeration circuit bypassing means
-
- 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
Definitions
- This application relates to a refrigerant system having an economizer circuit, wherein the refrigerant injection to the compressor occurs above a critical point in a transcritical operation.
- Refrigerant compressors circulate a refrigerant through a refrigerant system to condition a secondary fluid.
- a compressor compresses a refrigerant and delivers it downstream to a first heat exchanger.
- Refrigerant from the first heat exchanger passes through an expansion device, in which its pressure and temperature are reduced. Downstream of the expansion device, a refrigerant passes through a second heat exchanger and then back to the compressor.
- a portion of refrigerant is tapped from a main refrigerant stream downstream of the first heat exchanger.
- This tapped refrigerant is passed through an expansion device, to be expanded to an intermediate pressure and temperature, and then this partially expanded tapped refrigerant passes in heat exchange relationship with a main refrigerant flow in an economizer heat exchanger.
- the main refrigerant is cooled further such that it will have a greater thermodynamic cooling potential when it reaches the second heat exchanger, enhancing refrigerant system performance.
- the tapped refrigerant typically in a superheated thermodynamic state, is returned to an intermediate compression point in the compressor downstream of the economizer heat exchanger.
- economizer cycles is especially advantageous in refrigerant systems utilizing carbon dioxide (CO 2 ) as a refrigerant, because of increased capacity and efficiency gains in transcritical operation.
- CO 2 carbon dioxide
- the use of a two-stage (or multi-stage) economized cycle is even more beneficial, although the performance gain at each stage is typically smaller.
- Carbon dioxide is an environmentally friendly natural refrigerant that nowadays is more commonly used in vapor compression systems operating for at least a portion of the time in a transcritical region. Since carbon dioxide has a low critical point, most vapor compression systems utilizing carbon dioxide as the refrigerant operate in a transcritical region (or above the critical point on a high pressure side) in at least some environmental conditions.
- the pressure of a subcritical fluid is essentially a function of temperature only under saturated conditions (when both liquid and vapor are present), or in other words, one is directly interrelated to the other.
- the temperature of the fluid is higher than the critical temperature (supercritical)
- the saturated state no longer exists, and pressure and temperature become independent thermodynamic variables defining a thermodynamic state of the fluid. Therefore, for any set of heat sink temperature conditions, it is possible to operate a refrigerant system at many high side pressure conditions.
- the economizer refrigerant injection occurred at an intermediate compression point early in the compression cycle, and below a critical point. For an economizer circuit in a refrigerant system operating transcritically, this may not be achievable.
- a similar situation would occur when partially expanded refrigerant tapped at the exit of the first heat exchanger is injected into a compression process to reduce the discharge temperature.
- the cooling refrigerant may be injected at supercritical conditions.
- a refrigerant system operates in a transcritical regime, at least for a portion of the time.
- An economizer cycle is incorporated into the refrigerant system.
- Refrigerant from the economizer cycle is reinjected back into the compressor at a point designed and selected such that the re- injection may occur above the critical point.
- the benefits of an economizer function can be achieved in a transcritical refrigerant system operating at high discharge pressure that is well above the critical pressure.
- there is a single stage compressor and the intermediate pressure injection point is selected and designed into the compressor to allow the injection to occur above the critical point.
- the refrigerant system incorporates multiple economizer circuits, and the compressor has a multi-stage refrigerant injection.
- the compressor In the upper injection stage, the refrigerant injection occurs above the critical point and at the lower injection stage the injection may occur below the critical point.
- the compressor can be represented by two separate compression stages (such as two reciprocating compressor cylinders placed in serial arrangement) or two compressors connected in series. In this case, refrigerant injection is taking place between the compression stages.
- refrigerant injection can be internal to the compression pockets located within a single compressor.
- the refrigerant system may have a refrigerant injection cooling branch, that is typically utilized to reduce the discharge temperature of the refrigerant exiting the compressor, through which a partially expanded portion of refrigerant tapped from the exit of the heat rejection heat exchanger is directed and injected at a point in the compression process designed and selected such that the injection may take place above the critical point.
- a refrigerant injection cooling branch that is typically utilized to reduce the discharge temperature of the refrigerant exiting the compressor, through which a partially expanded portion of refrigerant tapped from the exit of the heat rejection heat exchanger is directed and injected at a point in the compression process designed and selected such that the injection may take place above the critical point.
