EP1629198B1 - Hermetic compressor - Google Patents
Hermetic compressor Download PDFInfo
- Publication number
- EP1629198B1 EP1629198B1 EP05741280A EP05741280A EP1629198B1 EP 1629198 B1 EP1629198 B1 EP 1629198B1 EP 05741280 A EP05741280 A EP 05741280A EP 05741280 A EP05741280 A EP 05741280A EP 1629198 B1 EP1629198 B1 EP 1629198B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- cylinder
- outer circumferential
- hermetic compressor
- circumferential surface
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Not-in-force
Links
- 239000003507 refrigerant Substances 0.000 claims description 29
- 230000006835 compression Effects 0.000 claims description 11
- 238000007906 compression Methods 0.000 claims description 11
- 230000001154 acute effect Effects 0.000 claims description 3
- 238000009751 slip forming Methods 0.000 claims 1
- 239000003921 oil Substances 0.000 description 33
- 239000000314 lubricant Substances 0.000 description 7
- 230000000694 effects Effects 0.000 description 6
- 238000007789 sealing Methods 0.000 description 5
- NNPPMTNAJDCUHE-UHFFFAOYSA-N isobutane Chemical compound CC(C)C NNPPMTNAJDCUHE-UHFFFAOYSA-N 0.000 description 4
- LVGUZGTVOIAKKC-UHFFFAOYSA-N 1,1,1,2-tetrafluoroethane Chemical compound FCC(F)(F)F LVGUZGTVOIAKKC-UHFFFAOYSA-N 0.000 description 3
- 238000001816 cooling Methods 0.000 description 3
- 239000001282 iso-butane Substances 0.000 description 2
- 238000005461 lubrication Methods 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 239000004215 Carbon black (E152) Substances 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 229930195733 hydrocarbon Natural products 0.000 description 1
- 150000002430 hydrocarbons Chemical class 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000001629 suppression Effects 0.000 description 1
- 230000002195 synergetic effect Effects 0.000 description 1
- 238000010792 warming Methods 0.000 description 1
- 238000004804 winding Methods 0.000 description 1
Images
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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
- F04B39/0022—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons piston rods
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0094—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 crankshaft
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
- F04B39/122—Cylinder block
-
- 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
- F25B31/02—Compressor arrangements of motor-compressor units
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2210/00—Working fluid
- F05B2210/10—Kind or type
- F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S417/00—Pumps
- Y10S417/902—Hermetically sealed motor pump unit
Definitions
- the present invention relates to a hermetic compressor used in a refrigerating cycle of a Refrigerator Freezer, etc.
- Fig. 7 is a longitudinal sectional view showing a general hermetic compressor described in US Patent No. 5,228,843 ; and Fig. 8 is a perspective view showing a piston described in International Publication WO 02/02944 .
- hermetic housing 1 houses motor element 4 consisting of stator 2 having winding portion 2a and rotor 3, and compression element 5 driven by motor element 4. Moreover, in the lower part of hermetic housing 1, oil 6 is contained.
- Crankshaft 10 includes main shaft 11 to which rotor 3 is press-fitted and fixed and eccentric shaft 12 formed eccentric to main shaft 11. Inside main shaft 11, oil pump 13 is housed and an opening portion of oil pump 13 is disposed in oil 6.
- Block 20 provided at the upper side of motor element 4 has cylinder 21 having a substantially cylindrical shape and bearing 22 for supporting main shaft 11. Piston 30 is inserted into cylinder 21 of block 20 capable of reciprocating sliding and coupled to eccentric shaft 12 via connecting means 41.
- Piston 30 includes top surface 31, skirt surface 32 and outer circumferential surface 33. Furthermore, outer circumferential surface 33 includes seal surface 34, two guide surfaces 35 and removed portions 36.
- seal surface 34 is a surface in the circumferential direction, which is formed so as to be brought into close contact with the inner circumferential surface of cylinder 21.
- Guide surface 35 is formed so as to be brought into close contact with a part of the inner circumferential surface of cylinder 21 and extends substantially in parallel in the direction of the movement of piston 30.
- Removed portion 36 is a concave portion that is not brought into close contact with the inner circumferential surface of cylinder 21.
- an angle made by lines respectively connecting between central axis 37 of cylindrical piston 30 and two boundary edges 35a and 35b of guide surface 35 in the direction of the radius of piston 30 is generally 40° or less and preferably 30° or less.
- piston 30 reciprocates in the horizontal direction in the drawing. In the vicinity of the bottom dead center, a part of the skirt side of piston 30 is protruded to the outside of cylinder 21. From this state, when piston 30 enters cylinder 21, that it is to say, when piston 30 moves in the right direction of Fig. 7, piston 30 is guided by guide surface 35 and thereby can enter cylinder 21 smoothly.
- piston 30 is likely to be inclined in the vertical direction.
- top surface 31 of piston 30 undergoes compression load of a refrigerant gas and furthermore, crankshaft 10 is pressed in the direction that is not the direction of a piston (downward direction in Fig. 7) via connecting means 41, and thereby the inclination of piston 30 in the vertical direction is likely to be increased.
- a hermetic compressor according to the preamble of either claim 1 or 8 is known from prior art JP 2004 027969 .
- Prior art US 5,860,395 discloses an apparatus and a method of cooling a piston by passing a stream of lubricating oil against the underside of the piston and more specifically by providing an enclosed reservoir space between the engine cylinder wall and the side wall of the piston formed by a depression in the piston and providing a passageway in the piston aimed to direct oil to a desired location on the underface of the piston.
- a hermetic compressor as defined in claim 1 or claim 8 is provided.
