EP1727982B1 - Hermetischer verdichter - Google Patents

Hermetischer verdichter Download PDF

Info

Publication number
EP1727982B1
EP1727982B1 EP05703790A EP05703790A EP1727982B1 EP 1727982 B1 EP1727982 B1 EP 1727982B1 EP 05703790 A EP05703790 A EP 05703790A EP 05703790 A EP05703790 A EP 05703790A EP 1727982 B1 EP1727982 B1 EP 1727982B1
Authority
EP
European Patent Office
Prior art keywords
piston
hermetic compressor
axis part
cylinder
oil
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
EP05703790A
Other languages
English (en)
French (fr)
Other versions
EP1727982A1 (de
Inventor
Kosuke Tsuboi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Panasonic Corp
Original Assignee
Panasonic Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Panasonic Corp filed Critical Panasonic Corp
Publication of EP1727982A1 publication Critical patent/EP1727982A1/de
Application granted granted Critical
Publication of EP1727982B1 publication Critical patent/EP1727982B1/de
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • 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 4ab formed with the two lines connecting two boundary edges 4a and 4b 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.
  • Document EP 0 789 145 A shows a piston having an outer circumferential surface that is provided with at least one groove extending in the direction of the axis of the piston.
  • This piston reciprocates between a top dead center and a bottom dead center in a cylinder bore by means of a driving body mounted on a rotary shaft in a crank chamber during the rotation of the rotary shaft.
  • lubricating oil adhered to the inner circumferential surface of the cylinder bore collects in the groove.
  • the lubricating oil in the groove is supplied to the inside of the crank chamber lubricating the driving body and other parts in the crank chamber.
  • Document GB 507 798 A describes an air compressor with two cylindrical coaxial compression chambers of different diameter, which are oppositely disposed and have their pistons respectively arranged at the ends of one and the same rod which is provided with a transverse crank guide driven by a crank.
  • the pistons have no elastic packing surfaces, the packing being obtained by means of peripheral grooves in the pistons, in which grooves the oil collects.
  • a hermetic compressor In a hermetic compressor 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 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.
  • 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.
  • 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 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Reciprocating Pumps (AREA)

Claims (8)

  1. Hermetischer Kompressor, der umfasst:
    einen Kompressionsmechanismus (105), der enthält:
    eine Kurbelwelle (110), die vertikal angeordnet ist und einen Haupt-Achsenteil (111) sowie einen exzentrischen Achsenteil (112) hat,
    einen Zylinder (131),
    einen Kolben (140), der so eingerichtet ist, dass er sich in dem Zylinder hin- und herbewegt, und der eine obere Fläche (142) sowie eine Mantelfläche (143), die beide vertikal zu einer Richtung der Hin- und Herbewegung sind, sowie eine Außenumfangsfläche enthält, die parallel zu einer Richtung der Hin- und Herbewegung ist,
    einen Verbinder (141), der den exzentrischen Achsenteil und den Kolben verbindet, und
    eine Ölzufuhrstruktur (120) zum Zuführen von Öl zu einer Außenfläche des Kolbens;
    ein elektromotorisches Element (104); und
    ein Gehäuse (101), das den Kompressionsmechanismus und das elektromotorische Element enthält;
    wobei der Kolben wenigstens zwei Nuten (144) an seiner Außenumfangsfläche aufweist, die Nuten unabhängig voneinander sind und an einem Teil der Umfangsfläche mit Ausnahme eines Randes der oberen Fläche und eines Randes der Mantelfläche ausgebildet sind und die Nuten mit einem Raum in dem Gehäuse in Verbindung stehen, wenn sich der Kolben an einem unteren Totpunkt befindet, dadurch gekennzeichnet, dass die Nuten in der Umfangsrichtung breit sind und die Gesamtflächenausdehnung der Nuten nicht weniger als die Hälfte einer Flächenausdehnung der Außenumfangsfläche des Kolbens beträgt.
  2. Hermetischer Kompressor nach Anspruch 1, wobei die Nut (144) so eingerichtet ist, dass das Öl darin gespeichert wird.
  3. Hermetischer Kompressor nach Anspruch 1, wobei die Kurbelwelle (110) des Weiteren einen sekundären Achsenteil (113) koaxial zu einem Haupt-Achsenteil (111) enthält und der exzentrische Teil von dem sekundären Achsenteil und dem Haupt-Achsenteil eingeschlossen ist, und
    der Kompressor des Weiteren ein sekundäres Lager (133) enthält, das den sekundären Achsenteil schwenkbar trägt.
  4. Hermetischer Kompressor nach Anspruch 1, wobei eine Form eines Randes an der Mantelseite (143) der Nut (144) eine Form enthält, die keine Linie parallel zu der Mantelfläche bildet, wenn die Außenumfangsfläche des Kolbens (144) auf einer Ebene abgewickelt wird.
  5. Hermetischer Kompressor nach Anspruch 4, wobei die Form des Randes an der Mantelseite (143) der Nut (144) einen Bogen mit einer vorgegebenen Krümmung enthält.
  6. Hermetischer Kompressor nach Anspruch 1, wobei das elektromotorische Element (104) bei einer Vielzahl von Betriebsfrequenzen, die wenigstens eine Netzfrequenz oder eine darunter liegende Frequenz einschließen, umrichtergespeist wird.
  7. Hermetischer Kompressor nach Anspruch 1, wobei der Kompressionsmechanismus so eingerichtet ist, dass er ein Kühlgas komprimiert, und das Kühlgas R600a ist.
  8. Hermetischer Kompressor nach Anspruch 1, wobei das Öl aus ISO-Viskositätsklassen von einschließlich VG10 bis einschließlich VG5 ausgewählt wird.
EP05703790A 2004-03-16 2005-01-12 Hermetischer verdichter Expired - Fee Related EP1727982B1 (de)

