WO2010117214A2 - 로터리식 2단 압축기 - Google Patents
로터리식 2단 압축기 Download PDFInfo
- Publication number
- WO2010117214A2 WO2010117214A2 PCT/KR2010/002145 KR2010002145W WO2010117214A2 WO 2010117214 A2 WO2010117214 A2 WO 2010117214A2 KR 2010002145 W KR2010002145 W KR 2010002145W WO 2010117214 A2 WO2010117214 A2 WO 2010117214A2
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- low pressure
- high pressure
- rotary
- stage compressor
- refrigerant
- Prior art date
Links
Images
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
-
- 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
- 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
-
- 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
-
- 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
- F04C2240/00—Components
- F04C2240/80—Other components
- F04C2240/806—Pipes for fluids; Fittings therefor
-
- 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
- F04C2250/00—Geometry
Definitions
- the present invention relates to a rotary two stage compressor. More particularly, the present invention relates to a rotary two-stage compressor that improves the structure of a connecting pipe for guiding a medium pressure refrigerant compressed in a low pressure compression assembly to a high pressure compression assembly.
- a compressor is a mechanical device that increases pressure by receiving power from a power generator such as an electric motor or a turbine to compress air, refrigerant, or various other working gases. It is widely used throughout.
- These compressors can be classified into reciprocating compressors for compressing refrigerant while linearly reciprocating inside the cylinders by forming a compression space in which the working gas is absorbed and discharged between the piston and the cylinder.
- a rotary compressor for compressing the refrigerant while the roller is eccentrically rotated along the inner wall of the cylinder to form a compression space in which the working gas is sucked and discharged between the roller and the cylinder which are eccentrically rotated.
- a scroll compressor for compressing the refrigerant while the turning scroll is rotated along the fixed scroll to form a compressed space in which the working gas is sucked and discharged between the orbiting scroll and the fixed scroll.
- the rotary compressor has two rollers and two cylinders at the top and the bottom, and a pair of roller and cylinders at the top and the bottom, and a rotary twin compressor for compressing the part and the rest at the top and the bottom.
- Two-stage compressor with two rollers and two cylinders in communication one pair compresses relatively low pressure refrigerant and the other compresses relatively high pressure refrigerant after low pressure compression stage Further development.
- a rotary compressor In the Republic of Korea Patent Publication No. 1994-001001 a rotary compressor is disclosed.
- the motor is located inside the shell, and a rotating shaft is installed to penetrate the motor.
- a cylinder is located under the electric motor, and an eccentric portion fitted to the rotating shaft and a roller fitted to the eccentric portion are located inside the cylinder.
- the cylinder has a coolant discharge hole and a coolant inlet hole, and a vane is provided between the coolant discharge hole and the coolant inlet hole to prevent the uncompressed low pressure refrigerant from mixing with the compressed high pressure refrigerant.
- a spring is installed at one end of the vane to maintain the eccentric and rotating roller and the vane in contact.
- Republic of Korea Patent Publication No. 10-2005-0062995 discloses a rotary twin compressor. Referring to FIG. 1, two cylinders 1035 and 1045 and an intermediate plate 1030 which compress the same capacity are provided, and the compression capacity is improved by twice compared to the first stage compressor.
- Republic of Korea Patent Publication No. 10-2007-0009958 discloses a rotary two-stage compressor.
- the compressor 2001 includes an electric motor 2014 having a stator 2007 and a rotor 2008 above an inside of a sealed container 2013, and two rotary shafts 2002 connected to the electric motor are provided. Eccentricity is provided.
- the main bearing 2009, the high pressure compression element 2020b, the intermediate plate 2015, the low pressure compression element 2020a and the sub bearing 2019 are laminated in order from the electric motor 2014 side with respect to the rotating shaft 2002.
- an intermediate tube 2040 for introducing refrigerant compressed in the low pressure compression element 2020a into the high pressure compression element 2020b.
- the present invention provides a connection pipe for guiding the refrigerant compressed in the low pressure compression assembly to the high pressure compression assembly having different inner diameters according to the role of each part, thereby ensuring the reliability of the compressor and improving the refrigeration capacity of the compressor.
- An object of the present invention is to provide a rotary two stage compressor having a pipe.
- the present invention is provided in a closed container, a closed container provided with a rotating shaft for transmitting rotational force, a low pressure roller that rotates eccentrically about a center of the rotating shaft, a low pressure cylinder in which the low pressure roller is accommodated, and a low pressure vane partitioning the low pressure cylinder internal space.
- High pressure compression assembly having a low pressure compression assembly, a high pressure roller that rotates eccentrically about the center of the rotating shaft, a high pressure cylinder accommodating the high pressure roller, and a high pressure vane partitioning the inner space of the high pressure cylinder, the refrigerant compressed in the low pressure compression assembly
- a connecting pipe providing a flow path to be introduced into the assembly and an injection pipe connected to the connecting pipe, wherein the ratio of the stroke volume (V2) of the high pressure cylinder to the stroke volume (V1) of the low pressure cylinder is 0.43 ⁇ V2 / V2 ⁇ 0.82. It provides a rotary two-stage compressor characterized by satisfying the.
- the present invention is provided in a closed container, a closed container, provided with a rotating shaft for transmitting rotational force, a low pressure roller that rotates eccentrically about the center of the rotating shaft, a low pressure cylinder to accommodate the low pressure roller and a low pressure vane partitioning the inner space of the low pressure cylinder.
