WO2011019114A1 - 압축기 - Google Patents
압축기 Download PDFInfo
- Publication number
- WO2011019114A1 WO2011019114A1 PCT/KR2009/007166 KR2009007166W WO2011019114A1 WO 2011019114 A1 WO2011019114 A1 WO 2011019114A1 KR 2009007166 W KR2009007166 W KR 2009007166W WO 2011019114 A1 WO2011019114 A1 WO 2011019114A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- oil
- vane
- fixed shaft
- oil supply
- eccentric
- 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
- 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
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/02—Arrangements of bearings
-
- 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
- F04C18/32—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 both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
- F04C18/322—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 both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and 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
- 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
- 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
- F04C23/02—Pumps characterised by combination with or adaptation to specific driving engines or motors
-
- 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
- F04C29/0071—Couplings between rotors and input or output shafts acting by interengaging or mating parts, i.e. positive coupling of rotor and shaft
-
- 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
- F04C29/0085—Prime movers
-
- 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
- F04C29/023—Lubricant distribution through a hollow driving shaft
-
- 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
- F04C2230/00—Manufacture
- F04C2230/60—Assembly methods
- F04C2230/603—Centering; Aligning
-
- 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
- F04C2240/10—Stators
-
- 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
- F04C2240/30—Casings or housings
-
- 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
- F04C2240/40—Electric motor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/50—Bearings
- F04C2240/52—Bearings for assemblies with supports on both sides
-
- 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
-
- 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
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/12—Vibration
Definitions
- the present invention relates to a compressor for compressing a refrigerant while rotating while being supported on a bearing while the rotating member is suspended by the fixing member.
- the present invention not only provides structural stabilization but also improves assembly performance and improves lubrication performance.
- the present invention relates to a compressor capable of securing reliability.
- a compressor is a mechanical device that increases power by receiving air from a power generator such as an electric motor or a turbine and compressing air, a refrigerant, or various other working gases, and a home appliance such as a refrigerator and an air conditioner. Or widely used throughout the industry.
- 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.
- the rotary compressor is configured such that the motor portion and the compression mechanism portion are mounted on the drive shaft in a sealed container.
- a roller located around the eccentric portion of the drive shaft is positioned in a cylinder forming a cylindrical compression space, and at least one vane It extends between the compression spaces and partitions the compression space into the suction zone and the compression zone, and the roller is located eccentrically in the compression space.
- the vane is supported by a spring in the groove portion of the cylinder to pressurize the surface of the roller, and by this vane, the compression space is divided into a suction zone and a compression zone as described above.
- the suction shaft gradually grows as the drive shaft rotates, the suction zone or the working fluid is sucked into the suction zone, and the compression zone gradually decreases, thereby compressing the refrigerant or the working fluid therein.
- the height of the compressor is inevitably increased as a whole.
- the weight of the motor portion and the compression mechanism portion are different from each other, not only a difference in inertia force is generated but also an unbalance inevitably occurs on the upper and lower sides of the driving shaft. Therefore, in order to compensate for the imbalance of the motor portion and the compression mechanism portion, the weight member can be added to the relatively small weight, but this causes a result of applying an additional load to the rotating body, which causes a problem of lowering driving efficiency and compression efficiency. .
- the eccentric portion of the drive shaft rotates to continuously slide contact with the inner surface of the stationary cylinder on which the roller is fixed, and also continuously slides with the end surface of the vane on which the roller is fixed.
- This changing rotary compressor is disclosed.
- the rotary compressor disclosed in the Japanese Laid-Open Patent Publication is conventionally provided between the vane and the eccentric portion (piston portion) because the vane is in sliding contact with the outer surface of the eccentric portion (piston portion) which is fixed and supported at the same time by the rotating rotor.
- the rotary compressor disclosed in the Japanese Patent Laid-Open Publications is practically applicable because it does not disclose any possible configuration for the suction and discharge flow paths of the working fluid, the lubricating oil in the compression mechanism part, and the mounting of the bearing member. There is not enough.
- US Patent Publication No. 7,217,110 discloses a rotary compressor in which a fixed shaft and an eccentric part are integrally formed, and a compression space is formed between the outer surface of the roller rotatably positioned in the eccentric and the inner surface of the rotating rotor.
- the rotational force of the rotor has a configuration that is transmitted to the roller through the vane fixed to the upper and lower plates of the rotor that rotates integrally with the rotor, by using the pressure difference in the sealed container and the pressure difference in the compression space, the center of the fixed shaft
- the working fluid and the lubricating oil are introduced into the compression space through the formed longitudinal flow path.
- the rotary compressor disclosed in the US Patent Publication also forms a compression mechanism inside the rotor, it is considered that the problems caused by the motor portion and the compression mechanism portion installed in the height direction in the conventional rotary compressor can be solved.
- the rotor, vanes and rollers since the rotor, vanes and rollers all rotate integrally, there is no difference in relative speed between them, and there is no fear of friction loss due to them.
- the rotary compressor disclosed in the U.S. Patent Publication discloses that one end of the fixed shaft is fixed to the hermetically sealed container, but the other end of the fixed shaft is manufactured to be suspended in the sealed container in a state in which the other end of the fixed shaft is separated from the hermetically sealed container. It is difficult to center, very vulnerable to lateral vibrations due to the inevitable eccentric rotation due to the nature of the rotary compressor, the actual production is quite difficult, or assembly productivity is poor. In addition, since the vanes protrude inwardly from the rotor and the vane grooves are formed in the rollers to guide the movement trajectory of the vanes, the rollers inevitably become large in order to form the vane grooves.
- the lubricating oil may be used by using a pressure difference in a sealed container and a compression space. Since it is configured to circulate with the working fluid by pulling up into the compression space, in this case, inevitably a large amount of lubricating oil is incorporated into the working fluid, and there is a problem in that the lubrication performance can be lowered because the compressor can exit the compressor together with the working fluid.
- an object of the present invention is to provide a compressor that can be easily assembled to center the parts in the sealed container to increase the structural safety.
- an object of the present invention is to provide a compressor that not only reduces the lateral vibration due to eccentric rotation but also is easy to assemble in actual production.
- an object of the present invention is to provide a compressor that can easily lubricate the vanes by allowing the oil stored in the sealed container to be easily introduced into the vane mounting holes equipped with vanes.
- Compressor for solving the above problems is a sealed container in which oil is stored; A stator fixed in a sealed container; A first fixing member including a fixed shaft extending at an upper end of the sealed container and extending inwardly into the sealed container and an eccentric portion formed to be eccentric to the fixed shaft; A second fixing member which is formed to be spaced apart from the lower end of the fixed shaft and is installed to not move below the sealed container; Located between the stator and the first fixing member, the refrigerant can be sucked into the compression space formed therein while rotating about the first fixing member by the rotating electromagnetic field from the stator, and compresses the second fixing member. Rotating member while rotatably supporting; And a lubricating oil passage for guiding the oil stored in the sealed container by using the rotational force of the rotating member to a portion in which the rotating member and the fixing member are bearing.
- the rotating member the rotor is installed between the stator and the holding member to rotate about the holding member by mutual electromagnetic force with the stator, and is laminated on the rotor to rotate with the rotor and the compression space is provided therein
- a vane elastically supported by the cylinder so as to partition the cylinder, the compression space between the eccentric portion and the cylinder into a suction pocket into which the refrigerant is sucked, and a compression pocket through which the refrigerant is compressed and discharged, to rotate together with the cylinder, and to make sliding contact with the outer surface of the eccentric part;
- a vane mounting hole formed in a slot shape on the inner circumferential surface of the cylinder, a vane spring stopper for blocking the vane mounting hole for installing the vane spring to elastically support the vane, and an upper and lower portion of the compression space to be fixed together with the rotating member.
- an upper and lower bearing cover that rotates about the member.
- the rotating member, the cylindrical rotor is rotatably supported on the fixed member so as to rotate about the fixed shaft by the rotating electromagnetic field from the stator, and the eccentric together with the cylindrical rotor by receiving the rotational force of the cylindrical rotor It is divided into a roller which forms a compression space between the cylindrical rotor while rotating about the part, and a suction pocket which transmits rotational force from the cylindrical rotor to the roller and the compression space in which the refrigerant is compressed and discharged.
- a vane mounting hole formed integrally with the roller so as to protrude toward the cylindrical rotor from the outer circumferential surface of the roller and accommodating the vane, and forming upper and lower portions of the compression space to rotate about the fixing member together with the rotating member. It is characterized by consisting of the upper and lower bearing cover.
- the lower bearing cover includes a lower shaft portion surrounding the fixed shaft, and a lower cover portion coupled to the cylinder to form a lower portion of the compression space, the lower end of the lower shaft portion is installed to be immersed in the oil stored in the sealed container,
- the lubricating oil passage is characterized in that it comprises a groove formed on the inner peripheral surface and the outer peripheral surface of the fixed shaft to the lower shaft portion.
