CN102410221B - Double-cylinder rotary compressor - Google Patents
Double-cylinder rotary compressor Download PDFInfo
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- CN102410221B CN102410221B CN201110401530.3A CN201110401530A CN102410221B CN 102410221 B CN102410221 B CN 102410221B CN 201110401530 A CN201110401530 A CN 201110401530A CN 102410221 B CN102410221 B CN 102410221B
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- air cylinder
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- 239000007788 liquid Substances 0.000 claims abstract description 58
- 230000004323 axial length Effects 0.000 claims description 3
- 239000012530 fluid Substances 0.000 abstract description 9
- 230000010349 pulsation Effects 0.000 abstract 1
- 230000006835 compression Effects 0.000 description 28
- 238000007906 compression Methods 0.000 description 28
- 239000007789 gas Substances 0.000 description 24
- 238000005096 rolling process Methods 0.000 description 12
- 239000003921 oil Substances 0.000 description 4
- 238000000034 method Methods 0.000 description 3
- 230000004888 barrier function Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 1
- 230000003044 adaptive effect Effects 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 229910052799 carbon Inorganic materials 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 239000010779 crude oil Substances 0.000 description 1
- 230000007123 defense Effects 0.000 description 1
- 208000002925 dental caries Diseases 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 230000007257 malfunction Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 230000006641 stabilisation Effects 0.000 description 1
- 238000011105 stabilization Methods 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 230000000007 visual effect Effects 0.000 description 1
- 239000002699 waste material Substances 0.000 description 1
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- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The invention relates to a double-cylinder rotary compressor. The rotary compressor comprises an outer air cylinder, an ellipse rotor, and an inner air cylinder which are concentrically installed, wherein an inner short shaft of the ellipse rotor is equal to the outer diameter of the inner air cylinder, and an outer long shaft of the ellipse rotor is equal to the inner diameter of the outer air cylinder; the external surface of the ellipse rotor and the inner wall surface of the outer air cylinder are tangent at any kinetic instant, the internal surface of the ellipse rotor and the outer side wall of the inner air cylinder are tangent, the inner air cylinder and the outer air cylinder are respectively provided with two pairs of slip sheets; the inner air cylinder is provided with two pairs of air inlet cavities and exhaust cavities; crescent volume is divided into two pairs of air inlet (liquid) cavities and compressing, exhaust (liquid) cavities by the inner air cylinder and the outer air cylinder so as to form four pairs of corresponding working volumes; and the inner air cylinder and the outer air cylinder are respectively provided with four pairs of air inlet ports and exhaust (liquid) ports. The double-cylinder rotary compressor provided by the invention has the advantages of high efficiency, no vibration, small volume, uniform stressing of a main shaft, small gas pulsation, simple structure, is stable in operation, and eliminates unbalanced force caused by rotation; and the double-cylinder rotary compressor can be used in different gas compressors, fluid pumps and vacuum pumps.
Description
Technical field
The present invention relates to a kind of rotary compressor, be specifically related to a kind of compression that can be used for various gases, the conveying of fluid and oil, gas mix the twin-tub rotation-type compressor of defeated and field of vacuum.
Background technique
Compressor and fluid pump are a kind of universal machines that is widely used in the every field such as machinery, chemical industry, communications and transportation, air conditioner refrigerating and national defense construction.In field of Refrigeration and Air-conditioning, compressor is important heart equipment especially; In oilfield exploitation, it is the technical barrier of oil field in mixed defeated that the heterogeneous long distance of crude oil, association G&W is carried, especially in mountain area, desert and marine oil field oil-gas mixed delivery pump study hotspot especially, oil, gas mixed defeated not only can cost saving, simplification of flowsheet and raising tar productivity, also can greatly reduce due to the burn carbon emission amount that produces and reclaim associated gas of associated gas, save the energy, mixed defeated visual plant is oil-gas mixed delivery pump.
