US20080240954A1 - Rotary compressor - Google Patents

Rotary compressor Download PDF

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Publication number
US20080240954A1
US20080240954A1 US12/073,484 US7348408A US2008240954A1 US 20080240954 A1 US20080240954 A1 US 20080240954A1 US 7348408 A US7348408 A US 7348408A US 2008240954 A1 US2008240954 A1 US 2008240954A1
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United States
Prior art keywords
compressing section
stage
low
stage compressing
shaft
Prior art date
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Abandoned
Application number
US12/073,484
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English (en)
Inventor
Naoya Morozumi
Kenshi Ueda
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Fujitsu General Ltd
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Fujitsu General Ltd
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Assigned to FUJITSU GENERAL LIMITED reassignment FUJITSU GENERAL LIMITED ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MOROZUMI, NAOYA, UEDA, KENSHI
Publication of US20080240954A1 publication Critical patent/US20080240954A1/en
Abandoned legal-status Critical Current

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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
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • F04C23/001—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 of similar working principle
    • 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
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
    • 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
    • F04C2240/60—Shafts
    • F04C2240/601—Shaft flexion

Definitions

  • the present invention relates to a rotary compressor having two-stage compressing sections including a low-stage compressing section and a high-stage compressing section. More particularly, it relates to a technique for preventing a deflection occurring on a shaft connecting a motor and the compressing section to each other to enhance the reliability.
  • a compressing section is arranged in the lower part of a closed vessel in which lubricating oil accumulates.
  • a two-stage compression rotary compressor in order to make better the balance of compressive load torques produced in two compressing sections and the balance of centrifugal forces acting on the off-center parts corresponding to the two compressing sections, that is, turning pistons and the off-center parts of a shaft engaging with the pistons, the compression phases of a low-stage compressing section and a high-stage compressing section are shifted through 180 degrees.
  • the volume of the high-stage compressing section must be smaller than the volume of the low-stage compressing section.
  • the thickness of compression chamber that is, the thickness of a cylinder is decreased
  • the turning radius of the piston is decreased.
  • the low-stage compressing section is arranged above the high-stage compressing section, there arises a problem described below.
  • the oil level of lubricating oil lowers from the compressing section arranged on the upper side in the closed vessel, and the compressing section on the upper side is exposed to refrigerant gas. Therefore, the refrigerant leaks into a suction chamber and the compression chamber passing through a gap between a vane and a vane groove, whereby a leakage loss is created.
  • the low-stage compressing section is arranged on the upper side, since the interior of closed vessel has the discharge pressure of the high-stage compressing section, the difference in pressure between the suction chamber and the compression chamber is large as compared with the case where the high-stage compressing section is arranged on the upper side, so that the quantity of refrigerant leaking into the suction chamber and the compression chamber through the gap increases, which presents a problem of further decreased efficiency of compressor.
  • an object of the present invention is to provide a rotary compressor in which the mass of a balancer can be decreased, and thereby the deflection of a shaft is reduced, so that the seizure in bearing parts and the contact of a rotor with a stator can be prevented.
  • a rotary compressor having a two-stage compressing section including a low-stage compressing section and a high-stage compressing section provided in a closed shell, and a motor for driving the two-stage compressing section, the high-stage compressing section being arranged on the motor side is characterized in that when the axial length of the off-center part of shaft corresponding to the low-stage compressing section, that is, a low-stage side crankshaft, is taken as L 1 , and the axial length of the off-center part of shaft corresponding to the high-stage compressing section, that is, a high-stage side crankshaft, is taken as L 2 , L 2 is longer than L 1 .
