EP2762803A2 - Zweischrittkompressionsvorrichtung und Kühl-/Klimaanlage damit - Google Patents

Zweischrittkompressionsvorrichtung und Kühl-/Klimaanlage damit Download PDF

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Publication number
EP2762803A2
EP2762803A2 EP14152364.7A EP14152364A EP2762803A2 EP 2762803 A2 EP2762803 A2 EP 2762803A2 EP 14152364 A EP14152364 A EP 14152364A EP 2762803 A2 EP2762803 A2 EP 2762803A2
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EP
European Patent Office
Prior art keywords
compressor
stage
oil
low
side compressor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP14152364.7A
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English (en)
French (fr)
Other versions
EP2762803A3 (de
EP2762803B1 (de
Inventor
Masahiro Taniguchi
Hisao Mizuno
Yoshiyuki Kimata
Youhei Hotta
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 of EP2762803A2 publication Critical patent/EP2762803A2/de
Publication of EP2762803A3 publication Critical patent/EP2762803A3/de
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Publication of EP2762803B1 publication Critical patent/EP2762803B1/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
    • 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
    • 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

Definitions

  • the present invention relates to a two-stage compression device which compresses a refrigerant in two stages with two serially connected compressors, and to a chilling/air-conditioning device using the same.
  • Two-stage compression device which compresses a refrigerant in two stages.
  • One type has two compression mechanisms of which a low stage-side compression mechanism and a high stage-side compression mechanism, which are provided inside a single hermetic housing and driven by a common electric motor.
  • the other type has two separate electric compressors connected in series to perform two-stage compression, with a front stage-side compressor as a low stage-side compressor and a rear stage-side compressor as a high stage-side compressor.
  • the former can be controlled in the same way as with a stand-alone compressor with respect to lubrication of the compressor with lubricating oil (chiller oil) and oil outflow from the compressor (oil circulation rate; OC%).
  • lubricating oil chloriller oil
  • oil circulation rate oil circulation rate
  • Patent Literature 1 discloses a two-stage compression device having two serially connected compressors, of which a high stage-side compressor is a compressor of an internal low-pressure system (low pressure housing type), and is provided with an oil separator in the downstream of a discharge pipe to return from its oil tank the oil separated by the oil separator to each compressor through respective oil pipes and oil level controllers, while intermediate pressure is applied to the oil tank.
  • a high stage-side compressor is a compressor of an internal low-pressure system (low pressure housing type)
  • an oil separator in the downstream of a discharge pipe to return from its oil tank the oil separated by the oil separator to each compressor through respective oil pipes and oil level controllers, while intermediate pressure is applied to the oil tank.
  • Patent Literature 2 discloses a two-stage compression device, in which a high pressure housing-type compressor is used as a low stage-side compressor and a low pressure housing-type compressor is used as a high stage-side compressor, and an oil separator is provided in the downstream of a discharge pipe of the high stage-side compressor, being the low pressure housing type, to return the oil separated by the oil separator through an oil return pipe to the low stage-side compressor, while an oil equalizing pipe is provided between the low stage-side compressor and the high stage-side compressor.
  • Patent Literatures 1 and 2 if a low pressure housing-type compressor is used as the low stage-side compressor and the high stage-side compressor in the two-stage compression device having two serially connected compressors, it is necessary to control so that each compressor does not run short of the lubricating oil, by providing an oil separator in the downstream of the discharge pipe of the respective compressors, or at least in the downstream of the discharge pipe of the high stage-side compressor, to return the oil separated by the oil separator to the respective compressors. For this reason, installation of the oil separator is essential. However, the increase in the number of components is accompanied by problems such as a more complicated structure, a higher cost, and an increase in the unit size to secure an installation space.
  • the present invention has been made in view of this situation, and an object thereof is to provide a two-stage compression device having two serially connected compressors, the number of components of which is reduced through omission of an oil separator, and thereby the configuration is made simpler, lower in cost, and more compact, and a chilling/air-conditioning device using the two-stage compression device.
  • a two-stage compression device is a two-stage compression device which compresses a refrigerant in two stages and includes two serially connected compressors of which a low stage-side compressor and a high stage-side compressor, wherein, of the two compressors, the low stage-side compressor is a low pressure housing-type compressor, while the high stage-side compressor is a high pressure housing-type compressor, and an oil sump of the high pressure housing-type compressor and an oil sump of the low pressure housing-type compressor are connected through an oil return pipe.
