US20060013706A1 - Compressor - Google Patents
Compressor Download PDFInfo
- Publication number
- US20060013706A1 US20060013706A1 US10/531,452 US53145205A US2006013706A1 US 20060013706 A1 US20060013706 A1 US 20060013706A1 US 53145205 A US53145205 A US 53145205A US 2006013706 A1 US2006013706 A1 US 2006013706A1
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- Prior art keywords
- compressor
- insertion member
- oil
- sleeve
- set forth
- Prior art date
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Classifications
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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
- F04B39/0223—Lubrication characterised by the compressor type
- F04B39/023—Hermetic compressors
- F04B39/0261—Hermetic compressors with an auxiliary oil pump
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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
- F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
- F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
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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
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B31/00—Compressor arrangements
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K1/00—Details of the magnetic circuit
- H02K1/06—Details of the magnetic circuit characterised by the shape, form or construction
- H02K1/12—Stationary parts of the magnetic circuit
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K1/00—Details of the magnetic circuit
- H02K1/06—Details of the magnetic circuit characterised by the shape, form or construction
- H02K1/22—Rotating parts of the magnetic circuit
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- 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
- F05B2210/11—Kind or type liquid, i.e. incompressible
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- 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
- F05B2240/00—Components
- F05B2240/10—Stators
-
- 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
- F05B2240/00—Components
- F05B2240/20—Rotors
-
- 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
- F05B2240/00—Components
- F05B2240/50—Bearings
-
- 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
- F05B2240/00—Components
- F05B2240/50—Bearings
- F05B2240/51—Bearings magnetic
- F05B2240/511—Bearings magnetic with permanent magnets
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Power Engineering (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Compressor (AREA)
Abstract
Description
- The present invention relates to an improvement of a viscous pump for supplying oil to sliding areas of a compressor.
- Recently, household refrigerators and air-conditioners have been increasingly and rapidly shifting to energy-saving types to meet demands for protection of the global environment. In this situation, increasing numbers of refrigerant compressors are inverter-controlled, and the number of driving revolution is decreased to reduce the rotational speed. Accordingly, it is difficult to obtain sufficient lubrication by using conventional centrifugal pumps.
- A conventional compressor, which is disclosed in JP-T-2002-519589, for example, includes a viscous pump which has stable pumping capability even at the time of low-speed revolution in lieu of a centrifugal pump.
- The related-art compressor mentioned above is herein described with reference to the drawings. In this description, the positional correlations in the vertical direction are shown based on the condition in which a closed type electrically-powered compressor is installed in a normal position.
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FIG. 34 is a cross-sectional view illustrating a main part of a conventional compressor. InFIG. 34 ,oil 7102 is stored in the bottom area of closedcontainer 7101. Electrically-poweredelement 7105 includesstator 7106 androtor 7107 which contains permanent magnet. Rotor 7107 engages withhollow shaft 7111 of compressingelement 7110, andsleeve 7112 which is soaked withoil 7102 at least at its lower end and rotates integrally withshaft 7111 is fixed toshaft 7111. - Substantially U-shaped
bracket 7115 made from elastic material has a concave center portion and its both ends are fixed toshroud 7116 secured tostator 7106.Insertion member 7120 made from plastic material and inserted intosleeve 7112 has a spiral groove on its outer surface to provide oil passage betweeninsertion member 7120 andsleeve 7112. The lower end ofinsertion member 7120 is fixed to the center portion ofbracket 7115. - The operation of the conventional compressor having the above structure is now described.
- When electrically-powered
element 7105 is energized,rotor 7107 rotates. Shaft 7111 revolves with the rotation ofrotor 7107, and compressingelement 7110 carries out predetermined compressing operations.Oil 7102 rises through the oil passage formed between the spiral groove formed on the outer surface ofinsertion member 7120 and sleeve 7112 in accordance with the revolution ofsleeve 7112 while rotating and being pulled by the inner surface of the sleeve due to viscosity, thereby drawing upoil 7102 toward the upper hollow region ofshaft 7111. - A compressor has a closed container which stores oil and accommodates a compressing element for compressing refrigerant and an electrically-powered element for driving the compressing element, wherein: the electrically-powered element includes a stator and a rotor; and the compressing element includes a shaft which extends in a vertical direction and rotates, and a viscous pump which is formed inside the shaft and communicates with the oil, the viscous pump having a cylindrical hollow portion formed in the shaft, an insertion member coaxially and rotatably inserted into the cylindrical hollow portion, a spiral groove formed between the inner surface of the cylindrical hollow portion and the outer surface of the insertion member along a direction where the oil rises, and prevention means for preventing rotation of the insertion member.
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FIG. 1 is a cross-sectional view illustrating a main part of a compressor in a first embodiment of the present invention. -
FIG. 2 is a perspective view of a lower part of a shaft in the first embodiment of the invention. -
FIG. 3 is a cross-sectional view illustrating the main part of the compressor in a driving condition immediately after start-up in the first embodiment of the invention. -
FIG. 4 is a cross-sectional view illustrating a main part of a compressor in a second embodiment of the invention. -
FIG. 5 is a perspective view of a lower part of a shaft in the second embodiment of the invention. -
FIG. 6 is a cross-sectional enlarged view illustrating a sleeve in the second embodiment of the invention. -
FIG. 7 is a cross-sectional view illustrating a main part of a compressor in a third embodiment of the invention. -
FIG. 8 is a perspective view of a lower part of a shaft in the third embodiment of the invention. -
FIG. 9 is a cross-sectional enlarged view illustrating a sleeve in the third embodiment of the invention. -
FIG. 10 is a cross-sectional view illustrating a compressor in a fourth embodiment of the invention. -
FIG. 11 is a cross-sectional view illustrating a main part of the compressor in the fourth embodiment of the invention. -
FIG. 12 is a perspective view illustrating the main part of the compressor in the fourth embodiment of the invention. -
FIG. 13 is a cross-sectional view illustrating a main part of a compressor in a fifth embodiment of the invention. -
FIG. 14 is a cross-sectional view illustrating a main part of a compressor in a sixth embodiment of the invention. -
FIG. 15 is a cross-sectional view of a compressor in a seventh embodiment of the invention. -
FIG. 16 is a cross-sectional view illustrating a main part of the compressor in the seventh embodiment of the invention. -
FIG. 17 is a cross-sectional view illustrating a main part of a compressor in an eighth embodiment of the invention. -
FIG. 18 is a main part assembly view of the compressor in the eighth embodiment of the invention. -
FIG. 19 is a cross-sectional view illustrating a compressor in a ninth embodiment of the invention. -
FIG. 20 is a cross-sectional view illustrating a main part of the compressor in the ninth embodiment of the invention. -
FIG. 21 is a cross-sectional view illustrating a compressor in a tenth embodiment of the invention. -
FIG. 22 is a cross-sectional view illustrating a main part of the compressor in the tenth embodiment of the invention. -
FIG. 23 is a cross-sectional view illustrating a compressor in an eleventh embodiment of the invention. -
FIG. 24 is a cross-sectional view illustrating a main part of the compressor in the eleventh embodiment of the invention. -
FIG. 25 is an enlarged view illustrating a main part of an insertion member in the eleventh embodiment of the invention. -
FIG. 26 is a cross-sectional view illustrating a compressor in a twelfth embodiment of the invention. -
FIG. 27 is a cross-sectional view illustrating a main part of the compressor in the twelfth embodiment of the invention. -
FIG. 28 is a cross-sectional view illustrating a compressor in a thirteenth embodiment of the invention. -
FIG. 29 is a cross-sectional view illustrating a main part of the compressor in the thirteenth embodiment of the invention. -
FIG. 30 is a cross-sectional view illustrating a compressor in a fourteenth embodiment of the invention. -
FIG. 31 is a cross-sectional view illustrating a main part of the compressor in the fourteenth embodiment of the invention. -
FIG. 32 is a cross-sectional view illustrating a main part of a viscous pump in the fourteenth embodiment of the invention. -
FIG. 33 is a cross-sectional view illustrating a main part of a compressor in a fifteenth embodiment of the invention. -
FIG. 34 is a cross-sectional view illustrating a main part of a conventional compressor. - According to the description of the structure of the above-described conventional compressor, a hollow opening is provided in an upper area of the viscous pump, and there is a large space for storing transferred oil. Especially, the process for further raising oil drawn by the viscous pump immediately after the start-up requires sufficient time for storing oil until the hollow opening is substantially filled with oil.
- As a result, oil is transferred upward at lower speed and thus oil supply to sliding areas becomes unstable. This causes sliding components to contact each other while sliding, forming scratches and abrasion therebetween. These damages lead to a locked condition of the compressing element.
- In order to solve the above problem, an object of the present invention is to provide a highly reliable compressor which transfers oil to each sliding area at high speed and has reliable and stable oil transfer capability even at the time of low-speed driving.
- For achieving the above object, a compressor of the present invention includes a viscous pump which opens to oil stored in a lower region of a closed container and a second viscous pump connected to an upper region of the former viscous pump, both the viscous pumps being attached to a main shaft portion of a shaft. Since most area of an oil passage in the main shaft portion is occupied by the pumps, the space for storing oil and refrigerant is reduced. Consequently, the oil transfer speed increases. Additionally, oil receives not only centrifugal force which decreases at the time of low-speed revolution but also upward pressure while being pulled due to viscosity within the passage.
- The compressor provided according to the present invention, which includes a viscous pump and a second viscous pump disposed above the viscous pump, is a highly reliable compressor which transfers oil at high speed and has stable oil transfer capability even at the time of low-speed driving.
- First through third embodiments of the present invention is hereinafter described with reference to the drawings. The present invention is not limited to those embodiments.
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FIG. 1 is a cross-sectional view illustrating a main part of a compressor in the first embodiment of the invention,FIG. 2 is a perspective view of a lower part of a shaft in the first embodiment, andFIG. 3 is a cross-sectional view illustrating the main part of the compressor in a driving condition immediately after start-up in the first embodiment. - In
FIGS. 1, 2 and 3,oil 3102 is stored inclosed container 3101 which is charged with refrigerant 3103. - Compressing
element 3110 includes: block 3109 which formscylinder 3108;piston 3113 reciprocatively inserted intocylinder 3108;shaft 3111 havingmain shaft portion 3116 supported bymain bearing 3114 ofblock 3109 andeccentric portion 3117; and connectingrod 3118 for connectingeccentric portion 3117 andpiston 3113. Compressingelement 3110 forms a reciprocating compressing mechanism. - Electrically-powered element 105 is fixed below
block 3109. Electrically-powered element 105 includesstator 3106 connected to an inverter driving circuit (not shown) androtor 3107 which contains permanent magnet (not shown) and is fixed tomain shaft portion 3116. Electrically-powered element 105 is an electrically-powered element 105 for driving the inverter, and is driven at a plurality of driving frequencies including those at least in a range from 600 to 1,200 r/min. by the inverter driving circuit. -
Springs 3104 elasticallysupport compressing element 3110 viastator 3106 so that compressingelement 3110 is elastically held on closedcontainer 3101. -
Main shaft portion 3116 ofshaft 3111 hasviscous pump 3130 soaked withoil 3102 and secondviscous pump 3150 connected withviscous pump 3130 through communicatinghole 3140. Secondviscous pump 3150 is disposed aboveviscous pump 3130. - Next, the structures of
viscous pump 3130 and secondviscous pump 3150 connected with each other are described in detail. -
Viscous pump 3130 includes: cylindricalhollow portion 3135 formed inmain shaft portion 3116;sleeve 3131 secured to the lower region of cylindricalhollow portion 3135;insertion member 3133 coaxially inserted into cylindricalhollow portion 3135 andsleeve 3131; and supportingmember 3132. Supportingmember 3132 has restrictingmeans 3139 for restricting floating ofinsertion member 3133 in the rotational and vertical directions. - The upper end of cylindrical
hollow portion 3135 reaches the lower region ofmain bearing 3114. -
Sleeve 3131 is substantially cylindrical and cap-shaped, whose top and bottom are open.Sleeve 3131 is made from iron plate press material which offers comparatively high accuracy, but may be formed from leaf spring steel. - Thread-shaped
spiral groove 3134 is formed on the outer surface ofinsertion member 3133 to provide a spiral oil passage betweenspiral groove 3134 andsleeve 3131, through whichpassage oil 3102 is allowed to flow.Insertion member 3133 has refrigerant-resistance and oil-resistance properties, and is made from plastic material having lower thermal conductivity than the metal material which formsshaft 3111, such as PPS, PBT, and PEEK. - Supporting
member 3132 is substantially U-shaped and made from elastic material such as iron spring wire. Both ends of supportingmember 3132 are fixed to the lower position ofstator 3106. The center portion of supportingmember 3132 engages withengagement holes 3137 throughnotches 3136 provided at the lower end ofinsertion member 3133.Notches 3136 are disposed before engagement holes 3137 in the advancing direction ofmain bearing 3114 and joined withengagement holes 3137. The length of joiningportions 3138 ofengagement holes 3137, i.e., the length of the openings in contact withnotches 3136 is smaller than the outside diameter of supportingmember 3132. - Second
viscous pump 3150 includesmain shaft portion 3116,lead groove 3151 engraved on the outer surface ofmain shaft portion 3116, andmain bearing 3114. -
Main bearing 3114 is secured to block 3109, or formed integrally withblock 3109 to be secured thereto.Lead groove 3151 having a trapezoidal or substantially semicircular cross section is formed on the outer surface ofmain shaft portion 3116, whereby a spiral oil passage through which oil flows is provided betweenmain bearing 3114 andlead groove 3151. - The upper end of
lead groove 3151 communicates with eccentric communicatingportion 3160 positioned withineccentric portion 3117. - The operation and action of the compressor having the above structure are now described.
