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
  • F04B39/02—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.
• 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. Further, on the outer periphery of the sleeve 12, 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; Upon electrifying the motor 5, its rotor 7 rotates. Therefore, the shaft 11 which is fit and fixed to the rotor 7 forming a single unit also rotates. By this rotation of the shaft 11, the compressor unit 10 performs its prescribed compressor action. And when the sleeve 12 rotates by the rotation action of the shaft 11, the inner wall of the sleeve 12 becomes to rotate with respect to the outer wall of the rod 20.
• oil 2 receives a rotating force and is dragged by the viscosity existing in the relative rotation between the sleeve 12 and the rod 20 within the oil channel formed between the helical thread 20' formed on the outer periphery of the rod 20 and the inner wall of the sleeve 12. That is, due to the relative rotation of the sleeve 12, 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 manuf cturing 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.
• an effective viscosity pump can be formed with a small number of parts.
• the compressor unit of the present invention Since the bottom part of the shaft and bottom face of the above-mentioned sleeve are coupled freely in their rotation, the relative position of the shaft and the sleeve is restricted, resulting in reducing a chance of occurrence of twisting action between the sleeve and the shaft . According to the compressor unit of the present invention, 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 for suppress
• a technical effect through which a compressor in accordance with the above-mentioned feature can be offered wherein 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.
• a technical effect through which a compressor in accordance with either one of the above- mentioned features can be offered, wherein the above- mentioned sleeve is formed by integral molding of the synthetic resin.
• a technical effect through which a compressor in accordance with either one of the above- mentioned features can be offered, wherein the above- mentioned compressor unit is supported elastically in the above-mentioned hermetic container.
• a technical effect through which a compressor in accordance with either one of the above- mentioned features can be offered, wherein the above- mentioned electric motor unit is driven by operation frequencies including frequencies less than the power source frequency.
• Figure 1 is a vertical cross-sectional drawing of a compressor according to Example 1 of the present invention.
• Figure 2 is a vertical cross-sectional drawing of a part of the compressor according to Example 1 of the present invention.
• Figure 3 is a vertical cross-sectional drawing of a compressor according to Example 2 of the present invention .
• Figure 4 is a vertical cross-sectional drawing of a part of the compressor according to
• Example 2 of the present invention is a vertical cross-sectional drawing of a compressor according to Example 3 of the present invention.
• Figure 6 is a vertical cross-sectional drawing of a part of the compressor according to Example 3 of the present invention.
• Figure 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.
• Figure 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 R600a, which is hydrocarbon coolant, and the oil 102 is preferably synthetic oil.
• 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 at the lower end of the main shaft part 120 of the shaft 125.
• an oil pump 140 immersed in oil 102 is provided at the lower end of the main shaft part 120 of the shaft 125.
• an oil pump 140 immersed in oil 102 is provided at the lower end of the main shaft part 120 of the shaft 125.
• a lower part helical groove 142 is provided on the periphery of the lower part of the main shaft part 120.
• 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 vertxcal 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
• 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.
• 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 main shaft 120 attached with the bolt 160 is engaged to the sleeve 146 freely in its rotation.
• 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.
• 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. Accompanying with the rotation of the shaft
• coolant gas 103 is preferably a hydrocarbon type coolant, 600a, 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.
• 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. And, owing to the oil pressure created in the upper and lower part helical grooves 142' and 142, the gap between the main shaft part 120 and the sleeve 146 as well as each gap on the main shaft is maintained at a good condition.
• 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. Furthermore, as for 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
• Figure 4 is a sectional view of expanded principal part of the lower part according to the same example
• sleeve 246 that is installed to the lower end of the main shaft part 120 of the shaft 125 constituting a compressor unit 210
• an oil pump 240 that is immersed in the oil 102 is formed.
• detailed explanation is given on the configuration of an oil pump 240.
• 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 Figure 2.
• a vertxcal hole 144 is provided inside the main shaft part 120 along its axial center (as shown in Figure 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 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 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. According to the above-mentioned action, in the oil 102 in the helical groove, a frictional resistive force due to the viscous resistance with respect to the sleeve 146 is caused.
• coolant gas 103 is preferably a hydrocarbon type coolant, 600a, 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 is a gap from 100 ⁇ 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 main shaft part 120 attached with the bolt 160 is engaged to the sleeve 246 freely in its rotation and the relative position between them is determined by the relative relation between the head of the bolt 160 and the main shaft 120 above-mentioned above.
• 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. Owing to the action of oil pressure produced in the lower part helical groove 142, the gap between the sleeve 246 and the main shaft part 120 is maintained constant.
• 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
• Figure 6 is an expanded cross-sectional drawing of lower main part of the compressor according to the same example mode of the present invention
• 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 Figure 2.
• a vertical hole 144 is provided inside the main shaft part 120 along its axial center (as shown in Figure 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 dxameter 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 oil 102 rotates in the rotating direction of the sleeve 346 seen relatively from the lower part helical groove 142, and by this relative rotation with respect to the lower part helical groove 142, a certain amount of oil pressure takes place and by this oil pressure the oil rises up in the lower part helical groove 142.
• an oil pressure takes place in the oil in the lower part helical groove 142, and due to this, the oil 102 rises up in the vertical hole 144.
• the oil thus rising up reaches the slide-motion part formed by the inner peripheral surface of the bearing 116 and the outer peripheral surface of the main shaft part 120, and rubricates it.
• coolant gas 103 is a preferably hydrocarbon type coolant, 600a, 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 bolt 160 seals the bottom end of the vertical hole
• 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 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 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)
• Control Of Positive-Displacement Pumps (AREA)

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• 2004
  • 2004-11-11 US US10/578,199 patent/US20070081908A1/en not_active Abandoned
  • 2004-11-11 WO PCT/JP2004/017134 patent/WO2005047699A1/en active Application Filing
  • 2004-11-11 EP EP04799747A patent/EP1687533A1/en not_active Withdrawn
  • 2004-11-11 JP JP2006519258A patent/JP2007510836A/ja not_active Withdrawn
  • 2004-11-11 CN CNB2004800334609A patent/CN100453807C/zh not_active Expired - Fee Related
  • 2004-11-11 KR KR1020067009560A patent/KR20060120119A/ko not_active Application Discontinuation

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