CN104603459A - Hermetic compressor - Google Patents
Hermetic compressor Download PDFInfo
- Publication number
- CN104603459A CN104603459A CN201380044925.XA CN201380044925A CN104603459A CN 104603459 A CN104603459 A CN 104603459A CN 201380044925 A CN201380044925 A CN 201380044925A CN 104603459 A CN104603459 A CN 104603459A
- Authority
- CN
- China
- Prior art keywords
- type compressor
- race
- hermetic type
- thin plate
- axle
- 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.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0094—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 crankshaft
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/02—Lubrication
-
- 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
- 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
- F04B39/128—Crankcases
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
- F16C27/08—Elastic or yielding bearings or bearing supports, for exclusively rotary movement primarily for axial load, e.g. for vertically-arranged shafts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/66—Special parts or details in view of lubrication
- F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
- F16C33/664—Retaining the liquid in or near the bearing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/10—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for axial load mainly
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Compressor (AREA)
Abstract
This hermetic compressor is provided with an electric drive element (110) having a stator (114) and a rotor (116), a compression element (112), and a sealed container (102) in which the electric drive element (110) and the compression element (112) are housed and a lubricant (104) is stored. The compression element (112) is provided with a shaft (118) including a main shaft part (120) and an eccentric shaft part (112), a cylinder block (124), a main bearing (126) provided on the cylinder block (124) and axially supporting the main shaft part (120), and a thrust rolling bearing (176) arranged on the thrust surface (160) of the main bearing (126). The thrust rolling bearing (176) is provided with a top race (164), a bottom race (170), and multiple rollers (166) held by a holder unit (168), wherein an annular, flat thin plate (180) is arranged between the bottom race (170) and the thrust surface (160) of the main bearing (16).
Description
Technical field
The present invention relates to the hermetic type compressor for cooling cycle systems such as freezing-cooling storerooms.
Background technique
In recent years, expect to carry out high efficiency for reducing power consumption and low noise to the hermetic type compressor used in the refrigeration plants such as freezing-cooling storeroom.Known a kind of bearing means for hermetic type compressor (such as with reference to patent documentation 1) for the purpose of the efficient activity of hermetic type compressor.Below, with reference to Fig. 8 and Fig. 9, bearing means disclosed in patent documentation 1 is described.
Fig. 8 is the partial enlarged drawing of bearing means disclosed in patent documentation 1.Fig. 9 is the stereogram of the support unit representing the bearing means shown in Fig. 8.Wherein, in fig. 8, the above-below direction of bearing means is expressed as the above-below direction in figure.
As shown in Figure 8, in bearing means disclosed in patent documentation 1, radial bearing hub 26 has the upper tubular extension part 62 of the extension part of supporting crankshaft 20.Further, in the outside of upper tubular extension part 62, axial antifriction bearing 76 is installed.
Axial antifriction bearing 76 has the circular retainer (circular cage) 68 comprising multiple ball 66, and the plurality of retainer 66 is supported by top toroidal race 64 and lower annular seat ring 70.Top toroidal race 64 is arranged at the surface of the circumferential flange 74 of bent axle 20.In addition, between the lower surface and the top circumferentia 60 of radial bearing hub 26 of lower annular seat ring 70, support unit 80 is configured with.
Support unit 80 is configured to vibrate relative to the top circumferentia 60 of lower annular seat ring 70 and radial bearing hub 26 respectively.Specifically, support unit 80 is formed as circular, has a pair interarea (upper surface and lower surface).At the upper surface of support unit 80, be formed with a pair upper contact face 80a outstanding upward compared with this upper surface.In addition, at the lower surface of support unit 80, be formed with a pair lower contact surface 80b outstanding compared with this lower surface downwards.Upper contact face 80a and lower contact surface 80b is formed as staggering 90 degree relative to the axis of bent axle 20 respectively.
In addition, support unit 80 is configured to upper contact face 80a and contacts with the lower surface of lower annular seat ring 70, and lower contact surface 80b contacts with the top circumferentia 60 of radial bearing hub 26.In addition, between the part and the top circumferentia 60 of radial bearing hub 26 of relative with upper contact face 80a (corresponding) of the lower surface of support unit 80, space (gap) is formed with.Equally, between the part and the lower surface of lower annular seat ring 70 of relative with lower contact surface 80b (corresponding) of the upper surface of support unit 80, space (gap) is formed with.That is, support unit 80 is from substantially horizontal, is formed as wavy.
Thus, support unit 80 can flexibly support axial antifriction bearing 76.
Prior art document
Patent documentation
Patent documentation 1: Japanese Unexamined Patent Application Publication 2005-500476 publication
Summary of the invention
The technical problem solved is wanted in invention
But the present inventor find, if adopt the top toroidal race 64 of bearing means disclosed in above-mentioned patent documentation 1 or lower annular seat ring 70 to arrange the structure of the rail ring formed by the groove of ring-type, just have following technical problem.That is, when base ring shape becomes rail ring, due to its trueness error, there is ripple in rail ring.And, also find following technical problem: when with the frequency High Rotation Speed hermetic type compressor exceeding power frequency supply frequency, due to rail ring ripple caused by exciting, bent axle 20 resonates at above-below direction, likely causes the noise and vibration of compressor to increase.
The present invention makes in order to the problem solving above-mentioned prior art, though its object is to provide a kind of also can avoid when running up with the frequency exceeding power frequency supply frequency axle above-below direction resonate, the hermetic type compressor of low noise and low vibration.