  • the lubricating oil returned along with sucked refrigerant gas to the low stage-side compressor is separated inside a low-pressure housing and accumulated in its oil sump.
  • the lubricating oil discharged along with compressed gas from the low stage-side compressor is directly sucked into a compression chamber of the high stage-side compressor and used for sealing, etc. of the compression chamber.
  • the lubricating oil is thereafter discharged together with the high-pressure refrigerant gas into a high-pressure housing, and separated from the high-pressure refrigerant gas due to a change in velocity, collision with internal components, etc. at the time of being discharged.
  • the lubricating oil accumulated in the oil sump inside the high-pressure housing is partly returned through the oil return pipe to the oil sump inside the low-pressure housing of the low stage-side compressor, and used for lubrication of each compressor by being accumulated in a predetermined amount in the respective oil sumps of the low stage-side compressor and the high stage-side compressor.
  • the high pressure housing-type high stage-side compressor may be either a rotary compressor or a scroll compressor.
  • the low pressure housing-type low stage-side compressor may be a scroll compressor, while the high pressure housing-type high stage-side compressor may be a rotary compressor.
  • a chilling/air-conditioning device has a compressor of any one of the above-described two-stage compression devices.
  • the chilling/air-conditioning device using the efficient two-stage compression device by suppressing the oil outflow (oil circulation rate; OC%) from the two-stage compression device, the heat exchange efficiency in the condenser and the evaporator can be further increased.
  • the lubricating oil returned along with the sucked refrigerant gas to the low stage-side compressor is separated inside the low-pressure housing and accumulated in its oil sump.
  • the lubricating oil discharged along with the compressed gas from the low stage-side compressor is directly sucked into the compression chamber of the high stage-side compressor and used for sealing, etc. of the compression chamber.
  • the lubricating oil is thereafter discharged together with the high-pressure refrigerant gas into the high-pressure housing, and separated from the high-pressure refrigerant gas due to a change in velocity, collision with the internal components, etc. at the time of being discharged.
  • the lubricating oil accumulated in the oil sump inside the high-pressure housing is partly returned through the oil return pipe to the oil sump inside the low-pressure housing of the low stage-side compressor, and used for lubrication of each compressor by being accumulated in a predetermined amount in the respective oil sumps of the low stage-side compressor and the high stage-side compressor. Therefore, in the two-stage compression device having two serially connected compressors, it is possible to control the compressors so as not to run short of the lubricating oil by separating the oil from the refrigerant gas through the use of the high-pressure housing of the high stage-side compressor, without providing an oil separator, and partly returning the oil to the oil sump of the low stage-side compressor. Accordingly the number of components as a two-stage compression device can be reduced, and thereby the configuration can be made simpler, lower in cost, and more compact.
  • the chilling/air-conditioning device of the present invention in the chilling/air-conditioning device using the efficient two-stage compression device, by suppressing the oil outflow (oil circulation rate; OC%) from the two-stage compression device, the heat exchange efficiency in the condenser and the evaporator can be further increased. Therefore, it is possible to further increase the efficiency and the performance of the chilling/air-conditioning device, as well as to make it lower in cost and more compact.
  • Fig. 1 is a chilling cycle diagram of a two-stage compression device according to the one embodiment of the present invention and a chilling/air-conditioning device using the same.
  • a chilling/air-conditioning device 1 in this embodiment includes a closed chilling cycle 8 constituted of a compressor (two-stage compression device) 2, a condenser 3, a receiver 4, an electronic expansion valve (EEV) 5, and an evaporator 6 sequentially connected in this order through a refrigerant pipe 7.
  • a closed chilling cycle 8 constituted of a compressor (two-stage compression device) 2, a condenser 3, a receiver 4, an electronic expansion valve (EEV) 5, and an evaporator 6 sequentially connected in this order through a refrigerant pipe 7.
  • the compressor 2 integrated in the chilling cycle 8 is a two-stage compression device 2 having two separately configured hermetic electric compressors 10 and 20 connected in series, of which a front stage-side compressor in a circulation direction of a refrigerant is the low stage-side compressor 10, and a rear stage-side compressor serially connected with this compressor is the high stage-side compressor 20.
  • the low stage-side compressor 10 is a motor-embedded hermetic electric compressor 10, in which an electric motor 12 and a compressor 13 are embedded inside a hermetic housing (low-pressure housing) 11 and the compressor 13 is driven by rotation of the electric motor 12.
