KR20150021443A - Hermetic compressor and refrigerator using the same - Google Patents

Hermetic compressor and refrigerator using the same Download PDF

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Publication number
KR20150021443A
KR20150021443A KR20140076497A KR20140076497A KR20150021443A KR 20150021443 A KR20150021443 A KR 20150021443A KR 20140076497 A KR20140076497 A KR 20140076497A KR 20140076497 A KR20140076497 A KR 20140076497A KR 20150021443 A KR20150021443 A KR 20150021443A
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KR
South Korea
Prior art keywords
insertion member
crankshaft
hermetic compressor
gap
lubricating oil
Prior art date
Application number
KR20140076497A
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Korean (ko)
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KR101646044B1 (en
Inventor
미나코 가나다
히로카츠 고소카베
슈헤이 나가타
마사카즈 가노
Original Assignee
히타치 어플라이언스 가부시키가이샤
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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
    • F04B39/0027—Pulsation and noise damping means
    • 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
    • F04B39/0094—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 crankshaft
    • 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
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • F04B39/0261—Hermetic compressors with an auxiliary oil pump
    • 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
    • F04B39/0284—Constructional details, e.g. reservoirs in the casing
    • F04B39/0292—Lubrication of pistons or cylinders
    • 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
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/121—Casings
    • 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
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/122—Cylinder block
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B5/00—Joining sheets or plates, e.g. panels, to one another or to strips or bars parallel to them
    • F16B5/02—Joining sheets or plates, e.g. panels, to one another or to strips or bars parallel to them by means of fastening members using screw-thread
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/12—Kind or type gaseous, i.e. compressible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/96—Preventing, counteracting or reducing vibration or noise
    • F05B2260/962—Preventing, counteracting or reducing vibration or noise by means creating "anti-noise"
    • 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
    • Y10S417/00—Pumps

Abstract

An objective of the present invention is to provide a hermetic compressor improving a fueling performance in case of low speed operation to reduce sliding loss; and a refrigerator using the same. To achieve the objective, provided is a hermetic compressor which includes a compression element 930 and an electric element (2) inside a hermetic container (1); a crank shaft (8) rotating the electric element (2); lubricating oil (4) stored in a lower portion of the hermetic container (1); a lower cylindrical portion (8g) of the crank shaft (8); a cylindrical member (19) indented inside the lower cylindrical portion (8g); and an insertion member (20) between an inner wall of the lower cylindrical portion (8g) and an outer wall of the cylindrical member (19), wherein the length of a diametric interval between the lower cylindrical portion (8g) and the insertion member (20) is different from the length of a diametric interval between the cylindrical member (19) and the insertion member (20).

Description

TECHNICAL FIELD [0001] The present invention relates to a hermetic compressor and a refrigerator using the hermetic compressor.

The present invention relates to a hermetic compressor and a refrigerator using the hermetic compressor.

BACKGROUND ART [0002] Conventionally, in a hermetically sealed compressor of small capacity which is used in a domestic refrigerator, the insulation performance of a refrigerator has been improved, and a low speed operation of the compressor by inverter control has been promoted. In order to improve the efficiency of the hermetic compressor for a refrigerator and to improve the reliability of the sliding portion, it is required to supply stable lubricating oil to the sliding portion at low speed operation. A structure for supplying sufficient lubricating oil at a low speed operation of a hermetic compressor is provided with a viscous pump which is capable of obtaining a stable pump performance even at a low speed operation instead of a centrifugal pump.

For example, Japanese Laid-Open Patent Publication No. 1-180796 (Patent Document 1) has an insertion portion that is rotatably inserted coaxially in a cylindrical hollow portion formed in a shaft, And a helical groove is provided in a direction in which the lubricating oil rises, thereby performing a function as a viscous pump. A centrifugal pump is installed at the top of the viscous pump.

[Patent Document 1] Japanese Patent Application Laid-Open No. 2012-180796

However, in Patent Document 1, a centrifugal pump is provided on the upper part of the viscous pump in order to reduce the sliding loss. The lubricating oil raised by the viscous pump reaches the centrifugal pump through the supply port provided at the center of the shaft. In this configuration, since the lubricating oil is subjected to centrifugal force, the amount of lubricating oil passing through the oil filler at the center of the shaft is small.

