JP2010139155A - Refrigeration apparatus - Google Patents

Refrigeration apparatus Download PDF

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Publication number
JP2010139155A
JP2010139155A JP2008315651A JP2008315651A JP2010139155A JP 2010139155 A JP2010139155 A JP 2010139155A JP 2008315651 A JP2008315651 A JP 2008315651A JP 2008315651 A JP2008315651 A JP 2008315651A JP 2010139155 A JP2010139155 A JP 2010139155A
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JP
Japan
Prior art keywords
compressor
oil
pipe
suction pipe
refrigeration
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.)
Abandoned
Application number
JP2008315651A
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Japanese (ja)
Inventor
Tetsuya Ito
Takamitsu Kurokawa
Takahiro Matsunaga
Shintaro Sanada
Hideya Tamura
Satoshi Tomioka
哲也 伊藤
聡 冨岡
隆廣 松永
秀哉 田村
慎太郎 真田
貴光 黒川
Original Assignee
Fujitsu General Ltd
株式会社富士通ゼネラル
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Fujitsu General Ltd, 株式会社富士通ゼネラル filed Critical Fujitsu General Ltd
Priority to JP2008315651A priority Critical patent/JP2010139155A/en
Publication of JP2010139155A publication Critical patent/JP2010139155A/en
Abandoned legal-status Critical Current

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B31/00Compressor arrangements
    • F25B31/002Compressor arrangements lubrication
    • F25B31/004Compressor arrangements lubrication oil recirculating arrangements
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B2313/00Compression machines, plant, or systems with reversible cycle not otherwise provided for
    • F25B2313/023Compression machines, plant, or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233Compression machines, plant, or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B2400/00General 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
    • F25B2400/07Details of compressors or related parts
    • F25B2400/075Details of compressors or related parts with parallel compressors
    • F25B2400/0751Details of compressors or related parts with parallel compressors the compressors having different capacities
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B2500/00Problems to be solved
    • F25B2500/16Lubrication

Abstract

When one compressor connected in parallel is a compressor with a small oil discharge amount and the other compressor is a compressor with a large oil discharge amount, the amount of refrigerating machine oil in each compressor is reduced. Almost equalize.
At least two compressors, a first compressor (110) and a second compressor (120) connected in parallel to an outdoor unit (100), are provided, and oil separators (111, 121) are provided in discharge pipes of the compressors (110, 120). The first oil separator 111 on the first compressor side is connected to the suction pipe 164 of the second compressor 120 via the oil return pipe 114, and the second oil separator 121 on the second compressor side is connected to the oil return pipe 124. In the refrigeration apparatus connected to the suction pipe 163 of the first compressor 110 through the rotary compressor, a rotary compressor is used as the first compressor 110, a scroll compressor is used as the second compressor 120, and the oil of the first compressor 110 is used. The reservoir 110b is connected to the suction pipe 164 of the second compressor 120 via the oil guide pipe 118.
[Selection] Figure 2