- When
stator 3106 is energized by the inverter driving circuit,rotor 3107 rotates withshaft 3111. The eccentric motion ofeccentric portion 3117 thus caused reciprocatespiston 3113 withincylinder 3108 via connectingrod 3118, thereby carrying out predetermined compressing actions for taking in and compressing refrigerant 3103. - In accordance with the rotation of
main shaft portion 3116 ofshaft 3111,oil 3102 rises through the oil passage formed between the outer surface ofinsertion member 3133 and the inner surface ofsleeve 3131 included inviscous pump 3130 while being pulled by the rotation ofsleeve 3131.Oil 3102 then passes through communicatinghole 3140 and reaches the starting point oflead groove 3151. Subsequently, oil 7302 further rises through the oil passage formed betweenlead groove 3151 provided on the outer surface ofmain shaft portion 3116 of secondviscous pump 3150 and the inner surface ofmain bearing 3114 while being pulled by the rotation ofmain shaft portion 3116. Finally,oil 3102 is transferred toeccentric portion 3117, connectingrod 3118 and other components through eccentric communicatingportion 3160. - In this embodiment as described above, most area of the oil passage of
main shaft portion 3116 is occupied byviscous pump 3130 and secondviscous pump 3150 and the space for storing refrigerant 3103 andoil 3102 is small. Therefore, oil 7302 is transferred to each sliding area at high speed without decreasing the speed. Moreover,oil 3102 receives not only centrifugal force which decreases at the time of low-speed revolution but also upward pressure whileoil 3102 is being pulled within the oil passage due to viscosity, thereby drawing upoil 3102 in a reliable and stable manner even at the time of low-speed revolution. - Additionally, when
oil 3102 in which refrigerant 3103 dissolves is heated by compressingelement 3110, electrically-poweredelement 3105 and other components and refrigerant 3103 is thus vaporized within the oil passage, the refrigerant gas is transferred together withoil 3102 owing to the high oil-transfer performance ofviscous pump 3130 and secondviscous pump 3150 connected with each other without hindering transfer ofoil 3102. As a result,oil 3102 can be transferred to each sliding area at high speed immediately after start-up even at the time of low-speed revolution such as 600 r/min., thereby realizing stable oil transfer capability. - Accordingly, damages such as flaws and abrasion which may lead to excessive wear or a locked condition of compressing
element 3110 are not caused when the sliding components contact each other. - In this embodiment,
rotor 3107 is fitted tomain shaft portion 3116 by shrinkage fitting or press fitting. However, since the inside diameter of cylindricalhollow portion 3135 alters at the time of attachment ofrotor 3107, the dimension of the space between cylindricalhollow portion 3135 andinsertion member 3133 in the radial direction is difficult to control. Thus,viscous pump 3130 is not provided in the region whererotor 3107 is fitted tomain shaft portion 3116. The length of that region, i.e., the length from the top surface ofinsertion member 3133 to communicatinghole 3140 is in a range from about 10 mm to about 20 mm, which is substantially equivalent to the fitting length ofrotor 3107. - However, according to our finding from experiments in this embodiment, a known parabolic free surface is produced on the upper surface of
oil 3102 within the cylindrical hollow portion due to centrifugal force immediately after start-up, andoil 3102 having reached the upper end surface ofinsertion member 3133 instantly comes to communicatinghole 3140 as illustrated inFIG. 3 . Thus, the oil transfer speed is scarcely affected if the length of the region where the pump is not provided is from about 10 mm to about 20 mm. - Since the oil transfer speed is considerably high,
oil 3102 within cylindricalhollow portion 3135 rapidly flows intolead groove 3151 immediately after start-up, causing negative pressure inside cylindricalhollow portion 3135. As a result, such a phenomenon thatinsertion member 3133 is sucked toward the upper region of cylindricalhollow portion 3135 is caused in very few cases. Additionally, reaction force against the force for moving oil upward caused by viscosity is always applied toinsertion member 3133 in the downward direction during continuous operation. - However, floating of
insertion member 3133 in the vertical direction is restricted by the engagement between the center portion of supportingmember 3132 andengagement holes 3137 ofinsertion member 3133. Thus, the structure ofviscous pump 3130 in whichoil 3102 is drawn up through the space between cylindricalhollow portion 3135 andinsertion member 3133 due to viscosity can be maintained both at the start-up and during continuous driving. - Since the clearance between
sleeve 3131 andinsertion member 3133 is maintained by the oil pressure generated withinspiral groove 3134, the possibility of sliding abrasion and fixation betweensleeve 3131 andinsertion member 3133 is extremely low. Additionally, by determining the difference between the inside diameter ofengagement holes 3137 and the outside diameter of supportingmember 3132 in a range from several hundred μm to 1 mm instead of completely fixing supportingmember 3132 toengagement holes 3137, the clearance betweensleeve 3131 andinsertion member 3133 can be similarly maintained. - Joining
portions 3138 ofengagement holes 3137 are open in the advancing direction ofmain shaft portion 3116, and a force in the rotational direction is applied on the side on which engagement holes 3137 are closed even at the time of high-speed revolution at a driving frequency in a range from 4,200 to 4,800 r/min., for example. However, this force is scarcely applied on the side on which joiningportions 3138 are open. In this structure,insertion member 3133, which does not rotate by the restriction of supportingmember 3132, is prevented from coming off from the predetermined position even at the time of high-speed driving. - The length of the regions of joining
portions 3138 which are open tonotches 3136 is smaller than the outside diameter of supportingmember 3132. Thus, supportingmember 3132 does not easily come off fromengagement holes 3137 once it is inserted intoengagement holes 3137, even if uncertain events such as vibrations occur during assembly at the line or transportation. - The compressor in this embodiment is inexpensive, as it does not require additional components for restricting rotation and vertically floating of
insertion member 3133. - Since a reliable and sufficient amount of
oil 3102 is transferred even at the time of low-speed revolution, it is possible to reduce heat generated frommain shaft portion 3116, electrically-poweredelement 3105 and other components and thus prevent temperature increase ofoil 3102. Accordingly, while R600a as isobutane is more soluble inoil 3102 than R134a, vaporization of R600a and resultant accumulation of the gas do not occur within the oil passage, thereby preventing generation of obstruction for the transfer ofoil 3102 such as a gas choke phenomenon. -
Viscous pump 3130 and secondviscous pump 3150 are assembled integrally with electrically-poweredelement 3105 and compressingelement 3110, inserted into closedcontainer 3101, and finally supported with elasticity bysprings 3104 inside closedcontainer 3101. Thus, constituting components forviscous pump 3130 and secondviscous pump 3150 are not required to be provided inclosed container 3101. Accordingly, the compressor in this embodiment is easily assembled and has high productivity, and requires only the minimum number of components and thus realizes cost reduction in manufacture. - In this embodiment,
sleeve 3131 is fastened within cylindricalhollow portion 3135. However,insertion member 3133 may be directly inserted into cylindricalhollow portion 3135 formed by the processed main shaft portion to provide a viscous pump instead of usingsleeve 3131, if the accuracy within 500 μm can be secured for the clearance between the outermost surface ofinsertion member 3133 and the inside surface of cylindricalhollow portion 3135. While the number of components in this structure is different from that of the above-described embodiment, both cases are basically identical in the aspects of operation, action and advantages. -
FIG. 4 is a cross-sectional view illustrating a main part of a compressor in a second embodiment of the invention,FIG. 5 is a perspective view of a lower part of a shaft in the second embodiment, andFIG. 6 is a cross-sectional enlarged view illustrating a sleeve in the second embodiment. - The second embodiment is herein described with reference to
FIGS. 4, 5 and 6. Similar numbers are given to the structures similar to those of the first embodiment, and detailed description of those is omitted. -
Main shaft portion 3216 ofshaft 3211 included in compressingelement 3210 hasviscous pump 3230 soaked withoil 3102 and secondviscous pump 3150 connected withviscous pump 3230 through communicatinghole 3140. Secondviscous pump 3150 is disposed aboveviscous pump 3230. - Next, the structures of
viscous pump 3230 and secondviscous pump 3150 connected with each other are described in detail. -
Viscous pump 3230 is coaxially inserted into cylindricalhollow portion 3235 formed inmain shaft portion 3216 andsleeve 3231 secured to the lower region of cylindricalhollow portion 3235.Viscous pump 3230 includesinsertion member 3233 having two supportingmembers 3232 which extend from the lower end ofinsertion member 3233 in the almost horizontal direction, and restricting means 339 havingfree joints 3261 which is combined with supportingmembers 3232 such thatfree joints 3261 and supportingmembers 3232 can freely rotate so as to restrict floating ofinsertion member 3233. - The upper end of cylindrical
hollow portion 3235 reaches the lower part ofmain bearing 3114. - Thread-shaped
spiral groove 3234 is formed on the inner surface ofsleeve 3231 to provide a spiral oil passage betweenspiral groove 3234 andinsertion member 3233, through whichpassage oil 3102 is allowed to flow. -
Insertion member 3233 has refrigerant-resistance and oil-resistance properties, and is made from plastic material or other material having lower thermal conductivity than metal material. Supportingmembers 3232 made from metal wire penetrate through the lower end ofinsertion member 3233 to be fixed thereto. - Substantially L-shaped free joint 3261 is fixed to the lower part of
stator 3106 at one end, and hasnotch 3236 andengagement hole 3237 at the other end. The end of supportingmember 3232 which is formed at the lower end ofinsertion member 3233 is inserted throughnotche 3236 intoengagement hole 3237, thereby combining supportingmember 3232 and free joint 3261 such that both can freely rotate. This structure restricts floating ofinsertion member 3233 in the rotational and vertical directions. -
Notches 3236 are disposed before engagement holes 3237 in the advancing direction ofmain shaft portion 3216 and joined withengagement holes 3237. The length of joiningportions 3238 ofengagement holes 3237, i.e., the length of the openings in contact withnotches 3236 is smaller than the outside diameter of supportingmembers 3232. - Second
viscous pump 3250 includemain shaft portion 3216,lead groove 3251 engraved on the outer surface ofmain shaft portion 3216, andmain bearing 3114. -
Lead groove 3251 having a trapezoidal or substantially semicircular cross section is formed on the outer surface ofmain shaft portion 3216, whereby a spiral oil passage through whichoil 3102 flows is provided betweenmain bearing 3114 andlead groove 3251. - The operation and action of the compressor having the above structure are now described.
- When
stator 3106 is energized by the inverter driving circuit,main shaft portion 3216 ofshaft 3211 rotates. In accordance with this rotation,oil 3102 rises through the oil passage formed between the inner surface ofsleeve 3231 and the outer surface ofinsertion member 3233 included inviscous pump 3230 while being pulled by the rotation ofsleeve 3231.Oil 3102 then passes through communicatinghole 3140 and reaches the starting point oflead groove 3251. - Subsequently,
oil 3102 further rises through the oil passage formed betweenlead groove 3251 provided on the outer surface ofmain shaft portion 3216 and the inner surface ofmain bearing 3114 included in secondviscous pump 3250 while being pulled by the rotation ofmain shaft portion 3216. - In the embodiment as described above,
oil 3102 is transferred to each sliding area at high speed by the similar mechanism as in the first embodiment. Moreover, the stable oil transfer capability can be maintained even at the time of low-speed revolution such as 600 r/min. Accordingly, damages such as flaws and abrasion which may lead to excessive wear or a locked condition of compressingelement 3210 are not caused when the sliding components contact each other, and thus a highly reliable compressor can be provided. - Moment generated through the rotation applies load, and the load applied to a certain position decreases as the distance from that position to the rotational shaft center of
shaft 3211 increases. Since the distance between the rotational shaft center and combiningportion 3263 for combining supportingmember 3232 and free joint 3261 included in restrictingmeans 3239 is large in this embodiment, the load applied to combiningportions 3263 is decreased, thereby considerably reducing the possibility of breaking of combiningportions 3263. - In this embodiment,
spiral groove 3234 is formed on the inner surface ofsleeve 3231 to enlarge the area of inner surface of the rotational body in contact withoil 3102 by adding the surface area of the concaves ofspiral groove 3234. This structure causes large viscous resistance, thereby enhancing oil transfer capability. - Furthermore, centrifugal force generated through the rotation of
main shaft portion 3216 is applied tooil 3102 existing within the oil passage formed between the inner surface ofsleeve 3231 and the outside surface ofinsertion member 3233 andoil 3102 rises while rotating and inclining toward the farthermost surface from the rotational shaft center in the oil passage. Since there is no clearance in the oil passage to which the centrifugal force is most applied in this embodiment,oil 3102 does not fall to flow out and thus the amount ofoil 3102 which falls to flow out can be controlled. Accordingly, the compressor in this embodiment has considerably higher transfer capability ofoil 3102 than the example in which the spiral groove is formed oninsertion member 3233. -
FIG. 7 is a cross-sectional view illustrating a main part of a compressor in a third embodiment of the invention,FIG. 8 is a perspective view of a lower part of a shaft in the third embodiment, andFIG. 9 is a cross-sectional enlarged view illustrating a sleeve in the third embodiment. - The third embodiment is herein described with reference to
FIGS. 7, 8 and 9. Similar numbers are given to the structures similar to those of the first embodiment, and detailed description of those is omitted. -
Main shaft portion 3316 ofshaft 3311 included in compressingelement 3310 hasviscous pump 3330 soaked withoil 3102 and secondviscous pump 3350 connected withviscous pump 3330 through communicatinghole 3140. Secondviscous pump 3150 is disposed aboveviscous pump 3330. - Next, the structures of
viscous pump 3330 and secondviscous pump 3350 connected with each other are described in detail. -
Viscous pump 3330 includes: cylindricalhollow portion 3335 formed inmain shaft portion 3316;sleeve 3331 secured to cylindricalhollow portion 3335;spiral member 3373 as a coil spring fixed to the inner surface ofsleeve 3331;insertion member 3333 coaxially inserted into cylindricalhollow portion 3335 andsleeve 3331; and restrictingmeans 3339 having supportingmember 3332 for restricting floating ofinsertion member 3333. - Supporting
member 3332 is substantially U-shaped and made from elastic material such as iron spring wire. Both ends of supportingmember 3332 are fixed to the lower region ofstator 3106. The center portion of supportingmember 3332 engages withengagement grooves 3336 provided at the lower end ofinsertion member 3333 to restrict floating ofinsertion member 3333 in the rotational and vertical directions. -
Eccentric passage 3372 formed above cylindricalhollow portion 3335 has a smaller inside surface diameter than the inside diameter ofsleeve 3331, and is off-centered from the rotational shaft center toward the side where communicatinghole 3140 is provided. The floating ofinsertion member 3333 in the upward direction is restricted by contacting withupper bottom 3380 of cylindricalhollow portion 3335. The clearance between the upper surface ofinsertion member 3333 andupper bottom 3380 of cylindricalhollow portion 3335 is so determined as to be smaller than a height (B) ofengagement groove 3336 in the longitudinal direction so as to prevent separation ofinsertion member 3333 from supportingmember 3332 wheninsertion member 3333 rises. - The upper end of
eccentric passage 3372 reaches the lower part ofmain bearing 3114, whereeccentric passage 3372 communicates with communicatinghole 3140. - An oil passage is formed between
spiral member 3373 as the coil spring fixed to the inner surface ofsleeve 3331 andinsertion member 3333, through whichpassage oil 3102 is allowed to flow. - Substantially
cylindrical sleeve 3331 has a shape of a cap whose top and bottom are open.Sleeve 3331 has substantially L-shapedspring holder 3374 at its lower region.Sleeve 3331 is made from iron plate press material which can be processed with relatively high accuracy in this embodiment, but may be made from leaf spring steel. - The length of the coil spring of
spiral member 3373 is larger than the total length of the inner surface ofsleeve 3331 from which the length of thespring holder 3374 in the axial direction is subtracted. As a result,spiral member 3373 is compressed betweenupper bottom 3380 of cylindricalhollow portion 3335 andspring holder 3374 and fixed to the inner surface ofsleeve 3331. -
Spiral member 3373 is made from oil temper wire for springs (SWOV) in this embodiment, but may be made from other material including iron steel such as piano wire (SWP) and spring steel (SUP), non-iron metal such as aluminum, plastic material (PC, PA) whose thermal deformation temperature is 100° C. or higher and which has high formability, and other material having oil transfer capability of the spiral groove. - Second
viscous pump 3350 includesmain shaft portion 3316,lead groove 3351 engraved on the outer surface ofmain shaft portion 3316, andmain bearing 3114. -
Lead groove 3351 having a trapezoidal or substantially semicircular cross section is formed on the outer surface ofmain shaft portion 3316, whereby a spiral oil passage through whichoil 3102 flows is provided betweenmain bearing 3114 andlead groove 3351. - The operation and action of the compressor having the above structure are now described.