For the technological scheme of dealing with problems
In order to solve the problem of above-mentioned prior art, the hermetic type compressor of this programme comprises: the electrical components comprising stators and rotators; The compression element driven by above-mentioned electrical components; With the above-mentioned electrical components of storage and above-mentioned compression element, the seal container that has the lubricant oil for lubricating above-mentioned compression element, above-mentioned compression element comprises: have and be fixed with the main shaft part of above-mentioned rotor and the axle of eccentric axial portion; There is the cylinder body of pressing chamber; Reciprocating piston in above-mentioned pressing chamber; Link the linking department of above-mentioned piston and above-mentioned eccentric axial portion; Be arranged at the main bearing supporting above-mentioned main shaft part for axle of above-mentioned cylinder body; With the thrust bearing of thrust face being configured at above-mentioned main bearing, above-mentioned thrust bearing comprises: top race; Bottom race; Be configured in the holding part between above-mentioned top race and above-mentioned bottom race; With the multiple rotors being held in above-mentioned holding part, at above-mentioned top race and above-mentioned bottom race interarea respect to one another, be provided with the rail ring formed by the groove of ring-type, above-mentioned rotor is configured with at the rail ring of above-mentioned top race and above-mentioned bottom race, between above-mentioned bottom race and the thrust face of above-mentioned main bearing, be configured with ring-type and the thin plate of flat condition.
Thus, between the thrust face of main bearing and thin plate and between bottom race and thin plate, soak into lubricant oil, utilize the attenuation effect of lubricant film thus, axle can be avoided to resonate at above-below direction.
Invention effect
According to hermetic type compressor of the present invention, when running up, axle also can be avoided to resonate at above-below direction, therefore, it is possible to the generation of restraint speckle and vibration.
Accompanying drawing explanation
Fig. 1 is the longitudinal section of the hermetic type compressor of present embodiment 1.
Fig. 2 is the schematic diagram after the major component of the hermetic type compressor shown in Fig. 1 is amplified.
Fig. 3 is the schematic diagram after the major component of the thrust bearing of the hermetic type compressor shown in Fig. 1 is amplified.
Fig. 4 is the schematic diagram after the major component of the hermetic type compressor of present embodiment 2 is amplified.
Fig. 5 is the schematic diagram after the major component of the hermetic type compressor of present embodiment 3 is amplified.
Fig. 6 is the longitudinal section of the hermetic type compressor of present embodiment 4.
Fig. 7 is the schematic diagram after the major component of the hermetic type compressor shown in Fig. 6 is amplified.
Fig. 8 is the partial enlarged drawing of bearing means disclosed in patent documentation 1.
Fig. 9 is the stereogram of the support unit representing the bearing means shown in Fig. 8.
Embodiment
Hermetic type compressor of the present invention, is characterized in that, comprising: the electrical components comprising stators and rotators; The compression element driven by above-mentioned electrical components; With the above-mentioned electrical components of storage and above-mentioned compression element, the seal container that has the lubricant oil for lubricating above-mentioned compression element, above-mentioned compression element comprises: have and be fixed with the main shaft part of above-mentioned rotor and the axle of eccentric axial portion; There is the cylinder body of pressing chamber; Reciprocating piston in above-mentioned pressing chamber; Link the linking department of above-mentioned piston and above-mentioned eccentric axial portion; Be arranged at the main bearing supporting above-mentioned main shaft part for axle of above-mentioned cylinder body; With the thrust bearing of thrust face being configured at above-mentioned main bearing, above-mentioned thrust bearing comprises: top race; Bottom race; Be configured in the holding part between above-mentioned top race and above-mentioned bottom race; With the multiple rotors being held in above-mentioned holding part, at above-mentioned top race and above-mentioned bottom race interarea respect to one another, be provided with the rail ring formed by the groove of ring-type, above-mentioned rotor is configured with at the rail ring of above-mentioned top race and above-mentioned bottom race, between above-mentioned bottom race and the thrust face of above-mentioned main bearing, be configured with ring-type and the thin plate of flat condition.
In addition, in hermetic type compressor of the present invention, multiple above-mentioned thin plate can be configured between bottom race and the thrust face of main bearing.
In addition, in hermetic type compressor of the present invention, above-mentioned thin plate can contain at least one metal in the metal of chosen from Fe, copper, aluminium.
In addition, in hermetic type compressor of the present invention, above-mentioned gauge of sheet can be less than 1/5 of the thickness of described bottom race.
In addition, in hermetic type compressor of the present invention, above-mentioned gauge of sheet can be more than 0.1mm and below 0.2mm.
In addition, in hermetic type compressor of the present invention, the planeness of the interarea contacted with above-mentioned thrust face of above-mentioned thin plate can be less than the planeness of above-mentioned thrust face.
In addition, in hermetic type compressor of the present invention, at above-mentioned axle, the mode that another interarea with above-mentioned top race is relative can be provided with flange surface, between the flange surface and another interarea of above-mentioned top race of above-mentioned axle, be configured with above-mentioned thin plate.
Below, with reference to accompanying drawing, embodiments of the present invention are described.In addition, in all of the figs, to identical or corresponding part mark same reference numerals, repeat specification is omitted.In addition, in all of the figs, in order to the present invention is described, the structural element sometimes plucking choosing necessary illustrates, and has given birth to the diagram of other structural elements.In addition, the invention is not restricted to following mode of execution.
