CN101619727A - Vortex flow fan - Google Patents
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- CN101619727A CN101619727A CN200910005754A CN200910005754A CN101619727A CN 101619727 A CN101619727 A CN 101619727A CN 200910005754 A CN200910005754 A CN 200910005754A CN 200910005754 A CN200910005754 A CN 200910005754A CN 101619727 A CN101619727 A CN 101619727A
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Abstract
Provided is a vortex flow fan capable of reducing noises. The vortex flow fan is provided with a housing (12) with a circular arc shape still flow path (20) and an impeller (14) with several vanes (17) corresponding with the still flow path (17), the housing (12) is provided with an inlet flow path (21) communicated with one end of the still flow path and an outlet flow path (20) communicated with the other end of the still flow path (20). An inlet side guide surface (25) for forming one end face of the still flow path (20) and an outlet side guide surface (26) for forming the other end face of the still flow path (20) are provided with diffused reflection parts (30a, 30b) separately. The diffused reflection parts (30a, 30b) make the noises of the wind in the still flow path (20) to have a diffused reflection so as to prevent a resonance phenomenon of the still flow path (20).
Description
Technical field
The present invention relates to utilize the impeller rotation continuously air to be given the turbo-fan of kinetic energy and force feed air.
Background technique
Turbo-fan---be that the eddy current gas fan has the housing that is formed with circular-arc static stream and is provided with the impeller of multi-disc blade accordingly in a circumferential direction every the interval of regulation with this static stream, the impeller rotation is mounted freely on the housing.Housing is provided with suction passage that is communicated with an end of static stream and the discharge stream that is communicated with the other end of static stream.When impeller rotates, carry out following two processes repeatedly from the suction passage leaked-in air, that is: the blade of impeller flowed into the static stream from interior circumferential periphery speedup each other and in static stream, be directed slowing down to circumferencial direction, the process of supercharging, and flow into blade process each other once more, flow into air and given kinetic energy and pressurized repeatedly by impeller.Air after the pressurization is discharged to the outside by discharging stream.On the housing with the next door of separating between blade is provided with static stream two ends mutually opposed to each other, with this next door the suction passage and the opening portion by impeller one side of discharging stream are separated, suction passage directly is not communicated with the discharge stream.
The turbo-fan of this structure is compared with centrifugal blower, can improve the pressure coefficient of the merit of expression impeller per unit external diameter, can miniaturization and, therefore be widely used as the less air power source of Capacity Ratio in the general industrial machinery.As the use form of turbo-fan, use is arranged from the situation of the positive pressure air of discharge stream discharge and the situation of the negative pressure of using suction passage to produce.For example, when using turbo-fan, use positive pressure air for the smear metal of eliminating lathe, when using turbo-fan in order to adsorb the carrying workpiece, the negative pressure air that uses suction passage to produce.
As such turbo-fan, the wheel cap (shroud) with the annular slot that is provided with opposed to each other mutually with static stream that has No. 2680136 communique of Japan Patent to put down in writing is taken turns the multi-disc blade that covers is along the circumferential direction separated annular slot every the interval of regulation type with being arranged on.And turbo-fan also has the type that also forms static stream on the inner face that is installed in the cap on the housing by impeller of Japanese kokai publication hei 4-228899 communique record.As the form of blade, there are straight line type that the straight radial direction along impeller of blade extends and the inner face that makes blade crooked and make the top end of blade radially crooked along sense of rotation, bending blade is become the flexure type of 3D shape etc.
In the turbo-fan, the noise that produces when suppressing to drive is very important solution problem.The wind noise that the mobile noise that the frequency ratio that the noise of turbo-fan has sinuous flow to produce is lower and the blade of impeller and next door interfere the pressure oscillation of generation to cause.The wind noise has by the number of blade and multiply by the frequency characteristic that the noise of the high secondary frequencies of the frequency of rotating speed and integral multiple thereof constitutes, and compares with above-mentioned mobile noise, and noise level is bigger, therefore in order to reduce the noise of turbo-fan, must reduce the wind noise.Thought in the past that the mechanism that the wind noise produces was that the pressure interference in blade and next door causes pressure oscillation, sounds thus.
Therefore, in order to reduce the wind noise, proposed at suction passage and discharged in the stream friction type shock absorber that has used sound absorbing material is set for turbo-fan before this, for the effective various sympathetic response type shock absorbers of wind noise that reduce characteristic frequency.In the turbo-fan of patent documentation 2 record, by suction passage and discharge stream by the inner face of the opening portion of impeller one side or next door on the configuration sound absorbing material reduce the wind noise.
