EP2863151A2 - Zweistufiger Kompressionszyklus - Google Patents

Zweistufiger Kompressionszyklus Download PDF

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Publication number
EP2863151A2
EP2863151A2 EP20140188877 EP14188877A EP2863151A2 EP 2863151 A2 EP2863151 A2 EP 2863151A2 EP 20140188877 EP20140188877 EP 20140188877 EP 14188877 A EP14188877 A EP 14188877A EP 2863151 A2 EP2863151 A2 EP 2863151A2
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EP
European Patent Office
Prior art keywords
stage compressor
oil
stage
compressor
stage compression
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.)
Granted
Application number
EP20140188877
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English (en)
French (fr)
Other versions
EP2863151A3 (de
EP2863151B1 (de
Inventor
Yoshiaki Miyamoto
Yoshiyuki Kimata
Youhei Hotta
Hajime Sato
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Heavy Industries Thermal Systems Ltd
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Mitsubishi Heavy Industries Ltd
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Publication date
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Publication of EP2863151A2 publication Critical patent/EP2863151A2/de
Publication of EP2863151A3 publication Critical patent/EP2863151A3/de
Application granted granted Critical
Publication of EP2863151B1 publication Critical patent/EP2863151B1/de
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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
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line 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
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/072—Intercoolers therefor
    • 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
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors

