WO2019146100A1 - Séparateur d'huile, compresseur et dispositif à cycle frigorifique - Google Patents

Séparateur d'huile, compresseur et dispositif à cycle frigorifique Download PDF

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Publication number
WO2019146100A1
WO2019146100A1 PCT/JP2018/002689 JP2018002689W WO2019146100A1 WO 2019146100 A1 WO2019146100 A1 WO 2019146100A1 JP 2018002689 W JP2018002689 W JP 2018002689W WO 2019146100 A1 WO2019146100 A1 WO 2019146100A1
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WO
WIPO (PCT)
Prior art keywords
inner cylinder
oil separator
oil
protrusion
gas refrigerant
Prior art date
Application number
PCT/JP2018/002689
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English (en)
Japanese (ja)
Inventor
伊藤　健
Original Assignee
三菱電機株式会社
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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 PCT/JP2018/002689 priority Critical patent/WO2019146100A1/fr
Publication of WO2019146100A1 publication Critical patent/WO2019146100A1/fr

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
    • B04C—APPARATUS USING FREE VORTEX FLOW, e.g. CYCLONES
    • B04C5/00—Apparatus in which the axial direction of the vortex is reversed
    • B04C5/12—Construction of the overflow ducting, e.g. diffusing or spiral exits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/04—Measures to avoid lubricant contaminating the pumped fluid
    • 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
    • F04C29/02—Lubrication; Lubricant separation
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant

Definitions

  • the present invention relates to a cyclone-type oil separator, a compressor, and a refrigeration cycle apparatus that discharge gas refrigerant separated from oil from compressed refrigerant.
  • the compressor In the compressor, a large amount of oil is supplied to the bearing and the compression chamber for the purpose of bearing lubrication, compression heat cooling and gap sealing. However, the supplied oil is discharged from the compression chamber to the discharge portion together with the compressed gas refrigerant. For this reason, in the oil separator, the oil and the gas refrigerant are separated from the compressed refrigerant, and the separated oil needs to be supplied again to the bearing and the compression chamber. In addition, when the oil discharged to the discharge portion is discharged to the refrigeration cycle device side outside the compressor, the heat exchange in the condenser and the evaporator is adversely affected, causing a factor of performance degradation. Therefore, the oil needs to be separated and recovered from the gas refrigerant by the oil separator before being discharged to the refrigeration cycle apparatus side.
  • compressors provided with an oil separator for separating oil and gas refrigerant as described above.
  • a system for separating oil and gas refrigerant in an oil separator there is a system called a cyclone system in which oil and gas refrigerant are separated by centrifugal force using a density difference of gas and liquid.
  • the structure of the cyclone type oil separator is provided with a double cylindrical portion, and a centrifugal portion which generates a centrifugal force for oil separation, and a gas refrigerant which is separated from the oil by the centrifugal force and descends while swirling
  • a passage portion which is pivoted and raised to the inside of the inner cylinder portion and discharged to the side of the refrigeration cycle device is constituted.
  • the oil adheres to the inner side surface of the outer cylinder by the centrifugal separation portion, the oil adhered to the inner side surface of the outer cylinder descends, and the lowered oil is stored in the oil reservoir provided at the lower portion.
  • oil separation is achieved by dividing the internal space of the inner cylinder at right angles to the circumference by means of a flow straightening plate to reduce the flow velocity in the turning direction by means of a rectifying device to decelerate the swirling component after oil separation.
  • compressors with oil separators that increase the efficiency and performance of the refrigeration cycle system.
  • compressor provided with a protrusion for decelerating a swirling component after oil separation see, for example, Patent Document 1.
  • a swirl enhancement plate that maintains the swirl flow velocity of the centrifugal portion and a straightening vane that suppresses the velocity of the swirl upflow of the passage portion.
  • work such as welding occurs, the manufacturability such as assembly of parts is poor, and there is a problem that manufacturing takes time and cost.
  • Patent Document 1 does not describe the specific shape of the protrusion, and it is not clear how the protrusion is formed to achieve the effect of decelerating the swirling component of the gas refrigerant after oil separation.
  • the present invention is intended to solve the above-mentioned problems, and it is possible to decelerate the swirling component of the gas refrigerant in the vicinity of the inner side surface portion of the inner cylinder of the oil separator, as well as efficiently separating oil with low cost and simple structure.
  • An object of the present invention is to provide an oil separator, a compressor and a refrigeration cycle device which can realize performance improvement by reducing pressure loss.
  • the oil separator according to the present invention includes an outer cylinder connected to a discharge port through which compressed refrigerant is discharged, an inner cylinder disposed inside the outer cylinder, and an opening covering an opening of one end of the inner cylinder. And a lid portion for discharging a gas refrigerant separated from the oil from the portion, wherein the inner surface portion of the inner cylinder is provided with one or more protrusions.