- the inventive compressor of claim 1 makes it possible to reduce sliding loss due to the reduction in a sliding area. Furthermore, by the sliding surface provided in the parallel and in the perpendicular direction of the piston pin, the inclination of the piston with respect to the cylinder is suppressed, thus suppressing the leakage of refrigerant. Furthermore, by supplying the sliding portion with oil through the under cut, the sealing property can be improved. With the above-mentioned effect, a hermetic compressor with high efficiency can be provided. Preferred embodiments of the inventive hermetic compressors are defined in the dependent claims.
- Fig. 1 is a longitudinal sectional view showing a hermetic compressor in an exemplary embodiment of the present invention
- Fig. 2 is an enlarged sectional view showing an element around a piston
- Fig. 3 is a front view showing a piston
- Fig. 4 is a sectional view of a part along line 4-4 of FIG. 3
- Fig. 5 is an enlarged sectional view showing an end face of an under cut of a piston
- Fig. 6 is an enlarged sectional view showing a tip of a piston.
- housing 101 houses motor element 104 and compression mechanism 105 driven by motor element 104, and moreover contains oil 106.
- Motor element 104 includes stator 102 and rotor 103, and enables inverter driving by using a control circuit, etc. controlled at plural operational frequencies including operation frequency that is not higher than power supply frequency.
- the hermetic compressor of this exemplary embodiment uses hydrocarbon-based refrigerant Isobutane (or R600a).
- Refrigerant R600a is a natural refrigerant with low global warming potential.
- Crankshaft 110 includes main shaft 111 and eccentric shaft 112 and is disposed in substantially the vertical direction.
- rotor 103 is press-fitted and fixed to main shaft 111 and eccentric shaft 112 is disposed eccentric to main shaft 111.
- Oil supplying structure 120 includes centrifugal pump 122, vertical hole 123, and lateral hole 124.
- centrifugal pump 122 formed inside of crankshaft 110 is opened in oil 106 with another end connected to viscosity pump 121.
- One end of vertical hole 123 is connected to one end of viscosity pump 121 with another end opened in space inside housing 101.
- Block 130 includes substantially cylindrical cylinder 131, main bearing 132 for supporting main shaft 111 and collision-portion 134 provided on the upper side of cylinder 131.
- Cylinder 131 includes notch 135 provided on the upper side of the edge at the side of crankshaft 110.
- Piston 140 is inserted into cylinder 131 capable of reciprocating sliding.
- Piston 140 has piston pin hole 141 formed in parallel to the center axis of eccentric shaft 112.
- piston pin hole 141 formed in parallel to the center axis of eccentric shaft 112.
- piston pin 142 is fitted into piston pin hole 141.
- Piston pin 142 is fixed to piston 140 by hollow cylindrical lock pin 143.
- Piston pin 142 is connected to eccentric shaft 112 via connecting rod 146.
- Hollow part 144 of piston pin 142 communicates with space inside housing 101 via vent hole 145.
- Fig. 4 is a sectional view of a part of piston 140 taken along line 4-4 of FIG. 3, showing a state of cylindrical central axis 170 of the piston seen from the left direction.
- under cut 153 is formed excluding a region with a predetermined width in parallel direction 147 with respect to the axis of piston pin 142 and a region with a predetermined width in the perpendicular direction 148 with respect to the axis of piston pin 142.
- Total area of under cut 153 is not less than one half of an area of outer circumferential surface 150 of the piston.
- angle ⁇ made by edge 180 of under cut 153 and outer circumferential surface 150 of the piston is set to be an acute angle.
- the right end portion of piston 140 is provided with circumferentially formed land 190, on which under cut 153 is not formed, in a predetermined width from top surface 151.
- outer circumferential surface 150 that does not belong to any of circumferentially formed land 190 and under cut 153 is referred to as axially formed land 192.
- axially formed land 192 is provided in parallel to cylindrical central axis 170 and extends from circumferentially formed land 190 and reaches skirt surface 152.
- axially formed lands 192 are formed in a predetermined width on an outer circumferential surfaces at 0°, 90°, 180° and 270° with respect to the cylinder axis as a center.
- the width of axially formed land 192 is set so that angle ⁇ made by two lines linking between cylindrical central axis 170 of piston 140 and two boundary portions of axially formed land 192 in the direction of radius of the piston is set to 40° or less and preferably 30° or less.
- upper sliding surface 154 and lower sliding surface 155 are provided in the vertical direction and side sliding surface 160 is provided in the direction of the side surface. These correspond to one or both of circumferentially formed land 190 and axially formed land 192.
- annular grooves 191 are provided in the outer circumferential direction of the piston. Furthermore, on outer circumferential surface 150 of the piston, at both end portions of top surface 151 side and skirt surface 152 side, minute tapers 201 and 202 are provided.
- centrifugal pump 122 By the rotation of crankshaft 110, centrifugal pump 122 is rotated so as to generate centrifugal force. By the centrifugal force, oil 106 moves upwardly in centrifugal pump 122 to reach viscosity pump 121. Oil 106 which reached viscosity pump 121 further moves upwardly in viscosity pump 121 and are scattered in housing 101 via vertical hole 123 and lateral hole 124.
- oil 106 entering under cut 153 is accumulated in the vicinity of edge 180 of under cut 153.
- oil 106 is carried to an inner part of cylinder 131.
- oil 106 is drawn into between cylinder 131 and outer circumferential surface 150 of the piston so as to efficiently lubricate the vicinity of circumferentially formed land 190.
- angle ⁇ made by edge 180 and outer circumferential surface 150 of the piton is made to be an acute angle, in accordance with the movement of piston 140, oil 106 is efficiently drawn into between cylinder 131 and outer circumferential surface 150 of the piston.
- under cut 153 since four under cuts 153 are provided in the axial direction of piston 140, through under cut 153, oil 106 is supplied to the wide range of outer circumferential surface 150 of the piston.
