CN1264792A - Blade-type rotary compressor - Google Patents
Blade-type rotary compressor Download PDFInfo
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- CN1264792A CN1264792A CN 00114129 CN00114129A CN1264792A CN 1264792 A CN1264792 A CN 1264792A CN 00114129 CN00114129 CN 00114129 CN 00114129 A CN00114129 A CN 00114129A CN 1264792 A CN1264792 A CN 1264792A
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Abstract
A blade-type rotary compressor is composed of rotary cylinder sleeve and rotor offset in the cylinder sleeve. Said rotor has flat slide slots. The outer end of isolating flat blade is hinged to inner surface of rotary cylinder sleeve and its inner end is matched with said slide slot. Two follow-up end covers are linked to both ends of cylinder sleeve. The isolating blade can slide relatively to rotor and swing relatively to cylinder sleeve, so avoiding the interference with cylinder sleeve. It also has low relative speed to follow-up end covers, so having less friction loss of blade sides. It has bigger air-inlet angle as an air-sucking opening is made radically at one side of air-sucking cavity of rotary cylinder sleeve and is correspondent to the annular air channel between cylinder body and rotary cylinder sleeve.
Description
The present invention relates to a kind of compressor, specifically, relate to a kind of rotary compressor, more particularly, relate to a kind of blade-type rotary compressor.
Chinese patent application CN1153259A discloses a kind of rotary compressor, and this compressor has a cylinder body, a rotor, a rotating sleeve, an isolated blade and two fixed side end caps.Wherein: described cylinder body has a cylinder hole, and described rotor has the outer surface that circles round, and described rotating cylinder is with the inner hole surface of circling round, and described isolated blade is flat.Rotating sleeve places in the described cylinder hole, and rotor is biased in the described rotating sleeve, and the fixed side end cap splits the both end sides at described rotating sleeve.The axis of two ends of rotor is bearing on the fixed side end cap respectively and the son that rotates circles round outer surface rotates in fixed axis, and rotating sleeve rotates in fixed axis around the axis of the inner hole surface of self circling round, and rotor outer surface and the rotating sleeve inner hole surface of circling round of circling round is rotated and contacted.Isolated blade is along being parallel to the circle round direction setting of inner hole surface axis of rotating sleeve, and its outer end and rotating sleeve inner hole wall are fastening, and its inner rotor that inserts is along in the groove of radial direction formation, and is slidingly matched with one section flat groove face of this groove.Isolated blade becomes two active chambers with the separated by spaces that rotating sleeve, rotor, two fixed side end caps are sealed, when rotor rotates, isolated blade and rotating sleeve also rotate thereupon, the volume of one of them active chamber is scaled to and is air aspiration cavity, and meanwhile, the volume of another active chamber then reduces gradually and becomes compression chamber.Have a suction port and a relief opening on the cylinder body, on rotating sleeve, have an air-breathing and public common port of exhaust of confession, along with the rotation of rotating sleeve, common port alternately with cylinder body on suction port and relief opening connect, carry out breathing process and exhaust process with this.
The major defect of above-mentioned rotary compressor is: rotor includes one section flat guide side along the groove that radial direction forms, and this section directed side and isolated blade are slidingly matched, and it defines isolated blade can only be with respect to the rotor moving linearly.Inner hole surface axis and the rotor outer surface axis that circles round does not overlap because rotating sleeve circles round, so isolated blade must have the swing with respect to rotating sleeve, but isolated blade and rotating sleeve fasten as one, limited the swing of isolated blade around rotating sleeve, this will cause isolated blade and rotating sleeve to interfere phenomenon, thereby cause bending blade and frictional loss to increase.Typical situation is when isolated blade during along the rotating sleeve radial arrangement, isolated blade must point to the inner hole surface axis that circles round of rotating sleeve all the time, what the flat part of radial groove required on the rotor at this moment then is the outer surface axis that circles round that isolated blade must point to rotor, and this obviously is a contradiction.In addition, adopt a shared gas port to be difficult to realize abundant air inlet.Obviously, along with the rotation of rotor, rotating sleeve and isolated blade, the air aspiration cavity of isolated blade both sides and compression chamber are carrying out two inverse process of volume increase and volume reducing synchronously.For guaranteeing that the then shared gas port of compression must close and the getting in touch of suction port early, the result causes air inlet insufficient; In fact, if this shared gas port in compression chamber one side this moment, then air aspiration cavity must cause the vacuum resistance to suction because of replenishing new working medium; If shared gas port is at this moment in air aspiration cavity one side, then compression chamber is because of can't exhaust causing overvoltage to block.This explanation only can't realize abundant air inlet with a shared gas port.
