EP0219578A1 - Centrifugal fans and blowers - Google Patents
Centrifugal fans and blowers Download PDFInfo
- Publication number
- EP0219578A1 EP0219578A1 EP85306321A EP85306321A EP0219578A1 EP 0219578 A1 EP0219578 A1 EP 0219578A1 EP 85306321 A EP85306321 A EP 85306321A EP 85306321 A EP85306321 A EP 85306321A EP 0219578 A1 EP0219578 A1 EP 0219578A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- shaft
- bearing
- impellers
- main
- fan
- 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.)
- Granted
Links
- 238000010276 construction Methods 0.000 description 8
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 241000239290 Araneae Species 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000005242 forging Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
Images
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
- F04D29/04—Shafts or bearings, or assemblies thereof
-
- 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
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/056—Bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows
- F04D25/166—Combinations of two or more pumps ; Producing two or more separate gas flows using fans
-
- 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
- F04D29/60—Mounting; Assembling; Disassembling
- F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
- F04D29/624—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
- F04D29/626—Mounting or removal of fans
Definitions
- the present invention relates to centrifugal fans or blowers.
- Conventional heavy duty double suction centrifugal fans and blowers basically consist of a bearing arrangement, a shaft rotatable about its axis in said bearing arrangement, two single inlet centrifugal fan impellers mounted on said shaft and rotatable therewith, a fan casing surrounding the impellers and drive means for rotating the shaft. While such designs are well proven in service, they do have significant disadvantages in very large size fans, due to scale effects on the basic geometry of the rotor.
- the present invention aims to overcome the major problems resulting from the scale effect, by providing the bearing arrangement so that it includes a main bearing which is located between the impellers, this main bearing taking a major portion of the bearing load of the impellers.
- the diameter of the shaft can be significantly reduced and it is determined largely by the torque which the remainder of the shaft has to transmit from the drive source, such as an electric motor. It is also possible very significantly to reduce the impeller hub weight and therefore its cost.
- the drive means may be connected to the shaft at a location between the impellers, for example either by mounting a drive motor between the impellers or by providing a belt or chain drive or gearbox drive.
- the bearing assembly includes a second bearing at a location spaced along the shaft from the main bearing, the drive means being positioned adjacent the second bearing.
- the outer bearing There will be a much reduced load on the outer bearing which will allow the size of this bearing to be greatly reduced. Because of the very much reduced total rotor weight, there will be easier handling, less starting torque and reduced foundation loads.
- the shaft can be made of lesser diameter than hitherto, and when the second portion of smaller diameter is provided, the shaft blockage of the flow of air to the inlet of the impellers will be greatly reduced on one side and will totally eliminated on the other side from that on which the drive motor will be provided. The other side, of course, will only be an overhung portion cantilevered out from the main bearing.
- the main portion of the shaft may be detachably connected to the second portion of the shaft and the casing may include slots and removable cover panels, so that when cover panels are removed and the main shaft portions are disconnected from the second shaft portion, the impellers can be rolled out of the casing.
- the two fan impellers and their volutes may be of a different size and/or design.
- impeller or impellers which are mounted in overhung relation to the main bearing may be provided with a simple disc flow control.
- the assembly illustrated therein includes a horizontal axis large diameter shaft 10 mounted between two bearings 12 and 14.
- the shaft passes through a casing indicated by the general reference numeral 16 and including first and second inlet ducts 18, 20 located just inwardly of the bearing 12, 14.
- the inlet ducts 18 have laterally extending inlet frusto-conical portions 22, 24 substantially coaxial with the shaft 10.
- Mounted centrally on the shaft 10 is a double inlet impeller 26, 27 which is surrounded by volute portions 28, 29, respectively, of the fan casing.
- the two bearings 12 and 14 are spaced apart from one another by a substantial distance and the shaft 10 will need to have a fairly large diameter to enable it to support a heavy duty double inlet impeller 26, 27.
- the shaft is driven by a motor indicated schematically at 30 positioned to the left of the bearing 14.
- Figure 2 shows an alternative known arrangement in which like parts have been indicated by like reference numerals.
- This construction differs from that of Figure 1 in that there is only a single inlet 18 mounted centrally of the assembly and the two impellers 26, 27 are mounted adjacent the bearings 12, 14.
- This design results in a significant reduction in shaft diameter compared to that shown in Figure 1, with all the advantages that this will bring. It does, however, present considerable practical problems with regard to flow control in the common inlet 18 and in some applications the additional complexity resulting from this is unlikely to be offset by the cost savings resulting from the reduced shaft size.
