CN1912395B - Middle-speed high-pressure multi-stage centrifugal blowing machine - Google Patents
Middle-speed high-pressure multi-stage centrifugal blowing machine Download PDFInfo
- Publication number
- CN1912395B CN1912395B CN2005100911706A CN200510091170A CN1912395B CN 1912395 B CN1912395 B CN 1912395B CN 2005100911706 A CN2005100911706 A CN 2005100911706A CN 200510091170 A CN200510091170 A CN 200510091170A CN 1912395 B CN1912395 B CN 1912395B
- Authority
- CN
- China
- Prior art keywords
- blower
- impeller
- cylinder body
- mentioned
- gear
- 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.)
- Expired - Fee Related
Links
Images
Landscapes
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
A medium speed high pressure blower of multistage centrifugal type is prepared as applying vertical split cylinder structure, setting multiple steel or aluminium impeller on master shaft, supporting master shaft by bearing box at one end of cylinder and body-connected gear box at another end of cylinder, using body-connected gear box as part of cylinder on blower for raising rotary speed of impeller to obtain higher pressure.
Description
Technical field
The present invention relates to the mechanical type blower field of using in the various commercial Application, particularly a kind of multiple-stage centrifugal fan of middling speed high pressure.
Background technique
Centrifugal blower is normally used for using the blower language in the multiple commercial Application, be (5-15 pound/square inch) with respect to pressing in traditional, and the pressure of 15-25 (pound/square inch) is commonly referred to high pressure.In commercial Application, use example to have with high pressure ability blower: the deep trouth aeration tank that modern sewage treatment works uses, for multiple combustion process provides oxygenous air, the supercharging of various gas, and can be used as the vacuum power source.
But conventional direct connection drives the pressure that multiple-stage centrifugal fan is difficult to realize 15-25 (pound/square inch).This is lower mainly due to the impeller rotational speed, and progression is subjected to the restriction of rotor critical velocity, and because the outlet high temperature that the interior leakage that seals by excessive enclosing cover for impeller causes.
Therefore, most of multiple-stage centrifugal fans belong to the type of low pressure to middle pressure, the outlet gauge pressure is generally 5-15 pound/square inch (when import approximately is barometric pressure), and the blower that is lower than 5 pounds/square inch is called as fan, above 25 pounds/square inch then be called as compressor.
With reference to diagram 1, arrow 10 has shown that a kind of typical conventional direct connection drives multistage (being called for short DDMS) centrifugal blower among the figure.The DDMS centrifugal blower is simple in structure, seldom needs to safeguard.Low speed and direct the driving make it reliable, and noise is lower.
As shown in fig. 1, traditional DDMS blower 10 has 14 1 of axises, has been connected in series several impellers 12 on the axle, and the axle two ends respectively have a rolling bearing 16 to support.Each grade is made up of the Diffuser 18 and the bend return channel 20 that are installed in the impeller 12 on the axle 14 and closely follow thereafter.Usually be 3000 rev/mins induction alternating current (AC) motor (country at 60 hertz of power supplys then is 3600 rev/mins) with revolution, come blower by direct live axle 22.
Usually need several such level series connection to obtain required pressure, the pressure of the voluminous more life of progression is just high more.In traditional DDMS blower, often adopt the structural type of vertical split surface to satisfy the requirement of supercharging, extra pressure can easily obtain by increasing progression.Yet maximum progression is limited by the critical speed of rotation of rotor.Because adopt rolling bearing (simplified structure) usually, running speed must be lower than 15～20% of first critical speed of rotation.Therefore, use the aluminum alloy impeller can alleviate rotor weight, so that increase progression that can be maximum, thereby pressure maximum obtained.
Every grade compression process starts from rotary blade 12, and the wherein effect of impeller blade is quickened air, pressure be increased (being directly proportional with velocity squared).Air-flow enters Diffuser 18 subsequently, and around here, the speed of air-flow reduces, and makes kinetic energy further be converted to the pressure energy.The gas that speed reduces enters bend return channel 20 then, the rotational component of blade place to go air-flow wherein, and be directed to the import of next stage.This process will constantly repeat in level subsequently, reach requirement up to pressure.But gas temperature also is improved in this compression process.
Because the improving constantly of gas pressure in serial connection level, requirement is with sealing the leakage loss that reduces each grade between rotary blade wheel cap and fixing cylinder.Therefore, the efficient of these sealings is directly relevant with the efficient and the outlet temperature of blower.
