WO2009096193A1 - エコノマイザ - Google Patents
エコノマイザ Download PDFInfo
- Publication number
- WO2009096193A1 WO2009096193A1 PCT/JP2009/000365 JP2009000365W WO2009096193A1 WO 2009096193 A1 WO2009096193 A1 WO 2009096193A1 JP 2009000365 W JP2009000365 W JP 2009000365W WO 2009096193 A1 WO2009096193 A1 WO 2009096193A1
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- WIPO (PCT)
- Prior art keywords
- refrigerant
- liquid
- expansion valve
- tank
- gas
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
- F25B41/315—Expansion valves actuated by floats
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
- F25B1/053—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of turbine type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
- F25B2400/23—Separators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
Definitions
- the present invention relates to an economizer used in a multistage compression refrigeration apparatus.
- this two-stage compression refrigeration apparatus has been used.
- this two-stage compression refrigeration apparatus separates the gas refrigerant from the gas-liquid two-phase refrigerant and guides the gas refrigerant to the intermediate pressure portion of the two-stage compressor.
- An economizer is used (see, for example, Patent Document 1).
- the economizer described in FIG. 2 of Patent Document 1 includes an introduction part for introducing a refrigerant, a gas outlet part for introducing the separated gas refrigerant to the two-stage compressor, and a liquid outlet for introducing the separated liquid refrigerant to the evaporator. And a tank formed with a portion. The tank is provided with a float expansion valve that is attached to the liquid outlet and adjusts the amount of throttling in accordance with the liquid level of the liquid refrigerant.
- Japanese Patent Laid-Open No. 11-344265 Japanese Patent Laid-Open No. 11-344265
- the conventional economizer has only one liquid outlet, and a large amount of liquid refrigerant flows out from one liquid outlet. For this reason, the conventional economizer has to use a large float expansion valve, which increases the cost.
- a large float expansion valve which increases the cost.
- a larger float expansion valve is required, and thus the problem is serious.
- the present invention has been made in view of such a point, and an object thereof is to provide an economizer used in a multistage compression refrigeration apparatus at a low cost.
- the first invention includes a refrigerant circuit (20) in which a multistage compressor (21), a condenser (22), a multistage expansion mechanism (23, 25), and an evaporator (26) are sequentially connected.
- gas-liquid two-phase refrigerant is separated into gas and liquid, the gas refrigerant is guided to the intermediate pressure part of the multistage compressor (21), and the liquid refrigerant is fed to the evaporator (26
- the economizer includes an introduction part (24d) for introducing the refrigerant of the refrigerant circuit (20), a liquid outlet part (24b) for leading the liquid refrigerant to the evaporator (26), and the multistage compressor (21
- the liquid refrigerant flows out from the tank (24a) through the plurality of liquid outlet portions (24b), and the amount of the liquid refrigerant flowing out is the plurality of float expansion valves (25). Controlled by. Therefore, the control amount required for each float expansion valve (25) is smaller than when the outflow amount is controlled by one float expansion valve (25). Therefore, a small float expansion valve (25) can be used.
- the second invention is the first invention, wherein the liquid outlet part (24b) and the float expansion valve (25) are provided two by two.
- the outflow amount of the liquid refrigerant flowing out from the tank (24a) is controlled by the two float expansion valves (25).
- required by one float expansion valve (25) becomes a half of the past, a float expansion valve (25) smaller than before can be used.
- the tank (24a) is a horizontally long tank
- the introduction portion (24d) is formed at a central portion in the longitudinal direction of the tank (24a)
- the liquid outlet portion (24b) and the float expansion valve (25) are arranged one by one on both sides of the introduction part (24d) in the longitudinal direction of the tank (24a).
- the float expansion valve (25) is arranged on both sides of the introduction part (24d) in the longitudinal direction of the tank (24a). Thereby, each float expansion valve (25) is arrange
- the tank (24a) is crossed between the introduction part (24d), the two liquid outlet parts (24b) and the float expansion valve (25). Baffles (24e, 24f) extending in the surface direction are provided.
