WO2010011115A1 - 오일 회수 부재 및 이를 적용한 전동기구와 압축기 - Google Patents
오일 회수 부재 및 이를 적용한 전동기구와 압축기 Download PDFInfo
- Publication number
- WO2010011115A1 WO2010011115A1 PCT/KR2009/004164 KR2009004164W WO2010011115A1 WO 2010011115 A1 WO2010011115 A1 WO 2010011115A1 KR 2009004164 W KR2009004164 W KR 2009004164W WO 2010011115 A1 WO2010011115 A1 WO 2010011115A1
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- WIPO (PCT)
- Prior art keywords
- oil recovery
- diameter
- recovery member
- oil
- ratio
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/02—Lubrication
- F04B39/0207—Lubrication with lubrication control systems
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/04—Measures to avoid lubricant contaminating the pumped fluid
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- 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
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- 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
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- 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
- F04C29/026—Lubricant separation
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- 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
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
-
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/04—Heating; Cooling; Heat insulation
- F04C29/045—Heating; Cooling; Heat insulation of the electric motor in hermetic pumps
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S418/00—Rotary expansible chamber devices
- Y10S418/01—Non-working fluid separation
Definitions
- the present invention is limited to the installation position and size of the oil recovery member and the other members close to the oil recovery as the rotary shaft is rotated, the oil recovery member that can form a flow path for effectively recovering the oil, and the electric mechanism applying the same Relates to a compressor.
- a compressor is a mechanical device that increases pressure by receiving power from a power generator such as an electric motor or a turbine and compresses air, refrigerant, or various other working gases. It is widely used throughout the industry.
- 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.
- Korean Patent Laid-Open Publication No. 10-1996-0023817 discloses a rotary compressor, in which a cylinder and an electric motor are configured to be stacked in an axial direction, so that a refrigerant is compressed in a cylinder for compressing a predetermined capacity.
- the rotational speed of the motor is uniform to adjust the compression capacity per hour uniformly, but if the inverter type motor is employed as the electric motor, it is possible to change the compression capacity per hour as the rotation speed of the motor is variable. Can be.
- Republic of Korea Patent Publication No. 10-2005-0062995 discloses a rotary twin compressor, the two cylinders and the electric motor is configured to be laminated in the axial direction, so that the compression of the refrigerant occurs at the same time in two cylinders compressing the same capacity The compression capacity is once improved over the compressor.
- Korean Patent Laid-Open Publication No. 10-2007-0009958 discloses a rotary two-stage compressor, in which two cylinders and an electric motor are stacked in an axial direction and provided with separate flow paths connecting two cylinders at the same time, thereby compressing in one cylinder.
- the compressed refrigerant was compressed in the remaining cylinders, thereby doubling the amount of compression once compared to the compressor.
- Such a rotary compressor is employed in a refrigerating cycle, in which oil is circulated in order to cool / lubricate components therein as the rotary compressor is operated. At this time, the liquid oil in the rotary compressor is partially withdrawn along with the refrigerant in the form of gas.
- the reliability of the parts inside the rotary compressor due to the lack of oil wears down and / or overheats, or as the oil flows along the refrigeration cycle Due to this, there is a problem that is difficult to recover by stacking on the flow path. Therefore, various oil recovery structures are applied to the rotary compressor to prevent oil from escaping along the refrigerating cycle along with the high pressure refrigerant.
- the rotary compressor is provided with a compression mechanism and a motor-type motor unit for driving the same, the motor is divided into a distribution winding (Distributed winding), and a concentrated winding (Concentrated winding) according to the winding method.
- a distribution winding distributed winding
- a concentrated winding Concentrated winding
- the distribution range is a manner in which windings of each phase are distributed and wound in a plurality of slots. As a plurality of coil bundles are spread over the slots, the coil end in the axial direction of the windings becomes large, so that the winding spot ratio inserted into the slots is not high. Therefore, since the rotary compressor employing the distribution winding motor does not have a high winding spot ratio and there is a lot of empty space in the motor, even if oil is pumped, it is recovered through the distribution winding motor. Do.
- Concentrated zones are wound in a concentrated manner in one slot.
- Concentrated slots have a smaller area and a larger number of poles than a distributed sphere, but a direct winding type in which a coil is wound directly on a pole, or a coil Is wound into an insert winding type in which the inner diameter slot opening of the stator is inserted.
- the coil end in the axial direction of the winding is shorter than the distribution range and the winding spot ratio is also increased. Therefore, a rotary compressor employing a concentrated motor has a high winding spot ratio, so that there is not much empty space in the motor, and thus there is not much empty space for oil to be recovered. Therefore, even if oil is pumped, it is difficult to recover through a distribution motor. It is preferable that an oil recovery port or an oil recovery structure is applied to facilitate recovery.
- FIG. 1 is a longitudinal cross-sectional view showing the entire structure of a conventional rotary compressor
- Figure 2 is an assembled exploded view showing the attachment structure of the oil separation member applied to FIG.
- Japanese Patent Application No. 94-317020 discloses a rotary compressor and an oil recovery structure.
- an electric motor unit 11 and a compression unit 12 are provided inside a sealed casing 10.
- the motor unit 11 is composed of a stator 13, a rotor 14, and a rotation shaft 15, and an oil separating member 50 is mounted at the top center of the rotor 14. Therefore, when the power is supplied, as the rotating shaft 15 is rotated by the mutual electromagnetic force of the stator 13 and the rotor 14, the refrigerant is compressed in the compression unit 12, and then filled in the sealed casing 10 It is discharged to the outside.
- the oil stored in the bottom surface of the airtight casing 10 also rises along the rotation shaft 15, passing through the center of the rotor 14 and hitting the oil separation member 50 rotated together with the rotor 14 in the radial direction. Then guided back to the bottom of the hermetic casing 10 through a gap between the stator 13 and the rotor 14, including a plurality of holes 54 axially penetrating around the center of the rotor 14. It is recovered.
- Figure 3 is a graph analyzing the oil flow path of the conventional rotary compressor, the rotary compressor shown in Figure 3 is configured in the same manner as the rotary compressor shown in Figure 1, only the oil separation member is omitted.
- the rotary compressor When the rotary compressor is operated to compress the refrigerant, the oil rises along the main flow path portion A around the rotating shaft along with the refrigerant, and then the recovery flow path portion around the main flow path portion A while hitting the sealed casing. Recovered through (B).