Another shortcoming of above-mentioned rotary compressor is: there are bigger relative velocity in isolated blade and both sides fixedly end cap, because of itself and rotating sleeve can be vertically play back and forth, so frictional loss is more; In addition, also there are bigger relative velocity in rotating sleeve and cylinder hole, and more frictional loss is arranged equally.
Above-mentioned rotary compressor also has a shortcoming to be: only adopt an isolated blade can cause the exhaust gas pressure pulse amplitude excessive, comparatively devices sensitive is for example very unfavorable the refrigeration compressor concerning pressure surge for some for this.
The present invention is directed to that existing the problems referred to above provide a kind of blade-type rotary compressor in the prior art, its main purpose is: this blade-type rotary compressor can overcome the interference problem of isolated blade and rotating sleeve on the one hand effectively, can also realize abundant air inlet on the other hand.
Another object of the present invention is: after interference problem that overcomes isolated blade and rotating sleeve and the inadequate problem of air inlet, reduce between isolated blade and the side end cap effectively and rotating sleeve and cylinder hole between relative velocity, thereby reduce the frictional loss at above-mentioned position.
A further object of the invention promptly reduces the pulse amplitude of its exhaust pressure.
Above-mentioned purpose of the present invention is achieved in that provides a kind of blade-type rotary compressor, described compressor to comprise a cylinder body, a rotor, a rotating sleeve, an isolated blade and two fixed side end caps; Described cylinder body has a cylinder hole, and described rotor has an outer surface and have the chute of a flat along the rotor radius direction of circling round, and described rotating cylinder is with the inner hole surface of circling round, and described isolated blade is flat; Rotating sleeve places in the described cylinder hole, and rotor is biased in the described rotating sleeve, and the fixed side end cap splits the both end sides at described rotating sleeve; The axis of two ends of rotor is bearing on the fixed side end cap respectively and the son that rotates circles round outer surface rotates in fixed axis, and rotating sleeve rotates in fixed axis around the axis of the inner hole surface of self circling round, and rotor outer surface and the rotating sleeve inner hole surface of circling round of circling round is rotated and contacted; It is characterized in that having on the described rotating sleeve one with the circle round arc groove of inner hole surface parallel axes of rotating sleeve; Described rotor rollaway nest can also be along being parallel to circle round other direction settings of outer surface axis of rotor except that radial direction; The outer end of described isolated blade and rotating sleeve arc groove are hinged and be rotatably assorted, and it is inner to insert in rotor rollaway nest and be slidingly matched with it; Radial direction at described rotating sleeve has intakeport, this intakeport is close to the hinge point of described isolated blade and described rotating sleeve and is positioned at a described isolated blade side of sense of rotation dorsad, simultaneously, between the outer surface of the internal face in described cylinder hole and described rotating sleeve, be formed with and the corresponding annular air channel of described intakeport;
In a preferred embodiment, the described rotating sleeve two ends servo-actuated end cap that has been located by connecting respectively, these servo-actuated end caps are bearing in respectively on described two fixed side end caps with bearing structure, and rotating sleeve is by the supporting of described servo-actuated end cap and rotate in fixed axis around the axis of the inner hole surface of circling round of rotating sleeve synchronously;
In a further advantageous embodiment, except that described isolated blade, also have additional the circle round flat isolated blade of inner hole surface parallel axes of one or more and rotating sleeve in addition, be parallel to simultaneously the circle round direction of inner hole surface axis of rotating sleeve and set up the arc groove of same quantity in the rotating sleeve upper edge, and be parallel to the circle round direction of outer surface axis of rotor in the rotor upper edge and set up corresponding arc groove, all be fitted with a rotary column in the rotor arc groove, each rotary column has a flat chute along being parallel to the rotary column axial direction; The outer end of the isolated blade of setting up is hinged in the corresponding rotating sleeve arc groove and is rotatably assorted, and it is inner to insert in the chute of corresponding rotary column and be slidingly matched.