- High pressure compression assembly having a low pressure compression assembly, a high pressure roller which rotates eccentrically about the center of the rotating shaft, a high pressure cylinder accommodating the high pressure roller, and a high pressure vane partitioning the inner space of the high pressure cylinder, and the refrigerant compressed in the low pressure compression assembly is It provides a rotary two-stage compressor comprising a connecting pipe for providing a flow path to be introduced into the compression assembly and an injection pipe connected to the connecting pipe, the inner diameter of the intermediate portion of the connecting pipe is larger than both ends of the connecting pipe.
- the present invention further includes an intermediate pressure chamber in which a refrigerant compressed in a low pressure compression assembly is discharged and temporarily stored, wherein one end of the connection pipe is connected to the intermediate pressure chamber, and the other end is connected to the high pressure cylinder.
- a rotary two stage compressor Provided is a rotary two stage compressor.
- the inner diameter Du of the high pressure side end portion of the connecting pipe satisfies the relational expression of 0.4 ⁇ Du / H ⁇ 0.85 with respect to the height H of the high pressure cylinder. Provides only a compressor.
- a rotary two-stage compressor characterized in that the inner diameter Du of the high pressure side end of the connecting pipe is at least 5 mm smaller than the height H of the high pressure cylinder.
- the intermediate pressure chamber is formed in the lower bearing, and the inner diameter Du of the low pressure side end of the connecting pipe has a relation of 0.4 ⁇ Du / H ⁇ 0.85 with respect to the height H of the lower bearing. It provides a rotary two-stage compressor characterized in that it satisfies.
- the intermediate pressure chamber is formed in the lower bearing, and the inner diameter Du of the low pressure side end of the connecting pipe is at least 5 mm smaller than the height H of the lower bearing.
- the low pressure cylinder further includes a refrigerant inlet tube through which low pressure refrigerant is sucked, and an inner diameter of the refrigerant inlet tube and an inner diameter of the low pressure side end portion of the connection pipe have substantially the same size.
- a rotary two stage compressor Provides a rotary two stage compressor.
- the injection pipe provides a rotary two-stage compressor, characterized in that connected to the intermediate portion having an inner diameter larger than both ends of the connection pipe.
- a rotary two-stage compressor characterized in that the injection pipe is connected closer to the lower pressure end than to the high pressure end.
- the rotary shaft includes a low pressure eccentric portion at a position eccentric with respect to the center of the rotary shaft, the low pressure eccentric portion includes a contact portion in contact with the inner circumferential surface of the low pressure roller and a non-contact portion not in contact with the inner circumferential surface of the low pressure roller,
- a rotary two-stage compressor characterized in that the height of the contact portion of the eccentric portion has a length of 70% or less with respect to the height of the low pressure roller.
- the rotating shaft includes a high pressure eccentric portion at a position eccentric with respect to the center of the rotating shaft, the high pressure eccentric portion is provided with a contact portion in contact with the inner circumferential surface of the high pressure roller and a non-contact portion not in contact with the inner circumferential surface of the high pressure roller,
- the height of the contact portion of the eccentric portion provides a rotary two-stage compressor, characterized in that it has a length of at least 70% of the height of the high pressure roller.
- a rotary two-stage compressor characterized in that the sum of the mass of the low pressure roller and the low pressure eccentric portion and the sum of the mass of the high pressure roller and the high pressure eccentric portion are the same.
- the stroke volume is different, thereby reducing the overcompression loss, thereby improving the freezing capacity (COP),
- the rotary two-stage compressor provided by the present invention increases the inner diameter of the intermediate portion of the connecting pipe for guiding the refrigerant compressed in the low pressure compression assembly to the high pressure compression assembly, and is discharged from the low pressure compression assembly by the increased volume of the connection pipe to obtain a high pressure.
- the pulsation of the refrigerant can be reduced in the process of being sucked into the compression assembly.
- the rotary two-stage compressor provided by the present invention may increase the inner diameter of the injection pipe connected to the connecting pipe as the inner diameter of the intermediate portion of the connecting pipe increases, and may increase the amount of gas refrigerant injected through the injection pipe. Can improve the freezing capacity (COP).
- the rotary two-stage compressor provided by the present invention is to ensure the reliability of the compressor to improve the performance of the compressor at the same time to ensure that the inner diameter of both ends of the connecting pipe has a predetermined range with respect to the height of the lower bearing or high pressure cylinder. Can be.
- FIG. 1 is a view showing an example of a conventional rotary two-stage compressor
- FIG. 2 is a view showing an example of a conventional rotary twin compressor
- FIG. 3 is a schematic diagram showing an example of a cycle including a rotary two-stage compressor
- FIG. 4 illustrates a rotary two stage compressor according to one embodiment of the present invention
- FIG. 6 shows a low pressure cylinder, a high pressure cylinder, a lower bearing and a connecting pipe according to an embodiment of the present invention
- FIG. 7 is a view showing a connection pipe provided in a rotary two-stage compressor according to an embodiment of the present invention.
- FIG. 9 is a graph showing a change in the suction flow rate of the refrigerant and the injection amount of the gas refrigerant through the injection pipe according to the expansion of the inner diameter of the intermediate portion of the connecting pipe of the present invention.
- FIG. 3 is a schematic diagram illustrating an example of a refrigeration cycle configured by a rotary two-stage compressor.
- the heating cycle includes components such as rotary two stage compressor 100, condenser 300, evaporator 400, phase separator 500, and four-way valve 600.