Definitions

  • the present invention relates to a two-stage compression system in which a lower-stage compressor and a higher-stage compressor are disposed in series.
  • oil separators are individually provided on the discharge sides of the respective compressors and oil separated at the oil separators is returned to the respective compressors, or an oil-equalizing pipe is provided between the individual compressors.
  • Patent Literature 1 discloses a system in which a single oil separator is provided in an discharge pipe of a higher-stage compressor, oil-returning circuits are provided so as to individually connect the oil separator to the lower-stage compressor and the higher-stage compressor, and thus, oil is returned to the individual compressors without being affected by a pressure difference, which eliminates an imbalance in oil levels in the individual compressors, and in which a second oil-returning circuit is also provided between the higher-stage compressor and the lower-stage compressor, thus making the imbalance in oil levels between the lower-stage compressor and the higher-stage compressor smaller.
  • Patent Literature 1 With the system described in Patent Literature 1, it suffices to install just one oil separator, and the configuration thereof can be simplified; however, subtle adjustment of the return-oil volume in the individual oil-returning circuits is essential in order to eliminate the imbalance in the oil levels in the individual compressors, and there is a problem in that, in order to make the imbalance smaller, it is necessary to provide a second oil-returning circuit between the two compressors, or the like.
  • the present invention has been conceived in light of the above-described circumstances, and an object thereof is to provide a two-stage compression system that has no need for oil equalization between a lower-stage compressor and a higher-stage compressor, making it possible to simplify the configuration, and that makes it possible to reliably ensure an appropriate oil level in both the lower-stage compressor and the higher-stage compressor.
  • a two-stage compression system of the present invention provides the following solutions.
  • a two-stage compression system is a two-stage compression system in which a lower-stage compressor and a higher-stage compressor are disposed in series, and an oil separator is provided on an discharge side of the higher-stage compressor, the two-stage compression system including a first oil-returning circuit and a second oil-returning circuit that are independent of each other and that are provided so as to be connected between the oil separator and the lower-stage compressor and the higher-stage compressor, respectively, the relationship V1 > V2 being satisfied, wherein V1 is the volume of oil returned to the lower-stage compressor from the first oil-returning circuit, and V2 is the volume of oil returned to the higher-stage compressor from the second oil-returning circuit is V2.
  • the oil separator is provided on the discharge side of the higher-stage compressor; the first oil-returning circuit and the second oil-returning circuit, which are independent of each other, are provided so as to be connected between the oil separator and the lower-stage compressor and the higher-stage compressor; because V1 > V2 is satisfied, assuming that the volume of oil returned to the lower-stage compressor from the first oil-returning circuit is V1, and the volume of oil returned to the higher-stage compressor from the second oil-returning circuit is V2, by returning the oil separated at the oil separator provided on the discharge side of the higher-stage compressor to the lower-stage compressor via the first oil-returning circuit and also to the higher-stage compressor via the second oil-returning circuit, it is possible to ensure a certain oil level in the lower-stage compressor and the higher-stage compressor, respectively; and, additionally, by making the volume V1 of the oil returned to the
  • the first oil-returning circuit may be provided with a first capillary tube for adjusting the return-oil volume V1
  • the second oil-returning circuit may be provided with a second capillary tube for adjusting the return-oil volume V2
  • V1 > V2 may be achieved by setting a flow of the first capillary tube to be higher than a flow of the second capillary tube.
  • a switching means may be provided in an discharge pipe of the lower-stage compressor, and, by using the switching means, it may be allowed to switch between a single-stage compression operation, in which the lower-stage compressor is independently operated, and a two-stage compression operation by guiding refrigerant gas compressed by the lower-stage compressor to the oil separator by bypassing the higher-stage compressor through an discharge bypass circuit.
  • the switching means is provided in the discharge pipe of the lower-stage compressor, and, because, by using this switching means, it is possible to switch between the single-stage compression operation, in which the lower-stage compressor is independently operated, and the two-stage compression operation by guiding the refrigerant gas compressed by the lower-stage compressor to the oil separator by bypassing the higher-stage compressor through the discharge bypass circuit, the operation of the two-stage compression system can be switched to a single-stage compression system, in which the lower-stage compressor is independently operated, by switching the switching means provided in the discharge pipe of the lower-stage compressor, thereby guiding the refrigerant gas compressed by the lower-stage compressor to the oil separator by bypassing the higher-stage compressor through the discharge bypass circuit.
