WO2015114851A1 - Compresseur à vis - Google Patents

Compresseur à vis Download PDF

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Publication number
WO2015114851A1
WO2015114851A1 PCT/JP2014/067254 JP2014067254W WO2015114851A1 WO 2015114851 A1 WO2015114851 A1 WO 2015114851A1 JP 2014067254 W JP2014067254 W JP 2014067254W WO 2015114851 A1 WO2015114851 A1 WO 2015114851A1
Authority
WO
WIPO (PCT)
Prior art keywords
screw
rotor
screw rotor
casing
screw compressor
Prior art date
Application number
PCT/JP2014/067254
Other languages
English (en)
Japanese (ja)
Inventor
雅浩 神田
雅章 上川
和幸 塚本
Original Assignee
三菱電機株式会社
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 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to CN201480041290.2A priority Critical patent/CN105392996B/zh
Priority to JP2015559726A priority patent/JPWO2015114851A1/ja
Publication of WO2015114851A1 publication Critical patent/WO2015114851A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/48—Rotary-piston pumps with non-parallel axes of movement of co-operating members
    • F04C18/50—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees
    • F04C18/52—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/56—Bearing bushings or details thereof

Definitions

  • the present invention relates to a screw compressor used for refrigerant compression of a refrigerator, for example.
  • a screw compressor includes a single screw compressor including one screw rotor and two gate rotors.
  • FIG. 5 is a schematic configuration diagram of a conventional single screw compressor. As shown in FIG. 5, in the conventional single screw compressor, one screw rotor 2 and two gate rotors 3 are accommodated in a casing 1. A plurality of spiral screw grooves 5 are formed in the screw rotor 2, and the screw grooves 5 are engaged with and engaged with a pair of gate rotors 3 arranged in the radial direction of the screw rotor 2, so that a compression chamber is formed. It is formed.
  • a low pressure space and a high pressure space are formed.
  • the screw rotor 2 is fixed to the screw shaft 7, and one end side of the screw shaft 7 is supported by the bearing support 4 via the bearing 6 disposed on the discharge side (left side in FIG. 5) of the screw rotor 2.
  • the suction side (the right side in FIG. 5) is connected to the motor rotor 10.
  • the discharge side where the screw groove 5 communicates with the discharge chamber 15 during operation is a high-pressure space, and a bearing formed between the discharge side of the screw rotor 2 and the bearing 6.
  • the chamber 21 is a low pressure space.
  • the bearing chamber 21 is partitioned from the high-pressure space of the screw rotor 2 by a seal portion at the end face of the bearing support 4, and is communicated to the low-pressure side by a pressure equalizing hole 22 formed in the screw shaft 7.
  • a clearance for rotating the screw rotor 2 is required between the outer peripheral surface of the screw rotor 2 and the casing 1, and leakage of high-pressure fluid also occurs from this clearance.
  • leakage of the high pressure fluid as described above occurs, the operating efficiency of the single screw compressor decreases.
  • the gap between the screw rotor 2 and the bearing support 4 and the gap between the screw rotor 2 and the casing 1 are reduced to reduce leakage of high-pressure fluid. It is effective.
  • the cooled oil or liquid refrigerant is injected into the screw groove serving as the compression chamber to suppress the temperature rise of the gas refrigerant compressed in the compression chamber, thereby suppressing the thermal expansion of the screw rotor.
  • a screw compressor has been proposed (see, for example, Patent Document 1).
  • An object of the present invention is to provide a highly reliable screw compressor that suppresses such contact and seizure.
  • a screw compressor includes a screw rotor housed in a casing and formed with a plurality of helical screw grooves, a gate rotor that meshes with and engages with the screw grooves of the screw rotor, and forms a compression chamber.
  • a motor that rotationally drives the screw rotor connected via a screw shaft, and a bearing support that supports the screw shaft via a bearing disposed on the discharge side of the screw rotor, and in the casing and At least one of oil and refrigerant liquid is jetted from the flow path formed in the bearing support toward the screw rotor.