- the condenser 300 constitutes an indoor unit
- the compressor 100, the evaporator 400, and the phase separator 500 constitute an outdoor unit.
- the refrigerant compressed by the compressor 100 is introduced into the condenser 300 of the indoor unit through the four-way valve 600, and the compressed refrigerant gas is condensed by exchanging heat with the surroundings.
- the condensed refrigerant passes through the expansion valve to low pressure.
- the refrigerant passing through the expansion valve is separated into gas and liquid in the phase separator 500, and the liquid flows into the evaporator 400.
- the liquid is evaporated by heat exchange in the evaporator 400 and flows into the accumulator 200 in a gas state, and flows into the low pressure compression assembly (not shown) through the refrigerant inlet pipe 151 of the compressor 100 in the accumulator 200. do.
- the gas separated from the phase separator 500 is introduced into the compressor 100 through the injection pipe 153.
- the medium pressure refrigerant compressed by the low pressure compression assembly of the compressor 100 and the refrigerant introduced through the injection tube 153 are introduced into the high pressure compression assembly (not shown) of the compressor 100 and compressed to high pressure.
- the discharge pipe 152 is discharged to the outside of the compressor 100 again.
- Rotary two-stage compressor 100 according to an embodiment of the present invention, the lower pressure compression assembly 120, the intermediate plate 140, the high pressure compression assembly 130 and the electric motor 110 from the bottom in the sealed container 101 It includes. In addition, it includes a refrigerant inlet pipe 151 penetrating through the sealed container 101 and connected to the accumulator 200 and a refrigerant discharge pipe 152 for discharging the compressed refrigerant to the outside of the sealed container.
- the motor 110 includes a stator 111, a rotor 112, and a rotation shaft 113.
- the stator 111 includes a lamination of a ring-shaped electrical steel sheet and a coil wound on the lamination.
- the rotor 112 also has a lamination in which an electronic steel sheet is laminated.
- the rotating shaft 113 penetrates the center of the rotor 112 and is fixed to the rotor 112. When a current is applied to the motor 110, the rotor 112 rotates by the mutual electromagnetic force between the stator 111 and the rotor 112, and the rotating shaft 113 fixed to the rotor 112 also rotates with the rotor 112. Rotate together.
- the rotating shaft 113 extends from the rotor 112 to the vicinity of the bottom surface of the sealed container 101 so as to penetrate the center portion of the low pressure compression assembly 120, the intermediate plate 140, and the high pressure compression assembly 130.
- the low pressure compression assembly 120 and the high pressure compression assembly 130 are stacked in the order of the low pressure compression assembly 120-the middle plate 140-the high pressure compression assembly 130 from the bottom with the intermediate plate 140 interposed therebetween.
- the high pressure compression assembly 120, the middle plate 140, and the high pressure compression assembly 130 may be stacked in order from the bottom.
- the lower bearing and the upper bearing 161 and the upper bearing 162 are respectively installed It helps the rotation of the rotary shaft 113, and supports the load of each component of the two-stage compression assembly stacked vertically.
- the upper bearing 162 is welded to the sealed container 101 three-point, supports the load of the two-stage compression assembly, and is fixed to the sealed container 101.
- the low pressure compression assembly 120 is connected to the refrigerant inlet pipe 151 introduced through the sealed container 101 from the outside.
- a lower bearing 161 is positioned below the low pressure compression assembly 120.
- the intermediate pressure chamber Pm is formed in the lower bearing 161.
- the intermediate pressure chamber Pm is a space in which the refrigerant compressed in the low pressure compression assembly 120 is discharged, and is a space in which the refrigerant is temporarily stored before the refrigerant is introduced into the high pressure compression assembly 130, from the low pressure compression assembly 120.
- the high pressure compression assembly 130 serves as a buffer space on the flow path through which the refrigerant flows.
- the refrigerant compressed in the low pressure compression assembly 120 and the pressure increased to the intermediate pressure is discharged into the intermediate pressure chamber Pm formed in the lower bearing 161 and then sucked into the high pressure compression assembly 130 through the connection pipe 180.
- the high pressure compression assembly 130 the refrigerant is secondarily compressed, the pressure is increased to high pressure, and then discharged from the high pressure compression assembly 130.
- the high pressure refrigerant is discharged into the discharge space between the upper bearing 162 located above the high pressure compression assembly 130 and the discharge cover 163 located above the upper bearing 162, and then the discharge cover 163. Discharge into the sealed container 101 through the discharge port (not shown) formed in the.
- the refrigerant discharged into the sealed container 101 through the discharge port (not shown) is discharged to the outside through the refrigerant discharge pipe 152 located above the sealed container 101.
- the low pressure compression assembly 120 includes a low pressure cylinder 121, a low pressure roller 123, a low pressure vane 124, a low pressure elastic member 125, and a low pressure inlet hole 126.
- the rotating shaft 113 passes through the center of the low pressure cylinder 121, the low pressure roller 123 is rotatably coupled to the low pressure eccentric portion 113a which is integrally formed on the rotating shaft 113, the low pressure roller 123 is the rotating shaft In accordance with the rotation of the 113 is rotated while rolling along the inner diameter of the low pressure cylinder 121.
- the low pressure inlet hole 126 and the intermediate pressure discharge hole 127 are formed at both sides of the low pressure vane 124.
- the space in the low pressure cylinder 121 is partitioned by the low pressure vane 124 and the low pressure roller 123, and the refrigerant before and after compression coexists in the low pressure cylinder 121.