With reference to Fig. 2, what Fig. 2 showed is a kind of common and the most most economical enclosing cover for impeller sealing of using on traditional DDMS 10.As shown in Figure 2, enclosing cover for impeller 24 is level and smooth labyrinth comb teeth shape sealings.The labyrinth broach can be on the rotary blade 12 or be arranged on the fixing cylinder 26.Traditional enclosing cover for impeller sealing 28 is for radially, and just the tip of labyrinth broach and the minimum interval between the apparent surface are radially.Raise the efficiency in order to reduce to leak, particularly flow hour, the gap should be as much as possible little.Yet too little interval can increase manufacture cost, and improves by impeller 12 and contact the possibility that the rotor that caused is killed with cylinder body.
When the DDMS centrifugal blower is used to use 50 hertz of power supply countries (global 2/3 country), also there is other problems.
Such as, if the rotating speed of a blower is lowered 20% 3600 rev/mins of 3000 rev/mins of dropping to 50 hertz of power supplys of 60 hertz of power supplys (for example from), for the blower of same size size, about 20% flow and 44% pressure will be lost.Still drive simultaneously in order to compensate this pressure loss, can increase more a plurality of progression with direct connection.This is not only expensive but also be subjected to the restriction of rotor critical speed.Perhaps adopt the external coupling type gear-box to improve the rotating speed of blower.But this combined volume is huge, makes the machine installation and maintenance intricate, and has increased cost.DDMS centrifugal blower another potential problem in high-voltage applications is caused by those normally used enclosing cover for impeller radial seals.Because the interface of the critical piece of blower is vertical split surface, connect by seam during assembling, radially will have cumulative limit and interval, this cumulative limit and interval have reduced the design gaps of enclosing cover for impeller, the sealing of potential enclosing cover for impeller and the possibility of cylinder friction are increased, and this again and then cause blower rotor to be killed.Simultaneously, because the thermal expansion coefficient of aluminium is the twice of cast iron, the thermal expansion difference between aluminium matter impeller and cast iron cylinder will further reduce spaced radial.This influence under high pressure (because high pressure brings high temperature usually, this opposes to cause bigger thermal expansion difference again) will be more abominable.
In order partly to solve the rotating speed restriction, the centrifugal blower of another type: disjunctor gear single-stage high-speed (being called for short IGSS) centrifugal blower has obtained application more and more widely, in the past particularly in the country that uses 50 hertz of power supplys in 20 years.
With reference to Fig. 3, a kind of existing typical IGSS centrifugal blower of 30 expressions.
As shown in Figure 3, IGSS centrifugal blower 30 has only an impeller 32 on high speed gear shaft 34 ends that are suspended on disjunctor gear speedup case 36, and lower velocity shaft is driven by the motor (among the figure and do not show) of standard.In order once to obtain desired pressure in single stage compression, the rotating speed of impeller 32 is very high, generally at 10000 rev/mins to 100000 rev/mins.Flow and pressure can recently be adjusted by changing gear transmission.
By changing gear ratio rather than changing blower, the IGSS blower has solved existing 50 hertz to the 60 hertz transfer problems of DDMS blower.IGSS blower volume is little in light weight, and for improving the performance of off-design point, also can select to be equipped with entry guide vane (IGV) or adjustable diffuser vane (VDV).
Yet the corresponding high speed technology of high speed inevitable requirement of impeller and extreme accurate production method realize.
For example, need to use expensive sliding bearing 40 rather than rolling bearing cheaply.In addition, also want the higher and complicated more force-feed lubrication system 42 of user cost rather than simple splash-lubricating system 449 (referring to shown in Figure 1).Quick runner Final 32 degree requires very high, makes by the five jig mills system of milling or for welding steel usually, rather than cast aluminium cheaply.
Compare with low speed DDMS 10, the rotating speed of High Speed I GSS blower 30 and blade loading are all very high, so also high many of noise.Therefore its frequency noise height is recruited disagreeable or can be produced potential harm to nearby operator very much.For high like this noise, environmental protection regulations and standard require to add the sound insulation cabinet through regular meeting and reduce noise magnitude, have further increased the product expense and have increased the machine maintenance difficulty.So our expectation provides a kind of design and structure of new high pressure centrifugal blower, to obtain higher pressure and pressure ratio, solves the problem that exists in those conventional centrifugal blowers simultaneously.
