CN105518307A - Centrifugal rotor - Google Patents
Centrifugal rotor Download PDFInfo
- Publication number
- CN105518307A CN105518307A CN201480042093.2A CN201480042093A CN105518307A CN 105518307 A CN105518307 A CN 105518307A CN 201480042093 A CN201480042093 A CN 201480042093A CN 105518307 A CN105518307 A CN 105518307A
- Authority
- CN
- China
- Prior art keywords
- flange
- centrifugal rotor
- passage
- longitudinal axis
- centrifugal
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/24—Vanes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/2261—Rotors specially for centrifugal pumps with special measures
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/08—Centrifugal pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/2205—Conventional flow pattern
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/2261—Rotors specially for centrifugal pumps with special measures
- F04D29/2272—Rotors specially for centrifugal pumps with special measures for influencing flow or boundary layer
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/30—Vanes
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
This centrifugal rotor (2) comprises: a hub (10) having a longitudinal axis (8), a fluid inlet (20), a first flange referred to as upstream flange (12) and having an opening (22) around the hub (10), a second flange referred to as downstream flange (14) separated from the first flange by blades (16) thus forming ducts each delimited by the first flange (12), the second flange (14) and two blades (16) and extending from the fluid inlet (20) to a peripheral outlet (26), near the peripheral outlet (26) the first flange (12) having a concave zone (32) facing towards the ducts whereas the second flange (14) itself has a convex zone (34) facing towards the ducts.
Description
Invention field
The present invention relates to a kind of centrifugal rotor.
Technical field of the present invention is the field of fluid, liquid or gas compression.Therefore the present invention relates to the pump and the compressor both that make liquid or gas supply source may become more high pressure respectively from setting pressure.
Background technique
There is many technology for increasing hydrodynamic pressure.Common technology is that the fluid to pressure is applied in thereon carries out centrifugal, and this causes its pressure to increase then.For the enforcement of this technology, depend on the many parameters comprising associated fluid, environment (size etc.) and desired performance (compressibility etc.), there is many different pumps and compressor arrangement.Subsequently, the pump and compressor that comprise at least one centrifugal rotor associated with axial diffusion device will be concentrated on.
Centrifugal rotor is the rotor with spin axis.It is designed to be compressed in the fluid flowed in the direction with its rotation axis parallel, and compressed fluid outwards leaves rotor in radial directions.When the necessary axial flow of compressed fluid, a solution guides the fluid leaving rotor to change flow direction to make its.Element for this object is the standing part being called axial diffusion device, and it has at least one conduit for guiding compressed fluid.The downstream end of conduit, namely away from the end of centrifugal rotor, come axially directed according to the direction of desired guiding compressed fluid.The object of axial diffusion device be make subsequently from centrifugal rotor fluid out turn about 90 ° axially to guide it.
Document FR-2874241 discloses a kind of efficient centrifugal rotor with the use tack blade of radial diffuser.The wake flow of blade is reclosed (reclose) in diffuser, and is formed in the stratified flow expanded gradually in diffuser by working together with the wake flow of other adjacent blades.Therefore in this document, a kind of rotor in conjunction with diffuser is found.Very thick blade is arranged in the low portion of rotor.
US-1,447,916 another embodiments that the rotor in conjunction with diffuser is shown.Diffuser can be single piece with the rotor portion comprising blade, or it can be the separation member being fixed to the rotor portion comprising blade.But should point out, in all figure that wheel blade is shown, they only extend and do not extend to the periphery output terminal of device on a part for device (corresponding to centrifugal rotor), and should point out, the part corresponding to centrifugal rotor has the outlet of the complete radial direction being positioned at diffuser upstream.
The technical problem that this structure runs into is that it is the root of the pressure loss in compressed fluid.In fact when the fluid is flowing known, it experiences the pressure loss, and the pressure loss depend on fluid existing in pipeline, comprise experienced any direction and change.
It is impossible for eliminating the pressure drop relevant especially with the character of fluid itself (specifically its viscosity), but the present invention will provide the device minimizing these as much as possible and lose.
Summary of the invention
Therefore, target of the present invention comprises centrifugal rotor and axial diffusion device to increase the performance of this one-level for given compression stage, namely such as obtain more high compression ratio for given power or for given compression, thus minimizing needs to be applied on rotor with the mechanical output making it rotate.