- the recovery flow path portion (B) as mentioned above, the first recovery passage B1, which is a plurality of holes provided to penetrate in the axial direction around the center of the rotor, and the second recovery interval, which is a gap between the stator and the rotor.
- the oil recovery rate decreases, and the speed of oil pumped through the main flow path portion is about 10 m / s. Since the speed of oil recovered through the flow path is about 0.005 m / s, it is easy for a large amount of oil to stay on the upper side of the hermetic casing and escape with the high temperature and high pressure refrigerant to the outside of the hermetic casing. As described above, there is a problem of deteriorating operation reliability due to friction / wear of parts.
- the present invention has been made to solve the above problems of the prior art, by using a centrifugal force of the rotor to increase the oil recovery rate to increase the oil recovery rate proportional to the pumping speed of the oil and the oil recovery member and electric transmission using the same
- the object is to provide a mechanism and a compressor.
- the present invention provides an oil recovery member and a power mechanism and a compressor using the oil recovery member for forcibly guiding the flow of oil in the radial direction, even when the oil is pumped in the axial direction, and to be quickly recovered in the outermost portion of the radial direction.
- an oil recovery member and a power mechanism and a compressor using the oil recovery member for forcibly guiding the flow of oil in the radial direction, even when the oil is pumped in the axial direction, and to be quickly recovered in the outermost portion of the radial direction.
- One embodiment of the present invention for solving the above problems is a cylindrical body formed in a wider diameter from the bottom to the top in the axial direction; And, a guide portion extended in the radial direction on the top of the main body; including, the ratio of the diameter (a) of the guide portion to the lower diameter (b) of the main body is characterized in that to maintain more than 2.85 (a / b ⁇ 2.85) An oil recovery member is provided.
- the ratio of the diameter (a) of the guide portion to the lower diameter (b) of the main body is characterized by maintaining 3.15 or less (a / b ⁇ 3.15).
- the ratio a / b plus the axial height Lo (a / b + Lo) is maintained at 35.85 or more (a / b + Lo ⁇ 35.85).
- the present invention is characterized in that the ratio (a / b) plus the axial height (Lo) (a / b + Lo) maintains 47.5 or less (a / b + Lo ⁇ 47.5).
- another example of the present invention is a rotary shaft is the lower end is contained in oil;
- a rotor engaged with an outer circumferential surface of the rotating shaft;
- a stator installed on the outer circumferential surface of the rotor and having a coil end at an upper portion thereof as the coil is wound around the core;
- an oil recovery member coupled to the center of the rotor and having a height Lo in the axial direction higher than the axial height Lc of the coil end in order to radially guide the oil rising by the rotation of the rotation shaft. It provides a power mechanism characterized in that.
- the ratio of the upper diameter d2 of the oil recovery member d2 / d1 to the inner diameter d1 of the coil end is maintained at 0.63 or more in order to increase the oil recovery rate.
- the ratio of the upper diameter d2 of the oil recovery member d2 / d1 to the inner diameter d1 of the coil end is maintained at 1.19 or less in order to reduce the flow path resistance.
- the oil recovery member is composed of a cylindrical body formed in a wider diameter from the bottom to the top in the axial direction, and a guide portion extended radially on the upper end of the body, the top diameter (d2) of the oil recovery member It is characterized in that the diameter of the guide portion.
- the ratio of the top diameter (a) of the oil recovery member to the bottom diameter (b) of the oil recovery member is characterized in that to maintain 2.85 or more (a / b ⁇ 2.85) in order to increase the oil recovery rate.
- the ratio of the upper diameter (a) of the oil recovery member to the lower diameter (b) of the oil recovery member is characterized by maintaining 3.15 or less (a / b ⁇ 3.15) to reduce the flow path resistance.
- the ratio (a / b) plus the axial height (Lo) of the oil recovery member (a / b + Lo) maintains 35.85 or more (a / b + Lo ⁇ 35.85). It features.
- the ratio (a / b) to the value (a / b + Lo) of the oil recovery member plus the axial height (Lo) is maintained at 47.5 or less (a / b + Lo ⁇ 47.5). It features.
- the oil recovery member is composed of a cylindrical body formed in a wider diameter from the bottom to the top in the axial direction, and a guide portion extended radially on the upper end of the body, the top diameter (a) of the oil recovery member is It is the diameter of the guide portion, the lower diameter (b) of the oil recovery member is characterized in that the lower diameter of the main body.
- another example according to the present invention is a sealed container in which the refrigerant flows in and out, oil is stored on the bottom surface;
- a compression mechanism unit fixed to the inner side of the sealed container and compressing the refrigerant;
- An electric mechanism part fixed to the upper part of the sealed container and supplying power to the compression mechanism part;
- an oil recovery member coupled to the center of the power transmission mechanism and configured to radially guide oil rising along the power transmission mechanism by the operation of the power transmission mechanism, wherein an upper end of the oil recovery member is in the axial direction. It is characterized by being installed higher.
- the transmission mechanism is composed of a rotating shaft, a rotor, and a stator having a coil end at the upper portion as the coil is wound around the core, and the oil recovery member has an axial height Lo of the oil recovery member. It is characterized in that it is coupled to the center of the rotor to maintain more than the axial height (Lc) of the end (Lo ⁇ Lc).
- the transmission mechanism is composed of a rotating shaft, a rotor, and a stator having a coil end at the upper portion as the coil is wound around the core, and the axial height Lo of the oil recovery member is the axial direction of the coil end. (Lo ⁇ Lc + f), which is equal to or less than the sum of the height Lc and the axial height f of the wire lead-out space.
- the wire drawing space is characterized in that the minimum space required for the operation of drawing the wire from the coil end to the sealed container.
- the oil recovery member further comprises a plurality of oil recovery port for recovering the oil hit the oil recovery member under the sealed container, the ratio of the cross-sectional area (A2) of the oil recovery ports to the cross-sectional area (A1) of the sealed container.
- (A2 / A1) is characterized by being 3% or less.
- the oil recovery ports include a plurality of first oil recovery ports provided between the sealed container and the stator, a second oil recovery port which is a gap between the rotor and the stator, and a plurality of third oil recovery devices provided in the rotor itself. At least one or more of the phrases.
- the electric motor unit is fixed to the rotary shaft connected to the compression mechanism, the cylindrical rotor engaged with the outer peripheral surface of the rotating shaft, the sealed container so as to maintain a gap on the outer peripheral surface of the rotor, the coil end is wound as the coil is wound around the core
- the ratio of the upper diameter (d2) of the oil recovery member (d2 / d1) to the inner diameter (d1) of the coil end is characterized in that to maintain more than 0.63 to increase the oil recovery rate.
