US20060204373A1 - Hermetic compressor - Google Patents

Hermetic compressor Download PDF

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Publication number
US20060204373A1
US20060204373A1 US10/544,339 US54433905A US2006204373A1 US 20060204373 A1 US20060204373 A1 US 20060204373A1 US 54433905 A US54433905 A US 54433905A US 2006204373 A1 US2006204373 A1 US 2006204373A1
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Prior art keywords
piston
hermetic compressor
axis part
cylinder
oil
Prior art date
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Abandoned
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US10/544,339
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English (en)
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Kosuke Tsuboi
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Panasonic Corp
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Individual
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Assigned to MATSUSHITA ELECTRIC INDUSTRIAL CO., LTD. reassignment MATSUSHITA ELECTRIC INDUSTRIAL CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: TSUBOI, KOSUKE
Publication of US20060204373A1 publication Critical patent/US20060204373A1/en
Assigned to PANASONIC CORPORATION reassignment PANASONIC CORPORATION CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: MATSUSHITA ELECTRIC INDUSTRIAL CO., LTD.
Abandoned legal-status Critical Current

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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
    • F04B39/0005—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 adaptations of pistons
    • 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
    • F04B39/0215—Lubrication characterised by the use of a special lubricant
    • 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
    • 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
    • F04B39/0238—Hermetic compressors with oil distribution channels
    • 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
    • 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
    • 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
    • Y10S417/902—Hermetically sealed motor pump unit
    • 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
    • Y10S62/00—Refrigeration
    • Y10S62/02—Refrigerant pumps