- When
stator 3106 is energized by the inverter driving circuit,main shaft portion 3316 ofshaft 3311 rotates. In accordance with this rotation,oil 3102 rises through the oil passage formed betweenspiral member 3373 and the outer surface ofinsertion member 3333 included inviscous pump 3330 while being pulled by the rotation ofsleeve 3331.Oil 3102 then passes through communicatinghole 3140 and reaches the starting point oflead groove 3351. - Subsequently,
oil 3102 further rises through the oil passage formed betweenlead groove 3351 and the inner surface ofmain bearing 3114 included in secondviscous pump 3350 while being pulled by the rotation ofmain shaft portion 3116. - In the embodiment as described above, oil is transferred to each sliding area at high speed by the similar mechanism as in the first embodiment. Moreover, the stable oil transfer capability can be maintained even at the time of low-speed revolution such as 600 r/min. Accordingly, damages such as flaws and abrasion which may lead to excessive wear or a locked condition of compressing
element 3310 are not caused when the sliding components contact each other, and thus a highly reliable compressor can be provided. - In assembly, the position of
insertion member 3333 within cylindricalhollow portion 3335 in the vertical direction can be determined by aligning the upper surface ofinsertion member 3333 withupper bottom 3380 of cylindricalhollow portion 3335. Supportingmember 3332 can be attached toinsertion member 3333 by bringing supportingmember 3332 into engagement withengagement grooves 3336 provided at the lower end ofinsertion member 3333. Thus, the assembly is facilitated. - In this embodiment,
viscous pump 3330 which uses the shape of the coil spring itself asspiral member 3373 provided on the inner surface ofsleeve 3331 can be far more easily formed than the structure in which a spiral groove is directly engraved on the inner surface ofsleeve 3331. - From the viewpoint of energy saving, the amount of oil transfer can be appropriately controlled by replacing the coil spring with the one having a different wire diameter, wire cross-sectional shape, number of winding etc., in accordance with the driving frequency required by the system side such as household refrigerators and air conditioners. Thus, the compressor of this embodiment is highly flexible and capable of meeting a wide variety of demands.
- Attachment of
sleeve 3331 to the lower end ofmain shaft portion 3316 is completed by forcedly insertingsleeve 3331, which has the coil spring ofspiral member 3373 around its inner surface in advance, into cylindricalhollow portion 3335 formed coaxially withmain shaft portion 3316. Also, formation of the spiral groove necessary for the upward transfer ofoil 3102 is completed by compressingspiral member 3373 betweenupper bottom 3380 of cylindricalhollow portion 3335 andspring holder 3374 and securingspiral member 3373 to the inner surface ofsleeve 3331. - Thus, the assembly is extremely practical and easy, thereby enhancing productivity.
- In the invention as described above, since most area of the oil passage of the main shaft portion is occupied by the pumps, the space for storing oil and refrigerant is small and oil is transferred at high speed. Also, not only centrifugal force which decreases at the time of low-speed revolution but also upward pressure is given to oil while oil is being pulled within the passage due to viscosity, thereby drawing up oil in a reliable and stable manner even at the time of low-speed revolution. Therefore, a highly reliable compressor having positive and stable oil transfer capability can be provided.
- In addition to the above advantage, the highly reliable compressor provided according to the invention has high productivity and is manufactured at low cost.
- Another advantage of the highly reliable compressor provided according to the invention is that the rotation, rising and falling of the insertion member can be securely prevented even at the start-up and during continuous driving, thereby realizing reliable and stable oil transfer capability.
- Another advantage of the highly reliable compressor provided according to the invention is that rising and resultant separation of the insertion member from the restricting means and also abrasion and chipping of the insertion member due to the contact and collision between the inner surface of the cylindrical hollow portion and the outer surface of the insertion member are prevented, thereby realizing reliable and stable oil transfer capability.
- Another advantage of the highly reliable compressor provided according to the invention is that the possibility of breaking of the restricting means is extremely low.
- Another advantage of the highly reliable compressor provided according to the invention is that assembly of the compressor is facilitated.
- Another advantage of the highly reliable compressor provided according to the invention is that multiplicatively large oil transfer capability can be obtained.
- Another advantage of the highly reliable compressor provided according to the invention is that the compressor is highly flexible and has enhanced productivity.
- Another advantage of the highly reliable compressor provided according to the invention is that power consumption is reduced since input to the compressor is decreased and oil supply is stabilized.
- Another advantage of the highly reliable compressor provided according to the invention is that the compressor is easily assembled to achieve enhanced productivity and includes the viscous pumps.
- Another advantage of the highly reliable compressor provided according to the invention is that generation of obstructions to the oil transfer such as gas choke phenomenon is prevented.
- Another advantage of the highly reliable compressor provided according to the invention is that the compressor gives extremely little adverse effect on the global environment since the greenhouse effect coefficient of R600a employed is substantially zero and low-speed revolution reduces power consumption.
- In the above-described conventional structure in which
bracket 7115 supportsinsertion member 7120,insertion member 7120 comes to be fixed withinsleeve 7112 if the dimensional precision is insufficient. This fixation is absorbed by the elasticity of the material ofbracket 7115. However, if the fixation is extremely large, abrasion is generated betweensleeve 7112 andinsertion member 7120. The abrasion thus caused may decrease the pumping ability and generate abrasion powder which is circulated with oil toward the sliding area and caught between the sliding components and thus brings about a locked condition of the compressing element. - Additionally, as
insertion member 7120 passes throughrotor 7107 to be indirectly fixed tostator 7106, additional long components forinsertion member 7120 withstator 7106 and suitable means and processes for fixing those components are required. Thus, the cost of the compressor is inevitably raised. It is thus an object of the invention to provide a highly reliable and inexpensive compressor. - Compressors in Fourth and fifth embodiments of the present invention are herein described with reference to the drawings.
-
FIG. 10 is a cross-sectional view illustrating a compressor in the fourth embodiment of the invention,FIG. 11 is a cross-sectional view illustrating a main part of the compressor in the fourth embodiment, andFIG. 12 is a perspective view illustrating the main part of the compressor in the fourth embodiment. - In FIGS. 10 to 12,
oil 1102 is stored inclosed container 1101 which is filled withrefrigerant gas 1103. - Compressing
element 1110 includes: block 1115 which formscylinder 1113;piston 1117 reciprocatively inserted intocylinder 1113;shaft 1125 havingmain shaft portion 1120 supported bymain bearing 1116 ofblock 1115 andeccentric portion 1122; and connectingrod 1119 for connectingeccentric portion 1122 andpiston 1117. Compressingelement 1110 forms a reciprocating compressing mechanism. - Electrically-powered
element 1135 is fixed belowblock 1115. Electrically-poweredelement 1135 includesstator 1136 connected to an inverter driving circuit (not shown) androtor 1137 which contains permanent magnet and is fixed tomain shaft portion 1120. Electrically-poweredelement 1135 thus forms an electrically-powered element for driving the inverter. -
Springs 1139 elasticallysupport compressing element 1110 viastator 1136 so that compressingelement 1110 can be elastically supported onclosed container 1101. -
Main shaft portion 1120 ofshaft 1125 hasviscous pump 1140 soaked withoil 1102 at its lower end.Viscous pump 1140 includes: cylindricalhollow portion 1142 formed in the lower region ofmain shaft portion 1120;insertion member 1145 coaxially and rotatably inserted into cylindricalhollow portion 1142; and impellers 147 having a plurality of vanes which are formed integrally withinsertion member 1145. A thread-shapedspiral projection 1149 is provided on the outer surface ofinsertion member 1145, thereby forming aspiral groove 1150 through whichoil 1102 flows betweenspiral projection 1149 and cylindricalhollow portion 1142. -
Insertion member 1145 andimpellers 1147 havecomponent 1151 formed by a shaped plastic component having refrigerant-resistance and oil-resistance properties.Component 1151 is hollow and hasupper region 1152 wherepenetration 1153 is opened.Screw 1157 inserted intopenetration 1153 rotatably connectscomponent 1151 to the ceiling of cylindricalhollow portion 1142. - Communicating
hole 1160 extends upward from the ceiling of cylindricalhollow portion 1142 to connect cylindricalhollow portion 1142 withlateral hole 1162 which is open to a sliding area formed by the inner surface of bearing 1116 and the outer surface ofmain shaft portion 1120. - The operation of the compressor having the above structure is now described. When
stator 1136 is energized by the inverter driving circuit,rotor 1137 rotates withshaft 1125. In accordance with this rotation, the eccentric motion ofeccentric portion 1122 reciprocatespiston 1117 withincylinder 1113 via connectingrod 1119, thereby carrying out predetermined actions for compressing gas which is taken in. - Cylindrical
hollow portion 1142 rotates with the rotation ofmain shaft portion 1120 ofshaft 1125.Insertion member 1145 then tries to rotate with the rotation of cylindricalhollow portion 1142, but inreality insertion member 1145 rotates at a number of revolution far smaller than that of cylindricalhollow portion 1142 sinceimpellers 1147 receive strong viscous resistance in the rotational direction withinoil 1102. Thus, there is a difference in the number of revolution between cylindricalhollow portion 1142 andinsertion member 1145, which difference is near the number of revolution ofshaft 1125. Consequently,oil 1102 rises withinspiral groove 1150 while being pulled by the rotation of cylindricalhollow portion 1142. Then,oil 1102 further rises through communicatinghole 1160 by the oil pressure thus generated, passes throughlateral hole 1162, and reaches the sliding area formed by the inner surface of bearing 1116 and the outer surface ofmain shaft portion 1120 to lubricate that area. - At this stage,
oil 1102 rises while rotating not only by the centrifugal force which decreases at low-speed revolution but by a pulling force generated by viscosity. Thus, oil can be drawn up in a stable manner even at the time of low-speed revolution such as 600 rpm. - According to this embodiment, since
component 1151 is rotatably connected to the ceiling of cylindricalhollow portion 1142 only by screw 157 inserted intopenetration 1153, lateral pressure due to fixation is scarcely applied between cylindricalhollow portion 1142 andinsertion member 1145, and there is very few possibility of occurrence of sliding abrasion between cylindricalhollow portion 1142 andinsertion member 1145. It is thus possible to prevent generation of abrasion powder which is circulated with oil toward the sliding area and caught between the sliding components and thus brings about a locked condition of the compressing element. Accordingly, the compressor provided according to this embodiment is highly reliable. - Furthermore, the rotation of
insertion member 1145 is prevented whileimpellers 1147 are receiving strong viscous resistance in the rotational direction withinoil 1102. Thus, indirect fixing ofinsertion member 1145 tostator 1136 as in the conventional example is not needed. Also, since the structure is extremely simple in whichinsertion member 1145 is rotatably connected to the ceiling of cylindricalhollow portion 1142 only byscrew 1157 inserted intopenetration 1153 ofupper region 1152, only a small number of components and processes are required and cost-reduction of the compressor is attained. -
FIG. 13 is a cross-sectional view illustrating a main part of a compressor in a fifth embodiment according to the invention. The fifth embodiment is herein described with reference toFIG. 13 . Similar numbers are given to the structures similar to those of the fourth embodiment, and detailed description of those is omitted. -
Viscous pump 1240 soaked withoil 1102 is provided at the lower end ofmain shaft portion 1220 ofshaft 1225. - Communicating
hole 1241 is coaxially formed withinmain shaft portion 1220.Viscous pump 1240 includes:sleeve 1243 forcedly inserted into communicatinghole 1241 and fixed thereto to form cylindricalhollow portion 1242;insertion member 1246 coaxially and rotatably inserted intosleeve 1243; andimpellers 1247 having a plurality of vanes which are formed integrally withinsertion member 1246. -
Sleeve 1243 is substantially cylindrical and cap-shaped, and hasupper surface 1245 wherescrew hole 1244 is provided.Upper surface 1245 haspath hole 1248 through whichoil 1102 flows. -
Sleeve 1243 is made from iron plate press material which offers comparatively high accuracy and is an appropriate material through whichinsertion member 1246 slides, but may be formed from other suitable materials through whichinsertion member 1246 slides such as plastics and leaf spring steel. - A thread-shaped
spiral projection 1249 is provided on the outer surface ofinsertion member 1246, thereby formingspiral groove 1250 through whichoil 1102 flows betweenspiral projection 1249 andsleeve 1243. -
Insertion member 1246 andimpellers 1247 havecomponent 1251 formed by a shaped plastic component having refrigerant-resistance and oil-resistance properties.Component 1251 is hollow and hasupper region 1252 wherepenetration 1253 is provided.Screw 1257 inserted throughpenetration 1253 is screwed intoscrew hole 1244 viawasher 1257 a to rotatably connectcomponent 1251 toupper surface 1245. -
Washer 1257 a is made from 4-fluorinated ethylene and controls the sliding withcomponent 1251 in the thrust direction. - Communicating
hole 1241 opens to a sliding area formed by the inner surface of bearing 1116 and the outer surface ofmain shaft portion 1220 to communicate with the sliding area throughlateral hole 1262. - The operation of the compressor having the above structure is now described.