For this reason, the present invention proposes a kind of centrifugal rotor, and it comprises:
-wheel hub, it has longitudinal axis,
-fluid input,
-the first flange, it is positioned at wheel hub upstream and has the opening around wheel hub,
-the second flange, it is positioned at the first flange downstream, is separated with the first flange by wheel blade, thus the passage forming each freedom first flange, the second flange and limit from two wheel blades that fluid input extends to perimeter outlet.
According to the present invention, near perimeter outlet, the first flange has the concave regions towards passage orientation, and the second flange has towards the convex region of passage orientation.
Owing to therefore giving the form of outlet passage, the radial flow in centrifugal rotor is transformed into the axial flow in the diffuser of rotor upstream in too not rude mode, thus pressure loss when making likely limit fluid change direction.
In order to have the rotor being easy to manufacture, it is round-shaped that the first flange and the second flange advantageously have around longitudinal axis.
Such as, it is contemplated that tangent with the concave regions of the first flange leaving channel surface, and be formed in the angle of (preferably between 10 and 30) between 1 ° and 45 ° perpendicular to the radial plane of longitudinal axis.Similarly, it is contemplated that tangent with the convex region of the second flange leaving channel surface, and be formed in the angle of (preferably between 10 and 30) between 1 ° and 45 ° perpendicular to the radial plane of longitudinal axis.
In order to guide according to the fluid in centrifugal rotor of the present invention better, advantageously suppose that wheel blade extends to the outer periphery outward edge of the first flange and/or the second flange.
In order to easily make the fluid leaving centrifugal rotor accelerate, the first flange advantageously has the outer peripheral edge of adjacent channel, and described outer peripheral edge has larger diameter compared with the outer peripheral edge of the passage of contiguous second flange.Corresponding to give centrifugal rotor outlet curved shape outside the edge with larger diameter, speed is therefore higher.This is preferred, because the path will advanced along outside of turning is larger compared with turning medial.In this way, when fluid moves up in substantially longitudinal side subsequently, promote speed evenly distribution.
The invention still further relates to a kind of centrifugal compressor and/or the centrifugal pump that comprise centrifugal rotor as above.
Accompanying drawing explanation
Details of the present invention and advantage will become more obvious from the description carried out below with reference to accompanying drawing, wherein:
Fig. 1 illustrates the centrifugal rotor of prior art with the sectional view installing half rotor within the compressor,
Fig. 2 is the view of the centrifugal rotor according to first embodiment of the invention similar with Fig. 1 view,
Fig. 3 is the view according to second embodiment of the invention similar with previous figures, and
Fig. 4 is the perspective cross-sectional view of the line of cut IV-IV along Fig. 2.
Embodiment
Those skilled in the art will recognize in Fig. 1 the centrifugal rotor 2 being arranged on shell 4 (such as, compressor case) inside, and have the axle 6 of longitudinal axis 8.Below describe and carry out with reference to control air compressor (or more generally, gaseous fluid compressor), but the present invention also can be applicable to liquor pump.
When making centrifugal rotor 2 rotate by axle 6, air (or other gaseous fluids) is sucked in centrifugal rotor 2 relative to longitudinal axis 8 in a longitudinal direction, and be driven in centrifugal rotor 2 and carry out mixed flow motion, rotate simultaneously and be rendered as relative to longitudinal axis 8 radial.
Centrifugal rotor 2 is built into single type and comprises wheel hub 10, first flange or upstream flange 12, second flange or downstream flange 14 and wheel blade 16.
Wheel hub 10 realizes the connection between axle 6 and centrifugal rotor 2.It has shape that is overall circular, columniform, tubulose, and is provided with the device for it being fastened to axle 6.Such as, cannelure is set usually in wheel hub 10 and axle 6 to receive the connection of longitudinal spline or even groove or any other type.
Downstream flange 14 is directly connected to wheel hub 10, and extends relative to longitudinal axis 8 radial direction.Upstream/downstream direction limits relative to the airflow direction in centrifugal rotor 2.In fact, in FIG (and in other figure), after back leaving centrifugal rotor 2 towards the left side of figure in a longitudinal direction, air is sucked into the right of rotor, and be longitudinally moved to the left subsequently, driven in the radial direction the most directed afterwards.Therefore, in the drawings, upstream element is disposed in the right of downstream components.