  • a switching means may be provided in an discharge pipe of the lower-stage compressor, and, by using the switching means, it may be allowed to switch between a single-stage compression operation, in which the higher-stage compressor is independently operated, and a two-stage compression operation by guiding low-pressure refrigerant gas to the higher-stage compressor from an intake side of the lower-stage compressor by bypassing the lower-stage compressor through an intake bypass circuit.
  • the switching means is provided in the discharge pipe of the lower-stage compressor, and, because, by using this switching means, it is possible to switch between the single-stage compression operation, in which the higher-stage compressor is independently operated, and the two-stage compression operation by guiding the low-pressure refrigerant gas to the higher-stage compressor from the intake side of the lower-stage compressor by bypassing the lower-stage compressor through the intake bypass circuit, the operation of the two-stage compression system can be switched to a single-stage compression system, in which the higher-stage compressor is independently operated, by switching the switching means provided in the discharge pipe of the lower-stage compressor, thereby guiding the low-pressure refrigerant gas to the higher-stage compressor from the intake side of the lower-stage compressor by bypassing the lower-stage compressor through the intake bypass circuit, and compressing the low-pressure refrigerant gas.
  • a first solenoid valve and a second solenoid valve may be provided in the first oil-returning circuit and the second oil-returning circuit, respectively, and the oil-returning circuit leading to a stopped compressor may be closed during the independent operation of the lower-stage compressor or the higher-stage compressor.
  • first solenoid valve and the second solenoid valve are provided in the first oil-returning circuit and the second oil-returning circuit, respectively, and because the oil-returning circuit leading to the stopped compressor can be closed during the independent operation of the lower-stage compressor or the higher-stage compressor, by closing the solenoid valve provided in the oil-returning circuit leading to the stopped compressor during the independent operation of the lower-stage compressor or the higher-stage compressor, it is possible to prevent oil accumulation in the stopped compressor. Therefore, it is possible to reliably ensure an appropriate oil level in the operating compressor even when the lower-stage compressor or the higher-stage compressor is independently operated.
  • an intercooler may be provided in the discharge pipe of the lower-stage compressor that guides the refrigerant gas compressed by the lower-stage compressor to the higher-stage compressor.
  • the intercooler is provided in the discharge pipe of the lower-stage compressor that guides the refrigerant gas compressed by the lower-stage compressor to the higher-stage compressor, when performing two-stage compression, the refrigerant gas compressed by the lower-stage compressor can be taken into the higher-stage compressor after the refrigerant gas is cooled by the intercooler. Therefore, the compression efficiency at the higher-stage compressor can be increased and the COP (Coefficient Of Performance) of the two-stage compression system can be enhanced.
  • the intercooler is provided so as to allow heat exchange with an evaporator.
  • the intercooler is provided so as to allow heat exchange with the evaporator, the refrigerant gas discharged from the lower-stage compressor can be cooled by the intercooler to a necessary and sufficient level by using the heat of evaporation of the evaporator as a heat source. Therefore, the compression efficiency at the higher-stage compressor can be increased by reliably cooling the refrigerant gas discharged from the lower-stage compressor.
  • the present invention by returning oil separated by the oil separator provided on the discharge side of the higher-stage compressor to the lower-stage compressor via the first oil-returning circuit and also to the higher-stage compressor via the second oil-returning circuit, it is possible to ensure a certain oil level in the lower-stage compressor and the higher-stage compressor, respectively; and, additionally, by making the volume V1 of the oil returned to the lower-stage compressor greater than the volume V2 of the oil returned to the higher-stage compressor (i.e., V1 > V2), it is possible to increase the amount of oil that circulates to the oil separator from the lower-stage compressor via the higher-stage compressor, and, by doing so, it is possible to more easily ensure an appropriate oil level in the higher-stage compressor.
  • FIG. 1 A first embodiment of the present invention will be described below by using Fig. 1 .
  • Fig. 1 is a diagram showing the configuration of portions in the vicinity of compressors of a two-stage compression system according to this embodiment.
  • a two-stage compression system 1 is formed of a refrigeration system employing CO2 refrigerant, in which a lower-stage compressor 2 and a higher-stage compressor 3 are connected in series.
  • the lower-stage compressor 2 and the higher-stage compressor 3 may be compressors employing any configuration or system having an oil sump in an airtight housing thereof.