  • the mass of a balancer attached to a rotor can be made small by making the axial length of the high-stage side crankshaft longer than that of the low-stage side crankshaft. Thereby, the deflection of the whole of the shaft is reduced, so that seizure caused by a local excessive load of a bearing part and the contact of the rotor with a stator can be prevented.
  • the rotary compressor is characterized in that the rotational speed of the compressing section is variable.
  • the rotational speed is variable, when the rotational speed is high, the centrifugal forces acting on an upper balancer and a lower balancer increase, by which the deflection of the shaft is increased, and therefore the effect of the present invention is further increased.
  • FIG. 1 is a longitudinal sectional view of a rotary compressor in accordance with one embodiment of the present invention
  • FIG. 2 is a transverse sectional view of a compressing section of the rotary compressor shown in FIG. 1 ;
  • FIG. 3 is a schematic view showing rotating parts of the rotary compressor shown in FIG. 1 and centrifugal forces acting thereon;
  • FIG. 4 is a schematic view showing a deflected state of a shaft formed by centrifugal forces of the rotary compressor shown in FIG. 1 .
  • a rotary compressor 1 includes a cylindrical closed vessel 2 arranged in the vertical direction, a motor 4 provided in an upper part in the closed vessel 2 , and a compressing section 3 in a lower part therein.
  • the closed vessel 2 consists of a cylindrical main shell 21 , a dome-shaped top shell 22 that closes the upper end part of the main shell 21 , and a dome-shaped bottom shell 23 that closes the lower end part of the main shell 21 .
  • the top shell 22 and the bottom shell 23 are fixed to the main shell 21 by welding.
  • the top shell 22 is provided with a refrigerant discharge pipe 24 for discharging the refrigerant having been discharged into the closed vessel 2 from the compressing section 3 to the outside of the closed vessel 2 .
  • a stator 41 of the motor 4 is shrinkage fitted to the main shell 21 .
  • a rotor 42 of the motor 4 is shrinkage fitted onto a shaft 7 mechanically connecting the motor 4 to the compressing section 3 .
  • an upper balancer 43 and a lower balancer 44 are attached, respectively, to balance the centrifugal forces of the whole of rotating parts.
  • the compressing section 3 is provided with a high-stage compressing section 32 in the upper part thereof and a low-stage compressing section 31 in the lower part thereof.
  • the discharge side of the low-stage compressing section 31 and the suction side of the high-stage compressing, section 32 are connected to each other by an intermediate connection pipe 26 on the outside of the closed vessel 2 , by which a two-stage compressing section is formed.
  • FIG. 2 shows the transverse cross section of the low-stage compressing section 31 shown in FIG. 1 .
  • the configuration of the high-stage compressing section 32 is the same as that of the low-stage compressing section 31 except that the pistons are 180° out-of-phase.
  • Each of the compressing sections 31 and 32 has a cylinder 200 , 400 and a cylindrical piston 220 , 420 accommodated in a cylindrical cylinder bore 200 a , 400 a formed on the inside of the cylinder 200 , 400 . Between the internal wall of the cylinder bore 200 a , 400 a and the outer peripheral surface of the piston 220 , 420 , a working space for refrigerant is formed.
  • the cylinder 200 , 400 is provided with a cylinder groove 200 b , 400 b directed from the cylinder bore 200 a , 400 a toward the outer periphery direction, and has a flat plate shaped vane 230 , 430 in the cylinder groove 200 b , 400 b.
  • a spring 240 , 440 is provided between the vane 230 , 430 and the internal wall of the closed vessel 2 .
  • the tip end of the vane 230 , 430 is brought into sliding contact with the outer wall of the piston 220 , 420 , by which the working space is divided into a suction chamber V 1 , V 2 and a compression chamber C 1 , C 2 .
  • each of the cylinder 200 , the piston 220 , and the vane 230 on the high-stage side has a smaller thickness in the axial direction than each of the cylinder 400 , the piston 420 , and the vane 430 on the low-stage side.
  • the compressor 1 has a main frame 100 above the high-stage side cylinder 200 , an intermediate partition plate 300 between the high-stage side cylinder 200 and the low-stage side cylinder 400 , and a sub-frame 500 below the low-stage side cylinder 400 , and the upside and the downside of each of the two working spaces are closed by the main frame 100 , the intermediate partition plate 300 , and the sub-frame 500 , whereby each of the two working spaces is formed into a closed space.
