WO2018015185A1 - Système de réfrigération - Google Patents
Système de réfrigération Download PDFInfo
- Publication number
- WO2018015185A1 WO2018015185A1 PCT/EP2017/067200 EP2017067200W WO2018015185A1 WO 2018015185 A1 WO2018015185 A1 WO 2018015185A1 EP 2017067200 W EP2017067200 W EP 2017067200W WO 2018015185 A1 WO2018015185 A1 WO 2018015185A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- refrigerant
- heat exchanger
- suction gas
- condenser
- refrigeration system
- Prior art date
Links
- 238000005057 refrigeration Methods 0.000 title claims abstract description 34
- 239000003507 refrigerant Substances 0.000 claims abstract description 108
- 239000007788 liquid Substances 0.000 claims abstract description 30
- 238000009835 boiling Methods 0.000 claims abstract description 24
- 230000007423 decrease Effects 0.000 claims abstract description 6
- 230000009977 dual effect Effects 0.000 claims description 4
- 238000004891 communication Methods 0.000 description 10
- 239000012530 fluid Substances 0.000 description 9
- 102100029091 Exportin-2 Human genes 0.000 description 7
- 101710147878 Exportin-2 Proteins 0.000 description 7
- YBGRCYCEEDOTDH-JYNQXTMKSA-N evap protocol Chemical compound O=C1C=C[C@]2(C)[C@H]3[C@@H](O)C[C@](C)([C@@](CC4)(O)C(=O)CO)[C@@H]4[C@@H]3CCC2=C1.O([C@H]1C[C@@](O)(CC=2C(O)=C3C(=O)C=4C=CC=C(C=4C(=O)C3=C(O)C=21)OC)C(=O)CO)[C@H]1C[C@H](N)[C@H](O)[C@H](C)O1.COC1=C(O)C(OC)=CC([C@@H]2C3=CC=4OCOC=4C=C3C(O[C@H]3[C@@H]([C@@H](O)[C@@H]4O[C@H](C)OC[C@H]4O3)O)[C@@H]3[C@@H]2C(OC3)=O)=C1.C([C@H](C[C@]1(C(=O)OC)C=2C(=C3C([C@]45[C@H]([C@@]([C@H](OC(C)=O)[C@]6(CC)C=CCN([C@H]56)CC4)(O)C(=O)OC)N3C)=CC=2)OC)C[C@@](C2)(O)CC)N2CCC2=C1NC1=CC=CC=C21 YBGRCYCEEDOTDH-JYNQXTMKSA-N 0.000 description 6
- 230000009286 beneficial effect Effects 0.000 description 4
- 238000001704 evaporation Methods 0.000 description 4
- 230000008020 evaporation Effects 0.000 description 4
- 239000000463 material Substances 0.000 description 4
- 238000013021 overheating Methods 0.000 description 4
- 101150099000 EXPA1 gene Proteins 0.000 description 3
- 102100029095 Exportin-1 Human genes 0.000 description 3
- 101100119348 Saccharomyces cerevisiae (strain ATCC 204508 / S288c) EXP1 gene Proteins 0.000 description 3
- 101100269618 Streptococcus pneumoniae serotype 4 (strain ATCC BAA-334 / TIGR4) aliA gene Proteins 0.000 description 3
- 108700002148 exportin 1 Proteins 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 238000013459 approach Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000012546 transfer Methods 0.000 description 2
- 230000032258 transport Effects 0.000 description 2
- 235000016936 Dendrocalamus strictus Nutrition 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000002860 competitive effect Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000001627 detrimental effect Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 229910000679 solder Inorganic materials 0.000 description 1
- 230000001131 transforming effect 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
- 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
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
-
- 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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
-
- 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
- F25B2600/2501—Bypass valves
-
- 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
Definitions
- the present invention relates to a refrigeration system comprising a compressor for compressing a gaseous refrigerant, such that the temperature and pressure thereof increase, whereas the boiling point thereof decreases, a condenser, in which the gaseous refrigerant from the compressor exchanges heat with a high temperature heat carrier, said heat exchange resulting in the refrigerant condensing, an expansion valve reducing the pressure of liquid refrigerant from the condenser, hence reducing the boiling point of the refrigerant, an evaporator, in which the low boiling point refrigerant exchanges heat with a low temperature heat carrier, such that the refrigerant vaporizes, and a suction gas heat exchanger exchanging heat between high temperature liquid refrigerant from the condenser and high temperature gaseous refrigerant from the evaporator.
- all heat exchangers comprised in a refrigeration system should be as large and efficient as possible. Also, they should have an as low hold-up volume as possible, and a low pressure drop. As could be understood, these criteria cannot all be met.