  • the lower-stage compressor 2 is connected to an intake pipe 4B for taking in low-pressure gas refrigerant via an accumulator 5 provided in an exit refrigerant pipe 4A of an evaporator (not shown).
  • This lower-stage compressor 2 is connected to the higher-stage compressor 3 via an discharge pipe 4C, and the higher-stage compressor 3 takes in the medium-pressure refrigerant gas compressed by the lower-stage compressor 2, thus performing two-stage compression.
  • the high-pressure refrigerant gas compressed by the higher-stage compressor 3 is guided to an oil separator 7 via a higher-stage discharge pipe 4D and a check valve 6, and is guided to a condenser (not shown) via a high-pressure gas pipe 4E after oil in the refrigerant gas is separated.
  • a switching means 8 formed of a three-way valve or the like is provided in the discharge pipe 4C of the lower-stage compressor 2, and, by switching this switching means 8, it is possible to switch to a high-pressure-difference operation, in which the two-stage compression system is used, by guiding the refrigerant gas compressed by the lower-stage compressor 2 directly to the higher-stage compressor 3, or to single-stage compression, in which only the lower-stage compressor 2 is used, by guiding the refrigerant gas compressed by the lower-stage compressor 2 to the oil separator 7 via an discharge bypass circuit 9 and a check valve 10 by bypassing the higher-stage compressor 3.
  • the oil separator 7 is provided on the downstream side of a point at which the higher-stage discharge pipe 4D from the higher-stage compressor 3 and the discharge bypass circuit 9 join, and has functions for separating oil contained in the refrigerant gas discharged from the higher-stage compressor 3 or the lower-stage compressor 2 and for returning this oil to the lower-stage compressor 2 and the higher-stage compressor 3.
  • this oil separator 7 it is possible to employ a known oil separator 7, such as a centrifugal separation system or the like.
  • An independent first oil-returning circuit 11 and second oil-returning circuit 12 for retuning oil to the lower-stage compressor 2 and the higher-stage compressor 3 are connected to the bottom portion of the oil separator 7.
  • the first oil-returning circuit 11 and the second oil-returning circuit 12 may be connected to the oil sumps inside the lower-stage compressor 2 and the higher-stage compressor 3, or they may be connected to intake pipes of the lower-stage compressor 2 and the higher-stage compressor 3, that is, the intake pipe 4B, which serves as the intake pipe of the lower-stage compressor 2, and the discharge pipe 4C from the lower-stage compressor 2, which serves as the intake pipe of the higher-stage compressor 3.
  • the first and second oil-returning circuits 11 and 12 are provided with a first solenoid valve 13 and a second solenoid valve 14 that are opened and closed in accordance with whether or not the lower-stage compressor 2 and the higher-stage compressor 3 are in operation or stopped and a flow-volume adjusting first capillary tube 15 and second capillary tube 16 for adjusting return-oil volumes.
  • the return-oil volumes of the first and second oil-returning circuits 11 and 12 are set so that "V1 > V2" is satisfied, assuming that the volume of oil returned to the lower-stage compressor 2 from the first oil-returning circuit 11 is V1, and the volume of oil returned to the higher-stage compressor 3 from the second oil-returning circuit 12 is V2.
  • this embodiment affords the following operational advantages.
  • the high-pressure refrigerant gas fed to the oil separator 7 is guided to the condenser (not shown) via the high-pressure gas pipe 4E, thus circulating in the refrigeration system.
  • the oil separated from the refrigerant gas at the oil separator 7 is returned to the lower-stage compressor 2 and the higher-stage compressor 3 via the first oil-returning circuit 11 and the second oil-returning circuit 12 because the first solenoid valve 13 and the second solenoid valve 14 are both open.
  • the volumes V1 and V2 of the oil that are returned to the lower-stage compressor 2 and the higher-stage compressor 3 via the first oil-returning circuit 11 and the second oil-returning circuit 12 are always "V1 > V2" because flow reduction levels are set so that "the flow reduction level of the first capillary tube 15 ⁇ the flow reduction level of the second capillary tube 16" by using the same kind of capillary tubes as the flow-volume adjusting first capillary tube 15 and second capillary tube 16.
  • the switching means (three-way valve) 8 is provided in the discharge pipe 4C of the lower-stage compressor 2 of the two-stage compression system 1, and because, by using this switching means 8, it is possible to switch between the single-stage compression operation, in which the lower-stage compressor 2 is independently operated, and the two-stage compression operation by guiding the refrigerant gas compressed by the lower-stage compressor 2 to the oil separator 7 by bypassing the higher-stage compressor 3 through the discharge bypass circuit 9, the operation of the two-stage compression system 1 can be switched to the single-stage compression system, in which the lower-stage compressor 2 is independently operated, by switching the switching means 8 provided in the discharge pipe 4C of the lower-stage compressor 2, thereby guiding the refrigerant gas compressed by the lower-stage compressor 2 to the oil separator 7 by bypassing the higher-stage compressor 3 through the discharge bypass circuit 9.