- the lubricating oil passage includes a first oil supply passage formed in the axial direction under the fixed shaft, and a second oil supply passage formed in the eccentric portion so as to communicate with the first oil supply passage and the upper surface of the eccentric portion. It is done.
- the present invention further comprises a refrigerant suction passage through the fixed shaft and the eccentric portion connected to the suction pocket of the compression space, the second oil supply passage bypasses the refrigerant suction passage characterized in that it extends to the upper portion of the eccentric portion do.
- the lubricating oil passage includes upper and lower grooves formed on the upper and lower surfaces of the eccentric, respectively, and the upper and lower grooves function as storage grooves for oil for lubrication of the thrust surface between the rotating member and the eccentric. It is characterized by.
- the lubricating oil passage is provided with a first oil storage groove provided at a portion where the eccentric portion and the fixed shaft lower and lower bearing cover abut so as to communicate with the first oil supply passage, and the eccentric portion so as to communicate with the second oil supply passage. And a second oil storage groove provided at a portion where the fixed shaft upper portion and the upper bearing cover are in contact with each other.
- the upper bearing cover includes an upper shaft portion which partially covers the upper end of the fixed shaft, the lubricating oil passage further comprises a groove provided on the inner peripheral surface of the shaft portion of the upper bearing cover to communicate with the second oil storage groove. do.
- the compressor is characterized in that it further comprises an oil supply member which is mounted to the lower portion of the rotating member, and pumps oil into the lubricating oil as the rotating member is rotated.
- the lower bearing cover includes a lower shaft portion surrounding the fixed shaft, and the oil supply member is fixed inside the hollow shaft portion so as to spirally raise oil in accordance with the rotation of the lower shaft portion and the lower shaft portion. It is characterized by consisting of the propeller.
- the compressor communicates a part of the vane mounting port to the inner space of the sealed container so that the oil supply hole to supply the oil in the vane mounting hole; characterized in that it comprises a.
- the compressor includes an oil supply hole for communicating a portion of the vane mounting port to the inner space of the sealed container so that the oil in the inner space is supplied to the vane mounting hole, the oil supply hole, so as to communicate with the vane mounting hole
- the vane spring stopper is formed at a position lower than the oil level of the oil stored in the sealed container, so that the oil can be supplied to the vane mounting hole.
- the vane mounting hole extends to the vane evacuation protrusion formed by protruding from the cylinder outer circumferential surface, and the open space of the vane evacuation protrusion which is not closed by at least one of the upper and lower bearing covers functions as an oil supply hole to the vane mounting hole. Characterized in that.
- the compressor includes an oil supply hole for communicating a portion of the vane mounting port to the inner space of the sealed container so that the oil in the inner space is supplied to the vane mounting hole, by one or more of the upper and lower bearing cover
- the open space of the vane mounting holes that are not closed may function as oil supply holes to the vane mounting holes.
- the compressor according to the present invention configured as described above is assembled to suspend the rotating member to the fixing member, and then the fixing member is fixed to the upper bearing and the rotating member is rotatably supported on the lower bearing, and the upper and lower bearings are sealed. Since the parts are fixed to the container, the parts can be easily assembled and centered in the sealed container, thereby increasing structural safety and assemblability.
- the compressor according to the present invention even if the eccentric portion is eccentric from the axial center of the fixed shaft to protrude in all the radial directions of the fixed shaft to maintain a stationary state, while the cylinder and the rotor rotates about the fixed shaft and the vanes rotate about the eccentric portion As the cylinder, rotor and vanes rotate about each axis, eccentric rotation does not occur.
- the balance weight is adopted to reduce the lateral vibration caused by the eccentric rotation and to reduce the vibration caused by the eccentric rotation. Since it can be omitted, the efficiency can be increased, and the actual production assembly is easy.
- the compressor according to the present invention while the oil stored in the airtight container is supplied through the flow path in communication with the lower bearing cover and the fixing member of the rotating member to lubricate the contact surface with each other, and then the flow path communicated by being pumped by the oil supply member Since the upper bearing cover of the rotating member and the fixing member lubricate the surfaces contacted with each other, the oil can be supplied to parts located above the set height from the oil surface by the oil supply member, and the components lubricated by the oil The friction loss between them can be reduced, thereby increasing not only the compression efficiency but also the operational reliability.
- the compressor according to the present invention even if the vane is elastically supported by the vane spring, or even if the vanes are installed to abut between the bushes, the oil supply hole for communicating the vane mounting hole equipped with the vane and the inner space of the sealed container in which the oil is stored. Since the oil level is maintained higher than the oil supply hole, the oil can be easily introduced into the vane mounting hole to increase the lubrication performance of the vane, and reduce the friction and wear of the vane and its parts, as well as the movement of the vane. This can be done smoothly to increase operational reliability.
- FIG. 1 is a side sectional perspective view showing a first embodiment of a compressor according to the present invention
- FIG. 2 is an exploded perspective view showing a first embodiment of a compressor according to the present invention
- FIG. 3 is a side sectional view showing a first embodiment of a compressor according to the present invention.
- Figure 4 is a plan view showing the vane mounting structure in the first embodiment of the compressor according to the present invention.
- FIG. 5 is a plan view showing an operation cycle of the compression mechanism in the first embodiment of the compressor according to the present invention.
- Figure 6 is a side sectional view showing an example as a lubricant in the first embodiment of the compressor according to the present invention.
- FIG. 7 and 8 are perspective views each showing a lubricating oil passage provided in the lower bearing cover and the upper bearing cover in the first embodiment of the compressor according to the present invention.
- FIG. 9 is a perspective view showing an example of the vane lubrication structure in the first embodiment of the compressor according to the present invention.
- FIG. 10 is a side sectional perspective view showing a second embodiment of a compressor according to the present invention.
- FIG. 11 is an exploded perspective view showing a second embodiment of a compressor according to the present invention.
- FIG. 12 is a side sectional view showing a second embodiment of a compressor according to the present invention.
- FIG. 13 is a plan view showing a vane mounting structure in a second embodiment of a compressor according to the present invention.
- FIG. 14 is a plan view showing the operating cycle of the compression mechanism in the second embodiment of the compressor according to the present invention.
- Figure 15 is a side sectional view showing an example as a lubricating oil in the second embodiment of the compressor according to the present invention.
- 16 is a perspective view showing a lubricating oil passage provided in the fixing member in the second embodiment of the compressor according to the present invention.
- 17 and 18 are perspective views each showing a lubricating oil passage provided in the lower bearing cover and the upper bearing cover in the second embodiment of the compressor according to the present invention.
- 19 is a perspective view showing an example of the vane lubrication structure in the second embodiment of the compressor according to the present invention.
- FIG. 1 to 3 show a first embodiment of a compressor according to the invention.
- the first embodiment of the compressor according to the present invention is a sealed container 110, a stator 120 fixed in the sealed container 110, and a rotating electromagnetic field from the stator 120 as shown in FIGS.
- the rotating member 130 is rotatably installed inside the stator 120 to compress the refrigerant, and the rotating member 130 is installed to hang on the outer circumferential surface thereof, and the upper and lower ends of the fixed shaft 141 are sealed in the container 110.
- Fixed member 140 fixed to not move in the upper portion, the upper bearing 150 for fixing the upper end of the fixed shaft 141 inside the sealed container 110, and the lower end of the fixed shaft 141 and at the same time rotating member 130 includes a lower bearing 160 fixed inside the sealed container 110 so as to be rotatably supported on the upper surface.
- the electric mechanism for providing power through the electrical action comprises a rotor 131 of the rotating member 130, including the stator 120, the compressor mechanism for compressing the refrigerant through the mechanical action rotating member 130 It includes a fixing member 140, including. Therefore, by partially stacking the electric mechanism part and the compression mechanism part in the vertical direction and providing the radial direction, the overall compressor height can be lowered.
- the airtight container 110 has a cylindrical body part 111, upper and lower shells 112 and 113 coupled to the upper and lower parts of the body part 111, and a lower shell to fasten and fix the airtight container 110 to another product.
- 113 is made of a mounting portion 114 provided in the radial direction on the bottom surface, the oil lubricating the rotating member 130 and the fixing member 140 may be stored up to an appropriate height therein.
- a suction tube (not shown) in which the refrigerant is sucked is provided at the center of the upper shell 112 so that the fixed shaft 141 is directly exposed, and a discharge tube capable of discharging the refrigerant at a predetermined position of the upper shell 112 ( 115) is provided, and the inside of the sealed container 110 is determined to be high-pressure or low-pressure depending on whether the inside of the sealed container 110 is filled with a compressed refrigerant or a refrigerant before being compressed, and the suction tube and the discharge tube may be changed accordingly.
- the fixed shaft 141 which is a suction pipe is provided to protrude to the outside of the sealed container (110).
- the fixed shaft 141 does not need to protrude excessively outside the sealed container 110, it is preferable to install a suitable fixed structure outside the sealed container 110 to connect to the external refrigerant pipe.