Definitions

  • the present invention relates to a hermetic compressor used in refrigeration cycles for such as a refrigerator with freezer.
  • FIG. 8 is a perspective view of a piston used for the conventional hermetic compressor described in document 1.
  • piston 1 includes: sealing surface 3 formed on outer circumferential surface 2 so as to contact the inner circumferential surface of the cylinder; at least two guide surfaces 4 formed on outer circumferential surface 2 so as to contact a part of the inner circumferential surface of the cylinder, and also extending roughly in parallel with the direction of movement of piston 1 ; and cut portion 5 that does not contact the inner circumferential surface of the cylinder, characterized that the angle 4 ab formed with the two lines connecting two boundary edges 4 a and 4 b of guide surface 4 , to cylinder central axis 6 of piston 1 , in the radial direction of the piston, is 40° or less, desirably 30° or less.
  • piston 1 While in operation, piston 1 is moving reciprocally. Near the bottom dead center, a part of the skirt side of piston 1 deviates from the cylinder. Guided by guide surface 4 , piston 1 can enter the cylinder smoothly.
  • the above-mentioned conventional piston has cut portion 5 , the area on the outer circumferential surface of piston 1 , that is closer to the skirt side than sealing surface 3 , in other words, the lower side in FIG. 8 is not cylindrical but multilevel. In such a case, a rotative honing stone while processing does not stay stably, and thus a through-feed centerless grinder cannot be used, reducing productivity.
  • the vertical posture of piston 1 to the cylinder is regulated by the clearance between outer circumferential surface 2 of piston 1 and the inner circumferential surface of the cylinder, only in the short section between the edge of the top surface and the lower edge of sealing surface 3 , causing the piston to easily tilt relative to the direction of the cylinder. Consequently, leakage of a large amount of refrigerant decreases the freezing capacity, so does the efficiency.
  • a hermetic compressor In a hermetic compressor according to the present invention, at least two grooves are formed on the outer circumferential surface of the piston, where the grooves do not communicate with the top and skirt surfaces of the piston, and at the same time do communicate with the space in the housing at least near the bottom dead center.
  • This makeup stabilizes a rotative honing stone while processing, owing to the outer circumferential surface, substantially cylindrical, on the top and skirt sides of the piston; causes the piston to be resistant to vertically tilting relative to the direction of the cylinder; and supplies the sliding part with oil through the grooves.
  • the above-mentioned makeup provides a hermetic compressor with high productivity, freezing capacity, and efficiency.
  • FIG. 1 is a longitudinal sectional view of a hermetic compressor according to the first exemplary embodiment of the present invention.
  • FIG. 2 is a perspective view of a piston used for the hermetic compressor according to the first exemplary embodiment of the present invention.
  • FIG. 3 is a characteristic diagram showing the freezing capacity and coefficient of performance (C.O.P.) of the hermetic compressor according to the first exemplary embodiment of the present invention.
  • FIG. 4 is a longitudinal sectional view of a hermetic compressor according to the second exemplary embodiment of the present invention.
  • FIG. 5 is a perspective view of a piston used for the hermetic compressor according to the second exemplary embodiment of the present invention.
  • FIG. 6 is a longitudinal sectional view of a hermetic compressor according to the third exemplary embodiment of the present invention.
  • FIG. 7 is a perspective view of a piston used for the hermetic compressor according to the third exemplary embodiment of the present invention.
  • FIG. 8 is a perspective view of a piston used for a conventional hermetic compressor.
  • the present invention provides a hermetic compressor with high productivity, and high freezing capacity and efficiency by suppressing leakage of a refrigerant from between the piston and cylinder.
  • a hermetic compressor can store oil in the housing, and a compression mechanism for compressing a refrigerant gas is housed in the housing.
  • the compression mechanism is provided with: a crankshaft allocated substantially vertically, having a main axis part and a eccentric axis part; a block forming a cylinder; a piston moving reciprocally in the cylinder; a connector for connecting the eccentric axis part with the piston; and an oil supplying structure for supplying the outer circumferential surface of the piston with oil.
  • the piston has an outer circumferential surface formed with grooves that do not communicate with the top and skirt surfaces of the piston, where the grooves communicate with the space in the housing when the piston is positioned near the bottom dead center.
  • the grooves that do not communicate with the top and skirt surfaces of the piston refer to two grooves formed independently each other, on the outer circumferential surface of the piston, but excluding the edges of the top and skirt surfaces.
  • the grooves are not formed on an area with a predetermined width from the top and skirt surfaces, meaning the outer circumferential shape of the piston is retained.
  • This makeup stabilizes a rotative honing stone while processing, owing to the outer circumferential surface, substantially cylindrical, on the top and skirt sides of the piston.
  • tilting of the piston in an off-axis direction relative to that of the central axis of the cylinder is regulated on the edges of top surface and on the skirt side, suppressing the tilting.
  • supplying the sliding part with oil through the grooves brings high productivity, freezing capacity, and efficiency.
  • the area of the grooves is to be half or more of the area of the outer circumferential surface of the piston. This suppresses leakage of a refrigerant gas from between the piston and the cylinder. In addition, a large size of an area that does not contact the cylinder extensively decreases a sliding loss occurring between the piston and the cylinder. In addition, supplying a wide range of the outer surface of the piston with oil through the grooves increases efficiency.