- Figure 3 illustrates a construction according to the present invention which obviates many of the disadvantages of the arrangements of Figures 1 and 2, and like parts have again been indicated by like reference numerals.
- the structure is very similar to Figure 1 in that there are two inlets 18, 20, to frusto-conical portions 22, 24 and two outlet volutes 28, 29.
- the two inlet impellers 26, 27 are formed as single inlet impellers mounted on the common shaft 10 and a main bearing 12 is mounted between them and bears most of the weight load of the shaft 10 and of the impellers 26, 27.
- An overhung portion 11 of the shaft 10 extends to the right of the main bearing 12 as seen in Figures 3, and the first single inlet impeller 26 is mounted thereon.
- the remaining portion 13 of the shaft 10 carries the second single inlet impeller 27 and extends to the second bearing 14 and from there to a drive motor 30.
- the diameter of the shaft 10 can be made significantly smaller than in the structure of Figure 1. This means that the restriction to flow of air into the impeller 27 is greatly reduced, thus increasing the efficiency of that fan. Furthermore, because all of the parts can be made much lighter, the construction of the foundations 32, 34 can be reduced for a fan of the same size. Alternatively, of course, using conventional size parts, the size of the fan can be increased.
- FIG 4 illustrates a similar construction to that in Figure 3 and again like parts have been indicated by like reference numerals.
- the fan constituted by the impeller 26 and the volute 28 is different from that constituted by the impeller 27 and the volute 29.
- FIG. 6 is a further modification.
- the two fans are themselves substantially identical, but a disc type flow control is provided by a shaft 36 mounted in a first slide bearing 38 in the housing 16 and the second slide bearing 40 carried on a spider 41.
- a frusto-conical disc flow control On the end of the shaft 36 is formed a frusto-conical disc flow control. Movement of the shaft in the direction indicated by the arrows will affect the flow of air through the fan.
- the structure of Figure 7 differs from that of Figure 3 in that the shaft 10 includes not only the overhung portion 11, but a further overhung portion 13 of about the same length as the portion 11, and of a fairly robust diameter, and it is connected to a smaller diameter drive shaft 15 by a simple coupling 17.
- a pin (not shown) can pass through the coupling 17 and the shaft 15.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
- The present invention relates to centrifugal fans or blowers.
- Conventional heavy duty double suction centrifugal fans and blowers basically consist of a bearing arrangement, a shaft rotatable about its axis in said bearing arrangement, two single inlet centrifugal fan impellers mounted on said shaft and rotatable therewith, a fan casing surrounding the impellers and drive means for rotating the shaft. While such designs are well proven in service, they do have significant disadvantages in very large size fans, due to scale effects on the basic geometry of the rotor.
- The problems of such heavy duty fans are discussed later in this specification with reference to Figures 1 and 2.
- The present invention aims to overcome the major problems resulting from the scale effect, by providing the bearing arrangement so that it includes a main bearing which is located between the impellers, this main bearing taking a major portion of the bearing load of the impellers.
- With such an arrangement because the actual load bearing portion of the shaft can be relatively short, the diameter of the shaft can be significantly reduced and it is determined largely by the torque which the remainder of the shaft has to transmit from the drive source, such as an electric motor. It is also possible very significantly to reduce the impeller hub weight and therefore its cost.
- The drive means may be connected to the shaft at a location between the impellers, for example either by mounting a drive motor between the impellers or by providing a belt or chain drive or gearbox drive.
- Preferably, however, the bearing assembly includes a second bearing at a location spaced along the shaft from the main bearing, the drive means being positioned adjacent the second bearing. There will be a much reduced load on the outer bearing which will allow the size of this bearing to be greatly reduced. Because of the very much reduced total rotor weight, there will be easier handling, less starting torque and reduced foundation loads.
- Because the shaft can be made of lesser diameter than hitherto, and when the second portion of smaller diameter is provided, the shaft blockage of the flow of air to the inlet of the impellers will be greatly reduced on one side and will totally eliminated on the other side from that on which the drive motor will be provided. The other side, of course, will only be an overhung portion cantilevered out from the main bearing.
- The main portion of the shaft may be detachably connected to the second portion of the shaft and the casing may include slots and removable cover panels, so that when cover panels are removed and the main shaft portions are disconnected from the second shaft portion, the impellers can be rolled out of the casing.