- crankshaft 110 is pressed toward the opposite direction to the piston and may be inclined.
- piston 140 may be inclined in the vertical direction with respect to cylinder 131, thereby forming a part in which space between cylinder 131 and outer circumferential surface 150 of the piston may be broadened.
- leakage of a refrigerant gas from the part may be accelerated.
- the inclination of piston 140 may deteriorate the lubricant state between piston 140 and cylinder 131 and may increase a sliding noise.
- the sliding loss generated when piston 140 reciprocates in cylinder 131 is in a state of fluid lubricant in which the loss is reduced in proportion to reduction of the sliding area.
- the area of under cut 153 is set to not less than one half of the area of outer circumferential surface 150 of the piston, sliding loss of piston 140 is about one half.
- under cut 153 always communicates with skirt surface 152.
- another configuration mentioned below can provide the same effect because a high pressure gas is released into space inside housing 101. That is to say, without allowing under cut 153 to communicate with skirt surface 152, under cut 153 may be allowed to communicate with space inside housing 101 only in the vicinity of the bottom dead center, or under cut 153 may be allowed to communicate with piston pin hole 141.
- joined oil 106 and the refrigerant gas are expanded and contracted repeatedly, so that the pressure is reduced, whereby a so-called labyrinth seal effect is generated and the sealing property with respect to the leakage of refrigerant from cylinder 131 is improved. From the effect mentioned above, oil supply to the circumferentially formed land is further promoted, the lubricant property can be more improved, and furthermore, high efficiency can be achieved.
- minute tapers 201 and 202 provided at the end portions both at top surface 151 side and skirt surface 152 side of piston 140 is described.
- oil 106 moves around circumferentially formed land 190 of piston 140 so as to improve the lubricant property of piston 140 and to also improve the sealing property.
- piston 140 moves from the top dead center to the bottom dead center, by the wedge effect of minute taper 202 at the skirt surface 152 side, oil 106 enters minute taper 202 so as to form an oil film and lubricant property and sealing property are improved. That is to say, the presence of minute tapers 201 and 202 suppresses the leakage of refrigerant and reduces the sliding loss. Furthermore, high efficiency can be achieved.
- the density of refrigerant R600a used in the hermetic compressor of this exemplary embodiment is smaller than the density of refrigerant R134a (1,1,1,2-tetrafluoroethane), which has been conventionally used in refrigerators. Therefore, when refrigerating ability that is the same as in a hermetic compressor using refrigerant R134a is intended to be obtained by using refrigerant R600a, cylinder capacity is increased and the outer diameter of piston 140 may be increased. Necessarily, the flow passage area for a refrigerant is increased and the amount of refrigerant leaking into housing 101 from cylinder 131 is likely to increase. However, in the hermetic compressor of this exemplary embodiment, since the inclination of piston 140 with respect to cylinder 131 can be suppressed, the efficiency can be improved.
- crankshaft 110 may be provided with secondary axis which is provided on the same axis as main shaft 111 and opposed to main shaft with eccentric shaft 112 therebetween, and at the same time, a secondary bearing for supporting the secondary axis may be provided.
- crankshaft 110 since crankshaft 110 is supported at both ends with eccentric shaft 112 sandwiched therebetween, resulting in effectively suppressing the inclination of piston 140 in the vertical direction with respect to cylinder 131. Consequently, since the behavior of piston 140 becomes stable, sliding loss can be reduced and the increase in noise can be suppressed, it is possible to realize a hermetic compressor with high efficiency and low noise property.
- a hermetic compressor according to the present invention yields high productivity, and can increase efficiency and reliability, it can be widely applied to an application of a hermetic compressor of, for example, an air conditioner, a vending machine, and the like.
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- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
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Description
- The present invention relates to a hermetic compressor used in a refrigerating cycle of a Refrigerator Freezer, etc.
- Recently, reduction in power consumption of this kind of hermetic compressors has been strongly demanded. In a hermetic compressor disclosed in
International Publication WO 02/02944 - Hereinafter, a conventional hermetic compressor is described with reference to drawings.
- Fig. 7 is a longitudinal sectional view showing a general hermetic compressor described in
US Patent No. 5,228,843 ; and Fig. 8 is a perspective view showing a piston described in International PublicationWO 02/02944 - As shown in Fig. 7,
hermetic housing 1 housesmotor element 4 consisting ofstator 2 having windingportion 2a androtor 3, andcompression element 5 driven bymotor element 4. Moreover, in the lower part ofhermetic housing 1,oil 6 is contained. -
Crankshaft 10 includesmain shaft 11 to whichrotor 3 is press-fitted and fixed andeccentric shaft 12 formed eccentric tomain shaft 11. Insidemain shaft 11,oil pump 13 is housed and an opening portion ofoil pump 13 is disposed inoil 6.Block 20 provided at the upper side ofmotor element 4 hascylinder 21 having a substantially cylindrical shape and bearing 22 for supportingmain shaft 11. Piston 30 is inserted intocylinder 21 ofblock 20 capable of reciprocating sliding and coupled toeccentric shaft 12 viaconnecting means 41. - Next, a conventional piston is described with reference to Fig. 8. Piston 30 includes
top surface 31,skirt surface 32 and outercircumferential surface 33. Furthermore, outercircumferential surface 33 includesseal surface 34, twoguide surfaces 35 and removedportions 36. Herein,seal surface 34 is a surface in the circumferential direction, which is formed so as to be brought into close contact with the inner circumferential surface ofcylinder 21.Guide surface 35 is formed so as to be brought into close contact with a part of the inner circumferential surface ofcylinder 21 and extends substantially in parallel in the direction of the movement ofpiston 30. Removedportion 36 is a concave portion that is not brought into close contact with the inner circumferential surface ofcylinder 21. Furthermore, an angle made by lines respectively connecting betweencentral axis 37 ofcylindrical piston 30 and twoboundary edges guide surface 35 in the direction of the radius ofpiston 30 is generally 40° or less and preferably 30° or less. - Next, an operation of a conventional hermetic compressor shown in Fig. 7 is described.