  • the crankshaft has a secondary axis part which is coaxial with the main axis part, and the eccentric axis is sandwiched by the secondary axis part and the main axis part.
  • the hermetic compressor further has a secondary bearing pivotally supporting the secondary axis part. This makeup prevents the crankshaft from inclining away from the vertical direction, and the piston connected to the crankshaft by means of a connector becomes substantially parallel with the direction of the cylinder axis.
  • the structure prevents the edge of the groove on the skirt side from touching the cylinder edge, when the piston moves from the bottom dead center to the top dead center, stabilizing the behavior of the piston.
  • the structure further suppresses leakage of a refrigerant, increasing freezing capacity and efficiency as well as reducing noise.
  • the shape of the groove on the skirt side includes a shape that does not form a parallel line with the skirt surface of the piston. This makeup allows the edge of the groove on the skirt side to act as a vertical guide between the piston and the cylinder, when the piston moves from the bottom dead center to the top dead center, stabilizing the behavior of the piston to reduce noise.
  • the hermetic compressor according to the present invention is inverter-driven with a plurality of operation frequencies including at least a frequency or lower. Applying the frequency suppresses leakage of a refrigerant by storing oil in the grooves, even though less oil is supplied during a slow operation, further increasing the freezing capacity and efficiency.
  • the hermetic compressor according to the present invention uses R600a for its refrigerant.
  • Using the refrigerant causes the piston to be resistant to tilting in the off-axis direction relative to that of the cylinder.
  • external diameter of the piston becomes larger and leakage of the refrigerant usually tends to becomes larger as compared with the compressor using conventional R134a.
  • the present invention prevents the piston from tilting against the cylinder, leakage of the refrigerant is suppressed, and the freezing capacity and efficiency increase.
  • oil with its viscosity grade of VG10 to VG5 can be selected.
  • a conventional compressor using low-viscosity oil leaks a large amount of refrigerant gas, while the makeup according to the present invention suppresses leakage of the refrigerant, further increasing the freezing capacity and efficiency.
  • FIG. 1 is a longitudinal sectional view of a hermetic compressor according to the first exemplary embodiment.
  • FIG. 2 is a perspective view of a piston used for the hermetic compressor according to the first exemplary embodiment.
  • FIG. 3 is a characteristic diagram showing the freezing capacity and coefficient of performance (C.O.P.).
  • C.O.P. represents efficiency of a compressor, namely the ratio of freezing capacity (W) to input power (W) of the electromotive element of a compressor, where a higher freezing capacity tends to raise C.O.P.
  • housing 101 houses electromotive element 104 composed of stator 102 and rotor 103 , able to inverter-drive with a plurality of operation frequencies including a power-line frequency or lower, by using such as a control circuit; and compression mechanism 105 driven by electromotive element 104 .
  • housing 101 stores oil 106 therein.
  • the refrigerant used for this compressor is R600a, which is a natural hydrocarbon refrigerant with a low global warming potential.
  • Oil 106 is a combination of oils from ISO VG10 to ISO VG5, low-viscosity grades, having compatibility one another.
  • Crankshaft 110 substantially vertically allocated, includes: main axis part 111 with rotor 103 press-fitted; eccentric axis part 112 formed eccentrically from main axis part 111 ; and secondary axis part 113 provided coaxially with main axis part 111 , and eccentric axis part 112 is sandwiched between main axis part 111 and secondary axis part 113 .
  • Oil supplying structure 120 is composed of oil cone 122 fixed to the bottom end of main axis part 111 , where one end of the cone is open in oil 106 , and the other end communicates with oil supplying duct 121 ; and oil supplying duct 121 formed inside crankshaft 110 , where the duct communicates with oil cone 122 , and is open at the top end of eccentric axis part 112 .
  • Block 130 has substantially cylindrical cylinder 131 , as well as main bearing 132 pivotally supporting main axis part 111 , and secondary bearing 133 pivotally supporting secondary axis part 113 .
  • Cylinder 131 has a top provided with dash-board 134 thereon, and is further equipped with notch 135 provided on the top edge on the crankshaft 110 side, and chamfered part 136 provided on the circumferential edge on the crankshaft 110 side.
  • Piston 140 is inserted to cylinder 131 of block 130 reciprocally slidably, connected to eccentric axis part 112 by means of connector 141 .
  • Piston 140 is further provided with at least two grooves 144 that do not communicate with top surface 142 and skirt surface 143 of piston 140 , on outer circumferential surface 145 of the piston.
  • top surface 142 and skirt surface 143 refer to surfaces vertical to the direction of the reciprocal movement of the piston, as shown in FIG. 1
  • outer circumferential surface 145 refers to a side parallel with the reciprocal movement.
  • Top surface 142 and skirt surface 143 correspond to the surfaces on the top dead center and the bottom dead center of piston 140 , respectively.
  • Groove 144 is substantially quadrangle in a state where the outer circumferential surface of the piston is developed on a plane.
  • edge 441 on the skirt side of groove 144 is to be positioned at piston 140 , approximately 2 mm away from skirt surface 143 in arrow T direction.
  • Edge 442 on the top side of groove 144 is to be positioned 7 mm to 8 mm away from top surface 142 in arrow S direction.
  • the depth of groove 144 is to be 0.1 mm to 0.5 mm from outer circumferential surface 145 of piston 140 .