  • the compressor concerning the present invention is provided with the above-mentioned oil separator, and the compression mechanism part provided with the above-mentioned discharge mouth which compresses a refrigerant, and discharges a compression refrigerant.
  • a refrigeration cycle apparatus includes the above-described compressor.
  • the inner side surface portion of the inner cylinder is provided with one or more protrusions. Therefore, the swirling component of the gas refrigerant can be decelerated near the inner side surface portion of the inner cylinder of the oil separator. Thereby, the flow velocity in the swirling direction of the upflow of the gas refrigerant after oil separation can be suppressed, and the pressure loss due to the swirling upflow of the gas refrigerant can be reduced. Therefore, it is possible to realize performance improvement by highly efficient oil separation and pressure loss reduction with an inexpensive and simple structure.
  • FIG. 1 is a longitudinal sectional view showing a screw compressor 1 according to Embodiment 1 of the present invention.
  • a longitudinal cross section obtained by cutting the compressor main body 2 which is a compression mechanism of the screw compressor 1 in the longitudinal direction is shown on the right side of the dashed line in the central portion.
  • disconnected the oil separator 4 of the screw compressor 1 longitudinally is shown on the left side from the dashed-dotted line of a center part.
  • the screw compressor 1 is a single screw compressor equipped with an oil separator 4.
  • the screw compressor 1 includes a compressor body 2 that is a screw compression mechanism, and an oil separator 4 that is fastened by a bolt to a casing 3 that divides the compressor body 2.
  • the compressor body 2 is provided with a discharge port 12 a that compresses the refrigerant and discharges the compressed refrigerant.
  • the oil separator 4 has an outer cylinder 13 connected to the discharge port 12a from which the compressed refrigerant is discharged.
  • the compressor body 2 includes a cylindrical casing 3, a motor 5 accommodated in the casing 3, a screw shaft 6 fixed to the motor 5 and rotationally driven by the motor 5, and a screw A screw rotor 7 fixed to the shaft 6 and a bearing 8 rotatably supporting an end of the screw shaft 6 not fixed to the motor 5 are provided.
  • a pair of gate rotors 9 arranged to be axially symmetrical with respect to the screw shaft 6 is provided on the side surface of the screw rotor 7.
  • a slide valve 10 slidably provided is provided between the side surface of the casing 3 and the screw rotor 7.
  • the motor 5 has a stator 5a fixed inward in the casing 3 and a motor rotor 5b disposed inside the stator 5a.
  • the motor rotor 5 b is fixed to the screw shaft 6 and arranged in line with the screw rotor 7.
  • the screw rotor 7 is cylindrical. On the outer peripheral surface of the screw rotor 7, a plurality of screw grooves 7a extending in a plurality of spirals are formed from one end on the right side of the screw rotor 7 in the drawing to the other end on the left side in the drawing.
  • the casing 3 separates a suction pressure side filled with a low pressure gas refrigerant from a discharge pressure side filled with a high pressure gas refrigerant.
  • One end side of the screw rotor 7 on the right side in the drawing is a suction side of the gas refrigerant, and communicates with the suction pressure side.
  • the other end side of the screw rotor 7 on the left side in the drawing is a discharge side of the gas refrigerant, and the screw groove 7a communicates with the discharge pressure side.
  • the gate rotor 9 has a disk shape.
  • a plurality of tooth portions 9 a are provided on the outer peripheral surface of the gate rotor 9 along the circumferential direction.
  • the teeth 9 a of the gate rotor 9 are arranged to mesh with the screw grooves 7 a of the screw rotor 7.
  • a space surrounded by the screw groove 7a, the tooth portion 9a of the gate rotor 9, the inner peripheral surface of the casing 3 and the slide valve 10 is formed in the compression chamber 11 filled with the gas refrigerant to be compressed.
  • An oil for lubricating the bearing 8 and sealing the compression chamber 11 is injected into the compression chamber 11.
  • the slide valve 10 is provided slidably along the outer peripheral surface of the screw rotor 7 on the suction pressure side and the discharge pressure side of the screw rotor 7.
  • An opening 10 a is formed at the center of the slide valve 10.
  • a discharge port 12 a connected to the oil separator 4 from the discharge chamber 12 is opened on the inner peripheral surface on the discharge pressure side of the casing 3.
  • the high-pressure gas refrigerant and oil filled in the compression chamber 11 are discharged into the discharge chamber 12 through the opening 10 a opened in the slide valve 10 and the discharge port 12 a.
  • the discharge chamber 12 is a space in the compression chamber 11 into which high-pressure gas refrigerant and oil are discharged.
  • the high pressure gas refrigerant and oil filled in the discharge chamber 12 are led to the oil separator 4.
  • FIG. 2 is a longitudinal cross-sectional view showing an oil separator 4 according to Embodiment 1 of the present invention.
  • FIG. 3 is a cross-sectional view showing an oil separator 4 according to Embodiment 1 of the present invention.