Applications Claiming Priority (2)

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

Publications (2)

Publication Number Publication Date
EP1727982A1 EP1727982A1 (de) 2006-12-06
EP1727982B1 true EP1727982B1 (de) 2009-09-30

Family

ID=34960010

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05703790A Expired - Fee Related EP1727982B1 (de) 2004-03-16 2005-01-12 Hermetischer verdichter

Country Status (7)

Country Link
US (1) US20060204373A1 (de)
EP (1) EP1727982B1 (de)
JP (1) JP4429769B2 (de)
KR (1) KR100724843B1 (de)
CN (1) CN100445558C (de)
DE (1) DE602005016904D1 (de)
WO (1) WO2005088127A1 (de)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
JP4687634B2 (ja) * 2006-11-15 2011-05-25 パナソニック株式会社 密閉型圧縮機
JP2009518565A (ja) * 2007-02-23 2009-05-07 パナソニック株式会社 密閉型圧縮機
CN101542121A (zh) * 2007-04-25 2009-09-23 松下电器产业株式会社 具有推力球轴承的封闭往复式压缩机
JP5353445B2 (ja) * 2009-05-26 2013-11-27 パナソニック株式会社 密閉型圧縮機および冷凍冷蔵装置
WO2011052195A1 (ja) * 2009-10-27 2011-05-05 パナソニック株式会社 密閉型圧縮機
WO2014103320A1 (ja) * 2012-12-27 2014-07-03 パナソニック株式会社 密閉型圧縮機及びそれを備える冷凍装置
JP2017075531A (ja) * 2015-10-13 2017-04-20 日立アプライアンス株式会社 密閉型圧縮機及びこれを備えた機器
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

Family Cites Families (31)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1492397A (en) * 1922-05-25 1924-04-29 Edward F F Roberts Piston for internal-combustion engines
US2113628A (en) * 1936-09-09 1938-04-12 George R Stull Ringless piston
GB507798A (en) * 1938-05-04 1939-06-21 Ugo Radaelli Improved air compressor
US2407440A (en) * 1944-01-07 1946-09-10 Osborne Walter Piston for internal-combustion engines
CH466638A (de) * 1966-11-17 1968-12-15 Sulzer Ag Tauchkolben einer Kolbenbrennkraftmaschine
DE2808914C2 (de) * 1978-03-02 1983-10-27 Mahle Gmbh, 7000 Stuttgart Leichtmetallhubkolben für Verbrennungsmotoren
ZA825602B (en) * 1981-08-11 1984-03-28 Ae Plc Pistons
GB8309832D0 (en) * 1983-04-12 1983-05-18 Ae Plc Pistons and castings
DE3338474A1 (de) * 1983-10-22 1985-05-09 Mahle Gmbh, 7000 Stuttgart Tauchkolben fuer verbrennungsmotoren
IT1208802B (it) * 1985-04-12 1989-07-10 Ae Borgo Spa Perfezionamento relativo ai pistoni per motori endotermici alternativi per realizzare la lubrificazione a cuscino d olio degli stessi
DE3531801A1 (de) * 1985-09-06 1987-03-19 Kolbenschmidt Ag Leichtmetallkolben
US5118263A (en) * 1990-04-27 1992-06-02 Fritchman Jack F Hermetic refrigeration compressor
US5205723A (en) * 1991-01-22 1993-04-27 Matsushita Refrigeration Company Hermetically sealed compressor
US5239955A (en) * 1993-01-07 1993-08-31 Ford Motor Company Low friction reciprocating piston assembly
JPH0734842A (ja) * 1993-07-26 1995-02-03 Yamaha Motor Co Ltd エンジンのエアブリーザ構造
MY119900A (en) * 1995-03-14 2005-08-30 Panasonic Corp Refrigerating apparatus, and refrigerator control and brushless motor starter used in same
TW353705B (en) * 1995-06-05 1999-03-01 Toyoda Automatic Loom Works Reciprocating piston compressor
JP2885133B2 (ja) * 1995-06-12 1999-04-19 トヨタ自動車株式会社 内燃機関のピストン
CN1163668C (zh) * 1996-06-14 2004-08-25 松下冷机株式会社 封闭式压缩机
US6092993A (en) * 1997-08-14 2000-07-25 Bristol Compressors, Inc. Adjustable crankpin throw structure having improved throw stabilizing means
JP3964534B2 (ja) * 1998-03-27 2007-08-22 サンデン株式会社 ピストン
JP2001165049A (ja) * 1999-12-08 2001-06-19 Toyota Autom Loom Works Ltd 往復式圧縮機
AT413233B (de) * 2000-07-03 2005-12-15 Verdichter Oe Ges M B H Kolbenfreistellung
AU2002213255A1 (en) * 2000-10-18 2002-04-29 Federal Mogul Corporation Multi-axially forged piston
KR100395950B1 (ko) * 2000-12-29 2003-08-27 주식회사 엘지이아이 밀폐형 압축기의 오일공급구조
JP4682441B2 (ja) * 2001-05-07 2011-05-11 パナソニック株式会社 密閉型電動圧縮機
CN101338745A (zh) * 2001-07-20 2009-01-07 乐金电子(天津)电器有限公司 密闭型压缩机的阀组合体
KR100474329B1 (ko) * 2002-05-07 2005-03-08 엘지전자 주식회사 냉장고의 압축기 운전제어방법
JP2004027969A (ja) * 2002-06-26 2004-01-29 Matsushita Refrig Co Ltd 密閉型圧縮機
JP2004245073A (ja) * 2003-02-12 2004-09-02 Matsushita Electric Ind Co Ltd 電動圧縮機
CN2619069Y (zh) * 2003-04-30 2004-06-02 黄石东贝电器股份有限公司 一种应用于活塞式压缩机的非圆柱形活塞