Thus, the present invention provides a hermetic compressor in which sliding performance is improved by improving lubrication performance during low-speed operation, and a refrigerator using the hermetic compressor.

In order to solve the above problems, for example, the configuration described in the claims is adopted. The present invention includes a plurality of means for solving the above-mentioned problems. For example, the present invention can be applied to a compressor having a compression element and an electric element in a hermetically sealed container, a crankshaft rotating by the electric element, A cylindrical member which is press-fitted into the lower cylindrical portion, and an insertion member which is located inside the cylindrical member, the lower cylindrical portion of the crankshaft and the insertion member The gap in the radial direction and the gap in the radial direction of the cylindrical member and the insertion member are different from each other.

According to the present invention, it is possible to provide a hermetic compressor having reduced sliding loss by improving lubrication performance during low-speed operation, and a refrigerator using the hermetic compressor.

1 is a longitudinal sectional view of a hermetic compressor according to a first embodiment of the present invention.
2 is a cross-sectional view of a hermetic compressor equivalent to the cross-section AA in Fig.
Fig. 3 is an enlarged view of the main part schematically showing the lubricating mechanism according to the present embodiment. Fig.
Fig. 4 is an enlarged cross-sectional view showing the essential parts of the lubricant supply mechanism according to the present embodiment. Fig.
Fig. 5 is an enlarged cross-sectional view showing a substantial part of a cross-sectional structure of a crankshaft according to the present embodiment. Fig.
Fig. 6 is an enlarged cross-sectional view showing a substantial part of a shaft according to a second embodiment of the present invention; Fig.
FIG. 7 is an enlarged cross-sectional view of a substantial part of a shaft according to a third embodiment of the present invention. FIG.
8 is a calculation result of the amount of oil supply when the diameter gap between the cylindrical member 19 and the insertion member 20 is changed.
9 is a longitudinal sectional view of a refrigerator in which a hermetic compressor according to the present embodiment is mounted.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.

[Example 1]

Hereinafter, a first embodiment of the present invention will be described in detail with reference to Figs. 1 to 5. Fig. 1 and 2, the overall configuration of the hermetic compressor will be described. FIG. 1 is a longitudinal sectional view of a hermetic compressor according to a first embodiment of the present invention, and FIG. 2 is a top view of the hermetic compressor of FIG.

The hermetic compressor 50 of the present embodiment houses the electric element 2 comprising the stator 2a and the rotor 2b and the compression element 3 in the hermetic container 1. The compression element 3 is formed in such a manner that the radial bearing 5c and the frame portion 5b are inserted into the cylinder 5 formed in the cylinder block 5 integrally with the eccentric portion of the crankshaft 8 Called reciprocal type in which the piston 7 connected to the shaft 8b reciprocates. The lower portion of the crankshaft 8 is rotatably fitted in the radial bearing 5c of the cylinder block 5 and the crankshaft 8 is fixed to the rotor 2b at the lower portion of the crankshaft 8. [ The compression element 3 is elastically supported at the bottom of the closed container 1 by a coil spring via a stator 2a fixed to the lower portion of the frame portion 5b. The crankshaft 8 is rotated by the rotation of the rotor 2b and the eccentric shaft 8b is eccentrically rotated so that the piston 7 reciprocates in the cavity in the cylinder 5a.

The cavity in the cylinder 5a is closed by the cylinder head 10 in which the intake valve and the discharge valve (not shown) are assembled and constitutes the compression working chamber 12 with the piston 7. A head cover 11 having a discharge chamber 11a formed therein is fixed to the cylinder block 5 by fastening bolts 13 at four positions in the cylinder head 10. The intake silencer 15 attenuates the pressure pulsation of the working fluid in the suction path to reduce noise and is located above the frame portion 5b of the cylinder block 5. [

Next, the refrigerant path inside the compressor will be described.

The refrigerant introduced through the suction pipe 14 connected to the hermetically sealed container 1 passes through the suction silencer 15 made of plastic and flows from the suction valve of the cylinder head 10 to the compression operation of the cylinder 5a And enters the chamber 12. In the compression operating chamber 12, the refrigerant is sucked and compressed by the reciprocating movement of the piston 7, and is discharged from the discharge valve. The compressed refrigerant enters the discharge chamber (not shown) in the head cover 11 from the discharge valve of the cylinder head 10 and passes through the discharge siren 16 formed integrally with the cylinder block 5 from the discharge chamber , And is discharged from the discharge pipe (18) through the discharge pipe (17) as an external refrigeration cycle.