- The two fan impellers and their volutes may be of a different size and/or design.
- Furthermore, the impeller or impellers which are mounted in overhung relation to the main bearing may be provided with a simple disc flow control.
- In order that the present invention may more readily be understood, the following description is given, merely by way of example, reference being made to the accompanying drawings, in which:-
- Figure 1 is a schematic, broken away side elevation of one known form of large capacity double centrifugal fan or blower;
- Figure 2 is a view similar to Figure 1 of a second known form of such apparatus;
- Figures 3, 4, 5, 6 and 7 are similar views of five different embodiments of large capacity double centrifugal fans or blowers according to the present invention; and
- Figure 8 is an end elevation of the arrangement of Figure 3.
- Referring first to Figure 1, the assembly illustrated therein includes a horizontal axis
large diameter shaft 10 mounted between twobearings general reference numeral 16 and including first andsecond inlet ducts bearing inlet ducts 18 have laterally extending inlet frusto-conical portions shaft 10. Mounted centrally on theshaft 10 is adouble inlet impeller volute portions - The two
bearings shaft 10 will need to have a fairly large diameter to enable it to support a heavy dutydouble inlet impeller bearing 14. - Problems arise with the construction of Figure 1 mainly from the fact that, in order to maintain an acceptable critical speed for the rotor, the ratio of shaft to impeller weight is size dependent and, in very large fans, the shaft weight can be of the order of 3 times the impeller weight. A most obvious disadvantage of this is the total rotor weight can become excessive resulting in very high loads on the
foundations bearings shaft 10 is of a relatively large diameter it also provides a substantial blockage on the in flowing air through the frusto-conical portions - Figure 2 shows an alternative known arrangement in which like parts have been indicated by like reference numerals. This construction differs from that of Figure 1 in that there is only a
single inlet 18 mounted centrally of the assembly and the twoimpellers bearings common inlet 18 and in some applications the additional complexity resulting from this is unlikely to be offset by the cost savings resulting from the reduced shaft size. - Figure 3 illustrates a construction according to the present invention which obviates many of the disadvantages of the arrangements of Figures 1 and 2, and like parts have again been indicated by like reference numerals. The structure is very similar to Figure 1 in that there are two
inlets conical portions - In this construction, however, the two
inlet impellers common shaft 10 and amain bearing 12 is mounted between them and bears most of the weight load of theshaft 10 and of theimpellers overhung portion 11 of theshaft 10 extends to the right of themain bearing 12 as seen in Figures 3, and the firstsingle inlet impeller 26 is mounted thereon. Theremaining portion 13 of theshaft 10 carries the secondsingle inlet impeller 27 and extends to the second bearing 14 and from there to adrive motor 30. - Because the main bearing 12 carries most of the weight load, and because the
overhung portion 11 and the corresponding part of theportion 13 of theshaft 10 are relatively short, the diameter of theshaft 10 can be made significantly smaller than in the structure of Figure 1. This means that the restriction to flow of air into theimpeller 27 is greatly reduced, thus increasing the efficiency of that fan. Furthermore, because all of the parts can be made much lighter, the construction of thefoundations - Figure 4 illustrates a similar construction to that in Figure 3 and again like parts have been indicated by like reference numerals. Here it can be seen that the fan constituted by the
impeller 26 and thevolute 28 is different from that constituted by theimpeller 27 and thevolute 29. - The construction of Figure 5 is again similar but here the fan constituted by the