- When
stator 1136 is energized by the inverter driving circuit,rotor 1137 rotates withshaft 1225. - In accordance with the rotation of
main shaft portion 1220 ofshaft 1225, cylindricalhollow portion 1242 formed bysleeve 1243 rotates.Insertion member 1246 then tries to rotate with the rotation of cylindricalhollow portion 1242, but inreality insertion member 1246 rotates at a number of revolution far smaller than that of cylindricalhollow portion 1242 sinceimpellers 1247 receive strong viscous resistance in the rotational direction withinoil 1102. Thus, there is a difference in the number of revolution between cylindricalhollow portion 1242 andinsertion member 1246, which difference is near the number of revolution ofshaft 1225. Consequently, oil rises throughspiral groove 1250 while being pulled by the rotation of cylindricalhollow portion 1242. Then,oil 1102 further rises throughpath hole 1248 in communicatinghole 1241 by the oil pressure thus caused, passes throughlateral hole 1262, and reaches the sliding area formed by the inner surface of bearing 1116 and the outer surface ofmain shaft portion 1220 to lubricate that area. - At this stage,
oil 1102 rises while rotating not only by the centrifugal force which decreases at low-speed revolution but by a pulling force generated by viscosity. Thus, oil can be drawn up in a stable manner even at the time of low-speed revolution such as 600 rpm. - According to this embodiment,
component 1251 is rotatably connected toupper surface 1245 viawasher 1257 a only byscrew 1257 inserted throughpenetration 1253. Thus, lateral pressure due to fixation is scarcely applied betweensleeve 1243 andinsertion member 1246, and there is very few possibility of occurrence of sliding abrasion betweensleeve 1243 andinsertion member 1246. It is thus possible to prevent generation of abrasion powder which is circulated with oil and caught between the sliding components and thus brings about a locked condition of the compressing element. Accordingly, the compressor provided according to this embodiment is highly reliable. - A force in the downward direction as a reaction to a force for pushing up
oil 1102 is applied tosleeve 1243. The downward force is given to the sliding surface as a load in the thrust direction. The sliding area exists at the position betweenupper surface 1245 ofsleeve 1243 andwasher 1257 a in this embodiment, but extreme abrasion at that position is prevented by the self-lubrication ability ofwasher 1257 a which is made from 4-fluorinated ethylene. - The rotation of
insertion member 1246 is prevented whileimpellers 1247 are receiving strong viscous resistance in the rotational direction withinoil 1102. Thus, indirect fixing ofinsertion member 1246 tostator 1136 as in the conventional example is not needed. Also, since the structure is extremely simple in whichinsertion member 1246 is rotatably connected toupper surface 1245 viawasher 1257 a only byscrew 1257 inserted throughpenetration 1253 ofupper region 1252, only a small number of components and processes are required and thus cost-reduction of the compressor can be attained. - In this embodiment,
viscous pump 1240 is assembled in advance as an independent component by joiningsleeve 1243 andcomponent 1251 byscrew 1257 inserted viawasher 1257 a. Afterrotor 1137 is forcedly fitted toshaft 1225,viscous pump 1240 as the independent component is forcedly fitted to communicatinghole 1241 to complete the assembly. Thus, drastically practical and enhanced productivity can be attained. -
FIG. 14 is a cross-sectional view illustrating a main part of a compressor in a sixth embodiment according to the present invention. The sixth embodiment is herein described with reference toFIG. 14 . Similar numbers are given to the structures similar to those of the fourth embodiment, and detailed description of those is omitted. -
Viscous pump 1340 soaked withoil 1102 is provided at the lower end ofmain shaft portion 1320 ofshaft 1325. - Communicating
hole 1341 is coaxially formed withinmain shaft portion 1320.Viscous pump 1340 includes:sleeve 1343 forcedly inserted into communicatinghole 1341 and fixed thereto to form cylindricalhollow portion 1342;insertion member 1346 coaxially and rotatably inserted intosleeve 1343; andimpellers 1347 having a plurality of vanes which are formed separately frominsertion member 1346. -
Sleeve 1343 is substantially cylindrical and cap-shaped, and hasbottom surface 1345 whererod hole 1344 is formed at its center.Bottom surface 1345 haspath hole 1348 through whichoil 1102 flows.Sleeve 1343 is made from iron plate press material which offers comparatively high accuracy and is an appropriate material through which insertion member 1336 slides, but may be formed from other suitable materials through which insertion member 1336 slides such as plastics and leaf spring steel. -
Insertion member 1346 is formed by a shaped plastic component having refrigerant-resistance and oil-resistance properties and has thread-shapedspiral projection 1349 on its outer surface, thereby formingspiral groove 1350 through whichoil 1102 flows betweenspiral projection 1349 andsleeve 1343.Bottom region 1352 has a small-diameter hole 1353. - In this embodiment,
impellers 1347 are stamped out from thin iron plate, androd 1349 made from steel wire which is resistance-welded toimpellers 1347 is forcedly inserted throughrod hole 1344 into small-diameter hole 1353 formed onbottom region 1352 to be fixed thereto. Communicatinghole 1341 opens to a sliding area formed by the inner surface of bearing 1116 and the outer surface ofmain shaft portion 1320 throughlateral hole 1362 to communicate with the sliding area. - The operation of the compressor having the above structure is now described. When
stator 1136 is energized by the inverter driving circuit,rotor 1137 rotates withshaft 1325. In accordance with the rotation ofmain shaft portion 1320 ofshaft 1325, cylindricalhollow portion 1342 formed bysleeve 1343 rotates.Insertion member 1346 tries to rotate with the rotation of cylindricalhollow portion 1342, but inreality insertion member 1346 rotates at a number of revolution far smaller than that of cylindricalhollow portion 1342 sinceimpellers 1347 receive strong viscous resistance in the rotational direction withinoil 1102. Thus, there is a difference in the number of revolution between cylindricalhollow portion 1342 andinsertion member 1346, which difference is near the number of revolution ofshaft 1325. Consequently, the oil having entered throughpath hole 1348 rises throughspiral groove 1350 while being pulled by the rotation of cylindricalhollow portion 1342. Then, the oil further rises through communicatinghole 1341 by the oil pressure thus generated, passes throughlateral hole 1362, and reaches the sliding area formed by the inner surface of bearing 1116 and the outer surface ofmain shaft portion 1320 to lubricate that area. - At this stage,
oil 1102 rises while rotating not only by the centrifugal force which decreases at low-speed revolution but by a pulling force generated by viscosity. Thus, oil can be drawn up in a stable manner even at the time of low-speed revolution such as 600 rpm. - According to this embodiment,
insertion member 1346 andsleeve 1343 provide a thrust sliding area formed bybottom region 1352 andbottom surface 1345 which rotatably contact with each other. Thus, lateral pressure due to fixation is scarcely applied betweensleeve 1343 andinsertion member 1346, and there is very few possibility of occurrence of sliding abrasion betweensleeve 1343 andinsertion member 1346. It is thus possible to prevent generation of abrasion powder which is circulated with oil toward the sliding area and caught between the sliding components and thus brings about a locked condition of the compressing element. Accordingly, the compressor provided according to this embodiment is highly reliable. - A force in the downward direction as a reaction to a force for pushing up
oil 1102 is applied tosleeve 1343. The downward force is given to the thrust sliding area forming by above mentionedbottom region 1352 andbottom surface 1345 as a load in the thrust direction. In this embodiment, the surface pressure applied to the thrust sliding area can be reduced by wideningbottom surface 1345 ofsleeve 1343, thereby improving abrasion resistance. - While not shown in the above respective embodiments, a spacer having abrasion resistance such as 4-fluorinated ethylene and valve steel may be interposed between
bottom region 1352 andbottom surface 1345 to further enhance abrasion resistance. - The rotation of
insertion member 1346 is prevented whileimpellers 1347 are receiving strong viscous resistance in the rotational direction withinoil 1102. Thus, indirect fixing ofinsertion member 1346 tostator 1136 by a component for preventing the rotation ofinsertion member 1346 as in the conventional example is not needed. Also, since the structure is extremely simple, only a small number of components and processes are required and thus cost-reduction of the compressor can be attained. - According to the above respective embodiments,
viscous pump 1340 is assembled in advance as an independent component by insertinginsertion member 1346 intosleeve 1343 and forcedly insertingrod 1349 to whichimpellers 1347 are fixed throughrod hole 1344 into small-diameter hole 1353 formed onbottom region 1352. Afterrotor 1137 is forcedly inserted intoshaft 1325,viscous pump 1340 as the independent component is forcedly inserted into communicatinghole 1341 to complete the assembly. Thus, drastically practical and enhanced productivity can be attained. - While the spiral projection is provided on the insertion member in the fourth through sixth embodiments, the spiral projection may be disposed on the cylindrical hollow portion to similarly form the spiral groove through which oil flows.
- While description is made based on the reciprocating internal suspended-type compressor in the fourth through sixth embodiments, the present invention is applicable to internal fixed-type compressors such as vertical rotary-type compressors and scroll-type compressors as long as the lower end of their shafts extends to reach oil.
- Types of gas and oil are not specifically limited. Needless to say, the advantages of the invention can be generally offered in any combination of all types of refrigerant involving environment-protective refrigerant such as HFC, HC and CO2 and all types of oil involving oil compatible with those refrigerant by employing the above materials having gas-resistance and oil-resistance properties for the components included in the viscous pump.
- According to the invention as described above, a component for fixing the insertion member to the stator is not required, and thus a highly reliable and inexpensive compressor can be provided.
- Another advantage offered according to the invention is that a material having high abrasion resistance can be used to further enhance reliability.
- Another advantage offered according to the invention is that the viscous pump is assembled into one piece in advance, and thus a further inexpensive compressor can be provided.
- Another advantage offered according to the invention is that the viscous pump assembled into one piece in advance, and thus a further inexpensive compressor can be provided.
- Another advantage offered according to the invention is that the viscous pump is incorporated in the compressor which is elastically supported, and thus a highly reliable and inexpensive compressor can be provided.
- Another advantage offered according to the invention is that the compressor is driven at a low-speed revolution, and thus a highly reliable and inexpensive compressor can be provided.
- The force for pulling oil due to viscosity increases as the contact area between the inner surface of the rotational body and oil increases. However, the contact surface is chiefly formed by the flat smooth surface of
sleeve 7112 and only insufficient force is applied to oil in the structure of the conventional example. - Additionally, there is a clearance between the end surface of spiral projection 7121 and the inner surface of
sleeve 7112, which clearance is positioned at the outermost surface ofinsertion member 7120 in the conventional structure. The centrifugal force generated through the rotation ofshaft 7111 is applied to oil within the oil passage formed by the spiral groove and the inner surface ofsleeve 7112, and oil rises while rotating and inclining toward the inside surface. Thus, oil falls to flow out through the clearance between spiral projection 7121 and inner surface ofsleeve 7112 and the oil supply amount to the upper area decreases. - Accordingly, especially in an extremely low driving frequency range such as 600 to 1,200 r/min., the force for pulling oil due to viscosity decreases and also the amount of oil which falls to flow out through the clearance between
sleeve 7112 andinsertion member 7120 increases. In this case, a sufficient oil amount cannot be transferred to the sliding area positioned above. - It is therefore an object of the present invention to provide a compressor capable of drawing up a sufficient amount of oil with efficiency even at the time of low-speed revolution.
- Compressors in seventh and eighth embodiments are herein described with reference to the drawings.
-
FIG. 15 is a cross-sectional view of a compressor in the seventh embodiment of the invention;FIG. 16 is across-sectional view illustrating a main part of the compressor in the seventh embodiment. - In
FIGS. 15 and 16 ,oil 2102 is stored inclosed container 2101 which is filled withrefrigerant gas 2103. - Compressing
element 2110 includes: block 2115 which formscylinder 2113;piston 2117 reciprocatively inserted intocylinder 2113;shaft 2125 havingmain shaft portion 2120 supported by bearing 2116 ofblock 2115 andeccentric portion 2122; and connectingrod 2119 for connectingeccentric portion 2122 andpiston 2117. Compressingelement 2110 forms a reciprocating compressing mechanism. - Electrically-powered
element 2135 is fixed belowblock 2115. Electrically-poweredelement 2135 includesstator 2136 connected to an inverter driving circuit (not shown) androtor 2137 which contains permanent magnet and is fixed tomain shaft portion 2120, thus providing an electrically-powered element for driving the inverter. -
Springs 2139 elasticallysupport compressing element 2110 viastator 2136 such that compressingelement 2110 can be elastically held on closedcontainer 2101. -
Viscous pump 2140 soaked withoil 2102 is provided at the lower end ofmain shaft portion 2120 ofshaft 2125.Viscous pump 2140 includes: cylindricalhollow portion 2142 formed in the lower region ofmain shaft portion 2120;insertion member 2145 coaxially inserted into cylindricalhollow portion 2142; and substantially-U-shaped bracket 2143 both ends of which are fixed to the lower region ofstator 2136.Bracket 2143 engages with the lower end ofinsertion member 2145 to supportinsertion member 2145 such thatinsertion member 2145 cannot rotate. - Thread-shaped
spiral projection 2149 is formed on the inner surface of cylindricalhollow portion 2142 to provide a spiral groove through whichoil 2102 is allowed to flow betweenspiral projection 2149 andinsertion member 2145. -
Insertion member 2145 is hollow and a shaped component made from resin having refrigerant-resistance and oil-resistance properties.Insertion member 2145 hasbracket insertion portion 2146 and riseprevention member 2147.Insertion member 2145 floats inside the cylindrical hollow portion, but is prevented from rising too high and rotating therein. - The operation of the compressor having the above structure is now described. When
stator 2136 is energized by the inverter driving circuit,rotor 2137 rotates withshaft 2125. The eccentric motion ofeccentric portion 2122 thus caused reciprocatespiston 2117 withincylinder 2113 via connectingrod 2119, thereby carrying out predetermined actions for compressing gas which is taken in. - In accordance with the rotation of
main shaft portion 2120 ofshaft 2125, cylindricalhollow portion 2142 rotates.Insertion member 2145 engages with the center portion of substantiallyU-shaped bracket 2143 both ends of which are fixed to the lower region ofstator 2136 to be supported bybracket 2143 in such a manner as not to rotate. In this structure, oil rises through the spiral groove while being pulled by the rotation of cylindricalhollow portion 2142. Then, oil further rises through communicatinghole 2160 by the oil pressure thus caused, passes throughlateral hole 2162, and finally reaches a sliding area formed by the inner surface of bearing 2116 and the outer surface ofmain shaft portion 2120 to lubricate that area. - At this stage,
oil 2102 rises while rotating not only by the centrifugal force which decreases at low-speed revolution but by a pulling force generated by viscosity. In addition,spiral projection 2149 is formed on the cylindrical hollow portion to enlarge the area of the inner surface of the rotational body in contact with oil by adding the surface area ofspiral projection 2149 in this embodiment. This structure causes large viscous resistance, thereby enhancing oil transfer capability. - Furthermore, centrifugal force generated by the rotation of
shaft 2120 is applied to oil existing in the space between the spiral groove formed on the inner surface of cylindricalhollow portion 2142 andinsertion member 2145. Thus, oil rises while rotating and inclining toward the roots of the spiral groove, i.e., the farthermost surface from the rotational shaft center ofshaft 2120. Structurally there is no clearance in the vicinity of the roots of the spiral groove to which the centrifugal force is applied. Accordingly, oil does not fall to flow out, thereby preventing fall and outflow of oil. - As described above, enhanced oil transfer capability can be realized, allowing drawing up oil in a stable manner even at the time of low-speed revolution such as 600 r/min.