- During operation,
piston 30 reciprocates in the horizontal direction in the drawing. In the vicinity of the bottom dead center, a part of the skirt side ofpiston 30 is protruded to the outside ofcylinder 21. From this state, whenpiston 30 enterscylinder 21, that it is to say, whenpiston 30 moves in the right direction of Fig. 7,piston 30 is guided byguide surface 35 and thereby can entercylinder 21 smoothly. - However, in a conventional hermetic compressor, inclination in the vertical direction of
piston 30 with respect tocylinder 21 is regulated by space between outercircumferential surface 33 andcylinder 21 only inshort section 34A between the edge oftop surface 31 and the edge ofseal surface 34. Therefore,piston 30 is likely to be inclined in the vertical direction. In particular, during the compression stroke from the bottom dead center to the top dead center (movement in the right direction in Fig. 7),top surface 31 ofpiston 30 undergoes compression load of a refrigerant gas and furthermore,crankshaft 10 is pressed in the direction that is not the direction of a piston (downward direction in Fig. 7) via connectingmeans 41, and thereby the inclination ofpiston 30 in the vertical direction is likely to be increased. As a result, there has been a problem that leakage of refrigerant increases, and the refrigerating capacity is deteriorated so as to lower the efficiency. - In particular, when low-density refrigerant Isobutane (R600a) was used, the outer diameter of
piston 30 was increased and leakage of refrigerant was likely to occur, and therefore the efficiency was lowered remarkably. - A hermetic compressor according to the preamble of either
claim 1 or 8 is known from prior artJP 2004 027969 - Further prior art
US 2003/223891 discloses a hermetically enclosed refrigerant compressor, with at least one cylinder and a piston reciprocating in said cylinder, the piston being connected with a driving road via a piston pin and having in its outer jackets surface a circumferential lubrication groove whereas the piston pin was a longitudinal bore, which is connected with a lubrication source. - Prior art
US 5,860,395 discloses an apparatus and a method of cooling a piston by passing a stream of lubricating oil against the underside of the piston and more specifically by providing an enclosed reservoir space between the engine cylinder wall and the side wall of the piston formed by a depression in the piston and providing a passageway in the piston aimed to direct oil to a desired location on the underface of the piston. - In order to solve the above-mentioned problems with a prior art, a hermetic compressor as defined in
claim 1 or claim 8 is provided. The inventive compressor ofclaim 1 makes it possible to reduce sliding loss due to the reduction in a sliding area. Furthermore, by the sliding surface provided in the parallel and in the perpendicular direction of the piston pin, the inclination of the piston with respect to the cylinder is suppressed, thus suppressing the leakage of refrigerant. Furthermore, by supplying the sliding portion with oil through the under cut, the sealing property can be improved. With the above-mentioned effect, a hermetic compressor with high efficiency can be provided. Preferred embodiments of the inventive hermetic compressors are defined in the dependent claims. -
- Fig. 1 is a longitudinal sectional view showing a hermetic compressor in an exemplary embodiment of the present invention.
- Fig. 2 is an enlarged sectional view showing an element around a piston used for a hermetic compressor in an exemplary embodiment.
- Fig. 3 is a front view Showing a piston used for a hermetic compressor in an exemplary embodiment.
- Fig. 4 is a sectional view of a part along line 4-4 of FIG. 3.
- Fig. 5 is an enlarged sectional view showing an end face of an under cut of a piston used for a hermetic compressor in an exemplary embodiment.
- Fig. 6 is an enlarged sectional view showing a tip of a piston used for a hermetic compressor in an exemplary embodiment.
- Fig. 7 is a longitudinal sectional view showing a conventional hermetic compressor.
- Fig. 8 is a perspective view showing a piston used for a conventional hermetic compressor.
- Hereinafter, an exemplary embodiment of the present invention is described with reference to drawings. Note here that the present invention is not limited by the exemplary embodiment.
- Fig. 1 is a longitudinal sectional view showing a hermetic compressor in an exemplary embodiment of the present invention; Fig. 2 is an enlarged sectional view showing an element around a piston; Fig. 3 is a front view showing a piston; Fig. 4 is a sectional view of a part along line 4-4 of FIG. 3; Fig. 5 is an enlarged sectional view showing an end face of an under cut of a piston; and Fig. 6 is an enlarged sectional view showing a tip of a piston.
- As shown in Figs. 1 to 6,
housing 101 housesmotor element 104 andcompression mechanism 105 driven bymotor element 104, and moreover containsoil 106.Motor element 104 includesstator 102 androtor 103, and enables inverter driving by using a control circuit, etc. controlled at plural operational frequencies including operation frequency that is not higher than power supply frequency. - The hermetic compressor of this exemplary embodiment uses hydrocarbon-based refrigerant Isobutane (or R600a). Refrigerant R600a is a natural refrigerant with low global warming potential.