(mode of execution 1)
[structure of hermetic type compressor]
Fig. 1 is the longitudinal section of the hermetic type compressor of present embodiment 1.Fig. 2 is the schematic diagram after the major component of the hermetic type compressor shown in Fig. 1 is amplified.Fig. 3 is the schematic diagram after the major component of the thrust bearing of the hermetic type compressor shown in Fig. 1 is amplified.In addition, in Fig. 1 ~ Fig. 3, the above-below direction of hermetic type compressor is expressed as the above-below direction in figure.
As shown in FIG. 1 to 3, the hermetic type compressor 100 of mode of execution 1 stores lubricant oil 104 at the inner bottom part of seal container 102, and compressor main body 106 is located in seal container 102 by suspension spring 108 suspension bracket.
In addition, in seal container 102, such as, be filled with the R600a (isobutane) as the low refrigeration agent of global warming up trend.
The compression element 112 that compressor main body 106 comprises electrical components 110 and driven by it.In addition, at seal container 102, the power supply terminal 113 for supplying electric power to electrical components 110 is installed.Power supply terminal 113 is electrically connected with inverter 200 via lead-in wire 201.
Inverter 200 is electrically connected with power frequency supply 203 via electric wire 202.The electric power that inverter 200 is configured to being supplied to electrical components 110 via power supply terminal 113 carries out inversion control.Thus, electrical components 110 can drive with multiple operating frequency, such as, to exceed the frequency High Rotation Speed of power frequency supply frequency.
First, electrical components 110 is described.The iron core that electrical components 110 is included in laminated thin plate reels the rotor 116 of winding made of copper and the stator 114 that formed and the internal side diameter that is configured in stator 114.
Then, compression element 112 is described.In present embodiment 1, compression element 112 is configured in the top of electrical components 110.In addition, compression element 112 comprises axle 118, cylinder body 124, piston 130, linking department (connect mechanism) 136 and thrust ball bearing (thrust bearing) 176.
Axle 118 comprises main shaft part 120 and has the eccentric axial portion 122 with the axle center of the axis parallel of main shaft part 120.In addition, main shaft part 120 is connected by joint 121 with eccentric axial portion 122.At joint 121, be formed with the flange surface 174 formed in the mode that the axle center with main shaft part 120 is roughly at a right angle.
In addition, be fixed with rotor 116 in main shaft part 120, form axle assembly (shaft assembly) 118a by main shaft part 120 and rotor 116.In addition, the lower end of axle 118 impregnated in lubricant oil 104, and axle 118 comprises the oil feeding mechanism 128 being arranged on and being made up of the spiral helicine groove 128a etc. on main shaft part 120 surface.
Be provided with the through hole of above-below direction extension at cylinder body 124, this through hole forms lubricant oil tap hole 177.Be supplied to the lubricant oil 104 of axle 118 grade from oil feeding mechanism 128, be discharged to below from lubricant oil tap hole 177.
In addition, cylinder body 124 comprises the cylinder 134 in the hole portion as cylindrical shape, and piston 130 is back and forth inserted into cylinder 134 freely.Cylinder 134 and piston 130 form pressing chamber 148.Axle 118 and piston 130 are linked by linking department 136.Specifically, the bore portion being arranged on the two ends of linking department 136 is not nested into the wrist pin 138 and eccentric axial portion 122 that are installed on piston 130, links respectively with eccentric axial portion 122 and piston 130.
At the end face of cylinder 134, valve plate 146 is installed.In addition, cylinder cap 150 is fixed with in the mode covering valve plate 146.In addition, between valve plate 146 and cylinder cap 150, absorbing silencer 152 is configured with.Absorbing silencer 152 is formed by resin formings such as PBT (polybutylene-terephthalate), is formed with silence space therein.
In addition, cylinder body 124 comprises the main bearing 126 with columnar internal surface, and the main shaft part 120 of axle 118 is inserted into main bearing 126 with rotatable state and is supported.Compression element 112 is formed as by the main shaft part 120 of the downside being configured in eccentric axial portion 122 and main bearing 126 supporting role in the structure of the cantilever bearings of the load of eccentric axial portion 122.
And, between the flange surface 174 and the main bearing 126 of cylinder body 124 of axle 118, be provided with thrust ball bearing 176.Thus, thrust ball bearing 176 is utilized to make the smooth rotation of axle 118.In addition, flange surface 174 is seen from below, is formed as the circular centered by main shaft part 120.
Then, with reference to Fig. 1 ~ Fig. 3, the main bearing 126 of axle 118, cylinder body 124 and the structure of thrust ball bearing 176 are described in more detail.
The joint 121 of axle 118 is formed as the roughly discoideus of wall thickness.At the interarea of the downside of joint 121, be formed with main shaft part 120 in the mode extended from its middle body downwards, at the interarea of the upside of joint 121, be formed with eccentric axial portion 122 in the mode extended upward near its perimembranous.
At the main bearing 126 of cylinder body 124, be formed with thrust face 160 in the mode that the axle center with this main bearing 126 is roughly at a right angle.Thrust face 160, from above-below direction, is formed as circular.In addition, in the inner peripheral portion of thrust face 160, be configured with cylindric tubular protrusions 162 in the mode of giving prominence to upward from thrust face 160.The inner peripheral surface of tubular protrusions 162 is formed as relative with the outer circumferential face of main shaft part 120.