- According to this embodiment, the compressing element is elastically supported, and
insertion member 2145 engages with the center ofbracket 2143 made from an elastic body to float within cylindricalhollow portion 2142 without rotating. Thus, lateral pressure due to fixation is scarcely applied between cylindricalhollow portion 2142 andinsertion member 2145, and there is very few possibility of occurrence of sliding abrasion between cylindricalhollow portion 2142 andinsertion member 2145. It is thus possible to prevent generation of abrasion powder which is circulated with oil toward the sliding area and caught between the sliding components and thus brings about a locked condition of the compressing element. Accordingly, the compressor provided according to this embodiment is highly reliable. -
FIG. 17 is a cross-sectional view illustrating a main part of a compressor in an eighth embodiment of the invention; andFIG. 18 is an assembly view of the main part in the eighth embodiment. The eighth embodiment is herein described with reference toFIGS. 17 and 18 . Similar numbers are given to the structures similar to those of the seventh embodiment, and detailed description of those is omitted. - Viscous pump 2240 soaked with
oil 2102 is provided at the lower end ofmain shaft portion 2220 of shaft 2225. - Communicating
hole 2260 andsleeve attachment hole 2254 are coaxially formed withinmain shaft portion 2220. Viscous pump 2240 includes:sleeve 2251 which is forcedly inserted intosleeve attachment hole 2254 to be fixed thereto and forms cylindricalhollow portion 2242;coil spring 2253 secured to the inner surface ofsleeve 2251 as a spiral member;insertion member 2145 coaxially and rotatably inserted intosleeve 2251; andbracket 2143.Bracket 2143 which is made from an elastic body is substantially U-shaped, both ends of which are fixed to the lower region ofstator 2136. The center ofbracket 2143 engages with the lower end ofinsertion member 2145 to supportinsertion member 2145 in such a manner that insertion member cannot rotate. -
Sleeve 2251 is substantially cylindrical and cap-shaped, whose top and bottom are open.Sleeve 2251 hasspring holder 2252 at its lower end.Sleeve 2251 is made from iron plate press material which offers comparatively high accuracy, but may be formed from other materials such as leaf spring steel. - The length of
coil spring 2253 is larger than the total length of the inner surface ofsleeve 2251 from which the height of thespring holder 2252 is subtracted.Coil spring 2253 is made from oil temper wire for springs (JIS:SWOV) in this embodiment, but may be made from other material including iron steel such as piano wire (JIS:SWP) and spring steel (JIS:SUP), non-iron metal such as aluminum, and resins whose thermal deformation temperature is 100° C. or higher and which has high formability such as polycarbonate (PC) and polyamide (PA). -
Cylindrical hole 2255 formed by the lowermost end surface ofmain shaft portion 2220 has one step to provide a smaller-diameter hole.Sleeve attachment hole 2254 in to which a predetermined length ofsleeve 2251 is forcedly inserted is formed in a hole on the first step, while communicatinghole 2260 is formed in a hole on the second step. The inner surface diameter of communicatinghole 2260 is slightly smaller than the inner surface diameter of sleeve 225 i.Coil spring 2253 is compressed betweenspring holder 2252 at the lower end of the sleeve and the step formed by the difference in the inner surface diameter betweensleeve 2251 and communicatinghole 2260 to be fixed to the inner surface ofsleeve 2251. -
Insertion member 2145 is formed by a shaped resin component having refrigerant-resistance and oil-resistance properties in this embodiment, but may be comparatively light metal such as aluminum.Insertion member 2145 is a hollow component, and hasbracket insertion portion 2146 and riseprevention member 2147.Insertion member 2145 floats inside the cylindrical hollow portion, but is prevented from rising too high and rotating therein. - The operation of the compressor having the above structure is now described.
- When
stator 2136 is energized by the inverter driving circuit,rotor 2137 rotates withshaft 2125. Then, operations similar to those in the seventh embodiment are performed to supply oil. - According to this embodiment, the structure which uses the shape of the coil spring itself as the spiral groove provided on the inner surface of the lower end of the shaft can be far more easily formed than the structure in which a spiral groove is directly engraved on the inner surface of the lower end of the shaft. From the viewpoint of energy saving, the amount of oil transfer can be appropriately controlled by replacing the coil spring with the one having a different wire diameter, wire cross-sectional shape, number of winding etc., in accordance with the driving frequency required by the system side such as household refrigerators and air conditioners. Thus, the compressor of this embodiment is highly flexible and capable of meeting a wide variety of demands. Moreover, by forcedly inserting
sleeve 2251 provided withcoil spring 2253 on its inner surface in advance intosleeve attachment hole 2254 formed coaxially withmain shaft portion 2220,sleeve 2251 is attached to the lower end region ofmain shaft portion 2220 and simultaneouslycoil spring 2253 is compressed betweenspring holder 2252 at the lower end of the sleeve and the step formed by the difference in the inner surface diameter betweensleeve 2251 and communicatinghole 2260 to be fixed to the inner surface ofsleeve 2251. Accordingly, the formation of the spiral groove necessary for transferring oil upward is easily completed, and thus considerably practical and high productivity can be achieved. - According to the present invention as described above, it is possible to secure a wide area in contact with oil which causes viscous resistance needed for the rotational rising movement of oil. Accordingly, the force for pulling oil due to viscosity increases and thus an enhanced oil transfer capability can be obtained.
- Another advantage of the invention is that the assembly in this embodiment which uses the shape of the coil spring itself as the spiral groove is more facilitated than in an example in which a groove is engraved. Also, the amount of oil transfer can be appropriately controlled by replacing the coil spring with the one having a different wire diameter, wire cross-sectional shape, number of winding etc., which enhances the flexibility. Further, the spiral groove formed by the coil spring is simultaneously provided when the sleeve is forcedly inserted, which increases the productivity.
- Another advantage of the invention is that power consumption of household refrigerators and air-conditioners is reduced since input to the compressor is decreased during low-speed driving and oil supply is stabilized.
- Another advantage of the invention is that the insertion member floats but not rotates inside the cylindrical hollow portion during the operation of the compressing element. This provides a structure in which oil is pulled by viscosity and also prevents abrasion and chipping due to the contact and collision between the inner surface of the cylindrical hollow portion and the outer surface of the insertion member which damages may lead to deterioration of the pumping ability and bring about excessive abrasion and a locked condition of the compressing element. Accordingly, long-term reliability can be secured.
- Another advantage of the invention is that the components included are not required to be fixed on the closed container. Since the insertion member only floats inside the cylindrical hollow portion, lateral pressure due to fixation is scarcely applied between the cylindrical hollow portion and the insertion member and there is very few possibility of occurrence of sliding abrasion between the cylindrical hollow portion and the insertion member. Thus, a highly reliable compressor which includes the viscous pump and is elastically supported can be provided.
- In the above-described conventional structure,
bracket 7115 andinsertion member 7120 engage with each other through longitudinal groove 7521. Thus, the wall surface of the longitudinal groove ofinsertion member 7120 collides with engagement portion 7523 ofbracket 7115 at every start-up, and the wall surface of the longitudinal groove is kept pressed thereon during continuous driving. As a result, abrasion occurs due to rubbing of the engagement portion, orbracket 7115 is twisted and the stress is concentrated on the bended portion or other position ofbracket 7115, which causes fatigue to develop for a period of time. - When abrasion and fatigue thus caused further develop, thin film projections (extrusion) and depression of cracks (intrusion) occur at the engagement portion and the bended portion. Especially, the depression develops into visual minute cracks, which gradually spread to finally cause corruption of
bracket 7115. In this case, the rotation ofinsertion member 7120 insidesleeve 7112 may not be restricted. - Thus, it is difficult to maintain the structure of
viscous pump 7113 in a stable condition for a long period of time. - For solving the above problem, an object of the present invention is to provide a highly reliable compressor capable of maintaining the structure of
viscous pump 7113 for a long-term period without causing abrasion and fatigue by the contact between components at the time of restriction of the rotation ofinsertion member 7120. - Ninth and tenth embodiments according to the present invention are now described with reference to the drawings. However, the invention is not limited to those embodiments.
-
FIG. 19 is a cross-sectional view illustrating a compressor in the ninth embodiment of the invention, andFIG. 20 is a cross-sectional view illustrating a main part of the compressor in the ninth embodiment. - In
FIGS. 19 and 20 ,oil 4102 is stored inclosed container 4101 which is filled withrefrigerant gas 4103. - Compressing
element 4110 includes: block 4115 which formscylinder 4113;piston 4117 reciprocatively inserted intocylinder 4113;shaft 4125 havingmain shaft portion 4120 supported by bearing 4116 ofblock 4115 andeccentric portion 4122; and connectingrod 4119 for connectingeccentric portion 4122 andpiston 4117. Compressingelement 4110 forms a reciprocating compressing mechanism. - Electrically-powered
element 4135 is fixed belowblock 4115, and includesstator 4136 connected to an inverter driving circuit (not shown) androtor 4137 which contains permanent magnet and is fixed tomain shaft portion 4120. Electrically-poweredelement 4135 provides an electric motor for driving the inverter, and is driven at a plurality of driving frequencies including those below 20 Hz, for example, by the inverter driving circuit (not shown). -
Springs 4139 elasticallysupport compressing element 4110 viastator 4136 such that compressingelement 4110 is elastically held on closedcontainer 4101. -
Viscous pump 4140 soaked withoil 4102 is provided at the lower end ofmain shaft portion 4120 ofshaft 4125. - Next, the structure of
viscous pump 4140 is described in detail. - Cylindrical
hollow portion 4141 is formed inmain shaft portion 4120.Hollow sleeve 4142 is fixed to the lower region of cylindricalhollow portion 4141.Sleeve 4142 is substantially cylindrical and cap-shaped, whose top and bottom are open.Sleeve 4142 is made from iron plate press material which offers comparatively high accuracy in this embodiment, but may be formed from leaf spring steel. -
Insertion member 4143 coaxially inserted into cylindricalhollow portion 4141 andsleeve 4142 is made from a plastic material which has lower thermal conductivity than the metal material which formsshaft 4125 and possesses refrigerant-resistance and oil-resistance properties such as PPS, PBT, and PEEK.Spiral groove 4144 is engraved on the outer surface ofinsertion member 4143, wherebyoil passage 4145 through which oil flows is provided betweenspiral groove 4144 and the inner surface ofsleeve 4142. The difference between the outermost diameter ofinsertion member 4143 and the inside diameter ofsleeve 4142, i.e., the matching clearance is established in a range from 100 μm to 500 μm.Insertion member 4143 hasbolt hole 4146 at its upper end surface, and a plurality ofarms 4147 at its lower sides which extend substantially in the horizontal direction. -
Bolt 4150 is employed as supportingmember 4152 for slidingly connectinginsertion member 4143 withsleeve 4142.Bolt 4150 inserted throughwasher 4151 penetratesbolt hole 4146 and reaches the upper surface of cylindricalhollow portion 4141 to be attached thereto, thereby rotatably connectinginsertion member 4143 tomain shaft portion 4120 ofshaft 4125 and closing the lower end ofbolt hole 4146.Washer 4151 is made from a plastic material having high abrasion-resistance property such as self-lubrication characteristic (PPS, PEE and PEEK etc.). Alternatively,bolt 4150 may be formed from a similar self-lubrication material to eliminatewasher 4151. - First
permanent magnet 4148 is fixed to eacharm 4147 which is disposed on the lower sides ofinsertion member 4143 to extend substantially in the horizontal direction. Also, each secondpermanent magnet 4149 is provided on the inner surface of the bottom ofclosed container 4101 via joint 4153 such that the S-pole of secondpermanent magnet 4149 is opposed to the S-pole of firstpermanent magnet 4148 in the rotational direction with a predetermined space therebetween sufficiently within the reach of magnetic force. Alternatively, the N-poles of bothpermanent magnets - The operation of the compressor having the above structure is herein described.
-
Main shaft portion 4120 rotates with the rotation ofshaft 4125.Sleeve 4142 fixed tomain shaft portion 4120 rotates in synchronization with the rotation ofmain shaft portion 4120.Insertion member 4143 is pulled by the rotation ofsleeve 4142, but the rotation ofinsertion member 4143 is prevented by the repulsion between the same poles of firstpermanent magnet 4148 provided on the insertion member and secondpermanent magnet 4149. As a result, oil rises throughoil spiral passage 4145 while rotating and being pulled by the inner surface ofsleeve 4142 due to viscosity. - At this stage,
oil 4102 rises while rotating not only by the centrifugal force which decreases at low-speed revolution but by a pulling force generated by viscosity. Thus,oil 4102 can be drawn up in a stable manner even at the time of low-speed revolution such as 600 rpm. - According to this embodiment as described above, the rotation of
insertion member 4143 is prevented by a non-contact method utilizing the repulsion between firstpermanent magnet 4148 and secondpermanent magnet 4149, causing no abrasion and fatigue by the contact between the components in relation to the restriction ofinsertion member 4143. Accordingly, the structure ofviscous pump 4140 is maintained in a stable condition for a long period of time, and thus a highly reliable compressor can be provided. - According to this embodiment, second
permanent magnet 4149 is disposed in the vicinity of the inner surface of the bottom ofclosed container 4101 for the structural reason of the compressor. Thus,joints 4153 require not a complicated but an extremely simple structure so as to secure secondpermanent magnet 4149 to closedcontainer 4101. - Second
permanent magnet 4149 is directly or indirectly fixed onclosed container 4101, but is kept prevented from contacting with firstpermanent magnet 4148 since the same poles are opposed. Consequently, sound and vibration generated from compressingelement 4110 and electrically-poweredelement 4135 are not transmitted though firstpermanent magnet 4148 and secondpermanent magnet 4149 to closedcontainer 4101. - According to this embodiment,
insertion member 4143 is rotatably connected tomain shaft portion 4120 ofshaft 4125 by means ofbolt 4150 which is inserted throughwasher 4151. Thus, the position ofinsertion member 4143 relative tosleeve 4142 fixed at the lower end ofmain shaft portion 4120 is determined by this connecting portion, and an almost constant clearance is maintained betweeninsertion member 4143 andsleeve 4142. This clearance is maintained by the fact that lateral pressure due to fixation is scarcely caused and also that the oil pressure is generated betweeninsertion member 4143 andsleeve 4142. Accordingly, there is very few possibility of occurrence of sliding abrasion betweeninsertion member 4143 andsleeve 4142. -
Spiral groove 4144 is provided on the outer surface ofinsertion member 4143 to formspiral oil passage 4145 in this embodiment, but may be disposed on the inner surface ofsleeve 4142 to formoil passage 4145. In this case, the area of the inner surface of the rotational body in contact withoil 4102 is enlarged by adding the surface area of the concaves of the spiral groove. This structure causes large viscous resistance, thereby enhancingoil 4102 transfer capability. Moreover, centrifugal force generated through the rotation ofmain shaft portion 4120 is applied tooil 4102 existing within theoil passage 4145 formed between the inner surface ofsleeve 4142 and the outside surface ofinsertion member 4143, and the oil rises while rotating and inclining toward the farthermost surface from the rotational shaft center inoil passage 4145. Since there is no clearance in the position to which the centrifugal force is most applied, oil does not fall to flow out and thus the amount of oil which falls to flow out can be decreased. Accordingly, the compressor in this embodiment obtains considerably higher oil transfer capability than the example in which spiralgroove 4144 is formed oninsertion member 4143. -
FIG. 21 is a cross-sectional view illustrating a compressor in a tenth embodiment of the invention, andFIG. 22 is a cross-sectional view illustrating a main part of the compressor in the tenth embodiment. - The tenth embodiment is herein described with reference to
FIGS. 21 and 22 . Similar numbers are given to the structures similar to those of the ninth embodiment, and detailed description of those is omitted. -
Viscous pump 4240 soaked withoil 4202 is provided at the lower end ofmain shaft portion 4120 ofshaft 4125. - Next, the structure of
viscous pump 4240 is described in detail. - Cylindrical
hollow portion 4241 is formed inmain shaft portion 4120.Hollow sleeve 4242 is fixed to the lower region of cylindricalhollow portion 4241.Sleeve 4242 is substantially cylindrical and cap-shaped, whose top and bottom are open.Sleeve 4242 is made from iron plate press material which offers comparatively high accuracy in this embodiment, but may be formed from leaf spring steel. -
Insertion member 4243 coaxially inserted into cylindricalhollow portion 4241 andsleeve 4242 is made from a plastic material which has lower thermal conductivity than the metal material which formsshaft 4125 and possesses refrigerant-resistance and oil-resistance properties such as PPS, PBT, and PEEK.Spiral groove 4244 is engraved on the outer surface ofinsertion member 4243, wherebyoil passage 4245 through which oil flows is provided betweenspiral groove 4244 and the inner surface ofsleeve 4242. The difference between the outermost diameter ofinsertion member 4243 and the inside diameter ofsleeve 4242, i.e., the matching clearance is established in a range from 100 μm to 500 μm.Insertion member 4243 hasbolt hole 4246 at its upper end surface, and a plurality ofarms 4247 at its lower sides which extend substantially in the horizontal direction. -
Bolt 4250 is employed as supportingmember 4252 for slidingly connectinginsertion member 4243 withsleeve 4242.Bolt 4250 inserted throughwasher 4251 penetratesbolt hole 4246, and reaches the upper surface of cylindricalhollow portion 4241 to be attached thereto, thereby rotatably connectinginsertion member 4243 tomain shaft portion 4120 ofshaft 4125 and closing the lower end ofbolt hole 4246.Washer 4251 is made from a plastic material having high abrasion-resistance property such as self-lubrication characteristic (PPS and PEEK etc.). Alternatively,bolt 4250 may be formed from a similar self-lubrication material to eliminatewasher 4251. - First
permanent magnet 4248 is fixed to eacharm 4247 which is disposed on the lower sides ofinsertion member 4243 to extend substantially in the horizontal direction. Also, each secondpermanent magnet 4249 is provided such that the S-pole of secondpermanent magnet 4249 is opposed to the S-pole of firstpermanent magnet 4248 in the rotational direction with a predetermined space therebetween sufficiently within the reach of magnetic force. Each secondpermanent magent 4249 is fixed on one end of substantially L-shaped joint 4253 the other end of which is secured to the lower region ofstator 4136. The N-poles of bothpermanent magnets - The operation of the compressor having the above structure is herein described.
