US20070081908A1 - Compressor - Google Patents

Compressor Download PDF

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Publication number
US20070081908A1
US20070081908A1 US10/578,199 US57819904A US2007081908A1 US 20070081908 A1 US20070081908 A1 US 20070081908A1 US 57819904 A US57819904 A US 57819904A US 2007081908 A1 US2007081908 A1 US 2007081908A1
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United States
Prior art keywords
sleeve
oil
compressor
shaft
rotation
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.)
Abandoned
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US10/578,199
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English (en)
Inventor
Hidetoshi Nishihara
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Panasonic Corp
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Individual
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Publication date
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Publication of US20070081908A1 publication Critical patent/US20070081908A1/en
Assigned to MATSUSHITA ELECTRIC INDUSTRIAL CO., LTD. reassignment MATSUSHITA ELECTRIC INDUSTRIAL CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: NISHIHARA, HIDETOSHI
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
    • F04B39/02—Lubrication
    • 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
    • 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
    • F04B39/0246—Hermetic compressors with oil distribution channels in the rotating shaft

Definitions

  • the present invention relates to a compressor having an improved oil feeding means.
  • coolant compressor is made to be an inverter type, and greater efforts are given on lowering the rotation rate further.
  • a centrifugal pump such as of prior art that was described in “National publication (in the Japanese) of translation of international patent application 2002-519589”, it became difficult to obtain an ample oil feeding.
  • FIG. 7 is a cross-sectional drawing of a main part of the above-mentioned compressor of prior art.
  • a hermetic container 1 stores oil 2 in its bottom part.
  • An electric motor 5 is composed of a stator 6 having a coil, and a rotor 7 including a permanent magnet within it.
  • sleeve 12 is fit and fixed so that it rotates integrally with the shaft 11 .
  • the rotor 7 is inserted and fixed. And the bottom end of the sleeve 12 is immersed in the oil 2 .
  • a bracket 15 formed in an approximately U-letter shape with a thread of piano wire is fixed at its both ends to a bottom plate 16 that is fixed to the rotor 7 of the motor 5 .
  • the sleeve 12 is made of plastic material, in which a rod 20 with a helical thread 20 ′ formed on its outer periphery is inserted in rotation-free manner. Between outer peripheral surface of the rod 20 and inner surface of the sleeve 12 facing to the outside of the rod 20 via a narrow gap, an oil channel is formed. The bottom end of the rod 20 is fixed to the central part of the bracket 15 so that the rod 20 remains at rest within the sleeve 12 even when the sleeve 12 rotates together with the shaft 11 as a single unit.
  • the compressor of prior art constituted as described above operates as follows;
  • oil layer contacting its inner surface provides a rotating force due to the viscosity to oil layer on the rod surface as well as in the above-mentioned helical thread 20 ′, then this rotating force drags the oil in the channel along the helix so as to let it being rotated and moved upward.
  • the oil moved upward inside the sleeve 12 is pumped up toward the upper hollow part of the shaft 11 via a horizontal hole in the shaft 11 and through the vertical hole in the center shaft part of the shaft 11 .
  • This upward movement of the oil 2 toward the upper hollow part of the shaft 11 is not caused by the centrifugal force, but it is due to the action of rotating upward movement by a force dragged by the viscosity, thereby a stable oil pumping-up at a low rotating rate at which the centrifugal force is small can be achieved.
  • the structure is such that the bracket 15 made of wire holds and fixes the rod 20 . Therefore, when the dimensional accuracy of the bracket 15 is low, good coaxial relationship between the outer wall of the rod 20 and the wall of the sleeve 12 is not maintained, the rod 20 is forced on some parts of the inner wall somewhere of the sleeve 12 and causes undesirable contact on the sleeve 12 . In order to absorb the occurrence of a large frictional force due to this contact, the bracket 15 is designed to be formed of elastic material.
  • the rod 20 requires a mold, which necessitates a complicated process in its manufacturing period to form a helical groove on its whole outer peripheral surface, and hence there was a shortcoming that causes the rise of cost of the compressor.