What in above-mentioned field, use at present is that rolling piston compressor tool and rotor compression machinery all have a selenodont active chamber, by slide plate, selenodont active chamber is isolated into air-inlet cavity and compression chamber, the rotation of rotor or rolling piston makes air-inlet cavity and compression chamber volume produce variation, realizes air-breathing (liquid) and the exhaust (liquid) of compressed machinery.But, this traditional rolling piston compressor tool and the insurmountable problem of rotor compression machinery are: the first often turns only has a volume in the compression of carrying out gas, efficiency is low, cause the unstable of the waste of the energy and electrical network, change in torque in the another one operation cycle is large, in order to make rotating speed even, need a larger flywheel balancing, increase manufacturing expense; Its two be a work cycle exhaust once, in pipeline, formed larger gas, caused the vibration of pipeline, affected mechanical stability and reliability; It three is rotor geometrical center and the rotating center decentraction of compressor with rolling rotor, there is a throw of eccentric, the machining error of crank throw can run up on the sealing surface of rotor and cylinder, not only affect the sealing of outer surface and the cylinder inner wall face of rotor, reduce volumetric efficiency, centrifugal inertia force also can cause the vibration of machine, simultaneously the processing technology more complicated of crank shaft.
Summary of the invention
The object of the invention is the shortcoming for traditional rolling piston compressor tool and rotor compression machinery, provide that a kind of efficiency that can effectively solve traditional rolling piston compressor and rotor-type compressor is low, gas is large, the unsettled twin-tub rotation-type compressor of machine run.
For achieving the above object, the technical solution used in the present invention is: comprise the outside cylinder, elliptic rotor, inside cylinder and the cylinder head that are arranged on one heart on bracket, main shaft is arranged on the geometrical center of elliptic rotor, the external diameter of elliptic rotor major axis equals the internal diameter of outside cylinder, the internal diameter of elliptic rotor minor axis equals the external diameter of inside cylinder, on outside cylinder and inside cylinder, be separately installed with two outside cylinder slide plates that are oppositely arranged and two inside cylinder slide plates that are oppositely arranged, one end of two outside cylinder slide plates and the outer surface of elliptic rotor are tangent, the other end contacts with outside cylinder sliding blade spring, outside cylinder internal face, the outer surface of elliptic rotor and two outside cylinder slide plates form four outer swept volumes, and order offers outside cylinder air inlet (liquid) mouth and outside cylinder exhaust (liquid) mouthful in the upper both sides in two outside cylinder slide plates that are oppositely arranged of outside cylinder,
Described one end of two inside cylinder slide plates and the internal surface of elliptic rotor are tangent, the other end contacts with inside cylinder sliding blade spring, inside cylinder outer wall, the internal surface of elliptic rotor and two inside cylinder slide plates form four interior swept volumes, the both sides order that is positioned at two inside cylinder slide plates that are oppositely arranged on inside cylinder offers inside cylinder air inlet (liquid) mouth and inside cylinder exhaust (liquid) mouthful, wherein inside cylinder air inlet (liquid) mouthful is connected with inside cylinder air inlet (liquid) chamber respectively, inside cylinder exhaust (liquid) mouthful is connected with inside cylinder exhaust (liquid) chamber respectively.
On described outside cylinder, inside cylinder, relatively offer two for outside cylinder vane slot and the inside cylinder vane slot of outside cylinder slide plate, inside cylinder slide plate are installed.
The axial length of described elliptic rotor, outside cylinder, inside cylinder, outside cylinder slide plate and inside cylinder slide plate equates.
The outside of described cylinder head is also provided with exhausting buffer.
On described inside cylinder exhaust (liquid) mouth and outside cylinder exhaust (liquid) mouth, inside cylinder outlet valve and outside cylinder outlet valve are all installed.