Next, the fuel supply mechanism which is a feature of the present embodiment will be described in detail with reference to Figs. 2 to 5. Fig. 3 is a sectional view of the crankshaft and the oil supply mechanism under the crankshaft according to the present embodiment, and Fig. 4 is a cross-sectional view of the oil supply mechanism according to this embodiment. Fig. Fig. 3 is an enlarged cross-sectional view showing a substantial part of the cross-sectional structure of the lower portion of the crankshaft.

According to the present embodiment, the compression element has a crankshaft 8 for rotating and a cylindrical member 19 press-fitted into the lower cylindrical portion 8g formed in the lower portion of the shaft 8. The insertion member 20 is inserted into the cylindrical member 19.

The insertion member 20 is made of, for example, a resin such as polyphenylene sulfide resin (PPS). The outer surface of the insertion member 20 has a helical groove 20b through which lubricating oil passes. The cross-sectional area of the helical groove 20b is a trapezoid in consideration of easiness of machining. The insertion member 20 has a convex portion 20a having a hole in its bottom surface and the wire 21 is passed through the hole and arranged in the stator 2a. Accordingly, the insertion member 20 does not rotate integrally with the crankshaft 8 even when the crankshaft 8 rotates.

When the compressor starts, the crankshaft 8 rotates with the rotation of the rotor (not shown). The rotation of the crankshaft 8 causes the cylindrical member 19 and the insertion member 20 to move in the axial direction due to the speed difference generated in the cylindrical member 19 and the insertion member 20 pushed into the lower portion of the crankshaft 8, And the lubricant passes through the gap between the insertion member 20 and the cylindrical member 19 along the helical groove 20b on the outer surface of the insertion member 20 to be guided to the crankshaft 8 .

The lubricating oil that has risen inside the crankshaft 8 is conveyed to the communicating hole 8c with the crankshaft outer surface provided at the center of the crankshaft 8. [

The lubricating oil that has reached the gap between the outer surface of the crankshaft and the radial bearing 5c through the communication hole 8c acts on the crankshaft outer surface and the radial bearing 5c by a speed difference. The lubricating oil is guided to the upper side of the crankshaft along the helical groove 8e on the outer surface of the crankshaft by the viscous force. Thereafter, the lubricating oil passes through the communication hole 8f on the outer surface of the crankshaft and enters the inside of the crankshaft 8 again. The lubricating oil which has entered the crankshaft 8 is guided upward through the helical groove 8c formed on the outer periphery of the crankshaft 8 and is guided to the piston 6 7) are connected to each other. (Not shown) provided in such a manner as to partially penetrate a balance weight (not shown) attached to the upper end of the eccentric shaft 8b and finally to the periphery from the upper end of the eccentric shaft 8b . Lubricating and sealing between the piston 7 and the cylinder 5a is mainly performed by the lubricating oil 4 injected.

If the gap between the cylindrical member 19 through which the lubricant passes and the insertion direction of the insertion member 20 is too small, a partial contact with the cylindrical member 19 is caused by the slight eccentricity of the insertion member 20 There is a possibility that the sliding loss becomes large. On the contrary, if the gap between the cylindrical member 19 and the insertion member 20 is excessively large, the leakage amount flowing backward in the axial direction through the gap between the cylindrical member 19 and the insertion member 20 increases. If the leakage amount increases, the supply amount of the lubricating oil to the upper portion of the crankshaft 8 is reduced, and there is a possibility that the lubricating oil in the sliding portion in the compressor can not be sufficiently lubricated.

However, according to the present embodiment, the gap in the radial direction between the lower cylindrical portion 8g of the lower end portion of the crankshaft 8 and the insertion member 20 is reduced, Is set to be larger than the gap in the radial direction of the insertion member (19) and the insertion member (20).

8 is a calculation result of the amount of oil supply flow when the diameter gap between the cylindrical member 19 and the insertion member 20 is changed. The diameter gap between the cylindrical member 19 and the insertion member 20 is set to 0.1 mm to 0.5 mm on the basis of the results of the experiments in Fig. 8 and the hermetic compressor.