  • FIG. 4 is a development view showing an inner side surface portion 14b of the inner cylinder 14 of the oil separator 4 according to Embodiment 1 of the present invention.
  • the oil separator 4 is a cyclone-type oil separator that separates a gas refrigerant and an oil. As shown in FIG. 1, the oil separator 4 is fixed to the casing 3 of the compressor body 2 by fastening bolts.
  • the oil separator 4 is formed of a double cylinder.
  • the oil separator 4 covers the outer cylinder 13, the inner cylinder 14 provided inside the outer cylinder 13, the lid 15 covering the upper openings of the outer cylinder 13 and the inner cylinder 14, and the bottom of the outer cylinder 13.
  • a bottom portion 16 and a wave adjustment plate 17 provided below the inside of the outer cylinder 13 are provided.
  • the outer cylinder 13 is fixed to the compressor body 2 by fastening a bolt, and is connected to the discharge port 12 a of the compressor body 2 from which the compressed refrigerant is discharged.
  • An inlet 13 a communicating with the discharge chamber 12 of the compressor body 2 is provided above the inner side surface of the outer cylinder 13. That is, the compressed refrigerant flows into the outer cylinder 13 from the compressor body 2 via the discharge port 12 a, the discharge chamber 12 and the inflow port 13 a.
  • the inner cylinder 14 is disposed inside the outer cylinder 13.
  • the inner cylinder 14 is formed to extend downward shorter than the outer cylinder 13 in a state in which the outer cylinder 13 and the upper end thereof are aligned with each other.
  • the outer cylinder 13 and the inner cylinder 14 are concentric circles having the same central axis C.
  • a mixture of gas refrigerant and oil which is a compressed refrigerant, flows into the cylindrical gap 20 between the outer cylinder 13 and the inner cylinder 14 from the inflow port 13a, and the circumferential direction along the shape of the cylindrical gap 20 It descends while turning.
  • a cylindrical space 21 is formed which is folded back by the wave adjustment plate 17 after the gas refrigerant and the oil move downward while swirling.
  • the lid 15 is disk-shaped. At the center of the lid portion 15, a hole-shaped outlet portion 15a which penetrates up and down and has a diameter smaller than the inner diameter of the inner cylinder 14 is provided.
  • the lid 15 covers the opening at one end of the inner cylinder 14 at the upper side in the drawing, and discharges the gas refrigerant separated from the oil from the outlet 15 a.
  • the lid 15 covers the inner cylinder 14 as well as the opening at one end of the outer cylinder 13 at the upper side in the drawing.
  • the inner cylinder 14 and the lid 15 are integrated.
  • the lid portion 15 is fixed to the outer cylinder 13 by fastening a bolt.
  • the outlet portion 15 a discharges the gas refrigerant after oil separation in the oil separator 4 from the screw compressor 1 to the outside.
  • a check valve 18 is provided downstream of the outlet 15 a.
  • the wave adjustment plate 17 is a plate-like member, and extends parallel to the open end surface of the inner cylinder 14 on the lower side in the drawing.
  • the wave adjustment plate 17 turns back the gas refrigerant that flows into the outer cylinder 13 and descends downward in the outer cylinder 13, and suppresses the disturbance of the oil surface of the oil reservoir 19.
  • the outer cylinder 13 is substantially closed at the bottom by the wave adjustment plate 17.
  • the outer cylinder 13 is provided with an oil outlet 13 b at a lower projection portion of the inlet 13 a with respect to the central axis C.
  • the bottom portion 16 forms, at the lowermost end inside the outer cylinder 13, an oil reservoir 19 for storing oil separated from the gas refrigerant.
  • the inner cylinder 14 is formed by casting.
  • the inner side surface portion 14b of the inner cylinder 14 is provided with one protrusion 14a extending from the other end on the lower side in the drawing of the inner cylinder 14 in the direction of one end on the upper side.
  • the protrusion 14 a is formed to extend from the other end of the lower side of the inner cylinder 14 in the drawing to the lid 15.
  • the height of the protrusion 14 a toward the central axis C of the inner cylinder 14 is 3% or more and 15% or less of the inner diameter of the inner cylinder 14.
  • FIGS. 1 the inner side surface portion 14b of the inner cylinder 14 is provided with one protrusion 14a extending from the other end on the lower side in the drawing of the inner cylinder 14 in the direction of one end on the upper side.
  • the protrusion 14 a is formed to extend from the other end of the lower side of the inner cylinder 14 in the drawing to the lid 15.
  • the protrusion 14 a is formed to extend in parallel with the central axis C of the inner cylinder 14. As shown in FIGS. 1 to 4, orthogonal cross sections orthogonal to the central axis C of the inner cylinder 14 in the protrusion 14 a and different in the central axis C direction have the same shape. Therefore, the height of the protrusion 14 a facing the central axis C of the inner cylinder 14 is formed to be constant.