- the upper shell 112 is provided with a terminal 116 for supplying power to the stator 120.
- the stator 120 is composed of a core and a coil wound around the core, and fixed to the inside of the body portion 111 of the sealed container 110 by shrinkage.
- the core employed in the existing BLDC motor has nine slots along the circumference, whereas in the preferred embodiment of the present invention, the diameter of the stator 120 is relatively large so that the core of the BLDC motor has twelve slots along the circumference. It is composed. As the number of slots of the core increases, the number of turns of the coil increases, so that the height of the core may be lowered in order to generate the electromagnetic force of the stator 120 as in the prior art.
- the rotating member 130 includes a rotor 131, a cylinder 132, a vane 133, a vane spring 134, an upper bearing cover 135, and a lower bearing cover 138.
- the rotor 131 is provided with a plurality of permanent magnets in the axial direction so as to rotate by the rotating electromagnetic field from the stator 120, and is installed to maintain a gap inside the stator 120.
- the cylinder 132 is formed in a cylindrical shape provided with a compression space therein, the inner circumferential surface is provided with a vane mounting hole (132H) formed long in the radial direction so that the vanes 133 and the vane spring 134 can be mounted.
- the rotor 131 and the cylinder 132 are coupled such that the rotor 131 and the cylinder 132 are stacked up and down on the basis of the upper bearing cover 135 so as to rotate integrally.
- the vane 133 is one end is supported on the outer peripheral surface of the eccentric portion 142 to be described below, while the other end is installed to be elastically supported by the vane spring 134 in the vane mounting hole 132H of the cylinder 132, the cylinder
- the compressed space between the 132 and the eccentric portion 142 is divided into a suction pocket (S: shown in FIG. 4) into which the refrigerant is sucked and a compression pocket (D: shown in FIG. 4) into which the refrigerant is compressed and discharged.
- the lubrication structure is applied to the vanes 133 to move smoothly in the eccentric portion 142 and the vane mounting holes 132H of the cylinder 132.
- the upper bearing cover 135 is installed in contact with the fixing member 140 in contact with the journal bearing or the thrust bearing, and is coupled to the rotor 131 and the cylinder 132 so as to be stacked in the vertical direction.
- the outer peripheral portion of the upper surface of the upper bearing cover 135 is formed to be stepped so that the rotor 131 can be fastened, while the rotor 131 is mounted on the stepped portion on the outer peripheral surface of the upper bearing cover 135.
- the bolt is fastened, and the cylinder 132 is bolted to the center of the bottom surface of the upper bearing cover 135.
- the upper bearing cover 135 is provided with a discharge port (not shown) through which the refrigerant compressed in the compression space can be discharged, and a discharge valve 135A installed therein.
- the discharge hole of the upper bearing cover 135 is provided to reduce the dead volume. It is preferably located adjacent to the vane 133.
- the upper bearing cover 135 is coupled to the bottom of the rotor 131 and the upper surface of the cylinder 132, the lower bearing cover 135 is coupled to the bottom of the cylinder 131, a fastening member such as a kind of long bolt Each is fastened by
- the fixed member 140 has a fixed shaft 141 provided in a cylindrical shape and a fixed shaft 141 in all radial directions of the fixed shaft 141 to have a cylindrical shape having a larger diameter than the cylinder of the fixed shaft 141. And an eccentric portion 142 eccentrically formed on the fixed shaft 141 at the same time.
- a lower portion of the fixed shaft 141 is formed with a first oil supply passage 141A through which oil stored in the sealed container 110 can be supplied, while a lower pressure refrigerant can be sucked into the upper portion of the fixed shaft 141. Since the vertical suction passage 141B is formed and the first oil supply passage 141A and the vertical suction passage 141B are formed to be isolated, the oil may be prevented from escaping together with the refrigerant.
- the eccentric portion 142 is formed to extend in all radial directions of the fixed shaft 141, and extends to the outer circumferential surface in the radial direction of the eccentric portion 142 so as to communicate with the vertical suction passage 141B of the fixed shaft 141.
- the horizontal suction passage 142B is provided, and the vane 133 may pass along the horizontal suction passage 142B.
- a supply passage for lubricating oil is formed on the upper and lower surfaces of the eccentric portion 142. Since the outer circumferential surface of the eccentric portion 142 is installed to be in contact with the vane 133, it is preferable that a supply passage of lubricating oil for lubricating between the vane 133 and the eccentric portion 142 is formed.
- the upper and lower bearings 150 and 160 fix the fixed shaft 141 to the airtight container 110 so as not to move and at the same time rotatably support the rotating member 130.
- the upper bearing 150 is fixed to the upper shell 112 of the sealed container 110 by welding, the upper portion of the fixed shaft 141 is fitted. At this time, the upper bearing 150 is formed smaller in the radial direction than the lower bearing 160, in order to prevent interference with the suction pipe 115 or the terminal 116 provided in the upper shell (112).
- the lower bearing 160 is spaced apart from the lower portion of the fixed shaft 141, the shaft portion of the lower bearing cover 136 surrounding the lower portion of the fixed shaft 141 is rotatably supported by the thrust bearing 161,
- the body portion 111 of the sealed container 110 is fixed by shrinkage or three-point welding or the like.
- the upper and lower bearings 150 and 160 are manufactured by press working, but the vanes 133, the upper and lower bearing covers 135 and 136, the fixed shaft 141 and the eccentric portion 142 are all cast from cast iron, It is manufactured by grinding and further machining.
- the upper and lower bearing covers 135, 136 are rotatably installed on the fixing member 130 and the lower bearing 160.
- the upper bearing cover 135 is composed of an upper shaft portion 135a surrounding an upper portion of the fixed shaft 141, and upper cover portions 135b and 135c contacting the upper surface of the eccentric portion 142, and the upper cover portion ( 135b and 135c have a relatively thick thickness to withstand the pressure of the compression space, and a relatively thin thickness so that the cylinder mounting portion 135b is bolted to the bottom surface of the cylinder 132 and the outer peripheral surface of the cylinder mounting portion 135b is stepped.
- the rotor mounting portion 135c is bolted in the state where the rotor 131 is seated on the upper surface.
- the inner circumferential surface of the upper shaft portion (135a) is provided with a journal bearing for journal supporting the upper outer circumferential surface of the fixed shaft (142), the eccentric portion (142) on the bottom surface of the upper cover portion (135b, 135c) or the cylinder coupling portion (135b)
- the thrust bearing which thrust-supports the upper surface is provided.
- the lower bearing cover 136 includes a lower shaft portion 136a surrounding the lower portion of the fixed shaft 141 and a lower cover portion 136b in contact with the bottom surface of the eccentric portion 142.
- the inner circumferential surface of the lower shaft portion 136a is provided with a journal bearing for journal-supporting the lower outer circumferential surface of the fixed shaft 142, and a thrust bearing for thrust supporting the bottom of the eccentric portion 142 is provided on the upper surface of the lower cover portion 136b.
- the lower bearing 160 has a stepped cylindrical bearing portion 160a surrounding the lower shaft portion 136b, and a mounting portion 160b extended in the radial direction of the bearing portion 160a to be welded and fixed inside the sealed container 110.
- the inner circumferential surface of the bearing portion 160a is provided with a journal bearing for journal-supporting the outer circumferential surface of the lower shaft portion 136a, and a thrust bearing for supporting the lower end of the lower axial portion 136a on the stepped bottom surface of the bearing portion 160a. It may be provided, or a separate plate-shaped thrust bearing 161 may be inserted therebetween.
- the bottom surface of the cylinder engaging portion 135b of the upper bearing cover 135 becomes a cylinder.
- 132 is bolted to abut the upper surface and the upper surface of the rotor coupling portion 135c of the upper bearing cover 135 is bolted to abut the bottom surface of the rotor 132, the cover portion of the lower bearing cover 136 ( 136b) is bolted to abut the bottom surface of the cylinder 132.
- the upper shaft portion 135a is supported by the journal bearing on the upper portion of the fixed shaft 141 and the upper cover portions 135b and 135c are supported by the upper surface of the eccentric portion 142 so that the upper bearing cover 135 is fixed to the fixing member ( 140 is rotatably installed, and the lower shaft portion 136a is supported by the journal bearing under the fixed shaft 141, while the lower cover portion 136b is thrust supported on the bottom of the eccentric portion 142.
- 136 is rotatably installed relative to the fixing member 140.
- the lower shaft portion 136a of the lower bearing cover 136 is fitted to the bearing portion 160a of the lower bearing 160, and the lower bearing cover 136 is supported by the bearings in the journal surface or the thrust surface which abut each other. It is rotatably supported with respect to the lower bearing 160.
- Figure 4 is a plan view showing the vane mounting structure in the first embodiment of the compressor according to the present invention.