impeller 26 and thevolute 28 is much smaller than that constituted by theimpeller 27 and thevolute 29. - Figure 6 is a further modification. The two fans are themselves substantially identical, but a disc type flow control is provided by a
shaft 36 mounted in a first slide bearing 38 in thehousing 16 and the second slide bearing 40 carried on aspider 41. On the end of theshaft 36 is formed a frusto-conical disc flow control. Movement of the shaft in the direction indicated by the arrows will affect the flow of air through the fan. - The structure of Figure 7 differs from that of Figure 3 in that the
shaft 10 includes not only theoverhung portion 11, but afurther overhung portion 13 of about the same length as theportion 11, and of a fairly robust diameter, and it is connected to a smaller diameter drive shaft 15 by a simple coupling 17. A pin (not shown) can pass through the coupling 17 and the shaft 15. - The advantage of this construction is that
panels 44 can be removed, the pin passing through the connector 17 and the shaft 15 can be disengaged, and if thebearing 12 is opened up, theimpellers shaft portions horizontal slots 50 provided in the vertical facingwalls volutes
Claims (8)
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE8585306321T DE3568614D1 (en) | 1985-09-05 | 1985-09-05 | Centrifugal fans and blowers |
EP85306321A EP0219578B1 (en) | 1985-09-05 | 1985-09-05 | Centrifugal fans and blowers |
AU61799/86A AU605106B2 (en) | 1985-09-05 | 1986-08-25 | Centrifugal fans and blowers |
ZA866641A ZA866641B (en) | 1985-09-05 | 1986-09-02 | Centrifugal fans and blowers |
KR1019860007387A KR870003317A (en) | 1985-09-05 | 1986-09-04 | Centrifugal blower |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP85306321A EP0219578B1 (en) | 1985-09-05 | 1985-09-05 | Centrifugal fans and blowers |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0219578A1 true EP0219578A1 (en) | 1987-04-29 |
EP0219578B1 EP0219578B1 (en) | 1989-03-08 |
Family
ID=8194354
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP85306321A Expired EP0219578B1 (en) | 1985-09-05 | 1985-09-05 | Centrifugal fans and blowers |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP0219578B1 (en) |
KR (1) | KR870003317A (en) |
AU (1) | AU605106B2 (en) |
DE (1) | DE3568614D1 (en) |
ZA (1) | ZA866641B (en) |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2702011A1 (en) * | 1993-02-24 | 1994-09-02 | Valeo Thermique Habitacle | Blower, particularly for a heating or air-conditioning device of a motor vehicle |
WO2002073039A1 (en) * | 2001-03-14 | 2002-09-19 | Howden Power Limited | Method of enhancing the aerodynamic performance of a fan |
CN1295438C (en) * | 2003-09-15 | 2007-01-17 | 海尔集团公司 | Blower fan with single electric machine and bilobed wheel |
EP3396054A1 (en) | 2017-04-24 | 2018-10-31 | Candy S.p.A. | A condensation type laundry dryer machine |
RU188901U1 (en) * | 2018-02-08 | 2019-04-29 | Елена Ивановна Швецова | CENTRIFUGAL PUMP WITH TWO-SIDE INPUT WHEEL |
WO2019144059A1 (en) * | 2018-01-19 | 2019-07-25 | Concepts Nrec, Llc | Turbomachines with decoupled collectors |
CN112682338A (en) * | 2020-12-24 | 2021-04-20 | 北京理工大学 | Air compressor for fuel cell system |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR101952826B1 (en) | 2018-03-20 | 2019-05-22 | 한동대학교 산학협력단 | degumming boiler of bast fiber |
KR101952830B1 (en) | 2018-03-20 | 2019-05-22 | 한동대학교 산학협력단 | washing device of bast fiber |
CN211901014U (en) * | 2018-11-29 | 2020-11-10 | 曾固 | Centrifugal through-flow water navigation body propulsion device and application equipment |
Citations (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB191411029A (en) * | 1914-05-05 | 1915-01-14 | Oswald Stott | Improvements in or relating to Centrifugal Fans. |
US1646319A (en) * | 1927-05-17 | 1927-10-18 | York Heating And Ventilating C | Fan-housing construction |
US2450708A (en) * | 1946-12-23 | 1948-10-05 | Anderson Paul | Centrifugal fan |
US2652816A (en) * | 1949-03-26 | 1953-09-22 | Adiel Y Dodge | Thermostatically controlled clutch and fan drive |
DE1106918B (en) * | 1955-01-19 | 1961-05-18 | Bruno Eck Dr Ing | Radial fan runner |
FR1279221A (en) * | 1959-07-23 | 1961-12-22 | Improvements to electric motors | |