  • the protrusion 14a is a straight rod-like body. As shown in FIG. 3, the protrusion 14 a has a flat surface at the tip 14 a 1. As shown to FIG. 1, FIG. 2, the projection part 14a is provided in the inner surface part 14b most separated with respect to the inflow port 13a of the outer cylinder 13. As shown in FIG.
  • the gas refrigerant and the compressed refrigerant containing oil that have reached the oil separator 4 flow into the inside of the outer cylinder 13 from the inflow port 13 a that penetrates the inside and the outside of the outer cylinder 13 and flow into the inside of the outer cylinder 13. While rotating around the cylindrical gap 20 between them. At this time, oil having a density higher than that of the gas refrigerant among the gas refrigerant and oil that is turning downward is blown to the inner side surface portion 13c of the outer cylinder 13 by centrifugal force, and the oil and the gas refrigerant are separated.
  • the oil separated by the swirling flow falls into the oil reservoir 19 by gravity.
  • the oil stored in the oil storage portion 19 is supplied to the compression chamber 11 and the bearing 8 through a path (not shown) provided in the casing 3.
  • the gas refrigerant separated from the oil descends while turning and collides with the wave-regulating plate 17 to be folded back.
  • the folded gas refrigerant flows upward into the inner cylinder 14 as the upward flow while continuing the swirling.
  • the flow rate of the gas refrigerant, which is an upward flow is lower than that of the gas refrigerant falling while swirling, and flows centrally in the central portion inside the outer cylinder 13. For this reason, the gas refrigerant to be the upward flow flows into the inside of the inner cylinder 14 which is further in the center direction inside the outer cylinder 13.
  • the projection 14a Since the projection 14a is provided on the inner side surface portion 14b of the inner cylinder 14, it becomes a swirling resistance of the gas refrigerant flowing into the inner cylinder 14, and the flow velocity in the swirling direction of the gas refrigerant is suppressed. It will be a rising flow forward.
  • the gas refrigerant which has risen passes from the outlet portion 15a of the cover 15 through the check valve 18 and flows out to the refrigeration cycle apparatus 200 side.
  • the protrusion 14 a collides with the swirling gas refrigerant, and the flow velocity in the swirling direction of the gas refrigerant is reduced, so that the pressure loss is suppressed and the performance of the screw compressor 1 can be improved.
  • a part of the oil that can not be separated into the oil and the gas refrigerant by swirling the gap 20 between the outer cylinder 13 and the inner cylinder 14 is the inner side surface portion of the inner cylinder 14 while turning the inner cylinder 14 It is accumulated in 14b.
  • the swirling component of the gas refrigerant collides with the projection 14a, the oil is accumulated in the projection 14a.
  • the oil accumulated on the inner side surface portion 14b of the inner cylinder 14 falls into the oil reservoir 19 by gravity. Thereby, the separation efficiency of the oil and the gas refrigerant can be improved as compared to the case where the inner cylinder 14 does not have the protrusion 14 a.
  • the projection 14a is a casting. Therefore, the oil separation efficiency can be improved, and the flow velocity in the swirling direction of the upward flow inside the inner cylinder can be suppressed. Thereby, the pressure loss in the inner cylinder 14 can be reduced.
  • the flow velocity of the swirling flow which flows through the inside of the inner cylinder 14 can be suppressed without providing the straightening vane by providing the projection 14a formed of a casting.
  • the inner cylinder 14 can be reduced in weight and cost can be reduced as compared with the case where the straightening vanes are provided, and the screw compressor 1 with high performance and high oil separation efficiency which is inexpensive can be easily obtained.
  • the oil separator 4 includes the outer cylinder 13 connected to the discharge port 12a from which the compressed refrigerant is discharged.
  • the oil separator 4 includes an inner cylinder 14 disposed inside the outer cylinder 13.
  • the oil separator 4 includes a cover 15 that covers the opening at one end of the inner cylinder 14 at the upper side in the drawing and discharges the gas refrigerant separated from the oil from the outlet 15 a.
  • the oil separator 4 is a cyclone type oil separator.
  • One protrusion 14 a is provided on the inner side surface 14 b of the inner cylinder 14.
  • one protrusion 14 a extending in the direction from the other end of the lower side of the inner cylinder 14 provided in the inner side surface 14 b of the inner cylinder 14 to the one end in the upper direction in the drawing is the inner cylinder 14 of the oil separator 4.
  • the swirling component of the gas refrigerant in the vicinity of the inner side surface portion 14 b collides, and the swirling component of the gas refrigerant in the vicinity of the inner side surface portion 14 b of the inner cylinder 14 of the oil separator 4 can be decelerated.
  • the flow velocity in the swirling direction of the upflow of the gas refrigerant after oil separation can be suppressed, and the pressure loss due to the swirling upflow of the gas refrigerant can be reduced. Therefore, it is possible to realize performance improvement by highly efficient oil separation and pressure loss reduction with an inexpensive and simple structure.