  • groove 144 on the skirt side of piston 140 protrudes from the cylinder 131 to the inside of housing 101 , near the bottom dead center, the part of groove 144 is exposed in the space inside housing 101 near at least the bottom dead center. At that position groove 144 communicates to the space inside housing 101 . Grooves 144 are made so that their total area exceeds half the area of outer circumferential surface 145 of piston 140 .
  • Rotor 103 of electromotive element 104 rotates crankshaft 110 , and transmitting the rotational movement of eccentric axis part 112 to piston 140 through connector 141 , causes piston 140 to move reciprocally in cylinder 131 .
  • This movement causes the refrigerant gas to be suctioned and compressed from the cooling system (not illustrated) to the inside of cylinder 131 , and again discharged to the cooling system.
  • oil supplying structure 120 raises oil 106 in oil supplying duct 121 with a centrifugal force generated by the rotation of oil cone 122 involved in the rotation of crankshaft 110 , and sprays oil 106 into housing 101 from near the top end of secondary axis part 113 .
  • Oil 106 having been sprayed strikes dash-board 134 , travels through notch 135 , and attaches to outer circumferential surface 145 and chamfered part 136 of the piston. Attached Oil 106 penetrates into outer circumferential surface 145 of the piston and groove 144 according to the reciprocal movement of piston 140 , acting as a lubricant between outer circumferential surface 145 of the piston and cylinder 131 .
  • oil 106 attached to chamfered part 136 , and oil 106 penetrated into groove 144 are gathered by means of edge 441 on the skirt side of groove 144 , when piston 140 moves from the bottom dead center (S direction end) to the top dead center (T direction end), and stored near the edge of groove 144 of piston 140 .
  • the movement of piston 140 causes oil 106 stored between cylinder 131 and outer circumferential surface 145 of the piston, to be attracted to a clearance between piston 140 and cylinder 131 , and the entire clearance near top surface 142 is filled with oil 106 , improving sealability.
  • a wide range of outer circumferential surface 145 of the piston can be supplied with oil 106 through groove 144 , allowing oil 106 to be supplied more effectively.
  • piston 140 faces to the inner surface of cylinder 131 , owing to the two edges: one near top surface 142 and the other near skirt surface 143 , and thus piston 140 can be regulated so as to suppress a tilt. Consequently, the clearance between cylinder 131 and the outer circumferential surface 145 of the piston can be limited, suppressing leakage of the refrigerant from cylinder 131 to the inside of housing 101 , to increase the freezing capacity. Meanwhile, groove 144 does not contact cylinder 131 , reducing a sliding loss. The synergistic effect allows increasing the efficiency.
  • the area of grooves 144 is more than half the area of outer circumferential surface 145 of the piston, and thus the area that does not contact cylinder 131 can be enlarged, while suppressing leakage of the refrigerant from the clearance between piston 140 and cylinder 131 .
  • This makeup significantly reduces a sliding loss occurring between piston 140 and cylinder 131 .
  • crankshaft 110 tilts when eccentric axis part 112 of crankshaft 110 is applied with a compressive load from piston 140 . Consequently, piston 140 vertically tilts, and particularly for piston 140 according to this exemplary embodiment, the edge on the skirt side strikes the edge of cylinder 131 , possibly making a noise.
  • crankshaft 110 includes secondary axis part 113 provided coaxially with main axis part 111 , where eccentric axis part 112 is sandwiched between main axis part 111 and secondary axis part 113 ; and secondary bearing 133 pivotally supports secondary axis part 113 , and a tilt of crankshaft 110 is suppressed. Therefore, piston 140 connected to crankshaft 110 with connector 141 is retained substantially in parallel with the axial direction of cylinder 131 . Consequently, this prevents the edge on the skirt side of groove 144 provided on the skirt surface of piston 140 , from striking the edge of cylinder 131 on the crankshaft 110 side, when piston 140 moves from the bottom dead center to the top dead center. This suppresses a striking noise, and also stabilizes the behavior of piston 140 , suppressing leakage of the refrigerant, and increasing the freezing capacity and efficiency.
  • groove 144 can store oil 106 therein, sustaining high freezing capacity and efficiency.
  • the density of R600a refrigerant is low as compared to R134a refrigerant conventionally used for a refrigerator.
  • a hermetic compressor using R600a refrigerant needs to have a larger cylinder volume and a larger external diameter of piston 140 , if the same level of freezing capacity as the compressor using R134a refrigerant is required. Therefore, more refrigerant may leak from cylinder 131 to the inside of housing 101 because of the larger area of the duct in case of using R600a refrigerant.
  • a hermetic compressor according to the first exemplary embodiment suppresses a tilt of piston 140 relative to the direction of cylinder 131 and prevents R600a refrigerant from leaking and the efficiency is improved.
  • Low-viscosity oil with an ISO viscosity grade from VG10 to VG5 can be used for oil 106 .
  • low viscosity oil reduces a sliding loss, while oil 106 becomes discontinuous in the clearance between cylinder 131 and outer circumferential surface 145 of the piston, causing the seal to break and the refrigerant to leak into housing 101 .
  • the first exemplary embodiment can store oil 106 in groove 144 and can supply the clearance between cylinder 131 and piston 140 with oil 106 , preventing the seal from breaking and the refrigerant from leaking and the efficiency is improved.
  • the vertical right axis indicates the freezing capacity of the compressor
  • the vertical left axis indicates the coefficient of performance (W/W) characteristic.
  • Both the conventional compressor and the compressor in the first exemplary embodiment use R600a refrigerant.
  • the operation frequency of the reciprocal movement of the piston is 50 Hz.
  • the operating temperature is ⁇ 25° C. for vaporization temperature, and 55° C. for condensation temperature, which are usual conditions in a refrigerator operation.