  • the operation using the two-stage compression cycle is performed during winter when the high-pressure-difference operation is required due to low outdoor temperatures or the like, and the operation is switched to the single-stage compression cycle during the intermediate seasons (spring and fall).
  • the first solenoid valve 13 and the second solenoid valve 14 are provided in the first oil-returning circuit 11 and the second oil-returning circuit 12, respectively, and because the oil-returning circuit 12 leading to the stopped compressor (higher-stage compressor 3) can be closed during the independent operation of the lower-stage compressor 2, by closing the solenoid valve 14 provided in the oil-returning circuit 12 leading to the higher-stage compressor 3 during the independent operation of the lower-stage compressor 2, it is possible to prevent oil accumulation in the higher-stage compressor 3. Accordingly, it is possible to reliably ensure an appropriate oil level in the operating compressor even when the lower-stage compressor 2 is independently operated.
  • This embodiment differs from the first embodiment described above in that it is possible to independently operate the higher-stage compressor 3 during the single-stage compression operation. Because other points are the same as those of the first embodiment, descriptions thereof will be omitted.
  • an intake bypass circuit 17 branched off from the intake pipe 4B is connected to a switching means (three-way valve) 8A provided in the discharge pipe 4C of the lower-stage compressor 2, as shown in Fig. 2 , and, during the independent operation of the higher-stage compressor 3, the low-pressure refrigerant gas from the intake pipe 4B can directly be taken into the higher-stage compressor 3 by bypassing the lower-stage compressor 2 through the intake bypass circuit 17.
  • the switching means (three-way valve) 8A is provided in the discharge pipe 4C of the lower-stage compressor 2, and in which, by using this switching means 8A, the low-pressure refrigerant gas can directly be taken into the higher-stage compressor 3 from the intake pipe 4B of the lower-stage compressor 2 by bypassing the lower-stage compressor 2 through the intake bypass circuit 17, the operation of the two-stage compression system 1 can be switched to a single-stage compression system in which the higher-stage compressor 3 is independently operated.
  • first solenoid valve 13 and the second solenoid valve 14 are provided in the first oil-returning circuit 11 and the second oil-returning circuit 12, and because the oil-returning circuit 11 leading to the stopped compressor (lower-stage compressor 2) can be closed during the independent operation of the higher-stage compressor 3, by closing the solenoid valve 13 provided in the oil-returning circuit 11 leading to the lower-stage compressor 2 during the independent operation of the higher-stage compressor 3, it is possible to prevent oil accumulation in the lower-stage compressor 2. Accordingly, it is possible to reliably ensure an appropriate oil level in the operating compressor even when the higher-stage compressor 3 is independently operated.
  • This embodiment differs from the first embodiment described above in that, during the two-stage compression cycle, medium-pressure refrigerant gas compressed by the lower-stage compressor 2 is taken into the higher-stage compressor 3 after the refrigerant gas is cooled by an intercooler 18. Because other points are the same as those of the first embodiment, descriptions thereof will be omitted.
  • the intercooler 18 is provided in the discharge pipe 4C of the lower-stage compressor 2, which guides the refrigerant gas compressed by the lower-stage compressor 2 to the higher-stage compressor 3, when subjecting the low-pressure refrigerant gas to two-stage compression, as shown in Fig. 4 , the medium-pressure refrigerant gas compressed by the lower-stage compressor 2 can be taken into the higher-stage compressor 3 after the refrigerant gas is cooled by the intercooler 18. Therefore, the compression efficiency at the higher-stage compressor 3 can be increased and the COP (Coefficient Of Performance) of the two-stage compression system 1 can be enhanced.
  • the intercooler 18 is provided so as to allow heat exchange with the evaporator 19, the refrigerant gas discharged from the lower-stage compressor 2 can be cooled by the intercooler 18 to a necessary and sufficient level by using the heat of evaporation of the evaporator 19 as a heat source, and, by doing so, the compression efficiency at the higher-stage compressor 3 can be increased by reliably cooling the refrigerant gas discharged from the lower-stage compressor 2.
  • the present invention is not limited to the invention according to the above-described embodiments, and appropriate modifications are possible within a range that does not depart from the scope thereof.
  • the switching means 8 is not limited to a three-way valve, and a switching means that uses two solenoid valves in combination or the like can be employed as an alternative.
  • the intercooler 18 is not limited to the one that performs heat exchange with the evaporator 19, and the intercooler 18 may be configured so as to perform heat exchange with the low-pressure refrigerant pipe 4A or the like.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP14188877.6A 2013-10-18 2014-10-14 Zweistufiger Kompressionszyklus Active EP2863151B1 (de)