  • the present invention purposes to provide a compressor that is highly reliable and does not require any marked high cost in its manufacturing.
  • an oil pump of a compressor of the present invention is provided with a helical groove engraved helically on the outer periphery of the above-mentioned shaft and an approximately cup shaped sleeve that is associated loosely to the outer periphery of the above-mentioned shaft.
  • the bottom part of the above-mentioned shaft and bottom face of the above-mentioned sleeve are coupled freely in their rotation, and a rotation suppression means for suppressing the rotation of the above-mentioned sleeve is provided.
  • the technical effect is obtained such that a compressor having a high mechanical reliability can be offered.
  • a compressor can be offered, wherein in a hermetic container containing oil therein, an electric motor including a stator and a rotor contained in the above-mentioned hermetic container, and a compressor unit which is driven by the above-mentioned electric motor, are provided; and the above-mentioned compressor unit comprises shafts expanding in the vertical direction and making the rotating motion and an oil pump which is formed at the lower end of the above-mentioned shaft and connected to the above-mentioned oil; the above-mentioned oil pump includes a helical groove provided helically on the outer periphery of the above-mentioned shaft and a cup-shaped sleeve that is loosely coupled on the outer peripheral end part of the above-mentioned shaft so that it covers the lower end of the above-mentioned helical groove and is coupled in rotation-free manner to the bottom part of the above-mentioned shaft, and the rotation-suppression means
  • the above-mentioned rotation suppression means is the bracket which is held between the above-mentioned stator and the above-mentioned sleeve and fixes the above-mentioned sleeve to the above-mentioned stator.
  • the above-mentioned rotation suppression means is a wing part which is formed on the outer periphery of the above-mentioned sleeve and generates the viscous resistance with respect to the oil.
  • a technical effect through which a compressor in accordance with either one of the above-mentioned features can be offered wherein the above-mentioned shaft has, on its shaft center, an oil hole expanding in the vertical direction which is connected to the sliding-motion part between the shaft and a member accepting and allowing the sliding-rotation motion of the shaft within it, and the upper end of said helical groove is connected to said oil hole expanding in the vertical direction.
  • FIG. 1 is a vertical cross-sectional drawing of a compressor according to Example 1 of the present invention.
  • FIG. 2 is a vertical cross-sectional drawing of a part of the compressor according to Example 1 of the present invention.
  • FIG. 3 is a vertical cross-sectional drawing of a compressor according to Example 2 of the present invention.
  • FIG. 4 is a vertical cross-sectional drawing of a part of the compressor according to Example 2 of the present invention.
  • FIG. 5 is a vertical cross-sectional drawing of a compressor according to Example 3 of the present invention.
  • FIG. 6 is a vertical cross-sectional drawing of a part of the compressor according to Example 3 of the present invention.
  • FIG. 7 is a vertical cross-sectional drawing of a part of a compressor of prior art.
  • FIG. 1 is a cross-sectional drawing of a compressor unit according to Example 1 of the present invention
  • FIG. 2 is a main part cross-sectional drawing of the main part of according to the same Example 1.
  • a hermetic container 101 stores lubrication oil 102 , and at the same time it is charged up with coolant gas 103 .
  • the coolant gas 103 is R 600 a , which is hydrocarbon coolant, and the oil 102 is preferably synthetic oil. Also, mineral oil, or polyol ether oil, which are those having compatibility with the above-mentioned coolant gas 103 .
  • a compressor unit 110 is provided with a block 115 having a cylinder 113 , a piston 117 inserted into the cylinder 113 so as to make reciprocating motion therewith, a shaft 125 consisting of a main shaft part 120 supported by a bearing section 116 of the block 115 and an eccentric part 122 , and a connecting rod 119 connecting the eccentric section 122 and a piston 117 , thereby building a reciprocal type compressor unit.
  • Electric motor 135 comprises a stator 136 , which is connected to an inverter drive circuit (not shown) fixed underneath the block 115 and the rotor 137 , which includes a permanent magnet within it and is fixed to the main shaft part 120 .