- the baffle plates (24e, 24f) are provided between the introduction part (24d) and the float expansion valve (25), the refrigerant introduced from the introduction part (24d) is used as the float expansion valve (25). Direct spraying is avoided.
- the liquid outlet portion is longer than the baffle plates (24e, 24f) in the longitudinal direction of the tank (24a). It is arranged on the (24b) side.
- the gas refrigerant is not concentrated to the gas refrigerant from one gas outlet (24c) but is sucked by being distributed to the two gas outlets (24c). Therefore, compared with the case where only one gas outlet part (24c) is provided, the force at which each gas outlet part (24c) sucks the gas refrigerant is halved. Thereby, the rise in the liquid refrigerant level caused by the suction of the gas refrigerant near the gas outlet (24c) is suppressed. As a result, a so-called liquid return in which a part of the liquid refrigerant is sucked from the gas outlet (24c) to the multistage compressor (21) side is avoided.
- a small float expansion valve (25) can be used.
- the unit price of the float expansion valve (25) can be significantly reduced, and the cost can be reduced.
- the present invention since a plurality of float expansion valves (25) are provided, even if one float expansion valve (25) does not operate due to a malfunction, the other float expansion valve (25) causes liquid refrigerant to flow. Pressure reduction and liquid level control in the tank (24a) can be performed. Therefore, even when a malfunction occurs in the float expansion valve (25), the operation can be continued by partial load operation or the like without immediately stopping the operation of the multistage compression refrigeration apparatus (1).
- the unit price of the float expansion valve (25) can be significantly reduced, and the number of float expansion valves (25) can be reduced to two. The cost for the entire economizer can be reduced.
- each float expansion valve (25) is disposed at a distance from the introduction portion (24d)
- the refrigerant introduced from the introduction portion (24d) is used as the float expansion valve (25).
- the baffle plates (24e, 24f) are provided, so that the gas-liquid separation is reliably performed when the gas-liquid two-phase refrigerant collides with the baffle plates (24e, 24f). be able to. Furthermore, it is possible to prevent the refrigerant introduced from the introduction part (24d) from directly blowing on the float expansion valve (25) and affecting the operation of the float expansion valve (25).
- the fifth aspect of the invention it is possible to suppress an increase in the liquid refrigerant level caused by the suction of the gas refrigerant near the gas outlet (24c). Therefore, it is possible to prevent so-called liquid return that a part of the liquid refrigerant is sucked from the gas outlet (24c) to the multistage compressor (21) side.
- FIG. 1 is a piping system diagram illustrating a schematic configuration of a multistage turbo chiller according to an embodiment.
- FIG. 2 is a longitudinal sectional view of the economizer.
- 3A is a cross-sectional view taken along line IIIA-IIIA in FIG. 2
- FIG. 3B is a cross-sectional view taken along line IIIB-IIIB in FIG.
- Two-stage turbo refrigerator (multistage compression refrigeration system) 20 Refrigerant circuit 21 Two-stage turbo compressor (multistage compressor) 22 Condenser 23 High-stage expansion valve (multi-stage expansion mechanism) 24 economizer 24a tank 24b liquid outlet 24c gas outlet 24d introduction part 24e first partition (baffle plate) 24f 2nd partition wall (binder plate) 25 Float expansion valve (multistage expansion mechanism) 25a Valve body 25b Float 26 Evaporator 28 Gas piping
- a two-stage turbo chiller including a two-stage turbo compressor will be described as a multistage compression refrigeration apparatus using the economizer according to the present invention.
- FIG. 1 is a piping system diagram schematically showing the configuration of a two-stage turbo chiller (1) according to an embodiment of the present invention.
- the two-stage turbo refrigerator (1) includes a two-stage turbo compressor (21), a condenser (22), a high stage side expansion valve (23), and a float stage expansion valve (25) that is a low stage side expansion valve.
- an evaporator (26) are sequentially connected by a refrigerant pipe to provide a refrigerant circuit (20) for performing a vapor compression refrigeration cycle.
- an economizer (24) including the float expansion valve (25) is provided between the high-stage expansion valve (23) and the evaporator (26) of the refrigerant circuit (20).