In the turbo-fan of patent documentation 1 record, reduce noise, make the guide portion inclination of suction passage one side leave the impeller outer perimembranous and interfere with blade for its top by setting on the next door and suction passage and the opposed guide portion of opening portion of discharging stream; The guide portion of discharging stream one side is tilted leave in the impeller perimembranous and interfere with blade for its top.Thus, make to flow into the air flows in the static stream and flow to the air flows of discharging stream in the static stream to become smooth and easy, reduce the noise that produces from suction passage.Thus and thus, in the past, perhaps time of the pressure oscillation that causes by the interference that makes the top end that is arranged on the guide portion on the next door tilt to prolong blade and next door, pressure is gradually changed, perhaps to the high noise of the frequency that produced, utilize sound absorbing material or sympathetic response type shock absorber to make sound attenuating, implement to reduce the noise of turbo-fan, quiet countermeasure, but reduce limited the noise of turbo-fan.Especially the problem that has the dominant frequency that can not reduce the wind noise.
In order to probe into its reason, carried out making the pure tone of single-frequency in the circular-arc static stream of turbo-fan, to flow, between suction passage one side and discharge stream one side, move the experiment that MIC microphone is collected sound along static stream.The result is to have detected the neat up and down waveform of clearly distinguishing antinode and node of amplitude under characteristic frequency.When making the frequency pure tone different with this frequency flow through in the static stream, the amplitude that has become waveform is irregular up and down, can't distinguish the antinode of waveform and the state of node.As a result, can think that the sound of characteristic frequency and static stream have produced the sympathetic response on the sound.
On housing, to have formed in order guiding swimmingly and to have flowed into the air of an end of static stream and crooked suction side guide surface from suction passage, and to have formed in order guiding swimmingly from the other end of static stream and to be discharged to the air of discharging the stream and side directed of crooked discharge, each guide surface forms the end face of circular-arc static stream respectively.Therefore can think that static stream has and is provided with the gas column of two end faces or the resonance frequency of pipeline equivalence.The resonance frequency of pipeline is the reflected wave phase place of coming when the progressive wave of sound and end face reflection from pipeline when consistent and overlapping, and waveform does not advance, and appears to the waveform that stops at the state that the there vibrates, and is called standing wave.Because standing wave is the overlapping ripple of ripple of same phase, therefore to compare with original waveform, the amplitude of expression acoustic pressure is exaggerated.So, can think when the sound that produces in the pipeline and the resonance frequency of pipeline be standing wave when consistent, sound is exaggerated.Because suction passage and discharge stream and be arranged on opposed to each other mutually on the housing with the guide surface that becomes reflective surface respectively, so the sound that has amplified emits to the outside with regard to former state.
About the frequency of standing wave, when stream is the straight such plane wave of straight tube during perpendicular to surface feeding sputtering, can think that sound field is an one dimension, therefore, the frequency resonance frequency of standing wave is tried to achieve with following formula during the end face seal of pipeline.That is, when the hypothesis velocity of sound is the length of C, straight tube when being L, the frequency f of standing wave is f=(2m-1) C/ (4L).M is an integer in the formula.
The static stream that makes turbo-fan forms the shape of pipeline for crooked circular-arc stream, and sound reflection takes place at the flexure plane place that forms static stream both ends of the surface, can think the same standing wave that exists with straight tube.For the dominant frequency that makes the wind noise and the resonance frequency of static stream are provided with turbo-fan inconsistently, the static flow path length of being determined by the diameter of impeller, the rotating speed of the impeller of determining dominant frequency and the number of blade of impeller become variable.Therefore, if always with certain rotating speed drives impeller, the frequency of wind noise and the resonance frequency of pipeline are staggered.
But owing to changing rotating speed ground and control in order to make turbo-fan be optimized running, so the frequency of wind noise not necessarily.And the working principle of turbo-fan is to utilize the shearing force of fluid to boost, and therefore owing to the increase of working fluid frictional heat, the temperature of fluid also rises, and temperature rises velocity of sound is increased, and then wavelength is elongated, and the resonance frequency of static stream also changes.Therefore be difficult to the advantage noise under all running statees of shock absorber or quieter material reduction use turbo-fan.