  • the low stage-side compressor 10 is a so-called low pressure housing-type compressor (a type of compressor in which the inside of the hermetic housing 11 is at a low pressure), in which low-pressure refrigerant gas sucked from the evaporator 6 through a suction pipe 7A is sucked into the hermetic housing 11, and the refrigerant gas is taken into the compressor 13 and compressed before being discharged from a discharge chamber through a discharge pipe 14 directly to the outside.
  • the low pressure housing-type hermetic electric compressor 10 for example, a known hermetic scroll compressor can be used.
  • This hermetic electric scroll compressor 10 has an oil sump 15, which is filled with a predetermined amount of lubricating oil (chiller oil), at the bottom of the hermetic housing 11, and the compressor 13 can be lubricated with this lubricating oil.
  • lubricating oil chloriller oil
  • the high stage-side compressor 20 is a motor-embedded hermetic electric compressor 20, in which an electric motor 22 and a compressor 23 are embedded inside a hermetic housing (high-pressure housing) 21 and the compressor 23 is driven by rotation of the electric motor 22.
  • the high stage-side compressor 20 is a so-called high pressure housing-type compressor (a type of compressor in which the inside of the hermetic housing 21 is at a high pressure), in which an intermediate-pressure refrigerant gas compressed in the low stage-side compressor 10 is directly sucked into a compression chamber of the compressor 23 through a connection pipe 16, and after being compressed to a high pressure, the high-pressure compressed gas is discharged into the hermetic housing 21.
  • the high-pressure refrigerant gas discharged into the hermetic housing 21 is introduced through a discharge pipe 24 and a discharge pipe 7B to the condenser 3.
  • this high pressure housing-type hermetic electric compressor 20 for example, a known hermetic electric rotary compressor or hermetic electric scroll compressor 20 can be used.
  • the hermetic electric rotary compressor or hermetic electric scroll compressor 20 has an oil sump 25, which is filled with a predetermined amount of the lubricating oil (chiller oil), at the bottom of the hermetic housing 21, and the compressor 23 can be lubricated with this lubricating oil.
  • the high stage-side compressor 20 is a high pressure housing-type compressor, and is configured such that the high-pressure refrigerant gas compressed in the compressor 23 is discharged into the hermetic housing 21. Therefore, the oil contained in the refrigerant gas is separated from the refrigerant gas due to a change in velocity, collision with internal components including a motor, etc. at the time of being discharged into the hermetic housing 21. Accordingly, the refrigerant gas is discharged to the outside with a lower oil content.
  • the high pressure housing-type hermetic electric rotary compressor which has the compressor 23 installed at the lower part and can secure a sufficient internal volume (space) for oil separation, is considered to be capable of reducing the oil outflow and therefore is suitable as the high stage-side compressor 20.
  • the hermetic housing 21 function as the oil separator and separate the oil content from the refrigerant gas inside the hermetic housing 21 before discharging the refrigerant gas to the outside.
  • the oil separator conventionally installed in the downstream of the discharge pipe 7B can be omitted.
  • the lubricating oil separated inside the hermetic housing 21 of the high stage-side compressor 20 is returned from the oil sump 25 through the oil return pipe 27, which includes a flow-regulating capillary tube 26 as a pressure reduction means, to the oil sump 15 of the low stage-side compressor 10, whereby a predetermined amount of the lubricating oil is respectively secured in the low stage-side compressor 10 and the high stage-side compressor 20 so that the compressors 10 and 20 do not run short of the lubricating oil.
  • the height position at which the oil return pipe 27 is connected to the hermetic housing 21 of the high stage-side hermetic electric rotary compressor 20 is at about the middle position in the height direction of a cylinder of the compressor 23 which is immersed in the oil sump 25.
  • the high-temperature, high-pressure refrigerant gas discharged from the compressor (two-stage compression device) 2 of the chilling/air-conditioning device 1 releases heat through heat exchange with the outside air, etc. and is turned into condensate in the condenser 3.
  • This refrigerant is temporarily accumulated in the receiver 4, and thereafter supplied to the electronic expansion valve (EEV) 5 in a regulated circulation amount, and undergoes adiabatic expansion while passing through the electronic expansion valve 5 before being supplied to the evaporator 6.
  • EEV electronic expansion valve
  • the refrigerant absorbs heat through heat exchange with the room air, etc. and is evaporated into gas.
  • the gasified low-pressure refrigerant gas is returned to the compressor 2 and circulated in the chilling cycle 8. In this way, the refrigerant is used for chilling, air conditioning, etc.
  • the compressor 2 in this embodiment is the two-stage compression device 2 having the low stage-side compressor 10 and the high stage-side compressor 20 connected in series, of which the low stage-side compressor 10 is the low pressure housing-type hermetic electric compressor (e.g., known hermetic scroll compressor) 10, while the high stage-side compressor 20 is the high pressure housing-type hermetic electric compressor (e.g., known hermetic electric rotary compressor or hermetic electric scroll compressor) 20.
  • the low stage-side compressor 10 is the low pressure housing-type hermetic electric compressor (e.g., known hermetic scroll compressor) 10