Thrust ball bearing 176 comprises circular top race 164, multiple ball (rotor) 166, the circular holding part 168 keeping ball 166 and circular bottom race 170, by making multiple ball 166 roll with point cantact state, thus make friction very little.Thus, by reducing slippage loss, the efficiency of compressor can be improved.
With regard to forming each parts of thrust ball bearing 176, go to upside from thrust face 160, configure bottom race 170, holding part 168, top race 164 successively.More specifically, bottom race 170 and holding part 168 are configured to the central hole that tubular protrusions 162 is inserted into bottom race 170 and holding part 168.In addition, top race 164 is positioned at the top of tubular protrusions 162, and is configured to the central hole that main shaft part 120 is inserted into top race 164.In addition, between tubular protrusions 162 and thrust ball bearing 176, axial clearance 178 is formed with.
Top race 164 and bottom race 170 have a pair interarea respectively.With top race 164 and bottom race 170 interarea respect to one another (plane of trajectory orbital), be formed with the groove of ring-type, this groove form rail ring 179.Rail ring 179 is formed as arc-shaped in the mode that sectional shape is similar to the contour shape of ball 166.In addition, rail ring 179 is formed by the forging that utilizes press machine and carry out or machining, produces the ripple (out-of-flatness) caused by machining accuracy.
In addition, thrust ball bearing 176 is configured between flange surface 174 and thrust face 160, and the upper surface of top race 164 contacts with flange surface 174.In addition, between the lower surface and thrust face 160 of bottom race 170, be configured with the thin plate 180 of the ring-type (circular) with central hole.More specifically, thin plate 180 is configured to the center superposition with the revolution orbit of ball 166 viewed from above-below direction.
Thin plate 180 is configured at least one metal comprised in iron, copper and aluminium.In addition, thin plate 180 such as by SPCC (cold rolled sheet), also can adopt gasket ring (shim ring).
In addition, the thickness of thin plate 180 can be formed as less than 1/5 of the thickness of bottom race 170, also can be formed as more than 0.1mm and below 0.2mm.When the thickness of thin plate 180 is more than 0.1mm, fully can guarantee rigidity, when thickness is below 0.2mm, even if existing hermetic type compressor 100, also can configure thin plate 180 and design without the need to changing.
In addition, length (length of the half of the difference of external diameter and the internal diameter) size of the width direction of thin plate 180 both can from the view point of the resonance of above-below direction suppressing axle 118, more than the width direction size of rail ring 179, also can from the view point of being configured in thrust face 160, below the size for the width direction of thrust face 160.
In addition, thin plate 180, from the view point of being configured in thrust face 160, is formed as the external diameter that its internal diameter is greater than tubular protrusions 162, is less than the external diameter of thrust face 160.In addition, whether hermetic type compressor 100 when or not forming the mode of tubular protrusions 162 main bearing 126 tubular protrusions 162, and thin plate 180 is formed as the external diameter that its internal diameter is greater than main shaft part 120.
In addition, the planeness that thin plate 180 is formed as a pair interarea is less than the planeness of thrust face 160, is formed as respective interarea almost parallel each other.In other words, a pair interarea of thin plate 180 does not form the ripple (distortion) as wave washer.In addition, planeness refers to using when two exactly parallel geometrically planes clamp the plane as object, the interval of two planes when the interval of two parallel planes reaches minimum.
In addition, the face of the planeness of less than the 50 μm degree that machining is formed is formed at thrust face 160.Therefore, between thrust face 160 and the lower surface of thin plate 180, whole is formed with small gap 181.Equally, between the lower surface and the upper surface of thin plate 180 of bottom race 170, whole is formed with small gap 182.And lubricant oil 104 soaks into this gap 181 and gap 182, form oil film.
Therefore, whole of the lower surface of thin plate 180 contacts with thrust face 160 across oil film, and whole of the upper surface of thin plate 180 contacts across the lower surface of oil film with bottom race 170.Thus, the whole oil film being present in the lubricant oil 104 in these gaps 181 and gap 182 plays a role as oil damper (oil damper).
In addition, the oil film being formed at gap 181 and gap 182 is formed in the following manner: in the manufacturing process of hermetic type compressor 100, when main bearing 126 configures thin plate 180 and thrust ball bearing 176, lubricant oil 104 is coated in thin plate 180 etc.
[action of hermetic type compressor]
Then, with reference to Fig. 1 ~ Fig. 3, the action of the hermetic type compressor 100 of mode of execution 1 is described.
First, inverter 200, by supplying next electric power from power frequency supply 203 via lead-in wire 201 and power supply terminal 113 etc., is supplied to the stator 114 of electrical components 110.Thus, produce magnetic field at stator 114, rotor 116 rotates, and the main shaft part 120 being fixed on the axle 118 of rotor 116 thus rotates.
The eccentric rotary of the eccentric axial portion 122 of carrying out with the rotation of main shaft part 120 is changed by linking department 136, makes piston 130 to-and-fro motion in cylinder 134.In addition, the volume-variation of pressing chamber 148, carries out the refrigeration agent in seal container 102 being drawn into the compressed action carrying out in pressing chamber 148 compressing thus.
In the suction stroke carried out with compressed action, refrigeration agent in seal container 102 is inhaled in pressing chamber 148 via absorbing silencer 152 off and on, in pressing chamber 148 after compression, the refrigeration agent of High Temperature High Pressure is sent to refrigeration cycle (not shown) from seal container 102 via discharging pipe arrangement etc.
