CN104675702A - Rotary compressor - Google Patents
Rotary compressor Download PDFInfo
- Publication number
- CN104675702A CN104675702A CN201410708297.7A CN201410708297A CN104675702A CN 104675702 A CN104675702 A CN 104675702A CN 201410708297 A CN201410708297 A CN 201410708297A CN 104675702 A CN104675702 A CN 104675702A
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- China
- Prior art keywords
- blade
- rotary
- cylindrical shell
- blade groove
- piston
- 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.)
- Pending
Links
- 230000006835 compression Effects 0.000 claims description 22
- 238000007906 compression Methods 0.000 claims description 22
- 238000005057 refrigeration Methods 0.000 claims description 17
- 238000003825 pressing Methods 0.000 claims description 9
- 230000002093 peripheral effect Effects 0.000 claims description 4
- 239000003507 refrigerant Substances 0.000 abstract description 5
- 239000003795 chemical substances by application Substances 0.000 description 16
- 239000002184 metal Substances 0.000 description 9
- 230000003584 silencer Effects 0.000 description 6
- 230000000052 comparative effect Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 230000009471 action Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- BGOFCVIGEYGEOF-UJPOAAIJSA-N helicin Chemical compound O[C@@H]1[C@@H](O)[C@H](O)[C@@H](CO)O[C@H]1OC1=CC=CC=C1C=O BGOFCVIGEYGEOF-UJPOAAIJSA-N 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
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
- F04C18/34—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 the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—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 the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
-
- 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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
-
- 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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/06—Silencing
-
- 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
- F04C2250/00—Geometry
- F04C2250/30—Geometry of the stator
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The invention provides a rotary compressor. A channel, namely a groove (72) used for introducing discharge pressure to the indraft side of a blade (12) is formed in a side wall (7h) close to the indraft side of a blade groove (7g) of a cylinder body (7), so that the difference between the indraft side pressure load and the discharge side pressure load generated on the two sides of the blade (12) is reduced, the following property of the blade (12) relative to a rotary piston (11) can be improved, the noise can be inhibited and the leak of a refrigerant from the high-pressure side to the low-pressure side can be reduced.
Description
Technical field
The present invention relates to the rotary compressor being applied to the changes in temperature equipment such as air conditioner.
Background technique
The rotary-piston of rotary compressor is arranged to movable with the state of the internal face linear contact lay with the central space portion in cylindrical shell, and described rotary-piston is inlaid in the eccentric axial portion of bent axle.In addition, this rotary-piston also becomes the state abutted with the blade in the blade groove being disposed in cylindrical shell.And the space that the gap between cylindrical shell and rotary-piston is formed is divided into pressing chamber and suction chamber by blade.
In this rotary compressor, when rotary-piston eccentric rotary (revolution), continuously and a series of suction/compression stroke of stroke to the stroke transition successively of compression refrigerant gas of repeatedly carrying out from sucking refrigerant gas.By the gas after compressing after being released in seal container, be admitted to refrigerating circuit from discharge tube.
In the compression section of rotary compressor, till the phase place of the eccentric axial portion of bent axle is 180 °, blade bears the pressure of the back pressure chamber from blade groove base portion, thus the racking that produces of differential pressure inside and outside reason pressing chamber and follow rotary-piston towards lower dead center and move, phase place more than 180 °, blade bears the load from rotary-piston along with the rotation of bent axle and moves (such as with reference to patent documentation 1) to top dead center.
Patent documentation 1: Japanese Unexamined Patent Publication 11-166495 publication (paragraph [0003], [0004], Fig. 3)
But, in rotary compressor, there is following problem: at blade to (phase place of the eccentric axial portion of bent axle became before 180 °) during lower dead center movement, if the slip resistance between blade and blade groove becomes large, then blade becomes and does not follow rotary-piston, blade and rotary-piston leave, then produce noise when contacting, and refrigeration agent from pressing chamber side (high pressure side) to suction chamber side (low voltage side) leaks and performance reduction.