Description

  The present invention relates to a refrigeration apparatus including at least two compressors, a first compressor and a second compressor, connected in parallel to an outdoor unit, and suitable for large buildings such as office buildings and apartment buildings. For example, the present invention relates to a technique for almost equalizing the amount of refrigeration oil in each compressor.
  A so-called multi-air conditioner system that supplies refrigerant from a single outdoor unit to a plurality of indoor units installed in the building is employed in air conditioning equipment for large buildings such as office buildings and apartment buildings. In a large-scale system, there may be a plurality of outdoor units.
  In the multi-air conditioner system, the cooling capacity or the heating capacity required differs depending on the number of operating indoor units. Therefore, in order to cope with this, a plurality of compressors are mounted on the outdoor unit.
  A description will be given of a case where there are two compressors. Usually, an inverter-controlled variable-speed compressor is used for the first compressor, and a constant-speed compressor with a constant rotational speed is used for the second compressor. Is used.
  Up to a predetermined capacity, the second compressor is stopped and only the first compressor is operated with the rotation speed controlled by the inverter. On the other hand, when the capacity | capacitance more than predetermined is requested | required, the 2nd compressor of a constant speed type is drive | operated with a 1st compressor.
  As described above, when only the first compressor is operated, it is necessary to prevent excess or shortage of refrigeration oil in each compressor in any case where both the first and second compressors are operated. is there.
  As an example of the countermeasure, in the invention described in Patent Document 1, the oil storage part of the first compressor and the suction pipe of the second compressor are connected via an oil return pipe, and the oil storage of the second compressor is performed. And the suction pipe of the first compressor are connected via an oil return pipe.
JP 2001-324230 A
  According to the invention described in Patent Document 1, when both of the compressors are operated, surplus from the first compressor to the second compressor and from the second compressor to the first compressor, respectively. When the refrigerating machine oil is returned and only one compressor is operated, surplus refrigerating machine oil is returned to the own machine, so that an appropriate amount of refrigerating machine oil is maintained in each compressor.
  However, when the amount of refrigerating machine oil discharged (the amount of refrigerating machine oil discharged together with the discharge gas) differs among the compressors, the above-described conventional technology may not be able to cope with it.
  For example, if the first compressor by inverter control that is always operated is a rotary compressor, and the constant-speed second compressor that is operated when a capacity exceeding a predetermined level is required is a scroll compressor, In particular, the scroll compressor has more oil discharge than the rotary compressor.
  The reason for this is that, in a rotary compressor, the refrigerant compressor is usually arranged on the lower side of the electric motor, and the refrigerant gas generated in the refrigerant compressor is discharged from the discharge pipe through the passages and gaps existing on the electric motor. Therefore, the refrigerant gas and the refrigerating machine oil are easily separated. On the other hand, in a scroll compressor, the refrigerant compressor is usually disposed at the top of the electric motor, so that the refrigerant gas generated in the refrigerant compressor passes through the electric motor almost even in the case of the internal high-pressure type. Without being discharged from the discharge pipe.
  In this way, when the compressor oil amount is uneven due to the difference in the amount of oil discharged from each compressor, it is difficult to eliminate the difference with the above-mentioned conventional technology. There is a risk of burn-in. Note that the amount of oil discharge may be different even in the same rotary compressor or in the same scroll.
  Therefore, the problem of the present invention is that even when one compressor connected in parallel is a compressor with a small oil discharge amount and the other compressor is a compressor with a relatively large oil discharge amount. The purpose is to substantially equalize the amount of refrigeration oil in each compressor.
  In order to solve the above problems, the present invention includes an outdoor unit including at least two compressors, a first compressor and a second compressor, connected in parallel, and an oil separator is provided in a discharge pipe of each compressor. A first oil separator on the first compressor side is connected to a suction pipe of the second compressor via a first oil return pipe, and a second oil separator on the second compressor side is provided In the refrigeration apparatus connected to the suction pipe of the first compressor via the second oil return pipe, the first compressor and the second compressor have different oil discharge amounts, and the oil discharge amount is smaller. The oil storage section of the first compressor is connected to the suction pipe of the second compressor having the larger oil discharge amount via an oil guide pipe including a pressure reducing means.
  In particular, a rotary compressor is used for the first compressor, and a scroll compressor is used for the second compressor.
  In the present invention, the suction pipe of the first compressor and the suction pipe of the second compressor communicate with each other, and the first oil return pipe and the oil guide pipe are connected to the suction pipe of the second compressor. The position is such that when the second compressor is in an operation stop state, the refrigeration oil supplied to the second compressor side from the first oil return pipe and the oil guide pipe falls due to gravity, and enters the first compressor. It is preferable that it is a position to be sucked.