- BPHE compact brazed plate heat exchanger
- heat exchangers comprise a number of plates made from sheet metal and provided with a pressed pattern of ridges and grooves adapted to keep the plates on a distance from one another under formation of interplate flow channels for the media to exchange heat.
- the plates are brazed to one another, meaning that each plate pair will be active in containing the refrigerant under pressure in the heat exchanger.
- Brazed plate heat exchangers have the benefit that virtually all material in the heat exchanger is actually active for heat exchange, unlike the heat exchangers comprising a shell, wherein the shell has the sole purpose of containing the refrigerant.
- suction gas heat exchanger may be arranged by simply placing the piping from the evaporator to the compressor in the vicinity of the piping from the condenser to the expansion valve close to one another and braze or solder them together, such that heat may be transferred between the pipings.
- a suction gas heat exchanger may be arranged by simply placing the piping from the evaporator to the compressor in the vicinity of the piping from the condenser to the expansion valve close to one another and braze or solder them together, such that heat may be transferred between the pipings.
- the BPHE could be competitive with the flooded shell and tube heat exchanger also in terms of efficiency, while retaining its benefits in terms of compactness and material efficiency.
- a refrigeration system according to the preamble of the attached independent claim, further comprising means for controlling the amount of heat exchange in the suction gas heat exchanger.
- the means for controlling the amount of heat exchange in the suction gas heat exchanger may a controllable by -pass valve, which controls the amount of refrigerant bypassing the suction gas heat exchanger. This embodiment is beneficial in that the refrigeration will be relatively easy to control.
- the bypass valve may bypass liquid refrigerant from the condenser.
- the means for controlling the amount of heat exchange in the suction gas heat exchanger comprises dual expansion valves, wherein a first of the expansion valves is connected between an inlet of the evaporator and the suction gas heat exchanger and a second of the expansion valves is connected between the inlet of the evaporator and the condenser.
- This embodiment is beneficial in that it allows full bypass of the suction gas heat exchanger.
- the dual expansion valves may be controllable.
- Fig. 1 is a schematic plan view showing a refrigeration system according to a first embodiment
- Fig. 2 is a schematic plan view showing refrigeration systems according to a second and a third embodiment.
- Fig. 3 is a schematic plan view showing a refrigeration system according to a fourth embodiment. DESCRIPTON OF EMBODIMENTS
- a refrigeration system according to a first embodiment comprises a compressor C, an outlet of which being connected to an inlet opening CI of a condenser COND.
- This inlet opening is in fluid communication with an outlet opening C3.
- An inlet opening C4 is in fluid communication with an outlet opening C2, and a heat carrier flows between these inlet and outlet openings under heat exchange with initially gaseous refrigerant delivered from the outlet of the compressor C to the inlet CI of the condenser COND. Due to the heat exchange, the initially gaseous refrigerant will condensate during its passage between the inlet CI and the outlet C3.
- the outlet C3 is fluidly connected to both an inlet EXP 1 of an expansion valve EXPV and an inlet S 1 of a suction gas heat exchanger SGHX.
- the inlet SI is in fluid communication with an outlet S4 of the suction gas heat exchanger SGHX, wherein the outlet S4 is in fluid communication with an inlet EXP2 of the expansion valve EXPV.
- the expansion valve EXPV is in fluid communication with an inlet El of an evaporator EVAP, and the inlets EXP 1 and EXP2 can be individually controlled to decide whether the refrigerant shall travel directly from the outlet C3 of the condenser COND or via the suction gas heat exchanger SGHX, or both.
- the inlet El is in fluid communication with an outlet E3 of the evaporator EVAP, and during the passage between the inlet El and the outlet E2, the refrigerant will absorb heat from a heat carrier flowing from an inlet E4 to an outlet E2 of the evaporator EVAP. During its passage between the inlet El and the outlet E3, the refrigerant will evaporate by absorbing heat from the heat carrier flowing between the inlet E4 and the outlet E2.
- the outlet E3 is in fluid communication with an inlet S2 of the suction gas heat exchanger SGHX, which in turn is in fluid communication with an outlet S3 of the suction gas heat exchanger SGHX.
- the outlet S3 is in fluid communication with the compressor C, meaning that the refrigerant circle now is complete.
- a refrigeration cycle transports heat between a low temperature source and a high temperature source. This is achieved by two different temperature and pressure levels in the refrigeration circuit, namely a high pressure, high temperature zone on a condenser side of the refrigeration circuit between the compressor C and the expansion vale EXPV, and a low temperature, low pressure side on an evaporator side between the expansion valve EXPV and the compressor C.