- the high-stage expansion valve (23) and the float expansion valve (25) constitute a multistage expansion mechanism.
- the two-stage turbo compressor (21) includes a low stage impeller (21a) and a high stage impeller (21b).
- the low stage impeller (21a) and the high stage impeller (21b) are connected in series.
- the two-stage turbo compressor (21) is provided with a suction capacity control mechanism (21c) for controlling the suction capacity and a discharge capacity control mechanism (21d) for controlling the discharge capacity.
- the low-stage impeller (21a) sucks low-pressure (PL) refrigerant, compresses it to an intermediate pressure (PM), and supplies it to the high-stage impeller (21b).
- the high stage impeller (21b) sucks an intermediate pressure (PM) refrigerant, compresses it to a high pressure (PH), and discharges a high pressure (PH) gas refrigerant.
- the condenser (22) is a so-called shell-and-tube condenser including a shell (cylindrical copper) and a plurality of cooling pipes arranged in the shell.
- a high-pressure (PH) gas refrigerant compressed in the two-stage turbo compressor (21) is introduced into the shell, and the gas refrigerant is cooled by cooling water flowing in the cooling pipe.
- PH high-pressure
- the high-stage expansion valve (23) is formed by a temperature-sensitive automatic expansion valve that controls the suction refrigerant superheat degree to a constant level by adjusting the amount of decompression according to the suction refrigerant superheat degree.
- the liquid refrigerant condensed in the condenser (22) is decompressed to the intermediate pressure (PL) by the high stage side expansion valve (23) and introduced into the economizer (24).
- the economizer (24) is connected to a gas pipe (28) connected to the intermediate pressure part of the two-stage turbo compressor (21).
- the intermediate pressure (PL) gas refrigerant is led to the intermediate pressure portion of the two-stage turbo compressor (21) via the gas pipe (28), while the liquid refrigerant is led to the evaporator (26). It is burned.
- the float expansion valve (25) is configured to adjust the throttle amount in accordance with the liquid level of the liquid refrigerant in the economizer (24), and is built in the economizer (24). That is, the economizer (24) reduces the pressure by the float expansion valve (25) when the gas-liquid separated liquid refrigerant flows out toward the evaporator (26).
- the evaporator (26) is constituted by a full liquid evaporator, and in this embodiment, is constituted by a so-called shell and tube type evaporator.
- the liquid refrigerant that has been gas-liquid separated in the economizer (24) is supplied by being decompressed by the float expansion valve (25).
- a heat transfer tube is provided in the shell, and water as an object to be cooled flows in the heat transfer tube.
- the liquid refrigerant supplied into the shell absorbs heat from the water in the heat transfer tube, evaporates, and is converted into a gas that is led to the suction side of the two-stage turbo compressor (21).
- the economizer (24) is a horizontally long tank composed of a cylindrical body portion and closed portions that close both ends of the body portion ( 24a).
- the tank (24a) has an introduction part (24d) for introducing the refrigerant of the refrigerant circuit (20), a liquid outlet part (24b) for guiding the internal liquid refrigerant to the evaporator (26), and an internal gas refrigerant And a gas outlet part (24c) for guiding the gas to the intermediate pressure part of the two-stage turbo compressor (21).
- the introduction part (24d) is formed in the central part in the longitudinal direction of the tank (24a). As shown in FIG. 3A, the introduction portion (24d) is configured by a cylindrical body that penetrates the inside and outside of the tank (24a), curves in the tank (24a), and opens upward.
- liquid outlet portions (24b) are provided as shown in FIG.
- the two liquid outlet portions (24b) are formed at both ends in the longitudinal direction of the tank (24a).
- the liquid outlet part (24b) is formed by a cylindrical body that penetrates the inside and outside of the tank (24a), curves in the tank (24a), and opens downward.
- the two gas outlet portions (24c) are arranged one on each side of the introduction portion (24d) in the longitudinal direction of the tank (24a).