-
Crankshaft 110 includesmain shaft 111 andeccentric shaft 112 and is disposed in substantially the vertical direction. Herein,rotor 103 is press-fitted and fixed tomain shaft 111 andeccentric shaft 112 is disposed eccentric tomain shaft 111. -
Oil supplying structure 120 includescentrifugal pump 122,vertical hole 123, andlateral hole 124. One end ofcentrifugal pump 122 formed inside ofcrankshaft 110 is opened inoil 106 with another end connected toviscosity pump 121. One end ofvertical hole 123 is connected to one end ofviscosity pump 121 with another end opened in space insidehousing 101. -
Block 130 includes substantiallycylindrical cylinder 131, main bearing 132 for supportingmain shaft 111 and collision-portion 134 provided on the upper side ofcylinder 131.Cylinder 131 includes notch 135 provided on the upper side of the edge at the side ofcrankshaft 110. - Piston 140 is inserted into
cylinder 131 capable of reciprocating sliding.Piston 140 haspiston pin hole 141 formed in parallel to the center axis ofeccentric shaft 112. Intopiston pin hole 141, hollowcylindrical piston pin 142 is fitted.Piston pin 142 is fixed topiston 140 by hollowcylindrical lock pin 143.Piston pin 142 is connected toeccentric shaft 112 via connectingrod 146. -
Hollow part 144 ofpiston pin 142 communicates with space insidehousing 101 viavent hole 145. - On outer
circumferential surface 150 ofpiston 140, undercut 153 is formed. Undercut 153 does not reachtop surface 151 ofpiston 140 but reachesskirt surface 152. Fig. 4 is a sectional view of a part ofpiston 140 taken along line 4-4 of FIG. 3, showing a state of cylindricalcentral axis 170 of the piston seen from the left direction. As shown in Fig. 4, undercut 153 is formed excluding a region with a predetermined width inparallel direction 147 with respect to the axis ofpiston pin 142 and a region with a predetermined width in theperpendicular direction 148 with respect to the axis ofpiston pin 142. Total area of undercut 153 is not less than one half of an area of outercircumferential surface 150 of the piston. Furthermore, as shown in Fig. 5 that is an enlarged view showing the vicinity ofedge 180 of undercut 153, angle θ made byedge 180 of undercut 153 and outercircumferential surface 150 of the piston is set to be an acute angle. - Furthermore, as shown in Fig. 3, the right end portion of
piston 140 is provided with circumferentially formedland 190, on which undercut 153 is not formed, in a predetermined width fromtop surface 151. Furthermore, outercircumferential surface 150 that does not belong to any of circumferentially formedland 190 and undercut 153 is referred to as axially formedland 192. In Fig. 3, axially formedland 192 is provided in parallel to cylindricalcentral axis 170 and extends from circumferentially formedland 190 and reachesskirt surface 152. As shown in Fig. 4, axially formedlands 192 are formed in a predetermined width on an outer circumferential surfaces at 0°, 90°, 180° and 270° with respect to the cylinder axis as a center. - Furthermore, as shown in Fig. 4, it is preferable that the width of axially formed
land 192 is set so that angle ω made by two lines linking between cylindricalcentral axis 170 ofpiston 140 and two boundary portions of axially formedland 192 in the direction of radius of the piston is set to 40° or less and preferably 30° or less. - As shown in Fig. 4, in outer
circumferential surface 150 of the piston, upper slidingsurface 154 and lower slidingsurface 155 are provided in the vertical direction andside sliding surface 160 is provided in the direction of the side surface. These correspond to one or both of circumferentially formedland 190 and axially formedland 192. - Furthermore, on circumferentially formed
land 190, twoannular grooves 191 are provided in the outer circumferential direction of the piston. Furthermore, on outercircumferential surface 150 of the piston, at both end portions oftop surface 151 side andskirt surface 152 side, minute tapers 201 and 202 are provided. - In this exemplary embodiment, as shown in Fig. 1, in the vicinity of the bottom dead center, a part of the skirt side of
piston 140 is protruded fromcylinder 131. With such a configuration, even in a shape in which undercut 153 does not reachskirt surface 152, undercut 153 is opened in space inside the housing when at leastpiston 140 is in the bottom dead center. - Next, the operation and action of the hermetic compressor of the exemplary embodiment are described.
- When
rotor 103 ofmotor element 104 rotatescrankshaft 110, the rotation movement ofeccentric shaft 112 is transmitted topiston 140 via connectingrod 146 andpiston pin 142 as a connecting portion, and therebypiston 140 reciprocates incylinder 131. Whenpiston 140 reciprocates, a refrigerant gas is sucked from a cooling system (not shown) intocylinder 131, compressed and then discharged into the cooling system, again. - Next, an operation of
oil supplying structure 120 is described. By the rotation ofcrankshaft 110,centrifugal pump 122 is rotated so as to generate centrifugal force. By the centrifugal force,oil 106 moves upwardly incentrifugal pump 122 to reachviscosity pump 121.Oil 106 which reachedviscosity pump 121 further moves upwardly inviscosity pump 121 and are scattered inhousing 101 viavertical hole 123 andlateral hole 124. -
Oil 106 scattered inhousing 101 collides with collision-portion 134 and moves along notch 135 so as to be attached to outercircumferential surface 150 of the piston. Attachedoil 106 moves around outercircumferential surface 150, undercut 153,annular groove 191 and minute tapers 201 and 202 in accordance with the reciprocating movement ofpiston 140, and works as a lubricant between outercircumferential surface 150 andcylinder 131. - In the hermetic compressor of this exemplary embodiment, as shown in Fig. 1, in the vicinity of the bottom dead center, a part of the skirt side of
piston 140 is protruded fromcylinder 131. Therefore, whenpiston 140 comes to the bottom dead center, at least a part of undercut 153 is protruded fromcylinder 131 and can be brought into direct contact withoil 106 scattered inhousing 101. Thus, enough amount ofoil 106 is always supplied to undercut 153. - As shown in Fig. 5,
oil 106 entering undercut 153 is accumulated in the vicinity ofedge 180 of undercut 153. Whenpiston 140 moves from the bottom dead center to the top dead center,oil 106 is carried to an inner part ofcylinder 131. On the other hand, whenpiston 140 moves from the top dead center to the bottom top dead center, in accordance with the movement ofpiston 140,oil 106 is drawn into betweencylinder 131 and outercircumferential surface 150 of the piston so as to efficiently lubricate the vicinity of circumferentially formedland 190. - Furthermore, since angle θ made by