Summary of the invention
This turbo-fan is exactly illustrating of the mechanism that produces according to above-mentioned noise, distinguishes by preventing that resonance phenomenon that static stream that the wind noise causes produces from can reduce the invention that this situation of noise of turbo-fan is made.
Therefore, the objective of the invention is to provide a kind of turbo-fan that can reduce noise.
Turbo-fan of the present invention, have housing and impeller, this housing is provided with circular-arc static stream, this impeller and above-mentioned static stream are provided with the multi-disc blade every the interval of regulation accordingly in a circumferential direction, and, it is characterized in that this turbo-fan has: suction passage by motoring, be arranged on communicatively on the above-mentioned housing with an end of above-mentioned static stream, with air from exterior guiding to above-mentioned static stream; Discharge stream, be arranged on communicatively on the above-mentioned housing, forced air is directed to the outside from above-mentioned static stream with the other end of above-mentioned static stream; And diffuse reflection portion, on any one face at least in being arranged on the suction side guide surface and discharging side directed, this suction side guide surface form end face of above-mentioned static stream and with air from above-mentioned suction passage guiding to above-mentioned static stream, this discharge side directed form another end face of above-mentioned static stream and with air from above-mentioned static stream guiding to above-mentioned discharge currents road.
Description of drawings
By the description below in conjunction with accompanying drawing, above-mentioned and other feature of the present invention, purpose and advantage will become more obvious.Among the figure:
Fig. 1 is the broken section perspective view of the turbo-fan of expression an embodiment of the invention.
Fig. 2 is the longitudinal section of the part of expression turbo-fan shown in Figure 1.
Fig. 3 is the 3-3 line sectional view of Fig. 2.
Fig. 4 (A) is the front view of the inner face of expression impeller, and Fig. 4 (B) is the front view of expression impeller variation.
Fig. 5 (A) is the sectional view of the 5A-5A line of Fig. 4 (A), and Fig. 5 (B) is the 5B-5B line sectional view among Fig. 4 (B), and Fig. 5 (C) is the sectional view of the variation of expression blade.
Fig. 6 is the 6-6 line amplification view among Fig. 3.
Fig. 7 (A) is the 7A-7A line sectional view among Fig. 6, and Fig. 7 (B) is the 7B-7B line sectional view among Fig. 6, and Fig. 7 (C) is the 7C-7C line sectional view among Fig. 6.
Fig. 8 is the sectional view of the variation of expression diffuse reflection portion.
Fig. 9 carries out the schematic representation of the situation of sound collecting experiment for turbo-fan as a comparative example for expression.
Figure 10 carries out the waveform line chart of sound collecting result of experiment to comparative example shown in Figure 9 for expression.
Figure 11 is the performance plot of expression to the measured performance curve of the turbo-fan of turbo-fan of the present invention and comparative example.
Embodiment
Though expression and described several embodiments of the present invention, apparent, disclosed mode of execution is easy to change in not exceeding scope of the present invention or improve.Therefore, be not that intention limits the present invention by concrete expression and detailed description, but cover all changes and improvements with additional claim.
Describe embodiments of the present invention below with reference to the accompanying drawings in detail.Fig. 1 is the broken section perspective view of the turbo-fan of expression an embodiment of the invention, Fig. 2 is the longitudinal section of the part of expression turbo-fan shown in Figure 1, Fig. 3 is the 3-3 line sectional view of Fig. 2, Fig. 4 (A) is the front view of expression impeller inner face, Fig. 4 (B) is the front view of expression impeller variation, Fig. 5 (A) is the sectional view of the 5A-5A line of Fig. 4 (A), and Fig. 5 (B) is the 5B-5B line sectional view among Fig. 4 (B), and Fig. 5 (C) is the sectional view of the variation of expression blade.
As shown in Figure 1, this turbo-fan has the motor 11 that is installed on the base 10, is assembled with housing 12 on the motor 11.Motor 11 usage induction motors are by inverter control rotating speed.As depicted in figs. 1 and 2, housing 12 has the cylindrical part 12c that rotation freely is installed with the disc portion 12a of the running shaft 13 of motor 11, is arranged on the curved part 12b in the disc portion 12a outside and is arranged on the curved part 12b outside integratedly integratedly.Impeller 14 is installed on the running shaft 13, and impeller 14 is by motor 11 rotary driving.Impeller 14 have be provided with the disc portion 15a that is fixed on the running shaft 13 and with the wheel cap 15 of the opposed curved part 15b of curved part 12b, on the inner face of curved part 15b, be formed with circular groove 16.This circular groove 16 by in the curved part 15b of wheel cap 15 along the circumferential direction every the interval of regulation be provided with the multi-disc blade---be that fin (blade) 17 is divided, blade 17 constitutes eccentric groove 18 each other.Cap 19 is installed on the cylindrical part 12c of housing 12, and impeller 14 is covered by cap 19.