  • the high stage-side compressor 20 is the high pressure housing-type hermetic electric compressor (e.g., known hermetic electric rotary compressor or hermetic electric scroll compressor) 20.
  • the low-pressure refrigerant gas evaporated into gas in the evaporator 6 is sucked into the hermetic housing 11 of the low pressure housing-type hermetic electric compressor 10 through the suction pipe 7A, and the lubricating oil returned along with the sucked refrigerant gas from the chilling cycle 8 to the low stage-side compressor 10, is separated inside the low-pressure hermetic housing 11 and accumulated in the oil sump 15 so as to be used for lubrication of the compressor 13 of the low stage-side compressor 10.
  • the lubricating oil discharged from the low stage-side compressor 10 together with the refrigerant gas compressed in the low stage-side compressor 10 is directly sucked into the compression chamber of the compressor 23 of the high stage-side compressor 20 serially connected through the connection pipe 16.
  • the high stage-side compressor 20 is the high pressure housing-type hermetic electric compressor (e.g., known hermetic electric rotary compressor or hermetic electric scroll compressor) 20 in which the high-pressure refrigerant gas compressed in the compressor 23 is discharged into the hermetic housing 21.
  • the lubricating oil mixed in the high-pressure refrigerant gas is separated by a change in velocity, collision with the internal components including the electric motor 22, etc. at the time of being discharged into the hermetic housing 21, and accumulated in the oil sump 25.
  • the high-pressure refrigerant gas from which the lubricating oil has been adequately separated, is discharged from the discharge pipe 7B and delivered to the condenser 3, whereby the oil outflow toward the chilling cycle 8 (oil circulation rate; OC%) can be reduced.
  • the lubricating oil is separated through the use of the hermetic housing 21 of the high stage-side compressor 20, and the lubricating oil accumulated in the oil sump 25 is partly returned to the oil sump 15 of the low stage-side compressor 10 through the oil return pipe 27 including the capillary tube 26. In this way, it is possible to secure a predetermined amount of the lubricating oil respectively in the low stage-side compressor 10 and the high stage-side compressor 20 and lubricate the respective compressors 13 and 23 so as not to run short of the oil.
  • the two-stage compression device having the two compressors 10 and 20 connected in series, it is possible to control the respective compressors 10 and 20 so as not to run short of the oil by separating the oil from the refrigerant gas through the use of the high-pressure housing 21 of the high stage-side compressor 20, without providing an oil separator, and partly returning the oil to the oil sump 15 of the low stage-side compressor 10. Accordingly, the number of components as the two-stage compression device 2 can be reduced, and thereby the configuration can be made simpler, lower in cost, and more compact.
  • the high pressure housing-type high stage-side compressor 20 is either a rotary compressor or a scroll compressor.
  • the high stage-side compressor 20 by using either the existing direct suction-type rotary compressor or scroll compressor as the high stage-side compressor 20, it is possible to configure the highly-reliable two-stage compression device 2 which uses the low pressure housing-type compressor as the low stage-side compressor 10 and the high pressure housing-type compressor as the high stage-side compressor 20.
  • the number of the components as the two-stage compression device 2 can be reduced, and thereby the configuration can be made simpler, lower in cost, and more compact.
  • the low pressure housing-type low stage-side compressor 10 is a scroll compressor
  • the high pressure housing-type high stage-side compressor 20 is a rotary compressor.
  • the low pressure housing-type scroll compressor which, albeit with a relatively large oil outflow (oil circulation rate; OC%), has good efficiency, as the low stage-side compressor 10
  • the high pressure housing-type rotary compressor which has smaller oil outflow (oil circulation rate; OC%), as the high stage-side compressor 20
  • the oil outflow can be suppressed on the high pressure housing-type rotary compressor side, so that the oil outflow in the two-stage compression device 2 as a whole can be suppressed.
  • the chilling/air-conditioning device 1 in this embodiment has, as a compressor, the above-described two-stage compression device 2.
  • the heat exchange efficiency in the condenser 3 and the evaporator 6 can be further increased.
  • the present invention is not limited to the invention according to the above-described embodiment, but can be appropriately modified within the scope of the invention.
  • the example of the unidirectional chilling cycle 8 has been described.
  • the present invention can be as well applied to a reversible chilling cycle provided with a four-way switching valve. Needless to say, the present invention can also be applied to heat pumps for a water heater, etc.
  • the low pressure housing-type hermetic electric scroll compressor is used as the low stage-side compressor 10
  • the hermetic electric rotary compressor or the hermetic electric scroll compressor is used as the high stage-side compressor 20.
  • the low stage-side compressor 10 and the high stage-side compressor 20 may be another type of low pressure housing-type compressor or another type of high pressure housing-type compressor.