Applications Claiming Priority (1)

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JP2013216944A JP6301101B2 (ja) 2013-10-18 2013-10-18 ２段圧縮サイクル

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EP2863151A2 true EP2863151A2 (de) 2015-04-22
EP2863151A3 EP2863151A3 (de) 2015-07-29
EP2863151B1 EP2863151B1 (de) 2019-10-02

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CN105758066A (zh) * 2016-04-25 2016-07-13 广东美的暖通设备有限公司 多联机系统的室外机及多联机系统
CN106766371A (zh) * 2016-11-29 2017-05-31 珠海格力电器股份有限公司 一种双级压缩机热泵及其回油控制系统和控制方法
CN108444137A (zh) * 2018-03-23 2018-08-24 天津商业大学 双级压缩热泵系统的运行控制方法及热泵系统
EP3385640A4 (de) * 2016-03-28 2019-01-23 Mitsubishi Heavy Industries Thermal Systems, Ltd. Mehrstufige kompressionsvorrichtung, kühlkreislauf damit und betriebsverfahren für eine mehrstufige kompressionsvorrichtung
CN110325803A (zh) * 2017-01-12 2019-10-11 艾默生环境优化技术有限公司 用于微增压器型超市制冷系统的油管理
US11415342B2 (en) 2018-09-28 2022-08-16 Daikin Industries, Ltd. Multistage compression system
US11428226B2 (en) 2018-09-28 2022-08-30 Daikin Industries, Ltd. Multistage compression system
US11428225B2 (en) 2018-09-28 2022-08-30 Daikin Industries, Ltd. Multistage compression system
US11994127B2 (en) 2018-09-28 2024-05-28 Daikin Industries, Ltd. Multistage compression system

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JP2024011150A (ja) * 2022-07-14 2024-01-25 三菱重工業株式会社 圧縮機ユニット及び冷凍システム

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EP3385640A4 (de) * 2016-03-28 2019-01-23 Mitsubishi Heavy Industries Thermal Systems, Ltd. Mehrstufige kompressionsvorrichtung, kühlkreislauf damit und betriebsverfahren für eine mehrstufige kompressionsvorrichtung
CN105758066A (zh) * 2016-04-25 2016-07-13 广东美的暖通设备有限公司 多联机系统的室外机及多联机系统
CN106766371A (zh) * 2016-11-29 2017-05-31 珠海格力电器股份有限公司 一种双级压缩机热泵及其回油控制系统和控制方法
CN106766371B (zh) * 2016-11-29 2019-12-10 珠海格力电器股份有限公司 一种双级压缩机热泵及其回油控制系统和控制方法
CN110325803A (zh) * 2017-01-12 2019-10-11 艾默生环境优化技术有限公司 用于微增压器型超市制冷系统的油管理
CN110325803B (zh) * 2017-01-12 2021-09-17 艾默生环境优化技术有限公司 用于微增压器型超市制冷系统的油管理
CN108444137A (zh) * 2018-03-23 2018-08-24 天津商业大学 双级压缩热泵系统的运行控制方法及热泵系统
CN108444137B (zh) * 2018-03-23 2020-06-26 天津商业大学 双级压缩热泵系统的运行控制方法及热泵系统
US11415342B2 (en) 2018-09-28 2022-08-16 Daikin Industries, Ltd. Multistage compression system
US11428226B2 (en) 2018-09-28 2022-08-30 Daikin Industries, Ltd. Multistage compression system
US11428225B2 (en) 2018-09-28 2022-08-30 Daikin Industries, Ltd. Multistage compression system
US11994127B2 (en) 2018-09-28 2024-05-28 Daikin Industries, Ltd. Multistage compression system

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JP2015078804A (ja) 2015-04-23
EP2863151A3 (de) 2015-07-29
EP2863151B1 (de) 2019-10-02

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