Blade-type rotary compressor of the present invention owing to adopt on rotating sleeve, offer arc groove and with the hinged structure that cooperates in isolated blade outer end, make isolated blade in rotation process not only relatively rotor slide but also relatively rotating sleeve swing, thereby overcome the problem that isolated blade and rotating sleeve interfere, simultaneously, the structure of intakeport is radially offered in employing on rotating sleeve, and be aided with the corresponding annular air flue, the result makes flow inlet angle increase greatly, so solved the inadequate problem of air inlet; Owing to adopt the servo-actuated end cap to connect and support the structure of rotating sleeve, make isolated blade obviously reduce with respect to the speed of servo-actuated end cap, reduced the frictional loss between isolated blade and both sides end cap, in addition, because rotating sleeve does not contact with cylinder body cylinder hole, so solved the frictional loss problem at this position yet; Owing to adopt two and plural isolated blade structure, reduced the pulse amplitude of exhaust pressure.
Below in conjunction with accompanying drawing several preferred embodiments of the present invention is specifically described, wherein:
Fig. 1 is first embodiment's of a blade-type rotary compressor of the present invention longitudinal section schematic representation;
Fig. 2 is the schematic cross section of blade-type rotary compressor shown in Figure 1;
Fig. 3 is second embodiment's of a blade-type rotary compressor of the present invention longitudinal section schematic representation;
Fig. 4 is the A-A direction sectional view of blade-type rotary compressor shown in Figure 3, and wherein the part is broken away;
Fig. 5～7th, several structural representations that are located by connecting between the servo-actuated end cap of blade-type rotary compressor shown in Figure 3 and the rotating sleeve;
Fig. 8～10th, the servo-actuated end cap of blade-type rotary compressor shown in Figure 3 and fixing several supporting structure schematic representation between the end cap;
Figure 11 is the 3rd embodiment's of a blade-type rotary compressor of the present invention schematic cross section.
Fig. 1 and Fig. 2 show first embodiment's of blade-type rotary compressor of the present invention longitudinal section and schematic cross section.In this embodiment, described vane compressor comprises that 1, one of a cylinder body has 3, one of the rotors of the outer surface that circles round that isolated blade 5, two the fixed side end caps 6a and the 6b of 2, one flat of rotating sleeve of the inner hole surface of circling round are arranged.Cylinder body 1 has a cylinder hole 7, and rotating sleeve 2 places in this cylinder hole 7 and is rotatably assorted with it, and rotating sleeve rotates in fixed axis around the inner hole surface axes O 2 of self circling round.Rotor 3 is biased in the rotating sleeve 2, and its two ends are bearing in fixedly on the end cap 6a and 6b with sliding bearing 8a and 8b respectively, and this sliding bearing also can change rolling bearing or needle bearing (not shown) into.Fixedly end cap 6a and 6b split the both end sides at rotating sleeve 2, and fastening with cylinder body 1.Rotor 3 rotates in fixed axis around the outer surface axes O 1 of self circling round, and the inner hole surface of circling round of the circle round outer surface and the rotating sleeve 2 of rotor 3 is rotated and is contacted with the P line.The O1 direction that parallels to the axis in rotor 3 upper edges has flat chute 10, and the direction of the O2 that parallels to the axis in the inner hole wall upper edge of rotating sleeve 2 has arc groove 9.The outer end of isolated blade 5 and arc groove 9 are hinged and be rotatably assorted, its inner insertion in the flat chute 10, and be slidingly matched with flat chute 10.
The same inner hole surface of circling round of revolving outer surface and rotating sleeve 2 of above-mentioned rotor 3 can be that the cylndrical surface also can be a round table surface.The optimum structure assembly is the rotating sleeve (shown in Fig. 1-2) that the rotor of cylindrical outer surface is joined the cylinder inner hole surface, has the simplest manufacturability and assembling this moment; Another kind of preferable structure assembly is that round platform outer surface rotor is joined the round platform inner hole surface rotating sleeve (not shown) that tapering equates, this assembly also has better simply manufacturability and assembling.Adopt above-mentioned two kinds of structural group timings, the outer surface axes O 1 of circling round of rotor 3 is parallel with the inner hole surface axes O 2 of circling round of rotating sleeve 2.