- the ratio of the upper diameter d2 of the oil recovery member d2 / d1 to the inner diameter d1 of the coil end is maintained at 1.19 or less in order to reduce the flow path resistance.
- the oil recovery member is composed of a cylindrical body formed in a wider diameter from the bottom to the top in the axial direction, and a guide portion extended radially on the upper end of the body, the top diameter (d2) of the oil recovery member It is characterized in that the diameter of the guide portion.
- the oil recovery member further comprises a plurality of oil recovery port for recovering the oil hit the oil recovery member under the sealed container, the ratio of the cross-sectional area (A2) of the oil recovery ports to the cross-sectional area (A1) of the sealed container.
- (A2 / A1) is characterized by being 2.09% or less.
- the oil recovery ports include a plurality of first oil recovery ports provided between the sealed container and the stator, a second oil recovery port which is a gap between the rotor and the stator, and a plurality of third oil recovery devices provided in the rotor itself. At least one or more of the phrases.
- the ratio of the top diameter (a) of the oil recovery member to the bottom diameter (b) of the oil recovery member is characterized in that to maintain 2.85 or more (a / b ⁇ 2.85) in order to increase the oil recovery rate.
- the ratio of the upper diameter (a) of the oil recovery member to the lower diameter (b) of the oil recovery member is characterized by maintaining 3.15 or less (a / b ⁇ 3.15) to reduce the flow path resistance.
- the ratio (a / b) plus the axial height (Lo) of the oil recovery member (a / b + Lo) maintains 35.85 or more (a / b3 + Lo ⁇ 35.85). It features.
- the ratio (a / b) to the value (a / b + Lo) of the oil recovery member plus the axial height (Lo) is maintained at 47.5 or less (a / b + Lo ⁇ 47.5). It features.
- the oil recovery member includes a cylindrical body formed in a wider diameter from the bottom to the top in the axial direction, and a guide portion extended radially on the upper end of the body, the top diameter (a) of the oil recovery member It is the diameter of the guide portion, the lower diameter (b) of the oil recovery member is characterized in that the lower diameter of the main body.
- the oil recovery member further comprises a plurality of oil recovery port for recovering the oil hit the oil recovery member under the sealed container, the ratio of the cross-sectional area (A2) of the oil recovery ports to the cross-sectional area (A1) of the sealed container.
- (A2 / A1) is characterized by being 3% or less.
- the transmission mechanism is composed of a stator fixed to the inner surface of the sealed container, and a rotor rotatably installed inside the stator, the oil recovery ports are a plurality of oil recovery ports provided between the sealed container and the stator And an oil recovery port, a second oil recovery port which is a gap between the rotor and the stator, and at least one of a plurality of third oil recovery ports provided in the rotor itself.
- the oil recovery member according to the present invention configured as described above, the power mechanism and the compressor applying the same limit the installation position and size between the stator in close proximity to the oil recovery member, the oil is pumped along the rotating shaft and the rotor is filled in a sealed container Even when mixed with the refrigerant, since the oil is guided in the radial direction by the centrifugal force while hitting the oil recovery member, the oil is easily separated from the refrigerant, thereby preventing the oil from escaping with the refrigerant.
- the present invention is provided with an oil recovery port of the rotor itself, an oil recovery port which is a gap between the rotor and the stator, and in addition to the additional oil recovery port between the stator and the sealed container, the oil is guided by the oil recovery member and various oils Since it is recovered through the recovery port, even if the compressor is operated at a high speed, the oil is quickly recovered and recycled at the same time.
- the present invention even if the oil is pumped as the compressor is operated, the oil is guided in the radial direction while hitting the oil recovery member, so that the recovery through the oil recovery port between the outermost stator and the closed vessel in the radial direction, the compressor has the advantage of increasing the reliability of operation.
- FIG. 1 is a longitudinal sectional view showing the overall structure of a conventional rotary compressor.
- FIG. 2 is an exploded view illustrating the attachment structure of the oil separation member applied to FIG. 1.
- FIG. 2 is an exploded view illustrating the attachment structure of the oil separation member applied to FIG. 1.
- Figure 3 is a graph analyzing the oil flow path of the conventional rotary compressor.
- Figure 4 is a longitudinal sectional view showing the overall structure of a rotary compressor of one embodiment of the present invention.
- FIG. 5 shows an example of a first compression assembly of a rotary twin compressor according to the invention from below;
- FIG. 6 shows an example of a second compression assembly of a rotary twin compressor according to the invention from the top.
- FIG. 7 is a longitudinal sectional view showing the oil recovery structure of FIG. 4 in more detail.
- FIG. 8 is a cross-sectional view of the oil recovery port of FIG. 4 in more detail.
- FIG 9 is a graph showing the circulation rate of the refrigeration cycle according to the height ratio (Lo / Lc) of the oil recovery member to the height of the coil end in the rotary compressor of one embodiment of the present invention.
- FIG. 10 is a graph showing the compression efficiency according to the diameter ratio (d2 / d1) of the oil recovery member to the inner diameter of the coil end in the rotary compressor of one embodiment of the present invention and the circulation rate of the refrigeration cycle to which it is applied.
- FIG. 11 is a graph showing the compression efficiency according to the upper / lower diameter ratio (a / b) of the oil recovery member in the rotary compressor of one embodiment of the present invention and the circulation rate of the refrigeration cycle to which it is applied.
- Figure 4 is a longitudinal sectional view showing the overall structure of a rotary compressor of one embodiment of the present invention.
- One embodiment of the rotary compressor according to the present invention is a rotary twin compressor, as shown in Figure 4 is provided with a power mechanism (not shown) and a compression mechanism (not shown) in the upper and lower sealed container 101, the electric mechanism unit Is a motor 110 for generating a rotational force, and the compression mechanism portion is a first compression assembly 120 for compressing a part of the sucked refrigerant, the second compression assembly 130 for compressing the rest of the introduced refrigerant, 2 the intermediate plate 140 partitioning the compression assemblies 120 and 130, the first bearing 161 and the cover 171, and the second compression assembly constituting the first discharge space communicated with the lower side of the first compression assembly 120.
- the rotary twin compressor 100 constitutes a part of a refrigeration cycle such as a condenser, a capillary tube or an electronic expansion valve, a refrigerator or an air conditioner including an evaporator, and after the gas-liquid refrigerant is separated from the accumulator (A), Only the refrigerant is introduced into the rotary twin compressor 100.