  • a high-stage side discharge muffler cover 130 is provided, and a high-stage side discharge muffler chamber M 2 for reducing the pressure pulsation of discharged refrigerant is formed.
  • a low-stage side discharge muffler cover 510 is provided, and a low-stage side discharge muffler chamber M 1 for reducing the pressure pulsation of discharged refrigerant is formed.
  • the high-stage side discharge muffler cover 130 , the main frame 100 , the high-stage side cylinder 200 , the intermediate partition plate 300 , the low-stage side cylinder 400 , the sub-frame 500 , and the low-stage side discharge muffler cover 510 are fixed integrally with bolts (not shown), and further the outer peripheral part of the main frame 100 is fixed to the main shell 21 by spot welding.
  • the main frame 100 and the sub-frame 500 have bearing parts 110 and 502 , respectively, so that the shaft 7 is fitted in the bearing parts 110 and 502 so as to be rotatably supported.
  • the shaft 7 has two crankshafts 72 and 73 that are off-centered in the 180° different direction.
  • One crankshaft 72 engages with the piston 220 of the high-stage compressing section 32
  • the other crankshaft 73 engages with the piston 420 of the low-stage compressing section 31 .
  • the pistons 220 and 420 turn while slidingly contacting with the inside walls of the respective cylinder bores 200 a and 400 a , and following this turning motion of the pistons 220 and 420 , the vanes 230 and 430 reciprocate, by which the volumes of the suction chambers V 1 and V 2 and the compression chambers C 1 and C 2 are changed continuously.
  • the compressing section 3 repeats the suction and compression of refrigerant.
  • the suction chamber V 1 of the low-stage compressing section 31 is connected to a refrigerant suction pipe 64 via a low-stage side suction hole 410 provided in the cylinder 400 .
  • the compression chamber C 1 of the low-stage compressing section 31 is connected to the intermediate connection pipe 26 via a low-stage side discharge hole 520 provided in the sub-frame 500 and the low-stage side discharge muffler chamber M 1 .
  • the low-stage side discharge hole 520 is provided with a check valve 540 .
  • the refrigerant suction pipe 64 is connected to the low-stage side suction hole 410 via a low-stage side suction connection pipe 411
  • the intermediate connection pipe 26 is connected to the low-stage side discharge muffler chamber M 1 via an intermediate discharge connection pipe 521 .
  • the suction chamber V 2 of the high-stage compressing section 32 is connected to the intermediate connection pipe 26 via a high-stage side suction hole 210 provided in the cylinder 200 .
  • the compression chamber C 2 of the high-stage compressing section 32 is open to the interior of the closed vessel 2 via a high-stage side discharge hole 120 provided in the main frame 100 and the high-stage side discharge muffler chamber M 2 .
  • the high-stage side discharge hole 120 is provided with a check valve 140 .
  • the intermediate connection pipe 26 is connected to the high-stage side suction hole 210 via an intermediate suction connection pipe 211 .
  • an accumulator 6 consisting of an independent closed vessel 61 is provided.
  • a refrigerant return pipe 62 is provided above the accumulator 6 , the refrigerant return pipe 62 being connected to a heat pump system, not shown.
  • the refrigerant suction pipe 64 one end having an L shape of which is extended to the upper part in the accumulator 6 and the other end of which is connected to the suction chamber V 1 of the low-stage compressing section 31 from the side surface of the compressor 1 .
  • the low-stage side suction chamber V 1 comes to a position isolated from the low-stage side suction hole 410 , and is turned to the low-stage side compression chamber C 1 as it is, by which the refrigerant is compressed.
  • the check valve 540 When the pressure of the compressed refrigerant reaches the pressure in the low-stage side discharge muffler chamber M 1 on the outside of the check valve 540 provided in the low-stage side discharge hole 520 , that is, an intermediate pressure, the check valve 540 is opened, by which the compressed refrigerant is discharged into the low-stage side discharge muffler chamber M 1 .
  • the refrigerant After the pressure pulsation of refrigerant, which may cause noise, has been reduced in the low-stage side discharge muffler chamber M 1 , the refrigerant is guided into the suction chamber V 2 of the high-stage compressing section 32 through the intermediate connection pipe 26 .
  • the refrigerant guided into the suction chamber V 2 of the high-stage compressing section 32 is sucked, compressed, and discharged in the high-stage compressing section 32 on the same principle as that of the low-stage compressing section 31 .
  • the refrigerant is discharged into the closed vessel 2 .