-
Main shaft portion 4120 rotates with the rotation ofshaft 4125.Sleeve 4242 fixed tomain shaft portion 4120 rotates in synchronization with the rotation ofmain shaft portion 4120.Insertion member 4243 is pulled by the rotation ofsleeve 4242, but the rotation ofinsertion member 4243 is prevented by the repulsion between the same poles of firstpermanent magnet 4248 provided on the insertion member and secondpermanent magnet 4249. As a result, oil rises throughoil spiral passage 4245 while rotating and being pulled by the inner surface ofsleeve 4242 due to viscosity. - At this stage,
oil 4202 rises while rotating not only by the centrifugal force which decreases at low-speed revolution but by a pulling force generated by viscosity. Thus, oil can be drawn up in a stable manner even at the time of low-speed revolution such as 600 rpm. - According to this embodiment as described above, the rotation of
insertion member 4243 is restrained by a non-contact method through the same mechanism as in the ninth embodiment, causing no abrasion and fatigue by the contact between the components in relation to the restriction ofinsertion member 4243. Accordingly, the structure ofviscous pump 4240 is maintained in a stable condition for a long period of time, and thus a highly reliable compressor can be provided. - According to this embodiment,
insertion member 4243 having firstpermanent magnets 4248 is connected tomain shaft portion 4120 viabolt 4250, and secondpermanent magnets 4249 are secured to the lower region ofstator 4136 viajoints 4253. It is thus possible to attach all the components included inviscous pump 4240 to electrically-poweredelement 4135 or compressingelement 4110 in advance, and assembly is facilitated and productivity is enhanced by collectively installing those components inclosed container 4101. - Second
permanent magnets 4249 are fixed to the lower part of electrically-poweredelement 4135 havingstator 4136 throughjoints 4253 in this embodiment, but may be secured to any component of compressingelement 4110 such asblock 4115 throughjoints 4253. - As described above, no abrasion and fatigue by the contact between the components in relation to the restriction of the insertion member are caused in the invention and the structure of the viscous pump is maintained in a stable condition for a long period of time. Thus, a highly reliable compressor can be provided.
- In the invention, the structure is considerably simple and the second permanent magnets are kept prevented from contacting with the first permanent magnets since the same poles are opposed. As a result, sound and vibration generated from the compressing element and the electrically-powered element are not transmitted through the first permanent magnets and the second permanent magnets to the outside of the closed container, and thus a highly reliable compressor can be provided.
- In the invention, it is possible to attach all the components included in the viscous pump to the electrically-powered element or the compressing element in advance and collectively install these components in the closed container. Accordingly, assembly is facilitated and productivity is increased, and thus a highly reliable compressor can be provided.
- In the invention, generation of abnormal sound caused by vibration is prevented, and thus a highly reliable compressor can be provided.
- In the invention, input to the compressor which drives at driving frequencies including at least in a range from 600 to 1,200 r/min. is reduced and the structure of the viscous pump is maintained in a stable condition for a long period of time. Accordingly, power consumption is lowered and thus a highly reliable compressor is provided.
- In the invention, the rotation of the insertion member is prevented by a non-contact method utilizing repulsion between the permanent magnets. Accordingly, no abrasion and fatigue by the contact between the components in relation to the restriction of the insertion member are caused and the structure of the viscous pump is maintained in a stable condition for a long period of time. Thus, a highly reliable compressor can be provided.
- The structure of the viscous pump can be maintained in a stable condition for a long period of time by preventing the rotation of the insertion member by a non-contact method, and thus a highly reliable compressor can be provided.
- In the conventional structure in which
bracket 7115 supports the weight ofinsertion member 7120 at two points,insertion member 7120 inserted intosleeve 7112 is inclined andcontacts sleeve 7112. Whenbracket 7115 does not have high dimensional accuracy or the center of gravity ofinsertion member 7120 is off the shaft center, the contact between the upper end of longitudinal groove 7621 provided at the lower end ofinsertion member 7120 and bracket 15 becomes a point contact. In this case, abrasion or fixation betweensleeve 7112 andinsertion member 7120 may be caused, resulting in deterioration of the pumping ability and generation of abrasion powder which is circulated with oil toward the sliding area and caught between the sliding components and brings about a locked condition of the compressing element. - An object of the present invention is to provide a highly reliable compressor.
- Eleventh through thirteenth embodiments are herein described with reference to the drawings. The invention is not limited to those embodiments.
-
FIG. 23 is a cross-sectional view illustrating a compressor in the eleventh embodiment of the invention,FIG. 24 is a cross-sectional view illustrating a main part of the compressor in the eleventh embodiment, andFIG. 25 is an enlarged view illustrating a main part of an insertion member in the eleventh embodiment. - In
FIGS. 23, 24 and 25,oil 5102 is stored inclosed container 5101 which is filled withrefrigerant gas 5103. - Compressing
element 5110 includes: block 5115 which formscylinder 5113;piston 5117 reciprocatively inserted intocylinder 5113;shaft 5125 havingmain shaft portion 5120 supported by bearing 5116 ofblock 5115 andeccentric portion 5122; and connectingrod 5119 for connectingeccentric portion 5122 andpiston 5117. Compressingelement 5110 forms a reciprocating compressing mechanism. - Electrically-powered
element 5135 is fixed belowblock 5115, and includesstator 5136 connected to an inverter driving circuit (not shown) androtor 5137 which contains permanent magnet and is fixed tomain shaft portion 5120. Electrically-poweredelement 5135 provides an electric motor for driving an inverter, and is driven at a plurality of driving frequencies including those below 1,200 rpm, for example, by the inverter driving circuit (not shown). -
Springs 5139 elasticallysupport compressing element 5110 viastator 5136 such that compressingelement 5110 is elastically held on closedcontainer 5101. -
Viscous pump 5140 soaked withoil 5102 is provided at the lower end ofmain shaft portion 5120 ofshaft 5125. - Next, the structure of
viscous pump 5140 is described in detail. -
Hollow portion 5141 is formed inmain shaft portion 5120.Hollow sleeve 5142 is fixed to the lower region ofhollow portion 5141 to form cylindricalhollow portion 5143.Sleeve 5142 is substantially cylindrical and has a wall thickness in a range from about 0.5 mm to about 11.0 mm.Sleeve 5142 is cap-shaped whose top and bottom are open.Sleeve 5142 is made from iron plate press material which offers comparatively high accuracy in this embodiment, but may be formed from leaf spring steel. -
Insertion member 5144 coaxially inserted into cylindricalhollow portion 5143 has a plurality ofprojections 5145 on its upper outside surface, and receivingportion 5146 at the upper end of sleeve 5142 (corresponding to the thin-wall portion of sleeve 5142) rotatably receives the thrust surfaces ofprojections 5145 in a face contact condition. The difference between the inside diameter of cylindricalhollow portion 5143 and the outermost diameter ofprojections 5145 is determined within a range from 0.1 mm to 0.5 mm. As for the method of installinginsertion member 5144,projections 5145 ofinsertion member 5144 which has been inserted intosleeve 5142 in advance are disposed in such a position as to be received by receivingportion 5146 at the upper end ofsleeve 5142, and subsequentlysleeve 5142 is fixed. By this method, installment of the insertion member can be simultaneously completed. Alternatively, in a structure in whichprojections 5145 are disposed on free joint 5154 which is elastically deformable in the radial direction,insertion member 5144 may be inserted and positioned aftersleeve 5142 is forcedly inserted into cylindricalhollow portion 5141 and fixed thereto. -
Insertion member 5144 is made from a synthetic resin material which has lower thermal conductivity than the metal material which formsshaft 5125 and possesses refrigerant-resistance and oil-resistance properties such as PPS, PBT, and PEEK.Spiral groove 5147 is engraved on the outer surface ofinsertion member 5144, wherebyoil passage 5148 through which oil flows is provided betweenspiral groove 5147 and the inner surface ofsleeve 5142. The difference between the inside diameter ofsleeve 5142 and the outermost diameter ofinsertion member 5144 is almost equivalent to or slightly larger than the difference between the inside diameter of cylindricalhollow portion 5143 and the outermost diameter ofprojections 5145. - Substantially
U-shaped bracket 5149 formed by an elastic body both ends of which are fixed to the lower region ofstator 5136 are provided asmeans 5170 for preventing rotation ofinsertion member 5144. The center ofbracket 5149 engages withvertical groove 5150 provided at the lower end ofinsertion member 5144 to supportinsertion member 5144 while preventing the rotation of insertion member. -
Main shaft portion 5120 hashollow portion 5141 which includes large-diameter portion 5151 and small-diameter portion 5152.Insertion member 5144 is supported inside cylindricalhollow portion 5143 while being prevented from rising by disposingprojections 5145 in such a position as to be sandwiched between receivingportion 5146 andstep 5153 formed by large-diameter portion 5151 and small-diameter portion 5152 with a certain clearance in the vertical direction. - The operation of the compressor having the above structure is now described.
-
Main shaft portion 5120 rotates with the rotation ofshaft 5125. Cylindricalhollow portion 5143 rotates in synchronization with the rotation ofmain shaft portion 5120. The thrust surfaces ofprojections 5145 ofinsertion member 5144 are rotatably received by receivingportion 5146 formed onsleeve 5142.Insertion member 5144 is pulled by the rotation of cylindricalhollow portion 5143, but the rotation ofinsertion member 5144 is prevented bybracket 5149. - As a result, oil rises through
spiral oil passage 5148 while rotating and being pulled by the inner surface of cylindricalhollow portion 5143 due to viscosity. At this stage,oil 5102 rises while rotating not only by the centrifugal force which decreases at low-speed revolution but by a pulling force generated by viscosity. Thus,oil 5102 can be drawn up in a stable manner even at the time of low-speed revolution such as 600 rpm. - According to this embodiment, the position of
insertion member 5144 relative to cylindricalhollow portion 5143 is determined by the surface contact between receivingportion 5146 and the thrust surfaces ofprojections 5145 provided oninsertion member 5144. Accordingly, an almost constant clearance betweeninsertion member 5144 and cylindricalhollow portion 5143 is maintained and thus excessive lateral pressure which may be produced by fixation is scarcely generated. As fluid film pressure also develops withinspiral groove 5147, there is very few possibility of occurrence of sliding abrasion betweeninsertion member 5144 and cylindricalhollow portion 5143. - Accordingly, it is possible to prevent generation of abrasion powder which is circulated with oil toward the sliding area and caught between the sliding components and brings about a locked condition of the compressing element, and thus a highly reliable compressor can be provided.