In the past, by improving the problem of the slip resistance between above-mentioned this blade and blade groove to sidewall portion supply refrigerator oil (lubricant oil) of blade groove.But the factor producing slip resistance is the difference of the pressure loading of suction side and the discharge side produced in blade both sides.Be not conceived to this in the past, not suppress the generation of slip resistance itself.
Summary of the invention
The present invention proposes to solve problem as described above, its object is to, and makes it possible to the difference of the pressure loading reducing suction side and the discharge side produced in blade both sides, thus can suppress noise and reduce the leakage of refrigeration agent from high side to low side.
Rotary compressor involved in the present invention possesses compression mechanical part and motor part in seal container, compression mechanism portion compresses refrigeration agent, above-mentioned motor part forms the driving source of compression mechanical part, and compression mechanical part possesses: bent axle, and above-mentioned bent axle is by motor part rotary actuation; Rotary-piston, above-mentioned rotary-piston is chimeric with the eccentric axial portion of bent axle, and rotates together with this eccentric axial portion; Cylindrical shell, the inner peripheral surface of the storage rotary-piston of above-mentioned cylindrical shell is formed as cylindric, and the central shaft of inner peripheral surface is disposed on the central axis of the main shaft part of bent axle; Two bearings, the both ends of the surface of above-mentioned two bearing closed cylinders; Blade groove, above-mentioned blade groove is formed at cylindrical shell; And blade, above-mentioned blade reciprocatingly slides in compression section in blade groove, above-mentioned blade is along the outer circumferential face of rotary-piston, and the space formed by cylindrical shell and two bearings is divided into suction chamber and pressing chamber, at the sidewall by suction side of the blade groove of cylindrical shell, be provided with the path of the suction side introducing head pressure to blade.
According to rotary compressor of the present invention, the sidewall by suction side due to the blade groove at cylindrical shell is provided with the path of the suction side introducing head pressure to blade, therefore, it is possible to reduce the difference of the pressure loading of suction side and the discharge side produced in the both sides of blade.Therefore, blade improves relative to the tracing ability of rotary-piston, and blade and rotary-piston can not leave, and can suppress noise and reduce the leakage of refrigeration agent from high side to low side.
Accompanying drawing explanation
Fig. 1 is the integrally-built longitudinal section of the rotary compressor illustrated involved by embodiments of the present invention 1.
Fig. 2 is the details drawing of the major component of rotary compressor involved by embodiments of the present invention 1.
Fig. 3 is the schematic diagram of the power produced in blade side in the comparative example that rotary compressor is shown.
Fig. 4 is the schematic diagram of the power in blade side generation of the rotary compressor illustrated involved by embodiments of the present invention 1.
Fig. 5 is and comparative example compares and the chart of the relation between the phase place of the bent axle of the rotary compressor involved by embodiments of the present invention 1 and blade side load is shown.
Fig. 6 is the details drawing of the major component of rotary compressor involved by embodiments of the present invention 2.
Label declaration
1: seal container; 1a: discharge tube; 2: accumulator; 3: motor part; 4: compression mechanical part; 5: upper bearing (metal); 5a: tap hole; 5b: expulsion valve; 6: exhaust silencer; 6a: tap hole; 7: cylindrical shell; 7a: groove (introducing the path of head pressure); 7b: back pressure chamber; 7c: suction port; 7d: exhaust port; 7e: suck space; 7f: discharge space; 7g: blade groove; 7h: the sidewall of suction side; 8: lower bearing; 9: suction pipe; 10: bent axle; 10a: eccentric axial portion; 10b: main shaft part; 10c: countershaft portion; 11: rotary-piston; 12: blade; 13: leaf spring; 14: otch (introducing the path of head pressure); 31: stator; 32: rotor; 100: rotary compressor.
Embodiment
Mode of execution 1.
Below, according to illustrated embodiment, the present invention will be described.
Fig. 1 is the integrally-built longitudinal section of the rotary compressor illustrated involved by embodiments of the present invention 1.Fig. 2 is the details drawing of the major component of rotary compressor involved by embodiments of the present invention 1.