  • the refrigerant is further guided to a portion above the motor 4 after passing through a core notch (not shown) in the stator 41 of the motor 4 and a gap between a core and a coil, and is discharged to the system side through the discharge pipe 24 .
  • FIG. 3 is a schematic view extractingly showing the rotating parts in the compressor.
  • centrifugal forces acting on the rotating parts there are generated a centrifugal force (F 1 ) acting on the low-stage side crankshaft 73 and the low-stage side piston 420 engaging therewith, a centrifugal force (F 2 ) acting on the high-stage side crankshaft 72 and the high-stage side piston 220 engaging therewith, a centrifugal force (F 4 ) acting on the upper balancer 43 attached to above the rotor 42 , and a centrifugal force (F 3 ) acting on the lower balancer 44 attached to below the rotor 42 .
  • F 1 centrifugal force acting on the low-stage side crankshaft 73 and the low-stage side piston 420 engaging therewith
  • F 2 centrifugal force acting on the high-stage side crankshaft 72 and the high-stage side piston 220 engaging therewith
  • F 4 acting on the upper balancer 43 attached to above the rotor 42
  • F 3 centrifugal force
  • Equation (2) is obtained from the moment around the application point of F 3 .
  • F 3 and F 4 that is, the mass of the upper balancer 43 of the rotor 42 and the mass of the lower balancer 44 thereof are determined so as to satisfy Equation (2).
  • Equation (3) From Equation (3), it can be seen that F 4 can be decreased as F 1 is decreased or F 2 is increased.
  • the upper balancer 43 of the rotor 42 can be made smaller as the mass of the low-stage side crankshaft 73 is decreased or the mass of the high-stage side crankshaft 72 is increased.
  • FIG. 4 is a schematic view extractingly showing the shaft 7 and the bearing part 110 supporting the shaft 7 .
  • the shaft 7 deforms exceeding the gap between the shaft 7 and the bearing part 110 , and comes locally into contact with the bearing part 110 at the upper or lower part of the bearing part 110 , which may cause seizure.
  • the axial length of the high-stage side crankshaft 72 is made longer than the axial length of the low-stage side crankshaft 73 .
  • the upper balancer 43 of the rotor 42 can be made small, so that the deflection of the whole of the shaft 7 is reduced, whereby seizure caused by a local excessive load of the bearing part 110 and the contact of the rotor 42 with the stator 41 can be prevented.
  • the compression ratio ⁇ 2 of the high-stage compressing section 32 is high necessarily.
  • the load torque of the high-stage compressing section 32 is higher than that of the low-stage compressing section 31 .
  • the length of crankshaft not shorter than a predetermined length is necessary.
  • the increase in length of crankshaft achieved than necessary is unfavorable because it may cause an increase in slide loss in a crank part.
  • the axial length L 2 of the high-stage side crankshaft is made longer than the axial length L 1 of the low-stage side crankshaft (L 2 >L 1 ).
  • the rotary compressor 1 configured so that in the compressor provided with the two-stage compression type compressing section having the low-stage compressing section 31 and the high-stage compressing section 32 , the working space volume of the high-stage compressing section 32 is made smaller than that of the low-stage compressing section 31 by making the axial length of the high-stage compressing section 32 shorter than that of the low-stage compressing section 31 has been shown typically as a preferred mode.
  • the configuration of the rotary compressor 1 may be such that the working space volume of the high-stage compressing section 32 is made smaller by making the axial lengths of the low-stage compressing section 31 and the high-stage compressing section 32 equal to each other and by making the turning radius of the high-stage side piston 220 smaller than that of the low-stage side piston 420 .
  • the rotary compressor 1 may be a two-stage compression rotary compressor configured so that a gas injection cycle is used as the refrigerating cycle, and an injection refrigerant is allowed to flow into an intermediate compressing section between the low-stage compressing section 31 and the high-stage compressing section 32 .
  • the compressing mechanism of the compressing section 3 is not limited to the compressing mechanism shown in this embodiment if the compressor is configured so that the change in volumes of the suction chamber V 1 , V 2 and the compression chamber C 1 , C 2 caused by the turning motion of the piston 220 , 420 imparted by the crankshaft 72 , 73 is utilized.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)
US12/073,484 2007-03-28 2008-03-06 Rotary compressor Abandoned US20080240954A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2007083399A JP2008240667A (ja) 2007-03-28 2007-03-28 ロータリ圧縮機
JP2007-083399 2007-03-28