Summary of the invention
The object of the present invention is to provide the multiple-stage centrifugal fan of a kind of compact structure, middling speed high pressure, it comprises the centrifugal level of a disjunctor gear-box and a plurality of vertical subdivision polyphones, every grade is used aluminium or steel impeller, and enclosing cover for impeller is sealed into axial labyrinth comb teeth shape sealing.
A target of the present invention provides a kind of brand-new and unique blower design and structure, enables to obtain voltage rise and the pressure ratio higher than traditional centrifugal blower.
Another target of the present invention provides a kind of design and structure of brand-new and unique high pressure centrifugal blower, utilizes multi-stage impeller to dispose to obtain voltage rise and the pressure ratio of De Genggao.
Another target of the present invention provides a kind of design and structure of brand-new and unique high pressure centrifugal blower, utilizes the disjunctor gearbox configuration to obtain voltage rise and the pressure ratio of De Genggao.
Another target of the present invention provides a kind of design and structure of brand-new and unique high pressure centrifugal blower, utilizes temperature and the lower axial impeller wheel cap sealing of multistage susceptibility, obtains higher pressure capability under the prerequisite that does not increase cost.
Another target of the present invention provides a kind of design and structure of brand-new and unique high pressure centrifugal blower, but the axial impeller wheel cap that utilization can be worked under gap littler and more ex ante forecasting sealing, to improve the efficient and the reliability of blower.
Another target of the present invention provides a kind of design and structure of brand-new and unique high-pressure multi-stage centrifugal blowing machine, efficient, safety and reliable, and manufacture cost and freight are low, and are applicable to 50 hertz and 60 hertz of two kinds of electric power supply systems.
In order to realize above-mentioned task, best implementation of the present invention: the present invention is a compact structure, middling speed high pressure blower, it uses centrifugal level (use aluminium matter or steel and be furnished with the impeller of axial labyrinth comb teeth shape enclosing cover for impeller sealing) and a disjunctor gear speedup case of a plurality of vertical subdivision polyphones.
A kind of technical solution wherein is: a kind of centrifugal blower of middling speed high pressure, it is characterized in that, and which comprises at least:
A. have the suction port of vertical split surface and the housing structure of air outlet, interconnect by internal air passageway therebetween;
B. two-stage at least, each grade be all at the centrifugal impeller that is contained on the same pinion shaft, propellant gas flowing from above-mentioned import to above-mentioned outlet, thus obtain the higher pressure or the lifting of pressure ratio, and axle is supported by above-mentioned housing structure;
C. a disjunctor gear-box that is positioned at above-mentioned small gear axle head has a gear train of having determined the gear ratio in advance right in gear-box, in order to from live axle to above-mentioned pinion shaft conveying rotary motion; And
D. between the enclosing cover for impeller of above-mentioned impeller and said housing structure, adopt the sealing of axial impeller wheel cap, with reduce internal leakage and unexpectedly mechanicalness contact.
Another kind of technological scheme is: a kind of centrifugal blower of middling speed high pressure, it is characterized in that, and which comprises at least:
A. have the suction port of vertical split surface and the housing structure of air outlet, interconnect by internal air passageway therebetween;
B. two-stage at least, each grade all has the centrifugal impeller that is contained on the same pinion shaft, propellant gas flowing from above-mentioned import to above-mentioned outlet, thus obtain the higher pressure or the lifting of pressure ratio, and axle is supported by above-mentioned housing structure; And
C. a disjunctor gear-box that is positioned at above-mentioned small gear axle head has a gear train of having determined the gear ratio in advance right in gear-box, in order to from live axle to above-mentioned pinion shaft conveying rotary motion.
Another technological scheme is: a kind of centrifugal blower of middling speed high pressure, it is characterized in that, and which comprises at least:
A. have the suction port of vertical split surface and the housing structure of air outlet, interconnect by internal air passageway therebetween;
B. two-stage at least, each grade all has the centrifugal impeller that is contained on the same pinion shaft, propellant gas flowing from above-mentioned import to above-mentioned outlet, thus obtain the higher pressure or the lifting of pressure ratio, and axle is supported by above-mentioned housing structure; And
C. between the enclosing cover for impeller of above-mentioned impeller and said housing structure, adopt the sealing of axial impeller wheel cap, with reduce internal leakage and unexpectedly mechanicalness contact.