  • oil and liquid refrigerant are injected into the screw rotor from the second flow path provided in the bearing support and cooled, thereby suppressing thermal expansion of the screw rotor and improving operating efficiency. Therefore, even when the clearance between the screw rotor and the bearing support and the clearance between the screw rotor and the casing are reduced, contact and seizure can be suppressed, so that high reliability can be obtained.
  • FIG. 1 is a schematic configuration diagram of a screw compressor according to Embodiment 1 of the present invention.
  • the screw compressor according to the first embodiment is a single screw compressor, and as shown in FIG. 1, a cylindrical casing 1, a screw rotor 2 housed in the casing 1, a gate rotor 3, The motor 20 and the bearing support 4 are provided.
  • the screw rotor 2 has a plurality of spiral screw grooves 5 formed on the outer periphery thereof, and is provided on the discharge side (the left side in FIG. 1) of the casing 1.
  • the motor 20 includes a stator 9 inscribed and fixed to the casing 1, and a motor rotor 10 disposed inside the stator 9.
  • the motor 20 rotates and drives a screw rotor 2 connected via a screw shaft 7. In the case of the system, the rotation speed of the motor 20 is controlled.
  • the motor 20 is provided on the suction side (the right side in FIG. 1) of the casing 1.
  • Two gate rotors 3 are provided and are arranged so as to sandwich the screw rotor 2 in the radial direction.
  • a plurality of teeth are formed on the outer peripheral portion of the gate rotor 3, and these teeth engage with and engage with the screw grooves 5 of the screw rotor 2 to form a compression chamber.
  • a discharge chamber 15 in which the refrigerant compressed in the compression chamber is discharged is formed in the casing 1.
  • the screw rotor 2 and the motor rotor 10 are arranged on the same axis line, and both are fixed to the screw shaft 7.
  • One end 8 of the screw shaft 7 is supported by the bearing support 4 via a bearing 6 disposed on the discharge side (left side in FIG. 1) of the screw rotor 2.
  • a low pressure space and a high pressure space are formed in the casing 1.
  • a discharge side where the screw groove 5 communicates with the discharge chamber 15 during operation is a high pressure space.
  • the bearing chamber 21 formed between the two is a low pressure space.
  • the bearing chamber 21 is partitioned from the high-pressure space of the screw rotor 2 by a seal portion at the end face of the bearing support 4, and is communicated to the low-pressure side by a pressure equalizing hole 22 formed in the screw shaft 7.
  • a first flow path 11 is formed through which oil or liquid refrigerant can be injected into the compression chamber.
  • the reason why the oil or liquid refrigerant is injected into the compression chamber is to cool the gas refrigerant compressed in the compression chamber whose temperature has increased due to an increase in the number of rotations of the motor, and to suppress the temperature increase of the gas refrigerant. is there.
  • a flow path is formed in each of the casing 1 and the bearing support 4, and a second flow path 12 is formed through which these oils and liquid refrigerant can always be injected toward the screw rotor 2.
  • the reason why the oil or liquid refrigerant is injected toward the screw rotor 2 is to cool the screw rotor 2 and suppress thermal expansion of the screw rotor 2.
  • the operation of the single screw compressor according to the first embodiment will be described.
  • the motor rotor 10 By supplying power to the stator 9 from a power supply source (not shown), the motor rotor 10, the screw shaft 7 and the screw rotor 2 rotate. Further, the gate rotor 3 engaged with the screw rotor 2 also rotates. As a result, the gas refrigerant passes through the suction port (not shown) and is sucked into the single screw compressor. This gas refrigerant is sucked into the compression chamber through a gap called an air gap between the stator 9 and the motor rotor 10 and a passage (not shown) formed between the outer peripheral portion of the stator 9 and the casing 1.
  • high-pressure liquid refrigerant at the outlet of the condenser (not shown) and high-pressure oil separated from the gas refrigerant by the oil separator (not shown) are discharged from the first flow path 11 formed in the casing 1.
  • the gas refrigerant injected into the compression chamber and compressed in the compression chamber is cooled.
  • the high-pressure liquid refrigerant at the outlet of the condenser (not shown) and the high-pressure oil separated from the gas refrigerant by the oil separator (not shown) are formed in the casing 1 and the bearing support 4. It is injected toward the screw rotor 2 from the flow path 12 to directly cool the screw rotor 2.