- the sealed container 101 is a space filled with a high-pressure refrigerant, the side of the sealed container 101 is installed so that the first and second inlet pipes 151 and 152 through which the refrigerant is sucked into the first and second compression assemblies 120 and 130.
- the upper surface of the sealed container 101 is provided with an outlet pipe 153 for discharging a high pressure refrigerant.
- the motor 110 includes a stator 111, a rotor 112, and a rotation shaft 113.
- the stator 111 has a coil wound around the core 111a in which a ring-shaped electrical steel sheet is stacked. In the embodiment applied to the present invention, a large amount of empty space is provided as the coil is wound in an insert type during the intensive winding method.
- the non-constructed structure is adopted, and the coil end 111b is provided above and below the core 111a, and is installed to be fixed inside the hermetic container 101.
- the rotor 112 is also configured to stack the electrical steel sheet, and is installed to maintain a gap inside the stator 111.
- the rotating shaft 113 penetrates the center of the rotor 112 and is fixed to the rotor 112.
- the rotor 112 When a current is applied to the electric motor 110, the rotor 112 rotates by 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 first compression assembly 120 so as to pass through the center portion of the first compression assembly 120, the intermediate plate 140, and the second compression assembly 130.
- the first compression assembly 120 and the second compression assembly 130 have a middle plate 140 therebetween, and the first compression assembly 120-the middle plate 140-the second compression assembly 130 from the bottom.
- the second compression assembly 120, the middle plate 140, and the second compression assembly 130 may be stacked in order from the bottom.
- the first bearing 161 and the first bearing 161 and the first compression assembly 120, 130 may be disposed on the lower and upper portions, respectively.
- Two bearings 162 are installed to assist the rotation of the rotary shaft 113, and support the load of each component of the two-stage compression assembly (120, 130) stacked vertically.
- the second bearing 162 provided on the upper side is welded to the sealed container 101 at three points to support the load of the two-stage compression assembly 120 and 130 and to fix it to the sealed container 101.
- a first discharge space in which the refrigerant compressed in the first compression assembly 120 is temporarily stored by the first bearing 161 and the cover 171 is formed below the first compression assembly 120
- the second compression assembly A second discharge space in which the refrigerant compressed in the second compression assembly 130 is also temporarily stored by the second bearing 162 and the cover 172 is formed on the upper side, and the first and second discharge spaces are It serves as a buffer space on the refrigerant passage.
- discharge ports (not shown) and discharge valves (not shown) are provided in the first and second bearings 161 and 162 so that the refrigerant compressed into the first and second discharge spaces can flow in and out, and the covers 171 and 172. ) May be provided with a hole in communication with the interior of the sealed container (101).
- the first compression assembly 120 includes a first cylinder 121, a first eccentric 122, a first roller 123, and a first vane 124 as shown in FIG. 5.
- the first cylinder 121 is provided with a vane mounting hole 124h in which the first vane portion 122 is elastically supported by the elastic member S at an inner diameter thereof, and has a sealed container 101 at one side of the vane mounting hole 124h.
- the inlet 126 is provided to connect the first inlet pipe 151 penetrating through the ()
- the outlet 127 is provided on the other side of the vane mounting hole (124h) in communication with the first discharge space. That is, the inner space of the first cylinder 121 is divided into the suction region S and the discharge region D by the first roller 123 and the first vane 124, but the refrigerant before and after compression is first It coexists in the cylinder 121.
- the first eccentric portion 122 when the first eccentric portion 122 is rotated together with the rotation shaft 113, the first roller 123 is rolled along the inside of the first cylinder 121, and the first cylinder is driven by the first vane 124.
- the refrigerant sucked into the suction region through the first inlet pipe 151 and the suction port 126 is divided into the suction region S and the discharge region D between the 121 and the first roller 123. After being compressed in (D), it exits through the discharge port 127 and the first discharge space.
- the second compression assembly 130 includes a second cylinder 131, a second eccentric 132, a second roller 133, and a second vane 134 as shown in FIG. 6, but the first compression Since the assembly 120 is the same as the assembly 120, detailed descriptions of components and operations are omitted. However, like the first eccentric portion 122 (shown in FIG. 5), the second eccentric portion 132 is eccentric so as to have the same phase with respect to the rotation axis 113, and the vane mounting in which the second vane portion 134 is mounted.
- the hole 134h, the suction port 136 in communication with the second inlet pipe 152, and the discharge port 137 in communication with the second discharge space are vane mounting holes 124h formed in the first cylinder 121 (shown in FIG. 5). 4 is formed in the inner diameter of the second cylinder 131 so as to be located in the same manner as the suction port 126 (shown in FIG. 5) and the discharge port 127 (shown in FIG. 5).
- FIG. 7 is a longitudinal cross-sectional view of the oil recovery structure of FIG. 4 in more detail
- FIG. 8 is a cross-sectional view of the oil recovery port of FIG. 4 in more detail.
- the refrigerant is compressed in the first and second compression assemblies 120 and 130 (shown in FIG. 4).
- the oil stored on the bottom surface is supplied between parts while lubricating and cooling while being raised, and then hits the oil return member 180 and is radially guided as shown in FIG. 7.
- the oil recovery member 180 extends in a horizontal form on the top of the funnel-shaped main body 181 and the top of the main body 181 to radially guide the flow of oil to guide the rising flow of oil in the radial direction.
- the height Lo of the oil recovery member is the height Lc of the coil end so that the oil rising along the rotor 112 and the rotating shaft 113 can be guided to the outer diameter of the stator 111 by the oil recovery member 180. It is preferable to be selected to be larger, but more preferably, the upper end of the oil recovery member 180 is located higher than the upper end of the coil end 111b.
- the core 111a and the rotor 112 of the stator 111 are installed at the same height in order to maximize the electromagnetic force, and the coil end 111b and the rotor 112 exposed on the core 111a of the stator 111 are exposed.
- the upper end of the oil recovery member 180 is positioned higher than the top of the coil end 111b. It can be seen that it is configured higher than the height (Lc).
- Lc the height of the oil recovery member
- the inner diameter d2 of the coil end 111b so that the oil rising along the rotor 112 and the rotating shaft 113 can be radially dispersed along the space between the coil end 111b and the oil recovery member 180. It is preferable that the ratio d1 / d2 of the upper diameter d1 of the oil recovery member 180 with respect to is set within a setting range. That is, when the ratio d1 / d2 of the upper diameter d1 of the oil recovery member 180 to the inner diameter d2 of the coil end 111b is excessively small, the oil recovery member 180 disperses the oil.