edge 180 and outercircumferential surface 150 of the piton is made to be an acute angle, in accordance with the movement ofpiston 140,oil 106 is efficiently drawn into betweencylinder 131 and outercircumferential surface 150 of the piston. - In this exemplary embodiment, since four under
cuts 153 are provided in the axial direction ofpiston 140, through undercut 153,oil 106 is supplied to the wide range of outercircumferential surface 150 of the piston. - With the synergistic effect of them, the lubricant property of
piston 140 is improved, and extremely high sealing property can be obtained so as to suppress leakage of refrigerant. Therefore, high efficiency can be realized. - In general, when
piston 140 is in the vicinity of the top dead center, the inside ofcylinder 131 becomes high pressure due to a compressed refrigerant, so that a refrigerant gas is about to leak from betweencylinder 131 and outercircumferential surface 150 of the piston. At this time, by compression load generated insidecylinder 131, viapiston pin 142 and connectingroad 146,crankshaft 110 is pressed toward the opposite direction to the piston and may be inclined. When crankshaft 110 is inclined,piston 140 may be inclined in the vertical direction with respect tocylinder 131, thereby forming a part in which space betweencylinder 131 and outercircumferential surface 150 of the piston may be broadened. As a result, leakage of a refrigerant gas from the part may be accelerated. Furthermore, the inclination ofpiston 140 may deteriorate the lubricant state betweenpiston 140 andcylinder 131 and may increase a sliding noise. - However, in this exemplary embodiment, since upper sliding
surface 154 and lower slidingsurface 155 ofpiston 140 are provided over the full length ofpiston 140 fromtop surface 151 toskirt surface 152 as shown in Figs. 3 and 4, the inclination in the vertical direction ofpiston 140 is regulated, and thus the generation of inclination ofpiston 140 can be effectively suppressed. As a result of suppression of the inclination, leakage of refrigerant gas fromcylinder 131 tohousing 101 is suppressed, the behavior ofpiston 140 becomes stable, and it is possible to reduce sliding loss and to suppress the increase in noise. Consequently, high efficiency and low noise property can be achieved. - Furthermore, the sliding loss generated when
piston 140 reciprocates incylinder 131 is in a state of fluid lubricant in which the loss is reduced in proportion to reduction of the sliding area. In this exemplary embodiment, since the area of undercut 153 is set to not less than one half of the area of outercircumferential surface 150 of the piston, sliding loss ofpiston 140 is about one half. Thus, high efficiency by remarkable input reduction can be realized. - Furthermore, during the compression stroke, a high pressure gas inside
cylinder 131 leaks out to undercut 153. However, since under cut 153 always communicates with space insidehousing 101 atskirt surface 152 side, leaked refrigerant gas is not accumulated in undercut 153. Therefore, jet noise is not generated when the under cut comes out from the cylinder and a high pressure gas is released into low pressure space insidehousing 101 at once in the case of a piston having a structure in which an under cut does not communicates with space insidehousing 101. Furthermore, a high pressure gas accumulated in the under cut does not backflow intocylinder 131 to increase re-expansion loss during the suction stroke. - Note here that, in this exemplary embodiment, under
cut 153 always communicates withskirt surface 152. However, another configuration mentioned below can provide the same effect because a high pressure gas is released into space insidehousing 101. That is to say, without allowing undercut 153 to communicate withskirt surface 152, undercut 153 may be allowed to communicate with space insidehousing 101 only in the vicinity of the bottom dead center, or undercut 153 may be allowed to communicate withpiston pin hole 141. - Furthermore, when circumferentially formed
land 190 is provided withannular groove 191 andoil 106 is allowed to be brought into direct contact withannular groove 191 in the vicinity of the bottom dead center in whichpiston 140 is protruded fromcylinder 131, attachedoil 106 is spread over the entire part ofannular groove 191 by the capillary phenomenon. Thereafter, during the movement ofpiston 140 from the bottom dead center to the top dead center, when a refrigerant gas reachesannular groove 191 and is joined together withoil 106 ingroove 191, great viscosity resistance acts on the refrigerant gas. Furthermore, joinedoil 106 and the refrigerant gas are expanded and contracted repeatedly, so that the pressure is reduced, whereby a so-called labyrinth seal effect is generated and the sealing property with respect to the leakage of refrigerant fromcylinder 131 is improved. From the effect mentioned above, oil supply to the circumferentially formed land is further promoted, the lubricant property can be more improved, and furthermore, high efficiency can be achieved. - Next, the role of minute tapers 201 and 202 provided at the end portions both at
top surface 151 side andskirt surface 152 side ofpiston 140 is described. When the piston moves from the bottom dead center to the top dead center, by the wedge effect ofminute taper 201 attop surface 151 side ofpiston 140,oil 106 moves around circumferentially formedland 190 ofpiston 140 so as to improve the lubricant property ofpiston 140 and to also improve the sealing property. On the other hand, whenpiston 140 moves from the top dead center to the bottom dead center, by the wedge effect ofminute taper 202 at theskirt surface 152 side,oil 106 entersminute taper 202 so as to form an oil film and lubricant property and sealing property are improved. That is to say, the presence of minute tapers 201 and 202 suppresses the leakage of refrigerant and reduces the sliding loss. Furthermore, high efficiency can be achieved. - Furthermore, in the case where the motor element is inverter-driven at plural operation frequencies including operation frequency that is not more than power supply frequency, reciprocating movement speed of
