CN106014991B - Rotary closed type compressor - Google Patents
Rotary closed type compressor Download PDFInfo
- Publication number
- CN106014991B CN106014991B CN201610096224.6A CN201610096224A CN106014991B CN 106014991 B CN106014991 B CN 106014991B CN 201610096224 A CN201610096224 A CN 201610096224A CN 106014991 B CN106014991 B CN 106014991B
- Authority
- CN
- China
- Prior art keywords
- rotary
- countershaft
- type compressor
- eccentric shaft
- closed type
- 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.)
- Active
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/32—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
- F04C18/324—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members with vanes hinged to the inner member and reciprocating with respect to the outer member
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The present invention, which provides, a kind of is able to maintain that reliability is constant and realizes the rotary closed type compressor of high output (100).Rotary closed type compressor (100) is accommodated with motor (2) and compression mechanism (3) in closed container (1), compression mechanism (3) is linked in motor (2) lower part by crank axle (4) and motor (2), compression mechanism (3) has crank axle (4), crank axle (4) has the main shaft (4a) for being fixed on motor (2), countershaft (4b), and eccentric shaft (4c), the length of countershaft (4b) is being set as L, and when the length of eccentric shaft (4c) is set as l, make 0.75 or less l/L.
Description
Technical field
The present invention relates to the rotary closed type compressions for the compression that refrigerant gas is carried out used in cooling cycle system
Machine.
Background technique
In order to which piston is embedded in eccentric shaft in assemble compressible machine, need to make to subtract eccentric shaft from the radius of eccentric shaft opposite
The resulting value of eccentricity in the center of main shaft or countershaft is greater than or equal to the radius of main shaft or countershaft.Assuming that from bias
If the radius of axis is intended in the case where subtracting the resulting value of eccentricity less than the main shaft perhaps radius of countershaft across main shaft or countershaft
And if piston is embedded in eccentric shaft, then the internal diameter of the outer diameter of eccentric shaft and piston can generate interference and lead to not be embedded in.
If expanding discharge volume to expand the ability of compressor, need to reduce the outer diameter of piston, and increases bias
Amount.
But the following topics exist, it may be assumed that restriction when being embedded in because of piston as described above towards eccentric shaft, thus can not
Increase eccentricity so that subtracting the resulting value of eccentricity less than main shaft or the radius of countershaft from eccentric shaft radius.
In order to solve the above problems, following hermetic type compressor is shown in existing technology: making the countershaft of crank axle
Diameter be less than the diameter of main shaft, thus make to subtract from the radius of eccentric shaft the resulting value of eccentricity more than or equal to countershaft partly
Diameter (for example, referring to Fig. 1 and Fig. 7 of patent document 1).
Patent document 1: Japanese Unexamined Patent Publication 2011-127430 bulletin
However, the following topics exist for hermetic type compressor documented by above patent document 1: due to the diameter of countershaft becomes smaller
So that bearing portion generates a possibility that sintering and increases, in addition, being easy to produce because of the length for expanding discharge volume, i.e. lengthening eccentric shaft
Raw flexure.If discharge volume to be increased and the length for lengthening eccentric shaft, the gas load by discharge chambe in this case can be made
Eccentric shaft generate slight flexure, but the following topics exist, it may be assumed that countershaft can be in pair if eccentric shaft is largely bent
Bearing is tilted, and the oil film thickness in bearing is become smaller, and the lubrication state of bearing portion is deteriorated, and exists so as to cause axis and bearing
It is sintered in compressor operation, is thus possible to make the operating of compressor to stop and can not restart.For the above subject, special
The relationship of the length of supplementary bearing and the length of eccentric shaft is not accounted in technology documented by sharp document 1.
Summary of the invention
The present invention is made to solve project as described above, and its purpose is to provide one kind can be not generate
The mode of the sintering of supplementary bearing maintains reliability constant and increases the discharge volume of compressor and realize the rotary of high output
Hermetic type compressor.