- the oil recovery member 180 may be It acts as a resistance. Accordingly, in consideration of the oil dispersion effect and the oil flow resistance simultaneously, the numerical limitation related to the ratio of the top diameter d1 of the oil recovery member 180 to the inner diameter d2 of the coil end 111b is d. This will be explained in detail later.
- the upper and lower ends of the oil recovery member 180 so that oil rising along the rotor 112 and the rotating shaft 113 can be radially dispersed along the space between the coil end 111b and the oil recovery member 180.
- the diameter (a, b) is selected within the set range, the ratio of the top diameter (a) of the oil recovery member 180 to the bottom diameter (b) of the oil recovery member 180, that is, the diameter of the mounting portion 183 ( It is preferable that the diameter (a) ratio of the guide 182 with respect to b) is selected within a setting range.
- the top diameter a of the oil recovery member 180 is excessively small with respect to the bottom diameter b of the oil recovery member 180, the dispersion effect of oil is lowered by the oil recovery member 180.
- the upper diameter a of the oil recovery member 180 is excessively large with respect to the lower diameter b of the oil recovery member 180, the flow direction of the oil rising along the rotor 112 and the rotation shaft 113 is changed to oil.
- the oil recovery member 180 acts as a resistance of the oil flow as excessively changed by the recovery member 180. Accordingly, the numerical limitations related to the ratio of the top diameter a of the oil recovery member 180 to the bottom diameter b of the oil recovery member 180 in consideration of the oil dispersion effect and the flow resistance of the oil are described in detail below. Will be explained.
- the height Lo of the oil recovery member 180 is set higher than the height Lc of the coil end 111b, while considering the shape of the oil recovery member 180, the airtight container ( Since the height Lo of the oil recovery member 180 is selected in consideration of the minimum space for drawing the electric wire to 101, the oil recovery member 180 with respect to the bottom diameter b of the oil recovery member 180 is selected. As the upper diameter a is varied, the height Lo of the oil recovery member 180 may also be varied.
- the stator 111 since the stator 111 is provided with a coil end 111b on the upper side of the core 111a, the stator 111 itself cannot be provided with an oil return port separately, and the rotor 112 and the rotating shaft ( The oil rising along 113 is only radially guided by the oil recovery member 180 and through the first, second and third oil recovery ports H1, H2, H3 as shown in FIG. 101 is recovered to the bottom surface.
- the first oil recovery port H1 is formed between the cylindrical hermetically sealed container 101 and the stator 111 having a polygonal appearance in contact with it, and six pieces are provided.
- the second oil recovery port H2 is a ring-shaped gap formed between the stator 111 and the rotor 112 to form mutual electromagnetic force.
- the third oil recovery port H3 is provided in the rotor 112 itself, and eight are provided.
- the first, second, and third oil recovery ports H1, H2, and H3 may be configured in a number of forms, but the second and third oil recovery ports H2 and H3 may be the stator 111 and the rotor 112.
- the size and number of the second and third oil recovery holes H2 and H3 are preferably limited in order to efficiently generate mutual electromagnetic force. Therefore, as the size and number of the second and third oil recovery ports H2 and H3 are limited, the oil may not be quickly recovered by the second and third oil recovery ports H2 and H3.
- the first oil recovery port H1 may be provided between the sealed container 101 and the stator 111 in various sizes and numbers. At this time, it is required to recover the oil more effectively in the rotary compressor whose cross-sectional area of the first, second and third oil recovery ports H1, H2 and H3 with respect to the cross-sectional area of the sealed container 101 is smaller than the set ratio. To this end, in the present invention, as described above, it is necessary to limit the size, ratio, installation position, etc. of the oil recovery member 180 and the end coil 111b to a limited value.
- FIG 9 is a graph showing the circulation rate of the refrigeration cycle according to the height ratio (Lo / Lc) of the oil recovery member to the height of the coil end in the rotary compressor of one embodiment of the present invention.
- the diameter of the sealed container is 112
- the area of one first oil recovery port is 7.8, the area of the second oil recovery port is 49.33, and the area of one third oil recovery port is 15.724.
- such a rotary compressor has a cross-sectional area (A2) ratio (A2 / A1) of the oil recovery flow path to the longitudinal area (A1) of the sealed container of 2.09%.
- Such a rotary compressor is applied to various types of refrigeration cycles such as a refrigerator or an air conditioner.
- the circulation rate of the refrigeration cycle is reduced, which means that the amount of oil leaving the rotary compressor is reduced. More specifically, if the height Lc of the coil end is 36 and the height Lo of the oil recovery member is changed to 0, 22, 36, 44, the oil recovery member relative to the height Lc of the coil end in the rotary compressor The ratio of Lo (Lo / Lc) is increased to 0, 0.61, 1.00, 1.22, and when the rotary compressor is applied to the refrigeration cycle, the circulation rate (%) of the refrigeration cycle is lowered to 2.3, 1.8, 1.2, 0.3. You lose.
- FIG. 10 is a graph showing the compression efficiency according to the diameter ratio (d2 / d1) of the oil recovery member to the inner diameter of the coil end in the rotary compressor of one embodiment of the present invention and the circulation rate of the refrigeration cycle to which it is applied.
- the graph shown in FIG. 10 shows that the diameter of the sealed container is 112, the area of the first oil recovery port is 7.8, the area of the second oil recovery port is 49.33, and the area of the third oil recovery port is 15.724.
- a rotary compressor has a cross-sectional area (A2) ratio (A2 / A1) of the oil recovery flow path to the longitudinal area (A1) of the sealed container of 2.09%.
- Such a rotary compressor is applied to a refrigeration cycle.
- the upper diameter (d2) ratio (d2 / d1) of the oil return member to the inner diameter (d1) of the end coil is increased, the vertically flowing oil flows in the radial direction.
- the oil circulation rate of the refrigeration cycle is reduced because the oil can be effectively recovered by dispersing oil, which means that the amount of oil flowing out of the rotary compressor is reduced.
- the ratio (d2 / d1) of the upper diameter (d2) of the oil recovery member to the inner diameter d1 of the end coil is excessively large, the oil recovery member may act as a flow path resistance that impedes the flow of oil, thereby Since the efficiency can be drastically reduced, the ratio of the upper diameter d2 of the oil recovery member d2 / d1 to the inner diameter d1 of the end coil is required to be appropriately defined.