- the gas outlet (24c) is formed of a cylindrical body, extends downward from the upper side of the tank (24a), and has a tip that penetrates the upper surface of the tank (24a) and opens at the upper part of the tank (24a). Yes.
- the float expansion valve (25) described above is attached to the inflow side end of the liquid outlet (24b).
- the float expansion valve (25) includes a valve body (25a) formed at an inflow side end of a liquid outlet portion (24b) made of a cylindrical body, and a valve body ( And a float (25b) connected to 25a).
- the valve body (25a) moves in the direction of expanding the flow path in the liquid outlet (24b), and when the float (25b) descends, the flow in the liquid outlet (24b) It is configured to move in the direction of narrowing the road.
- the float expansion valve (25) has its throttle amount reduced when the liquid level in the tank (24a) rises, and increases when the liquid level falls, The outflow amount of the liquid is controlled in accordance with the circulation amount of the refrigerant.
- the introduction part (24d), the two liquid outlet parts (24b) and the float expansion valve (25) two kinds of partition walls (24e, 24e, extending in the cross-sectional direction of the tank (24a)) are provided.
- 24f) is provided.
- the first partition wall (24e) provided on the introduction part (24d) side is formed of a substantially circular plate-like body, and is formed with a substantially T-shaped notch.
- the 2nd partition (24f) provided in the liquid outlet part (24b) side is formed with the plate-shaped body formed in reverse T shape.
- the said 1st partition (24e) and the 2nd partition (24f) are provided in parallel at predetermined intervals, and comprise the baffle plate.
- the inside of the tank (24a) is divided into three spaces by the first partition wall (24e) and the second partition wall (24f). Specifically, the inside of the tank (24a) is formed in a central space where the introduction part (24d) is located and on both sides of the central space, and the liquid outlet part (24b) and the float expansion valve (25) It is partitioned into a side space. As shown in FIG. 3B, when the side space on the introduction portion (24d) side is viewed from the central space of the liquid outlet portion (24b), most of the cross section of the tank (24a) is the first. It is covered with a partition wall (24e) and a second partition wall (24f). With such a configuration, it is possible to prevent the refrigerant introduced from the introduction part (24d) from directly spraying on the float (25b) of the float expansion valve (25).
- the two gas outlets (24c) described above are disposed closer to the liquid outlet (24b) than the first partition (24e) and the second partition (24f). That is, the gas outlet portion (24c) is a central space in which the introduction portion (24d) is provided among the three spaces defined in the tank (24a) by the first partition wall (24e) and the second partition wall (24f). Instead, it is provided in each side space provided with the liquid outlet part (24b). By arranging the gas outlet part (24c) in the side space in this way, the gas-liquid two-phase refrigerant introduced from the introduction part (24d) is directly sucked into the gas outlet part (24c). Can be prevented.
- the low-stage and high-stage impellers (21a, 21b) of the two-stage turbo compressor (21) rotate, and the low-pressure (in the refrigerant circuit (20) ( PL) refrigerant is inhaled.
- the refrigerant capacity to be sucked is adjusted by the suction capacity control mechanism (21c).
- the low-pressure (PL) refrigerant sucked into the low-stage impeller (21a) is compressed to the intermediate pressure (PM) and supplied to the high-stage impeller (21b).
- the high-stage impeller (21b) compresses intermediate pressure (PM) refrigerant into high pressure (PH) gas refrigerant and discharges it to the refrigerant circuit (20).
- the refrigerant capacity discharged by the discharge capacity control mechanism (21d) is adjusted.
- the high-pressure (PH) refrigerant discharged from the two-stage turbo compressor (21) to the refrigerant circuit (20) is cooled and condensed in the condenser (22).
- the condensed liquid refrigerant is decompressed to the intermediate pressure (PL) by the high stage side expansion valve (23) and introduced into the economizer (24).
- the decompression amount of the high stage side expansion valve (23) is adjusted according to the degree of superheat of the suction refrigerant.
- the refrigerant circulation amount is controlled so that the suction refrigerant superheat degree becomes a predetermined value.
- the introduced gas-liquid two-phase refrigerant is gas-liquid separated.