  • This electric motor unit is driven by the inverter drive circuit (not shown) at various operation frequencies including operation frequencies below 20 Hz.
  • Spring 139 is engaged at its lower end to the bottom of the hermetic container 101 , and by its upper end supports the stator 136 and the compressor unit 110 which is composed integrally with the stator; and thus the spring supports the compressor unit 110 elastically with regard to and over the bottom part of the sealed container 101 .
  • an oil pump 140 immersed in oil 102 is provided.
  • a lower part helical groove 142 is provided on the periphery of the lower part of the main shaft part 120 . Also, an upper part helical groove 142 ′ is provided on the upper part of the main shaft periphery.
  • this main shaft part 120 there is a vertical hole 144 , which is concentric with respect to its center axis.
  • oil holes namely a lower part horizontal hole 144 ′ and an upper part horizontal hole 144 ′′, which are respectively connected to their respective outer faces of the main shaft part 120 at their respective slide-motion parts which slide on a lower sleeve 146 and its upper locating bearing 116 , respectively, are provided in the main shaft part 120 .
  • the lower part horizontal hole 144 ′ connects the upper end of the lower part helical groove 142 to the vertical hole 144 ; and the upper part horizontal hole 144 ⁇ connects upper end part of the vertical hole 144 which is along with the central axial part of the shaft 120 to the lower end part of the upper part helical groove 142 ′.
  • An approximately cup-shaped sleeve 146 which has a depth capable of accommodating the lower part helical groove 142 , is made of synthetic resin (desirably, integral-molded article of PBT polybutylene terephthalate) having the coolant resistant and oil-resistant property.
  • So-called approximately cup-shaped sleeve includes variants such as a cylindrical shape and a circular truncated cone shape, and besides the above, a cup shape having a side surface of the second-order may be usable.
  • the sleeve 146 has a bolt fastening hole 150 ( FIG. 2 ) provided on the bottom face, and an oil-intake 152 provided on the side surface, and the skirt part 154 protruded downward from the bottom plate.
  • an oil intake 152 may be provided on the bottom plate. Then, the gap between the inner diameter of the sleeve 146 and the lower part peripheral diameter of the main shaft 120 is selected to be from 100 ⁇ m to 500 ⁇ m in their diameters.
  • the bolt 160 is screw-fixed to the threaded bottom end part of the vertical hole 144 through the bolt fastening hole 150 provided on the bottom plate 146 ′ with a washer 162 inserted therebetween.
  • the bolt fastening hole 150 of the bottom plate 146 ′ is made to be larger than the outer diameter of the screw part of the bolt 160 , and the head of the bolt 160 is loosely fixed to the bottom plate of the sleeve 146 .
  • the bolt 160 seals the bottom end of the vertical hole 144 .
  • the washer 162 is formed of high abrasion resistant material (preferably, such as tetrafluoroethylene having the self-lubrication property), thereby enabling smooth rotation of the sleeve 146 with respect to the main shaft part.
  • Brackett 170 which is preferably formed in an approximately trapezoidal shape with a spring steel wire of iron material and is fixed to the stator 136 at both ends, engages with a skirt part 154 expanding below the sleeve 146 . Thereby the bracket holds the sleeve 146 such that the sleeve 146 does not rotate around its center axis.
  • the rotor 137 hence the shaft 125 , and the main shaft part 120 rotate when the stator 136 is turned on from the inverter driving circuit.
  • the eccentric motion of the eccentric part 122 forces the piston 117 to make the reciprocating motion in the cylinder 113 through the connecting rod 119 . Therefore, the piston 117 performs so-called compression action that compresses the intake gas inside of the cylinder.
  • the main shaft part 120 rotates, and then the lower part helical groove 142 rotates in the sleeve 146 , which is supported by the bracket 170 so as not to rotate. Accordingly, a frictional resistive force due to the viscous resistance with respect to the sleeve 146 is caused in the oil 102 in the lower part helical groove 142 .