As shown in Figure 1, the rotary compressor 100 involved by embodiments of the present invention 1 is accommodated with motor part 3 and compression mechanical part 4 in seal container 1.In addition, the bottom in seal container 1 contains refrigerator oil (not shown).Refrigerator oil mainly lubricates the slide part of compression mechanical part 4.Be connected with the suction pipe 9 be communicated with accumulator 2 at seal container 1, obtain refrigeration agent from accumulator 2.In addition, be connected with discharge tube 1a on the top of seal container 1, thus the refrigeration agent after compression is released.
Motor part 3, by being fixed on the stator 31 of seal container 1 and forming with the rotor 32 of bent axle 10 shrink fit, supplies electric power via not shown airtight terminal to this motor part 3 from outside and drives it.In addition, motor part 3 and compression mechanical part 4 link via bent axle 10.In addition, be formed with the oil-sucking hole of direction, the end opening to seal container 1 at the axis central part of bent axle 10, in oil-sucking hole, be provided with spiral helicine centrifugal pump, thus the refrigerator oil of the bottom accumulating in seal container 1 can be drawn and be supplied to slide part.
As shown in Figure 1 and Figure 2, compression mechanical part 4 possesses: cylindrical shell 7; Two bearings that is upper bearing (metal) 5 and lower bearing 8; Bent axle 10; Rotary-piston 11; Exhaust silencer 6; And blade 12.
This is described in further detail.Cylindrical shell 7 periphery being formed with pressing chamber in inside is formed as overlooking rounded, and has in inside and overlook rounded space that is cylindrical shell room.The axial both ends open of cylindrical shell room.Observe from the side, cylindrical shell 7 has the axial height of regulation.
As shown in Figure 2, at cylindrical shell 7, through being provided with is communicated with and the blade groove 7g extended along radial direction with the space of its circle that is cylindrical shell room vertically.Blade 12 embeds blade groove 7g sliding freely.In addition, at blade groove 7g by the sidewall 7h of suction side, introduce path that is the groove 7a of head pressure in its outer circumferential side suction side be formed to blade 12.In addition, be provided with the back pressure chamber 7b guiding head pressure to its base portion at blade groove 7g, groove 7a is communicated with back pressure chamber 7b.Thus, the wall of blade groove 7g both sides is formed as left-right asymmetry shape.Back pressure chamber 7b has and overlooks rounded space.
The through suction port 7c be provided with for passing through from the suction refrigeration agent of suction pipe 9 from the outer circumferential face of cylindrical shell 7 towards cylindrical shell room.
In addition, cylindrical shell 7 is provided with exhaust port 7d, this exhaust port 7d is formed by otch near the edge part of the circle by conglobate for shape space that is cylindrical shell room.
Rotary-piston 11 embeds the eccentric axial portion 10a of bent axle 10, and the indoor eccentric rotary (revolution) of cylindrical shell.Rotary-piston 11 is ring-type, and the inner circumferential of rotary-piston 11 is entrenched in the eccentric axial portion 10a of bent axle 10 sliding freely.
The shape of blade 12 is the cuboid of flat (length that the Thickness Ratio of circumferential direction is radial and axial is little).
Blade 12 is incorporated in the blade groove 7g of cylindrical shell 7, and is pushed on rotary-piston 11 by the leaf spring 13 being arranged at back pressure chamber 7b.In the running of rotary compressor 100, blade 12 is pushed on rotary-piston 11 by the racking (back pressure) produced by the differential pressure inside and outside pressing chamber and follows rotary-piston 11.Therefore, the object that blade 12 to be mainly pushed on rotary-piston 11 in order to when compressor start (when the pressure in seal container 1 and between cylindrical shell room does not exist poor state) by leaf spring 13 uses.
Upper bearing (metal) 5 is entrenched in the main shaft part 10b of bent axle 10 sliding freely, and the square end face (motor part 3 side) comprising the cylindrical shell room of blade groove 7g of closed cylinder 7.Upper bearing (metal) 5 is formed as observing from the side in falling T-shaped.
In addition, be positioned at the position of same position at upper bearing (metal) 5 and at the exhaust port 7d of top view and cylindrical shell 7, be provided with tap hole 5a, at tap hole 5a, expulsion valve 5b be installed.