In addition, rotated by axle 118, lubricant oil 104 is supplied to by oil feeding mechanism 128 lubrication that main shaft part 120 carries out this main shaft part 120.Then, the part of lubricant oil 104 is discharged downwards from the lubricant oil tap hole 177 of cylinder body 124 after carrying out the lubrication of each slide part from each portion that axial clearance 178 is supplied to compression element 112.In addition, other parts of lubricant oil 104 are supplied to thrust ball bearing 176 from axial clearance 178.In addition, after the lubricant oil 104 being supplied to thrust ball bearing 176 makes thrust face 160 lubricate, one partial saturation is to gap 181 and gap 182, and other parts are discharged downwards from lubricant oil tap hole 177.
[action effect of hermetic type compressor]
Then, with reference to Fig. 1 ~ Fig. 3, the action effect of the hermetic type compressor 100 of mode of execution 1 is described.
In the hermetic type compressor 100 of present embodiment 1, be configured with thrust ball bearing 176.Therefore, ball 166 rolls between top race 164 and bottom race 170, can suppress the slippage loss of axle 118 thus, can reduce the torque that axle 118 is rotated.Thereby, it is possible to reduce the electric power being supplied to electrical components 110, the efficient activity of hermetic type compressor 100 can be realized.
But the load of axle 118 and rotor 116 etc. acts on rail ring 179 via top race 164 and bottom race 170.And as mentioned above, there is the ripple caused by machining accuracy in rail ring 179.
Therefore, when hermetic type compressor 100 operates, the ball 166 on rail ring 179 is subject to the exciting caused by ripple.This exciting becomes large especially when the hermetic type compressor of the inverter motor being mounted with High Rotation Speed runs up, likely make low-resonance on axle 118 by top race 164 and bottom race 170.
But, in the hermetic type compressor 100 of present embodiment 1, between bottom race 170 and thrust face 160, be configured with the thin plate 180 of flat condition.Therefore, lubricant oil 104 is impregnated into the gap 182 of the lower surface of the gap 181 of the lower surface of thrust face 160 and thin plate 180 and the upper surface of thin plate 180 and bottom race 170, produces the attenuation effect caused by oil film be formed on whole.Thereby, it is possible to utilize attenuation effect to avoid the resonance of the above-below direction of axle 118, the noise and vibration of hermetic type compressor 100 can be suppressed to increase.
In addition, in bearing means disclosed in patent documentation 1, support unit 80 is configured between the lower surface of lower annular seat ring 70 and the top circumferentia 60 of radial bearing hub 26, but as mentioned above, support unit 80 is formed as waveform viewed from substantially horizontal.
Therefore, between the part and the top circumferentia 60 of radial bearing hub 26 of relative with upper contact face 80a (corresponding) of the lower surface of support unit 80, form space (gap).Equally, between the part and the lower surface of lower annular seat ring 70 of relative with lower contact surface 80b (corresponding) of the upper surface of support unit 80, form space (gap).Therefore, support unit 80 and top circumferentia 60 and lower annular seat ring 70 point cantact or linear contact lay, so the oil film being formed in contact segment is little, the attenuation effect of oil film is insufficient.
(mode of execution 2)
The hermetic type compressor of present embodiment 2 exemplifies the mode being configured with multiple thin plate between bottom race and the thrust face of main bearing.
[structure of hermetic type compressor]
Fig. 4 is the schematic diagram after the major component of the hermetic type compressor of present embodiment 2 is amplified.In addition, in Fig. 4, the above-below direction of hermetic type compressor represents the above-below direction in mapping.
As shown in Figure 4, the hermetic type compressor 100 of present embodiment 2 is identical with hermetic type compressor 100 basic structure of mode of execution 1, but difference is that thin plate 180 is configured with multiple (being 3 herein).Specifically, go to upside from thrust face 160, be configured with thin plate 180C, thin plate 180B and thin plate 180A successively.
Thus, between thin plate 180C and thin plate 180B, be formed with gap 184, between thin plate 180B and thin plate 180A, form gap 183.Further, lubricant oil 104 is impregnated into gap 183 and gap 184.
Therefore, the hermetic type compressor 100 of mode of execution 2 is compared with the hermetic type compressor 100 of mode of execution 1, produce further attenuation effect, the resonance of the above-below direction of axle 118 can be avoided thus, the noise and vibration of hermetic type compressor 100 can be suppressed further to increase.
(mode of execution 3)
The hermetic type compressor of present embodiment 3 exemplifies, on axle, the mode that another interarea with top race is relative is provided with flange surface, is configured with the mode of thin plate between the flange surface and another interarea of top race of axle.
Fig. 5 is the schematic diagram after the major component of the hermetic type compressor of present embodiment 3 is amplified.In addition, in Fig. 5, the above-below direction of hermetic type compressor represents the above-below direction in mapping.
As shown in Figure 5, the hermetic type compressor 100 of present embodiment 3 is identical with closed compressor 100 basic structure of mode of execution 1, but difference is, between the flange surface 174 and the upper surface of top race 164 of axle 118, be configured with the thin plate 190 of the ring-type (circular) with inner peripheral surface and outer circumferential face.