The present invention has a lot of novelties and unique feature and advantage.It provides a kind of can obtaining with the conventional centrifugal blower to compare the blower with higher voltage rise and pressure ratio, have the configuration of multi-stage impeller and disjunctor gear speedup case, but and the axial impeller wheel cap that can under gap littler and more ex ante forecasting, work sealing, improving the efficient and the reliability of blower, and more durable under higher temperature and during more progression.High-pressure multi-stage centrifugal blowing machine structure of the present invention is tight, efficient, safety and reliable, and the expense of manufacture cost and transportation is lower, and is applicable to 50 hertz and 60 hertz of two kinds of electric power supply systems.
These and other novelty and target of the present invention, with by following about diagrammatic sketch and literal detailed description, discussion and claim and more clear.
Description of drawings
Fig. 1 is a sectional view of the prior art, show that a traditional direct connection drives multistage (DDMS) centrifugal blower, its main structure be characterized as: use the aerodynamic force level of vertical subdivision structure, rolling bearing, radial impeller wheel cap sealing and splash system lubrication system;
Fig. 2 is the partial cross section figure of blower of the prior art, shows a kind of structure and feature that typically is used for the radial impeller wheel cap sealing in the conventional DDMS centrifugal blower;
Fig. 3 is a sectional view of blower of the prior art, shows a kind of conventional disjunctor gear single-stage (IGSS) centrifugal blower, its main structure be characterized as: use gear up, sliding bearing and force-feed lubrication system;
Fig. 4 is a sectional view, shows the present invention, i.e. the best implementation of high pressure disjunctor gear drive multistage (IGMS) centrifugal blower: have the sealing of disjunctor gear speedup case and axial impeller wheel cap;
Fig. 5 is partial cross section figure, and show the configuration of a kind of axial impeller wheel cap sealing of the present invention: broach is on impeller; And
Fig. 6 is partial cross section figure, and show the configuration of another kind of axial impeller wheel cap sealing of the present invention: promptly broach is on cylinder body.
The present invention is described in further detail below in conjunction with embodiment that accompanying drawing and inventor provide, but the present invention is not limited to these embodiments.
Embodiment
Although describe specific implementation of the present invention with reference to relevant diagram below, should be appreciated that the implementation here only is as an example and illustrates that other scheme that can realize according to principle of the present invention then has a variety of.Clearly, for the people who is familiar with these technologies, various variations and modification in category of the present invention will be considered to belong to spirit of the present invention, the row of scope and consideration, and this will further determine in additional claim.
With reference to Fig. 4, in 100 the optimum scheme that realizes high pressure disjunctor gear drive of the present invention multistage (IGMS) centrifugal blower.
As shown in Figure 4, IGMS blower 100 of the present invention has impeller 112 tandems of several aluminium matter (perhaps steel) on same high speed gear shaft 114, and the axle two ends are supported by rolling bearing 116.Each grade is included in impeller 112, Diffuser 118 and the bend backflow canal device of installing on the high speed gear shaft 114 120 thereafter.
IGMS centrifugal blower 100 of the present invention contains a disjunctor gear speedup case 136, is driven by live axle 144 by standard motor (not showing).
The gear-box 136 of IGMS centrifugal blower of the present invention is the whole constituent element of blower 100, and the DDMS that outreaches gear-box with the configuration of routine compares, and the structure that it makes blower 100 compactness and cost more is lower.
The gear ratio of high pressure disjunctor gear-box multiple-stage centrifugal fan 100 of the present invention can be since 1.2: 1 until 2: 1 or 3: 1, so fast many of the DDMS of impeller 112 rotating ratio routines.The impeller speed that promotes has increased the pressure that impeller 112 is produced, and makes the blower pressure that reaches identical only need less progression.This causes the weight of blower 100 and reducing of size.
The high speed capability of high pressure disjunctor gear-box multiple-stage centrifugal fan 100 of the present invention can adopt the higher backward bending type impeller 112 of efficient to replace the lower radial mode impeller of traditional efficient to improve the efficient of blower.Simultaneously, use back ward impeller 112 can make the performance curve of blower fan more precipitous, when being connected, improved control ability with pipe-line system.
In order to adapt to 50 hertz power supply, IGMS centrifugal blower 100 of the present invention can be with a gear up ratio that is higher than 1.2 times of former rotating speeds, impeller speed can be brought up to and uses 60 hertz of levels that power supply is identical.Because the rotating speed of IGMS centrifugal blower is than low many of traditional IGSS blower, still can use the rolling bearing 116 and the simple splash-lubricating system 144 of standard, and the production method cheaply of traditional DDMS still can be used, and makes cost of production save more than the IGSS blower.