- suction gas heat exchanger SGHX The purpose of the suction gas heat exchanger SGHX is to allow a heat exchange between cool gaseous refrigerant from the evaporator EVAP and warm liquid refrigerant from the condenser C. This has two effects: 1. The temperature of the gaseous refrigerant exiting the evaporator will be higher, meaning that its density will be lower.
- the temperature of the liquid refrigerant about to enter the expansion valve will be lower, which will minimize flash boiling of the refrigerant during its passage through the expansion valve.
- EXP 1 and EXP2 may be separate expansion valves.
- the expansion valve EXPV is a single expansion valve, i.e. an expansion valve having a single inlet for all liquid refrigerant.
- the amount of heat exchange in the suction gas is controlled by a bypass valve BPl, which when opened allows warm liquid refrigerant from the condenser COND to bypass the suction gas heat exchanger, hence reducing the amount of heat exchange in the suction gas heat exchanger.
- a second bypass valve BP2 is arranged to control the communication between the condenser COND and the suction gas heat exchanger.
- FIG. 3 A fourth embodiment is shown in Fig. 3. According to this embodiment, all warm liquid refrigerant from the condenser will pass the suction gas heat exchanger SGHX. The amount of heat exchange in the suction gas heat exchanger SGHX is controlled by an expansion valve EXPV3.
- the high pressure level reaching from the compressor C to the EXPV3.
- the boiling point of the refrigerator will be such that it may condense under heat exchange with the high temperature heat source in the condenser COND.
- expansion valve EXPV i.e. the "normal" expansion valve
- the boiling point of the refrigerant is controlled such that a desired heat exchange between liquid refrigerant from the condenser C and the gaseous refrigerant from the evaporator EVAP is achieved in the suction gas heat exchanger SGHX.
- the refrigerant pressure level is such that the refrigerant has a boiling point slightly lower than the temperature of the low temperature heat source with which the refrigerant exchanges heat in order to vaporize.
- a high ratio between the high pressure side and the low pressure side will allow for a large temperature difference between the source where heat is collected and the temperature source to which the heat is delivered.
- the expansion valves (which, together with the compressor, control the pressure ratio between the high pressure side and the low pressure side) will be impossible to control if the refrigerant passing there through contains any gas at all.
- the pressure ratio between the high pressure side and the low pressure side should be such that the refrigerant boiling point on the low pressure side is identical to the temperature of the low temperature heat source.
- the pressure ratio between the high pressure side and the low pressure side should be such that the refrigerant boiling temperature on the high pressure side is identical to the temperature of the high temperature heat source.
- the pressure ratio must be slightly higher than the theoretically optimal temperature, i.e. such that the refrigerant boiling temperature on the low pressure side is lower than the low temperature heat source and the refrigerant boiling temperature on the high pressure side is higher than the temperature of the high temperature heat source.
- the difference between the low pressure refrigerant boiling temperature and the low temperature heat source may cause overheating of the gaseous refrigerant leaving the evaporator.
- controllable suction gas heat exchanger presented herein, it is possible to control the overheating of the gaseous refrigerant, hence making it possible to fine- tune the pressure ratio to an optimum level, while securing that the overheating is neither too extensive - causing bad compressor efficiency - nor too low - causing refrigerant droplets entering the compressor, hence risking total compressor failure.
- expansion valves and the bypass valves used in the different embodiments of the invention are controllable, either in an analogue manner, i.e. by provision of pressure, temperature or pressure ratio sensing means being connected to the valve, e.g. by a capillary tube connected to a bulb in thermal contact with the refrigerant, the temperature of which should control the bypass or expansion valve.
- bypass valves and expansion valves it is possible to control the amount of heat exchange in the suction gas heat exchanger based on virtually any measured value, e.g. pressure ratio, temperature, compressor speed, load, etc, etc.
- bypass and expansion valves By controlling the expansion valves and/or bypass valves, it is possible to optimize a refrigeration system presented herein such that it performs as well at part load as it does on full load.