piston 140 is reduced during low speed operation. Furthermore, since an amount ofoil 106 scattered inhousing 101 is reduced, leakage of refrigerant from space between outercircumferential surface 150 of the piston andcylinder 131 is likely to be increased. On the other hand, in the hermetic compressor of this exemplary embodiment, sinceoil 106 can be accumulated in undercut 153 and inclination in the vertical direction ofpiston 140 can be suppressed, high efficiency can be maintained also during the low speed operation. - The density of refrigerant R600a used in the hermetic compressor of this exemplary embodiment is smaller than the density of refrigerant R134a (1,1,1,2-tetrafluoroethane), which has been conventionally used in refrigerators. Therefore, when refrigerating ability that is the same as in a hermetic compressor using refrigerant R134a is intended to be obtained by using refrigerant R600a, cylinder capacity is increased and the outer diameter of
piston 140 may be increased. Necessarily, the flow passage area for a refrigerant is increased and the amount of refrigerant leaking intohousing 101 fromcylinder 131 is likely to increase. However, in the hermetic compressor of this exemplary embodiment, since the inclination ofpiston 140 with respect tocylinder 131 can be suppressed, the efficiency can be improved. - Note here that crankshaft 110 may be provided with secondary axis which is provided on the same axis as
main shaft 111 and opposed to main shaft witheccentric shaft 112 therebetween, and at the same time, a secondary bearing for supporting the secondary axis may be provided. With such a configuration, sincecrankshaft 110 is supported at both ends witheccentric shaft 112 sandwiched therebetween, resulting in effectively suppressing the inclination ofpiston 140 in the vertical direction with respect tocylinder 131. Consequently, since the behavior ofpiston 140 becomes stable, sliding loss can be reduced and the increase in noise can be suppressed, it is possible to realize a hermetic compressor with high efficiency and low noise property. - As mentioned above, since a hermetic compressor according to the present invention yields high productivity, and can increase efficiency and reliability, it can be widely applied to an application of a hermetic compressor of, for example, an air conditioner, a vending machine, and the like.
-
- 101 housing
- 105 compression mechanism
- 106 oil
- 110 crankshaft
- 111 main shaft
- 112 eccentric shafts
- 120 oil supplying structure
- 130 block
- 131 cylinder
- 140 piston
- 142 piston pin
- 146 connecting rod
- 147 parallel direction of piston pin
- 148 perpendicular direction of piston pin
- 150 outer circumferential surface of piston
- 151 top surface
- 152 skirt surface
- 153 under cut
- 170 cylindrical central axis
- 180 edge
- 190 circumferentially formed land
- 191 annular groove
- 192 axial direction land
- 201, 202 minute taper
- θ angle made by edge of under-cut and outer circumferential surface of piston
Claims (10)
- A hermetic compressor comprising a housing (101) which contains oil and houses a compression mechanism (105) for compressing a refrigerant gas, the compression mechanism comprising:a crankshaft (110) disposed in a vertical direction and having a main shaft (111) and an eccentric shaft (112);a block (130) forming a cylinder (131);a piston (140) reciprocating in the cylinder (131) in a direction of a cylinder axis;a piston pin (142) disposed on the piston (140) in a way in which a center axis is in parallel to the eccentric shaft (112);a connecting rod (146) for connecting the eccentric shaft (112) to the piston pin (142); andan oil supplying structure (120) for supplying the oil to an outer circumferential surface of the piston (140),the piston (140) has an under cut (153) on the outer circumferential surface formed outside a region with a predetermined width in a parallel and perpendicular direction with respect to the axis of the piston pin ; andthe under cut (153) is separated from a top surface of the piston (140) along the outer circumferential surface and communicates with space inside the housing (101) at least when the piston (140) is in a bottom dead center;characterized in that,the under cut (153) is formed continuously to a skirt surface (152).
- The hermetic compressor according to claim 1, wherein an area of the under cut is not less than one half of the outer circumferential surface of the piston.
- The hermetic compressor according to claim 1, wherein an angle made by an edge of the under cut and the outer circumferential surface of the piston is an acute angle.
- The hermetic compressor according to claim 1, wherein the piston has a circumferentially formed land in a predetermined width from a top surface at a cylinder side of the piston, and the circumferentially formed land is provided with an annular groove (191).
- The hermetic compressor according to claim 1, wherein the piston has a taper in at least one of a boundary between a top surface at a cylinder side of the piston and the outer circumferential surface and a boundary between a skirt surface and the outer circumferential surface.
- The hermetic compressor according to claim 1, further comprising a motor element (104) for rotating the crankshaft, the motor element being inverter-driven at plural operation frequencies including an operation frequency that is at least power supply frequency or less.
- The hermetic compressor according to claim 1, wherein the refrigerant gas is R600a.
- A hermetic compressor comprising housing (101) which contains oil and houses a compression mechanism (105) for compressing a refrigerant gas, the compression mechanism comprising:a crankshaft (110) disposed in a vertical direction and having a main shaft (111) and an eccentric shaft (112);a cylinder (131):a cylindrical piston (140) reciprocating in the cylinder (131) in a direction of a cylinder axis; anda connecting portion (146) for connecting the piston (140) to the eccentric shaft (112);the piston (140) comprising:a skirt surface (152) at a side of the connecting portion (146);a top surface (151) at a side of the cylinder (131); andan outer circumferential surface (150) parallel to the cylinder (131) wherein the outer circumferential surface (150) includes a land (190,192) that is on the same surface as the outer circumferential surface (150) of the piston (140) and an under cut (153) that is recess with respect to the outer circumferential surface;characterized in thatthe land (190, 192) comprising:a circumferentially formed land (190) formed in a predetermined width from the top surface (151) toward the skirt surface (152) around the piston (140); andan axially formed land (192) formed in a predetermined width on an outer circumferential surfaces at 0°, 90° 180° and 270° with respect to the cylinder axis as a center, and continuously formed from the circumferentially formed land (190) to the skirt surface (152).