Expulsion valve 5b bears the pressure in the pressure of cylindrical shell indoor and seal container 1, and is pushed on exhaust port 7d and closes tap hole 5a when pressure in the pressure ratio seal container 1 of cylindrical shell indoor is low.In addition, expulsion valve 5b becomes than upwardly-directed being boosted by the pressure of cylindrical shell indoor during pressure height in seal container 1 at the pressure of cylindrical shell indoor and opens wide tap hole 5a, thus by the refrigeration agent after compression to the outdoor guiding of cylindrical shell.
In addition, at upper bearing (metal) 5 and thereon side is provided with exhaust silencer 6, utilizes exhaust silencer 6 and upper bearing (metal) 5 to form silence space.
The refrigerant gas of the high temp/high pressure of discharging from the tap hole 5a of upper bearing (metal) 5 temporarily enters silence space, is released in seal container 1 afterwards from the tap hole 6a of exhaust silencer 6.
Lower bearing 8 is entrenched in the countershaft portion 10c of bent axle 10 sliding freely, and the opposing party's end face (refrigerator oil side) comprising the cylindrical shell room of blade groove 7g of closed cylinder 7.Lower bearing 8 is formed as observing in T-shaped from the side.
Blade 12 has the function being divided into cylindrical shell room and sucking space 7e and discharge space 7f.
Next, the action of the rotary compressor 100 of embodiments of the present invention 1 is described.
In the rotary compressor 100 involved by embodiments of the present invention 1, after via suction pipe 9 and suction port 7c the refrigeration agent of accumulator 2 being directed into pressing chamber, drive motor portion 3 and make bent axle 10 eccentric rotary.Thus, the refrigeration agent of cylindrical shell indoor is compressed.Be discharged in silence space by the refrigeration agent after compressing from the tap hole 5a of upper bearing (metal) 5 cylindrical shell is indoor, be then discharged in seal container 1 via the tap hole 6a of exhaust silencer 6.The refrigeration agent be discharged is released from discharge tube 1a after the gap by motor part 3.
In refrigerant compression, be divided into by cylindrical shell 7, rotary-piston 11 and blade 12 in pressing chamber and suck space 7e and discharge space 7f.Due to above-mentioned differential pressure, be applied with load at blade 12 and the blade groove 7g of cylindrical shell 7, thus produce slip resistance.
But, the rotary compressor 100 of embodiments of the present invention 1 is provided with head pressure introducing path that is groove 7a at the sidewall 7h by suction side of blade groove 7g, therefore, it is possible to reduce the difference of the pressure loading of suction side and the discharge side produced in blade 12 both sides, the slip resistance of blade 12 can be reduced.Therefore, blade 12 improves relative to the tracing ability of rotary-piston 11, and blade 12 and rotary-piston 11 can not leave, and can suppress noise and reduce the leakage of refrigeration agent from high side to low side.
Fig. 3 is the schematic diagram of the power produced in blade side in the comparative example that rotary compressor is shown.Fig. 4 is the schematic diagram of the power in blade side generation of the rotary compressor illustrated involved by embodiments of the present invention 1.
Namely, Fig. 3 illustrates the distribution of working as when the sidewall 7h by suction side of blade groove 7g does not have head pressure introducing path that is groove 7a, in compressor operation blade side load, and Fig. 4 illustrates the distribution of when having head pressure introducing path that is groove 7a, in compressor operation blade side load.In Fig. 3 and Fig. 4, Pd is head pressure, Ps is suction pressure, Pm is pressure in compression, F1, f1 are the distributed loads produced by Pd, and F2 is the distributed load produced by Pd ~ Pm, and f2 is the distributed load produced by Pd ~ Ps, F3 is the distributed load produced by Pm, and f3 is the distributed load produced by Ps.
From Fig. 3 and Fig. 4, when having head pressure introducing path that is groove 7a, cause because of groove 7a the distributed load f2 (distributed load of the scope shown in the A in Fig. 4) produced by Pd ~ Ps to become large, deduct the aggregate value (f1+f2+f3) of distributed load f that is Σ f from the aggregate value (F1+F2+F3) of distributed load F that is Σ F and (Σ F-Σ f) minimizing of obtain.Therefore, the slip resistance between blade 12 and blade groove 7g diminishes, and blade 12 improves relative to the tracing ability of rotary-piston 11, and blade 12 can not leave from rotary-piston 11.As a result, do not produce noise, and refrigeration agent also disappears from the leakage of high side to low side thus can maintain performance.