In addition, because the IGSS blower of the wheel speed of IGMS centrifugal blower 100 of the present invention and routine is more than low,, they do not produce very high noise the IGSS blower so can not resembling.
The present invention, another of high pressure IGMS centrifugal blower 100 important, critical feature is, its uses the sealing of axial impeller wheel cap, is the sealing of radial impeller wheel cap and traditional DDMS blower uses.
With reference to Fig. 5, show axial impeller wheel cap sealing 152, broach is on impeller 112.
With reference to Fig. 6, show axial impeller wheel cap sealing 152, broach is on cylinder body 126.
As illustrated in Figures 5 and 6, the enclosing cover for impeller sealing is axial, rather than in the traditional drum blower fan radially, like this, axially spaced-apart with radially by between at different levels the assembling integration interval and the caused motion of thermal expansion difference between aluminium matter impeller and the cast iron housing be independent of each other mutually.Therefore, the air blast function is using more progression to obtain under the situation of high pressure more, may the reducing on the contrary of the rubbing contact that it is potential.
Certainly, the present invention specially arrests and is limited to any special form or configuration, the perhaps form of any uniqueness, and perhaps any specific use, open at this.Because, do not separating with scope with above showing spirit with the invention of describing, device of showing or method only are in order to illustrate and disclose a kind of optimised form of realizing, rather than show the multi-form or change that all the present invention may be implemented or operate.
The present invention has described in detail one of them and has planted the best implementation of form.But detailed like this description does not specially limit the present invention feature or principle widely by any way.
Claims (11)
1. the centrifugal blower of a middling speed high pressure is characterized in that, which comprises at least:
A. comprise and between described import cylinder body and described outlet cylinder body, interconnect import cylinder body with vertical split surface and the housing structure that exports cylinder body by internal air passageway;
B. two-stage at least, each grade all has the centrifugal impeller that is contained on the same pinion shaft, flowing of the outlet of propellant gas from the import of above-mentioned import cylinder body to above-mentioned outlet cylinder body, thereby obtain the higher pressure or the lifting of pressure ratio, and described pinion shaft is supported via bearing at two ends by above-mentioned housing structure; And
C. between the enclosing cover for impeller of above-mentioned impeller and described housing structure, adopt axial enclosing cover for impeller sealing, with reduce internal leakage and unexpectedly mechanicalness contact.
2. blower as claimed in claim 1 is characterized in that described impeller is to be made from aluminum or a steel.
3. blower as claimed in claim 1 is characterized in that, described import cylinder body and outlet cylinder body are made by cast iron.
4. blower as claimed in claim 1 is characterized in that, described bearing is a rolling bearing.
5. blower as claimed in claim 1 is characterized in that, also further comprises a Diffuser in the level of each in described two-stage at least.
6. blower as claimed in claim 1 is characterized in that, also further comprises a bend backflow canal device in the level of each in described two-stage at least.
7. blower as claimed in claim 1 is characterized in that, also further comprises a splash-lubricating system.
8. blower as claimed in claim 1, it is characterized in that, further also comprise a disjunctor gear-box that is positioned at the axle head of above-mentioned pinion shaft, in this gear-box, have a gear train of having determined the gear ratio in advance right, in order to from live axle to above-mentioned pinion shaft conveying rotary motion.
9. blower as claimed in claim 8 is characterized in that, described gear ratio is between 1.2: 1 and 3: 1.
10. as claim 1 or 8 described blowers, it is characterized in that the broach that carries out described axial enclosing cover for impeller sealing is on impeller.