Rotary closed type compressor according to the present invention is accommodated with motor and compression mechanism in closed container, should
Compression mechanism links in the lower part of the motor, and by crank axle and the motor, which has crank axle, the song
Arbor has: main shaft, is fixed on above-mentioned motor；Countershaft, central shaft are identical as the central axis of the main shaft；And it is eccentric
Axis is formed between above-mentioned main shaft and above-mentioned countershaft, and the eccentricity of central axis relative to above-mentioned main shaft, above-mentioned rotary closed
Type compressor is characterized in that, when the length of above-mentioned countershaft is set as L, and the length of above-mentioned eccentric shaft is set as l, makes l/L
It is 0.75 or less.
Also, it is preferred that the outer diameter of above-mentioned countershaft is set to be the outer diameter of above-mentioned main shaft or less.
Also, it is preferred that compression mechanism has: rotary-piston, it is chimeric with above-mentioned eccentric shaft；Cylinder body, above-mentioned rotation are living
Plug is inserted into the cylindric space of the inside of above-mentioned cylinder body, and above-mentioned cylinder body is fixed in closed container；Blade, will be by above-mentioned cylinder
The periphery of the medial surface of body and the above-mentioned rotary-piston rotated in above-mentioned cylinder body is formed by discharge chambe and is divided into sucking side pressure
Contracting room and discharge side discharge chambe, above-mentioned rotary-piston are formed as one with the blade.
Also, it is preferred that the longitudinal modulus of elasticity of the material of above-mentioned crank axle is 150000~220000N/mm2。
In accordance with the invention it is possible to provide the length ratio of a kind of length by suitably setting eccentric shaft and supplementary bearing come
It maintains the reliability for the sintering for not generating bearing constant, and increases the discharge volume of compressor, to realize the rotation of high output
Rotatable hermetic type compressor.
Detailed description of the invention
Fig. 1 is the longitudinal section view of rotary closed type compressor involved in embodiment 1.
Fig. 2 is the skeleton diagram for indicating the discharge chambe of piston involved in embodiment 1 and vane type.
Fig. 3 is the figure for indicating the crank axle of rotary closed type compressor involved in embodiment 1.
Fig. 4 is the value for indicating the l/L of rotary closed type compressor involved in embodiment 1 and the rough surface of countershaft
Generation situation relationship figure.
Fig. 5 is the skeleton diagram for indicating shuttle-type discharge chambe.
The explanation of appended drawing reference
1... closed container；1a... closed container；1b... closed container；2... motor；2a... stator；2b... turns
Son；3... compression mechanical part；4... crank axle；4a... main shaft；4b... countershaft；4c... eccentric shaft；5... base bearing；6...
Supplementary bearing；7... cylinder body；8... rotary-piston；8a... (swing type) rotary-piston；9... discharge chambe；9a... sucks side compression
Room；9b... discharge side discharge chambe；10... connecting piece is sucked；11... discharge pipe；12... reservoir；13... blade；100...
Rotary closed type compressor；L... the length of countershaft；L... the length of eccentric shaft.
Specific embodiment
Embodiment 1.
Fig. 1 is the longitudinal section view of rotary closed type compressor 100 involved in present embodiment.
Rotary closed type compressor 100 is in the enclosed high pressure environment being made of upper container 1a and bottom container 1b
In closed container 1, it is accommodated with by stator 2a and rotor the 2b motor 2 constituted and the compression mechanism driven by motor 2
Portion 3.
The rotary force of motor 2 is transmitted via crank axle 4 to compression mechanical part 3.
Crank axle 4 is made of such as lower component, it may be assumed that is fixed on the main shaft 4a of the rotor 2b of motor 2, across compression mechanical part
3 and the eccentric shaft 4c that is set to the countershaft 4b of the opposite side of main shaft 4a and is formed between main shaft 4a and countershaft 4b.Countershaft 4b
Central axis it is identical as the central axis of main shaft 4a.The size relationship of the outer diameter of main shaft 4a, countershaft 4b and eccentric shaft 4c is set
To subtract eccentric shaft from the radius of eccentric shaft 4c and being equal to relative to the resulting value of eccentricity at the center of main shaft and countershaft or greatly
In the radius of main shaft.In addition, being internally provided with oil supplying hole in crank axle 4.