  • the gas refrigerant and oil sucked into the compression chamber are compressed with the rotation of the screw rotor 2 and discharged to the discharge chamber 15. At this time, the sealing performance of the compression chamber is improved by the oil sucked into the compression chamber.
  • the refrigerant and oil discharged into the discharge chamber 15 then flow into an oil separator (not shown) where they are separated.
  • oil or liquid refrigerant is injected into the compression chamber from the first flow path 11 to cool the compression chamber, and oil or liquid refrigerant is formed in the bearing support 4.
  • contact and seizure can be suppressed, and a highly reliable single screw compressor can be obtained.
  • the thermal expansion of the screw rotor 2 is further suppressed by cooling the oil or liquid refrigerant flowing through the second flow path 12 by, for example, heat exchange with water or refrigerant using an oil cooler (not shown). Therefore, the effect of suppressing contact and seizure can be enhanced.
  • FIG. FIG. 2 is a schematic configuration diagram of a screw compressor according to Embodiment 2 of the present invention.
  • Embodiment 2 will be described, the same elements as those in Embodiment 1 are omitted, and the same or corresponding parts as those in Embodiment 1 are denoted by the same reference numerals.
  • a groove 13 is formed in a portion of the screw rotor 2 that receives injection of oil or liquid refrigerant from the second flow path 12 formed in the bearing support 4.
  • the groove 13 By forming the groove 13, the heat capacity of the screw rotor 2 is reduced, and the surface area of the screw rotor 2 that receives the injection of oil or liquid refrigerant from the second flow path 12 formed in the bearing support 4 is increased. Therefore, the thermal expansion of the screw rotor 2 can be suppressed as compared with the first embodiment. And if this groove
  • the screw rotor 2 is supported by the bearing support 4 than in the first embodiment. And it becomes difficult to come into contact with the casing 1 and it becomes difficult to seize.
  • FIG. 3 is a schematic configuration diagram of a screw compressor according to Embodiment 3 of the present invention.
  • the single screw compressor according to the third embodiment is provided with a valve 14 that can be controlled to open and close on the inlet side (casing 1 side) of the second flow path 12.
  • the valve 14 is opened only when the temperature of the gas refrigerant compressed in the compression chamber rises (for example, when the temperature of the gas refrigerant compressed in the compression chamber rises above a certain specified temperature). Oil or liquid refrigerant flows into the second flow path 12 and is injected into the screw rotor 2. And the screw rotor 2 which receives injection of oil or a liquid refrigerant is cooled, and thermal expansion is suppressed. Therefore, even when the clearance between the screw rotor 2 and the bearing support 4 and the casing 1 is made small in order to improve the operation efficiency, the screw rotor 2 becomes difficult to come into contact with the bearing support 4 and the casing 1 and seizure becomes difficult.
  • a single screw compressor having higher operating efficiency than those of the first and second embodiments can be obtained.
  • the oil or liquid refrigerant flowing through the second flow path 12 is cooled by heat exchange with water or refrigerant using, for example, an oil cooler (not shown), thereby further increasing the thermal expansion of the screw rotor 2. Since it can suppress, the effect of suppressing contact and seizure can be enhanced.
  • FIG. 4 is a schematic configuration diagram of a screw compressor according to Embodiment 4 of the present invention.
  • Embodiment 4 will be described, the same elements as those in Embodiment 1 are omitted, and the same or corresponding parts as those in Embodiment 1 are denoted by the same reference numerals.
  • a groove 13 is formed in a portion that receives the injection of oil or liquid refrigerant from the second flow path 12 formed in the bearing support 4, and further the second flow.
  • a valve 14 that can be controlled to open and close is provided on the inlet side of the passage 12.
  • the screw compressor is a single screw compressor, but the present invention can also be applied to other twin screw compressors, for example.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