  • the oil 102 rotates in the rotating direction of the sleeve 146 seen relatively from the lower part helical groove 142 .
  • coolant gas 103 is preferably a hydrocarbon type coolant, 600 a , and for oil 102 , synthetic oil, petrolatum, or polyol ester oil. All of them having the compatibility with the coolant gas 103 , is used.
  • this hydrocarbon type coolant its molecular weight is small because it contains no chlorine nor fluorine, and in particular, it has a high compatibility with synthetic oil or petrolatum. As a result, there may be induced an extreme declination in oil viscosity. In general, when the oil viscosity declines, the viscous resistance falls, likely bringing about disadvantages in the lubrication.
  • the sleeve 146 is short in its length and it is coupled with the bolt 160 in rotatable relation to the lower end of the main shaft part 120 of the shaft 125 with a washer 162 therebetween. Therefore, as for the relative positional relationship of the sleeve 146 with respect to the main shaft part 120 , an approximately constant clearance is kept between them in the direction of their diameter. Thereby, the lateral pressure due to inclination between them and also due to difference in their axial positions hardly occurs.
  • the main shaft part 120 because the upper part and the lower part helical grooves 142 ′ and 142 are provided directly on two parts of the outer periphery, they can be formed easily by, such as, end mill if processing is carried out while turning the main shaft part 120 , resulting in making the manufacturing automation easy.
  • the approximately cup-shaped sleeve 146 since it has a simple shape as it can be made in an integral molding article of PBT, any complex shaped mold is not necessary and it can be manufactured at low cost. Therefore, it becomes possible to be equipped with a high viscous pump having high productivity, resulting in making possible to provide a low cost compressor.
  • FIG. 3 is a sectional view in the vertical section of a compressor according to Example 2 of the present invention
  • FIG. 4 is a sectional view of expanded principal part of the lower part according to the same example
  • an oil pump 240 that is immersed in the oil 102 is formed.
  • a lower part helical groove 142 is provided on the periphery of the lower part of the main shaft part 120 . It is similar to the Example 1 shown in FIG. 2 .
  • a vertical hole 144 is provided inside the main shaft part 120 along its axial center (as shown in FIG. 4 ). The vertical hole 144 is connected to the sliding part, which is formed by the main shaft part 120 and the bearing 116 .
  • the upper end of the lower part helical groove 142 is connected to the vertical hole 144 through the horizontal connecting hole 144 ′.
  • the approximately cup-shaped sleeve 246 which has a depth capable of accommodating the lower part helical groove 142 , is made as an integral-molded article with synthetic resin (desirably PBT) having the coolant resistant and oil-resistant property.
  • the word of approximately cup-shaped sleeve means that it can include various variants as in the Example 1.
  • the sleeve 246 has a bolt fastening hole 250 provided on the bottom plate 246 ′, and an oil intake 252 provided on the side surface, and also has a plural number of wings 256 that are formed protruding outward to the outer peripheral direction.
  • the oil intake 252 can be provided on the bottom plate.
  • the gap between the inner diameter of the sleeve 246 and the lower part peripheral diameter in the main shaft part 120 is selected to be from 100 ⁇ m to 500 ⁇ m in their diameters.
  • the bolt 160 is screw-fixed to the threaded bottom end part of the vertical hole 144 through the bolt fastening hole 250 provided on a bottom plate 246 ′ locating near the lower end of a sleeve 246 with inserting a washer 162 therebetween.
  • the bolt fastening hole 250 of the bottom plate 246 ′ is made to be larger from the outer diameter of the screw part of the bolt 160 , and the head of the bolt 160 is loosely fixed to the bottom plate of the sleeve 246 .
  • the bolt 160 seals the bottom end of the vertical hole 144 .
  • the washer 162 is formed of high abrasion resistant material (preferably, such as tetrafluoroethylene having the self-lubrication property), thereby enabling smooth rotation of the sleeve 246 with respect to the main shaft part 120 .
  • the rotor 137 hence the shaft 125 , and the main shaft part 120 rotate and the lower part helical groove 142 rotates in the sleeve 246 when the stator 136 is turned on from the inverter drive circuit.