Thin plate 190 is formed substantially in the same manner as thin plate 180, but inner circumferential surface is different with the structure of outer circumferential face.Specifically, thin plate 190 never suppresses the viewpoint of the rotation of axle 118 to be set out, and the diameter of inner circumferential surface is formed as the diameter of the outer circumferential face being greater than main shaft part 120.In addition, the outer circumferential face of thin plate 190 can set arbitrarily in the scope of rotation not suppressing axle 118.
The flange surface 174 of axle 118 is same with thrust face 160, forms the face of the planeness of less than the 50 μm degree that mechanical machining causes.Therefore, between the upper surface of flange surface 174 and thin plate 190, be formed with small gap 185.Equally, between the lower surface and the upper surface of top race 164 of thin plate 190, be also formed with small gap (not shown).And lubricant oil 104 is impregnated into these gaps, form oil film.
Therefore, in the hermetic type compressor of mode of execution 3, compared with the hermetic type compressor 100 of mode of execution 1, produce further attenuation effect, the resonance of the above-below direction of axle 118 can be avoided thus, the noise and vibration of hermetic type compressor 100 can be suppressed further to increase.
In addition, in the hermetic type compressor 100 of present embodiment 3, adopt the mode of a configuration thin plate 190, but be not limited thereto.Also the mode configuring multiple thin plate 190 can be adopted.In addition, in the hermetic type compressor 100 of present embodiment 3, adopt the structure of a configuration thin plate 180, but be not limited thereto, also as the hermetic type compressor 100 of mode of execution 2, the mode of the multiple thin plate 180 of configuration can be adopted.
(mode of execution 4)
Fig. 6 is the longitudinal section of the hermetic type compressor of present embodiment 4.Fig. 7 is the schematic diagram after the major component of the hermetic type compressor shown in Fig. 6 is amplified.In addition, in Fig. 6 and Fig. 7, the above-below direction of hermetic type compressor represents the above-below direction in mapping.In addition, in Fig. 6, eliminate the diagram of inverter etc.
As shown in Figure 6 and Figure 7, the hermetic type compressor 100 of present embodiment 4 is also identical with in hermetic type compressor 100 basic structure of mode of execution 1, but difference is: compression element 112 is configured in the below this point of electrical components 110 and on rotor 116, is provided with flange surface 174 this point.In addition, thrust ball bearing 176 is configured between the flange surface 174 of rotor 116 and the thrust face 160 of main bearing 126.
The hermetic type compressor 100 of the present embodiment 4 of such formation, also can play the action effect same with the hermetic type compressor 100 of mode of execution 1.In addition, in the hermetic type compressor 100 of present embodiment 4, adopt the mode of a configuration thin plate 180, but be not limited thereto, also can as the hermetic type compressor 100 of mode of execution 2, adopt the mode of the multiple thin plate 180 of configuration, as the hermetic type compressor 100 of mode of execution 3, the mode of configuration thin plate 190 can also be adopted.
According to the above description, to those skilled in the art, the present invention can make multiple improvement and other mode of executions are apparent.Therefore, above-mentioned explanation should be interpreted as just exemplary, and the object provided is that instruction those skilled in the art implement optimum mode of execution of the present invention.Without departing from the spirit and scope of the invention, its structure and/or function can substantially be changed.In addition, the appropriately combined of multiple structural element disclosed in above-mentioned mode of execution can be utilized to realize various invention.
Utilizability in industry
Hermetic type compressor of the present invention also can be avoided when running up axle in above-below direction resonance and can suppress the noise and vibration of hermetic type compressor, can be widely used in air conditioner or vending machine etc. and employ hermetic type compressor used in the equipment of refrigeration cycle.
Description of reference numerals
20 bent axles
26 radial bearing hubs
60 top circumferentias
62 upper tubular extension parts
64 top toroidal race
66 balls
68 circular retainers
70 lower annular seat rings
74 circumferential flange
76 axial antifriction bearings
80 support units
80a upper contact face
80b lower contact surface
100 hermetic type compressors
102 seal containers
104 lubricant oil
106 compressor main bodies
108 suspension springs
110 electrical components
112 compression elements
113 power supply terminals
114 stators
116 rotors
118 axles
118a axle assembly
120 main shaft part
121 joints
122 eccentric axial portion
124 cylinder bodies
126 main bearings
128 oil feeding mechanisms
128a groove
130 pistons
134 cylinders
136 linking departments
138 wrist pins
146 valve plates
148 pressing chambers
150 cylinder caps
152 absorbing silencers
160 thrust faces
162 tubular protrusions
164 top races
166 balls
168 holding parts
170 bottom races
174 flange surfaces
176 thrust ball bearings
177 lubricant oil tap holes
178 axial clearances
179 rail rings
180 thin plates
180A thin plate
180B thin plate
180C thin plate
181 gaps
182 gaps
183 gaps
184 gaps
185 gaps
190 thin plates
200 inverters
201 lead-in wires
202 electric wires
203 power frequency supplies
Claims (7)
1. a hermetic type compressor, is characterized in that, comprising:
Comprise the electrical components of stators and rotators;
The compression element driven by described electrical components; With
Seal container that receive described electrical components and described compression element, that have the lubricant oil for lubricating described compression element,
Described compression element comprises: have and be fixed with the main shaft part of described rotor and the axle of eccentric axial portion; There is the cylinder body of pressing chamber; Reciprocating piston in described pressing chamber; Link the linking department of described piston and described eccentric axial portion; Be arranged at the main bearing supporting described main shaft part for axle of described cylinder body; With the thrust bearing of thrust face being configured at described main bearing,
Described thrust bearing comprises: top race; Bottom race; Be configured in the holding part between described top race and described bottom race; With the multiple rotors being held in described holding part,
At described top race and described bottom race interarea respect to one another, be provided with the rail ring formed by the groove of ring-type,
Described rotor is configured with at the rail ring of described top race and described bottom race,
Between described bottom race and the thrust face of described main bearing, be configured with ring-type and the thin plate of flat condition.