- In this embodiment,
sleeve 5142 is fixed tohollow portion 5141 provided in the lower region ofshaft 5125, and receivingportion 5146 is formed by the upper end ofsleeve 5142 to effectively utilize the thin-wall region ofsleeve 5142 as receivingportion 5146. Thus, complicated processing is not required to formsleeve 5142 andshaft 5125, and a compressor which is inexpensive and has high productivity can be provided. - In this embodiment,
insertion member 5144 includingprojections 5145,spiral groove 5147 andvertical groove 5150 is integrally formed from a self-lubricating synthetic resin. Thus, a compressor which is inexpensive and has high accuracy and high abrasion resistance can be provided. -
Spiral groove 5147 is formed on the outer surface ofinsertion member 5144 to provideoil passage 5148 in this embodiment, but the spiral groove may be disposed on the inner surface ofsleeve 5142 to formoil passage 5148. In this case, the area of the inner surface of the rotational body in contact with oil is enlarged by adding the surface area of the concaves of the spiral groove. This structure causes large viscous resistance, and thus oil transfer capability is enhanced. -
FIG. 26 is a cross-sectional view illustrating a compressor in a twelfth embodiment of the invention, andFIG. 27 is a cross-sectional view illustrating a main part of the compressor in the twelfth embodiment. - The twelfth embodiment is herein described with reference to
FIGS. 26 and 27 . Similar numbers are given to the structures similar to those of the eleventh embodiment, and detailed description of those is omitted. -
Viscous pump 5240 soaked withoil 5102 is provided at the lower end ofmain shaft portion 5220 ofshaft 5125. - Next, the structure of
viscous pump 5240 is described in detail. -
Hollow portion 5241 is formed inmain shaft portion 5220.Hollow sleeve 5242 is inserted from outside and fixed to the lower region ofhollow portion 5241 to form cylindricalhollow portion 5243.Sleeve 5242 is substantially cylindrical and has large-diameter portion 5251 and small-diameter portion 5252. The wall thickness ofsleeve 5242 is determined in a range from about 0.5 mm to about 1.0 mm.Sleeve 5242 is cap-shaped whose top and bottom are open.Sleeve 5242 is made from iron plate press material which offers comparatively high accuracy, but may be formed from leaf spring steel. -
Insertion member 5244 coaxially inserted into cylindricalhollow portion 5243 has a plurality ofprojections 5245 on its upper outside surface, and receivingportion 5246 formed by a step between large-diameter portion 5251 and small-diameter portion 5252 ofsleeve 5242 rotatably receives the thrust surfaces ofprojections 5245 in a face contact condition. The thrust surface of receivingportion 5246 has a tapered shape, and the thrust surfaces ofprojections 5245 have tapered shapes in correspondence therewith. The difference between the inside diameter of receivingportion 5246 and the outermost diameter ofprojections 5245 is determined within a range from 0.1 mm to 0.5 mm. As for the method of installinginsertion member 5244,projections 5245 ofinsertion member 5244 which has been inserted intosleeve 5242 in advance are disposed in such a position as to be received by receivingportion 5246 provided on the upper end ofsleeve 5242, and subsequentlyinsertion member 5244 is inserted from outside and fixed. By this method, installment ofinsertion member 5244 can be simultaneously completed. -
Insertion member 5244 is made from a synthetic resin material which has lower thermal conductivity than the metal material which formsshaft 5125 and possesses refrigerant-resistance and oil-resistance properties such as PPS, PBT, and PEEK.Spiral groove 5247 is engraved on the outer surface ofinsertion member 5244, wherebyoil passage 5248 through which oil flows is provided betweenspiral groove 5247 and the inner surface ofsleeve 5242. The difference between the inside diameter ofsleeve 5242 and the outermost diameter ofinsertion member 5244 is almost equivalent to or slightly larger than the difference between the inside diameter of receivingportion 5246 and the outermost diameter ofprojections 5245. - A plurality of
impellers 5249 as means 5270 for preventing rotation ofinsertion member 5244 are disposed at the lower sides ofinsertion member 5244 to extend toward the periphery. -
Insertion member 5244 is supported inside cylindricalhollow portion 5243 while being prevented from rising by disposingprojections 5245 in such a position as to be sandwiched between the lower end ofmain shaft portion 5220 and receivingportion 5246 formed by large-diameter portion 5251 and small-diameter portion 5252 with a certain clearance in the vertical direction. - The operation of the compressor having the above structure is now described.
-
Main shaft portion 5220 rotates with the rotation ofshaft 5125. Cylindricalhollow portion 5243 rotates in synchronization with the rotation ofmain shaft portion 5220. The thrust surfaces ofprojections 5245 ofinsertion member 5244 are rotatably received by receivingportion 5246 formed by large-diameter portion 5251 ofsleeve 5242 and small-diameter portion 5252.Insertion member 5244 is pulled by the rotation of cylindricalhollow portion 5243, but rotates at a rotational frequency far lower than that of cylindricalhollow portion 5243 sinceimpellers 5249 receive large viscous resistance in the rotational direction withinoil 5102. Thus, there is a difference in rotational frequency between cylindricalhollow portion 5243 andinsertion member 5244, which difference is near the rotational frequency ofshaft 5125. - As a result, oil rises through
spiral oil passage 5248 while rotating and being pulled by the inner surface of cylindricalhollow portion 5243 due to viscosity. At this stage,oil 5102 rises while rotating not only by the centrifugal force which decreases at low-speed revolution but by a pulling force generated by viscosity. Thus, oil can be drawn up in a stable manner even at the time of low-speed revolution such as 600 rpm. - According to this embodiment, the position of
insertion member 5244 relative to cylindricalhollow portion 5243 is determined by the surface contact between receivingportion 5246 and the thrust surfaces ofprojections 5245 provided oninsertion member 5244. Accordingly, an almost constant clearance betweeninsertion member 5244 and cylindricalhollow portion 5243 is maintained and thus excessive lateral pressure which may be produced by fixation is scarcely generated. As fluid film pressure is generated withinspiral groove 5247 and generation of the fluid film pressure is promoted by providing the tapered thrust surfaces ofprojections 5245 and receivingportion 5246, there is very few possibility of occurrence of sliding abrasion betweeninsertion member 5244 and cylindricalhollow portion 5243. - Accordingly, it is possible to prevent generation of abrasion powder which is circulated with oil toward the sliding area and caught between the sliding components and brings about a locked condition of the compressing element, and thus a highly reliable compressor can be provided.
- In this embodiment,
sleeve 5242 is fixed tohollow portion 5241 provided in the lower region ofshaft 5125, and receivingportion 5246 is formed by large-diameter portion 5251 and small-diameter portion 5252 ofsleeve 5242 to effectively utilize the step ofsleeve 5242 as receivingportion 5246. Thus, complicated processing is not required to formshaft 5125 andsleeve 5242, and a compressor which is inexpensive and has high productivity can be provided. - Since the rotation of
sleeve 5242 is prevented by large viscous resistance applied toimpellers 5249 in the rotational direction withinoil 5102, indirect fixing ofsleeve 5242 tostator 5136 or other components is not needed and the structure is considerably simplified requiring only a small number of components and processes. Thus, a viscous pump having high productivity can be provided. -
FIG. 28 is a cross-sectional view illustrating a compressor in a thirteenth embodiment of the invention, andFIG. 29 is a cross-sectional view illustrating a main part of the compressor in the thirteenth embodiment. - The thirteenth embodiment is herein described with reference to
FIGS. 28 and 29 . Similar numbers are given to the structures similar to those of the eleventh embodiment, and detailed description of those is omitted. -
Viscous pump 5340 soaked withoil 5102 is provided at the lower end ofmain shaft portion 5320 ofshaft 5125. - Next, the structure of
viscous pump 5340 is described in detail. -
Hollow portion 5341 is formed inmain shaft portion 5320.Hollow sleeve 5342 is inserted from outside and fixed to the lower region ofhollow portion 5341 to form cylindricalhollow portion 5343.Sleeve 5342 is substantially cylindrical and has large-diameter portion 5351 and small-diameter portion 5352. The wall thickness ofsleeve 5342 is determined in a range from about 0.5 mm to about 11.0 mm.Sleeve 5342 is cap-shaped whose top and bottom are open, and is made from iron plate press material which offers comparatively high accuracy, but may be formed from leaf spring steel. -
Insertion member 5344 coaxially inserted into cylindricalhollow portion 5343 has a plurality ofprojections 5345 on its upper outside surface, and receivingportion 5346 formed by a step between large-diameter portion 5351 and small-diameter portion 5352 ofsleeve 5342 rotatably receives the thrust surfaces ofprojections 5345 in a face contact condition. The thrust surface of receivingportion 5346 has a tapered shape, and the thrust surfaces ofprojections 5345 have tapered shapes in correspondence therewith. The difference between the inside diameter of receivingportion 5346 and the outermost diameter ofprojections 5345 is determined within a range from 0.1 mm to 0.5 mm. -
Spiral groove 5347 is engraved on the outer surface ofinsertion member 5344, wherebyoil passage 5348 through which oil flows is provided betweenspiral groove 5347 and the inner surface ofsleeve 5342. The difference between the inside diameter ofsleeve 5342 and the outermost diameter ofinsertion member 5344 is almost equivalent to or slightly larger than the difference between the inside diameter of receivingportion 5346 and the outermost diameter ofprojections 5345. A plurality ofarms 5349 radially project from the lower sides ofinsertion member 5344. - As means 5370 for preventing the rotation of
insertion member 5344,permanent magnet 5350 is fixed on eacharm 5349 formed oninsertion member 5344, and eachpermanent magnet 5360 is fixed to the inner surface of the bottom ofclosed container 5101 in such a position as to be substantially opposed to eachpermanent magnet 5350 with a sufficient predetermined clearance within the reach of mutual magnetic force. The opposed surfaces ofpermanent magnet 5350 andpermanent magnet 5360 have different poles from each other. -
Insertion member 5344 is supported inside cylindricalhollow portion 5343 while being prevented from rising by disposingprojections 5345 in such positions as to be sandwiched between the lower end ofmain shaft portion 5320 and receivingportion 5346 formed by large-diameter portion 5351 and small-diameter portion 5352 with a certain clearance in the vertical direction. - The operation of the compressor having the above structure is now described.
-
Main shaft portion 5320 rotates with the rotation ofshaft 5125. Cylindricalhollow portion 5343 rotates in synchronization with the rotation ofmain shaft portion 5320. The thrust surfaces ofprojections 5345 ofinsertion member 5344 are rotatably received by receivingportion 5346 formed by large-diameter portion 5351 ofsleeve 5342 and small-diameter portion 5352.Insertion member 5344 is pulled by the rotation of cylindricalhollow portion 5343, but the rotation ofinsertion member 5344 is prevented sincepermanent magnets 5350 andpermanent magnets 5360 adhere to each other. - As a result, oil rises through
spiral oil passage 5348 while rotating and being pulled by the inner surface of cylindricalhollow portion 5343 due to viscosity. At this stage,oil 5102 rises while rotating not only by the centrifugal force which decreases at low-speed revolution but by a pulling force generated by viscosity. Thus, oil can be drawn up in a stable manner even at the time of low-speed revolution such as 600 rpm. - According to this embodiment, the position of
insertion member 5344 relative to cylindricalhollow portion 5343 is determined by the surface contact between receivingportion 5346 and the thrust surfaces ofprojections 5345 provided oninsertion member 5344. Accordingly, an almost constant clearance betweeninsertion member 5344 and cylindricalhollow portion 5343 is maintained and thus excessive lateral pressure which may be produced by fixation is scarcely generated. As fluid film pressure is generated withinspiral groove 5347 and generation of the fluid film pressure is promoted by providing the tapered thrust surfaces ofprojections 5345 and receivingportion 5346, there is very few possibility of occurrence of sliding abrasion betweeninsertion member 5344 and cylindricalhollow portion 5343. - Accordingly, it is possible to prevent generation of abrasion powder which is circulated with oil toward the sliding area and caught between the sliding components and brings about a locked condition of the compressing element, and thus a highly reliable compressor can be provided.
- Additionally, the rotation of
insertion member 5344 is prevented bypermanent magnet 5350 fixed on eacharm 5349 formed oninsertion member 5344 andpermanent magnet 5360 each fixed to the inner surface of the bottom ofclosed container 5101 in such a position as to be substantially opposed to eachpermanent magnet 5360 with a predetermined clearance. As a result, indirect fixing ofinsertion member 5344 tostator 5136 or other components is not needed and the structure is considerably simplified requiring only a small number of components and processes. Accordingly, a viscous pump having high productivity can be provided. - An example which utilizes adhering force of the permanent magnets is shown in this embodiment, but similar operation and advantage can be attained by utilizing repulsion force generated by disposing the same poles of the permanent magnets in such positions as to be opposed to each other in the rotational direction of
shaft 5125 to prevent the rotation ofinsertion member 5344. - In this embodiment, iron dust such as abrasion powder floating in
oil 5102 is collected by the permanent magnets which are disposed inoil 5102. Accordingly, the dust is prevented in advance from being caught between the components in the viscous pump or in the sliding areas during oil circulation, and thus reliability can be enhanced. - According to the compressor of the invention, the position of the insertion member relative to the sleeve is restricted and abrasion and fixation between the insertion member and the sleeve are scarcely caused. Thus, a highly reliable compressor can be provided.
- In the compressor of the invention, the position of the insertion member relative to the sleeve is determined by the surface contact between the thrust surfaces of the projections and the receiving portion. Accordingly, abrasion and fixation between the insertion member and the cylindrical hollow portion are scarcely caused and thus a highly reliable compressor can be provided.
- In the compressor of the invention, complicated processing is not required for forming the sleeve. Thus, a compressor which is inexpensive and has high productivity and reliability can be provided.
- In the compressor of the invention, the step formed on the sleeve is utilized as the receiving portion. Accordingly, complicated processing is not required for forming the shaft and thus a compressor which is inexpensive and has high productivity and reliability can be provided.
- In the compressor of the invention, fluid film pressure is easily generated due to the oil having flowed into the clearance between the projections and the receiving portion. Accordingly, the contact between the projections and the receiving portion is prevented and thus a compressor having high durability and reliability can be provided.
- In the compressor of the invention, the rotation of the insertion member is prevented by a simple structure and the viscous pump is constructed in a reliable manner. Thus, a highly reliable compressor can be provided.
- In the compressor of the invention, a process for fixing the insertion member is not required. Accordingly, a compressor which is easily assembled and has high productivity and high reliability can be provided.
- In the compressor of the invention, the rotation of the insertion member is securely restrained and iron dust such as abrasion powder is collected by the magnets to prevent the dust from being caught between the components in the viscous pump or in the sliding areas in advance. Thus, a highly reliable compressor can be provided.
- In the compressor of the invention, the insertion member which is inexpensive and has high accuracy and high abrasion resistance is employed. Thus, a highly reliable compressor can be provided.
- In the compressor of the invention, vibration transmitted from the compressing element including the viscous pump and the electrically-powered element is reduced. Accordingly, generation of abnormal sound caused by vibration is eliminated and thus a highly reliable compressor can be provided.
- In the compressor of the invention, oil supply is stabilized, and input to the compressor is decreased since the electrically-powered element is driven at driving frequencies including those lower than the power source frequency. Accordingly, power consumption is reduced and thus a highly reliable compressor can be provided.
- In the above-described conventional structure, both ends of
bracket 7115 are fixed tostator 7106. Additionally, stopper 7623 for preventing rotation ofinsertion member 7120 is provided at a position extremely close to the rotational shaft center. As a result, moment generated through the rotation applies large load to stopper 7623, thereby curvingbracket 7115 into a twisted condition starting from the position of stopper 7623. If the twisted condition is continued, fatigue of material develops especially at the position of stopper 7623, and thin film projections (extrusion) and depression of cracks (intrusion) finally occur. Particularly, the depression develops into visual minute cracks, which gradually spread to finally cause corruption ofbracket 7115. In this case, the rotation ofinsertion member 7120 insidesleeve 7112 may not be prevented. - Moreover, for dispersing the load applied on stopper 7623 or increasing the fatigue resistance strength of stopper 7623,
bracket 7115 is required to have a complicated shape. In this case, the cost of the compressor is inevitably raised. - In order to solve these problems, an object of the present invention is to provide a compressor which is inexpensive and highly reliable, and is capable of maintaining the structure of
viscous pump 7113 in a stable condition for a long period of time without causing material fatigue to the components in relation to the restriction ofinsertion member 7120. - Fourteenth and fifteenth embodiments of the invention are hereinafter described with reference to the drawings, and the invention is not limited to those embodiments.