- the rotary compressor has an inner diameter d1 of the end coil.
- the upper diameter (d2) ratio (d2 / d1) of the oil recovery member is increased to 0, 0.63, 1.00, 1.09, 1.19, and when such a rotary compressor is applied to the refrigeration cycle, the circulation rate (%) of the refrigeration cycle is 2.3, 1.8.
- the efficiency (EER) of the rotary compressor increases to 10.7, 10.7, 10.74, 10.64, and 10.40, and then decreases to 0.3, 0.2, and 0.1.
- the ratio of the upper diameter (d2) of the oil recovery member (d2) to the inner diameter (d1) of the end coil is selected to be 0.63 or more, and the efficiency (EER) of the rotary compressor is selected.
- the ratio d2 / d1 of the upper diameter d2 of the oil recovery member to the inner diameter d1 of the end coil is set to 1.19 or less. That is, even if the oil recovery member is installed inside the end coil in the rotary compressor, the oil recovery member is installed to protrude from the end coil and at the same time the ratio of the upper diameter (d2) of the oil recovery member to the inner diameter d1 of the end coil (d2 / d1).
- the oil is guided in the radial direction by hitting the oil recovery member even when the oil rises along the rotational axis and the rotor, and the flow of oil is the third and the third outermost diameter including the first and second oil recovery ports.
- the oil recovery port is guided so that the oil can be recovered through the first, second and third oil recovery ports.
- the higher the rotational speed of the rotor the greater the amount of oil pumped along the rotating shaft and the rotor, and the oil is guided more quickly by being hit by an oil recovery member that rotates with the rotor to recover the first, second and third oils. Get out of the sphere.
- FIG. 11 is a graph showing the compression efficiency according to the upper / lower diameter ratio (a / b) of the oil recovery member and the circulation rate of the refrigeration cycle to which it is applied in the rotary compressor of one embodiment of the present invention.
- the graph shown in FIG. 11 shows that the diameter of the sealed container is 112, the area of one first oil recovery port is 7.8, the area of the second oil recovery port is 49.33, and the area of one third oil recovery port is 15.724.
- a rotary compressor has a cross-sectional area (A2) ratio (A2 / A1) of the oil recovery flow path to the longitudinal area (A1) of the sealed container of 2.09%.
- a rotary compressor equipped with such a funnel-shaped oil recovery member is applied to various types of refrigeration cycles such as a refrigerator or an air conditioner, and the upper diameter (a) of the oil recovery member with respect to the bottom diameter (b) of the oil recovery member.
- the circulation rate of the refrigeration cycle decreases because the oil flows in a radial direction to disperse the vertically rising oil in a radial direction, thereby reducing the amount of oil exiting the rotary compressor. it means.
- the ratio (a / b) of the top diameter (a) of the oil recovery member to the bottom diameter (b) of the oil recovery member becomes excessively large, the oil flow will change as the oil recovery member drastically changes the flow direction of the oil.
- the ratio of the upper diameter (a) of the oil recovery member (a / b) to the lower diameter (b) of the oil recovery member may be limited by a suitable numerical limit because it can act as a flow path resistance of the rotary compressor, which can drastically reduce the efficiency of the rotary compressor. Required.
- the bottom diameter b of the oil recovery member is 20
- the top diameter a of the oil recovery member is varied to 56, 57, 58.9, 63, 70
- the height Lo of the oil recovery member is 22 , 33, 44, 44, 44
- the height (Lo) of the oil recovery member is changed in conjunction with the shape of the oil recovery member and the wire lead-out space as described above, so that the upper and lower diameters of the oil recovery member ( Even if a, b) is changed, the height Lo of the oil recovery member cannot be set above a certain maximum value.
- the ratio (a / b) of the upper diameter (a) of the oil recovery member to the lower diameter (b) of the oil recovery member in the rotary compressor is changed to 2.8, 2.85, 2.945, 3.15, 3.5, and the oil in the ratio
- the height (a / b + Lo) plus the height (Lo) of the recovery member is changed to 24.8, 35. 85, 46. 945, 47.15, and 47.5.
- the circulation rate of the refrigeration cycle (%) Is lowered to 1.8, 1.2, 0.3, 0.2, and 0.1
- the efficiency (EER) of the rotary compressor rises to 10.7, 10.75, 10.74, 10.64, and 10.40 and then lowers.
- the ratio (a) of the upper diameter (a) of the oil recovery member to the lower diameter (b) of the oil recovery member is 2.85 or more and at the same time the oil recovery member It is preferable that the value (a / b + Lo) plus the height Lo of is selected to be 35.85 or more. Further, in consideration of the efficiency (EER) of the rotary compressor, the ratio (a / b) of the upper diameter (a) of the oil recovery member to the lower diameter (b) of the oil recovery member is 3.5 or less and the ratio of the oil recovery member It is preferable that the value a / b + Lo plus the height Lo is selected to be 47.5 or less.
- the oil recovery member is installed inside the coil end in the rotary compressor, the oil recovery member is installed to protrude from the coil end, and the upper and lower diameters (a, b) and the height (Lo) of the oil recovery member are adjusted appropriately.
- the flow path is formed, even if the oil rises along the rotating shaft and the rotor, the oil hits the oil recovery member to be guided in the radial direction, and the flow of oil is guided to the third oil recovery port located at the outermost diameter, including the first and second oil recovery ports. It can be recovered through the first, second, third oil recovery port.
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Abstract
Description
Claims (31)
- 축방향으로 하부에서 상부로 갈수록 직경이 넓게 형성된 통형 본체; 그리고,본체의 상단에 반경 방향으로 확장된 가이드부;를 포함하되,본체의 하부 직경(b)에 대한 가이드부의 직경(a) 비율은 2.85 이상을 유지하는(a/b≥2.85) 것을 특징으로 하는 오일 회수 부재.
- 제1항에 있어서,본체의 하부 직경(b)에 대한 가이드부의 직경(a) 비율은 3.15 이하를 유지하는(a/b≤3.15) 것을 특징으로 하는 오일 회수 부재.
- 제1항 또는 제2항에 있어서,상기 비율(a/b)에 축방향 높이(Lo)를 더한 값(a/b+Lo)이 35.85 이상을 유지하는(a/b+Lo≥35.85) 것을 특징으로 하는 오일 회수 부재.