  • the sleeve 246 is to rotate by being dragged by the rotation of the main shaft part 120 , because of strong viscous resistivity caused by the rotation of the wings 256 in oil 102 , the sleeve 246 rotates at a low rotation rate which is far below from the rotation rate of the main shaft 120 . Therefore, between the main shaft part 120 and the sleeve 246 , a rotation rate difference that is close to the rotation rate of the shaft 125 takes place.
  • coolant gas 103 is preferably a hydrocarbon type coolant, 600 a , and for the oil 102 , synthetic oil, petrolatum, or polyol ester oil. All of them having the compatibility with the coolant gas 103 , is used.
  • this hydrocarbon type coolant its molecular weight is small because it contains no chlorine nor fluorine, and in particular, it has a high compatibility with synthetic oil or petrolatum. As a result, there may be induced an extreme declination in oil viscosity. In general, when the oil viscosity declines, the viscous resistance falls, likely bringing about disadvantages in the lubrication.
  • the gap in the direction of the diameter between the inner diameter of the sleeve 246 and the lower part outer periphery of the main shaft part 120 is too large, oil drops therebetween and the amount of lubrication decreases.
  • the gap is a gap from 100 ⁇ m to 500 ⁇ m in diameter, and moreover that any inconvenient contact between the inner wall of sleeve 246 and the lower part outer periphery of the main shaft part 120 hardly occurs.
  • the sleeve 246 is coupled to the bolt 160 freely in its rotation with letting a washer 162 be present at the lower end of the main shaft part 120 .
  • the bolt fastening hole 250 of the bottom plate 246 ′ is made to be larger from the outer diameter of the screw part of the bolt 160 , and the head of the bolt 160 is loosely fixed to the bottom plate 246 ′ of the sleeve 246 .
  • the washer 162 is formed of high abrasion resistant material (preferably, such as tetrafluoroethylene having the self-lubrication property), thereby enabling smooth rotation of the sleeve 246 with respect to the main shaft part 120 .
  • high abrasion resistant material preferably, such as tetrafluoroethylene having the self-lubrication property
  • the lower part helical groove 142 provided on a part of the lower outer periphery of the main shaft part 120 is carved directly on the main shaft part made of metal, it can be formed by, such as, end mill when processing is carried while turning the main shaft part 120 , resulting in making the manufacturing automation easy.
  • the sleeve 246 can be formed together with the wings 256 with such as PBT by integration molding, and since it has a simple shape, no complex-shaped mold is necessary, thereby making a low cost manufacturing possible.
  • the wings 256 Since the wings 256 receives, in the oil 102 , a strong viscous resistance in the rotation direction, its own rotation is disturbed, it is not necessary to fix the sleeve 246 indirectly to the stator, hence the configuration becomes very simple that it is only required to couple it to the main shaft part 120 by the bolt 160 , requiring only a limited number of parts and manufacturing steps. Therefore, it becomes possible to equip a viscous pump having high productivity, thereby a low-cost compressor can be offered.
  • FIG. 5 is a vertical cross-sectional drawing of a compressor cut along the vertical section according to Example 3 of the present invention
  • FIG. 6 is an expanded cross-sectional drawing of lower main part of the compressor according to the same example mode of the present invention
  • an oil pump 240 immersed in the oil 102 is formed.
  • a lower part helical groove 142 is provided on the periphery of the lower part of the main shaft part 120 . It is similar to the Example 1 which is shown in FIG. 2 .
  • a vertical hole 144 is provided inside the main shaft part 120 along its axial center (as shown in FIG. 6 ). The vertical hole 144 is connected to the sliding part which is formed by the main shaft part 120 and the bearing 116 . The upper end of the lower part helical groove 142 is connected to the vertical hole 144 through the horizontal connecting hole 142 ′.
  • An approximately cup-shaped sleeve 346 which has a depth capable of accommodating the lower part helical groove 142 , is made by integral-molded article with synthetic resin (desirably PBT) having the coolant resistant and oil-resistant property.