Base bearing 5 is chimeric with the main shaft 4a of crank axle 4 in a manner of the gap with sliding, and main shaft 4a is pivotally supported
For that can rotate.In addition, supplementary bearing 6 is chimeric with the countershaft 4b of crank axle 4 in a manner of the gap with sliding, and by countershaft
4b is pivotally supported to rotate.Space between compression mechanical part 3 and motor 2 sets the axis of base bearing 5 as long as possible
To length.In the space of the lower part of compression mechanical part 3, is matched with the axial length of countershaft 4b and set pair as long as possible
Bearing 6.
From the upper direction in Fig. 1 using base bearing 5 and from below to using supplementary bearing 6 will be accommodated with rotary-piston 8 and
The axial ends face closure of the inner space of the cylinder body 7 of blade 13, to form discharge chambe 9, wherein rotary-piston 8 is with can
The mode of sliding is chimeric with the eccentric shaft 4c of crank axle 4.
Fig. 2 is the skeleton diagram for indicating the discharge chambe of piston and vane type involved in present embodiment.
Compression mechanical part 3 has cylinder body 7 and blade 13.Cylinder body 7 is fixed on the inner peripheral portion of closed container 1.Cylinder body 7 has circle
The inner space of tubular, in the inner space, configured with chimeric with the eccentric shaft 4c of crank axle 4 rotation in a manner of it can rotate
Turn a work plug 8.Blade 13 is moved along the slot for being set to cylinder body 7.Blade 13 follows the fortune that rotary-piston 8 is swung inside cylinder body 7
It moves and is moved, and be divided into suction side discharge chambe 9a for discharge chambe 9 is formed by by the inner wall of cylinder body 7 and rotary-piston 8
With discharge side discharge chambe 9b.
It is abutted with closed container 1 and is provided with reservoir 12.Sucking connecting piece 10 links cylinder body 7 and reservoir 12
Come.
It is discharged by the refrigerant gas that rotary-piston 8 and blade 13 have compressed into closed container 1 in cylinder body 7, and from
Discharge pipe 11 is sent out to cooling cycle systems such as refrigerating air conditioning devices, wherein above-mentioned rotary-piston 8 and the rotation by crank axle 4
Then the eccentric shaft 4c for the crank axle 4 being eccentrically rotated is chimeric.
Fig. 3 is the figure for indicating the crank axle of rotary closed type compressor 100 involved in present embodiment.
The central axis of the main shaft 4a and countershaft 4b of crank axle 4 are formed as coaxially, and the central axis of eccentric shaft 4c is relative to master
The distortion of axis 4a and countershaft 4b.As shown in figure 3, if the length of the eccentric shaft 4c of crank axle 4 is l, the length of countershaft 4b
For L, then make 0.75 or less l/L.
Due to constituting rotary closed type compressor 100 as described above, so for example in the energy in order to increase compressor
Power and in the case where expanding discharge volume, if lengthening the length of eccentric shaft 4c, the eccentric shaft of the gas load by discharge chambe 9
4c can slightly be bent, if but eccentric shaft 4c largely bend, incline in the countershaft 4b that the internal diameter of supplementary bearing 6 is supported
Tiltedly.The thinning part of the oil film thickness of the contact portion of supplementary bearing 6 and countershaft 4b is generated, as a result, so as to cause the lubrication of supplementary bearing 6
The reduction of performance.But according to the present embodiment, by make the eccentric shaft of crank axle 4 length l and countershaft 4b length L it
Than l/L 0.75 hereinafter, the rigidity of the crank axle 4 when so as to improve by gas load, thus, it is possible to inhibit countershaft 4b
It is tilted in the internal side diameter of supplementary bearing 6.
Fig. 4 is the surface for indicating the value of the l/L of rotary closed type compressor 100 and countershaft involved in present embodiment
The figure of the relationship of coarse generation situation."○" in figure indicates that the contact surface of countershaft 4b and supplementary bearing does not generate coarse, "×"
The contact surface of expression countershaft and supplementary bearing produces coarse.In the real machine of rotary closed type compressor 100, make eccentric shaft 4c
Length and the length ratio of countershaft 4b that is, the value of l/L change, and be confirmed whether to reach sintering by testing, it is interim,
In the case that l/L is greater than 0.75, the rough surface as caused by the sliding surface wear as sintering sign can be confirmed.In l/
When L is in 0.75 range below, although seeing abrasion, for smooth state of wear and the sign for leading to be sintered is not generated.