Upstream flange 12 flange 14 and being connected thereto by wheel blade 16 for the downstream, thus the passage of air is defined between two flanges.Therefore air is introduced between the internal surface of flange and wheel blade in centrifugal radial mode.
Upstream flange 12 does not extend to wheel hub 10, but with its maintenance certain distance.Above, stuffing box bearing 18 is towards wheel hub 10.Towards the inner side of centrifugal rotor 2, front stuffing box bearing 18 limits the suction chamber 20 with annular opening 22 together with wheel hub 10, and annular opening 22 is in the upstream of suction chamber 20.Towards the outside, front stuffing box bearing 18 machined to make it to work as and to rotate in shell 4 time form the Sealing of centrifugal rotor 2.Such as, Sealing, all like labyrinth rings 24 can be used as the interface between centrifugal rotor 2 and shell 4.As can be seen in the figures, on downstream side, centrifugal rotor 2 also comprises and to extend from downstream flange 14 and to receive the other stuffing box bearing 18 of another labyrinth ring 24 or rear stuffing box bearing.
The passage of the driving air between upstream flange 12 and downstream flange 14 has the outlet 26 (Fig. 1) of the maximum diameter place radial directed at flange separately.Air enters diffuser 28 subsequently, and in diffuser 28, air is guided to make air-flow be more longitudinal and non-static fields.Passage 30 in diffuser 28 also makes likely to convert the spiral motion of air-flow to substantially straight motion.
Fig. 2 and 4 illustrates the first embodiment according to centrifugal rotor of the present invention.As shown in the figure, in Fig. 1 and Fig. 2 to 4, general structure is substantially the same.Therefore, the reference symbol in Fig. 1 is used in reference to like in Fig. 2 to 4.Therefore the centrifugal rotor 2 be rotatably installed in around the axle 6 with longitudinal axis 8 in shell 4 is found.In particular by the stuffing box bearing 18 worked together with labyrinth ring 24 (or Sealing of other types), centrifugal rotor 2 relative to shell 4 by sealed-off, protected thus.The connection that wheel hub 10 such as realizes between rotor and axle 6 by means of unshowned spline.Centrifugal rotor 2 also comprises the upstream flange 12 and downstream flange 14 that are interconnected by wheel blade 16.Upstream flange 12 has stuffing box bearing 18, and stuffing box bearing 18 limits the suction chamber 20 with annular opening 22 together with wheel hub 10.In addition, when centrifugal rotor 2 rotates around longitudinal axis 8, air (or other fluids) is sucked by opening 22 (longitudinal suction) to be compressed in spiral centrifugal motion, again to become portrait orientation subsequently in the diffuser 28 being optionally provided with passage.
The rotor of prior art and be located substantially on output terminal 26 place according to the difference between centrifugal rotor 2 of the present invention, that is at the region place with maximum diameter of upstream flange 12, downstream flange 14 and wheel blade 16.
Compared with the centrifugal rotor of compressor well known in the prior art (or pump), the present invention's suggestion is provided for the outlet of the air-flow (or other fluids) in centrifugal rotor, and it is entered in longitudinal diffusion device with the velocity vector improved.For this purpose, desired is that air passageways will near outlet 26 place's slight bending (being limited by flange and wheel blade) in centrifugal rotor 2.Therefore produce curved section at the output of centrifugal rotor, curved section makes likely to increase air towards the speed outside curved section.
Although notice that the inner face of upstream flange 12 and the surface of downstream flange 14 are planes (and slight assemble) substantially in the implementation of figure 1, but the internal surface of upstream flange 12 has concave regions 32 near output terminal 26, and the internal surface of downstream flange 14 has the convex region 34 relative with concave regions 32 near outlet 26.
If consider on the tangent surface 36 of the internal surface of outlet 26 place and downstream flange 14 subsequently, this surface be substantially conical (the circular cone axis of longitudinal axis 8) and with radial plane angulation a shown by dashed lines.In the embodiment of fig. 2, this angle is about 15 °, and in the embodiment of Fig. 3, this angle is about 30 °.Preferably, this angle will be included between 10 ° and 45 °.In the centrifugal rotor of prior art, as illustrated by fig. 1, this angle is essentially 0.