When rotor 3 rotates (shown in the figure is clockwise direction), will drive isolated blade 5 by flat chute 10 and rotate, isolated blade 5 rotates by hinge point driven rotary cylinder sleeve 2 again.In rotation process, between isolated blade 5 and the flat chute 10 slide relative is arranged, relatively rotate between isolated blade 5 and the rotating sleeve 2 simultaneously.Constitute two active chambers of blade-type rotary compressor by rotor 3, rotating sleeve 2, isolated blade 5, left end cap 6b and right end cap 6a, wherein the left side is an air aspiration cavity 18, and the right is a compression chamber 19.Along with the rotation of rotor 3, the volume of air aspiration cavity 18 increases gradually, and working medium is inhaled in the chamber through appropriate intakeport, and meanwhile, the volume of compression chamber 19 reduces gradually, and the working medium in the chamber is compressed, and working medium can be discharged compression chamber through appropriate relief opening.
Need to prove that present embodiment can also transform rotating sleeve 2 driving link into and transform rotor 3 into driven member, this change can realize above-mentioned functions equally.
For avoiding intake process and exhaust process to clash, intakeport and relief opening should divide separately and be arranged:
A kind of air intake structure is to adopt traditional axial admission mode, promptly on the fixed side end cap, offer intakeport, shown in Fig. 2 double dot dash line 4, though this air intake structure is simple, but for guaranteeing that sufficient period of intake-cross section value is arranged, the inlet loss angle is often very big, generally reaches 90 ° more than the angle of rotor.
Another air intake structure is to adopt radial air inlet, shown in Fig. 1～2, open intakeport 11 in the radial direction of rotating sleeve 2, intakeport 11 is near isolated blade 5 outer ends and be positioned at air aspiration cavity 18 1 sides, be formed with between cylinder hole 7 and rotating sleeve 2 and intakeport 11 corresponding annular air channels 12 simultaneously, annular air channel 12 communicates with suction port 13; Annular air channel 12 can form on the inner hole wall in cylinder hole 7 separately, also can form on the outer surface of rotating sleeve 2 separately, can also be simultaneously forms (as shown in FIG.) on the outer surface of the inwall in cylinder hole 7 and rotating sleeve 2; When rotating sleeve 2 rotated, working medium reached annular air channel 12 through suction port 13 and enters air aspiration cavity 18 from intakeport 11 again.This air intake structure is not only simple, and because intakeport 11 communicates with annular air channel 12 all the time, so bigger time-cross section value is arranged, has realized abundant air inlet; By adjusting the position of intakeport 11, for example allow the outer end of its more close isolated blade 5, the inlet loss angle can also be controlled at small range.
A benefit that adopts the radial air inlet structure to bring is, can be provided with and intakeport 11 corresponding protruding lips 15 in intakeport 11 windward sides one side (be the left side among Fig. 2), and the effect of protruding lip 15 is that more working medium is scraped into air aspiration cavity 18.
Adopt axial exhaust in the present embodiment, structure is met to compression chamber one side at isolated blade 5 shown in Fig. 1～2, has the air drain 16 that leads to this isolated blade the inner, so that allow compression chamber 19 interior working medium enter the bottom land of chute 10; Can also on the side that is positioned at compression chamber one side on the chute 10, open air drain in addition, also can be directly on rotor 3 perforate compression chamber 19 is communicated with (not shown) with the bottom land of chute 10; Have exhaust port 17 on fixed side end cap 6a, this exhaust port 17 is communicated with the bottom land of chute 10; Compressed working medium is discharged compressor through air drain 16, exhaust port 17, one-way valve 20, filter screen 21, through hole 22, hyperbaric chamber 23 and relief opening 24.Another kind of axial exhaust structure is the gas port (not shown) that begins to rehearse near the fixedly end cap 6a of the compression chamber 19 1 sides Line of contact P of rotor 3 and rotating sleeve 2, and this structure also can realize smooth exhaust.