11., it is characterized in that the broach that carries out described axial enclosing cover for impeller sealing is on above-mentioned housing structure as claim 1 or 8 described blowers.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2005100911706A CN1912395B (en) | 2005-08-09 | 2005-08-09 | Middle-speed high-pressure multi-stage centrifugal blowing machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2005100911706A CN1912395B (en) | 2005-08-09 | 2005-08-09 | Middle-speed high-pressure multi-stage centrifugal blowing machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1912395A CN1912395A (en) | 2007-02-14 |
| CN1912395B true CN1912395B (en) | 2011-01-19 |
Family
ID=37721415
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2005100911706A Expired - Fee Related CN1912395B (en) | 2005-08-09 | 2005-08-09 | Middle-speed high-pressure multi-stage centrifugal blowing machine |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1912395B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102008057472B4 (en) * | 2008-11-14 | 2011-07-14 | Atlas Copco Energas GmbH, 50999 | Multi-stage radial turbocompressor |
| CN102400925A (en) * | 2010-09-18 | 2012-04-04 | 湖北省风机厂有限公司 | High pressure nitrogen circulating fan |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3756738A (en) * | 1971-10-22 | 1973-09-04 | Clarkson Ind Inc | Centrifugal pump with differential thermal expansion relief means |
| US4090813A (en) * | 1975-05-14 | 1978-05-23 | Hitachi, Ltd. | High-efficiency turbo-machine impellers |
| CN1041992A (en) * | 1988-09-14 | 1990-05-09 | 株式会社日立制作所 | Multistage centrifugal compressor |
| US5611663A (en) * | 1994-05-10 | 1997-03-18 | Man Gutehoffnungshutte Aktiengesellschaft | Geared multishaft turbocompressor and geared multishaft radial expander |
| CN2527755Y (en) * | 2001-12-07 | 2002-12-25 | 王凯 | Pressure centrifugal blower for transporting gas |
-
2005
- 2005-08-09 CN CN2005100911706A patent/CN1912395B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3756738A (en) * | 1971-10-22 | 1973-09-04 | Clarkson Ind Inc | Centrifugal pump with differential thermal expansion relief means |
| US4090813A (en) * | 1975-05-14 | 1978-05-23 | Hitachi, Ltd. | High-efficiency turbo-machine impellers |
| CN1041992A (en) * | 1988-09-14 | 1990-05-09 | 株式会社日立制作所 | Multistage centrifugal compressor |
| US5611663A (en) * | 1994-05-10 | 1997-03-18 | Man Gutehoffnungshutte Aktiengesellschaft | Geared multishaft turbocompressor and geared multishaft radial expander |
| CN2527755Y (en) * | 2001-12-07 | 2002-12-25 | 王凯 | Pressure centrifugal blower for transporting gas |
Non-Patent Citations (1)
| Title |
|---|
| JP平4-31700A 1992.02.03 |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1912395A (en) | 2007-02-14 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104179712B (en) | A kind of air suspension centrifugal blower | |
| CN2773358Y (en) | High-speed magnetic-suspension centrifugal blower | |
| CN104564717B (en) | Direct driven high-speed turbine vacuum pump and operation method thereof | |
| CN101988511B (en) | Pipeline shielding structural electric pump working in manner of internal circulation | |
| CN201461439U (en) | Pipeline shielding electric pump with internal circulation structure | |
| CN105485022A (en) | Sectional type multi-stage centrifugal pump and adjustable guide vane devices thereof | |
| CN105351206A (en) | Segmentation type multi-stage centrifugal pump | |
| US6935838B1 (en) | High pressure multi-stage centrifugal blower | |
| CN1912395B (en) | Middle-speed high-pressure multi-stage centrifugal blowing machine | |
| CN201982337U (en) | High-speed centrifugal blower | |
| CN201896763U (en) | Compressor | |
| CN1789727A (en) | High-pressure multistage centrifugal blower | |
| CN216077624U (en) | Multistage compressor adopting magnetic planetary rotor shafting for speed increase | |
| CN113294359B (en) | High-performance single-side double-impeller magnetic levitation high-speed direct-drive turbine compressor and working mechanism | |
| CN107605765A (en) | Centrifugal blower | |
| CN101922461A (en) | Double-impeller centrifugal blower | |
| CN107781176A (en) | A kind of stacked Multi-layer centrifugal formula blower fan | |
| CN204003584U (en) | A kind of air suspension centrifugal blower | |
| KR102036201B1 (en) | Turbo Compressor | |
| CN207960981U (en) | Centrifugal supercharger device | |
| CN201650801U (en) | Double-impeller centrifugal blower | |
| CN113819077A (en) | Magnetic suspension air blower with single-stage double-suction and double stator and rotor | |
| KR20190122608A (en) | Turbo Compressor | |
| CN206830475U (en) | A kind of centrifugal type oxygen tympanites blower fan | |
| CN110761844A (en) | High-efficiency steam turbine |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20110119 Termination date: 20150809 |
|
| EXPY | Termination of patent right or utility model |