  According to the present invention, the outdoor unit includes at least two compressors of a first compressor and a second compressor connected in parallel, and an oil separator is provided in a discharge pipe of each compressor, and the first compression The first oil separator on the machine side is connected to the suction pipe of the second compressor via the first oil return pipe, and the second oil separator on the second compressor side is connected to the second oil return pipe via the second oil return pipe. In the refrigeration apparatus connected to the suction pipe of one compressor, the first compressor and the second compressor have different oil discharge amounts, and the oil storage section of the first compressor having the smaller oil discharge amount is provided with a pressure reducing means. By connecting to the suction pipe of the second compressor having the larger amount of discharged oil through the oil guide pipe including the first compressor (for example, the rotary compressor) where the refrigerating machine oil is relatively abundant. An oil guide pipe is connected to a second compressor (for example, a scroll compressor) having a large oil discharge amount. Since the refrigerating machine oil is supplied Te, it is possible to substantially equalize the refrigerating machine oil of the compressor.
  In addition, the suction pipe of the first compressor and the suction pipe of the second compressor are communicated with each other, and the connection position of the first oil return pipe and the oil guide pipe with respect to the suction pipe of the second compressor is determined by the second compressor. When the engine is in a stopped state, the refrigeration oil supplied to the second compressor side from the first oil return pipe and the oil guide pipe falls by gravity and is brought into a position where it is sucked into the first compressor. When the operation is stopped, the refrigerating machine oil supplied to the second compressor side from the first oil return pipe and the oil guide pipe is sucked into the first compressor, and when the second compressor is in the operation state, the first oil return The refrigerating machine oil supplied to the second compressor side from the pipe and the oil guide pipe is sucked into the second compressor as it is.
  Next, an embodiment of the present invention will be described with reference to FIGS. 1 and 2, but the present invention is not limited to this. FIG. 1 is a refrigerant circuit diagram showing an overall configuration of a refrigeration apparatus according to an embodiment of the present invention, and FIG. 2 is an enlarged view showing a compression mechanism portion of an outdoor unit included in the refrigeration apparatus.
  First, referring to FIG. 1, this refrigeration apparatus includes an outdoor unit 100 and an indoor unit 200. The outdoor unit 100 includes a compression mechanism unit 101, a four-way valve (flow path switching valve) 130, an outdoor heat exchanger 140 having an outdoor fan 141, an outdoor expansion valve 150, and an accumulator 160.
  In the indoor unit 200, a plurality of indoor heat exchangers 210 each having an indoor expansion valve 211 (three in the drawing in this example) are connected in parallel between the liquid side pipe 11 and the gas side pipe 12. . Each indoor heat exchanger 210 is provided with an indoor fan, which is not shown.
  Next, referring to FIG. 2, according to this embodiment, the compression mechanism unit 101 includes first and second compressors 110 and 120 connected in parallel to the discharge-side gas pipe 13. Is provided.
  In this embodiment, the first compressor 110 is a rotary speed variable rotary compressor controlled by inverter control, and the second compressor 120 is a constant speed scroll compressor having a constant speed. It is done. The rotary compressor may be a single rotor, a normal twin rotor, an injection type twin rotor, or the like.
  The refrigerant discharge pipe 110a of the first compressor 110 is connected to the discharge side gas pipe 13 via the oil separator 111 and the check valve 112, and the refrigerant discharge pipe 120a of the second compressor 120 includes the oil separator 121 and The discharge side gas pipe 13 is connected via a check valve 122.
  The oil separators 111 and 121 each separate the refrigerating machine oil contained in the high-pressure discharge gas refrigerant, and the check valves 112 and 122 prevent the high-pressure discharge gas refrigerant from other machines from entering the own machine.
  The accumulator 160 is provided in the refrigerant | coolant suction side of each compressor 110,120, and the refrigerant | coolant which finished work is returned. A main suction pipe 161 for low-pressure refrigerant gas is drawn out from the accumulator 160, and a branch pipe 162 is provided at the end thereof.
  The branch pipe 162 is bifurcated, and the suction pipe 163 of the first compressor 110 is connected to one of the branches, and the suction pipe 164 of the second compressor 120 is connected to the other. In this embodiment, since the first compressor 110 is a rotary compressor that requires a smaller amount of liquid back, a sub-accumulator 113 is provided on the suction side of the first compressor 110. .
  The oil separator 111 on the first compressor 10 side is connected to the suction pipe 164 of the second compressor 120 via an oil return pipe 114 having a capillary tube 115 as decompression means.
  Similarly, the oil separator 121 on the second compressor 120 side is connected to the suction pipe 163 of the first compressor 120 via an oil return pipe 124 having a capillary tube 125 as a decompression means.
  In addition to this, in the present invention, the oil reservoir 110b of the first compressor (rotary compressor) 110 is connected to the second compressor (scroll compressor) 120 via an oil guide pipe 116 including a capillary tube 117 as decompression means. Connected to the suction pipe 164.
  The connection position of the oil return pipe 114 and the oil guide pipe 116 with respect to the suction pipe 164 is a position where the refrigeration oil supplied from the oil return pipe 114 and the oil guide pipe 116 to the second compressor 120 side can fall due to gravity. For example, when the suction pipe 164 has an inclined part that is inclined downward toward the branch pipe 162, the oil return pipe 114 and the oil guide pipe 116 are connected to the inclined part.