In order to avoid making figure transship, the not shown surface tangent with the internal surface of upstream flange 12.Also find the substantially conical surface around longitudinal axis 8 herein, this surface and shown radial plane form the angle being preferably less than 45 ° (such as, between 10 and 45 °).
Fig. 4 illustrates that wheel blade 16 extends in the convex region 34 of downstream flange 14.Certainly, they extend in the concave regions 32 of upstream flange 12 in a similar fashion.Preferably, as shown in this Fig. 4, wheel blade 16 extends the periphery edge of upstream flange 12 and downstream flange 14, that is extends to the output terminal 26 of rotor.
In figure 3, the line with maximum diameter of the internal surface of downstream flange 14 is referred to by H, and the line with maximum diameter of the internal surface of upstream flange 12 is referred to by S.S and H is the circle that the center of circle is positioned on longitudinal axis 8, and radius is respectively R
sand R
h.As from Fig. 3 significantly (this also shows in fig. 2, but slightly less obvious), R
s>R
h.Therefore, for the identical mean speed on the air outlet slit surface outside centrifugal rotor 2, the periphery speed of the air near some S is greater than the periphery speed of the air near a H.This is also applicable to absolute tangential velocity.Air is accelerated (outside the leaving of rotor " turning ") from upstream side, thus air may be had at the input end of substantially longitudinal area segments of diffuser evenly speed.Therefore, as long as in diffuser, the pressure loss is just reduced, and therefore makes the output likely increasing device.
Therefore allow more gently to be transitioned into longitudinal flow from radial air flow according to the shape of centrifugal rotor of the present invention.By the liquid speed of the passage region section of diffuser be more evenly distributed and regular.Therefore, when when it flow in axial diffusion device, basically radial flow is transformed into axial flow to fluid, pressure drop is limited, and obtains gain in output.
Notice that the passage in centrifugal rotor 2 has path, in described path, stream is radial substantially.The internal surface of upstream flange and downstream flange has bending inverting (inversionofcurvature) separately.The internal surface of upstream flange 12 has convex region near suction chamber 20, and it extends from wheel hub 10 subsequently, and after bending area, described internal surface has concave regions as above.The internal surface of upstream flange 14 has convex region near suction chamber 20, and it extends from wheel hub 10 subsequently, and after bending area, described internal surface has concave regions as above.Fluid track is in the channel limited by the flange in centrifugal rotor 2 and wheel blade and therefore has curve.
In order to guide the fluid in bending rotor better, wheel blade 16 extends in bending area (that is extend to the concave regions of the internal surface of upstream flange and extend to the convex region of the internal surface of downstream flange) and preferably fluid is directed into outlet 26.Therefore blade 16 is also bending.They preferably extend to line H and line S from suction chamber 20, or such as extend near these lines (at least extending to apart within these lines 10mm).
Certainly, the invention is not restricted to the above preferred embodiment described as limiting examples, but the variant in it also relates to reached by those skilled in the art scope.
It is also imagined the variant of the embodiment found within the scope of the professional skill of related domain in following claims framework.
Claims (10)
1. a centrifugal rotor (2), it comprises:
-wheel hub (10), it has longitudinal axis (8),
-fluid input (20),
-the first flange (12), it is positioned at described wheel hub (10) upstream and has the opening (22) around described wheel hub (10),
-the second flange (14), it is positioned at described first flange downstream, is separated with described first flange by wheel blade (16), thus the passage forming described first flange of each freedom (12), described second flange (14) and limit from two wheel blades (16) that described fluid input (20) extends to perimeter outlet (26)
It is characterized in that, near described perimeter outlet (26), described first flange (12) has the concave regions (32) towards described passage orientation, and described second flange (14) has towards the convex region (34) of described passage orientation.
2. centrifugal rotor according to claim 1, is characterized in that, it is round-shaped that described first flange (12) and described second flange (14) have around described longitudinal axis.
3. according to the centrifugal rotor in claim 1 or 2 described in, it is characterized in that, the surface that the described concave regions leaving described passage with described first flange (12) is tangent, and be formed in the angle between 1 ° and 45 ° perpendicular to the radial plane of described longitudinal axis (8).
4. centrifugal rotor according to claim 3, is characterized in that, with described first flange leave the described concave regions of described passage tangent described surperficial 36, and be formed in the angle between 10 ° and 30 ° perpendicular to the radial plane of described longitudinal axis.