Also Published As

Publication number Publication date
KR20060061288A (ko) 2006-06-07
JP4429769B2 (ja) 2010-03-10
CN100445558C (zh) 2008-12-24
US20060204373A1 (en) 2006-09-14
EP1727982A1 (de) 2006-12-06
KR100724843B1 (ko) 2007-06-04
WO2005088127A1 (en) 2005-09-22
DE602005016904D1 (de) 2009-11-12
JP2005264743A (ja) 2005-09-29
CN1777753A (zh) 2006-05-24

Similar Documents

Publication Publication Date Title
EP1727982B1 (de) Hermetischer verdichter
KR100701527B1 (ko) 밀폐형 압축기
US8210832B2 (en) Hermetic compressor
JP5870255B2 (ja) 密閉型圧縮機及び冷凍装置
JP5170111B2 (ja) 密閉型圧縮機およびそれを用いた冷凍冷蔵装置
KR100721081B1 (ko) 밀폐형 압축기
JP5212148B2 (ja) 密閉型圧縮機および冷凍装置
US20110176942A1 (en) Sealed compressor
JP2009085191A (ja) 密閉型圧縮機
JP2016205134A (ja) 密閉型圧縮機
JP2008223604A (ja) 密閉型圧縮機
JP2013241848A (ja) 密閉型圧縮機および該密閉型圧縮機を備える冷蔵庫
JP5810273B2 (ja) 密閉型圧縮機および冷凍装置
JP2005264740A (ja) 密閉型圧縮機
JP2009062954A (ja) 密閉型圧縮機
JP2009275651A (ja) 密閉型圧縮機
KR20020019225A (ko) 압축기용 크랭크샤프트
JP2012149564A (ja) 密閉型圧縮機および冷凍装置
JP2010242589A (ja) 密閉型圧縮機および冷凍装置
JP2013060908A (ja) 密閉型圧縮機

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20050831

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT

DAX Request for extension of the european patent (deleted)
RBV Designated contracting states (corrected)

Designated state(s): DE FR GB IT

17Q First examination report despatched

Effective date: 20080226

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: PANASONIC CORPORATION

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REF Corresponds to:

Ref document number: 602005016904

Country of ref document: DE

Date of ref document: 20091112

Kind code of ref document: P

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20100701

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20100112

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20100930

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100201

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100112

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20140109

Year of fee payment: 10

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150112

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 602005016904

Country of ref document: DE

Representative=s name: GRUENECKER PATENT- UND RECHTSANWAELTE PARTG MB, DE

Ref country code: DE

Ref legal event code: R081

Ref document number: 602005016904

Country of ref document: DE

Owner name: PANASONIC APPLIANCES REFRIGERATION DEVICES SIN, SG

Free format text: FORMER OWNER: PANASONIC CORPORATION, KADOMA-SHI, OSAKA, JP

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20220119

Year of fee payment: 18

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 602005016904

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230801