The present invention arranges inside and outside two cylinders, traditional rolling rotor and rotary compressor one are turned to a work cycle to be changed one into and turns inside and outside cylinder and be respectively two work cycle, therefore efficiency is high, namely turn middle one and have four pairs of swept volumes in air inlet (liquid) and compression simultaneously, have four exhaust processes, its air displacement increases nearly four times compared with the compressor with rolling rotor of same volume and rotary compressor; The asynchronism(-nization) step that interior outside cylinder starts compression differs 90 °, so live axle is stressed even, gas is little, and stabilization of speed need not arrange flywheel; Because inside and outside cylinder all arranges outlet valve, in the time that the pressure of gas in swept volume (fluid) reaches the pressure of system needs, gas (fluid) is discharged by the relief opening being arranged on inside and outside cylinder, avoid insufficient compression and the overcompression phenomenon in gas compressor, save power consumption, also avoided the phenomenon of fluid pressurized in active chamber, so can a tractor serves several purposes, both can be used as the compressor of various gases, can be used as again fluid pump; Be exactly the geometrical center of rotor due to the rotating center of rotor in addition, when work, without unbalanced inertial force, rotating speed is high, good stability, and volume is less, has saved manufacturing expense; Secondly, main working surface is circle, and technique is simple, good airproof performance, and fretting wear is little, volumetric efficiency height and saving power consumption.
Brief description of the drawings
Below in conjunction with accompanying drawing, the present invention is further described.
Fig. 1 is that end-face structure of the present invention shows intention.
Fig. 2 is cross-sectional view of the present invention.
Fig. 3 is fundamental diagram of the present invention.
Embodiment
Referring to Fig. 1,2, the present invention includes the outside cylinder 6, elliptic rotor 5, inside cylinder 4 and the cylinder head 21 that are arranged on one heart on bracket 27, in cylinder head 21 outsides, exhausting buffer 25 is installed, outside cylinder 6 and inside cylinder 4 are fixed, and main shaft 22 is arranged on the geometrical center of elliptic rotor 5 by bearing 23, the external diameter of elliptic rotor 5 major axis equals the internal diameter of outside cylinder 6, the internal diameter of elliptic rotor 5 minor axises equals the external diameter of inside cylinder 4, when elliptic rotor 5 is in the time that the rotating center O of oneself drives axle center 15 to rotate, the internal face of the outer surface of elliptic rotor 5 and outside cylinder 6 is tangent all the time, the outer wall of the internal surface of elliptic rotor 5 and inside cylinder 4 is tangent all the time, offer two for outside cylinder slide plate 1 is installed at outside cylinder 6 with relative on inside cylinder 4, 9, inside cylinder slide plate 13, 18 outside cylinder vane slot 34, 38 and inside cylinder vane slot 37, 41, and elliptic rotor 5, outside cylinder 6, inside cylinder 4, outside cylinder slide plate 1, 9 and inside cylinder slide plate 13, 18 axial length equates, one end of two outside cylinder slide plates 1,9 and the outer surface of elliptic rotor 5 are tangent, the other end contacts with outside cylinder sliding blade spring 20,8, the outer surface of outside cylinder 6 internal faces, elliptic rotor 5 and two outside cylinder slide plates 1,9 form four outer swept volumes, and the both sides order that is positioned at two outside cylinder slide plates that are oppositely arranged 1,9 on outside cylinder 6 offers outside cylinder air inlet (liquid) mouthfuls 2,10 and outside cylinder exhaust (liquid) mouth 19,7,
Two described inside cylinder slide plates 13, the internal surface of one end of 18 and elliptic rotor 5 is tangent, the other end and inside cylinder sliding blade spring 14, 16 contacts, inside cylinder 4 outer wall, the internal surface of elliptic rotor 5 and two inside cylinder slide plates 13, 18 form four interior swept volumes, on inside cylinder 4, be positioned at two inside cylinder slide plates 13 that are oppositely arranged, 18 both sides vertically order offer inside cylinder air inlet (liquid) mouth 12, 3 and inside cylinder exhaust (liquid) mouthfuls 11, 17, wherein inside cylinder air inlet (liquid) mouth 12, 3 are connected with inside cylinder air inlet (liquid) chamber respectively, inside cylinder exhaust (liquid) mouth 11, 17 are connected with inside cylinder exhaust (liquid) chamber respectively, described inside cylinder exhaust (liquid) mouth 11, 17 and outside cylinder exhaust (liquid) mouthfuls 19, inside cylinder outlet valve 40 is all installed on 7, 36 and outside cylinder outlet valve 35, 39.