As Fig. 1～shown in Figure 3, on the inner face of the curved part 12b of housing 12, be formed with circular-arc static stream 20.On housing 12, be provided with suction passage 21 communicatively with an end of this static stream 20, on housing 12, be provided with communicatively with the other end of static stream 20 and discharge stream 22.As shown in Figure 3, suction passage 21 has the 21a of open communication portion that is communicated with an end of static stream 20, discharge stream 22 and have the 22a of open communication portion that is communicated with the other end of static stream 20, between each 21a of open communication portion, 22a, be provided with the next door 23 of separating suction passage 21 and discharging stream 22.
Fig. 4 (B) and Fig. 5 (B) expression are provided with the impeller 14 of straight line type blade 17, the radially straight extension of each blade 17.Be provided with the impeller 14 of this blade 17, owing to be provided with blade 17 with respect to sense of rotation, therefore when making motor 11 counter-rotatings, suction passage 21 becomes the discharge stream with being symmetric shape, discharges stream 22 and becomes suction passage.Fig. 5 (C) is the variation of straight line type blade 17, is provided with plane of inclination 17c in the back side one side of the sense of rotation of blade 17.So, can use the impeller 14 of above-mentioned any type as turboblower illustrated in figures 1 and 2.
Fig. 6 is the 6-6 line amplification view among Fig. 3, and Fig. 7 (A) is the sectional view of the 7A-7A line among Fig. 6, and Fig. 7 (B) is the sectional view of the 7B-7B line among Fig. 6, and Fig. 7 (C) is the sectional view of the 7C-7C line among Fig. 6.
As shown in Figure 6 and Figure 7, suction passage 21 and discharge stream 22 are the direction of approximate right angle with respect to static stream 20.Therefore, the direction of air from suction passage 21 along approximate right angle flows into static stream 20, and in order to guide the attitude that flows into the air the static stream 20 from suction passage 21 swimmingly, housing 12 is provided with the suction side guide surface 25 of crooked balling-up interior shape.Equally, be discharged to the attitude of discharging the air the stream 22 in order to guide swimmingly from static stream 20, housing 12 is provided with side directed 26 of the discharge of crooked balling-up interior shape.
Discharge and be provided with the 30a of diffuse reflection portion for side directed 26, make and interfere the progressive wave of the wind noise that the pressure oscillation that causes produces because of the blade 17 and the pressure in next door 23 and produce diffuse reflection.The 30a of this diffuse reflection portion is by forming to the outstanding projection 31 of central part of discharging side directed 26, this projection 31 from discharging the end of side directed 26 static stream 20 1 sides, extends to the inside of discharge stream 22 through the open communication 22a of portion along the direction of air flows.Shown in Fig. 7 (A), be on the top 32 at the position, summit at the peak that becomes projection 31, with the corresponding part of the central part of static stream 20 be that the length direction central part of tip portion is the highest from discharging side directed 26.Shown in Fig. 7 (B), (C), the height of projection 31 reduces to two ends one side gradually from the central part of length direction.
As shown in Figure 3 and since the air stream in the turbo-fan when static stream 20 and impeller 14 in, observing in the shape of a spiral shape ground advance, even so projection 31 is given prominence to the central part of side directed 26 of discharge also can not hinder air flows, can reduce the pressure loss.And the bi-side 33 of projection 31 bend to concave, can suppress the increase of resistance of air.
As shown in Figure 6, also be provided with the 30b of diffuse reflection portion on suction side guide surface 25, the 30b of this diffuse reflection portion is formed by the shape projection 31 identical with the 30a of diffuse reflection portion.