- the vane evacuation protrusion (132A) protruding on one side of the outer peripheral surface of the cylinder 132 is provided, the vane evacuation protrusion (132A) on the inner / outer peripheral surface of the cylinder 132
- a vane mounting hole 132H penetrated in the radial direction and axially penetrated therein is provided, and a vane spring supporter is provided on the outer circumferential surface of the cylinder 132 to block the vane mounting hole 132H and to support the vane spring 134. 137: shown in FIG. 3). Therefore, one end of the vane 133 is elastically supported by the vane spring 134 in the vane mounting hole 132H, while the other end of the vane 133 is supported on the outer circumferential surface of the eccentric portion 142.
- the vane 133 mounted as described above divides the compression space provided between the cylinder 132 and the eccentric portion 142 into a suction pocket S and a compression pocket D.
- the horizontal suction flow path 142B of the eccentric portion 142 described above is positioned to communicate with the suction pocket S, and the discharge port and discharge valve 135A of the upper bearing cover 135 are positioned to communicate with the compression pocket D.
- the vanes 133 are preferably located close to each other.
- the cylinder 132 connected by the rotor 131 and the upper bearing cover 135 also rotates integrally.
- the vanes 133 are elastically supported by the vane mounting holes 132H of the cylinder 132 and are supported on the outer circumferential surface of the eccentric portion 142.
- the cylinder 132 rotates about the fixed shaft 141, and the vanes ( 133 rotates along the outer circumferential surface of the eccentric portion 142 with respect to the eccentric portion 142. That is, the inner circumferential surface of the cylinder 132 has portions corresponding to each other on the outer circumferential surface of the eccentric portion 142.
- the portions corresponding to each other are inhaled while repeating the process of contacting each time the cylinder 132 rotates once and away from each other.
- the pocket S gradually increases, the refrigerant or working fluid is sucked into the suction pocket S, and the compression pocket D gradually decreases while the refrigerant or working fluid therein is compressed, and then discharged.
- FIG. 5 is a plan view showing an operating cycle of the compression mechanism in the first embodiment of the compressor according to the present invention.
- the compressor configured as described above is installed so that the rotating member 130 is suspended to the fixing member 140, and is rotatably supported by the lower bearing 160 so that the rotating member 130 is provided. Is suspended to the fixing member 140, and the rotating member 130 is supported on the lower bearing 160, that is, the lubrication must be made on the surface, in addition to the rotating member 130 and the fixing member 140 And lubrication is required between the parts which abut each other in the lower bearing 160.
- Figure 6 is a side cross-sectional view showing an example as a lubricant in the first embodiment of the compressor according to the present invention
- Figures 7 and 8 are provided in the lower bearing cover and the upper bearing cover in the first embodiment of the compressor according to the present invention
- the lubricating oil passages shown are respectively perspective views.
- the oil level of the oil stored in the sealed container 110 is at least higher than the lower bearing 160 (shown in FIG. 3) or the lower portion of the lower bearing cover 136. It is preferable to be kept higher than the lowest end of the shaft portion 136a. Accordingly, as described above, the lower shaft portion 136a of the lower bearing cover 136 is accommodated in the bearing portion 160a (shown in FIG. 3) of the lower bearing 160 (shown in FIG. 3), that is, the surfaces contacting each other. The journal face and the thrust face are bearing-supported respectively, and the contact face is submerged in oil so that a separate lubrication flow path may not be provided.
- a lubricating oil passage is provided at a portion where the rotating member 130 (shown in FIG. 1) and the fixing member 140 (shown in FIG. 1) come into contact with each other. It can be divided into upper lubrication flow path.
- the lower lubricating oil passage is configured to supply oil stored in the lower portion of the sealed container 110 to abutting portions of the lower bearing cover 136, the fixed shaft 141, and the eccentric portion 142, and an oil supply member. 170 is configured to pump oil as it rotates together with the rotating member 130 (shown in FIG. 1), and the upper lubricating oil passage includes oil pumped by the oil supply member 170 and the upper bearing cover 135.
- the fixed shaft 141 and the eccentric portion 142 is configured to supply to abutting portions.
- the lower lubricating oil passage has a first oil supply passage 141A, which is a hollow space perpendicular to the lower portion of the fixed shaft 141, and an oil supply hole penetrated in the radial direction below the fixed shaft 141 so as to communicate with the oil supply passage 141A. (Not shown) and the first oil supply groove formed on the outer circumferential surface of the fixed shaft 141 directly below the eccentric portion 142 and the eccentric portion 142 which are in contact with the lower bearing cover 136 so as to communicate with the oil supply hole. , b).
- the first oil supply grooves (a, b) may also be formed in any of the portions in which the lower bearing cover 136, the fixed shaft 141, and the eccentric portion 142 are in contact with each other, but not only relatively thick. It is preferable to form a ring-shaped groove having a side cross-section 'a' on the lower outer circumferential surface of the fixed shaft 141 and the bottom of the eccentric portion 142 that are easy to machine. Of course, the oil surface is preferably formed so that the lower bearing cover 136 is locked. In addition, in order to supply oil to the first oil supply grooves a and b even if the oil does not pass through the first oil supply passage 141A and the oil supply hole, the lower bearing cover 136 of FIG. An inner circumferential surface of the lower shaft portion 136a may be formed with a straight or spiral groove 136g vertical to communicate with the first oil supply grooves a and b.
- the oil supply member 170 is installed in the hollow shaft portion 171 of the cylindrical shaft fitted to the lower shaft portion 136a of the lower bearing cover 136, and is installed inside the hollow shaft portion 171 and the hollow shaft portion 171 by a rotational force. It includes a propeller 172 so that the oil is supplied through the flow path. Therefore, the oil supply member 170 is rotated in the state submerged in the oil, such as the lower bearing cover 136, the oil is raised through the oil supply member 170.
- the upper lubrication structure includes two or more extending to the upper surface of the eccentric portion 142 so as to communicate with the first oil supply passage 141A of the fixed shaft 141 and the first oil supply passage 141A of the fixed shaft 141.
- Upper and eccentric portions of the eccentric portion 142 contacting the upper bearing cover 135 so as to communicate with the second oil supply passage 142A of the eccentric portion 142 and the second oil supply passage 142A of the eccentric portion 142.
- the second oil supply passage (142A) provided in the eccentric portion (142) is the eccentric portion (142) It is preferable to be provided so as not to overlap with the horizontal suction passage (142B: shown in Figure 3) provided in.
- the second oil supply grooves c and d may also be formed at any one of the portions in contact with the upper bearing cover 135, the fixed shaft 141, and the eccentric portion 142, but are not only relatively thick.
- a ring-shaped groove having a side cross-section 'b' on the upper outer circumferential surface of the fixed shaft 141 and the upper surface of the eccentric portion 142 that are easy to machine.
- vertical or straight grooves 135g may be formed on the inner circumferential surface of the upper shaft portion 135a of the upper bearing cover 135 so as to communicate with the second oil supply grooves c and d. have.
- the oil stored in the lower portion of the sealed container 110 is formed with a higher oil level than the oil supply hole, including the lower lower shaft portion 136a of the lower bearing cover 136.
- the first oil supply passage 141A, the oil supply hole of the fixed shaft 141, and the groove 136g of the lower bearing cover 136 are introduced into the first oil supply grooves a and b.
- lubrication is performed between the lower bearing 160 (shown in FIG. 3), and the lower bearing cover 136 supplies the first oil.
- the oil gathered in the grooves a and b and the groove 136g is lubricated between the fixed shaft 141 and the eccentric portion 142 and is rotatably installed.
- the oil is pumped by the oil supply member 170 as the rotating member 130 (shown in Figure 1), this oil is the first oil supply passage (141A), the eccentric portion (141) of the fixed shaft (141)
- the second oil supply passage 142A of 142 the second oil supply grooves c and d flow into the second oil supply grooves c and d, and are further raised through the groove 135g of the upper bearing cover 135.
- the upper bearing cover 135 is lubricated between the fixed shaft 141 and the eccentric portion 142 by the oil collected in the second oil supply grooves (c, d) and the groove (135g) so as to be rotatable at the same time. Is installed.
- FIG. 9 is a perspective view showing an example of the vane lubrication structure in the first embodiment of the compressor according to the present invention.
- a vane evacuation protrusion 132A protruding from the outer circumferential surface of the cylinder 132 is provided, and vane mounting penetrated from the inner circumferential surface of the cylinder 132 to the outer circumferential surface of the vane evacuation protrusion 132A.
- a sphere 132H is provided, and the vane mounting holes 132H extended to the outer circumferential surface of the vane evacuation protrusion 132A to elastically support the vanes 133 to the vane mounting holes 132H by the vane spring 134.
- the vane is provided with a vane spring stopper 137
- the vane spring stopper 137 is provided with an oil supply hole (137h) in communication with the inner space of the sealed container 110 (shown in Figure 1).
- the oil level of the oil is stored in the airtight container 110 (shown in FIG. 1) through the oil supply hole 137h of the vane spring stopper 137. It is preferable to maintain higher than the oil supply hole (137h).