  • the protrusion 14 a is formed from the other end of the lower end of the inner cylinder 14 in the lower side of the drawing in the direction of the one end in the upper side of the drawing.
  • the protrusion 14a extending from the other end in the lower side to the upper end in the upper direction in the drawing extends in one end direction with the swirling component of the gas refrigerant in the vicinity of the inner side surface 14b of the inner cylinder 14 of the oil separator 4
  • the swirling component of the gas refrigerant in the vicinity of the inner side surface portion 14b of the inner cylinder 14 of the oil separator 4 can be further decelerated.
  • the flow velocity in the swirling direction of the upflow of the gas refrigerant after oil separation can be further suppressed, and the pressure loss due to the swirling upflow of the gas refrigerant can be further reduced. Therefore, it is possible to realize performance improvement by highly efficient oil separation and pressure loss reduction with an inexpensive and simple structure.
  • the protrusion 14 a is formed to extend from the other end of the lower end in the drawing to the lid 15.
  • the protrusion 14 a extending from the other end on the lower side to the lid 15 up to the swirl component of the gas refrigerant in the vicinity of the inner side surface 14 b of the inner cylinder 14 of the oil separator 4 and the lid 15
  • the collision continues until the end, and the swirling component of the gas refrigerant near the inner side surface portion 14b of the inner cylinder 14 of the oil separator 4 can be further decelerated.
  • the flow velocity in the swirling direction of the upflow of the gas refrigerant after oil separation can be further suppressed, and the pressure loss due to the swirling upflow of the gas refrigerant can be further reduced. Therefore, it is possible to realize performance improvement by highly efficient oil separation and pressure loss reduction with an inexpensive and simple structure.
  • the height of the protrusion 14 a toward the central axis C of the inner cylinder 14 is 3% or more and 15% or less of the inner diameter of the inner cylinder 14.
  • the height of the protrusion 14 a facing the central axis C of the inner cylinder 14 is 3% to 15% of the inner diameter of the inner cylinder 14. Therefore, the projection 14 a efficiently collides with the swirling component of the gas refrigerant in the vicinity of the inner side surface portion 14 b of the inner cylinder 14 of the oil separator 4 and swirls the gas refrigerant in the vicinity of the inner side surface 14 b of the inner cylinder 14 of the oil separator 4
  • the ingredients can be decelerated more.
  • the protrusion 14 a is formed extending in parallel with the central axis C of the inner cylinder 14.
  • the protrusion 14a extending in parallel to the central axis C of the inner cylinder 14 is directed to the swirling component and the advancing direction of the swirling component of the gas refrigerant in the vicinity of the inner side surface 14b of the inner cylinder 14 of the oil separator 4.
  • the collisions occur substantially at right angles, the collision opportunity increases, and the swirling component of the gas refrigerant in the inner side surface portion 14 b of the inner cylinder 14 of the oil separator 4 can be further decelerated.
  • orthogonal cross sections orthogonal to the central axis C of the inner cylinder 14 in the protrusion 14 a and different in the central axis C direction have the same shape.
  • the protrusion 14 a collides with the swirling component of the gas refrigerant near the inner side surface 14 b of the inner cylinder 14 of the oil separator 4 without generating turbulent flow, and the gas refrigerant near the inner side surface 14 b of the inner cylinder 14 of the oil separator 4
  • the component of rotation of the gear can decelerate without generating useless turbulence.
  • the protrusion 14a has a flat surface at the tip 14a1.
  • the protrusion 14a has a flat surface at the tip 14a1.
  • the protrusion 14 a efficiently collides with the swirling component of the gas refrigerant in the vicinity of the inner side surface portion 14 b of the inner cylinder 14 of the oil separator 4, and the swirling of the gas refrigerant in the vicinity of the inner side surface 14 b of the inner cylinder 14 of the oil separator 4
  • the ingredients can be decelerated more.
  • the protrusion 14 a is provided on the inner side surface 14 b most separated from the inflow port 13 a connected to the discharge port 12 a in the outer cylinder 13.
  • the protrusion 14a provided on the inner side surface 14b most separated from the inflow port 13a of the outer cylinder 13 corresponds to the swirling component of the gas refrigerant in the vicinity of the inner side surface 14b of the inner cylinder 14 of the oil separator 4. It collides so that the momentum of the turning component can be reduced efficiently. Then, the swirling component of the gas refrigerant in the vicinity of the inner side surface portion 14b of the inner cylinder 14 of the oil separator 4 can be decelerated efficiently. In addition, the protrusions 14a can be disposed efficiently without waste, and the inner cylinder 14 does not become excessively heavy.