So, owing to gradually change as the height of the projection 31 of the 30a of diffuse reflection portion, 30b direction along air flows, and bi-side 33 become bending or are inclined to the face of concave, therefore, the diffuse reflection of the progressive wave of wind noise by each position of projection 31, conditioned reflex changes, and with the phase shifting of progressive wave and reflected wave, prevents the phenomenon of empathizing in static stream 20.In order to change the air quantity that turbo-fan is discharged, the rotating speed of inverter control motor 11.Therefore, though can not avoid impeller 14 being rotated this situation of driving,, diffuse reflection portion can prevent the phenomenon of empathizing in the static stream 20 by being set to produce the such rotating speed of the frequency wind noise consistent with the resonance frequency of static stream 20.Thus, no matter with which type of rotating speed drives impeller 14, can both reduce the noise of turbo-fan.Though on one at suction side guide surface 25 and in discharging side directed 26, the generation that diffuse reflection portion can suppress noise is set, on both, all is provided with more and can improves the inhibition effect.In addition, the solid arrow of symbol S is represented the progressive wave of wind noise among Fig. 6, and the dotted arrow of symbol R is represented reflected wave.
Fig. 8 is the sectional view of the variation of the expression diffuse reflection 30a of portion, 30b, the section shape of part same section shown in expression and Fig. 7 (A).The projection 31 that forms the diffuse reflection 30a of portion, 30b forms recess 34 on its top 32, recess 34 is along the direction extension of air flows, and the degree of depth of recess 34 is along with shoaling towards the two ends of projection 31 length directions.By on top 32, forming recess 34, make the progressive wave diffuse reflection, can make the complicated more variation of conditioned reflex.Though the bi-side 33 of projection 31 need not be bent to concave, be smooth plane of inclination and also can obtain diffuse effect, by bending to the generation that concave can reduce the pressure loss in the stream and can reduce noise.
Fig. 9 is for representing turbo-fan is as a comparative example carried out the schematic representation of the situation of sound collecting experiment, and Fig. 9 represents the inner face of housing 12.Inboard in the next door 23 of housing 12 shown in Figure 9, forming the suction side guide surface of static stream 20 end faces and discharging side directed face becomes the interior shape of ball, but diffuse reflection portion is not set on each guide surface.The pure tone that makes single-frequency flows through state the static stream 20 of such turbo-fan from loudspeaker under, MIC microphone is moved along static stream 20 between suction port one side and exhaust port one side as thick line is represented and collect sound.
Figure 10 carries out the waveform line chart of sound collecting result of experiment to comparative example shown in Figure 9 for expression.As shown in figure 10, in turbo-fan as a comparative example, when the pure tone that makes characteristic frequency flows through, detected the neat up and down waveform of clearly distinguishing antinode and node of amplitude.So, when the frequency of the sound that flows out from MIC microphone was consistent with the standing wave of the resonance frequency of static stream 20, noise was exaggerated and emits to the outside.In contrast, when the 30a of diffuse reflection portion, 30b being set when the suction side of the end face that is forming static stream 20 with on discharging side directed 25,26, do not find that such resonance phenomenon produces, and does not produce dominant frequency even flow out the sound of same frequency from MIC microphone yet.
Figure 11 is the performance plot of expression for the measured performance curve of turbo-fan of the present invention and the turbo-fan as a comparative example with housing shown in Figure 9.As shown in figure 11, when noise measuring set is configured in each turbo-fan around when the noise of various frequencies measured, find to compare with comparative example, diffuse reflection portion has reduced noise in the turbo-fan of the present invention.
The above invention that proposes according to the specifically clear present inventor of working of an invention mode, but the present invention is not subjected to the restriction of above-mentioned mode of execution, can carry out various changes in the scope that does not exceed its aim.For example, the both sides of being put down in writing as patent documentation 2 at the axial direction of the blade turbo-fan that formed static stream also can use the present invention.And, on the next door 23 the guide portion 23a that covers each 21a of open communication portion, 22a the place ahead is set like that shown in the double dot dash line in both can image pattern 6, the top end of guide portion 23a is tilted as patent documentation 1 record.
This turbo-fan is characterised in that above-mentioned diffuse reflection portion is set on above-mentioned suction side guide surface and side directed these two faces of above-mentioned discharge.Turbo-fan of the present invention is characterised in that above-mentioned diffuse reflection portion is outstanding and projection that extend along the direction of air flows to the center of stream.The height that turbo-fan of the present invention is characterised in that above-mentioned projection reduces to two ends gradually from the central part of the length direction of above-mentioned projection.Turbo-fan of the present invention is characterised in that the edgewise bend of above-mentioned projection becomes concave.