  According to this, since the suction pipe 163 and the suction pipe 164 communicate with each other at the branch pipe 162 portion, when the second compressor 120 is in the operation stop state, the oil return pipe 114 and the oil guide pipe 116 are connected to the first pipe. The refrigerating machine oil supplied to the second compressor side is sucked into the first compressor 110, and is supplied from the oil return pipe 114 and the oil guide pipe 116 to the second compressor 120 side when the second compressor 120 is in an operating state. The refrigerating machine oil is sucked into the second compressor 120 as it is.
  Next, the operation of this refrigeration apparatus will be described. Until the predetermined capacity, the second compressor 120 is stopped, and only the first compressor 110 is operated with the rotation speed controlled by the inverter. On the other hand, when the capacity | capacitance more than predetermined is requested | required, the 1st compressor 110 and the 2nd compressor 120 of a fixed speed type are drive | operated.
  During the cooling operation, the four-way valve 130 is switched to the solid line state of FIG. As a result, the gas refrigerant discharged from the compression mechanism unit 101 reaches the outdoor heat exchanger 140 from the four-way valve 130 and exchanges heat with the outside air to condense (during cooling operation, the outdoor heat exchanger 140 acts as a condenser. ).
  The liquid refrigerant condensed in the outdoor heat exchanger 140 passes through the check valve 151 connected in parallel to the outdoor expansion valve 150 and is supplied to the indoor unit 200.
  On the indoor unit 200 side, the liquid refrigerant is depressurized to a predetermined pressure by each indoor expansion valve 211 and then evaporated by exchanging heat with indoor air in the indoor heat exchanger 210, thereby cooling the indoor air ( During the cooling operation, the room heat exchanger 210 acts as an evaporator).
  The gas refrigerant evaporated in the indoor heat exchanger 210 enters the accumulator 160 through the four-way valve 130 and is returned to the compression mechanism unit 101 after the liquid refrigerant is separated.
  During the heating operation, the four-way valve 130 is switched to the chain line state of FIG. As a result, the gas refrigerant discharged from the compression mechanism unit 101 reaches the indoor heat exchanger 210 from the four-way valve 130 and exchanges heat with the indoor air to condense, thereby warming the indoor air (during heating operation, The heat exchanger 210 acts as a condenser).
  The liquid refrigerant condensed in the indoor heat exchanger 210 is supplied to the outdoor unit 100 through the indoor expansion valve 211 whose valve opening degree is controlled according to the heating capacity.
  On the outdoor unit 100 side, the liquid refrigerant is depressurized to a predetermined pressure by the outdoor expansion valve 150 and then evaporates by exchanging heat with the outside air by the outdoor heat exchanger 140 (during heating operation, the outdoor exchanger 140 serves as an evaporator). Act).
  The gas refrigerant evaporated in the outdoor heat exchanger 140 enters the accumulator 160 through the four-way valve 130 and is returned to the compression mechanism unit 101 after the liquid refrigerant is separated.
  When both the first and second compressors 110 and 120 are operating, the refrigerating machine oil separated by the oil separator 111 on the first compressor 110 side passes through the oil return pipe 114, and the first compressor The refrigerating machine oil in the oil reservoir 110b of 110 is supplied to the suction pipe 164 of the second compressor 120 via the oil guide pipe 116, and the refrigerating machine oil separated by the oil separator 121 on the second compressor 120 side is supplied. The oil is supplied to the suction pipe 163 of the first compressor 120 via the oil return pipe 124, whereby the amount of refrigeration oil in each of the compressors 110 and 120 is substantially equalized.
  In the rotary compressor of the first compressor 110 and the scroll compressor of the second compressor 120, the scroll compressor is structurally discharged from the rotary compressor together with the high-pressure gas than the rotary compressor for the reasons described above. However, according to the present invention, excess refrigeration oil is supplied from the rotary compressor side of the first compressor 110 to the scroll compressor side of the second compressor 120 through the oil guide pipe 116. Therefore, it is possible to eliminate the bias in the amount of refrigerating machine oil due to the difference in the amount of oil discharged between the compressors 110 and 120.
  Further, when only the first compressor 110 is operated and the second compressor 120 is stopped, the refrigerating machine oil supplied to the second compressor 120 side from the oil return pipe 114 and the oil guide pipe 116 is the first. Sucked into the compressor 110.
  In the above embodiment, a combination of one first compressor (rotary compressor by inverter control) and one second compressor (constant speed type scroll compressor) is used, but both the first and second compressors are combined. The present invention is applicable even when there are a plurality of units.
  Further, on the assumption that the amount of discharged oil is different, the two compressors may be the same compression type (for example, a rotary compressor or a scroll compressor).
The refrigerant circuit figure which shows the whole structure of the freezing apparatus which concerns on embodiment of this invention. The enlarged view which shows the compression mechanism part of the outdoor unit contained in the said freezing apparatus.
Explanation of symbols
DESCRIPTION OF SYMBOLS 100 Outdoor unit 101 Compression mechanism part 110 1st compressor 120 2nd compressor 111,121 Oil separator 112,122 Check valve 114,124 Oil return pipe 115,117,125 Capillary tube 116 Oil guide pipe 130 Four-way valve 140 Outdoor heat Exchanger 150 Outdoor expansion valve 160 Accumulator 163, 164 Suction pipe 200 Indoor unit 210 Indoor heat exchanger 211 Indoor expansion valve