From Fig. 1 and Fig. 2, inside cylinder inner ring is divided into two inside cylinder air inlets (liquid) chamber 31 and two inside cylinder exhausts (liquid) chamber 32,33 by inside cylinder 4 and cylinder head 21, gas (liquid) body enters inside cylinder air inlet (liquid) chamber 31 by axial inside cylinder air inlet (liquid) mouth 3,12, and compressed gas or liquid enter in inside cylinder exhaust (liquid) chamber 32,33 by inside cylinder exhaust (liquid) mouth 11,17, finally enter system by axial inside cylinder exhaust (liquid) mouth 11,17.
Shown in Figure 3, when elliptic rotor 5 under the driving of main shaft 22 in the time that rotating center O rotates, when β=0 °, two corresponding compression chambers of outer active chamber have completed a work cycle, exhaust just finishes, and two corresponding admission space V
sreach maximum, and there are two corresponding admission spaces in interior active chamber simultaneously
with two corresponding compression work volumes
along with corner, β constantly increases, and outer active chamber gas (liquid) is entered by air inlet (liquid) mouth 1 and 10 respectively, meanwhile compression chamber V
dconstantly dwindle, realize compression, pressure improves.And interior active chamber air-inlet cavity
constantly expand meanwhile compression chamber
constantly dwindle interior active chamber
pressure reach system need pressure time, compression chamber
in gas (liquid) discharge by exhaust (liquid) mouthfuls 11 and 17, at this moment the corresponding angle of the corner of rotor is just exhaust (liquid) angle of interior active chamber.In the time of β=90 °, two corresponding compression chambers of interior active chamber
completed a work cycle, exhaust just finishes, and two corresponding admission spaces
reach maximum; And there are two corresponding admission space V in outer active chamber simultaneously
swith two corresponding compression work volume V
d, along with corner, β constantly increases, and outer active chamber gas (liquid) continues respectively to be entered by air inlet (liquid) mouth 1 and 10, meanwhile compression chamber V
dconstantly dwindle, realization compression, pressure improves, and interior active chamber swept volume constantly expands, and gas (liquid) continues constantly to be entered by air inlet (liquid) mouth 11 and 17, meanwhile compression chamber
constantly dwindle interior active chamber
pressure reach system need pressure time, compression chamber
in gas (liquid) discharge by exhaust (liquid) mouthfuls 11 and 17, at this moment the corresponding angle of the corner of rotor is just exhaust (liquid) angle of interior active chamber.In the time of β=180 °, outer active chamber completes again a work cycle, and exhaust finishes, and interior active chamber has corresponding two air-inlet cavitys
and compression chamber
in the time of β=270 °, interior active chamber completes a work cycle, and exhaust just finishes.The air inlet, compression and the exhaust that go round and begin again successively in inside and outside chamber.
Shown in Fig. 1 and Fig. 3, on outside cylinder 6 and inside cylinder 4, be provided with the vane slot 34,38,37 and 41 that supplies slide plate 1,9 and slide plate 13,18 to move, under the effect of sliding blade spring, slide plate is cut in outer surface and the internal face of elliptic rotor 5 all the time, prevents outer, inner high voltage swept volume V
d,
gas (liquid) bleed to operating on low voltage volume V
swith
in.
Referring to Fig. 1 and Fig. 3, be provided with outlet valve 35 and 39 at outside cylinder, be also provided with outlet valve 36 and 40 at inside cylinder equally, to guarantee working pressure of the present invention and system pressure adaptive feature all the time, in the time that air inlet (liquid) pressure or system pressure change, at swept volume V
d,
in can there is not insufficient compression and overcompression problem, guarantee that this machine works all the time under optimum condition, this has just solved that compressor and fluid pump air inlet (liquid) pressure usually change and the technical barrier that causes compressor and fluid pump cisco unity malfunction.
Referring to Fig. 1 and Fig. 2, elliptic rotor 5 and outside cylinder 6, inside cylinder 4 are concentric, and the rotating center of elliptic rotor 5 is concentric with geometrical center, there is no unbalanced inertial force, and rotating speed can be higher and running is more steady.