  • FIG. 3 clearly shows that using the compressor in the first exemplary embodiment significantly improves the freezing capacity, C.O.P., and efficiency.
  • FIG. 4 is a longitudinal sectional view of a hermetic compressor according to the second exemplary embodiment of the present invention.
  • FIG. 5 is a perspective view of a piston used for the hermetic compressor according to the second exemplary embodiment.
  • the identical mark is given to omit its detailed description.
  • housing 101 houses compression mechanism 205 driven by electromotive element 104
  • Piston 240 included in compression mechanism 205 is provided with at least two grooves 244 that do not communicate with top surface 242 and skirt surface 243 of piston 240 on outer circumferential surface 245 of the piston.
  • the grooves 244 do not communicate each other.
  • Groove 244 communicates with the space inside housing 101 at least near the bottom dead center, and the right side is wider than the left one, viewing piston 240 from its top.
  • a line formed by edge 246 on the skirt side of groove 244 is curved or tilted so as not to form a line parallel with a line formed by skirt surface 243 of piston 240 , if outer circumferential surface 245 of the piston is developed on a plane.
  • FIG. 5 shows an example where edge 246 on the skirt side is processed into a curved shape having a predetermined curvature at the lower-left corner of the figure.
  • the shape is not limited to a curve with a curvature, but it may be a gradient straight line.
  • Rotor 103 of electromotive element 104 rotates crankshaft 110 clockwise, and the rotational movement of eccentric axis part 112 is transmitted to piston 240 through connector 141 , causing piston 240 to move reciprocally in cylinder 131 .
  • Edge 246 on the skirt side of piston 240 is curved so as not to form a line parallel with skirt surface 243 of piston 240 .
  • edge 246 on the skirt side of groove 244 provided on the skirt surface of piston 240 acts as a guide part continuously for the edge of cylinder 131 on a side of crankshaft 110 , when piston 240 moves from the bottom dead center to the top dead center. The effect prevents edge 246 on the skirt side from hitting the edge of cylinder 131 periodically, the behavior of piston 240 is stabilized, and occurrence of noise is suppressed.
  • the right side of groove 244 is wider, viewing from the top in FIG. 5 , and thus a wide range of the area most vulnerable to wear due to a side pressure can be supplied with oil 106 through groove 244 , to increase reliability.
  • crankshaft 110 includes secondary axis part 113 provided coaxially with main axis part 111 , eccentric axis part 112 is sandwiched between main axis part 111 and secondary axis part 113 , and secondary axis part 113 is pivotally supported by secondary bearing 133 .
  • crankshaft 110 is pivotally supported only by main bearing 132 , and even if piston 240 tends to vertically tilt relative to the direction of cylinder 131 due to a tilt from the vertical direction, the makeup as described in the second exemplary embodiment may bring the same actions and effects.
  • FIG. 6 is a longitudinal sectional view of a hermetic compressor according to the third exemplary embodiment of the present invention.
  • FIG. 7 is a perspective view of a piston used for the hermetic compressor according to the third exemplary embodiment.
  • housing 101 houses compression mechanism 305 driven by electromotive element 104 .
  • Piston 340 included in compression mechanism 305 is provided with at least two grooves 344 that do not communicate with top surface 342 and skirt surface 343 of piston 240 on outer circumferential surface 345 of the piston.
  • Groove 344 communicates with the space in housing 101 at least near the bottom dead center.
  • the shape of groove 344 is arcuate and the top side is widened as shown in FIGS. 6 and 7 .
  • FIG. 7 shows the shape of edge 346 on the skirt side of groove 344 .
  • the shape does not form a line parallel with skirt surface 343 , and is arcuate having a predetermined curvature.
  • the shape is not limited to an arc with a curvature, but may be a gradient straight line.
  • Rotor 103 of electromotive element 104 rotates crankshaft 110 , and the rotational movement of eccentric axis part 112 is transmitted to piston 340 through connector 141 , causing piston 340 to move reciprocally in cylinder 131 .
  • edge 346 on the skirt side of piston 340 does not form a line parallel with skirt surface 343 of piston 340 .
  • edge 346 on the skirt side of groove 344 provided on the skirt surface of piston 340 continuously acts as a guide part to the edge of cylinder 131 on the crankshaft 110 side, when piston 340 moves from the bottom dead center to the top dead center.
  • the effect prevents edge 346 on the skirt side from periodically hitting the edge of cylinder 131 , the behavior of piston 340 is stabilized, and noise caused by the hitting is suppressed.
  • oil 106 gathers to the top of piston 340 along edge 346 on the skirt side of groove 344 , further increasing sealability.
  • crankshaft 110 has secondary axis part 113 provided coaxially with main axis part 111 , eccentric axis part 112 is sandwiched between main axis part 111 and secondary axis part 113 , and secondary axis part 113 is pivotally supported by secondary bearing 133 .
  • secondary axis part 113 and secondary bearing 133 are not provided, in other words, crankshaft 110 is pivotally supported only by main bearing 132 , and even if piston 240 tends to vertically tilt relative to the direction of cylinder 131 due to a tilt from the vertical direction, the makeup as described in the third exemplary embodiment may bring the same actions and effects.
  • a hermetic compressor according to the present invention allows increasing productivity, efficiency, and reliability, and thus can be also used for an air conditioner and combined refrigerator with freezer.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Reciprocating Pumps (AREA)
US10/544,339 2004-03-16 2005-01-12 Hermetic compressor Abandoned US20060204373A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2004074278A JP4429769B2 (ja) 2004-03-16 2004-03-16 密閉型圧縮機
JP2004-074278 2004-03-16
PCT/JP2005/000553 WO2005088127A1 (en) 2004-03-16 2005-01-12 Hermetic compressor