Claims (3)

  1. The outdoor unit includes at least two compressors, a first compressor and a second compressor connected in parallel, and an oil separator is provided in a discharge pipe of each compressor, and the first compressor side A first oil separator is connected to the suction pipe of the second compressor via a first oil return pipe, and a second oil separator on the second compressor side is connected to the first oil return pipe via a second oil return pipe. In the refrigeration system connected to the suction pipe of the compressor,
    The first compressor and the second compressor have different oil discharge amounts, and the oil storage part of the first compressor having the smaller oil discharge amount has the oil discharge amount of the first compressor through an oil guide pipe including a pressure reducing means. A refrigerating apparatus, wherein the refrigerating apparatus is connected to a suction pipe of a larger number of second compressors.
  2.   The refrigeration apparatus according to claim 1, wherein the first compressor is a rotary compressor, and the second compressor is a scroll compressor.
  3.   The suction pipe of the first compressor and the suction pipe of the second compressor are in communication with each other, and the connection positions of the first oil return pipe and the oil guide pipe with respect to the suction pipe of the second compressor are as described above. When the second compressor is in an operation stop state, the refrigerating machine oil supplied to the second compressor side from the first oil return pipe and the oil guide pipe falls by gravity and is sucked into the first compressor. The refrigeration apparatus according to claim 1, wherein the refrigeration apparatus is provided.
JP2008315651A 2008-12-11 2008-12-11 Refrigeration apparatus Abandoned JP2010139155A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2008315651A JP2010139155A (en) 2008-12-11 2008-12-11 Refrigeration apparatus