Referring to Fig. 2, elliptic rotor 5 is directly driven by a straight live axle, and without eccentric shaft, the rolling piston compressor main shaft that the processing technology of main shaft is more traditional is like this more simple.
Twin-tub rotation-type compressor of the present invention has four pairs of corresponding volumes to work at the same time in a work cycle, so effectively increased the utilization ratio of cylinder.The twin-tub rotation-type compressor of this structure in addition, for each swept volume owing to working in slide plate both sides simultaneously, so make the work cycle of traditional compressor with rolling rotor change 180 ° into by 360 °, greatly shorten the time of a circulation, improve working efficiency, an even more important feature of this structure is that compressor has four pairs of swept volumes in addition, so the compressor with rolling rotor that its working efficiency is more traditional has improved nearly four times, that is to say, every pair of swept volume completes air inlet simultaneously in rotor one turns, compression and two work cycle of exhaust, both inherited traditional compressor with rolling rotor feature simple in structure, overcome again conventional compression engine efficiency low simultaneously, the shortcoming that gas is large.The important feature of another one is that this structure two is to swept volume, when its outer shell admission space reaches maximum value and inner casing arrive 90 ° of the time phase differences of full admission volume, so the time that interior outer shell compression starts also differs half, makes the moment on live axle more even, has saved flywheel; Secondly geometrical center and the rotating center of rotor are concentric, have guaranteed the stability of compressor rotation.Main shaft is a d-axis simultaneously, has effectively solved the precision of processing, has improved volumetric efficiency.
Claims (5)
1. a twin-tub rotation-type compressor, it is characterized in that: comprise the outside cylinder (6), elliptic rotor (5), inside cylinder (4) and the cylinder head (21) that are arranged on one heart on bracket (27), main shaft (22) is arranged on the geometrical center of elliptic rotor (5), the external diameter of elliptic rotor (5) major axis equals the internal diameter of outside cylinder (6), the internal diameter of elliptic rotor (5) minor axis equals the external diameter of inside cylinder (4), on outside cylinder (6) and inside cylinder (4), be separately installed with two outside cylinder slide plates (1 that are oppositely arranged, 9) and two inside cylinder slide plates (13 that are oppositely arranged, 18), two outside cylinder slide plates (1, 9) outer surface of one end and elliptic rotor (5) is tangent, the other end and outside cylinder sliding blade spring (20, 8) contact, outside cylinder (6) internal face, the outer surface of elliptic rotor (5) and two outside cylinder slide plates (1, 9) form four outer swept volumes, and on outside cylinder (6), be positioned at two outside cylinder slide plates (1 that are oppositely arranged, 9) both sides order offers outside cylinder air inlet liquid entering hole (2, 10) and outside cylinder exhaust liquid port (19, 7),
Two described inside cylinder slide plates (13, 18) internal surface of one end and elliptic rotor (5) is tangent, the other end and inside cylinder sliding blade spring (14, 16) contact, inside cylinder (4) outer wall, the internal surface of elliptic rotor (5) and two inside cylinder slide plates (13, 18) form four interior swept volumes, on inside cylinder (4), be positioned at two inside cylinder slide plates (13 that are oppositely arranged, 18) both sides order offers inside cylinder air inlet liquid entering hole (12, 3) and inside cylinder exhaust liquid port (11, 17), wherein inside cylinder air inlet liquid entering hole (12, 3) be connected with inside cylinder air inlet admission chamber respectively, inside cylinder exhaust liquid port (11, 17) be connected with inside cylinder exhaust exhaust chamber respectively.
2. twin-tub rotation-type compressor according to claim 1, is characterized in that: on described outside cylinder (6), inside cylinder (4), relatively offer two for outside cylinder vane slot (34,38) and the inside cylinder vane slot (37,41) of outside cylinder slide plate (1,9), inside cylinder slide plate (13,18) are installed.
3. twin-tub rotation-type compressor according to claim 1, is characterized in that: the axial length of described elliptic rotor (5), outside cylinder (6), inside cylinder (4), outside cylinder slide plate (1,9) and inside cylinder slide plate (13,18) equates.