- the portion including the low pressure refrigerant inlet hole 126 is the low pressure refrigerant inlet (S l ), the middle portion containing the intermediate pressure discharge hole 127 It is called a pressurized refrigerant discharge part D m .
- the low pressure elastic member 125 is a means for applying a force to the low pressure vane 124 so that the low pressure vane 124 maintains contact with the low pressure roller 123.
- the vane hole 124h formed in the low pressure cylinder 121 is formed to penetrate the low pressure cylinder 121 laterally so that the low pressure vane 124 can be located.
- the movement of the low pressure vane 124 is guided through the vane hole 124h, and the low pressure elastic member 125 for applying a force to the low pressure vane 124 penetrates the low pressure cylinder 121 through the vane hole 124h. It extends to the closed container 101.
- One end of the low pressure elastic member 125 is in contact with the low pressure vane 124, the other end is in contact with the closed container 101, so that the low pressure vane 124 maintains contact with the low pressure roller 123.
- the low pressure eccentric portion 113a rotates eccentrically about the center of the rotation shaft 113 by the rotation of the rotary shaft 113, and the low pressure roller 123 moves the low pressure cylinder 121 according to the rotation of the low pressure eccentric portion 113a. he rolls along, while increasing the volume of the low-pressure inlet (S l) since the low-pressure inlet (S l) a low pressure, the refrigerant flows through the low pressure inlet hole 126.
- the intermediate pressure discharge portion (D m) the volume is filled with the refrigerant in the intermediate pressure discharge portion (D m) compression, it loses of, and is discharged through the intermediate pressure discharge holes (127).
- the low pressure eccentric part 122 and the low pressure roller 123 rotate, the volume of the low pressure inlet part S 1 and the intermediate pressure discharge part D m continuously changes, and discharges the compressed refrigerant every one revolution.
- the refrigerant compressed in the low pressure compression assembly 120 is sucked into the high pressure compression assembly 130 through the intermediate pressure chamber Pm formed in the lower bearing 161 and the connecting pipe 180, and low pressure compression in the high pressure compression assembly 130.
- the refrigerant is compressed and discharged into the sealed container 101 in the same process as that of the refrigerant. That is, the medium pressure refrigerant sucked through the high pressure inflow hole 136 is compressed by the high pressure roller 133 which is eccentrically rotated by the high pressure eccentric portion 113b in the high pressure cylinder 131.
- FIG. 6 is a view illustrating a low pressure cylinder, a high pressure cylinder, a lower bearing, and a connecting pipe according to an embodiment of the present invention.
- the low pressure cylinder 121 and the high pressure cylinder 131 should be fixed to the inner surface of the sealed container 101, it is preferable to have an outer diameter corresponding to the inner diameter of the sealed container 101. Therefore, the outer diameters of the low pressure cylinder 121 and the high pressure cylinder 131 are almost the same. In addition, the inner diameters of the low pressure cylinder 121 and the high pressure cylinder 131 are almost the same.
- the low pressure roller 123 and the high pressure roller 133 are eccentrically rotated by the low pressure eccentric portion 113a and the high pressure eccentric portion 113b of the rotating shaft 113, respectively, and the inner diameters of the low pressure cylinder 121 and the high pressure cylinder 131 are changed. Thus it rotates and compresses the refrigerant.
- the weight of the low pressure roller 123, the high pressure roller 133, the low pressure eccentric portion 113a and the high pressure eccentric portion 113b is biased to one side to prevent the vibration and noise generated in the closed container 101 while rotating
- the low pressure roller 123-low pressure eccentric portion 113a and the high pressure roller 133-high pressure eccentric portion 113b are generally positioned at 180 ° intervals from each other.
- the RPM of the low pressure roller 123-low pressure eccentric part 113a and the RPM of the high pressure roller 133-high pressure eccentric part 113b are the same. Therefore, when the sum of the masses of the low pressure roller 123 and the low pressure eccentric part 113a is equal to the sum of the masses of the high pressure roller 133 and the high pressure eccentric part 113b, the low pressure roller 123 and the low pressure eccentric part ( The centrifugal force acting on 113a) and the centrifugal force acting on the high pressure roller 133 and the high pressure eccentric portion 113b are approximately equal to the outer diameter of the low pressure roller 123 and the outer diameter of the high pressure roller 133, that is, the inner diameter of the low pressure cylinder 121.
- the compression space formed in the low pressure cylinder 121 The volume (stroke volume) and the stroke volume formed in the high pressure cylinder 131 can be regarded as being proportional to the height of the low pressure cylinder 121 and the high pressure cylinder 131.
- the stroke volume required for the high pressure compression assembly 130 is required for the low pressure compression assembly. It is small compared to the administrative volume.
- the medium pressure gas refrigerant separated in the phase separator 500 see FIG. 3 is further introduced, so that the mass or moles of the refrigerant compressed in one rotation is compressed at high pressure.
- the stroke volume is larger in low pressure compression assembly 120.
- the ratio H2 / H1 of the height H1 of the low pressure cylinder 121 and the height H2 of the high pressure cylinder 131 is determined by the stroke volume of the low pressure compression assembly 120 and the high pressure compression assembly 130. It has a value nearly identical to the ratio V2 / V1.
- the height of the low pressure cylinder 121 and the high pressure cylinder 131 are the same, but by changing the inner diameter it may be adjusted differently the volume (administrative volume) of the compression space.