2. hermetic type compressor as claimed in claim 1, is characterized in that:
Multiple described thin plate is configured between bottom race and the thrust face of main bearing.
3. hermetic type compressor as claimed in claim 1 or 2, is characterized in that:
Described thin plate is containing at least one metal in the metal of chosen from Fe, copper, aluminium.
4. the hermetic type compressor as described in any one in claims 1 to 3, is characterized in that:
Described gauge of sheet is less than 1/5 of the thickness of described bottom race.
5. the hermetic type compressor as described in any one in Claims 1 to 4, is characterized in that:
Described gauge of sheet is more than 0.1mm below 0.2mm.
6. the hermetic type compressor as described in any one in Claims 1 to 5, is characterized in that:
The planeness of the interarea contacted with described thrust face of described thin plate is less than the planeness of described thrust face.
7. the hermetic type compressor as described in any one in claim 1 ~ 6, is characterized in that:
At described axle, the mode that another interarea with described top race is relative is provided with flange surface,
Described thin plate is configured with between the flange surface and another interarea of described top race of described axle.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2012-193776 | 2012-09-04 | ||
| JP2012193776 | 2012-09-04 | ||
| PCT/JP2013/005122 WO2014038163A1 (en) | 2012-09-04 | 2013-08-29 | Hermetic compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104603459A true CN104603459A (en) | 2015-05-06 |
| CN104603459B CN104603459B (en) | 2017-06-09 |
Family
ID=50236793
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380044925.XA Active CN104603459B (en) | 2012-09-04 | 2013-08-29 | Hermetic type compressor |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20150211507A1 (en) |
| JP (1) | JP6199293B2 (en) |
| CN (1) | CN104603459B (en) |
| WO (1) | WO2014038163A1 (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2017206650A1 (en) * | 2016-06-03 | 2017-12-07 | 珠海格力电器股份有限公司 | Bearing and air conditioner |
| CN107664110A (en) * | 2016-07-27 | 2018-02-06 | 日立空调·家用电器株式会社 | Hermetic type compressor |
| CN111287942A (en) * | 2018-12-10 | 2020-06-16 | 安徽美芝制冷设备有限公司 | Compressor with a compressor housing having a plurality of compressor blades |
| CN112523996A (en) * | 2020-12-05 | 2021-03-19 | 江西泛宇压缩机科技有限公司 | Novel compressor crankshaft |
| CN112539156A (en) * | 2020-12-05 | 2021-03-23 | 江西泛宇压缩机科技有限公司 | Compressor crankshaft capable of oiling rapidly |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105518299B (en) * | 2013-09-03 | 2019-06-21 | 松下电器制冷装置新加坡 | Hermetic type compressor and the freezer or refrigerating plant for being mounted with the compressor |
| US20180100415A9 (en) * | 2015-04-22 | 2018-04-12 | Carrier Corporation | Systems of preventing engine bearing damage |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3093427A (en) * | 1959-05-11 | 1963-06-11 | Vasta Francesco | Ball or roller bearings |
| CN1549898A (en) * | 2001-08-31 | 2004-11-24 | ѹ��������˾ | Axial bearing structure for closed compressor |
| JP2008002371A (en) * | 2006-06-23 | 2008-01-10 | Matsushita Electric Ind Co Ltd | Hermetic compressor |
| CN101111676A (en) * | 2005-11-22 | 2008-01-23 | 松下电器产业株式会社 | Hermetic compressor |
| CN101900100A (en) * | 2009-06-01 | 2010-12-01 | 松下电器产业株式会社 | Closed-type compressor |
| JP2012107515A (en) * | 2010-11-15 | 2012-06-07 | Panasonic Corp | Hermetic compressor |
| JP2012122333A (en) * | 2010-12-06 | 2012-06-28 | Panasonic Corp | Hermetic compressor |
Family Cites Families (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2593919A (en) * | 1948-03-20 | 1952-04-22 | Fafnir Bearing Co | Thrust bearing |
| US3058790A (en) * | 1960-12-07 | 1962-10-16 | Admiral Corp | Mounting for a phonograph turntable |
| US4699530A (en) * | 1985-06-28 | 1987-10-13 | Oiless Industry Co., Ltd. | Thrust ball bearing unit |
| JP3870592B2 (en) * | 1999-01-11 | 2007-01-17 | 日本精工株式会社 | Half toroidal continuously variable transmission |
| US7329048B2 (en) * | 2005-07-19 | 2008-02-12 | Rolls-Royce Corporation | Self contained squeeze film damping system |
| US20070058895A1 (en) * | 2005-09-13 | 2007-03-15 | Paschoalino Marcelo R | Anti-friction thrust bearing centering device for hermetic refrigeration compressors |
| US7517155B2 (en) * | 2006-08-30 | 2009-04-14 | Honeywell International Inc. | Resilient mount of uniform stiffness |
| JP5228812B2 (en) * | 2008-11-06 | 2013-07-03 | パナソニック株式会社 | Hermetic compressor |