- 제1항 또는 제2항에 있어서,상기 비율(a/b)에 축방향 높이(Lo)를 더한 값(a/b+Lo)이 47.5 이하를 유지하는 (a/b+Lo≤47.5)것을 특징으로 하는 오일 회수 부재.
- 오일에 하단이 담겨지는 회전축;회전축의 외주면에 맞물리는 로터;로터의 외주면에 간극을 유지하도록 설치되고, 코일이 코어에 권선됨에 따라 상부에 코일 엔드가 구비된 스테이터; 그리고,로터의 중심에 결합되고, 회전축의 회전에 의해 상승하는 오일을 반경방향으로 안내하기 위하여 축방향으로 높이(Lo)가 코일 엔드의 축방향 높이(Lc)보다 높은 오일 회수 부재;를 포함하는 것을 특징으로 하는 전동기구.
- 제5항에 있어서,코일 엔드의 내경(d1)에 대한 오일 회수 부재의 상단 직경(d2) 비율(d2/d1)은 오일 회수율을 높이기 위하여 0.63 이상을 유지하는 것을 특징으로 하는 전동기구.
- 제6항에 있어서,코일 엔드의 내경(d1)에 대한 오일 회수 부재의 상단 직경(d2) 비율(d2/d1)은 유로 저항을 줄이기 위하여 1.19 이하를 유지하는 것을 특징으로 하는 전동기구.
- 제7항에 있어서,오일 회수 부재는 축방향으로 하부에서 상부로 갈수록 직경이 넓게 형성된 원통형 본체와, 본체의 상단에 반경 방향으로 확장된 가이드부로 이루어지고,오일 회수 부재의 상단 직경(d2)은 가이드부의 직경인 것을 특징으로 하는 전동기구.
- 제5항에 있어서,오일 회수 부재의 하단 직경(b)에 대한 오일 회수 부재의 상단 직경(a) 비율은 오일 회수율을 높이기 위하여 2.85 이상을 유지하는(a/b≥2.85) 것을 특징으로 하는 전동기구.
- 제5항에 있어서,오일 회수 부재의 하단 직경(b)에 대한 오일 회수 부재의 상단 직경(a) 비율은 유로 저항을 줄이기 위하여 3.15 이하를 유지하는(a/b≤3.15) 것을 특징으로 하는 전동기구.
- 제9항에 있어서,상기 비율(a/b)에 오일 회수 부재의 축방향 높이(Lo)를 더한 값(a/b+Lo)이 35.85 이상을 유지하는(a/b+Lo≥35.85) 것을 특징으로 하는 전동기구.
- 제10항에 있어서,상기 비율(a/b)에 오일 회수 부재의 축방향 높이(Lo)를 더한 값(a/b+Lo)이 47.5 이하를 유지하는(a/b+Lo≤47.5) 것을 특징으로 하는 전동기구.
- 제9항 내지 제12항 중 어느 한 항에 있어서,오일 회수 부재는 축방향으로 하부에서 상부로 갈수록 직경이 넓게 형성된 통형 본체와, 본체의 상단에 반경 방향으로 확장된 가이드부로 이루어지고,오일 회수 부재의 상단 직경(a)은 가이드부의 직경이고,오일 회수 부재의 하단 직경(b)은 본체의 하부 직경인 것을 특징으로 하는 전동기구.
- 냉매가 유출입되고, 오일이 바닥면에 저장된 밀폐용기;밀폐용기 내측 하부에 고정되고, 냉매를 압축시키는 압축기구부;밀폐용기 내측 상부에 고정되고, 압축기구부에 동력을 공급하는 전동기구부; 그리고,전동기구부의 중심에 결합되고, 전동기구부의 작동에 의해 전동기구부를 따라 상승하는 오일을 반경방향으로 안내하는 오일 회수 부재;를 포함하되,오일 회수 부재의 상단이 축방향으로 전동기구부의 상단보다 높게 설치된 것을 특징으로 하는 압축기.
- 제14항에 있어서,전동기구부는 회전축과, 로터와, 코일이 코어에 권선됨에 따라 상부에 코일 엔드가 구비된 스테이터로 이루어지고,오일 회수 부재는 오일 회수 부재의 축방향 높이(Lo)가 코일 엔드의 축방향 높이(Lc) 이상을(Lo≥Lc) 유지하도록 로터의 중심에 결합된 것을 특징으로 하는 압축기.
- 제14항에 있어서,전동기구부는 회전축과, 로터와, 코일이 코어에 권선됨에 따라 상부에 코일 엔드가 구비된 스테이터로 이루어지고,오일 회수 부재의 축방향 높이(Lo)는 코일 엔드의 축방향 높이(Lc)에 전선 인출 공간의 축방향 높이(f)를 합한 값 이하인(Lo≤Lc+f) 것을 특징으로 하는 압축기.
- 제16항에 있어서,전선 인출 공간은 전선이 코일 엔드로부터 밀폐용기로 인출하는 작업을 위해 요구되는 최소한의 공간인 것을 특징으로 하는 압축기.
- 제14항 내지 제17항 중 어느 한 항에 있어서,오일회수부재에 부딪힌 오일을 밀폐용기 하부로 회수되도록 하는 복수개의 오일 회수구를 더 포함하되,밀폐용기의 단면적(A1)에 대한 오일 회수구들의 단면적(A2)에 대한 비율(A2/A1)이 3% 이하인 것을 특징으로 하는 압축기.
- 제18항에 있어서,오일 회수구들은 밀폐용기와 스테이터 사이에 구비된 복수개의 제1오일 회수구와, 로터와 스테이터 사이의 간극인 제2오일 회수구와, 로터 자체에 구비된 복수개의 제3오일 회수구 중 적어도 하나 이상을 포함하는 것을 특징으로 하는 압축기.
- 제14항에 있어서,전동기부는 압축기구부에 연결된 회전축과, 회전축의 외주면에 맞물리는 원통형 로터와, 로터의 외주면에 간극을 유지하도록 밀폐용기에 고정되고, 코일이 코어에 권선됨에 따라 코일 엔드가 상부에 구비된 원통형 스테이터를 포함하되,코일 엔드의 내경(d1)에 대한 오일 회수 부재의 상단 직경(d2) 비율(d2/d1)은 오일 회수율을 높이기 위하여 0.63 이상을 유지하는 것을 특징으로 하는 압축기.
- 제20항에 있어서,코일 엔드의 내경(d1)에 대한 오일 회수 부재의 상단 직경(d2) 비율(d2/d1)은 유로 저항을 줄이기 위하여 1.19 이하를 유지하는 것을 특징으로 하는 압축기.