- the outer diameters of the low pressure cylinder 121 and the high pressure cylinder 131 should be about the same as the inner diameter of the sealed container 101. Therefore, since the size between the outer diameter and the inner diameter of the high pressure cylinder 131 increases, the weight of the high pressure cylinder 131 increases, and the manufacturing cost increases, so that the inside of the low pressure cylinder 121 and the high pressure cylinder 131 are increased. It is advantageous in terms of manufacturing cost, weight reduction, etc. to make the outer diameter the same and the height different from the stroke volume.
- the heights of the low pressure roller 123 and the high pressure roller 133 correspond to the height of the low pressure cylinder 121 and the height of the high pressure cylinder 131, respectively.
- the centrifugal force applied by the low pressure roller 123 and the low pressure eccentric part 113a and the centrifugal force applied to the high pressure roller 133 and the high pressure eccentric part 113b are the inner diameter and the angular velocity of the low pressure cylinder 121 and the high pressure cylinder 131.
- the sum of the masses of the low pressure roller 123 and the low pressure eccentric portion 113a and the mass of the high pressure cylinder 133 and the high pressure eccentric portion 113b become another variable.
- the low pressure eccentric part 113a and the high pressure eccentric part 113b respectively include the non-contact part which does not contact the contact part which directly contacts the low pressure roller 123 and the high pressure roller 133, respectively. That is, the whole of the low pressure eccentric portion 113a and the high pressure eccentric portion 113b does not contact the low pressure roller 123 and the high pressure roller 133, respectively, but only a part of the low pressure part by reducing its size, By reducing the mass of the core portion 113a and the high-pressure eccentric portion 113b, it is possible to reduce the load generated for the rotation of the eccentric portions 113a and 113b instead of the load generated by the compression of the refrigerant when the motor is driven.
- the centrifugal force generated by the low pressure eccentric portion 113a and the high pressure eccentric portion 113b are generated.
- vibration and noise generated when the compressor is driven can be reduced.
- the compressor is provided with a connecting pipe 180, both ends of which are inserted into the lower bearing 161 and the high pressure cylinder 131, respectively, to guide the refrigerant compressed by the low pressure compression assembly 120 to the high pressure compression assembly 130.
- the connection pipe 180 guides the medium pressure refrigerant discharged from the low pressure compression assembly 120 to the high pressure compression assembly 130 and serves to reduce pulsation of the refrigerant. Pulsation of the coolant occurs because the coolant is discontinuously discharged from the low pressure compression assembly 120.
- the low pressure compression assembly 120 and the high pressure compression assembly 130 respectively discharge the refrigerant until the discharge valve (not shown) is opened and closed again at a predetermined pressure or more, and the opening of the discharge valve (not shown) is performed in one stroke ( Once per 1 revolution).
- the volume of the inlet (S 1 : see FIG. 5) increases in the low pressure cylinder 121 and the high pressure cylinder 131, a negative pressure is formed in the inlet S 1 and the low pressure compression assembly 120 and the high pressure compression. Intake of the refrigerant into the assembly 130 occurs.
- the volume of the inlet S 1 is continuously increased as the rollers 123 and 133 roll along the inner diameters of the cylinders 121 and 131, the volume of the refrigerant to the low pressure compression assembly 120 and the high pressure compression assembly 130 is increased. Inhalation also occurs continuously.
- the refrigerant sucked into the low pressure compression assembly 120 is a refrigerant stored in the accumulator 200, the pulsation is not largely a problem when the refrigerant is sucked into the low pressure compression assembly 120.
- the refrigerant sucked into the high pressure compression assembly 130 is the refrigerant compressed primarily in the low pressure compression assembly 120, the refrigerant may be discharged from the low pressure compression assembly 120 to be the high pressure compression assembly 130. Pulsation due to discontinuous discharge of refrigerant when discharged from the low pressure compression assembly 120 becomes a problem.
- the refrigerant discharged from the low pressure compression assembly 120 is temporarily stored in the intermediate pressure chamber Pm formed in the lower bearing 161 and reduces the pulsation to some extent.
- the pulsation of the refrigerant discharged from the low pressure compression assembly 120 can be effectively reduced.
- the medium pressure chamber formed in the lower bearing 161 There is also a limit to increasing the volume of Pm). That is, in order to increase the volume of the intermediate pressure chamber Pm, the length of the lower bearing 161 or the inner and outer diameters of the lower bearing 161 should be increased, but the increase in the length or the inner and outer diameters of the lower bearing 161 increases the length or diameter of the sealed container.
- the size of the compressor itself is unnecessarily large due to factors independent of the compression capacity, which is inefficient in terms of space utilization.
- the rotary two-stage compressor of the present invention increases the inner diameter of the connecting pipe 180 to connect The volume of the pipe 180 is increased, and the space inside the connecting pipe 180 can serve as a damping space to reduce pulsation of the medium pressure refrigerant.
- the compression capacities of the low pressure compression assembly 120 and the high pressure compression assembly 130 are predetermined according to the capacity of the compressor 100, the heights of the low pressure cylinder 121 and the high pressure cylinder 131 are also predetermined.
- the size of the lower bearing 161 is also determined to a predetermined size.
- connection pipe 180 may not be increased regardless of the height of the low pressure cylinder 121 and the high pressure cylinder 131. Therefore, the connecting pipe 180 of the rotary two-stage compressor of the present invention has both ends 181 and 182 having inner diameters enough to be inserted into the lower bearing 161 and the high pressure cylinder 131, respectively, An intermediate portion 183 having an inner diameter greater than the ends 181, 182. Therefore, the connecting pipe 180 may increase a volume that may be utilized as a space for reducing pulsation of the medium pressure refrigerant regardless of the height of the low pressure cylinder 121, the high pressure cylinder 131, and the lower bearing 161.