In addition, when the insertion member 20 is long, the inner wall of the crankshaft 8 and the sliding area increase. Further, while the convex portion of the helical groove 20b on the outer surface of the insertion member blocks the communication hole 8c, the path to the communication hole 8c is narrowed by the insertion member 20, so that the lubricant does not easily pass through.

However, according to the present embodiment, the upper end of the insertion member 20 has the same height as the communication hole 8c through which the lubricating oil passes, or a length located below the communication hole 8c. As a result, the inner wall of the crankshaft 8 and the sliding area of the insertion member 20 are prevented from becoming larger than necessary. The lubricating oil raised along the helical groove 20b of the insertion member 20 can easily reach the communication hole 8c without being blocked by the insertion member 20 in the lubricant path.

As described above, according to the hermetic compressor of the first embodiment, the compression element 3 and the electric element 2 in the hermetically sealed container 1, the crankshaft 8 which rotates by the electric element 2, And a lubricating oil 4 stored in the lower part of the hermetically sealed container 1. The lower cylindrical portion 8g of the crankshaft 8 and the cylindrical member 19 press-fitted into the lower cylindrical portion 8g, And an insertion member 20 between the inner wall of the lower cylindrical portion 8g and the outer wall of the cylindrical member 19. The gap between the lower cylindrical portion 8g and the insertion member 20 in the radial direction, The radial clearance between the cylindrical member 19 and the insertion member 20 is different.

Accordingly, it is possible to provide sufficient lubricity to the sliding portion even at low-speed operation with a low-cost and simple structure, thereby reducing the sliding loss and improving the efficiency and reliability of the compressor.

[Example 2]

Next, the structure of the hermetic compressor according to the second embodiment will be described with reference to Fig.

The present embodiment differs from the first embodiment in that a helical groove 8f is formed on the inner surface of the crankshaft 8 and a helical groove 19a is formed on the inner surface of the cylindrical member, . In addition, like the first embodiment, the cylinder member 19 is attached to the lower end of the crankshaft 8. [

A viscous force is generated by the speed difference between the outer surface of the insertion member 20 and the inner surface of the crankshaft 8 together with the rotation of the crankshaft 8. [ The lubricating oil in the gap between the insertion member 20 and the crankshaft 8 rises through the helical groove 8f on the inner surface of the crankshaft 8 due to the generated viscous force.

The gap between the crankshaft 8 (lower cylindrical portion 8g) and the insertion member 20 and the gap between the cylindrical member 19 and the insertion member 20 are different from each other. As a result, the crankshaft 8 (the lower cylindrical portion 8g) and the crankshaft 8 can be prevented from coming into contact with the cylindrical member 19 and the crankshaft 8, The leakage of the oil from the gap of the insertion member 20 and the gap between the cylindrical member 19 and the insertion member 20 can be prevented.

Accordingly, it is possible to provide sufficient lubricity to the sliding portion even at a low-speed operation with a low-cost and simple structure, and the efficiency and reliability of the compressor can be improved by reducing the sliding loss.

[Example 3]

Next, the structure of the hermetic compressor according to the third embodiment will be described with reference to Fig.

The present embodiment is different from the first embodiment in that a cylindrical member 19 is press-fitted into the outer surface of the lower end of the crankshaft 8,

The insertion member 20 at the lower end of the crankshaft 8 enlarges the diameter of the portion where the cylindrical member 19 is press-fitted so that the size of the gap between the insertion member 20 and the cylindrical member 19 is adjusted .

A viscous force is generated by the speed difference between the outer surface of the insertion member 20 and the inner surface of the crankshaft 8 (the lower cylindrical portion 8g) together with the rotation of the crankshaft 8. The lubricating oil in the gap between the insertion member 20 and the crankshaft 8 rises through the spiral groove on the outer surface of the crankshaft 8 due to the generated viscous force.

The gap between the crankshaft 8 (lower cylindrical portion 8g) and the insertion member 20 is different from the gap between the cylindrical member 19 and the insertion member 20, And the oil from the gap between the crankshaft 8 and the insertion member 20 and the gap between the cylindrical member 19 and the insertion member 20 while preventing partial abutment between the crankshaft 8 and the insertion member 20, Leakage can be prevented.

Further, in the present embodiment, since the diameter of the lubricating oil path under the insertion member 20 is enlarged, centrifugal force is likely to act on the lubricating oil.