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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)
  • Rotary Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP14152364.7A 2013-01-30 2014-01-24 Zweischrittkompressionsvorrichtung und Kühl-/Klimaanlage damit Active EP2762803B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2013015324A JP2014145556A (ja) 2013-01-30 2013-01-30 ２段圧縮装置およびそれを用いた冷凍・空調装置

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EP2762803A2 true EP2762803A2 (de) 2014-08-06
EP2762803A3 EP2762803A3 (de) 2015-11-18
EP2762803B1 EP2762803B1 (de) 2019-01-02

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104930738A (zh) * 2015-06-16 2015-09-23 广东美芝制冷设备有限公司 制冷循环装置
EP3392577A4 (de) * 2016-03-28 2018-12-26 Mitsubishi Heavy Industries Thermal Systems, Ltd. Mehrstufige kompressionsvorrichtung, kältekreislauf damit und betriebsverfahren für mehrstufige kompressionsvorrichtung
CN109441808A (zh) * 2018-09-19 2019-03-08 东莞市正旭新能源设备科技有限公司 单机多级螺杆压缩机系统
CN112344574A (zh) * 2020-11-27 2021-02-09 珠海格力电器股份有限公司 制冷系统、机组以及制冷系统润滑油油量调节方法

Citations (2)

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JPH0526526A (ja) 1991-07-17 1993-02-02 Sanyo Electric Co Ltd 二段圧縮式冷凍装置
JPH07301465A (ja) 1994-05-02 1995-11-14 Mitsubishi Heavy Ind Ltd 二段圧縮式冷凍装置

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JP2012042110A (ja) * 2010-08-18 2012-03-01 Panasonic Corp 冷凍サイクル装置

Patent Citations (2)

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Publication number Priority date Publication date Assignee Title
JPH0526526A (ja) 1991-07-17 1993-02-02 Sanyo Electric Co Ltd 二段圧縮式冷凍装置
JPH07301465A (ja) 1994-05-02 1995-11-14 Mitsubishi Heavy Ind Ltd 二段圧縮式冷凍装置

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104930738A (zh) * 2015-06-16 2015-09-23 广东美芝制冷设备有限公司 制冷循环装置
CN104930738B (zh) * 2015-06-16 2018-06-22 广东美芝制冷设备有限公司 制冷循环装置
EP3392577A4 (de) * 2016-03-28 2018-12-26 Mitsubishi Heavy Industries Thermal Systems, Ltd. Mehrstufige kompressionsvorrichtung, kältekreislauf damit und betriebsverfahren für mehrstufige kompressionsvorrichtung
CN109441808A (zh) * 2018-09-19 2019-03-08 东莞市正旭新能源设备科技有限公司 单机多级螺杆压缩机系统
CN112344574A (zh) * 2020-11-27 2021-02-09 珠海格力电器股份有限公司 制冷系统、机组以及制冷系统润滑油油量调节方法
CN112344574B (zh) * 2020-11-27 2024-05-10 珠海格力节能环保制冷技术研究中心有限公司 制冷系统、机组以及制冷系统润滑油油量调节方法

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EP2762803B1 (de) 2019-01-02
JP2014145556A (ja) 2014-08-14

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