The outer surface that circles round of the rotor 3 shown in Fig. 1-2 is that its diameter of cylndrical surface is d1, the inner hole surface of circling round of rotating sleeve 2 is that its diameter of cylindrical hole face is d2, axes O 1 is e1 with the distance of axes O 2, then: for guaranteeing between rotor 3 and the rotating sleeve 2 good sealing property is arranged, answer meeting geometric relation: d2-d1=2e1, but certain interval should be stayed between the two so that form oil film, in case the dry friction phenomenon takes place.
Fig. 3～4 show second embodiment's of blade-type rotary compressor of the present invention longitudinal section schematic representation and A-A generalized section.This embodiment is the further improvement of being done based on the foregoing description, and part sequence number is inherited Fig. 1～2.Wherein improved place is: the two ends of rotating sleeve 2 be located by connecting respectively servo-actuated end cap 25a and 25b, and be bearing in fixedly on the end cap 6a and 6b by servo-actuated end cap 25a and 25b, and wherein position structure is with outer stopper 26 location; Can locate with inner stopper 27 in addition, structure as shown in Figure 5; Also can locate with sleeve 28, structure as shown in Figure 6; Can also locate with locating stud 29, structure as shown in Figure 7.Fastening structure shown in Fig. 3～4 also can weld the structure (not shown) that another section is spirally connected with an interference close-fitting structure or an end in addition for adopting screw 30 fastening.The center portion of servo-actuated end cap 25a shown in the figure and 25b all makes a hole structure, the seat axially bored line is coaxial with the inner hole surface axes O 2 of circling round of rotating sleeve 2, fixedly the center portion of end cap 6a and 6b then makes journal structure, and sliding bearing 31a and 31b structure are formed in these axle journals and described follower ends cage hole.In addition, the servo-actuated end cap can be made axle journal and the fixed side end cap is made hole form a sliding bearing, its structure as shown in Figure 8; Also the servo-actuated end cap can be made axle journal and the fixed side end cap is made a hole, middle with rolling bearing 32 contacts, its structure as shown in Figure 9; The servo-actuated end cap can also be made a hole and fixedly end cap make axle journal, middle with rolling bearing 33 contacts, its structure is as shown in figure 10.Replacing above-mentioned rolling bearing 32 or 33 with needle roller also is feasible structure.
Need to prove that when compressor adopted vertical structure or tilting structural configuration, above-mentioned bearing support structure also should be done corresponding change, only need that one of them bearing is made axial thrust bearing this moment and get final product.
Because servo-actuated end cap 25a, 25b and rotating sleeve 2 rotate around dead axle O2 synchronously, and the outer end of isolated blade 5 and 2 hinged cooperations of rotating sleeve, therefore isolated blade 5 is little with the relative velocity of servo-actuated end cap 25a and 25b, in fact has only relative swing slightly, so reduced the frictional loss between them; Rotating sleeve 2 does not contact with cylinder bore 7 in addition, not only reduced the frictional loss (Outside Dimensions of noticing rotating sleeve 2 is big than the size of servo-actuated end cap block bearing) at this position, but also reduced the machining accuracy of rotating sleeve 2 and cylinder bore 7, manufacture cost is descended.Simultaneously, the lubricated of bearing also becomes relatively easy.
The inlet and outlet structure of present embodiment can adopt first embodiment's structure.
Figure 11 shows another embodiment's of blade-type rotary compressor of the present invention schematic cross section, it be above-mentioned first embodiment or second embodiment the basis on the further improvement done.Major part and layout are with reference to first embodiment or second embodiment, and part sequence number is inherited Fig. 1～2.Wherein: set up an isolated blade 5b, an intakeport 11b, and the direction of the O2 that correspondingly parallels to the axis in the endoporus wall upper edge of rotating sleeve 2 is set up an arc groove 9b; The direction of O1 of paralleling to the axis in the rotor upper edge is simultaneously set up arc groove and is rotated within it and is fitted with cylindrical rotary column 14, and rotary column 14 has the flat chute 10b that is parallel to this rotary column axes O 3.For preventing to interfere with rotating sleeve 2, rotary column 14 does not exceed the rotor outer surface scope of circling round.The outer end of isolated blade 5b and arc groove 9b are hinged and be rotatably assorted, and innerly are slidingly matched with chute 10b.Adopt axial exhaust port 40 to carry out exhaust.Because adopt double blade structure, it is milder that exhaust gas pressure pulse becomes.Structure can also adopt plural isolated blade structure according to this, and its effect is fine equally.Blade structure is preferable with basic symmetrical distribution.