- the inner diameters of both ends 181 and 182 have sufficient thicknesses around the intermediate pressure communication hole 161a and the high pressure inlet hole 136 of the lower bearing 161 and the high pressure cylinder 131, respectively, to sufficiently operate the reliability. At the same time, it should be determined within a range capable of reducing the pulsation of the refrigerant compressed to medium pressure by increasing the sizes of the inner diameters 181 and 182 at both ends.
- both ends 181 and 182 of the connecting pipe 180 should have sizes of less than a predetermined ratio with respect to the height of the lower bearing 161 and the high pressure cylinder 131 into which the inner diameters of the ends 181 and 182 are inserted, respectively. do.
- the inner diameter Du of both ends 181 and 182 preferably has a value between 0.4 < Du / H < 0.85 for the height H of the lower bearing 161 and the high pressure cylinder 131 to be inserted, respectively. If the value of 0.4 > Du / H, the middle portion 183 when the coolant flows from the lower bearing 161 into the connecting pipe 180 is too small because the inner diameter Du of both ends 181 and 182 is too small.
- the capacity of the compressor 100 is small and the height of the lower bearing 161 or the high pressure cylinder 131 is low, at least Du < H-5 (mm), that is, the lower bearing 161 or the high pressure cylinder 131 It is preferable that the inner diameters of the both ends 181 and 182 are at least 5 mm or smaller than the height.
- the portion where the injection pipe 190 is connected to the connection pipe 180 is preferably an intermediate portion 183 having a large inner diameter.
- the low pressure inflow hole 126 formed in the low pressure cylinder 121 and the intermediate pressure communication hole 161 a formed in the lower bearing 161 may have substantially the same size. That is, the inner diameter of the refrigerant inlet pipe 151 inserted into the low pressure inlet hole 126 and the inner diameter of the low pressure side end portion 181 of the connection pipe 180 are preferably approximately the same size. In this case, the formation of the intermediate pressure communication hole 161a and the low pressure inlet hole 126 and the connection of the refrigerant inlet pipe 151 and the connection of the low pressure side end 181 of the connection pipe 180 can be managed in the same way. The manufacturing process and manufacturing cost can be reduced.
- FIG. 7 is a view showing a connecting pipe provided in a rotary two-stage compressor according to an embodiment of the present invention
- Figure 8 is a graph showing the COP improvement according to the expansion of the inner diameter of the intermediate portion of the connecting pipe of the present invention
- Figure 9 Is a graph showing a change in the suction flow rate of the refrigerant and the injection amount of the gas refrigerant through the injection pipe according to the expansion of the inner diameter of the intermediate portion of the connecting pipe of the present invention.
- D1 is an inner diameter of the middle portion 183 of the connecting pipe 180
- D2 is an inner diameter of the high pressure side end 182 connected to the high pressure cylinder 131
- D3 is a lower bearing 161.
- the inner diameter of the low pressure side end 181 to be connected, D4, represents the inner diameter of the injection pipe 190.
- the middle portion 183 according to the present invention when the COP of the compressor is 100%.
- the size of the inner diameter (D1) of the inner diameter (D3, D2) of the both ends (181,182) is large, the COP is improved by 105% to 5%.
- the flow rate of the refrigerant flowing in the connection pipe 180 may be viewed as the flow rate of the refrigerant sucked into the high pressure compression assembly 130, the amount of the refrigerant compressed in the high pressure compression assembly 130 increases, and the COP is improved. That means improved freezing capacity.
- the increased volume of the connection pipe 180 serves as a damper to reduce the pressure pulsation, and also serves to reduce the overcompression loss in the low pressure compression assembly 120. That is, the pressure pulsation can be reduced, the overcompression loss can be reduced to improve vibration and noise, and the performance of the compressor can be improved.
Abstract
Description
Claims (13)
- 밀폐 용기;밀폐 용기 내에 구비되며, 회전력을 전달하는 회전축;회전축의 중심에 대해 편심되게 회전하는 저압 롤러, 저압 롤러가 수용되는 저압 실린더 및 저압 실린더 내부 공간을 구획하는 저압 베인을 구비하는 저압 압축 어셈블리;회전축의 중심에 대해 편심되게 회전하는 고압 롤러, 고압 롤러가 수용되는 고압 실린더 및 고압 실린더 내부 공간을 구획하는 고압 베인을 구비하는 고압 압축 어셈블리;저압 압축 어셈블리에서 압축된 냉매가 고압 압축 어셈블리로 유입되도록 유로를 제공하는 연결 파이프; 및연결 파이프에 연결되는 인젝션 파이프;를 포함하며,저압 실린더의 행정 체적(V1)에 대한 고압 실린더의 행정 체적(V2) 비가0.43 < V2 / V2 < 0.82의 관계식을 만족하는 것을 특징으로 하는 로터리식 2단 압축기.
- 제1항에 있어서,연결 파이프의 중간부의 내경이 연결 파이프의 양 단부보다 큰 것을 특징으로 하는 로터리식 2단 압축기.
- 제2항에 있어서,저압 압축 어셈블리에서 압축된 냉매가 토출되어 일시적으로 저장되는 중간압실;을 더 포함하고,연결 파이프의 일 단부는 중간압실에 연결되고, 타 단부는 고압 실린더에 연결되는 것을 특징으로 하는 로터리식 2단 압축기.