- The hermetic compressor according to claim 8, wherein the under cut is formed continuously to the skirt surface.
- The hermetic compressor according to claim 8, wherein the under cut is formed discontinuously to the skirt surface, and when the piston is at least in a bottom dead center, the under cut communicates with space inside the housing.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004159165A JP4337635B2 (en) | 2004-05-28 | 2004-05-28 | Hermetic compressor |
PCT/JP2005/009006 WO2005116450A1 (en) | 2004-05-28 | 2005-05-11 | Hermetic compressor |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1629198A1 EP1629198A1 (en) | 2006-03-01 |
EP1629198B1 true EP1629198B1 (en) | 2007-08-29 |
Family
ID=34968133
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP05741280A Not-in-force EP1629198B1 (en) | 2004-05-28 | 2005-05-11 | Hermetic compressor |
Country Status (7)
Country | Link |
---|---|
US (1) | US20060257274A1 (en) |
EP (1) | EP1629198B1 (en) |
JP (1) | JP4337635B2 (en) |
KR (1) | KR100701527B1 (en) |
CN (1) | CN100430598C (en) |
DE (1) | DE602005002205T2 (en) |
WO (1) | WO2005116450A1 (en) |
Families Citing this family (19)
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JP4760003B2 (en) | 2004-12-14 | 2011-08-31 | パナソニック株式会社 | Hermetic compressor |
WO2007035695A2 (en) * | 2005-09-19 | 2007-03-29 | Ingersoll-Rand Company | Air blower for a motor-driven compressor |
BRPI0603568A (en) * | 2006-08-16 | 2008-04-08 | Whirlpool Sa | reciprocating compressor piston and rod mounting arrangement |
JP4915205B2 (en) * | 2006-10-19 | 2012-04-11 | パナソニック株式会社 | Compressor |
EP1999370A1 (en) * | 2007-02-23 | 2008-12-10 | Panasonic Corporation | Hermetic compressor |
AT10065U1 (en) * | 2007-08-28 | 2008-08-15 | Acc Austria Gmbh | REFRIGERANT COMPRESSOR |
US8702405B2 (en) * | 2007-11-17 | 2014-04-22 | Brian Leonard Verrilli | Twisting translational displacement pump cartridge |
CN101952594B (en) * | 2008-01-10 | 2013-08-14 | Lg电子株式会社 | Reciprocating compressor |
WO2009139135A1 (en) | 2008-05-12 | 2009-11-19 | Panasonic Corporation | Hermetic compressor |
CN102597518B (en) * | 2009-10-27 | 2016-03-30 | 松下知识产权经营株式会社 | Hermetic type compressor |
JP5810273B2 (en) * | 2010-10-21 | 2015-11-11 | パナソニックIpマネジメント株式会社 | Hermetic compressor and refrigeration system |
JP2012197769A (en) * | 2011-03-23 | 2012-10-18 | Panasonic Corp | Hermetic compressor |
BRPI1101929A2 (en) * | 2011-04-26 | 2015-07-14 | Whirlpool Sa | Refrigeration compressor connecting rod |
JP5492917B2 (en) * | 2012-02-01 | 2014-05-14 | 株式会社豊田自動織機 | Variable capacity swash plate compressor |
CN104884803A (en) * | 2012-12-27 | 2015-09-02 | 松下知识产权经营株式会社 | Hermetic compressor and refrigeration device with same |
US10352312B2 (en) | 2013-01-22 | 2019-07-16 | Panasonic Appliances Refrigeration Devices Singapore | Hermetic compressor and refrigerator |
US10208743B2 (en) * | 2016-10-07 | 2019-02-19 | Westinghouse Air Brake Technologies Corporation | Piston cylinder arrangement for an oil free compressor having cooling passageways and method of cooling wrist pin bearing surface |
KR102351707B1 (en) * | 2017-06-20 | 2022-01-17 | 엘지전자 주식회사 | Piston for reciprocating compressor and method for manufacturing the same |
JP2020033873A (en) * | 2018-08-27 | 2020-03-05 | 日立グローバルライフソリューションズ株式会社 | Closed compressor and refrigerator having the same |
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- 2004-05-28 JP JP2004159165A patent/JP4337635B2/en not_active Expired - Fee Related
-
2005
- 2005-05-11 US US10/553,847 patent/US20060257274A1/en not_active Abandoned
- 2005-05-11 DE DE602005002205T patent/DE602005002205T2/en not_active Expired - Fee Related
- 2005-05-11 KR KR1020057020671A patent/KR100701527B1/en not_active IP Right Cessation
- 2005-05-11 CN CNB2005800001747A patent/CN100430598C/en not_active Expired - Fee Related
- 2005-05-11 EP EP05741280A patent/EP1629198B1/en not_active Not-in-force
- 2005-05-11 WO PCT/JP2005/009006 patent/WO2005116450A1/en active IP Right Grant
Non-Patent Citations (1)
Title |
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None * |
Also Published As
Publication number | Publication date |
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JP2005337160A (en) | 2005-12-08 |
DE602005002205T2 (en) | 2007-12-20 |
DE602005002205D1 (en) | 2007-10-11 |
CN1771394A (en) | 2006-05-10 |
EP1629198A1 (en) | 2006-03-01 |
JP4337635B2 (en) | 2009-09-30 |
CN100430598C (en) | 2008-11-05 |
KR20060038921A (en) | 2006-05-04 |
US20060257274A1 (en) | 2006-11-16 |
KR100701527B1 (en) | 2007-03-29 |
WO2005116450A1 (en) | 2005-12-08 |
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