| DE102008060116A1 (en) * | 2008-12-03 | 2010-06-10 | Ab Skf | Method for producing a bearing arrangement and bearing arrangement |
| JP5353414B2 (en) * | 2009-04-27 | 2013-11-27 | パナソニック株式会社 | Hermetic compressor and refrigeration system |
| US8337090B2 (en) * | 2009-09-10 | 2012-12-25 | Pratt & Whitney Canada Corp. | Bearing support flexible ring |
| JP5919745B2 (en) * | 2011-11-15 | 2016-05-18 | 株式会社島津製作所 | Vacuum pump |
-
2013
- 2013-08-29 US US14/423,987 patent/US20150211507A1/en not_active Abandoned
- 2013-08-29 JP JP2014534176A patent/JP6199293B2/en active Active
- 2013-08-29 WO PCT/JP2013/005122 patent/WO2014038163A1/en active Application Filing
- 2013-08-29 CN CN201380044925.XA patent/CN104603459B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3093427A (en) * | 1959-05-11 | 1963-06-11 | Vasta Francesco | Ball or roller bearings |
| CN1549898A (en) * | 2001-08-31 | 2004-11-24 | ѹ��������˾ | Axial bearing structure for closed compressor |
| CN101111676A (en) * | 2005-11-22 | 2008-01-23 | 松下电器产业株式会社 | Hermetic compressor |
| JP2008002371A (en) * | 2006-06-23 | 2008-01-10 | Matsushita Electric Ind Co Ltd | Hermetic compressor |
| CN101900100A (en) * | 2009-06-01 | 2010-12-01 | 松下电器产业株式会社 | Closed-type compressor |
| JP2012107515A (en) * | 2010-11-15 | 2012-06-07 | Panasonic Corp | Hermetic compressor |
| JP2012122333A (en) * | 2010-12-06 | 2012-06-28 | Panasonic Corp | Hermetic compressor |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2017206650A1 (en) * | 2016-06-03 | 2017-12-07 | 珠海格力电器股份有限公司 | Bearing and air conditioner |
| CN107664110A (en) * | 2016-07-27 | 2018-02-06 | 日立空调·家用电器株式会社 | Hermetic type compressor |
| CN111287942A (en) * | 2018-12-10 | 2020-06-16 | 安徽美芝制冷设备有限公司 | Compressor with a compressor housing having a plurality of compressor blades |
| CN111287942B (en) * | 2018-12-10 | 2022-05-03 | 安徽美芝制冷设备有限公司 | Compressor |
| CN112523996A (en) * | 2020-12-05 | 2021-03-19 | 江西泛宇压缩机科技有限公司 | Novel compressor crankshaft |
| CN112539156A (en) * | 2020-12-05 | 2021-03-23 | 江西泛宇压缩机科技有限公司 | Compressor crankshaft capable of oiling rapidly |
Also Published As
| Publication number | Publication date |
|---|---|
| JPWO2014038163A1 (en) | 2016-08-08 |
| US20150211507A1 (en) | 2015-07-30 |
| JP6199293B2 (en) | 2017-09-20 |
| CN104603459B (en) | 2017-06-09 |
| WO2014038163A1 (en) | 2014-03-13 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104603459A (en) | Hermetic compressor | |
| EP2325489B1 (en) | Sealed compressor | |
| US11710992B2 (en) | Motor and compressor including the same | |
| KR20140045318A (en) | Bearing arrangement for a reciprocating refrigeration compressor | |
| KR20080090391A (en) | Hermetic compressor | |
| JP2013160291A (en) | Thrust ball bearing | |
| CN105074219A (en) | Scroll compressor | |
| CN104379930A (en) | Hermetic compressor | |
| US9841024B2 (en) | Compressor and method for producing compressor | |
| KR101275956B1 (en) | Rotary compressor | |
| JP5939993B2 (en) | Thrust rolling bearings, especially ball bearings with single-side action thrust grooves | |
| CN103089630B (en) | Rotary compressor | |
| CN106438269A (en) | Oilless air compressor transmission mechanism | |
| CN102192128A (en) | Compressor and refrigerator with the same | |
| KR101563368B1 (en) | compressor | |
| JP2013119945A (en) | Thrust bearing and hermetic compressor | |
| CN203051034U (en) | Refrigerator compressor and oil filter device | |
| JP2014001812A (en) | Thrust ball bearing | |
| WO2013021652A1 (en) | Hermetic type compressor | |
| JP2014034898A (en) | Sealed compressor, and refrigerator or air conditioner including the same | |
| JP2014227919A (en) | Compressor | |
| JP2012107515A (en) | Hermetic compressor | |
| JP5942080B2 (en) | Hermetic compressor | |
| JP2014098382A (en) | Rotary compressor | |
| JP2013124640A (en) | Hermetic compressor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C41 | Transfer of patent application or patent right or utility model | ||
| TA01 | Transfer of patent application right |
Effective date of registration: 20170224 Address after: Osaka Japan Applicant after: Matsushita Electric Industrial Co.,Ltd. Address before: Osaka Japan Applicant before: PANASONIC INTELLECTUAL PROPERTY MANAGEMENT Co.,Ltd. |
|
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20180502 Address after: Singapore Bedok South 1 Street Patentee after: PANASONIC APPLIANCES REFRIGERATION DEVICES SINGAPORE Address before: Osaka Japan Patentee before: Matsushita Electric Industrial Co.,Ltd. |