As a result, the lubricating oil effectively rises inside the crankshaft. Accordingly, it is possible to provide sufficient lubrication to the sliding portion even at a low-speed operation with a low-cost and simple structure, and the efficiency and reliability of the compressor can be improved by reducing the sliding loss.

8 is a longitudinal sectional view of a refrigerator equipped with a hermetic compressor according to the first to third embodiments.

8, the hermetic compressor 50 of the present embodiment is mounted on a refrigerator 60 using a natural refrigerant R600a having a cooler 66 and having a small warming coefficient. The refrigerating compartment 62, the upper freezing chamber 63, The lower freezing chamber 64 and the vegetable chamber 65 is cooled by operating a refrigerating cycle (not shown) by driving the hermetic compressor 50. [

BACKGROUND ART [0002] In recent years, lowering of the rotation speed of a compressor is progressing due to mounting of inverter control and improvement of heat insulation performance of a refrigerator. However, lowering the speed of rotation of the compressor may lead to a decrease in the lubrication ability.

In the embodiments described in detail above, the lubricating oil can be efficiently and stably lifted at both the low speed operation and the high speed operation in the rotation speed control compressor, and the lubricating oil can be sufficiently lubricated in the sliding portion to improve the compressor efficiency And also to provide a hermetic compressor improved in reliability of the compressor.

In addition, the system to which the hermetic compressor is applied is not limited to a refrigerator, but may be applied to a system such as a room air conditioner or a refrigerator in a refrigeration and air conditioning system, and system efficiency of such a device can be greatly improved.

In addition, the present invention is not limited to the above-described embodiment, but includes various modifications. For example, the above-described embodiments have been described in detail in order to explain the present invention easily, and are not limited to the above-described embodiments. It is also possible to replace some of the configurations of the embodiments with the configurations of other embodiments. In addition, it is possible to add, delete, or substitute another configuration with respect to a part of the configuration of each embodiment.

One… Airtight container, 2 ... Electric element, 2a ... Stator, 2b ... Rotor, 3 ... Compression element, 4 ... Lubricants, 5a ... Cylinder, 7 ... Piston, 8 ... Crankshaft, 8a ... Eccentric shaft, 8b ... Communication hole, 8c ... Spiral groove, 8d ... Communication hole, 8e ... Pin section, 8f ... Spiral groove, 8g ... A lower cylindrical portion, 19 ... A cylindrical member, 19a ... Spiral groove, 20 ... Insertion member, 20a ... Convex portion, 20b ... Spiral groove, 21 ... Wire, 50 ... Hermetic compressor, 60 ... Refrigerator

Claims (5)

A compression element and an electric element in the hermetically sealed container, a crankshaft rotating by the electric element, and a lubricating oil stored in a lower portion of the hermetically sealed container,
A lower cylindrical portion of the crankshaft,
A cylindrical member press-fitted into the lower cylindrical portion,
And an insertion member inside the cylindrical member,
Wherein the gap between the lower cylindrical portion and the insertion member in the radial direction and the gap between the cylindrical member and the insertion member in the radial direction are different sizes. The method according to claim 1,
And the gap between the lower cylindrical portion and the insertion member in the radial direction is 0.1 to 0.5 mm. The method according to claim 1,
Wherein an upper end of the insertion member is at the same height as the communication hole in the side portion of the crankshaft or is located below the through hole. 4. The method according to any one of claims 1 to 3,
And the outer surface of the insertion member has a spiral groove as a lubricating oil path, and the cross-section of the spiral groove is a trapezoid. A refrigerator comprising the hermetic compressor according to claim 1.
KR1020140076497A 2013-08-20 2014-06-23 Hermetic compressor and refrigerator using the same KR101646044B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JPJP-P-2013-170049 2013-08-20
JP2013170049A JP6138625B2 (en) 2013-08-20 2013-08-20 Hermetic compressor and refrigerator using the same

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KR20150021443A true KR20150021443A (en) 2015-03-02
KR101646044B1 KR101646044B1 (en) 2016-08-05

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019017604A1 (en) * 2017-07-19 2019-01-24 Samsung Electronics Co., Ltd. Hermetic compressor

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115234473B (en) * 2022-07-18 2023-07-18 珠海格力电器股份有限公司 Compressor crankshaft, compressor and refrigeration equipment

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