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
JP2008315651A JP2010139155A (en) 2008-12-11 2008-12-11 Refrigeration apparatus
US12/591,856 US20100147018A1 (en) 2008-12-11 2009-12-03 Refrigeration apparatus
EP20090252757 EP2196747A1 (en) 2008-12-11 2009-12-09 Refrigeration apparatus
CN200910253720A CN101749889A (en) 2008-12-11 2009-12-10 Refrigeration apparatus
AU2009248463A AU2009248463A1 (en) 2008-12-11 2009-12-11 Refrigeration Apparatus

Publications (1)

Publication Number Publication Date
JP2010139155A true JP2010139155A (en) 2010-06-24

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JP2008315651A Abandoned JP2010139155A (en) 2008-12-11 2008-12-11 Refrigeration apparatus

Country Status (5)

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US (1) US20100147018A1 (en)
EP (1) EP2196747A1 (en)
JP (1) JP2010139155A (en)
CN (1) CN101749889A (en)
AU (1) AU2009248463A1 (en)

Cited By (4)

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CN104121715A (en) * 2014-07-29 2014-10-29 浙江青风环境股份有限公司 Parallel sharing system vortex hydraulic filling type direct cooling unit special for surface treatment industry
JP2016044883A (en) * 2014-08-22 2016-04-04 株式会社Nttファシリティーズ Steam compression type refrigeration cycle
JP2016145651A (en) * 2015-02-06 2016-08-12 株式会社富士通ゼネラル Air conditioner
WO2017038131A1 (en) * 2015-09-01 2017-03-09 株式会社デンソー Two-stage pressure boosting type refrigeration cycle

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CN102954624A (en) * 2012-11-27 2013-03-06 大连三洋压缩机有限公司 Parallel compressor oil return device and control method
CN103062959A (en) * 2012-12-29 2013-04-24 宁波奥克斯电气有限公司 Oil passage balance system of dual parallel compressor screw water chilling unit
CN103062948B (en) * 2012-12-29 2015-04-08 宁波奥克斯电气有限公司 Dual parallel compressor screw water chilling unit
KR102165351B1 (en) * 2014-02-05 2020-10-13 엘지전자 주식회사 A heat-pump system and a method controlling the same
JP6748217B2 (en) * 2016-10-31 2020-08-26 三菱電機株式会社 Refrigeration cycle equipment

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Publication number Priority date Publication date Assignee Title
CN104121715A (en) * 2014-07-29 2014-10-29 浙江青风环境股份有限公司 Parallel sharing system vortex hydraulic filling type direct cooling unit special for surface treatment industry
CN104121715B (en) * 2014-07-29 2016-06-08 浙江青风环境股份有限公司 The special sharing system vortex full-liquid type direct air-cooling units in parallel of Surface Processing Industry
JP2016044883A (en) * 2014-08-22 2016-04-04 株式会社Nttファシリティーズ Steam compression type refrigeration cycle
JP2016145651A (en) * 2015-02-06 2016-08-12 株式会社富士通ゼネラル Air conditioner
WO2017038131A1 (en) * 2015-09-01 2017-03-09 株式会社デンソー Two-stage pressure boosting type refrigeration cycle
JPWO2017038131A1 (en) * 2015-09-01 2018-02-08 株式会社デンソー Two-stage boost refrigeration cycle

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US20100147018A1 (en) 2010-06-17
CN101749889A (en) 2010-06-23
EP2196747A1 (en) 2010-06-16
AU2009248463A1 (en) 2010-07-01

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