US3182899A (en) * | 1960-06-01 | 1965-05-11 | Whirlpool Co | Wall mounted dual fan structure |
GB1079331A (en) * | 1964-04-15 | 1967-08-16 | Howden James & Co Ltd | Improvements in or relating to large-capacity double-suction centrifugal fans, blowers or the like |
DE1266133B (en) * | 1965-01-26 | 1968-04-11 | Loewe Pumpenfabrik G M B H | Centrifugal pump unit |
DE1901361A1 (en) * | 1968-01-29 | 1969-09-25 | Ludwig Baumann | Room fan with simultaneous delivery of outside air into the interior and of interior air to the outside, in particular with an intermediate seal |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
AU408954B2 (en) * | 1966-09-07 | 1970-12-22 | Blech Und Metallwarenfabrik Robert Fischbach Kg | Axial flow blower |
-
1985
- 1985-09-05 EP EP85306321A patent/EP0219578B1/en not_active Expired
- 1985-09-05 DE DE8585306321T patent/DE3568614D1/en not_active Expired
-
1986
- 1986-08-25 AU AU61799/86A patent/AU605106B2/en not_active Expired - Fee Related
- 1986-09-02 ZA ZA866641A patent/ZA866641B/en unknown
- 1986-09-04 KR KR1019860007387A patent/KR870003317A/en not_active Application Discontinuation
Patent Citations (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB191411029A (en) * | 1914-05-05 | 1915-01-14 | Oswald Stott | Improvements in or relating to Centrifugal Fans. |
US1646319A (en) * | 1927-05-17 | 1927-10-18 | York Heating And Ventilating C | Fan-housing construction |
US2450708A (en) * | 1946-12-23 | 1948-10-05 | Anderson Paul | Centrifugal fan |
US2652816A (en) * | 1949-03-26 | 1953-09-22 | Adiel Y Dodge | Thermostatically controlled clutch and fan drive |
DE1106918B (en) * | 1955-01-19 | 1961-05-18 | Bruno Eck Dr Ing | Radial fan runner |
FR1279221A (en) * | 1959-07-23 | 1961-12-22 | Improvements to electric motors | |
US3182899A (en) * | 1960-06-01 | 1965-05-11 | Whirlpool Co | Wall mounted dual fan structure |
GB1079331A (en) * | 1964-04-15 | 1967-08-16 | Howden James & Co Ltd | Improvements in or relating to large-capacity double-suction centrifugal fans, blowers or the like |
DE1266133B (en) * | 1965-01-26 | 1968-04-11 | Loewe Pumpenfabrik G M B H | Centrifugal pump unit |
DE1901361A1 (en) * | 1968-01-29 | 1969-09-25 | Ludwig Baumann | Room fan with simultaneous delivery of outside air into the interior and of interior air to the outside, in particular with an intermediate seal |
Non-Patent Citations (1)
Title |
---|
ZEITSCHRIFT DES VEREINES DEUTSCHER INGENIEURE, vol. 95, January 1953, pages 55,56, Düsseldorf, DE; E. SIEGWART: "Luftgekühlte Lager für Radial- und Axialheissgasgebläse" * |
Cited By (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2702011A1 (en) * | 1993-02-24 | 1994-09-02 | Valeo Thermique Habitacle | Blower, particularly for a heating or air-conditioning device of a motor vehicle |
WO2002073039A1 (en) * | 2001-03-14 | 2002-09-19 | Howden Power Limited | Method of enhancing the aerodynamic performance of a fan |
US6971840B2 (en) | 2001-03-14 | 2005-12-06 | Howden Power Limited | Method of enhancing the aerodynamic performance of a fan |
CN1295438C (en) * | 2003-09-15 | 2007-01-17 | 海尔集团公司 | Blower fan with single electric machine and bilobed wheel |
EP3396054A1 (en) | 2017-04-24 | 2018-10-31 | Candy S.p.A. | A condensation type laundry dryer machine |
WO2019144059A1 (en) * | 2018-01-19 | 2019-07-25 | Concepts Nrec, Llc | Turbomachines with decoupled collectors |
CN111601972A (en) * | 2018-01-19 | 2020-08-28 | 概创机械设计有限责任公司 | Turbine with separate collectors |
US11421695B2 (en) | 2018-01-19 | 2022-08-23 | Concepts Nrec, Llc | Turbomachines with decoupled collectors |
CN111601972B (en) * | 2018-01-19 | 2022-09-23 | 概创机械设计有限责任公司 | Turbine with separate collectors |
RU188901U1 (en) * | 2018-02-08 | 2019-04-29 | Елена Ивановна Швецова | CENTRIFUGAL PUMP WITH TWO-SIDE INPUT WHEEL |
CN112682338A (en) * | 2020-12-24 | 2021-04-20 | 北京理工大学 | Air compressor for fuel cell system |
Also Published As
Publication number | Publication date |
---|---|
KR870003317A (en) | 1987-04-16 |
EP0219578B1 (en) | 1989-03-08 |
ZA866641B (en) | 1987-05-27 |
DE3568614D1 (en) | 1989-04-13 |
AU6179986A (en) | 1987-03-12 |
AU605106B2 (en) | 1991-01-10 |
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