4. twin-tub rotation-type compressor according to claim 1, is characterized in that: the outside of described cylinder head (21) is also provided with exhausting buffer (25).
5. twin-tub rotation-type compressor according to claim 1, is characterized in that: inside cylinder outlet valve (40,36) and outside cylinder outlet valve (35,39) are all installed on described inside cylinder exhaust liquid port (11,17) and outside cylinder exhaust liquid port (19,7).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110401530.3A CN102410221B (en) | 2011-12-06 | 2011-12-06 | Double-cylinder rotary compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110401530.3A CN102410221B (en) | 2011-12-06 | 2011-12-06 | Double-cylinder rotary compressor |
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| Publication Number | Publication Date |
|---|---|
| CN102410221A CN102410221A (en) | 2012-04-11 |
| CN102410221B true CN102410221B (en) | 2014-07-09 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201110401530.3A Active CN102410221B (en) | 2011-12-06 | 2011-12-06 | Double-cylinder rotary compressor |
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| CN (1) | CN102410221B (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103511258A (en) * | 2012-12-25 | 2014-01-15 | 安徽美芝精密制造有限公司 | Rotary compressor and crank shaft piston assembly thereof |
| CN105179247A (en) * | 2015-09-29 | 2015-12-23 | 天津商业大学 | Horizontal totally-closed three-stage compression rotary compressor |
| CN105179246A (en) * | 2015-09-29 | 2015-12-23 | 天津商业大学 | Totally-closed vertical three-stage compression rotary compressor |
| CN108644008A (en) * | 2018-04-24 | 2018-10-12 | 胡登平 | Split-cylinder compression air supply type vane wheel rotor engine |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2762877A1 (en) * | 1997-04-30 | 1998-11-06 | Valeo Seiko Compressors Sa | Rotary compressor for motor vehicle air-conditioner |
| CN2551782Y (en) * | 2002-05-22 | 2003-05-21 | 广东工业大学 | Non-eccentric elliptic rotor compressor |
| CN101025159A (en) * | 2007-03-26 | 2007-08-29 | 浙江鑫磊机电股份有限公司 | Revolving compression apparatus with double cyinder, single rolling piston |
| JP2008255806A (en) * | 2007-04-02 | 2008-10-23 | Calsonic Compressor Inc | Gas compressor |
| CN102155407A (en) * | 2011-04-21 | 2011-08-17 | 西安交通大学 | Single-cylinder dual-function rotary-type compressor |
| CN202545248U (en) * | 2011-12-06 | 2012-11-21 | 侯敏 | Double-cylinder rotary compressor |
-
2011
- 2011-12-06 CN CN201110401530.3A patent/CN102410221B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2762877A1 (en) * | 1997-04-30 | 1998-11-06 | Valeo Seiko Compressors Sa | Rotary compressor for motor vehicle air-conditioner |
| CN2551782Y (en) * | 2002-05-22 | 2003-05-21 | 广东工业大学 | Non-eccentric elliptic rotor compressor |
| CN101025159A (en) * | 2007-03-26 | 2007-08-29 | 浙江鑫磊机电股份有限公司 | Revolving compression apparatus with double cyinder, single rolling piston |
| JP2008255806A (en) * | 2007-04-02 | 2008-10-23 | Calsonic Compressor Inc | Gas compressor |
| CN102155407A (en) * | 2011-04-21 | 2011-08-17 | 西安交通大学 | Single-cylinder dual-function rotary-type compressor |
| CN202545248U (en) * | 2011-12-06 | 2012-11-21 | 侯敏 | Double-cylinder rotary compressor |
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| Publication number | Publication date |
|---|---|
| CN102410221A (en) | 2012-04-11 |
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Effective date of registration: 20210126 Address after: 224100 the Yellow Sea West Road, Dafeng District, Yancheng City, Jiangsu Province, 92 Patentee after: JIANGSU FENGTAI FLUID MACHINERY TECHNOLOGY Co.,Ltd. Address before: 210046 box 98, Xianlin Campus, Nanjing University, 163 Xianlin Avenue, Qixia District, Nanjing City, Jiangsu Province Patentee before: Hou Min |