Fig. 5 is and comparative example compares and the chart of the relation between the phase place of the bent axle of the rotary compressor involved by embodiments of the present invention 1 and blade side load is shown, the relation between the phase place of bent axle 10 in a situation with head pressure introducing path that is groove 7a and the b situation without head pressure introducing path that is groove 7a and blade side load is shown.As the condition used in the calculation, refrigeration agent is CO
2refrigeration agent.Operating condition is: head pressure 8.3MPa, suction pressure 4.7MPa, rotating speed 40rps, and is the actual condition of carrying out using when rotary compressor being applied to water heater.As can be seen from Figure 5, when having head pressure introducing path that is groove 7a, no matter when which kind of angular orientation bent axle 10 be in, blade side load all reduces.
Mode of execution 2.
Fig. 6 is the details drawing of the major component of rotary compressor involved by embodiments of the present invention 2, marks identical label in the drawings to the funtion part identical with above-mentioned mode of execution 1.
In the rotary compressor involved by embodiments of the present invention 2, utilize otch 14 to form the head pressure introducing path of sidewall 7h by suction side of blade groove 7g, this otch 14 to be formed and axis along cylindrical shell 7 is through continuously from back pressure chamber 7b.Thus, herein, the wall of blade groove 7g both sides is also in left-right asymmetry shape.In addition structure is identical with the structure of above-mentioned mode of execution 1.
In the rotary compressor involved by embodiments of the present invention 2, to be formed continuously from back pressure chamber 7b owing to utilizing and to form the head pressure introducing path of the sidewall 7h by suction side of blade groove 7g along the otch 14 that the axis of cylindrical shell 7 is through, therefore processing becomes easy, can realize the improvement of processability.
In addition, here, be illustrated for situation the present invention being used for vertical rotary compressor, but also can be applied to horizontal rotary compressor from needless to say the present invention.
Claims (3)
1. a rotary compressor, is characterized in that,
Described rotary compressor possesses compression mechanical part and motor part in seal container, and described compression mechanical part compresses refrigeration agent, and described motor part forms the driving source of described compression mechanical part,
Described compression mechanical part possesses:
Bent axle, described bent axle is by described motor part rotary actuation;
Rotary-piston, described rotary-piston is chimeric with the eccentric axial portion of described bent axle, and rotates together with this eccentric axial portion;
Cylindrical shell, the inner peripheral surface of the described rotary-piston of storage of described cylindrical shell is formed as cylindric, and the central shaft of described inner peripheral surface is disposed on the central axis of the main shaft part of described bent axle;
Two bearings, the both ends of the surface of described cylindrical shell closed by described two bearings;
Blade groove, described blade groove is formed at described cylindrical shell; And
Blade, described blade reciprocatingly slides in compression section in described blade groove, and the space formed by described cylindrical shell and described two bearings along the outer circumferential face of described rotary-piston, and is divided into suction chamber and pressing chamber by described blade,
At the sidewall by suction side of the described blade groove of described cylindrical shell, be provided with the path of the suction side introducing head pressure to described blade.
2. rotary compressor according to claim 1, is characterized in that,
Described blade groove has the back pressure chamber of the base portion guiding head pressure to described blade groove,
Described path be formed at described blade groove by the sidewall of described suction side and the groove be communicated with described back pressure chamber.