  • the projection 14a is provided on the inner side surface 14b most separated from the oil outlet 13b. It will be. In that case, the largest amount of oil accumulated at the projection 14a flows toward the oil outlet 13b, and forms a flow which also takes in oil adhering to the other part. Thus, the oil separated from the compressed refrigerant can be efficiently recovered.
  • a screw compressor 1 as a compressor includes an oil separator 4.
  • the screw compressor 1 includes a compressor main body 2 as a compression mechanism provided with a discharge port 12 a that compresses a refrigerant and discharges a compressed refrigerant.
  • the protrusion 14 a collides with the swirling component of the gas refrigerant in the vicinity of the inner side surface 14 b of the inner cylinder 14 of the oil separator 4, and the gas refrigerant in the vicinity of the inner side surface 14 b of the inner cylinder 14 of the oil separator 4
  • the turning component can be decelerated.
  • the compressor is a screw compressor 1.
  • FIG. 5 is a longitudinal sectional view showing an oil separator 4 according to Embodiment 2 of the present invention.
  • FIG. 6 is a development view showing an inner side surface portion 14b of the inner cylinder 14 of the oil separator 4 according to Embodiment 2 of the present invention.
  • the second embodiment only the characteristic part will be described. The same matters as the other embodiments described above will not be described.
  • the protrusion 14 a extends from the other end on the lower side in the drawing to a length of one-fourth or more and less than one-half between the other end and the lid 15.
  • the protrusion 14 a is formed to have a smaller width in the circumferential direction of the inner cylinder 14 than the protrusion 14 a of the first embodiment.
  • the gas refrigerant reduces the flow velocity of the swirling flow in the vicinity of the inner side surface portion 14b of the inner cylinder 14 as it approaches the outlet portion 15a, and increases the upflow component. For this reason, the reduction effect of the swirling flow velocity of the protrusion 14 a provided on the upper portion of the inner cylinder 14 as in the first embodiment is low. So, in Embodiment 2, the projection part 14a is provided only in the lower part of the inner cylinder 14 with a large effect.
  • the protrusion 14 a is provided in a section between one-fourth and less than one-half between the lower end and the lower end of the inner cylinder 14 and the lid 15. Therefore, the weight reduction of the inner cylinder 14 can be achieved while the reduction effect of the swirl flow velocity of the gas refrigerant is maintained. That is, a high performance screw compressor 1 is achieved in which the weight reduction of the inner cylinder 14 is achieved while maintaining the same effect as that of the first embodiment.
  • the projection 14a is more preferably extended from the other end at the other end on the lower side of the drawing to a length of 1/3 between the other end at the other end and the lid 15. is there.
  • the protrusion 14a is a quarter or more and less than a half between the other end of the other end and the lid 15. It is formed extending to the length.
  • the projection 14 a extending from the other end to the other end and the length between the other end and the lid 15 is less than one-fourth and less than one-half, the inner surface 14 b of the inner cylinder 14 of the oil separator 4.
  • the swirling component of the gas refrigerant in the vicinity collides with the swirling component while it has the most momentum, and the swirling component of the gas refrigerant in the vicinity of the inner side surface portion 14b of the inner cylinder 14 of the oil separator 4 can be decelerated.
  • the protrusion 14a can be formed short, and the weight of the inner cylinder 14 can be reduced.
  • FIG. 7 is a cross-sectional view showing an oil separator 4 according to Embodiment 3 of the present invention.
  • the third embodiment only the characteristic part will be described. The same matters as the other embodiments described above will not be described.
  • the protrusion 14a is formed in a curved surface shape in the side surface portion 14a2 that connects the root and the tip portion 14a1.
  • the curved surface shape is an R shape in which the swirling component of the swirling flow of the gas refrigerant changes.
  • the shape of the protrusion 14a is the resistance of the swirling flow.
  • the protrusion 14 a of the third embodiment is formed to have a width in the circumferential direction of the inner cylinder 14 larger than that of the protrusion 14 a of the first embodiment. This is because the width that can form the curved side surface portion 14a2 of the protrusion 14a is required.
  • the side surface portion 14a2 of the projection 14a has an R shape so as to change the direction of the swirling component of the swirling flow of the gas refrigerant flowing along the side surface portion 14a2. For this reason, the flow velocity of the swirling flow of the gas refrigerant in the vicinity of the inner side surface portion 14b of the inner cylinder 14 is reduced, and the flow velocity of the upward flow component of the gas refrigerant is increased.
  • the side wall portion 14a2 of the projection 14a has a curved surface shape so that the swirling component of the gas refrigerant in the vicinity of the inner side surface portion 14b of the inner cylinder 14 changes the direction.
  • a high-performance screw compressor 1 capable of reducing pressure loss as compared with the first embodiment can be obtained.
  • the protrusion 14a is formed in a curved shape in the side surface portion 14a2 that connects the root portion on the inner side surface portion 14b side and the tip portion 14a1.