- Figure IA shows a first schematic.
- Figure IB is a P-h chart of the Figure IA embodiment.
- Figure 2A shows a second embodiment.
- Figure 2B is a P-h chart for the second embodiment.
- Figure 3A shows a third embodiment.
- Figure 3B is a P-h chart for the third embodiment.
- a refrigerant system 70 is illustrated in Figure IA having a compressor 20 compressing a refrigerant and delivering it downstream to a heat rejection heat exchanger 24, and then through an economizer heat exchanger 26.
- a compressor 20 compressing a refrigerant and delivering it downstream to a heat rejection heat exchanger 24, and then through an economizer heat exchanger 26.
- at least a portion refrigerant is tapped into a tap refrigerant line 28 from a main refrigerant line 30, downstream of the economizer heat exchanger 26, and directed through an economizer expansion device 32, and once again, through the economizer heat exchanger 26.
- This refrigerant further cools the refrigerant in the main refrigerant line 30.
- Refrigerant in the main refrigerant line 30 then passes through a main expansion device 34, and then to a heat accepting heat exchanger 36, before returning to the compressor 20.
- the refrigerant from the tap refrigerant line 28 passes back into the compressor 20 at an injection point 27 through an injection refrigerant line 29.
- the injection point 27 is selected during the design of the compressor to accommodate the conditions at which the injection may take place above the critical point in the transcritical operation of the refrigerant system 70.
- the injected refrigerant would not be transiting through a two-phase evaporation process while traveling through the economizer heat exchanger 26.
- the injected economized refrigerant would always transit through a two-phase evaporation process while traveling through the economizer heat exchanger.
- the economizer injection occurs above the critical point CP.
- the entirety of the economizer flow heating during heat transfer interaction in the economizer heat exchanger 26 will occur above the critical point CP and along the line X.
- the distance Z represents additional cooling provided by the economizer function to the main refrigerant flow in the economizer heat exchanger 26, and, as shown, also occurs entirely above the critical point CP.
- the refrigerant systems may operate in a transcritical regime at certain environmental conditions, at least for a portion of the time.
- the modification to the location of the injection of the economized refrigerant into the compression process provides the ability to efficiently achieve the economizer function in a refrigerant system 70 operating in transcritical regime.
- the economizer heat exchanger 26 is also designed to accommodate a single-phase refrigerant flow on its economized leg.
- the economizer expansion device 32 is also operated and designed to handle a single- phase refrigerant, both upstream and downstream of this expansion device. In the past, the expansion devices were not intended to operate with single-phase refrigerant at both locations upstream and downstream of the expansion device.
- another refrigerant system 50 includes two compressors (or two compression stages) 52 and 54 operating in series.
- the refrigerant from compressor 54 is directed downstream into a heat rejection heat exchanger 56.
- a first economizer function occurs within an economizer heat exchanger 58
- a second economizer function occurs within an economizer heat exchanger 60.
- the refrigerant from a main refrigerant line 62 serially passes through the two heat exchangers 58 and 60, through a main expansion device 64, and into a heat accepting heat exchanger 66, before returning to the lower stage compressor 52.
- tap refrigerant lines associated with each heat exchanger 58 and 60 pass through economizer expansion devices 94 and 92 respectively. .
- the tap refrigerant lines are shown to flow refrigerant in the same direction as the main refrigerant flow, although, this is generally for simplicity of illustration. In practice, it is often the case that the refrigerant is best to be arranged to flow in a counterflow direction, relative to the main flow, as illustrated in Figure IA.
- Refrigerant from the second downstream economizer heat exchanger 60 is directed through an injection refrigerant line 78 back to a point 72 intermediate the compression stages 52 and 54.
- the heat absorption by this economized refrigerant flow extends along the line Y, and is below the critical point CP.
- the upstream economizer circuit directs refrigerant through an injection refrigerant line 74 to a point 76 and along the line C, which is positioned above the critical point CP.
- the design of the compressor 54, and the location of the injection point 76 are selectively and carefully designed to optimize operation of the compressor 54, and to accommodate that the refrigerant injection above the critical point CP.