Must be pointed out that at last blade-type rotary compressor of the present invention also can be directly as pump, for example: various air pumps, vacuum pump, vacuum--compression dual-purpose pump etc.Therefore, all have with blade-type rotary compressor of the present invention also should be considered as category of the present invention with all kinds of pumps of spline structure and principle.
Claims (5)
1. blade-type rotary compressor, it comprises a cylinder body, a rotor, a rotating sleeve, an isolated blade and two fixed side end caps; Described cylinder body has a cylinder hole, and described rotor has the outer surface that circles round, and described rotating cylinder is with the inner hole surface of circling round, and described isolated blade is flat, and described rotor offers the chute of a flat along radial direction; Rotating sleeve places in the described cylinder hole, and rotor is biased in the described rotating sleeve, and the fixed side end cap splits the both end sides at described rotating sleeve; The axis of two ends of rotor is bearing on the fixed side end cap respectively and the son that rotates circles round outer surface rotates in fixed axis, and rotating sleeve rotates in fixed axis around the axis of the inner hole surface of self circling round, and the outer surface that circles round of rotor rotates with the inner hole surface of circling round of rotating sleeve and contacts; It is characterized in that described rotor rollaway nest can also be along being parallel to circle round other direction settings of outer surface axis of rotor except that radial direction is offered; Offer on the described rotating sleeve one with the circle round arc groove of inner hole surface parallel axes of rotating sleeve; The outer end of described isolated blade and this rotating sleeve arc groove are hinged and be rotatably assorted, and the inner of isolated blade is inserted in the rotor rollaway nest and is slidingly matched with it; Radially have intakeport on described rotating sleeve, this intakeport is close to the hinge point of described isolated blade and described rotating sleeve and is positioned at a described isolated blade side of sense of rotation dorsad; Between the outer surface of the internal face in described cylinder hole and described rotating sleeve, be formed with and the corresponding annular air channel of above-mentioned intakeport.
2. blade-type rotary compressor as claimed in claim 1, the two ends that the it is characterized in that described rotating sleeve servo-actuated end cap that has been located by connecting respectively, these servo-actuated end caps are bearing in respectively on described two fixed side end caps with the bearing mode, and described rotating sleeve rotates in fixed axis around the axis of the inner hole surface of circling round of rotating sleeve synchronously by the supporting of above-mentioned servo-actuated end cap and with the servo-actuated end cap.
3. blade-type rotary compressor as claimed in claim 1 or 2, it is characterized in that except that described isolated blade, also have additional the circle round flat isolated blade of inner hole surface parallel axes of one or more and described rotating sleeve in addition, be parallel to simultaneously the circle round direction of inner hole surface axis of rotating sleeve and have additional the arc groove of same quantity in described rotating sleeve upper edge, and be parallel to the circle round direction of outer surface axis of described rotor in described rotor upper edge and have additional the arc groove of respective numbers, all be fitted with a rotary column in each rotor arc groove, each rotary column all includes a flat chute of offering along the direction that is parallel to the rotary column axis; The outer end of the isolated blade of being set up all is hinged in the corresponding rotating sleeve arc groove and is rotatably assorted with it, and its inner is all inserted in the chute of corresponding rotary column and is slidingly matched.
4. blade-type rotary compressor as claimed in claim 1 or 2 is characterized in that the outer surface of described rotating sleeve is provided with and the corresponding protruding lip of described annular air channel, and the adjacent described intakeport of this protruding lockjaw also is positioned at described intakeport windward side one side.