  • the protrusion 14a formed in a curved shape on the side surface 14a2 connecting the root and the tip 14a1 changes the direction of the swirling component of the gas refrigerant near the inner surface 14b of the inner cylinder 14
  • the swirling component of the gas refrigerant in the vicinity of the inner side surface portion 14b of the inner cylinder 14 of the vessel 4 can be decelerated efficiently.
  • the protrusion 14 a has a length from a quarter to a half of the distance between the other end and the lid 15 from the other end on the lower side in the drawing. It extends.
  • the protrusion 14a is formed in a curved shape in the side surface portion 14a2 connecting the root and the tip portion 14a1.
  • the curved surface shape is an R shape in which the swirling component of the swirling flow of the gas refrigerant changes.
  • the protrusion 14 a of the fourth embodiment is formed so that the circumferential width of the inner cylinder 14 is larger than that of the protrusion 14 a of the first embodiment. This is because the width that can form the curved side surface portion 14a2 of the protrusion 14a is required.
  • the protrusion 14a extends from the lower end of the inner cylinder 14 to a length of a quarter or more and less than a half between the lower end and the lid 15. ing.
  • the weight reduction of the inner cylinder 14 can be achieved while maintaining the reduction of the swirl flow velocity of the gas refrigerant. That is, a high-performance screw compressor 1 can be obtained which is reduced in weight while maintaining the same effect as that of the third embodiment.
  • FIG. 8 is a cross-sectional view showing an oil separator 4 according to Embodiment 5 of the present invention.
  • the fifth embodiment only the characteristic part will be described. The same matters as the other embodiments described above will not be described.
  • protrusions 14 a are provided at equal intervals along the circumference of the inner cylinder 14.
  • one of the four protrusions 14 a is provided on the inner side surface 14 b that is most distant from the inflow port 13 a.
  • the number of protrusions 14a is one. However, it is not limited to this.
  • the number of the protrusions 14 a is not necessarily limited to one, and a plurality of the protrusions 14 a may be equally disposed along the circumference of the inner cylinder 14.
  • the swirling component of the gas refrigerant and the inner cylinder 14 in the vicinity of the inner side surface portion 14b of the inner cylinder 14 of the oil separator 4 are provided with four projections 14a provided at equal intervals along the circumference of the inner cylinder 14.
  • the collision of the gas refrigerant in the vicinity of the inner side surface portion 14b of the inner cylinder 14 of the oil separator 4 can be further decelerated.
  • the protrusion 14a is an example of the inner side surface 14b of the inner cylinder 14 extending from the other end of the lower end of the inner cylinder 14 in the lower side in the drawing in the direction of one end in the upper side in the drawing. However, it is not limited to this.
  • the protrusion 14a extends from the side adjacent to the upper side of the air gap to the upper side of the upper side of the drawing in the inner side surface 14b of the inner cylinder 14 with a space at the other end of the lower end of the inner cylinder 14 May be. Further, the length of the protrusion 14a can be designed as long as it extends from the other end on the lower side in the drawing in the direction of one end on the upper side in the drawing.
  • the protrusion 14a may be formed on the inner side surface 14 b of the inner cylinder 14 and may be formed extending in a direction other than the direction perpendicular to the central axis C of the inner cylinder 14.
  • the protrusion 14 a is not necessarily formed by casting, and may be welded to the inner cylinder 14.
  • the screw compressor 1 is disposed in a state in which the central axis C extends in the vertical direction in the outer cylinder 13 and the inner cylinder 14 of concentric circles in the oil separator 4.
  • the screw compressor 1 may be disposed such that the central axis C of the outer cylinder 13 and the inner cylinder 14 in the oil separator 4 extends in a direction diagonal to the horizontal direction or the upper and lower direction.
  • the operation of the screw compressor 1 may be either constant speed drive operating at a constant rotational speed, or inverter drive controlling the rotational speed of the motor 5.
  • the refrigerant applied to the screw compressor 1 is not limited to a specific refrigerant.
  • the refrigerant with a low GWP is, for example, R32, HFO-1123, HFO-1234yf, HFO-1234ze, or a mixed refrigerant containing at least one of these.
  • the refrigerant applied to the screw compressor 1 may be a natural refrigerant such as carbon dioxide.
  • FIG. 9 is a refrigerant circuit diagram showing a refrigeration cycle apparatus 200 to which a screw compressor 1 according to Embodiment 6 of the present invention is applied.
  • the refrigeration cycle apparatus 200 includes a screw compressor 1, a condenser 201, an expansion valve 202 and an evaporator 203.
  • the screw compressor 1, the condenser 201, the expansion valve 202, and the evaporator 203 are connected by refrigerant pipes to form a refrigeration cycle circuit. Then, the refrigerant that has flowed out of the evaporator 203 is drawn into the screw compressor 1 and becomes high temperature and high pressure. The high temperature and pressure refrigerant is condensed in the condenser 201 to become a liquid.