- 제3항에 있어서,연결 파이프의 고압측 단부의 내경(Du)은 고압 실린더의 높이(H)에 대해,0.4 < Du/H < 0.85의 관계식을 만족하는 것을 특징으로 하는 로터리식 2단 압축기.
- 제3항에 있어서,연결 파이프의 고압측 단부의 내경(Du)은 고압 실린더의 높이(H)보다 적어도 5mm 작은 것을 특징으로 하는 로터리식 2단 압축기.
- 제3항에 있어서,중간압실은 하부 베어링 내에 형성되며,연결 파이프의 저압측 단부의 내경(Du)은 하부 베어링의 높이(H)에 대해,0.4 < Du/H < 0.85의 관계식을 만족하는 것을 특징으로 하는 로터리식 2단 압축기.
- 제3항에 있어서,중간압실은 하부 베어링 내에 형성되며,연결 파이프의 저압측 단부의 내경(Du)은 하부 베어링의 높이(H)보다 적어도 5mm 작은 것을 특징으로 하는 로터리식 2단 압축기.
- 제2항에 있어서,저압 실린더는 저압의 냉매가 흡입되는 냉매 유입관을 더 포함하며,냉매 유입관의 내경과 연결 파이프의 저압측 단부의 내경은 대략 같은 크기를 가지는 것을 특징으로 하는 로터리식 2단 압축기.
- 제2항에 있어서,인젝션 파이프는 연결 파이프의 양단부보다 내경이 큰 중간부에 연결되는 것을 특징으로 하는 로터리식 2단 압축기.
- 제9항에 있어서,인젝션 파이프는 고압측 단부보다 저압측 단부에 더 근접한 곳에 연결되는 것을 특징으로 하는 로터리식 2단 압축기.
- 제1항 내지 제10항 중 어느 한 항에 있어서,회전축은 회전축의 중심에 대해 편심된 위치에 저압 편심부를 구비하며,저압 편심부는 저압 롤러의 내주면와 맞닿는 접촉부 및 저압 롤러의 내주면과 맞닿지 않는 비접촉부를 구비하고,저압 편심부의 접촉부의 높이는 저압 롤러의 높이에 대해 70% 이하의 길이를 가지는 것을 특징으로 하는 로터리식 2단 압축기.
- 제1항 내지 제10항 중 어느 한 항에 있어서,회전축은 회전축의 중심에 대해 편심된 위치에 고압 편심부를 구비하며,고압 편심부는 고압 롤러의 내주면와 맞닿는 접촉부 및 고압 롤러의 내주면과 맞닿지 않는 비접촉부를 구비하고,고압 편심부의 접촉부의 높이는 고압 롤러의 높이에 대해 70% 이상의 길이를 가지는 것을 특징으로 하는 로터리식 2단 압축기.
- 제1항 내지 제13항에 있어서,저압 롤러 및 저압 편심부의 질량 합과 고압 롤러 및 고압 편심부의 질량 합은 서로 같은 것을 특징으로 하는 로터리식 2단 압축기.
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US13/063,351 US8807973B2 (en) | 2009-04-09 | 2010-04-07 | Rotary-type 2-stage compressor |
CN201080002464.6A CN102138004B (zh) | 2009-04-09 | 2010-04-07 | 旋转式二级压缩机 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR10-2009-0031015 | 2009-04-09 | ||
KR1020090031015A KR101528645B1 (ko) | 2009-04-09 | 2009-04-09 | 로터리식 2단 압축기 |
Publications (2)
Publication Number | Publication Date |
---|---|
WO2010117214A2 true WO2010117214A2 (ko) | 2010-10-14 |
WO2010117214A3 WO2010117214A3 (ko) | 2011-01-20 |
Family
ID=42936726
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/KR2010/002145 WO2010117214A2 (ko) | 2009-04-09 | 2010-04-07 | 로터리식 2단 압축기 |
Country Status (4)
Country | Link |
---|---|
US (1) | US8807973B2 (ko) |
KR (1) | KR101528645B1 (ko) |
CN (1) | CN102138004B (ko) |
WO (1) | WO2010117214A2 (ko) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3312424A1 (en) * | 2016-10-19 | 2018-04-25 | Mitsubishi Heavy Industries Thermal Systems, Ltd. | Sealed rotary compressor |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR101981096B1 (ko) * | 2012-10-12 | 2019-05-22 | 엘지전자 주식회사 | 밀폐형 압축기 |
US9816506B2 (en) | 2013-07-31 | 2017-11-14 | Trane International Inc. | Intermediate oil separator for improved performance in a scroll compressor |
CN104675438A (zh) * | 2014-01-22 | 2015-06-03 | 摩尔动力(北京)技术股份有限公司 | 径向多级流体机构及包括其的装置 |
CN104727934A (zh) * | 2014-02-02 | 2015-06-24 | 摩尔动力(北京)技术股份有限公司 | 径向多级防窜流流体机构及包括其的装置 |
CN104895615A (zh) * | 2014-05-16 | 2015-09-09 | 摩尔动力(北京)技术股份有限公司 | 缸体流体机构及包括其的装置 |
CN105840500A (zh) * | 2015-04-02 | 2016-08-10 | 熵零股份有限公司 | 一种三缸共轴流体机构 |
CN106704189A (zh) * | 2015-08-10 | 2017-05-24 | 珠海格力节能环保制冷技术研究中心有限公司 | 压缩机和换热系统 |
CN105466060A (zh) * | 2015-12-28 | 2016-04-06 | 珠海格力电器股份有限公司 | 一种可变容双级压缩系统及其控制方法 |
CN108087273B (zh) * | 2017-11-30 | 2020-02-07 | 珠海格力电器股份有限公司 | 压缩机及具有其的空调器 |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20020159904A1 (en) * | 2000-03-15 | 2002-10-31 | Toshiyuki Ebara | Double-cylinder two-stage compression rotary compressor |
JP2006029085A (ja) * | 2004-07-12 | 2006-02-02 | Hitachi Home & Life Solutions Inc | 空気調和機及びそれに用いられるロータリ圧縮機 |
JP2008240667A (ja) * | 2007-03-28 | 2008-10-09 | Fujitsu General Ltd | ロータリ圧縮機 |