In addition, the song of rotary closed type compressor 100 involved in present embodiment when obtaining result shown in Fig. 4
The longitudinal modulus of elasticity of the material of arbor 4 is 150000~220000N/mm2.In addition, the value of I/L is lower, then crank axle 4 is rigid
Property it is higher, it is also more advantageous for the sintering of bearing, but under normal circumstances used in rotary closed type compressor 100,
Lower limit value in practical use is l/L=0.5 or so.
The size in each portion of crank axle 4 involved in present embodiment is as follows.
The length l of countershaft 4b is in the range of 10mm~100mm, and the diameter of countershaft 4b is in the range of 10mm~50mm.
The size for the pressure based on load that the effect length bearing portion of countershaft 4b and supplementary bearing 6 is born, the more short then pressure of length
It is bigger, it is also higher to generate a possibility that being sintered.The contact of the influence of the diameter of countershaft 4b and supplementary bearing 6 countershaft 4b and supplementary bearing 6
A possibility that relative velocity in face, relative velocity is higher, then generates the sintering of bearing portion is higher.Countershaft 4b and supplementary bearing 6
Diameter is smaller, then relative velocity is higher.
The diameter of eccentric shaft 4c is 20mm~80mm.The diameter of eccentric shaft 4c influences discharge volume, the diameter of eccentric shaft 4c
More big then discharge volume is bigger, and load suffered by eccentric shaft 4c is also bigger.If load is larger, what bearing portion generation was sintered can
Energy property is got higher.
The outer diameter of countershaft 4b is set to the outer diameter relative to main shaft 4a in diametrically small 0~5mm or so.By by countershaft
4b is set as smaller than main shaft 4a, to be capable of increasing partially compared with the case where main shaft 4a and countershaft 4b are made of identical diameter
The eccentricity of mandrel 4c, so as to increase discharge volume.At this point, subtracting eccentric shaft 4c relative to pair from the radius of eccentric shaft 4c
The resulting value of the eccentricity at the center of axis 4b needs the radius equal to or more than countershaft 4b, but might be less that the half of main shaft 4a
Diameter.If meeting the condition, rotary-piston 8 can be assembled from the side countershaft 4b.
In addition, implementing under conditions of rotary closed type compressor 100 used in general refrigeration machine etc. rotary
The operating condition of hermetic type compressor 100 (revolving speed uses refrigerant, lubricating oil).
According to the rotary closed type compressor 100 of above structure, by the length l and pair that make the eccentric shaft of crank axle 4
The ratio between the length L of axis 4b l/L is 0.75 hereinafter, gas load so as to inhibit the portion eccentric shaft 4c by crank axle 4 to be subject to
Caused flexure.Thereby, it is possible to coarse and bearing the burnings for the supplementary bearing for preventing the crank axle 4 to rotation from being supported
Knot can also obtain the rotary closed type compressor 100 of high reliablity even if increasing discharge volume.
In addition, in the present embodiment, individual is independent with blade 13 to rotary-piston 8 and is illustrated, still,
It, also can be as following even if the oscillating-piston that rotary closed type compressor 100 is integrated using rotary-piston 8 and blade 13
The rotary closed type compressor 100 of high reliablity is obtained as explanation.
Fig. 5 is the skeleton diagram for indicating swing type discharge chambe 9.For above explained compression mechanical part 3, make and rotary-piston
8 and the comparable sectoral integration of blade 13 and be formed as swinging type rotary piston 8a.Cylinder body 7 is again formed as living with swinging type rotary
The construction that plug 8a is matched.
In common operating, rotary closed type compressor 100 is sucked and the refrigerant compressed is as compression
Property fluid gas, but rotary closed type compressor 100 start when or under the low environment of ambient temperature operate when etc., deposit
In the feelings from the sucking of cooling cycle system side-wise rotary type hermetic type compressor 100 as the liquid refrigerant of incompressible fluid
Condition.If sucking the liquid refrigerant as incompressible fluid and being compressed, in the pressure meeting rapidly of the inside of discharge chambe 9
Rise, be accompanied by this, also can to by compressive load base bearing 5 and supplementary bearing 6 apply excessive load.