5. blade-type rotary compressor as claimed in claim 3 is characterized in that described rotary column drops within the scope of the outer surface that circles round of described rotor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 00114129 CN1264792A (en) | 2000-03-17 | 2000-03-17 | Blade-type rotary compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 00114129 CN1264792A (en) | 2000-03-17 | 2000-03-17 | Blade-type rotary compressor |
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| CN1264792A true CN1264792A (en) | 2000-08-30 |
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| CN 00114129 Pending CN1264792A (en) | 2000-03-17 | 2000-03-17 | Blade-type rotary compressor |
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Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
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| WO2009094862A1 (en) * | 2008-01-29 | 2009-08-06 | Jiangsu Super-Power Machinery Co., Lt | A rotary compressor |
| CN102052318A (en) * | 2009-11-04 | 2011-05-11 | 株式会社电装 | Compressor |
| WO2013036203A1 (en) * | 2011-09-08 | 2013-03-14 | Sanden International (Singapore) Pte Ltd | Revolving vane compressor |
| CN103967786A (en) * | 2013-01-31 | 2014-08-06 | 株式会社丰田自动织机 | Vane compressor |
| CN104471250A (en) * | 2012-06-26 | 2015-03-25 | 株式会社电装 | Rotary compressor |
| CN105840507A (en) * | 2015-01-15 | 2016-08-10 | 珠海格力节能环保制冷技术研究中心有限公司 | Pump body and rotary cylinder compressor |
| CN107035694A (en) * | 2017-05-19 | 2017-08-11 | 珠海凌达压缩机有限公司 | Compressor for reducing oil content of refrigerant |
| CN109322825A (en) * | 2018-11-22 | 2019-02-12 | 白晓瑞 | A kind of composite rotors compressor |
| CN110873048A (en) * | 2018-08-29 | 2020-03-10 | 朱秋萍 | Multi-type sliding plate plane rotary compressor |
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2000
- 2000-03-17 CN CN 00114129 patent/CN1264792A/en active Pending
Cited By (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8790099B2 (en) * | 2008-01-29 | 2014-07-29 | Dafeng Fengtai Fluid Machinery Technology Co., Ltd. | Rotary compressor with synchronous turning between cylinder block and rotor |
| US20100310400A1 (en) * | 2008-01-29 | 2010-12-09 | Dafeng Fengtai Fluid Machinery Technology Co., Ltd | Rotary Compressor |
| JP2011511198A (en) * | 2008-01-29 | 2011-04-07 | 大▲豊▼▲豊▼泰流体▲機▼械科技有限公司 | Rotary compressor |
| RU2470184C2 (en) * | 2008-01-29 | 2012-12-20 | Дафын Фынтай Флуид Машинери Технолоджи Ко., Лтд. | Rotary compressor |
| WO2009094862A1 (en) * | 2008-01-29 | 2009-08-06 | Jiangsu Super-Power Machinery Co., Lt | A rotary compressor |
| CN102052318A (en) * | 2009-11-04 | 2011-05-11 | 株式会社电装 | Compressor |
| CN103782035B (en) * | 2011-09-08 | 2016-08-24 | 三电国际（新加坡）私人有限公司 | Rotary vane compressor |
| CN103782035A (en) * | 2011-09-08 | 2014-05-07 | 三电国际（新加坡）私人有限公司 | Revolving vane compressor |
| WO2013036203A1 (en) * | 2011-09-08 | 2013-03-14 | Sanden International (Singapore) Pte Ltd | Revolving vane compressor |
| CN104471250A (en) * | 2012-06-26 | 2015-03-25 | 株式会社电装 | Rotary compressor |
| CN103967786A (en) * | 2013-01-31 | 2014-08-06 | 株式会社丰田自动织机 | Vane compressor |
| CN103967786B (en) * | 2013-01-31 | 2016-06-22 | 株式会社丰田自动织机 | Vane compressor |
| CN105840507A (en) * | 2015-01-15 | 2016-08-10 | 珠海格力节能环保制冷技术研究中心有限公司 | Pump body and rotary cylinder compressor |
| CN107035694A (en) * | 2017-05-19 | 2017-08-11 | 珠海凌达压缩机有限公司 | Compressor for reducing oil content of refrigerant |
| CN110873048A (en) * | 2018-08-29 | 2020-03-10 | 朱秋萍 | Multi-type sliding plate plane rotary compressor |
| CN109322825A (en) * | 2018-11-22 | 2019-02-12 | 白晓瑞 | A kind of composite rotors compressor |
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