- the refrigerant in the refrigerant systems 70 and 50 may be CO 2 .
- the refrigerant systems may operate in a transcritical regime, at least at some environmental conditions and for a portion of the time, and the modification to the location of the injection point of the economizer refrigerant provides the ability to efficiently execute the economizer function in a refrigerant system operating in a transcritical regime.
- the economizer heat exchanger 58 is designed to accommodate a single-phase refrigerant flow on its economized leg.
- the expansion device 94 is also designed to handle a single-phase refrigerant at both locations upstream and downstream of this expansion device. It should be emphasized that a two-stage economized design can also be accomplished using a single compressor where upper and lower injection stages are placed within the same compression element. It is also possible to have three independent compression stages where both upper and lower refrigerant injections will take place between the compression stages. Furthermore, the number of compression stages can be extended to more than three, and is only limited by practical cost, size, weight, etc. and diminishing performance return considerations.
- FIG. 3 A Another embodiment is shown in Figure 3 A where a portion of refrigerant can be selectively tapped through a refrigerant tap line 91 from the main refrigerant line 62 at the exit of the heat rejection heat exchanger 56. As before, this refrigerant is expanded to a lower intermediate pressure and temperature in an expansion device 90 and injected into the compression process. This refrigerant transverses the injection refrigerant line 74 but does not transverse a heat exchanger economizer 88 and therefore has a higher thermodynamic cooling potential while injected into the compression process.
- This tapped refrigerant is injected into the compression process at the intermediate point 76 and is typically used to reduce the refrigerant discharge temperature, in order to avoid the situations where it exceeds the allowable limit, which is likely to occur in a transcritical regime of operation.
- Such refrigerant injection is carefully and selectively designed to provide sufficiently low discharge temperature while conducting the injection process above the critical pressure, as shown in Figure 3B, at least at some environmental conditions and for at least a portion of the operational time. This would also allow reduction of the compressor power, since the injected refrigerant is only compressed from a higher supercritical pressure to a discharge pressure (also supercritical).
- the refrigerant injection is associated with a higher compression stage 54, it also can be done between the higher and lower compression stages 54 and 52 respectively.
- multiple sequential compression stages can be represented by separate compressors, a single compression device or a combination of both.
- the economizer and injection cooling features can be incorporated in combination with each other into the same refrigerant system, and the two tapped refrigerant flows may be injected through the same or different injection points into the compression process. Further, these two performance enhancement features can be operated on demand, simultaneously or separately.
- the heat exchanger economizer 88 having a separate refrigerant tap line 82 and a separate expansion device 84 can be associated with the same (as the refrigerant injection cooling feature) refrigerant injection line 74.
- the economizer feature can be utilized to provide the performance boost for the refrigerant system 80, and the refrigerant injection cooling feature can be used for the refrigerant discharge temperature reduction.
- the same refrigerant tap line can be utilized for both performance enhancement features. If the expansion devices 84 and 90 are not equipped with a refrigerant flow shutoff capability, separate flow control devices may be provided.
- the system shown above can operate as a heating unit or as a cooling unit. It can also operate as a combination of a heating and cooling unit with an appropriate location of a four-way reversing valve (not shown), as known in the art.
- a single compressor or compression stage as shown in Figures IA and 2 A can be substituted by several compressor operating in tandem or as compressor banks operating in parallel (not shown).
- the refrigerant systems that utilize this invention can be used in many different applications, including, but not limited to, air conditioning systems, heat pump systems, marine container units, refrigeration truck-trailer units, and supermarket refrigeration systems.
- the expansion devices may be a fixed orifice, capillary tube, TXV, EXV or expanders.
- the economizer is illustrated as a heat exchanger economizer, it should be understood that a flash tank economizer may provide similar economizer function, as known in the art.
- the refrigerant injection lines can be equipped with shutoff valves (not shown) to selectively turn the refrigerant injection ON and OFF, in case the economizer expansion devices are not provided with a shutoff function.
- the optional bypass lines and corresponding valves can also be included to selectively bypass at least a portion of refrigerant from the refrigerant injection line to a lower compression point.
- both economized refrigerant systems 70 and 50 may tap a portion of a refrigerant flow for the economizer function either upstream or downstream of the first refrigerant pass of the economizer heat exchanger.