-
FIG. 30 is a cross-sectional view illustrating a compressor in a fourteenth embodiment of the invention,FIG. 31 is a cross-sectional view illustrating a main part of the compressor in the fourteenth embodiment, andFIG. 32 is a cross-sectional view illustrating a main part of a viscous pump in the fourteenth embodiment. - In
FIGS. 30, 31 and 32,oil 6102 is stored inclosed container 6101 which is filled withrefrigerant gas 6103. - Compressing
element 6110 includes: block 6115 which formscylinder 6113;piston 6117 reciprocatively inserted intocylinder 6113;shaft 6125 havingmain shaft portion 6120 supported by bearing 6116 ofblock 6115 andeccentric portion 6122; and connectingrod 6119 for connectingeccentric portion 6122 andpiston 6117. Compressingelement 6110 forms a reciprocating compressing mechanism. - Electrically-powered
element 6135 is fixed belowblock 6115, and includesstator 6136 connected to an inverter driving circuit (not shown) androtor 6137 which contains permanent magnet and is fixed tomain shaft portion 6120. Electrically-poweredelement 6135 provides an electric motor for driving an inverter, and is driven at a plurality of driving frequencies including those below 1,200 rpm, for example, by the inverter driving circuit (not shown). - Springs 139 elastically
support compressing element 6110 viastator 6136 such that compressingelement 6110 is elastically held on closedcontainer 6101. -
Viscous pump 6140 soaked withoil 6102 is provided at the lower end ofmain shaft portion 6120 ofshaft 6125. - Next, the structure of
viscous pump 6140 is described in detail. - Cylindrical
hollow portion 6141 is formed inmain shaft portion 6120. Hollow sleeve 142 is fixed to the lower region of cylindricalhollow portion 6141. Sleeve 142 is substantially cylindrical and cap-shaped, whose top and bottom are open. Sleeve 142 is made from iron plate press material which offers comparatively high accuracy in this embodiment, but may be formed from leaf spring steel. -
Insertion member 6143 coaxially inserted into cylindricalhollow portion 6141 and sleeve 142 is made from a plastic material which has lower thermal conductivity than the metal material which formsshaft 6125 and possesses refrigerant-resistance and oil-resistance properties such as PPS, PBT, and PEEK.Spiral groove 6144 is engraved on the outer surface ofinsertion member 6143, wherebyoil passage 6145 through which oil flows is provided betweenspiral groove 6144 and the inner surface of sleeve 142. The difference between the outermost diameter ofinsertion member 6143 and the inner surface of sleeve 142, i.e., the matching clearance is established in a range from 100 μm to 500 μm.Insertion member 6143 hasbolt hole 6146 at its upper end, and a plurality of first contactingmembers 6147 at its lower sides off the rotational shaft center ofshaft 6125. - Each second contacting
member 6148 is fixed to the inner surface of the bottom ofclosed container 6101 in such a position as to be opposed to each first contactingmember 6147 in the rotational direction with a sufficient predetermined clearance from rotating sleeve 142. Both first contactingmembers 6147 and second contactingmembers 6148 are completely soaked withoil 6102 stored in the bottom area ofclosed container 6101. First contactingmembers 6147 are made from plastic and formed integrally withinsertion member 6143, but may be formed by fixing metal wires or fragments, for example, to the lower region ofinsertion member 6143. Second contactingmembers 6148 are substantially L-shaped and made from elastic material such as metal wires and fragments. -
Bolt 6150 is employed as supportingmember 6152 for slidingly connectinginsertion member 6143 with sleeve 142.Bolt 6150 inserted throughwasher 6151 penetratesbolt hole 6146, and reaches the upper surface of cylindricalhollow portion 6141 to be attached thereto, thereby rotatably connectinginsertion member 6143 tomain shaft portion 6120 ofshaft 6125 and closing the lower end ofbolt hole 6146.Washer 6151 is made from a plastic material having high abrasion-resistance property such as self-lubrication characteristic (PPS and PEEK etc.). Alternatively,bolt 6150 may be formed from a similar self-lubrication material to eliminatewasher 6151. - The operation of the compressor having the above structure is herein described.
-
Main shaft portion 6120 rotates with the rotation ofshaft 6125. Sleeve 142 fixed tomain shaft portion 6120 rotates in synchronization with the rotation ofmain shaft portion 6120.Insertion member 6143 is pulled by the rotation of sleeve 142, but the rotation ofinsertion member 6143 is prevented by the elastic contact between first contactingmembers 6147 provided oninsertion member 6143 and second contactingmembers 6148 provided onclosed container 6101. As a result, oil rises throughspiral oil passage 6145 while rotating and being pulled by the inner surface of sleeve 142 due to viscosity. At this stage,oil 6102 rises while rotating not only by the centrifugal force which decreases at low-speed revolution but by a pulling force generated by viscosity. Thus, oil can be drawn up in a stable manner even at the time of low-speed revolution such as 600 rpm. - In the embodiment as described above, first contacting
members 6147 and second contactingmembers 6148 are disposed away from the rotational shaft center ofshaft 6125. This arrangement decreases load applied by the moment which is generated through the rotation while first contactingmembers 6147 and second contactingmembers 6148 are contacting each other. Also, as both the contacting members elastically contact with each other, impact received is absorbed and material fatigue of the components in relation to the restriction ofinsertion member 6143 is scarcely caused. Accordingly, the structure ofviscous pump 6140 is maintained in a stable condition for a long period of time, and thus a highly reliable compressor can be provided. Moreover, first contactingmembers 6147 and second contactingmembers 6148 are not required to have a complicated shape for reducing the load applied by the moment generated through the rotation at the time of the contact. Thus, a considerably simple and inexpensive compressor can be provided. - Since first contacting
members 6147 and second contactingmembers 6148 are soaked withoil 6102, impact caused at the time of the contact between the contacting members is reduced by the viscosity ofoil 6102. Also, even if rubbing is caused between the contacting members due to vibration from compressingelement 6110, abrasion does not develop owing to the lubricating function ofoil 6102. Thus, reliability can be further increased. - Second contacting
members 6148 are formed by metal wires or fragments in this embodiment, but may be made from nitrile rubber (NBR) which is comparatively inexpensive and has oil-resistance and refrigerant-resistance properties, if mineral oil or diester synthetic oil is used asoil 6102. The nitrile rubber may be L-shaped as in the embodiment, or may be disposed on the contact portions of the metal wires or fragments. Additionally, it is possible to reduce sound and vibration transmitted to the outside ofclosed container 6101 at the time of the contact between the contacting members by utilizing the shock absorbing characteristic of the nitrile rubber. - According to this embodiment,
insertion member 6143 is rotatably connected tomain shaft portion 6120 ofshaft 6125 by means ofbolt 6150 which is inserted throughwasher 6151. Thus, the position ofinsertion member 6143 relative to sleeve 142 fixed at the lower end ofmain shaft portion 6120 is restricted by this connecting portion, and an almost constant clearance is maintained betweeninsertion member 6143 and sleeve 142. This clearance is maintained by the fact that lateral pressure due to fixation is scarcely caused and also by the oil pressure generated betweeninsertion member 6143 and sleeve 142, and thus there is very few possibility of occurrence of sliding abrasion betweeninsertion member 6143 and sleeve 142. -
Spiral groove 6144 is provided on the outer surface ofinsertion member 6143 to formspiral oil passage 6145 in this embodiment, but may be disposed on the inner surface of sleeve 142 to formoil passage 6145. In this case, the area of the inner surface of the rotational body in contact withoil 6102 is enlarged by adding the surface area of the concaves of the spiral groove. This structure causes large viscous resistance, thereby enhancing oil transfer capability. -
FIG. 33 is a cross-sectional view illustrating a main part of a compressor in a fifteenth embodiment of the invention. - The fifteenth embodiment is herein described with reference to
FIG. 33 . Similar numbers are given to the structures similar to those of the fourteenth embodiment, and detailed description of those is omitted. -
Insertion member 6143 coaxially inserted into sleeve 142 has a plurality of first contactingmembers 6247 at its lower sides off the rotational shaft center ofshaft 6125. - Each second contacting
member 6248 is fixed to the inner surface of the bottom ofclosed container 6101 in such a position as to be opposed to each first contactingmember 6247 in the rotational direction with a sufficient predetermined clearance from rotating sleeve 142. Both first contactingmembers 6247 and second contactingmembers 6248 are completely soaked withoil 6102 stored in the bottom area ofclosed container 6101. First contactingmembers 6247 are made from plastic and formed integrally withinsertion member 6143, but may be formed by fixing metal wires or fragments, for example, to the lower region ofinsertion member 6143. Second contactingmembers 6148 are substantially L-shaped and made from elastic material such as metal wires and fragments. Each second contactingmember 6248 has metalflat plate 6249 disposed in such a position as to contact with the face offirst contact member 6247. - According to this embodiment, since the faces of first contacting
members 6247 and second contactingmembers 6248 contact each other and also receive viscous resistance ofoil 6102, the face pressure is securely and extremely decreased by a simple structure. Accordingly, chipping at the contact portion is prevented and thus reliability can be further increased. - In this embodiment, each second contacting
member 6148 has metalflat plate 6249 in this embodiment. However,flat plate 6249 may be made from nitrile rubber (NBR) which is comparatively inexpensive and has oil-resistance and refrigerant-resistance properties, or has a coil spring or other means on the contact portion offlat plate 6249 to greatly enhance its shock absorbing characteristic at the time of the contact. - In the invention as described above, both the contacting members are disposed away from the rotational shaft center. This arrangement decreases load applied by the moment which is generated through the rotation at the time of the contact. Also, as both the contacting members elastically contact with each other, impact received is absorbed and material fatigue of the components in relation to the restriction of the insertion member is scarcely caused. Accordingly, as the contacting members are not required to have a complicated structure for reducing the load, the structure of the viscous pump is maintained in a stable condition for a long period of time, and thus a compressor which is inexpensive and highly reliable can be provided.
- In the invention, impact caused at the time of the contact between the contacting members is reduced by the viscosity of oil. Also, even if rubbing is caused between the contacting members due to vibration from the compressing element, abrasion does not develop. Thus, a compressor which is inexpensive and highly reliable can be provided.
- In the invention, at least either the first contacting members or the second contacting members are made from elastic bodies. Accordingly, the number of the components included is decreased and thus a compressor which is inexpensive and highly reliable can be provided.
- In the invention, the elastic body is interposed between the first contacting member and the second contacting member. As a result, comparatively large impact caused by the contact during assembly or transportation of the compressor is reduced, and the positions of the second contacting members are not required to be accurately determined. Thus, a compressor which is inexpensive and highly reliable can be provided.
- According to the invention, since the faces of the first contacting members and the second contacting members contact each other, the face pressure is securely more decreased by a simple structure. Accordingly, chipping at the contact portion is prevented and thus a compressor which is inexpensive and highly reliable can be provided.
- A compressor provided according to the present invention is a highly reliable compressor capable of transferring oil in a stable manner even at the time of low-speed driving. Thus, the compressor is applicable to household refrigerators, and also to refrigerant cycles in dehumidifiers, showcases, vending machines and so forth.
Claims (31)
Applications Claiming Priority (15)
Application Number | Priority Date | Filing Date | Title |
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JP2003-0700015 | 2003-03-14 | ||
JP2003070015 | 2003-03-14 | ||
JP2003073867 | 2003-03-18 | ||
JP2003-073867 | 2003-03-18 | ||
JP2003-361721 | 2003-10-22 | ||
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JP2004-019612 | 2004-01-28 | ||
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JP2004019612 | 2004-01-28 | ||
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JP2004019611 | 2004-01-28 | ||
JP2004-019614 | 2004-01-28 | ||
JP2004-019613 | 2004-01-28 | ||
JP2004019613 | 2004-01-28 | ||
PCT/JP2004/003394 WO2004081383A1 (en) | 2003-03-14 | 2004-03-15 | Compressor |
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US20060013706A1 true US20060013706A1 (en) | 2006-01-19 |
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US10/531,452 Abandoned US20060013706A1 (en) | 2003-03-14 | 2004-03-15 | Compressor |
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EP (1) | EP1605163A1 (en) |
JP (1) | JP4380630B2 (en) |
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US10704541B2 (en) * | 2012-02-20 | 2020-07-07 | Panasonic Intellectual Property Management Co., Ltd. | Slide member, refrigerant compressor incorporating slide member, refrigerator and air conditioner |
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US20170114782A1 (en) * | 2015-10-21 | 2017-04-27 | Whirlpool S.A. | Constructive Arrangement Introduced in a Reciprocating Compressor Including a Lubricant Oil Pump |
US20170204853A1 (en) * | 2016-01-19 | 2017-07-20 | Whirlpool S.A. | Oil Pump Assembly Arrangement in Cooling Compressor |
US20170204753A1 (en) * | 2016-01-19 | 2017-07-20 | Whirlpool S.A. | Variable Speed Cooling Compressor Including Lubricating Oil Pumping System |
US10844759B2 (en) * | 2016-01-19 | 2020-11-24 | Embraco—Industria De Compressores E Solucoes Em Refrigeracao Ltda. | Variable speed cooling compressor including lubricating oil pumping system |
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US11536272B2 (en) * | 2017-09-28 | 2022-12-27 | Lg Electronics Inc. | Lubricating oil supply apparatus and compressor using lubricating oil supply apparatus |
CN107781139A (en) * | 2017-10-16 | 2018-03-09 | 杭州钱江制冷压缩机集团有限公司 | A kind of structure that oils of compressor |
CN111480004A (en) * | 2017-12-11 | 2020-07-31 | 三星电子株式会社 | Compressor with a compressor housing having a plurality of compressor blades |
US11225957B2 (en) | 2018-09-28 | 2022-01-18 | Secop Gmbh | Lubricant receptacle for a refrigerant compressor |
US20210348808A1 (en) * | 2018-11-08 | 2021-11-11 | Panasonic Appliances Refrigeration Devices Singapore | Refrigerant compressor and equipment using the same |
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Also Published As
Publication number | Publication date |
---|---|
JP4380630B2 (en) | 2009-12-09 |
KR100679142B1 (en) | 2007-02-07 |
KR100679130B1 (en) | 2007-02-07 |
KR20050083696A (en) | 2005-08-26 |
KR20060110010A (en) | 2006-10-23 |
EP1605163A1 (en) | 2005-12-14 |
WO2004081383A1 (en) | 2004-09-23 |
JPWO2004081383A1 (en) | 2006-06-15 |
KR20060108780A (en) | 2006-10-18 |
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