According to this turbo-fan, owing on the guide surface that forms static stream end face, diffuse reflection portion is set, therefore interfere the wind noise impact diffuse reflection portion that advances to static stream end face that the pressure oscillation that causes produces by diffuse reflection because of blade and next door, become the phase place state different and be reflected in the static stream with the phase place of wind noise.Thus, also can prevent the phenomenon of empathizing in the static stream, can prevent the generation of advantage sound, can reduce the noise of turbo-fan even produce the frequency wind noise consistent with the resonance frequency of static stream.
Though can reduce the noise that the wind noise causes by on any one face in side directed of discharge and suction side guide surface diffuse reflection portion being set, can further improve the effect that reduces noise on two guide surfaces by diffuse reflection portion all is set.Since when the air after pressurized is observed in static stream and blade in the shape of a spiral shape ground flow, the flow velocity of stream central part is low, therefore by by outstanding to the center of stream and extend outstanding projection along air-flow direction and forms diffuse reflection portion, can be in the pressure loss in reducing the stream that diffuse reflection portion causes the generation of reduction noise.Height by making projection reduces to two ends gradually from the central part of the length direction of this projection, perhaps becomes concave by the edgewise bend with projection, reduces the generation of noise in can the pressure loss in reducing stream.
Claims (6)
1. a turbo-fan has housing and impeller, and this housing is provided with circular-arc static stream, this impeller and above-mentioned static stream are provided with the multi-disc blade every the interval of regulation accordingly in a circumferential direction, and, it is characterized in that this turbo-fan has by motoring:
Suction passage is arranged on the above-mentioned housing communicatively with an end of above-mentioned static stream, with air from exterior guiding to above-mentioned static stream;
Discharge stream, be arranged on communicatively on the above-mentioned housing, forced air is directed to the outside from above-mentioned static stream with the other end of above-mentioned static stream; And
Diffuse reflection portion, on any one face at least in being arranged on the suction side guide surface and discharging side directed, this suction side guide surface form end face of above-mentioned static stream and with air from above-mentioned suction passage guiding to above-mentioned static stream, this discharge side directed form another end face of above-mentioned static stream and with air from above-mentioned static stream guiding to above-mentioned discharge currents road.
2. turbo-fan as claimed in claim 1 is characterized in that,
Above-mentioned diffuse reflection portion is set on above-mentioned suction side guide surface and side directed these two faces of above-mentioned discharge.
3. turbo-fan as claimed in claim 1 or 2 is characterized in that,
Above-mentioned diffuse reflection portion is outstanding and projection that extend along the direction of air flows to the center of stream.
4. turbo-fan as claimed in claim 3 is characterized in that,
The height of above-mentioned projection reduces to two ends gradually from the central part of the length direction of above-mentioned projection.
5. turbo-fan as claimed in claim 3 is characterized in that,
The edgewise bend of above-mentioned projection becomes concave.
6. turbo-fan as claimed in claim 4 is characterized in that,
The edgewise bend of above-mentioned projection becomes concave.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP170896/2008 | 2008-06-30 | ||
| JP2008170896A JP5129668B2 (en) | 2008-06-30 | 2008-06-30 | Vortex blower |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101619727A true CN101619727A (en) | 2010-01-06 |
| CN101619727B CN101619727B (en) | 2011-05-25 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009100057545A Expired - Fee Related CN101619727B (en) | 2008-06-30 | 2009-02-06 | Vortex flow fan |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP5129668B2 (en) |
| CN (1) | CN101619727B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108350897A (en) * | 2015-11-24 | 2018-07-31 | 爱三工业株式会社 | Turbulence pump |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102017220623A1 (en) * | 2017-11-17 | 2019-05-23 | Robert Bosch Gmbh | Side channel compressor for a fuel cell system for conveying and / or sealing a gaseous medium |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5195609A (en) * | 1975-02-19 | 1976-08-21 | ||
| JPS61186789U (en) * | 1985-05-14 | 1986-11-21 |
-
2008
- 2008-06-30 JP JP2008170896A patent/JP5129668B2/en active Active
-
2009
- 2009-02-06 CN CN2009100057545A patent/CN101619727B/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108350897A (en) * | 2015-11-24 | 2018-07-31 | 爱三工业株式会社 | Turbulence pump |
| CN108350897B (en) * | 2015-11-24 | 2020-05-08 | 爱三工业株式会社 | Vortex pump |
Also Published As
| Publication number | Publication date |
|---|---|
| JP5129668B2 (en) | 2013-01-30 |
| CN101619727B (en) | 2011-05-25 |
| JP2010007632A (en) | 2010-01-14 |
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