3. rotary compressor according to claim 1, is characterized in that,
Described blade groove has the back pressure chamber of the base portion guiding head pressure to described blade groove,
Described path to be formed continuously and along the through otch of the axis of cylindrical shell from described back pressure chamber at the sidewall by described suction side of described blade groove.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013-246426 | 2013-11-28 | ||
| JP2013246426A JP5991958B2 (en) | 2013-11-28 | 2013-11-28 | Rotary compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN104675702A true CN104675702A (en) | 2015-06-03 |
Family
ID=53259182
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410708297.7A Pending CN104675702A (en) | 2013-11-28 | 2014-11-28 | Rotary compressor |
| CN201420735289.7U Expired - Fee Related CN204357709U (en) | 2013-11-28 | 2014-11-28 | Rotary compressor |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420735289.7U Expired - Fee Related CN204357709U (en) | 2013-11-28 | 2014-11-28 | Rotary compressor |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP5991958B2 (en) |
| CN (2) | CN104675702A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106438360A (en) * | 2015-08-11 | 2017-02-22 | 台州阳光电机泵业有限公司 | Rotary air compressor head |
| CN109416045A (en) * | 2016-07-08 | 2019-03-01 | 雀巢产品技术援助有限公司 | Rotary Compressor device |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPWO2017061014A1 (en) * | 2015-10-08 | 2018-04-26 | 三菱電機株式会社 | Rotary compressor |
| CN106930943A (en) * | 2015-12-29 | 2017-07-07 | 珠海凌达压缩机有限公司 | Compressor, pump body subassembly and cylinder thereof |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH08284857A (en) * | 1995-04-17 | 1996-10-29 | Hitachi Ltd | Hermetic rotary compressor |
| CN1233716A (en) * | 1998-04-27 | 1999-11-03 | 三星电子株式会社 | Hermetic Rotary Compressors |
| WO2004065794A1 (en) * | 2003-01-20 | 2004-08-05 | Matsushita Electric Industrial Co., Ltd. | Rotary compressor |
| CN101608620A (en) * | 2008-06-17 | 2009-12-23 | 三菱电机株式会社 | Rotary compressor |
| JP2010275974A (en) * | 2009-05-29 | 2010-12-09 | Daikin Ind Ltd | Rotary compressor |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6132594U (en) * | 1984-07-31 | 1986-02-27 | 三菱重工業株式会社 | rotary compressor |
| JPS6186590U (en) * | 1984-11-13 | 1986-06-06 | ||
| JPH0633781B2 (en) * | 1985-10-24 | 1994-05-02 | 日本電装株式会社 | Rolling piston type rotary machine |
| US4629403A (en) * | 1985-10-25 | 1986-12-16 | Tecumseh Products Company | Rotary compressor with vane slot pressure groove |
| JPH07217569A (en) * | 1994-02-03 | 1995-08-15 | Hitachi Ltd | Rotary compressor |
| KR100816656B1 (en) * | 2006-12-27 | 2008-03-26 | 엘지전자 주식회사 | Variable displacement rotary compressors |
| WO2013080519A1 (en) * | 2011-11-28 | 2013-06-06 | パナソニック株式会社 | Rotary compressor |
-
2013
- 2013-11-28 JP JP2013246426A patent/JP5991958B2/en active Active
-
2014
- 2014-11-28 CN CN201410708297.7A patent/CN104675702A/en active Pending
- 2014-11-28 CN CN201420735289.7U patent/CN204357709U/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH08284857A (en) * | 1995-04-17 | 1996-10-29 | Hitachi Ltd | Hermetic rotary compressor |
| CN1233716A (en) * | 1998-04-27 | 1999-11-03 | 三星电子株式会社 | Hermetic Rotary Compressors |
| WO2004065794A1 (en) * | 2003-01-20 | 2004-08-05 | Matsushita Electric Industrial Co., Ltd. | Rotary compressor |
| CN101608620A (en) * | 2008-06-17 | 2009-12-23 | 三菱电机株式会社 | Rotary compressor |
| JP2010275974A (en) * | 2009-05-29 | 2010-12-09 | Daikin Ind Ltd | Rotary compressor |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106438360A (en) * | 2015-08-11 | 2017-02-22 | 台州阳光电机泵业有限公司 | Rotary air compressor head |
| CN109416045A (en) * | 2016-07-08 | 2019-03-01 | 雀巢产品技术援助有限公司 | Rotary Compressor device |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2015105574A (en) | 2015-06-08 |
| CN204357709U (en) | 2015-05-27 |
| JP5991958B2 (en) | 2016-09-14 |
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