- the gas refrigerant after the gas-liquid separation is led to the intermediate pressure part of the two-stage turbo compressor (21) via the gas pipe (28), while the liquid refrigerant is led to the evaporator (26) side.
- the intermediate pressure (PM) gas refrigerant introduced to the intermediate pressure section of the two-stage turbo compressor (21) is compressed by the low pressure impeller (21a) of the two-stage turbo compressor (21) ( PM) and mixed into the higher stage impeller (21b) for compression.
- the low-pressure (PL) refrigerant thus depressurized by the float expansion valve (25) and supplied to the evaporator (26) absorbs heat from the water in the heat transfer pipe and evaporates to become a gas, which is a two-stage turbocharger. Guided to the suction side of the compressor (21). The gas refrigerant is compressed by the two-stage turbo compressor (21).
- the refrigerant introduced from the introduction part (24d) into the central space in the tank (24a) flows from the central space to the side spaces on both sides in the tank (24a).
- the refrigerant collides with both the partition walls (24e, 24f) and the inner wall surface of the tank (24a), whereby the gas and liquid are separated.
- the separated liquid refrigerant flows down along both the partition walls (24e, 24f) and the inner wall surface of the tank (24a), and accumulates at the bottom of the tank (24a).
- the gas refrigerant passes through both partition walls (24e, 24f) and flows into the side space on the liquid outlet (24b) side.
- the liquid refrigerant flows from the liquid outlet (24b) to the evaporator (26).
- the flow path formed in the liquid outlet part (24b) is throttled by the valve body (25a) of the float expansion valve (25). Therefore, the liquid refrigerant is decompressed by the float expansion valve (25).
- the throttle amount of the float expansion valve (25) is adjusted according to the liquid level of the liquid refrigerant in the tank (24a). That is, when the liquid level rises, the float (25b) rises and the valve body (25a) moves in a direction in which the flow path in the liquid outlet part (24b) further expands. As a result, the throttle amount decreases and the outflow amount of the liquid refrigerant increases, and the rising speed of the liquid level is slowed or the liquid level is lowered. On the other hand, when the liquid level is lowered, the float (25b) is lowered, and the valve body (25a) moves in a direction to further restrict the flow path of the liquid outlet part (24b).
- the throttle amount increases and the outflow amount of the liquid refrigerant decreases, and the descending speed of the liquid level is slowed or the liquid level rises.
- the float expansion valve (25) controls the throttling amount of the liquid refrigerant in the tank (24a) according to the refrigerant circulation amount.
- the gas refrigerant is sucked from the gas outlet part (24c) into the intermediate pressure part of the two-stage turbo compressor (21).
- the gas refrigerant is not intensively sucked from one gas outlet portion (24c), but is drawn into the two gas outlet portions (24c). Dispersed and sucked. Therefore, when the gas refrigerant is sucked, the vicinity of the gas outlet (24c) is lower in pressure than the other parts in the tank (24a), but compared with the case where there is only one gas outlet (24c), The degree of low pressure can be reduced.
- the economizer (24) is provided with two liquid outlet portions (24b) and two float expansion valves (25), which are conventionally provided only one. Therefore, liquid refrigerant flows out from the tank (24a) through the two liquid outlet portions (24b), and the outflow amount of the liquid refrigerant is controlled by the two float expansion valves (25). Become. Thereby, compared with the case where the outflow amount is controlled by one float expansion valve (25), the control amount required for each float expansion valve (25) is reduced. Therefore, the economizer (24) can use a small float expansion valve (25), and can greatly reduce the unit price of the float expansion valve (25). Therefore, the cost of the economizer (24) can be reduced.
- the economizer (24) is provided with two float expansion valves (25). Therefore, even if one float expansion valve (25) does not operate due to a malfunction, the pressure reduction of the liquid refrigerant and the liquid level control in the tank (24a) can be performed by the other float expansion valve (25). Therefore, even when a malfunction occurs in one float expansion valve (25), the operation of the two-stage turbo chiller (1) can be continued by partial load operation or the like without immediately stopping the operation. .