- the oil level of the oil should be kept at least higher than the lowest end of the oil supply hole 137h of the vane spring stopper 137.
- an oil recovery structure is applied in order to maintain an appropriate amount of oil or more in the sealed container 110 (shown in FIG. 1).
- the oil recovery structure of the above embodiment when the compressed refrigerant exiting the discharge port and the discharge valve 135A of the upper bearing cover 135 hits the oil separation plate 180 (shown in FIG. 1) installed directly on the rotor 131.
- the oil is separated from the compressed refrigerant.
- the refrigerant from which the oil is separated passes through the hole 180h (shown in FIG. 3) provided in the oil separation plate 180 (shown in FIG. 1), and the oil separated from the refrigerant is separated from the oil separation plate 180 (see FIG. 1). 1 above the rotor 131 or the upper bearing cover 135, and then to the lower portion of the sealed container 110 (shown in FIG. 1) along the oil return passage between the parts.
- the oil return flow passage may be composed of a gap between the stator 120 (shown in FIG. 1) and the rotor 131, or a jig may be mounted to bolt the cylinder 132 to the upper and lower bearing covers 135 and 136. It may be composed of a series of jig mounting holes (not shown) provided in the cylinder 131 and the upper and lower bearing covers 135 and 136 so as to communicate vertically.
- the lower bearing cover 136 is installed so as not to cover a part of the bottom surface of the vane mounting hole 132H of the cylinder 132, and the oil inside the sealed container 110 (shown in FIG. 1). It is preferable that not only the oil level of the lower bearing cover 136 is maintained but also the lowest end of the vane mounting hole 132H is locked. At this time, since the vane mounting holes 132H are provided in the vane evacuation protrusion 132A protruding from the circular cylinder 132, even if the lower cover portion 136b of the lower bearing cover 136 is formed in a disc shape, the vane evacuation protrusion is formed.
- the upper bearing cover 135 is installed so as not to cover a part of the upper surface of the vane mounting hole 132H of the cylinder 132, and the inside of the sealed container 110 (shown in FIG. 1).
- the oil level is preferably maintained higher than the upper bearing cover 135 as well as the top of the vane fitting 132H is locked.
- 10 to 12 show a second embodiment of a compressor according to the invention.
- the second embodiment of the compressor according to the present invention like the first embodiment, as shown in FIGS. 10 to 12, the sealed container 210, the stator 220 fixed in the sealed container 210, and the stator (
- the rotating member 230 is rotatably installed inside the stator 220 by the rotating electromagnetic field from the 220 and compresses the refrigerant, and the rotating member 230 is installed to hang on the outer circumferential surface, and at the same time, the upper and lower ends of the fixed shaft 241.
- the electric mechanism for providing power through the electrical action includes a rotor 231 of the rotating member 230, including the stator 220, the compressor mechanism for compressing the refrigerant through the mechanical action rotating member 230 It includes a fixing member 240, including. Therefore, by installing the transmission mechanism and the compression mechanism in the radial direction, the overall compressor height can be lowered.
- the airtight container 210 is formed of a body portion 211 and upper and lower shells 212 and 213 in the same manner as the airtight container 210 of the first embodiment, but the high pressure that the inside of the airtight container 210 is filled with a high pressure refrigerant It consists of That is, the fixed shaft 241 is directly exposed to the center of the upper shell 212 as an example of the suction tube in which the refrigerant is sucked, and the discharge tube 214 for discharging the high-pressure refrigerant at one side of the upper shell 212 is provided. A terminal 215 is also provided to supply power to the stator 220. At this time, the fixed shaft 241 does not need to protrude excessively to the outside of the sealed container 210, it is preferable to install a suitable fixed structure to the outside of the sealed container 210 to connect to the external refrigerant pipe.
- stator 220 is configured in the same manner as in the first embodiment, detailed description thereof will be omitted.
- the rotary member 230 includes a cylindrical rotor 231 and 232, a roller 233, a vane 234, a bush 235, an upper bearing cover 236 and a muffler 237, and a lower bearing cover 238.
- the cylindrical rotors 231 and 232 are rotated integrally with the rotor 231 by being located inside the rotor 231 with a plurality of permanent magnets in the axial direction so as to rotate by the rotating electromagnetic field from the stator 220.
- the rotor 231 and the cylinder 232 may be configured separately, but may be combined, but integrally formed in the form of a powder sintered body or a laminate in which iron pieces are laminated. May be
- the roller 233 is cylindrically mounted on the outer circumferential surface of the eccentric portion 242 of the fixing member 240 to be described below, and for this purpose, a lubrication structure is applied between the roller 233 and the eccentric portion 242. It is preferable.
- the roller 233 and the eccentric portion 242 is provided with suction guide flow paths 233A and 242C through which the refrigerant can be sucked, and the roller 233 has a suction port communicating with the suction guide flow paths 233A and 242C ( 233a).
- the vane 234 is integrally provided on the outer circumferential surface of the roller 233 so as to be located at one side of the suction port 233a of the roller 233, and is provided on the inner rotor surface of the cylindrical rotors 231 and 232 or the cylinder 232. It is installed to fit in the vane mounting holes 232H.
- the bush 235 is installed to support both end surfaces of the vanes 234 fitted into the vane mounting holes 232H of the cylindrical rotors 231 and 232.
- a lubrication structure is applied to allow the vanes 234 to move smoothly between the vane mounting holes 232H of the cylindrical rotors 231 and 232 and the bush 235.
- the upper bearing cover 236 and the muffler 237 and the lower bearing cover 238 are coupled to the cylindrical rotors 231 and 232 in the axial direction, between the cylindrical rotors 231 and 232 and the rollers 233 and vanes 234.
- the compression space is formed and installed in contact with the journal bearing or the thrust bearing at a portion in contact with the fixing member 240.
- the upper bearing cover 236 is provided with a discharge port (not shown) through which the refrigerant compressed in the compression space can be discharged and a discharge valve 236A installed therein. It is preferably located adjacent to the vane 233.
- the muffler 337 is coupled to the upper surface of the upper bearing cover 236, and is provided with a discharge chamber for reducing the opening and closing noise of the discharge valve 236A and the flow noise of the high-pressure refrigerant, the discharge chamber is the upper bearing
- the discharge hole (not shown) provided in the cover 236 and the muffler 237 are respectively communicated with.
- the upper bearing cover 236 and the muffler 237 are coupled to the upper surfaces of the cylindrical rotors 231 and 232, and the lower bearing cover 237 is coupled to the lower surfaces of the cylindrical rotors 231 and 232, and the cylindrical rotors 231 and 232. ) Is fastened at once by fastening members such as long bolts.
- the fixed member 240 has a fixed shaft 241 provided in a cylindrical shape and a fixed shaft 241 in all radial directions of the fixed shaft 241 to have a cylindrical shape having a larger diameter than the cylinder of the fixed shaft 241. And an eccentric portion 242 eccentrically formed on the fixed shaft 241 at the same time.
- a lower portion of the fixed shaft 241 is formed with a first oil supply passage 241A through which oil stored in the sealed container 210 can be supplied, while a lower pressure refrigerant can be sucked into the upper portion of the fixed shaft 241. Since the vertical suction passage 241B is formed and the first oil supply passage 241A and the vertical suction passage 241B are formed to be isolated, the oil may be prevented from escaping together with the refrigerant.
- the eccentric portion 242 is formed to extend in all radial directions of the fixed shaft 241, and extends to the outer circumferential surface in the radial direction of the eccentric portion 242 so as to communicate with the vertical suction passage 241B of the fixed shaft 241.
- the horizontal suction passage 242B is provided.
- the roller 233 rotates along the outer circumferential surface of the eccentric portion 242
- the refrigerant is provided because the ring-shaped suction guide flow paths 233A and 242C are provided between the inner circumferential surface of the roller 233 and the outer circumferential surface of the eccentric portion 242.
- the upper and lower bearings 250 and 260 have the same structure as in the first embodiment, and the rotating member 230 is installed to be suspended to the fixing member 240, and then the upper portion of the fixing shaft 241 is the upper bearing 250. ) Is welded and fixed to the upper portion of the sealed container 210 in a state of being fitted, and welded to the lower portion of the sealed container 210 in a state in which the lower bearing cover 238 is rotatably supported by the lower bearing 260.
- the upper bearing cover 236 has an upper shaft portion 236a provided with a journal bearing on an inner circumferential surface surrounding the upper portion of the fixed shaft 241, and an upper cover provided with a thrust bearing on a bottom surface in contact with the upper surface of the eccentric portion 242. Part 236b, but the upper cover portion 236b is bolted to the cylindrical rotor (231,232) on the bottom.
- the lower bearing cover 238 has a lower shaft portion 238a provided with a journal bearing on an inner circumferential surface surrounding the lower portion of the fixed shaft 241, and a lower cover portion provided with a thrust bearing on an upper surface which is in contact with the bottom surface of the eccentric portion 242. 238b).