Publications (1)

Publication Number Publication Date
US20080240954A1 true US20080240954A1 (en) 2008-10-02

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US12/073,484 Abandoned US20080240954A1 (en) 2007-03-28 2008-03-06 Rotary compressor

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US (1) US20080240954A1 (fr)
EP (1) EP1975413A1 (fr)
JP (1) JP2008240667A (fr)
CN (1) CN101275562A (fr)

Cited By (8)

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US20110150683A1 (en) * 2009-12-22 2011-06-23 Lee Yunhi Rotary compressor
US20110165004A1 (en) * 2009-04-09 2011-07-07 Joon-Hong Park Rotary-type 2-stage compressor
US20140105774A1 (en) * 2012-10-12 2014-04-17 Jinung Shin Hermetic compressor
US20170350394A1 (en) * 2014-12-15 2017-12-07 Samsung Electronics Co., Ltd. Rotary-type compressor
US20180017057A1 (en) * 2016-07-14 2018-01-18 Fujitsu General Limited Rotary compressor
US20210370620A1 (en) * 2018-10-04 2021-12-02 Premium Aerotec Gmbh Semi-Finished Product And Method For Producing A Structural Component
US11971037B2 (en) 2017-01-30 2024-04-30 Daikin Industries, Ltd. Drive shaft of compressor having oil groove portion and oil sump
US12565014B2 (en) 2018-10-04 2026-03-03 Premium Aerotec Gmbh Methods for producing a structural component

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JP5201045B2 (ja) * 2009-03-24 2013-06-05 株式会社富士通ゼネラル ２段圧縮ロータリ圧縮機
JP4655166B2 (ja) * 2009-08-06 2011-03-23 ダイキン工業株式会社 圧縮機
CN102691661B (zh) * 2011-03-23 2014-07-23 珠海格力节能环保制冷技术研究中心有限公司 旋转压缩机
CN109026693B (zh) * 2018-08-31 2023-10-03 珠海格力电器股份有限公司 泵体组件、压缩机及空调器
CN110685911A (zh) * 2019-09-29 2020-01-14 安徽美芝精密制造有限公司 压缩机及制冷设备

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US5006051A (en) * 1987-12-03 1991-04-09 Kabushiki Kaisha Toshiba Rotary two-cylinder compressor with delayed compression phases and oil-guiding bearing grooves
US5597293A (en) * 1995-12-11 1997-01-28 Carrier Corporation Counterweight drag eliminator
US6280168B1 (en) * 1999-07-01 2001-08-28 Sanyo Electric Co., Ltd Multi-cylinder rotary compressor
US6651458B1 (en) * 1999-08-31 2003-11-25 Sanyo Electric Co., Ltd. Internal intermediate pressure 2-stage compression type rotary compressor
US6732542B2 (en) * 2001-11-19 2004-05-11 Sanyo Electric Co., Ltd. Defroster of refrigerant circuit and rotary compressor

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US20110165004A1 (en) * 2009-04-09 2011-07-07 Joon-Hong Park Rotary-type 2-stage compressor
US8807973B2 (en) * 2009-04-09 2014-08-19 Lg Electronics Inc. Rotary-type 2-stage compressor
US20110150683A1 (en) * 2009-12-22 2011-06-23 Lee Yunhi Rotary compressor
US8967984B2 (en) * 2009-12-22 2015-03-03 Lg Electronics Inc. Rotary compressor
US20140105774A1 (en) * 2012-10-12 2014-04-17 Jinung Shin Hermetic compressor
US9188126B2 (en) * 2012-10-12 2015-11-17 Lg Electronics Inc. Hermatic compressor having a fluid guide disposed in an intermediate chamber
US20170350394A1 (en) * 2014-12-15 2017-12-07 Samsung Electronics Co., Ltd. Rotary-type compressor
US10851782B2 (en) * 2014-12-15 2020-12-01 Samsung Electronics Co., Ltd. Rotary-type compressor
US20180017057A1 (en) * 2016-07-14 2018-01-18 Fujitsu General Limited Rotary compressor
US10738779B2 (en) * 2016-07-14 2020-08-11 Fujitsu General Limited Rotary compressor
US11971037B2 (en) 2017-01-30 2024-04-30 Daikin Industries, Ltd. Drive shaft of compressor having oil groove portion and oil sump
US20210370620A1 (en) * 2018-10-04 2021-12-02 Premium Aerotec Gmbh Semi-Finished Product And Method For Producing A Structural Component
US12179438B2 (en) * 2018-10-04 2024-12-31 Premium Aerotec Gmbh Semi-finished product and method for producing a structural component
US12565014B2 (en) 2018-10-04 2026-03-03 Premium Aerotec Gmbh Methods for producing a structural component

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JP2008240667A (ja) 2008-10-09
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