In the rotary closed type compressor 100 that rotary-piston 8 and blade 13 are independent individual, there is following function:
When pressure in discharge chambe 9 so promptly rises, can also it apply pressure to blade 13, thus to blade in discharge chambe 9
13 act on the power towards outside, and blade 13 is separated from rotary-piston 8, thus high-pressure side (the discharge side compression of discharge chambe 9
Room 9b) it is connected to low-pressure side (suction side discharge chambe 9a) and prevents pressure from rising.Thereby, it is possible to alleviate to be directed to base bearing 5 and pair
The bearing load of bearing 6, to prevent the damage of bearing portion.
However, can not be prevented in the rotary closed type compressor 100 that rotary-piston 8 and blade 13 are formed as one
Rapid pressure in discharge chambe 9 as described above rises, and thus can apply excessive load to bearing portion and lead to damage
Possibility is got higher.But as described above, by making the ratio between the length l of eccentric shaft 4c and the length L of crank axle 4, also
Even if i.e. l/L is 0.75 hereinafter, to also can in the case where compressing to the liquid refrigerant as incompressible fluid
It is enough further to obtain the sintering for preventing bearing portion, damage, and improve the effect of the reliability of rotary closed type compressor 100.
Claims (4)
1. a kind of rotary closed type compressor, is accommodated with motor and compression mechanism in closed container, which exists
The lower part of the motor, and linked by crank axle and the motor,
The compression mechanism has crank axle, which has: main shaft is fixed on the motor；Countershaft, central shaft with
The central axis of the main shaft is identical；And eccentric shaft, it is formed between the main shaft and the countershaft, and relative to the main shaft
Eccentricity of central axis,
The rotary closed type compressor is characterized in that,
When the length of the countershaft is set as L, and the length of the eccentric shaft is set as l, make 0.75 or less l/L.
2. rotary closed type compressor according to claim 1, which is characterized in that
The outer diameter of the countershaft be set to be the main shaft outer diameter hereinafter,
The resulting value of the eccentricity for subtracting the eccentric shaft from the center of the countershaft from the radial dimension of the eccentric shaft is
It is more than the radius size of the countershaft.
3. rotary closed type compressor according to claim 1 or 2, which is characterized in that
The compression mechanism has:
Rotary-piston, it is chimeric with the eccentric shaft；
Cylinder body, the rotary-piston are inserted into the cylindric space of the inside of the cylinder body, and the cylinder body is fixed on closed container
It is interior；And
Blade will be formed by by the medial surface of the cylinder body and the periphery of the rotary-piston rotated in the cylinder body
Discharge chambe is divided into suction side discharge chambe and discharge side discharge chambe,
The rotary-piston is formed as one with the blade.
4. rotary closed type compressor according to claim 1 or 2, which is characterized in that
The longitudinal modulus of elasticity of the material of the crank axle is 150000~220000N/mm2。
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2015/058946 WO2016151769A1 (en) | 2015-03-24 | 2015-03-24 | Hermetic rotary compressor |
| JPPCT/JP2015/058946 | 2015-03-24 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106014991A CN106014991A (en) | 2016-10-12 |
| CN106014991B true CN106014991B (en) | 2019-03-08 |
Family
ID=56541353
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201620133087.4U Withdrawn - After Issue CN205423162U (en) | 2015-03-24 | 2016-02-22 | Rotary hermetic compressor |
| CN201610096224.6A Active CN106014991B (en) | 2015-03-24 | 2016-02-22 | Rotary closed type compressor |
Family Applications Before (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201620133087.4U Withdrawn - After Issue CN205423162U (en) | 2015-03-24 | 2016-02-22 | Rotary hermetic compressor |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JPWO2016151769A1 (en) |