- the lower bearing 260 is a stepped cylindrical bearing portion 260a surrounding the lower shaft portion 238a and a mounting portion 260b extended in the radial direction of the bearing portion 260a to be welded and fixed inside the sealed container 210.
- the inner circumferential surface of the bearing portion 260a is provided with a journal bearing for journal-supporting the outer circumferential surface of the lower shaft portion 238a, and a thrust bearing for thrust supporting the lower end of the lower shaft portion 238a on the stepped bottom surface of the bearing portion 260a. Or a separate plate-shaped thrust bearing 261 may be inserted therebetween.
- the bottom surface of the upper cover portion 236b of the upper bearing cover 236 becomes the cylindrical rotor ( 231,232 is bolted to abut the upper surface, the cover portion 238b of the lower bearing cover 238 is bolted to abut the bottom of the cylindrical rotor (231,232).
- the upper bearing cover 236 is fixed member 240.
- Lower bearing cover 238 because the lower shaft portion 238a is journal bearing supported under the fixed shaft 241 and the lower cover portion 238b is thrust supported on the bottom of the eccentric portion 242. Is rotatably installed relative to the fixing member 240.
- the lower shaft portion 238a of the lower bearing cover 238 is fitted to the bearing portion 260a of the lower bearing 260, and the lower bearing cover 238 is supported by bearings on the journal surface or the thrust surface which abut each other. It is rotatably supported with respect to the lower bearing 260.
- FIG. 13 is a plan view showing a vane mounting structure in a second embodiment of a compressor according to the present invention.
- the inner circumferential surface of the cylindrical rotors (231, 232) is provided with a vane mounting hole (232H) is formed in the radial direction and axially penetrated, the vane mounting hole ( After the pair of bushes 235 are fitted to the 232H, the vanes 234 integrally provided on the outer circumferential surface of the roller 233 are fitted between the bushes 235. At this time, a compression space is provided between the cylindrical rotors 231 and 232 and the roller 233, and the compression space is divided into the suction pocket S and the compression pocket D by the vanes 234.
- the suction port 233a of the roller 233 is located at one side of the vane 234 so as to be in communication with the suction pocket S, and the discharge port and discharge valve 236A of the upper bearing cover 236 (shown in FIG. 11) described above. 11 is located on the other side of the vane 234 to communicate with the compression pocket (D), it is preferable to be located close to the vane 234 to reduce the dead volume.
- the vane 234 integrally manufactured with the roller 233 in the compressor of the present invention is assembled to be slidably moved between the bushes 235 in the conventional rotary compressor. The friction loss caused by the sliding contact generated by the spring can be eliminated, and refrigerant leakage can be reduced between the suction pocket S and the compression pocket D.
- the cylindrical rotors 231 and 232 receive the rotational force by the rotating magnetic field with the stator 220 (shown in Fig. 10), the cylindrical rotors 231 and 232 rotate. While the vane 234 is fitted into the vane mounting holes 232H of the cylindrical rotors 231 and 232, the rotational force of the cylindrical rotors 231 and 232 is transmitted to the roller 233, and the vanes 234 according to the rotation of both vanes 234. ) Reciprocates linearly between the bushes 235. That is, the inner circumferential surfaces of the cylindrical rotors 231 and 232 have portions corresponding to each other on the outer circumferential surfaces of the rollers 233.
- the portions corresponding to each other are each of the cylindrical rotors 231 and 232 and the roller 233 rotates once.
- the suction pocket (S) gradually grows while repeating contact with each other, the suction pocket (S) gradually grows, while the refrigerant or working fluid is sucked into the suction pocket (S), and the compression pocket (D) gradually decreases. It is compressed and then discharged.
- FIG. 14 is a plan view showing an operation cycle of the compression mechanism in the second embodiment of the compressor according to the present invention.
- the cylindrical rotors 231 and 232 and the roller 233 rotate to (a), (b), (c) and (d). This shows one cycle where the relative position changes.
- the cylindrical rotors 231 and 232 and the roller 233 are located at (a)
- the refrigerant or the working fluid is sucked into the suction pocket S through the suction port 233a of the roller 233, and the suction pocket Compression occurs in the discharged compression pocket D, which is divided into S and the vanes 234.
- the compressor configured as described above is installed such that the rotating member 230 is suspended to the fixing member 240, and is rotatably supported by the lower bearing 260 so that the rotating member 230 is provided. Is suspended on the fixing member 240, and the rotating member 230 is supported on the lower bearing 260, that is, the lubrication must be made to the surface, in addition to the rotating member 230 and the fixing member 240 And lubrication is required between the parts abutting each other in the lower bearing 260.
- FIG. 15 is a side cross-sectional view showing an example of lubricating oil in a second embodiment of the compressor according to the present invention
- Figures 16 to 18 is a fixing member, a lower bearing cover, an upper bearing in a second embodiment of the compressor according to the present invention
- a lubricating oil passage provided in each cover is a perspective view.
- the oil level of the oil stored in the sealed container 210 is at least higher than the lower bearing 260 (shown in FIG. 12) or the lower portion of the lower bearing cover 238. It is preferable to be kept higher than the lowest end of the shaft portion 238a. Therefore, as described above, the lower shaft portion 238a of the lower bearing cover 238 is accommodated in the bearing portion 260a (shown in FIG. 12) of the lower bearing 260 (shown in FIG. 12).
- the journal face and the thrust face are bearing-supported respectively, and the contact face is submerged in oil so that a separate lubrication flow path may not be provided.
- a lubricating oil passage is provided at a portion where the rotating member 230 (shown in FIG. 10) and the fixing member 240 (shown in FIG. 10) come into contact with each other, the lubricating oil passage having a lower lubricating oil passage, an oil supply member, It can be divided into upper lubrication flow path.
- the lower lubrication flow passage is configured to supply oil stored in the lower portion of the sealed container 210 to the abutting portion of the lower bearing cover 238, the fixed shaft 241, and the eccentric portion 242, and an oil supply member.
- 270 is configured to pump oil as it rotates together with the rotating member 230 (shown in FIG. 10), and the upper lubricating oil passage includes oil pumped by the oil supply member 270 with the upper bearing cover 236.
- the fixed shaft 241 and the eccentric portion 242 is configured to supply to abutting portions.
- the lower lubricating oil passage has a first oil supply passage 241A, which is a hollow space perpendicular to the lower portion of the fixed shaft 241, and an oil supply hole penetrated in the radial direction below the fixed shaft 241 so as to communicate with the oil supply passage 241A.
- the first oil supply groove (a, b) may also be formed in any of the portions of the lower bearing cover 238, the fixed shaft 241 and the eccentric portion 242 abut each other, but not only relatively thick It is preferable to form a ring-shaped groove having a side cross section 'a' on a lower outer circumferential surface of the fixed shaft 241 and an eccentric portion 242 that are easy to machine.
- the oil surface is preferably formed so that the lower bearing cover 238 is locked.
- An inner circumferential surface of the lower shaft portion 238a of the 238 may have a straight or helical groove 238g vertical to communicate with the first oil supply grooves a and b.
- the oil supply member 270 is installed inside the hollow shaft portion 271 of the cylindrical shaft 271 fitted to the lower shaft portion 238a of the lower bearing cover 238, and the hollow shaft portion 271 and the hollow shaft portion 271 by a rotational force. It includes a propeller 272 to supply the oil through the flow path. Therefore, the oil supply member 270 rotates in the state submerged in the oil like the lower bearing cover 236, and the oil is raised through the oil supply member 270.
- the upper lubrication structure includes at least two extending to the upper surface of the eccentric portion 242 so as to communicate with the first oil supply passage 241A of the fixed shaft 241 and the first oil supply passage 241A of the fixed shaft 241.
- Upper and eccentric portions of the eccentric portion 242 contacting the upper bearing cover 236 so as to communicate with the second oil supply passage 242A of the eccentric portion 242 and the second oil supply passage 242A of the eccentric portion 242.
- a second oil supply groove (c, d) formed on the outer circumferential surface of the fixed shaft 241 immediately above, the second oil supply passage 242A provided in the eccentric portion 242 is the eccentric portion 242 It is preferable to be provided so as not to overlap with the horizontal suction passage (242B) provided in.
- the second oil supply grooves c and d may also be formed at any of the portions in contact with the upper bearing cover 236, the fixed shaft 241, and the eccentric portion 242, but are not only relatively thick. It is preferable to form a ring-shaped groove having a side cross-section 'b' on the upper outer circumferential surface of the fixed shaft 241 and the upper surface of the eccentric portion 242 that are easy to machine.
- a straight or spiral groove 236g perpendicular to the second oil supply grooves c and d may be formed on the inner circumferential surface of the upper shaft portion 236a of the upper bearing cover 236.
- the oil stored in the lower portion of the sealed container 210 has a higher oil surface than the oil supply hole 241h, including the lower lower shaft portion 238a of the lower bearing cover 238.