- the number of the liquid outlet part (24b) and the float expansion valve (25) is two, but three or more liquid outlet parts (24b) and the float expansion valve (25) may be provided. Good. Even in this case, the float expansion valve (25) can be downsized, and the economizer (24) can be manufactured at low cost. On the other hand, in this embodiment, the number of float expansion valves (25) is set to two, so that the size of the float expansion valve (25) is reduced and the unit price is greatly reduced, and the cost of the economizer (24) is further reduced. Can be reduced.
- each float expansion valve (25) is arranged on both sides of the introduction part (24d) in the longitudinal direction of the tank (24a). Therefore, each float expansion valve (25) is arranged with a space from the introduction part (24d). Thereby, it can be avoided that the refrigerant introduced from the introduction part (24d) is sprayed on the float (25b) of the float expansion valve (25). Therefore, it is possible to prevent the introduced refrigerant from affecting the operation of the float expansion valve (25).
- the economizer (24) has a plate-like shape extending in the cross-sectional direction of the tank (24a) between the introduction part (24d), the two liquid outlet parts (24b), and the float expansion valve (25). Body partition walls (24e, 24f) are provided. Thereby, the gas-liquid two-phase gas-liquid is separated, and the refrigerant introduced from the introduction part (24d) directly blows on the float (25b) of the float expansion valve (25) to float the float expansion valve (25). It is possible to prevent the operation from being affected.
- the economizer (24) is provided with two gas outlets (24c), and is arranged one on each side of the introduction part (24d) in the longitudinal direction of the tank (24a).
- the gas refrigerant is not intensively sucked from one gas outlet part (24c) but is sucked by being distributed to two gas outlet parts (24c). Therefore, compared with the case where only one gas outlet part (24c) is provided, the force at which each gas outlet part (24c) sucks the gas refrigerant is halved. Thereby, the rise of the liquid refrigerant surface caused by the suction of the gas refrigerant in the vicinity of the gas outlet (24c) can be suppressed. As a result, a so-called liquid return in which part of the liquid refrigerant is sucked from the gas outlet (24c) to the two-stage turbo compressor (21) side can be avoided.
- the number of the liquid outlet part (24b) and the float expansion valve (25) is two, but three or more liquid outlet parts (24b) and the float expansion valve (25) may be provided. Even in this case, the float expansion valve (25) can be downsized, and the economizer (24) can be manufactured at low cost.
- the introduction part (24d), the liquid outlet part (24b), and the gas outlet part (24c) are formed by the cylindrical body, but these may be formed by simple openings.