L'invention concerne un compresseur à vis comprenant : une vis rotor (2) logée dans un carter (1) et dans laquelle sont formées des gorges de filetage hélicoïdales (5) ; un rotor femelle (3) s'engrenant et venant en prise avec les gorges de filetage (5) de la vis rotor (2) de façon à former une chambre de compression ; un moteur (20) destiné à mettre en rotation et à entraîner la vis rotor (2) raccordée au moteur (20) par un arbre à vis (7) ; et un support de palier (4) pour soutenir l'arbre à vis (7) dans un palier (6) disposé sur le côté d'évacuation de la vis rotor (2). L'huile et/ou un liquide réfrigérant est évacué vers la vis rotor (2) depuis des passages d'écoulement formés dans le carter (1) et dans le support de palier (4).
PCT/JP2014/067254 2014-01-29 2014-06-27 Compresseur à vis WO2015114851A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201480041290.2A CN105392996B (zh) 2014-01-29 2014-06-27 螺杆压缩机
JP2015559726A JPWO2015114851A1 (ja) 2014-01-29 2014-06-27 スクリュー圧縮機

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2014014519 2014-01-29
JP2014-014519 2014-01-29

Publications (1)

Publication Number Publication Date
WO2015114851A1 true WO2015114851A1 (fr) 2015-08-06

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ID=53756455

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2014/067254 WO2015114851A1 (fr) 2014-01-29 2014-06-27 Compresseur à vis

Country Status (3)

Country Link
JP (2) JPWO2015114851A1 (fr)
CN (1) CN105392996B (fr)
WO (1) WO2015114851A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3505765A4 (fr) * 2016-08-23 2019-08-14 Mitsubishi Electric Corporation Compresseur à vis et dispositif à cycle frigorifique

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108150416A (zh) * 2017-12-13 2018-06-12 西安交通大学 一种单螺杆压缩机轴的悬臂式布置结构
CN112334660A (zh) * 2019-05-20 2021-02-05 开利公司 带有制冷剂润滑的轴承的直接驱动制冷剂螺杆压缩机
CN112747488A (zh) * 2021-02-18 2021-05-04 和昌(广州)家具有限公司 一种可根据温度调节制冷剂用量的中央空调制冷压缩装置

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5799982U (fr) * 1980-12-10 1982-06-19
JP2003286986A (ja) * 2002-03-27 2003-10-10 Mitsubishi Electric Corp シングルスクリュー圧縮機
JP2010249045A (ja) * 2009-04-16 2010-11-04 Mitsubishi Electric Corp スクリュー圧縮機
JP2013064331A (ja) * 2011-09-15 2013-04-11 Daikin Industries Ltd スクリュー圧縮機および冷凍装置
JP2014118931A (ja) * 2012-12-19 2014-06-30 Daikin Ind Ltd スクリュー圧縮機

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63130686U (fr) * 1987-02-18 1988-08-26
CN201269197Y (zh) * 2008-10-11 2009-07-08 广东正力精密机械有限公司 一种水冷单螺杆压缩机
US8858192B2 (en) * 2009-03-16 2014-10-14 Daikin Industries, Ltd. Screw compressor
JP5178613B2 (ja) * 2009-04-16 2013-04-10 三菱電機株式会社 スクリュー圧縮機
JP5696548B2 (ja) * 2011-03-22 2015-04-08 ダイキン工業株式会社 スクリュー圧縮機

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5799982U (fr) * 1980-12-10 1982-06-19
JP2003286986A (ja) * 2002-03-27 2003-10-10 Mitsubishi Electric Corp シングルスクリュー圧縮機
JP2010249045A (ja) * 2009-04-16 2010-11-04 Mitsubishi Electric Corp スクリュー圧縮機
JP2013064331A (ja) * 2011-09-15 2013-04-11 Daikin Industries Ltd スクリュー圧縮機および冷凍装置
JP2014118931A (ja) * 2012-12-19 2014-06-30 Daikin Ind Ltd スクリュー圧縮機

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3505765A4 (fr) * 2016-08-23 2019-08-14 Mitsubishi Electric Corporation Compresseur à vis et dispositif à cycle frigorifique

Also Published As

Publication number Publication date
JP2016048070A (ja) 2016-04-07
CN105392996B (zh) 2017-05-17
JP6113259B2 (ja) 2017-04-12
JPWO2015114851A1 (ja) 2017-03-23
CN105392996A (zh) 2016-03-09

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