  • the word of approximately cup-shaped sleeve means that it can include various variants as in the Example 1.
  • the sleeve 346 has a bolt fastening hole 350 provided on the bottom plate 346 ′, and an oil intake 352 provided on the side surface, and also has a plural number of arms 356 that are formed protruding outward to the outer peripheral direction.
  • an oil intake 352 can be provided on the bottom plate 346 ′.
  • the gap between the inner diameter of the sleeve 346 and the lower part peripheral diameter in the main shaft part 120 is selected from 100 ⁇ m to 500 ⁇ m.
  • rotating permanent magnets 358 are fixed respectively and the stationary permanent magnets 360 placed at positions approximately facing to the rotating permanent magnets 358 are provided on the inner bottom surface of the hermetic container 101 with suitable predetermined gaps through which mutual magnetic force with respective rotating permanent magnets 358 can act.
  • a plural number of arms 356 , rotating permanent magnets 358 , and stationary permanent magnets 360 constitute a rotation suppression means.
  • the rotating permanent magnets 358 and the stationary permanent magnets 360 are provided in a manner that their mutually facing faces become opposite poles, respectively.
  • the bolt 160 is screw-fixed to the threaded bottom end of the vertical hole 144 through a bolt fastening hole 350 provided on the bottom plate 346 ′ locating near the lower end of a sleeve 346 with a washer 162 instead therebetween.
  • the bolt fastening hole 350 of the bottom plate 346 ′ is made to be larger from the outer diameter of the screw part of the bolt 160 , and the head of the bolt 160 is loosely fixed to the bottom plate 346 ′ of the sleeve 346 ′.
  • the washer 162 is formed of high abrasion resistant material (preferably, such as tetrafluoroethylene having the self-lubrication property), thereby enabling smooth rotation of the sleeve 346 with respect to the main shaft part 120 .
  • the rotor 137 therefore the shaft 125 , and the main shaft part 120 rotate and the lower part helical groove 142 rotates in the sleeve 346 when the stator 136 is turned on from the inverter drive circuit.
  • the sleeve 346 is to rotate by being dragged by the rotation of the main shaft part 120 , since rotating permanent magnets 358 to which the arms are fixed and stationary permanent magnets 360 fixed on the bottom inner plane of the hermetic container 101 attracts to each other, free rotation of the sleeve 346 with respect to the main shaft 120 is prevented. As a result, difference between their rotation rates takes place.
  • coolant gas 103 is a preferably hydrocarbon type coolant, 600 a , and for the oil 102 , synthetic oil, petrolatum, or polyol ester oil. All of them having the compatibility with the coolant gas 103 is used.
  • the hydrocarbon type coolant its molecular weight is small because it contains neither chlorine nor fluorine, and in particular, it has a high compatibility with synthetic oil or petrolatum. As the result, there may be induced an extreme declination in oil viscosity. In general, when the oil viscosity declines, the viscous resistance falls, likely bringing about disadvantages in the lubrication.
  • the sleeve 346 is coupled to the bolt 160 freely in its rotation with letting the washer 162 be present at the lower end of the main shaft part 120 .
  • the bolt fastening hole 350 of the bottom plate 346 ′ is made to be larger from the outer diameter of the screw part of the bolt 160 , and the head of the bolt 160 is loosely fixed to the bottom plate 346 ′ of the sleeve 346 .
  • the washer 162 is formed of high abrasion resistant material (preferably, such as tetrafluoroethylene having the self-lubrication property), thereby enabling smooth rotation of the sleeve 346 with respect to the main shaft part 120 .
  • high abrasion resistant material preferably, such as tetrafluoroethylene having the self-lubrication property
  • the lower part helical groove 142 provided on a part of the lower outer periphery of the main shaft part 120 is carved directly on the main shaft part made of metal, it can be formed by a standard machinery such as end mill by processing while turning the main shaft part 120 , resulting in making the production automation easy.