- the two-stage compression / two-expansion refrigeration apparatus has been described as the multistage compression refrigeration apparatus including the economizer (24) according to the present invention. You may apply to a multistage compression refrigerating apparatus. At that time, a plurality of the economizers are arranged in series.
- the present invention is useful for a turbo refrigerator.
Abstract
Description
20 冷媒回路
21 二段ターボ圧縮機(多段圧縮機)
22 凝縮器
23 高段側膨張弁(多段膨張機構)
24 エコノマイザ
24a タンク
24b 液出口部
24c ガス出口部
24d 導入部
24e 第1隔壁(じゃま板)
24f 第2隔壁(じゃま板)
25 フロート膨張弁(多段膨張機構)
25a 弁体
25b フロート
26 蒸発器
28 ガス配管
以上より、本実施形態に係るエコノマイザ(24)は、従来1つしか設けられていなかった液出口部(24b)とフロート膨張弁(25)とが2つずつ設けられている。そのため、タンク(24a)内からは、2つの液出口部(24b)を介して液冷媒が流出することとなり、その液冷媒の流出量は2つのフロート膨張弁(25)によって制御されることとなる。これにより、1つのフロート膨張弁(25)によって流出量を制御する場合に比べ、1つ1つのフロート膨張弁(25)に求められる制御量が小さくなる。従って、上記エコノマイザ(24)は、小型のフロート膨張弁(25)を用いることができ、フロート膨張弁(25)の単価を大幅に抑えることができる。そのため、エコノマイザ(24)のコストを削減することができる。
上記実施形態では、液出口部(24b)及びフロート膨張弁(25)の個数を2つとしていたが、液出口部(24b)及びフロート膨張弁(25)は3つ以上設けることとしてもよい。その場合であっても、フロート膨張弁(25)を小型化することができ、エコノマイザ(24)を安価に製造することができる。
Claims (5)
- 多段圧縮機(21)と、凝縮器(22)と、多段膨張機構(23,25)と、蒸発器(26)とが順次接続された冷媒回路(20)を備えた多段圧縮式冷凍装置(1)に設けられ、気液二相状態の冷媒を気液分離し、ガス冷媒を上記多段圧縮機(21)の中間圧力部に導くと共に液冷媒を上記蒸発器(26)に導くエコノマイザであって、
上記冷媒回路(20)の冷媒を導入する導入部(24d)と、上記蒸発器(26)に液冷媒を導出するための液出口部(24b)と、上記多段圧縮機(21)の中間圧力部にガス冷媒を導入するためのガス出口部(24c)とが形成されたタンク(24a)と、
上記多段膨張機構(23,25)の一部を構成する膨張弁であって、上記液出口部(24b)に取り付けられ、上記タンク(24a)内の液冷媒の液面高さに応じて絞り量が調整されるフロート膨張弁(25)とを備え、
上記液出口部(24b)及び上記フロート膨張弁(25)は複数設けられている
ことを特徴とするエコノマイザ。 - 請求項1において、
上記液出口部(24b)及び上記フロート膨張弁(25)は2つずつ設けられている
ことを特徴とするエコノマイザ。 - 請求項2において、
上記タンク(24a)は横長のタンクであり、
上記導入部(24d)は上記タンク(24a)の長手方向の中央部に形成され、
上記液出口部(24b)及び上記フロート膨張弁(25)は、上記タンク(24a)の長手方向において、上記導入部(24d)の両側方に1つずつ配置されている
ことを特徴とするエコノマイザ。 - 請求項3において、
上記導入部(24d)と2つの上記液出口部(24b)及びフロート膨張弁(25)とのそれぞれの間には、上記タンク(24a)の横断面方向に延びるじゃま板(24e,24f)が設けられている
ことを特徴とするエコノマイザ。 - 請求項4において、
上記ガス出口部(24c)は2つ設けられ、上記タンク(24a)の長手方向において、それぞれ上記じゃま板(24e,24f)よりも上記液出口部(24b)側に配置されている
ことを特徴とするエコノマイザ。
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US12/865,580 US9027363B2 (en) | 2008-02-01 | 2009-01-30 | Economizer having multiple liquid outlets and multiple float expansion valves |
CN2009801034360A CN101932890B (zh) | 2008-02-01 | 2009-01-30 | 经济器 |
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JP2008023356A JP4404148B2 (ja) | 2008-02-01 | 2008-02-01 | エコノマイザ |
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CN103776188B (zh) * | 2013-01-21 | 2017-03-08 | 摩尔动力(北京)技术股份有限公司 | 间冷单工质热制冷制热系统 |
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JP6313090B2 (ja) * | 2014-03-28 | 2018-04-18 | 荏原冷熱システム株式会社 | ターボ冷凍機の蒸発器、および該蒸発器を備えたターボ冷凍機 |
CN104154687B (zh) | 2014-08-22 | 2016-08-24 | 珠海格力电器股份有限公司 | 闪发器和具有该闪发器的空调 |
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CN105571215B (zh) * | 2015-12-21 | 2018-05-01 | 重庆美的通用制冷设备有限公司 | 用于热泵机组的经济器及具有其的热泵机组 |
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JP2018151116A (ja) * | 2017-03-13 | 2018-09-27 | 荏原冷熱システム株式会社 | ターボ冷凍機 |
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JP2009186034A (ja) | 2009-08-20 |
US9027363B2 (en) | 2015-05-12 |
US20100326130A1 (en) | 2010-12-30 |
JP4404148B2 (ja) | 2010-01-27 |
CN101932890B (zh) | 2012-10-10 |
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