- the bypass and expansion valves will be controlled such that little or no heat exchange takes place in the suction gas heat exchanger during part load conditions, whereas they will be controlled such that the heat exchange in the suction gas heat exchanger will be significant during full load conditions.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
Ce système de réfrigération comporte un compresseur pour comprimer un réfrigérant gazeux, de telle sorte que la température et la pression de celui-ci augmentent, et que le point d'ébullition de celui-ci diminue. Le système de réfrigération comporte également un condenseur, dans lequel le réfrigérant gazeux provenant du compresseur échange de la chaleur avec un caloporteur à haute température. Cet échange de chaleur conduit à la condensation du réfrigérant. Un détendeur dans le système de réfrigération réduit la pression du réfrigérant liquide provenant du condenseur, réduisant ainsi le point d'ébullition du réfrigérant. Le système de réfrigération comporte en outre un évaporateur, dans lequel le réfrigérant à bas point d'ébullition échange de la chaleur avec un caloporteur à basse température, de telle sorte que le réfrigérant se vaporise, et un échangeur de chaleur de gaz d'aspiration qui échange de la chaleur entre le réfrigérant liquide à haute température provenant du condenseur et le réfrigérant gazeux à haute température provenant de l'évaporateur. Des moyens sont prévus dans le système de réfrigération pour réguler la quantité d'échange de chaleur dans l'échangeur de chaleur à gaz d'aspiration.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| SE1651072 | 2016-07-18 | ||
| SE1651072-9 | 2016-07-18 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| WO2018015185A1 true WO2018015185A1 (fr) | 2018-01-25 |
Family
ID=20302363
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| PCT/EP2017/067200 WO2018015185A1 (fr) | 2016-07-18 | 2017-07-10 | Système de réfrigération |
Country Status (1)
| Country | Link |
|---|---|
| WO (1) | WO2018015185A1 (fr) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SE2050092A1 (en) * | 2020-01-30 | 2021-07-31 | Swep Int Ab | A refrigeration system and a method for controlling such a refrigeration system |
| CN114945781A (zh) * | 2020-01-30 | 2022-08-26 | 舒瑞普国际股份公司 | 制冷系统和方法 |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001235239A (ja) * | 2000-02-23 | 2001-08-31 | Seiko Seiki Co Ltd | 超臨界蒸気圧縮サイクル装置 |
| JP2005106413A (ja) * | 2003-09-30 | 2005-04-21 | Sanyo Electric Co Ltd | 冷媒サイクル装置 |
| DE102007014410A1 (de) * | 2006-03-31 | 2007-10-04 | Denso Corp., Kariya | Überkritischer Kreislauf und Expansionsventil zur Verwendung in einem solchen Kreislauf |
| EP1850075A1 (fr) * | 2006-04-25 | 2007-10-31 | Valeo Systèmes Thermiques | Circuit de climatisation à cycle supercritique |
| EP2489774A1 (fr) * | 2011-02-18 | 2012-08-22 | Electrolux Home Products Corporation N.V. | Sèche-linge à pompe à chaleur |
| DE102013113221A1 (de) * | 2013-11-29 | 2015-06-03 | Denso Automotive Deutschland Gmbh | Innerer Wärmetauscher mit variablem Wärmeübergang |
-
2017
- 2017-07-10 WO PCT/EP2017/067200 patent/WO2018015185A1/fr active Application Filing
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001235239A (ja) * | 2000-02-23 | 2001-08-31 | Seiko Seiki Co Ltd | 超臨界蒸気圧縮サイクル装置 |
| JP2005106413A (ja) * | 2003-09-30 | 2005-04-21 | Sanyo Electric Co Ltd | 冷媒サイクル装置 |
| DE102007014410A1 (de) * | 2006-03-31 | 2007-10-04 | Denso Corp., Kariya | Überkritischer Kreislauf und Expansionsventil zur Verwendung in einem solchen Kreislauf |
| EP1850075A1 (fr) * | 2006-04-25 | 2007-10-31 | Valeo Systèmes Thermiques | Circuit de climatisation à cycle supercritique |
| EP2489774A1 (fr) * | 2011-02-18 | 2012-08-22 | Electrolux Home Products Corporation N.V. | Sèche-linge à pompe à chaleur |
| DE102013113221A1 (de) * | 2013-11-29 | 2015-06-03 | Denso Automotive Deutschland Gmbh | Innerer Wärmetauscher mit variablem Wärmeübergang |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SE2050092A1 (en) * | 2020-01-30 | 2021-07-31 | Swep Int Ab | A refrigeration system and a method for controlling such a refrigeration system |
| CN114930097A (zh) * | 2020-01-30 | 2022-08-19 | 舒瑞普国际股份公司 | 制冷系统和用于控制这种制冷系统的方法 |
| CN114945781A (zh) * | 2020-01-30 | 2022-08-26 | 舒瑞普国际股份公司 | 制冷系统和方法 |
| US20230030270A1 (en) * | 2020-01-30 | 2023-02-02 | Swep International Ab | A refrigeration system and method |
| SE545516C2 (en) * | 2020-01-30 | 2023-10-03 | Swep Int Ab | A refrigeration system and method for controlling such a refrigeration system |
| US12140356B2 (en) | 2020-01-30 | 2024-11-12 | Swep International Ab | Refrigeration system and a method for controlling such a refrigeration system |
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