JP2008248865A (ja) * | 2007-03-30 | 2008-10-16 | Fujitsu General Ltd | インジェクション対応2段圧縮ロータリ圧縮機およびヒートポンプシステム |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH05187374A (ja) * | 1992-01-13 | 1993-07-27 | Sanyo Electric Co Ltd | 密閉型圧縮機 |
KR100224652B1 (ko) * | 1992-06-30 | 1999-10-15 | 윤종용 | 반도체장치의 제조방법 |
KR100556970B1 (ko) * | 2003-12-19 | 2006-03-03 | 엘지전자 주식회사 | 회전식 트윈압축기의 토출장치 |
JP2006152931A (ja) * | 2004-11-30 | 2006-06-15 | Hitachi Home & Life Solutions Inc | ロータリ式2段圧縮機 |
-
2009
- 2009-04-09 KR KR1020090031015A patent/KR101528645B1/ko active IP Right Grant
-
2010
- 2010-04-07 CN CN201080002464.6A patent/CN102138004B/zh not_active Expired - Fee Related
- 2010-04-07 WO PCT/KR2010/002145 patent/WO2010117214A2/ko active Application Filing
- 2010-04-07 US US13/063,351 patent/US8807973B2/en not_active Expired - Fee Related
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20020159904A1 (en) * | 2000-03-15 | 2002-10-31 | Toshiyuki Ebara | Double-cylinder two-stage compression rotary compressor |
JP2006029085A (ja) * | 2004-07-12 | 2006-02-02 | Hitachi Home & Life Solutions Inc | 空気調和機及びそれに用いられるロータリ圧縮機 |
JP2008240667A (ja) * | 2007-03-28 | 2008-10-09 | Fujitsu General Ltd | ロータリ圧縮機 |
JP2008248865A (ja) * | 2007-03-30 | 2008-10-16 | Fujitsu General Ltd | インジェクション対応2段圧縮ロータリ圧縮機およびヒートポンプシステム |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3312424A1 (en) * | 2016-10-19 | 2018-04-25 | Mitsubishi Heavy Industries Thermal Systems, Ltd. | Sealed rotary compressor |
Also Published As
Publication number | Publication date |
---|---|
CN102138004A (zh) | 2011-07-27 |
US20110165004A1 (en) | 2011-07-07 |
KR101528645B1 (ko) | 2015-06-15 |
CN102138004B (zh) | 2015-04-01 |
KR20100112486A (ko) | 2010-10-19 |
US8807973B2 (en) | 2014-08-19 |
WO2010117214A3 (ko) | 2011-01-20 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
WO2010117214A2 (ko) | 로터리식 2단 압축기 | |
US8342825B2 (en) | 2 stage rotary compressor | |
US8430656B2 (en) | 2 stage rotary compressor | |
EP1195526A1 (en) | 2-cylinder, 2-stage compression type rotary compressor | |
US8398386B2 (en) | 2 stage rotary compressor | |
KR101681585B1 (ko) | 복식 로터리 압축기 | |
KR101381085B1 (ko) | 로터리식 2단 압축기 | |
WO2008044684A1 (fr) | Moteur de compresseur et compresseur | |
KR101380987B1 (ko) | 로터리식 압축기 | |
KR20090012841A (ko) | 로터리식 2단 압축기 | |
KR101392091B1 (ko) | 로터리식 2단 압축기 | |
KR101324865B1 (ko) | 로터리식 압축기 | |
KR101328229B1 (ko) | 로터리식 압축기 | |
KR101528646B1 (ko) | 로터리식 2단 압축기 | |
CN111608913B (zh) | 压缩机及空调系统 | |
KR101340164B1 (ko) | 로터리식 2단 압축기 | |
KR101268638B1 (ko) | 로터리식 2단 압축기 | |
KR101337082B1 (ko) | 로터리식 압축기 | |
KR101337079B1 (ko) | 로터리식 2단 압축기 | |
KR20090012855A (ko) | 로터리식 2단 압축기 | |
KR20090012861A (ko) | 로터리식 2단 압축기 | |
KR20100112487A (ko) | 로터리식 2단 압축기 | |
KR101322511B1 (ko) | 로터리식 트윈 압축기 | |
KR101268624B1 (ko) | 로터리식 2단 압축기 | |
KR20090012860A (ko) | 로터리식 2단 압축기 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
WWE | Wipo information: entry into national phase |
Ref document number: 201080002464.6 Country of ref document: CN |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 10761875 Country of ref document: EP Kind code of ref document: A2 |
|
WWE | Wipo information: entry into national phase |
Ref document number: 13063351 Country of ref document: US |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 10761875 Country of ref document: EP Kind code of ref document: A2 |