5. according to the centrifugal rotor in Claims 1-4 described in, it is characterized in that, leave the tangent described surface (36) of the described convex region (34) of described passage with described second flange (14), and be formed in the angle between 1 ° and 45 ° perpendicular to the radial plane of described longitudinal axis (8).
6. centrifugal rotor according to claim 5, it is characterized in that, leave the tangent described surface (36) of the described convex region (34) of described passage with described second flange (14), and be formed in the angle between 10 ° and 30 ° perpendicular to the radial plane of described longitudinal axis (8).
7. according to the centrifugal rotor in claim 1 to 6 described in, it is characterized in that, described wheel blade (16) extends to the periphery edge (H, S) of described first flange (12) and/or described second flange (14) outside.
8. according to the centrifugal rotor in claim 1 to 7 described in, it is characterized in that, described first flange (12) has the outer peripheral edge (S) of contiguous described passage, the diameter (R of described outer peripheral edge (S)
s) be greater than the diameter (R of the outer peripheral edge (H) of the described passage of contiguous described second flange (14)
h).
9. a centrifugal compressor, is characterized in that, it comprises according to the centrifugal rotor (2) described in claim 1 to 8.
10. a centrifugal pump, is characterized in that, it comprises according to the centrifugal rotor (2) in claim 1 to 8 described in.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| FR1355696 | 2013-06-18 | ||
| FR1355696A FR3007086B1 (en) | 2013-06-18 | 2013-06-18 | CENTRIFUGAL WHEEL |
| PCT/FR2014/051512 WO2014202903A1 (en) | 2013-06-18 | 2014-06-18 | Centrifugal rotor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN105518307A true CN105518307A (en) | 2016-04-20 |
Family
ID=48980150
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201480042093.2A Pending CN105518307A (en) | 2013-06-18 | 2014-06-18 | Centrifugal rotor |
Country Status (9)
| Country | Link |
|---|---|
| US (1) | US20160146215A1 (en) |
| EP (1) | EP3011185B1 (en) |
| JP (1) | JP2016522357A (en) |
| KR (1) | KR20160021229A (en) |
| CN (1) | CN105518307A (en) |
| CA (1) | CA2915720C (en) |
| FR (1) | FR3007086B1 (en) |
| RU (1) | RU2015154050A (en) |
| WO (1) | WO2014202903A1 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2944060B1 (en) * | 2009-04-06 | 2013-07-19 | Turbomeca | SECONDARY AIR SYSTEM FOR CENTRIFUGAL OR MIXED COMPRESSOR |
| JP5705945B1 (en) * | 2013-10-28 | 2015-04-22 | ミネベア株式会社 | Centrifugal fan |
| DE102013018286A1 (en) * | 2013-10-31 | 2015-04-30 | Man Diesel & Turbo Se | centrifugal compressors |
| US10533568B2 (en) * | 2017-10-30 | 2020-01-14 | Daikin Applied Americas Inc. | Centrifugal compressor with seal bearing |
| EP3916238A4 (en) * | 2019-01-21 | 2022-01-19 | Mitsubishi Electric Corporation | Fan blower, indoor unit, and air conditioner |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1447916A (en) * | 1920-12-18 | 1923-03-06 | American Blower Co | Centrifugal fan |
| CN1032063A (en) * | 1987-09-17 | 1989-03-29 | Ksb股份公司 | Centrifugal pump impeller |
| RU2197644C1 (en) * | 2001-07-30 | 2003-01-27 | Открытое акционерное общество "Татнефть" | Centrifugal pump impeller |
| FR2874241A1 (en) * | 2004-08-16 | 2006-02-17 | Max Sardou | Centrifugal impeller for pump and centrifugal blower, has hub and ring including trailing edge radii greater than trailing edge radii of truncated blade for closing of slipstream and detent of circulating fluid |