- 제21항에 있어서,오일 회수 부재는 축방향으로 하부에서 상부로 갈수록 직경이 넓게 형성된 원통형 본체와, 본체의 상단에 반경 방향으로 확장된 가이드부로 이루어지고,오일 회수 부재의 상단 직경(d2)은 가이드부의 직경인 것을 특징으로 하는 압축기.
- 제20항 내지 제22항 중 어느 한 항에 있어서,오일회수부재에 부딪힌 오일을 밀폐용기 하부로 회수되도록 하는 복수개의 오일 회수구를 더 포함하되,밀폐용기의 단면적(A1)에 대한 오일 회수구들의 단면적(A2)에 대한 비율(A2/A1)이 3.03.0하인 것을 특징으로 하는 압축기.
- 제23항에 있어서,오일 회수구들은 밀폐용기와 스테이터 사이에 구비된 복수개의 제1오일 회수구와, 로터와 스테이터 사이의 간극인 제2오일 회수구와, 로터 자체에 구비된 복수개의 제3오일 회수구 중 적어도 하나 이상을 포함하는 것을 특징으로 하는 압축기.
- 제14항에 있어서,오일 회수 부재의 하단 직경(b)에 대한 오일 회수 부재의 상단 직경(a) 비율은 오일 회수율을 높이기 위하여 2.85 이상을 유지하는(a/b≥2.85) 것을 특징으로 하는 압축기.
- 제25항에 있어서,오일 회수 부재의 하단 직경(b)에 대한 오일 회수 부재의 상단 직경(a) 비율은 유로 저항을 줄이기 위하여 3.15 이하를 유지하는(a/b≤3.15) 것을 특징으로 하는 압축기.
- 제25항에 있어서,상기 비율(a/b)에 오일 회수 부재의 축방향 높이(Lo)를 더한 값(a/b+Lo)이 35.85 이상을 유지하는(a/b3+Lo≥35.85) 것을 특징으로 하는 압축기.
- 제26항에 있어서,상기 비율(a/b)에 오일 회수 부재의 축방향 높이(Lo)를 더한 값(a/b+Lo)이 47.5 이하를 유지하는(a/b+Lo≤47.5) 것을 특징으로 하는 압축기.
- 제25항 내지 제28항 중 어느 한 항에 있어서,오일 회수 부재는 축방향으로 하부에서 상부로 갈수록 직경이 넓게 형성된 통형 본체와, 본체의 상단에 반경 방향으로 확장된 가이드부를 포함하고,오일 회수 부재의 상단 직경(a)은 가이드부의 직경이고,오일 회수 부재의 하단 직경(b)은 본체의 하부 직경인 것을 특징으로 하는 압축기.
- 제25항 내지 제28항 중 어느 한 항에 있어서,오일회수부재에 부딪힌 오일을 밀폐용기 하부로 회수되도록 하는 복수개의 오일 회수구를 더 포함하되,밀폐용기의 단면적(A1)에 대한 오일 회수구들의 단면적(A2)에 대한 비율(A2/A1)이 3% 이하인 것을 특징으로 하는 압축기.
- 제30항에 있어서,전동기구부는 밀폐용기 내측면에 고정된 스테이터와, 스테이터 내측에 회전 가능하게 설치된 로터로 이루어지고,오일 회수구들은 오일 회수구들은 밀폐용기와 스테이터 사이에 구비된 복수개의 제1오일 회수구와, 로터와 스테이터 사이의 간극인 제2오일 회수구와, 로터 자체에 구비된 복수개의 제3오일 회수구 중 적어도 하나 이상을 포함하는 것을 특징으로 하는 압축기.
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
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EP09800596.0A EP2317146B1 (en) | 2008-07-25 | 2009-07-27 | Oil recovery member, and motor mechanism and compressor using the same |
US13/055,667 US8864480B2 (en) | 2008-07-25 | 2009-07-27 | Oil recovery member, and motor mechanism and compressor using the same |
CN200980128715.2A CN102105692B (zh) | 2008-07-25 | 2009-07-27 | 机油回收部件及采用该部件的电动机构和压缩机 |
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KR10-2008-0073176 | 2008-07-25 | ||
KR1020080073176A KR101406521B1 (ko) | 2008-07-25 | 2008-07-25 | 전동기구 및 이를 적용한 압축기 |
KR10-2008-0073175 | 2008-07-25 | ||
KR1020080073175A KR101474019B1 (ko) | 2008-07-25 | 2008-07-25 | 전동기구 및 이를 적용한 압축기 |
KR10-2008-0076698 | 2008-08-05 | ||
KR1020080076698A KR101406509B1 (ko) | 2008-08-05 | 2008-08-05 | 오일 회수 부재 및 이를 적용한 전동기구와 압축기 |
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US (1) | US8864480B2 (ko) |
EP (1) | EP2317146B1 (ko) |
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CN103644119B (zh) * | 2008-07-25 | 2016-12-07 | Lg电子株式会社 | 电动机构和压缩机 |
CN102748298B (zh) * | 2012-06-13 | 2015-05-20 | 珠海格力电器股份有限公司 | 一种旋转压缩机吸气结构 |
CN104989619A (zh) * | 2015-06-07 | 2015-10-21 | 深圳市沃森空调技术有限公司 | 涡旋转子式双级空调压缩机 |
CN105090043B (zh) * | 2015-09-17 | 2017-06-16 | 广东美芝制冷设备有限公司 | 旋转式压缩机 |
CN105971849A (zh) * | 2016-06-27 | 2016-09-28 | 重庆赋昇汽车零部件有限公司 | 压缩机油分离装置 |
KR20200054785A (ko) * | 2018-11-12 | 2020-05-20 | 엘지전자 주식회사 | 압축기 |
EP3650699B1 (en) * | 2018-11-12 | 2024-03-06 | LG Electronics Inc. | Compressor |
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Publication number | Publication date |
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CN103644119A (zh) | 2014-03-19 |
EP2317146B1 (en) | 2017-08-30 |
EP2317146A4 (en) | 2011-12-07 |
CN102105692B (zh) | 2015-05-13 |
US8864480B2 (en) | 2014-10-21 |
CN102105692A (zh) | 2011-06-22 |
US20110158840A1 (en) | 2011-06-30 |
EP2317146A1 (en) | 2011-05-04 |
CN103644119B (zh) | 2016-12-07 |
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