  • the sleeve 346 can be formed together with the arms 356 preferably with PBT by integration molding, and since it has a simple shape, any complex shaped mold is not necessary, making a low cost production possible.
  • respective rotating permanent magnets 358 are fixed on the arms 356 , and due to the mechanism that the stationary permanent magnets 360 , which are placed at positions approximately facing to the rotating permanent magnets 358 , are provided on the inner bottom surface of the hermetic container 101 with a suitable predetermined gap, the rotation is disturbed, then it becomes unnecessary to fix the sleeve 346 indirectly to the stator 136 , and an extremely simple configuration of only connecting it to the main shaft part 120 with a bolt 160 can be employed, requiring only a limited number of parts and manufacturing steps. Therefore, it is possible to offer a low-cost compressor equipped with a viscous pump having high productivity.
  • the one using the attracting force of the permanent magnet has been described as the form of the present implementation.
  • the same or similar function can be gained also with using soft iron or soft ferrite for the one side of the magnets which are provided on the arms or on the bottom plate of the hermetic container.
  • the compressor in accordance with the present invention can be used for those apparatuses using the freezing cycle such as home-use refrigerators, dehumidifiers, food showcases, or vending machines.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
US10/578,199 2003-11-12 2004-11-11 Compressor Abandoned US20070081908A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2003382195 2003-11-12
JP2003-382195 2003-11-12
PCT/JP2004/017134 WO2005047699A1 (en) 2003-11-12 2004-11-11 Compressor

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US (1) US20070081908A1 (ja)
EP (1) EP1687533A1 (ja)
JP (1) JP2007510836A (ja)
KR (1) KR20060120119A (ja)
CN (1) CN100453807C (ja)
WO (1) WO2005047699A1 (ja)

Cited By (5)

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US20100287977A1 (en) * 2008-01-21 2010-11-18 Whirlpool S.A. Oil pump for a refrigeration compressor
US20120100020A1 (en) * 2010-10-26 2012-04-26 Kyoungjun Park Hermetic compressor
US20120269662A1 (en) * 2009-11-03 2012-10-25 Whirlpool S.A. Mounting arrangement for an eccentric shaft in a refrigeration compressor
US20130287603A1 (en) * 2012-04-25 2013-10-31 Samsung Electronics Co., Ltd. Hermetic reciprocating compressor
US20170204853A1 (en) * 2016-01-19 2017-07-20 Whirlpool S.A. Oil Pump Assembly Arrangement in Cooling Compressor

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Publication number Priority date Publication date Assignee Title
BRPI0604908A (pt) 2006-10-31 2008-07-01 Whirlpool Sa bomba de óleo para compressor de refrigeração
SI2178796T1 (sl) 2007-07-11 2021-04-30 Clene Nanomedicine, Inc. Kontinuiran postopek za obdelavo tekočin in proizvodnjo določenih sestavin
BRPI0804302B1 (pt) 2008-10-07 2020-09-15 Embraco Indústria De Compressores E Soluções Em Refrigeração Ltda Arranjo de montagem de bomba de óleo em compressor de refrigeração
WO2012062848A1 (en) * 2010-11-11 2012-05-18 Arcelik Anonim Sirketi Hermetic compressor with oil sucking member
WO2013098126A1 (en) * 2011-12-27 2013-07-04 Arcelik Anonim Sirketi A compressor comprising an oil sucking member
KR101997555B1 (ko) * 2012-10-12 2019-07-09 엘지전자 주식회사 압축기
WO2016192976A1 (en) * 2015-06-02 2016-12-08 Arcelik Anonim Sirketi Compressor with a movable oil suction apparatus
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JP7507961B2 (ja) 2021-04-14 2024-06-28 安徽美芝制冷設備有限公司 クランクシャフト、インバータ圧縮機及び冷凍機器

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KR20060120119A (ko) 2006-11-24
EP1687533A1 (en) 2006-08-09
WO2005047699A1 (en) 2005-05-26
JP2007510836A (ja) 2007-04-26
CN100453807C (zh) 2009-01-21

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