  • the refrigerant that has become a liquid is decompressed and expanded by the expansion valve 202 and becomes a low-temperature low-pressure gas-liquid two phase, and the gas-liquid two-phase refrigerant is heat-exchanged in the evaporator 203.
  • the screw compressor 1 of the first to fifth embodiments can be applied to such a refrigeration cycle apparatus 200.
  • refrigeration cycle apparatus 200 an air conditioning apparatus, a freezer, or a water heater etc. are mentioned, for example.
  • the refrigeration cycle apparatus 200 includes a screw compressor 1 as the compressor described in the first to fifth embodiments.
  • the protrusion 14 a collides with the swirling component of the gas refrigerant in the vicinity of the inner side surface portion 14 b of the inner cylinder 14 of the oil separator 4.
  • the swirling component of the gas refrigerant in the vicinity of the inner side surface portion 14b of the inner cylinder 14 can be decelerated.
  • Reference Signs List 1 screw compressor, 2 compressor body, 3 casing, 4 oil separator, 5 motor, 5a stator, 5b motor rotor, 6 screw shaft, 7 screw rotor, 7a screw groove, 8 bearing, 9 gate rotor, 9a tooth Parts, 10 slide valve, 10a opening, 11 compression chamber, 12 discharge chamber, 12a discharge port, 13 outer cylinder, 13a inlet, 13b oil outlet, 13c inner side, 14 inner cylinder, 14a protrusion, 14a1 tip, 14a2 side surface portion, 14b inner side surface portion, 15 lid portion, 15a outlet portion, 16 bottom portion, 17 wave adjustment plate, 18 check valve, 19 oil storage portion, 20 gap, 21 space portion, 200 refrigeration cycle device, 201 condenser, 202 expansion valve, 203 evaporator.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

La présente invention concerne un séparateur d'huile, à savoir un séparateur d'huile à cyclone comprenant : un cylindre externe relié à un orifice d'éjection à travers lequel un agent de refroidissement comprimé est éjecté ; un cylindre interne agencé à l'intérieur du cylindre externe ; et une partie couvercle destinée à recouvrir l'ouverture au niveau d'une extrémité du cylindre interne, éjectant en même temps un agent de refroidissement gazeux, qui a été séparé d'une huile, à travers une sortie. Le séparateur d'huile est conçu de sorte que la surface interne du cylindre interne soit pourvue d'une ou de plusieurs saillies.
PCT/JP2018/002689 2018-01-29 2018-01-29 Séparateur d'huile, compresseur et dispositif à cycle frigorifique WO2019146100A1 (fr)

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PCT/JP2018/002689 WO2019146100A1 (fr) 2018-01-29 2018-01-29 Séparateur d'huile, compresseur et dispositif à cycle frigorifique

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022269804A1 (fr) * 2021-06-23 2022-12-29 三菱電機株式会社 Compresseur à vis
US11747064B2 (en) 2020-03-30 2023-09-05 Carrier Corporation Integrated oil separator with flow management

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2771157A (en) * 1952-07-11 1956-11-20 Hjorth & Co Ab Method of converting kinetic energy to pressure energy and a device for carrying out the method
JPH07864A (ja) * 1993-03-26 1995-01-06 J M Voith Gmbh ウェットサイクロン
JP2003083272A (ja) * 2001-09-11 2003-03-19 Hitachi Ltd スクリュー圧縮機
JP2006102736A (ja) * 2004-10-08 2006-04-20 Samsung Kwangju Electronics Co Ltd サイクロン集塵装置
JP2007534377A (ja) * 2004-05-12 2007-11-29 ダイソン・テクノロジー・リミテッド サイクロン式分離装置
JP2015152204A (ja) * 2014-02-13 2015-08-24 日立アプライアンス株式会社 冷凍サイクル装置

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2771157A (en) * 1952-07-11 1956-11-20 Hjorth & Co Ab Method of converting kinetic energy to pressure energy and a device for carrying out the method
JPH07864A (ja) * 1993-03-26 1995-01-06 J M Voith Gmbh ウェットサイクロン
JP2003083272A (ja) * 2001-09-11 2003-03-19 Hitachi Ltd スクリュー圧縮機
JP2007534377A (ja) * 2004-05-12 2007-11-29 ダイソン・テクノロジー・リミテッド サイクロン式分離装置
JP2006102736A (ja) * 2004-10-08 2006-04-20 Samsung Kwangju Electronics Co Ltd サイクロン集塵装置
JP2015152204A (ja) * 2014-02-13 2015-08-24 日立アプライアンス株式会社 冷凍サイクル装置

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11747064B2 (en) 2020-03-30 2023-09-05 Carrier Corporation Integrated oil separator with flow management
WO2022269804A1 (fr) * 2021-06-23 2022-12-29 三菱電機株式会社 Compresseur à vis

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