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| US2543923A (en) * | 1948-04-13 | 1951-03-06 | Ward T Mixsell | Radial air compressor |
| US3850550A (en) * | 1971-08-05 | 1974-11-26 | Hydr O Matic Pump Co | Centrifugal pump and motor |
| GB1383420A (en) * | 1971-09-22 | 1974-02-12 | Torin Corp | Blower assembly |
| CH562964A5 (en) * | 1973-03-23 | 1975-06-13 | Saurer Ag Adolph | Centrifugal pump with flow deflecting rim - suitable for central heating plant, cavitation noise is almost eliminated |
| JPS5817358B2 (en) * | 1978-03-07 | 1983-04-06 | 川崎重工業株式会社 | Multi-stage turbo compressor |
| JPS57137689A (en) * | 1981-02-18 | 1982-08-25 | Matsushita Electric Ind Co Ltd | Blower |
| JPS59111989U (en) * | 1983-01-18 | 1984-07-28 | 松下電器産業株式会社 | Axial gap type motor pump |
| JPS61101698U (en) * | 1984-12-10 | 1986-06-28 | ||
| JPH0718434B2 (en) * | 1991-09-02 | 1995-03-06 | 株式会社クラコ | Fan and oil mist removing device using fan |
| JP3373012B2 (en) * | 1993-10-21 | 2003-02-04 | 株式会社荏原製作所 | Operation control device for turbo type fluid machinery |
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| JP2006289045A (en) * | 2005-04-14 | 2006-10-26 | Masayoshi Furuichi | Motor fan |
| JP4502057B2 (en) * | 2008-09-29 | 2010-07-14 | ダイキン工業株式会社 | Indoor unit of floor type air conditioner |
| GB2467968B (en) * | 2009-02-24 | 2015-04-22 | Dyson Technology Ltd | Centrifugal compressor with a diffuser |
| US8668446B2 (en) * | 2010-08-31 | 2014-03-11 | General Electric Company | Supersonic compressor rotor and method of assembling same |
| FR2975733B1 (en) * | 2011-05-23 | 2015-12-18 | Turbomeca | CENTRIFUGAL COMPRESSOR WHEEL |
| JP2013072360A (en) * | 2011-09-28 | 2013-04-22 | Panasonic Corp | Electric air blower and vacuum cleaner |
-
2013
- 2013-06-18 FR FR1355696A patent/FR3007086B1/en not_active Expired - Fee Related
-
2014
- 2014-06-18 KR KR1020167000966A patent/KR20160021229A/en not_active IP Right Cessation
- 2014-06-18 CA CA2915720A patent/CA2915720C/en active Active
- 2014-06-18 JP JP2016520722A patent/JP2016522357A/en active Pending
- 2014-06-18 CN CN201480042093.2A patent/CN105518307A/en active Pending
- 2014-06-18 WO PCT/FR2014/051512 patent/WO2014202903A1/en active Application Filing
- 2014-06-18 EP EP14737288.2A patent/EP3011185B1/en active Active
- 2014-06-18 RU RU2015154050A patent/RU2015154050A/en unknown
- 2014-06-18 US US14/898,239 patent/US20160146215A1/en not_active Abandoned
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1447916A (en) * | 1920-12-18 | 1923-03-06 | American Blower Co | Centrifugal fan |
| CN1032063A (en) * | 1987-09-17 | 1989-03-29 | Ksb股份公司 | Centrifugal pump impeller |
| RU2197644C1 (en) * | 2001-07-30 | 2003-01-27 | Открытое акционерное общество "Татнефть" | Centrifugal pump impeller |
| FR2874241A1 (en) * | 2004-08-16 | 2006-02-17 | Max Sardou | Centrifugal impeller for pump and centrifugal blower, has hub and ring including trailing edge radii greater than trailing edge radii of truncated blade for closing of slipstream and detent of circulating fluid |
Also Published As
| Publication number | Publication date |
|---|---|
| EP3011185B1 (en) | 2020-11-04 |
| RU2015154050A (en) | 2017-07-19 |
| CA2915720C (en) | 2021-09-07 |
| CA2915720A1 (en) | 2014-12-24 |
| KR20160021229A (en) | 2016-02-24 |
| RU2019113490A3 (en) | 2022-01-14 |
| EP3011185A1 (en) | 2016-04-27 |
| JP2016522357A (en) | 2016-07-28 |
| FR3007086A1 (en) | 2014-12-19 |
| FR3007086B1 (en) | 2015-07-03 |
| WO2014202903A1 (en) | 2014-12-24 |
| RU2019113490A (en) | 2019-06-04 |
| US20160146215A1 (en) | 2016-05-26 |
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