- lubrication is performed between the lower bearing 260 (shown in FIG. 12), and the lower bearing cover 238 supplies the first oil.
- the oil gathered in the grooves a and b and the groove 238g is lubricated between the fixed shaft 241 and the eccentric portion 242 and is rotatably installed.
- the oil is pumped by the oil supply member 270 as the rotating member 230 (shown in FIG. 10), the oil is the first oil supply passage 241A of the fixed shaft 241, the eccentric portion ( Through the second oil supply passage 242A of 242, it is introduced into the second oil supply grooves c and d and further rises through the groove 236g of the upper bearing cover 236.
- the upper bearing cover 236 is lubricated between the fixed shaft 241 and the eccentric portion 242 by the oil collected in the second oil supply grooves (c, d) and the grooves (236g) to be rotatable at the same time. Is installed.
- 19 is a perspective view showing an example of the vane lubrication structure in the second embodiment of the compressor according to the present invention.
- a coupling protrusion 232a protruding from the outer circumferential surface of the cylinder 232 is provided to form an inner circumferential surface of the rotor 231, and a vane mounting hole 232H extending from the inner circumferential surface of the cylinder 232 to a portion of the coupling protrusion 232a.
- the vane 234 is installed to abut the vane mounting holes 232H between the bushes 235, and the lower bearing cover 238 removes a portion of the bottom surface of the vane mounting holes 232H of the cylinder 232. Installed so as not to cover.
- the engaging projection even if the lower cover portion 238b of the lower bearing cover 238 is formed in a disc shape. It may be installed so as not to cover a part of the vane mounting holes (232H) extended to (232a).
- the outer circumferential portion thereof is formed stepped so as not to cover a part of the vane mounting holes 232H extending to the coupling protrusion 232a. Can be.
- the oil level of the oil inside the sealed container 210 is not only maintained higher than that of the lower bearing cover 238, but also the vane mounting hole. It is preferable that the bottom end of 232H be kept locked.
- an oil recovery structure is applied in order to maintain an appropriate amount of oil or more in the sealed container 210 (shown in FIG. 10).
- the oil separation is installed on the muffler 237 (shown in Fig. 12) immediately above the discharge port of the upper bearing cover 236 and the discharge port of the muffler 237 (shown in Figure 12).
- the oil is separated from the compressed refrigerant.
- the refrigerant from which the oil is separated exits through a hole (not shown) provided in the oil separation plate 280 (shown in FIG. 10), and the oil separated from the refrigerant is an oil separation plate (280 shown in FIG. 10).
- the oil return flow passage may be composed of a gap between the stator 220 and the rotor 231, or a jig may be mounted to bolt the cylinder 232 to the upper and lower bearing covers 236 and 238. It may be composed of a series of jig mounting holes (not shown) provided in the cylinder 231 and the upper and lower bearing cover (236,238) so as to communicate vertically.
- the upper bearing cover 236 is installed so as not to cover a part of the upper surface of the vane mounting hole 232H of the cylinder 232, and inside the sealed container 210 (shown in FIG. 10).
- the oil level is preferably kept higher than the upper bearing cover 236 as well as the top of the vane fitting 232H is locked.
Abstract
Description
Claims (15)
- 오일이 저장된 밀폐용기;밀폐용기 내에 고정된 스테이터;밀폐용기에 상단이 움직이지 않도록 설치됨과 동시에 밀폐용기 내부로 길게 연장되는 고정축과, 고정축에 편심되도록 형성된 편심부를 포함하는 제1고정부재;고정축의 하단과 이격되도록 형성되며, 밀폐용기의 하부에 움직이지 않도록 설치되는 제2고정부재;스테이터와 제1고정부재 사이에 위치하고, 스테이터로부터의 회전 전자기장에 의해 제1고정부재를 중심으로 회전하면서 그 내에 형성되는 압축공간으로 냉매를 흡입하여 압축시킬 수 있고, 제2고정부재에 하중을 가하면서 회전 가능하게 지지하는 회전부재; 그리고,회전부재의 회전력을 이용하여 밀폐용기 내에 저장된 오일을 회전부재와 고정부재가 베어링되는 부분으로 안내하는 윤활유로;를 포함하는 것을 특징으로 하는 압축기.
- 제1항에 있어서,회전부재는, 스테이터와의 상호 전자기력에 의해 고정부재를 중심으로 회전하도록 스테이터와 고정부재 사이에 설치된 로터와, 로터에 적층되어 로터와 함께 회전하고 압축공간이 내부에 구비된 실린더와, 편심부와 실린더 사이의 압축공간을 냉매가 흡입되는 흡입포켓과 냉매가 압축 및 토출되는 압축포켓으로 구획하도록 실린더에 탄성 지지되어 실린더와 함께 회전하며 편심부의 외면과 미끄럼 접촉하는 베인과, 실린더의 내주면에 슬롯 형상으로 형성되는 베인 장착구와, 베인을 탄성 지지하는 베인 스프링이 설치될 수 있도록 베인 장착구를 막아주는 베인 스프링 스토퍼와, 압축공간의 상부 및 하부를 형성하여 회전부재와 함께 고정부재를 중심으로 회전하는 상부 및 하부 베어링 커버를 포함하는 것을 특징으로 하는 압축기.
- 제1항에 있어서,회전부재는, 스테이터로부터의 회전 전자기장에 의해 고정축을 중심으로 회전하도록 고정부재에 회전 가능하게 지지되는 실린더형 로터와, 실린더형 로터의 회전력을 전달받아 실린더형 로터와 함께 편심부를 중심으로 회전하면서 실린더형 로터와의 사이에 압축공간을 형성하는 롤러와, 실린더형 로터로부터 롤러로 회전력을 전달하고 압축공간을 냉매가 흡입되는 흡입포켓과 냉매가 압축 및 토출되는 압축포켓으로 구획하는 베인과, 롤러의 외주면으로부터 실린더형 로터 쪽으로 돌출되도록 롤러에 일체로 형성됨과 동시에 베인을 수용하도록 형성된 베인 장착구와, 압축공간의 상부 및 하부를 형성하여 회전부재와 함께 고정부재를 중심으로 회전하는 상부 및 하부 베어링 커버로 이루어지는 것을 특징으로 하는 압축기.
- 제2항 또는 제3항에 있어서,하부 베어링 커버는 고정축을 에워싸는 하부 축부와, 실린더와 결합되어 압축공간의 하부를 형성하는 하부 커버부를 포함하고,하부 축부의 최하단이 밀폐용기 내에 저장된 오일에 잠기도록 설치되며,윤활유로는 하부 축부에 고정축의 외주면과 베어링되는 내주면에 형성된 그루브를 포함하는 것을 특징으로 하는 압축기.
- 제4항에 있어서,윤활유로는 고정축 하부에 축방향으로 형성된 제1오일공급유로와, 제1오일공급유로와 편심부 상면과 연통되도록 편심부에 형성된 제2오일공급유로를 포함하는 것을 특징으로 하는 압축기.
- 제5항에 있어서,고정축 및 편심부를 관통하여 압축공간의 흡입포켓으로 연결되는 냉매흡입유로를 더 포함하고,제2오일공급유로는 냉매흡입유로를 우회하여 편심부의 상부까지 연장되는 것을 특징으로 하는 압축기.
- 제5항에 있어서,윤활유로는 편심부의 상면 및 하면에 각각 형성된 상부 및 하부 요홈부를 포함하고,상부 및 하부 요홈부는 회전부재와 편심부 사이의 트러스트 면의 윤활을 위한 오일의 저장홈으로 기능하는 것을 특징으로 하는 압축기.
- 제5항에 있어서,윤활유로는 제1오일공급유로와 연통되도록 편심부와 고정축 하부 및 하부 베어링 커버가 맞닿는 부분에 구비된 제1오일저장홈과, 제2오일공급유로와 연통되도록 편심부와 고정축 상부 및 상부 베어링 커버가 맞닿는 부분에 구비된 제2오일저장홈을 더 포함하는 것을 특징으로 하는 압축기.
- 제8항에 있어서,상부 베어링 커버는 고정축 상단을 일부 감싸는 상부 축부를 포함하고,윤활유로는 제2오일저장홈과 연통되도록 상부 베어링 커버의 축부 내주면에 구비된 그루브를 더 포함하는 것을 특징으로 하는 압축기.
- 제2항 내지 제9항 중 어느 한 항에 있어서,압축기는, 회전부재의 하부에 장착되고, 회전부재가 회전됨에 따라 오일을 윤활유로로 펌핑하는 오일공급부재를 더 포함하는 것을 특징으로 하는 압축기.
- 제10항에 있어서,하부 베어링 커버는 고정축을 에워싸는 하부 축부를 포함하고,오일공급부재는 하부 축부에 압입된 중공축부와, 하부 축부의 회전에 따라 오일을 나선형으로 상승시키도록 중공축부 내측에 고정된 프로펠러로 이루어진 것을 특징으로 하는 압축기.