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US20060204373A1 true US20060204373A1 (en) 2006-09-14

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US10/544,339 Abandoned US20060204373A1 (en) 2004-03-16 2005-01-12 Hermetic compressor

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US (1) US20060204373A1 (ja)
EP (1) EP1727982B1 (ja)
JP (1) JP4429769B2 (ja)
KR (1) KR100724843B1 (ja)
CN (1) CN100445558C (ja)
DE (1) DE602005016904D1 (ja)
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US20090116982A1 (en) * 2007-04-25 2009-05-07 Kosuke Tsuboi Hermetic reciprocating compressor with thrust ball bearing
US20100221129A1 (en) * 2007-02-23 2010-09-02 Seigo Yanase Hermetic compressor
US20100300142A1 (en) * 2009-05-26 2010-12-02 Makoto Katayama Hermetic compressor and fridge-freezer
CN102597518A (zh) * 2009-10-27 2012-07-18 松下电器产业株式会社 密闭型压缩机
US20150330680A1 (en) * 2012-12-27 2015-11-19 Panasonic Intellectual Property Management Co., Ltd. Hermetic compressor and refrigeration apparatus including the same

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JP4687581B2 (ja) * 2006-06-23 2011-05-25 パナソニック株式会社 密閉型圧縮機
JP4687605B2 (ja) * 2006-08-03 2011-05-25 パナソニック株式会社 密閉型圧縮機
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CN106121969B (zh) * 2016-08-24 2019-02-26 珠海格力节能环保制冷技术研究中心有限公司 活塞及具有其的压缩机
CN106640590B (zh) * 2017-02-16 2018-10-26 于法周 一种带自润滑结构的空气压缩机

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100221129A1 (en) * 2007-02-23 2010-09-02 Seigo Yanase Hermetic compressor
US20090116982A1 (en) * 2007-04-25 2009-05-07 Kosuke Tsuboi Hermetic reciprocating compressor with thrust ball bearing
US20100300142A1 (en) * 2009-05-26 2010-12-02 Makoto Katayama Hermetic compressor and fridge-freezer
US8601933B2 (en) 2009-05-26 2013-12-10 Panasonic Corporation Hermetic compressor and fridge-freezer
CN102597518A (zh) * 2009-10-27 2012-07-18 松下电器产业株式会社 密闭型压缩机
US20120183419A1 (en) * 2009-10-27 2012-07-19 Panasonic Corporation Hermetic compressor
US20150330680A1 (en) * 2012-12-27 2015-11-19 Panasonic Intellectual Property Management Co., Ltd. Hermetic compressor and refrigeration apparatus including the same

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CN100445558C (zh) 2008-12-24
CN1777753A (zh) 2006-05-24
JP2005264743A (ja) 2005-09-29
WO2005088127A1 (en) 2005-09-22
DE602005016904D1 (de) 2009-11-12
EP1727982B1 (en) 2009-09-30
KR100724843B1 (ko) 2007-06-04
JP4429769B2 (ja) 2010-03-10
EP1727982A1 (en) 2006-12-06
KR20060061288A (ko) 2006-06-07

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