Abstract
Description
Claims
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/US2007/069505 WO2008150284A1 (en) | 2007-05-23 | 2007-05-23 | Refrigerant injection above critical point in a transcritical refrigerant system |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2153139A1 true EP2153139A1 (en) | 2010-02-17 |
EP2153139A4 EP2153139A4 (en) | 2012-10-10 |
Family
ID=40093952
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP07797666A Withdrawn EP2153139A4 (en) | 2007-05-23 | 2007-05-23 | Refrigerant injection above critical point in a transcritical refrigerant system |
Country Status (4)
Country | Link |
---|---|
US (1) | US20100024470A1 (en) |
EP (1) | EP2153139A4 (en) |
CN (1) | CN101688711A (en) |
WO (1) | WO2008150284A1 (en) |
Families Citing this family (16)
Publication number | Priority date | Publication date | Assignee | Title |
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CN101922823A (en) * | 2010-09-02 | 2010-12-22 | 广州德能热源设备有限公司 | Secondary air injection high-efficiency ultralow temperature heat pump unit |
DK2699853T3 (en) | 2011-04-21 | 2019-06-11 | Carrier Corp | TRANSCRIPTIONAL REFRIGERATORY VACUUM SYSTEM WITH CAPACITY RESIDENCE |
JP6300393B2 (en) * | 2012-11-20 | 2018-03-28 | 三星電子株式会社Samsung Electronics Co.,Ltd. | Air conditioner |
US9982929B2 (en) * | 2012-11-20 | 2018-05-29 | Samsung Electronics Co., Ltd. | Air conditioner |
JP6267483B2 (en) * | 2013-10-25 | 2018-01-24 | 日立ジョンソンコントロールズ空調株式会社 | Refrigerator unit and refrigeration equipment |
JP2016003840A (en) * | 2014-06-18 | 2016-01-12 | パナソニックIpマネジメント株式会社 | Refrigeration system and cooling coil |
US10119738B2 (en) | 2014-09-26 | 2018-11-06 | Waterfurnace International Inc. | Air conditioning system with vapor injection compressor |
CN104912772B (en) * | 2015-06-15 | 2018-01-19 | 珠海格力电器股份有限公司 | Compressor and there is its air conditioner |
CN105466080B (en) * | 2015-12-24 | 2017-09-12 | 宁波沃弗圣龙环境技术有限公司 | A kind of falling film type high temperature heat pump system |
CN105650919B (en) * | 2016-02-02 | 2018-11-30 | 珠海格力电器股份有限公司 | Air-conditioning system and jet degree of superheat adjusting method |
US10871314B2 (en) | 2016-07-08 | 2020-12-22 | Climate Master, Inc. | Heat pump and water heater |
US10866002B2 (en) | 2016-11-09 | 2020-12-15 | Climate Master, Inc. | Hybrid heat pump with improved dehumidification |
US10935260B2 (en) | 2017-12-12 | 2021-03-02 | Climate Master, Inc. | Heat pump with dehumidification |
US11592215B2 (en) | 2018-08-29 | 2023-02-28 | Waterfurnace International, Inc. | Integrated demand water heating using a capacity modulated heat pump with desuperheater |
CA3081986A1 (en) | 2019-07-15 | 2021-01-15 | Climate Master, Inc. | Air conditioning system with capacity control and controlled hot water generation |
CN111879030A (en) * | 2020-08-04 | 2020-11-03 | 深圳麦克维尔空调有限公司 | Air conditioner with two-stage economizer |
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- 2007-05-23 CN CN200780053089A patent/CN101688711A/en active Pending
- 2007-05-23 US US12/528,699 patent/US20100024470A1/en not_active Abandoned
- 2007-05-23 EP EP07797666A patent/EP2153139A4/en not_active Withdrawn
- 2007-05-23 WO PCT/US2007/069505 patent/WO2008150284A1/en active Application Filing
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See also references of WO2008150284A1 * |
Also Published As
Publication number | Publication date |
---|---|
US20100024470A1 (en) | 2010-02-04 |
EP2153139A4 (en) | 2012-10-10 |
CN101688711A (en) | 2010-03-31 |
WO2008150284A1 (en) | 2008-12-11 |
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