- 제2항 또는 제3항에 있어서,압축기는 베인 장착구의 일부를 밀폐용기의 내부공간으로 연통시켜 내부공간의 오일이 베인 장착구로 공급되도록 하는 오일공급홀;을 포함하는 것을 특징으로 하는 압축기.
- 제2항에 있어서,압축기는 베인 장착구의 일부를 밀폐용기의 내부공간으로 연통시켜 내부공간의 오일이 베인 장착구로 공급되도록 하는 오일공급홀;을 포함하고,오일공급홀은, 베인 장착구와 연통하도록 베인 스프링 스토퍼에, 밀폐용기에 저장된 오일의 유면보다 낮은 위치에 형성되어, 오일이 베인 장착구로 공급될 수 있도록 하는 것을 특징으로 하는 압축기.
- 제13항에 있어서,베인 장착구는 실린더 외주면으로부터 돌출되어 형성된 베인 피난 돌기부까지 연장되고,상부 및 하부 베어링 커버 중 하나 이상에 의해 폐쇄되지 않은 베인 피난 돌기부의 개방공간이 베인 장착구로의 오일공급홀로 기능하는 것을 특징으로 하는 압축기.
- 제3항에 있어서,압축기는 베인 장착구의 일부를 밀폐용기의 내부공간으로 연통시켜 내부공간의 오일이 베인 장착구로 공급되도록 하는 오일공급홀;을 포함하고,상부 및 하부 베어링 커버 중 하나 이상에 의해 폐쇄되지 않은 베인 장착구의 개방공간이 베인 장착구로의 오일공급홀로 기능하는 것을 특징으로 하는 압축기.
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN2009801606533A CN102472276A (zh) | 2009-08-10 | 2009-12-02 | 压缩机 |
US13/387,465 US9181947B2 (en) | 2009-08-10 | 2009-12-02 | Compressor |
Applications Claiming Priority (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR10-2009-0073279 | 2009-08-10 | ||
KR1020090073287A KR101575357B1 (ko) | 2009-08-10 | 2009-08-10 | 압축기 |
KR10-2009-0073287 | 2009-08-10 | ||
KR1020090073280A KR101563004B1 (ko) | 2009-08-10 | 2009-08-10 | 압축기 |
KR10-2009-0073280 | 2009-08-10 | ||
KR1020090073279A KR101557506B1 (ko) | 2009-08-10 | 2009-08-10 | 압축기 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2011019114A1 true WO2011019114A1 (ko) | 2011-02-17 |
Family
ID=43586275
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/KR2009/007166 WO2011019114A1 (ko) | 2009-08-10 | 2009-12-02 | 압축기 |
Country Status (3)
Country | Link |
---|---|
US (1) | US9181947B2 (ko) |
CN (1) | CN102472276A (ko) |
WO (1) | WO2011019114A1 (ko) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP6418329B2 (ja) * | 2015-07-13 | 2018-11-07 | 三菱電機株式会社 | 圧縮機 |
CN106168214A (zh) * | 2016-06-29 | 2016-11-30 | 珠海格力节能环保制冷技术研究中心有限公司 | 一种转缸增焓活塞压缩机及具有其的空调系统 |
KR101925331B1 (ko) * | 2017-03-16 | 2018-12-05 | 엘지전자 주식회사 | 영구자석을 가지는 전동기 및 이를 구비한 압축기 |
CN107701448A (zh) * | 2017-10-20 | 2018-02-16 | 珠海格力节能环保制冷技术研究中心有限公司 | 一种压缩机及具有其的空调器 |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2440593A (en) * | 1946-10-23 | 1948-04-27 | Harry B Miller | Radial vane pump mechanism |
US2670894A (en) * | 1950-10-20 | 1954-03-02 | Borg Warner | Compressor |
Family Cites Families (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1964415A (en) * | 1930-07-31 | 1934-06-26 | Frigidaire Corp | Motor-compressor unit |
US2309577A (en) * | 1938-10-01 | 1943-01-26 | Davidson Mfg Corp | Rotary compressor |
US2415011A (en) * | 1942-09-18 | 1947-01-28 | Borg Warner | Motor compressor assembly |
US2420124A (en) * | 1944-11-27 | 1947-05-06 | Coulson Charles Chilton | Motor-compressor unit |
US3664461A (en) * | 1971-03-31 | 1972-05-23 | Danfoss As | Oil pump for a motor compressor |
JPS62284985A (ja) | 1986-06-03 | 1987-12-10 | Matsushita Electric Ind Co Ltd | 回転圧縮機 |
DE3878073T2 (de) * | 1987-07-31 | 1993-06-03 | Toshiba Kawasaki Kk | Fluessigkeitsverdichter. |
JPH01100291A (ja) | 1987-10-12 | 1989-04-18 | Japan Carlit Co Ltd:The | クロムメッキ方法 |
KR950001693Y1 (ko) * | 1992-07-30 | 1995-03-11 | 이헌조 | 압축기의 급유 장치 |
JP2567050Y2 (ja) * | 1992-12-14 | 1998-03-30 | 株式会社東芝 | 縦形コンプレッサの給油装置 |
US5733112A (en) * | 1993-12-08 | 1998-03-31 | Samsung Electronics Co., Ltd. | Rotary compressor having a roller mounted eccentrically in a cylindrical chamber of a rotatable cylinder |
JP2000249064A (ja) * | 1999-02-25 | 2000-09-12 | Toshiba Corp | 圧縮機 |
CN100386526C (zh) | 2003-12-12 | 2008-05-07 | 乐金电子(天津)电器有限公司 | 旋转式压缩机的供油装置 |
US7217110B2 (en) * | 2004-03-09 | 2007-05-15 | Tecumseh Products Company | Compact rotary compressor with carbon dioxide as working fluid |
EP1805419B1 (en) | 2004-10-26 | 2015-07-22 | LG Electronics Inc. | Rotary compressor |
CN1782405A (zh) * | 2004-11-30 | 2006-06-07 | 乐金电子(天津)电器有限公司 | 旋转式压缩机的滑片结构 |
JP4780971B2 (ja) | 2005-02-17 | 2011-09-28 | 三洋電機株式会社 | ロータリコンプレッサ |
KR100835187B1 (ko) | 2007-03-20 | 2008-06-04 | 엘지전자 주식회사 | 로터리 압축기 |
JP4862925B2 (ja) * | 2009-07-31 | 2012-01-25 | 株式会社富士通ゼネラル | ロータリ圧縮機 |
-
2009
- 2009-12-02 US US13/387,465 patent/US9181947B2/en not_active Expired - Fee Related
- 2009-12-02 WO PCT/KR2009/007166 patent/WO2011019114A1/ko active Application Filing
- 2009-12-02 CN CN2009801606533A patent/CN102472276A/zh active Pending
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2440593A (en) * | 1946-10-23 | 1948-04-27 | Harry B Miller | Radial vane pump mechanism |
US2670894A (en) * | 1950-10-20 | 1954-03-02 | Borg Warner | Compressor |
Also Published As
Publication number | Publication date |
---|---|
US9181947B2 (en) | 2015-11-10 |
CN102472276A (zh) | 2012-05-23 |
US20120128516A1 (en) | 2012-05-24 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
WO2011019113A1 (ko) | 압축기 | |
WO2011019116A1 (ko) | 압축기 | |
WO2017188558A1 (ko) | 스크롤 압축기 | |
WO2011019114A1 (ko) | 압축기 | |
WO2010011115A1 (ko) | 오일 회수 부재 및 이를 적용한 전동기구와 압축기 | |
WO2011019115A1 (ko) | 압축기 | |
KR101573938B1 (ko) | 압축기 | |
KR101563368B1 (ko) | 압축기 | |
KR101563005B1 (ko) | 압축기 | |
KR20110015856A (ko) | 압축기 | |
KR101563006B1 (ko) | 압축기 | |
KR101139086B1 (ko) | 압축기 | |
KR101567086B1 (ko) | 압축기 | |
KR101521304B1 (ko) | 압축기 | |
KR101567089B1 (ko) | 압축기 | |
KR20110015851A (ko) | 압축기 | |
KR101587285B1 (ko) | 압축기 | |
KR101557506B1 (ko) | 압축기 | |
WO2019208951A1 (ko) | 스크롤 압축기 | |
KR20110015849A (ko) | 압축기 | |
KR101567088B1 (ko) | 압축기 | |
KR101105967B1 (ko) | 컴팩트형 압축기 | |
KR20110015858A (ko) | 압축기 | |
KR20110015862A (ko) | 압축기 | |
CN115434910A (zh) | 旋转式压缩机 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
WWE | Wipo information: entry into national phase |
Ref document number: 200980160653.3 Country of ref document: CN |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 09848300 Country of ref document: EP Kind code of ref document: A1 |
|
WWE | Wipo information: entry into national phase |
Ref document number: 13387465 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: 09848300 Country of ref document: EP Kind code of ref document: A1 |