| CN (2) | CN205423162U (en) |
| CZ (1) | CZ307910B6 (en) |
| WO (1) | WO2016151769A1 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2016151769A1 (en) * | 2015-03-24 | 2016-09-29 | 三菱電機株式会社 | Hermetic rotary compressor |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102132046A (en) * | 2008-08-29 | 2011-07-20 | 东芝开利株式会社 | Enclosed compressor, two-cylinder rotary compressor, and refrigerating cycle apparatus |
Family Cites Families (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1623315A (en) * | 1927-04-05 | Assigetob to kinney | ||
| WO1995001509A1 (en) * | 1993-06-30 | 1995-01-12 | Empresa Brasileira De Compressores S/A. - Embraco | A fixed vane rotary compressor |
| JP2003262192A (en) * | 2002-03-07 | 2003-09-19 | Daikin Ind Ltd | Sealed compressor |
| DE102004054186B3 (en) * | 2004-11-10 | 2006-06-14 | Danfoss Compressors Gmbh | Crankshaft for compressor has shaft element with at least two telescopic sectors engaging in overlapping region |
| WO2009028633A1 (en) * | 2007-08-28 | 2009-03-05 | Toshiba Carrier Corporation | Multicylinder rotary type compressor, and refrigerating cycle apparatus |
| CN102748288A (en) * | 2011-04-22 | 2012-10-24 | 广东美芝制冷设备有限公司 | Rotary compressor using R290 refrigerant |
| WO2013061879A1 (en) * | 2011-10-24 | 2013-05-02 | 三菱電機株式会社 | Multi-cylinder rotary compressor |
| US9435337B2 (en) * | 2012-12-27 | 2016-09-06 | Panasonic Intellectual Property Management Co., Ltd. | Scroll compressor |
| KR102051094B1 (en) * | 2013-06-03 | 2019-12-02 | 엘지전자 주식회사 | Scroll compressor |
| WO2016151769A1 (en) * | 2015-03-24 | 2016-09-29 | 三菱電機株式会社 | Hermetic rotary compressor |
-
2015
- 2015-03-24 WO PCT/JP2015/058946 patent/WO2016151769A1/en active Application Filing
- 2015-03-24 JP JP2017507224A patent/JPWO2016151769A1/en active Pending
- 2015-03-24 CZ CZ2017-673A patent/CZ307910B6/en unknown
-
2016
- 2016-02-22 CN CN201620133087.4U patent/CN205423162U/en not_active Withdrawn - After Issue
- 2016-02-22 CN CN201610096224.6A patent/CN106014991B/en active Active
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102132046A (en) * | 2008-08-29 | 2011-07-20 | 东芝开利株式会社 | Enclosed compressor, two-cylinder rotary compressor, and refrigerating cycle apparatus |
Also Published As
| Publication number | Publication date |
|---|---|
| CZ307910B6 (en) | 2019-08-07 |
| CN106014991A (en) | 2016-10-12 |
| JPWO2016151769A1 (en) | 2017-09-14 |
| CZ2017673A3 (en) | 2017-11-22 |
| CN205423162U (en) | 2016-08-03 |
| WO2016151769A1 (en) | 2016-09-29 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US8366405B2 (en) | Screw compressor with capacity control slide valve | |
| US20130101454A1 (en) | Rotary compressor | |
| CN203783900U (en) | Airtight rotating compressor | |
| US9291164B2 (en) | Scroll compressor having a bush bearing provided on a boss of orbiting scroll | |
| JP2003269348A (en) | Rotary type compressor | |
| CN105190045B (en) | Scroll compressor | |
| CN106014991B (en) | Rotary closed type compressor | |
| CN107542646B (en) | Hermetic motor compressor | |
| JP5263139B2 (en) | Rotary compressor | |
| JP2005307764A (en) | Rotary compressor | |
| JP2015040472A (en) | Rotary compressor | |
| JP2008121481A (en) | Scroll fluid machine | |
| JP2013213477A (en) | Rotary compressor | |
| JP2009167976A (en) | Rotary fluid machine | |
| CN205172942U (en) | Rotary compressor | |
| CN208330731U (en) | Rotary compressor | |
| JP2010112174A (en) | Rotary compressor | |
| JP4726914B2 (en) | Scroll fluid machinery | |
| CN103591023B (en) | A kind of eccentric block type radial flexible compensating mechanism of rolling piston class fluid machinery | |
| JP2019056336A (en) | Scroll type fluid machine | |
| JP6019669B2 (en) | Rotary compressor | |
| JP2010265830A (en) | Hermetic type compressor and refrigeration cycle equipment | |
| CN105937493A (en) | Rotary compressor | |
| JP2013139723A (en) | Rotary compressor | |
| JP6464583B2 (en) | Rotary 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 | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |