EP0467557B1 - Blower assembly with impeller for vacuum cleaner - Google Patents

Blower assembly with impeller for vacuum cleaner Download PDF

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Publication number
EP0467557B1
EP0467557B1 EP91306038A EP91306038A EP0467557B1 EP 0467557 B1 EP0467557 B1 EP 0467557B1 EP 91306038 A EP91306038 A EP 91306038A EP 91306038 A EP91306038 A EP 91306038A EP 0467557 B1 EP0467557 B1 EP 0467557B1
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EP
European Patent Office
Prior art keywords
impeller
vanes
shroud plate
inlet
axial
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 - Lifetime
Application number
EP91306038A
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German (de)
French (fr)
Other versions
EP0467557B2 (en
EP0467557A1 (en
Inventor
Yukiji Iwase
Shigenori Sato
Masao Sunagawa
Hisanori Toyoshima
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Hitachi Ltd
Original Assignee
Hitachi Ltd
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Publication date
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Application filed by Hitachi Ltd filed Critical Hitachi Ltd
Priority to EP94101775A priority Critical patent/EP0602007B1/en
Publication of EP0467557A1 publication Critical patent/EP0467557A1/en
Application granted granted Critical
Publication of EP0467557B1 publication Critical patent/EP0467557B1/en
Publication of EP0467557B2 publication Critical patent/EP0467557B2/en
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Classifications

    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47L—DOMESTIC WASHING OR CLEANING; SUCTION CLEANERS IN GENERAL
    • A47L9/00—Details or accessories of suction cleaners, e.g. mechanical means for controlling the suction or for effecting pulsating action; Storing devices specially adapted to suction cleaners or parts thereof; Carrying-vehicles specially adapted for suction cleaners
    • A47L9/02—Nozzles
    • A47L9/08—Nozzles with means adapted for blowing
    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47L—DOMESTIC WASHING OR CLEANING; SUCTION CLEANERS IN GENERAL
    • A47L5/00—Structural features of suction cleaners
    • A47L5/12—Structural features of suction cleaners with power-driven air-pumps or air-compressors, e.g. driven by motor vehicle engine vacuum
    • A47L5/22—Structural features of suction cleaners with power-driven air-pumps or air-compressors, e.g. driven by motor vehicle engine vacuum with rotary fans

Definitions

  • This invention relates to impellers for vacuum cleaners and to vacuum cleaners having an impeller and a blower motor driving the impeller.
  • JP-A-59-74396 discloses an impeller for an electric blower in which a shroud plate is defined in the vicinity of the inlet of an impeller by a continuous curve, as viewed in an axial plane, having a large curvature as compared to the inner diameter of the impeller.
  • This design can reduce exhaust noise, but is liable to relatively increase the sound transmitted through walls in the vacuum cleaner, due to vibrations transmitted to the walls.
  • JP-A-59-74396 also, a covering portion of the blower casing is disposed substantially perpendicularly to the shroud plate of the impeller in the vicinity of the inlet of the impeller. Consequently, when the axial direction of the incoming air flow changes to the radial direction in the inlet region of the impeller, the flow breaks away on the side of the shroud, causing a large loss. Since the aerodynamic condition of the flow is bad in the inlet section of the impeller, noise proportional to the product of the number of vanes and the rotational speed of the impeller tends to increase.
  • the length of overlap between the impeller inlet and the blower casing is determined by the thickness of the shroud plate of the impeller, the length of a sealing portion is limited to as small as 1 mm; thus, it is difficult to decrease the leakage flow rate between the shroud plate and the casing.
  • the leak flow is substantially perpendicular to the main flow at the inlet of the impeller, break-away of the flow is promoted.
  • the shroud plate is curved as viewed in the axial plane, the hub plate opposite the shroud plate and the shroud plate tend to be deformed during the fixing of the shroud plate and the vanes together, creating deviation of the impeller from the desired shape. Further, a gap tends to appear at the end surface of the vane inside the impeller, increasing leakage and loss.
  • the object of the present invention is at least partly to avoid the disadvantages described above, and to improve the air flow efficiency through the blower of a vacuum cleaner.
  • the present invention is set out in claim 1, and the impeller of the invention in another aspect is set out in claim 2.
  • the shroud plate of the impeller is frusto-conical in shape at its region adjacent the impeller vanes.
  • the extremity of the flange of the shroud plate is at an angle of not more than 30 ° to the axis, as seen in axial cross-section. Best results are obtained when the ratio of (a) the radius of curvature of the shroud plate, at its region of curvature into said flange, to (b) the vane inlet width in the axial direction, is in the range 0.5 to 1.0.
  • Embodiments of impellers and vacuum cleaner blowers of the invention will now be described. They may be fitted in conventional vacuum cleaners. Examples of vacuum cleaners in which they may be mounted are shown in European Patent Applications 91303152.2 and 91303496.3.
  • the electric vacuum cleaner blower shown in Fig. 1 and 2 is composed of a blower portion 80 and a motor portion 81. Disposed inside a housing 81 a of the motor portion 81 are a rotor 83 secured to a rotating shaft 82 and a stator 85 including coils 84a and 84b.
  • the housing 81 a has a bearing-retaining portion 81 formed at the centre of its end wall, and a bearing 86a for rotatably supporting one end of the rotating shaft 82 is disposed in the bearing-retaining portion 81 b.
  • the housing 81 a also has exhaust ports 81 c in its peripheral surface.
  • the housing 81 a has an end bracket 87 at the opposite end, and this end bracket 87 connects the blower portion 80 and the motor 81 together.
  • the end bracket 87 has a bearing retaining portion 87a at its centre and a flat portion 87b around its circumference.
  • the flat portion 87b is formed with suction ports 88 through which the air from the blower 80 is sent into the motor 81 to cool it.
  • Disposed in the bearing-retaining portion 87a is a bearing 86b for rotatably supporting the other end of the rotating shaft 82.
  • the end bracket 87 carries a diffuser 89, and on the upstream side of the diffuser, a centrifugal impeller 90 is secured to the rotating shaft 82 by means of a nut 91.
  • the centrifugal impeller 90 and the diffuser 89 are covered by a blower casing 92 pressure-fitted to the circumference of the end bracket 87.
  • the blower casing 92 has a suction port 93 formed in its central portion to provide an inlet to the central inlet region of the impeller.
  • the diffuser 89 is composed of a plurality of diffuser vanes 94 arranged radially outside the circumference of the centrifugal impeller 90.
  • a plurality of return guide vanes 95 are arranged on the back of a wall 89a lying adjacent the impeller 90 and supporting the diffuser vanes 94.
  • the wall 89a has a rounded outer peripheral edge to smooth the air flow from the diffuser vanes 94 to the return guide vanes 95, and in conjunction with the wall 89a and the end bracket 87, the return guide vanes 95 define a return guide passage through which the air flow is guided to the suction ports 88.
  • Fig. 2 shows the configuration of the centrifugal impeller 90 and the diffuser region in more detail.
  • the impeller 90 is composed of a plurality of vanes 96, a shroud plate 97 and hub plate 98.
  • Each vane 96 has on each edge three protrusions which are fitted in holes formed in the shroud plate 97 and the hub plate 98 and then caulked or upset, so that these components are rigidly and tightly secured together at these connection points.
  • the vanes 96 are curved as they extend outwardly, but for convenience this is not indicated in Fig. 2.
  • the outer diameter portion of the shroud plate 97 is frusto-conical, i.e. straight as seen in the axial plane, radially outwardly of the innermost point of connection 99 to the vanes 96. Inwardly of the point 99, the shroud plate 97 is shaped as to define a rounded portion 97a ending in an upwardly turned flange 97b whose end portion is at about 20 ° to the impeller axis. The radius of curvature of the rounded portion 87a is 0.7 times the vane inlet width.
  • the blower casing 92 is shaped to provide an inwardly bent flange 92a, and a leakage gap 100 is left between the flange 92a and the flange 97b of the impeller 90. As seen in Fig. 2, the flanges 92a and 97b overlap axially (see also Figs. 4 and 5), with the flange 92a radially inside.
  • the leak flow Since the direction of the leak flow is parallel to the axis and in this region the main flow is also parallel to the axis, the leak flow does not have bad influence on the main flow, and since the radius of curvature of the rounded portion 97a of the shroud plate is large, the main flow breaks away from the shroud plate 97 at most only slightly.
  • the shroud plate 97 is straight from its outer circumference to the innermost point of connection 99 as viewed in the axial plane, and there is only a small difference in height of the vane 96 between its inlet and outlet. Therefore, although the vane 96 is curved in the circumferential direction in a conventional manner, the force applied in caulking each protrusion of the vane 96 does not vary from one caulking point to another. Accordingly, the deformation of the shroud plate 97 and of the hub plate 98 is minimized even under the force applied to each caulking point. Consequently, hardly any gaps arise between the vanes 96, shroud plate 97 and hub plate 98, and leak flow between the pressure side and suction pressure side of the vane 96 is suppressed. Further, since any face deflection of the shroud plate 97 and of the hub plate 98 is small, unbalance hardly arises; thus, noise based on a frequency corresponding to the rotational speed decreases.
  • the shroud plate 97 is straight in its outer diameter portion, as viewed in the axial plane, and has a rounded portion 97a inwardly from the innermost point of connection 99, as in Fig. 2.
  • the shroud plate 97 in this case is provided with a cylindrical portion 97b extending axially from the end of the rounded portion 97a.
  • the blower casing 101 has an inwardly bent flange 101 a at its inner diameter region, so that the gap 100 is left between the flange 101 a and the cylindrical portion 97b of the impeller 90. Since the length of the gap 100 is much larger than the thickness of the shroud plate 97, the friction loss of the leak flow can be made very large, the leak flow can be reduced remarkably, and the efficiency of the electric blower can be improved.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Electric Suction Cleaners (AREA)

Description

  • This invention relates to impellers for vacuum cleaners and to vacuum cleaners having an impeller and a blower motor driving the impeller.
  • In the field of household vacuum cleaners, JP-A-59-74396 discloses an impeller for an electric blower in which a shroud plate is defined in the vicinity of the inlet of an impeller by a continuous curve, as viewed in an axial plane, having a large curvature as compared to the inner diameter of the impeller. This design can reduce exhaust noise, but is liable to relatively increase the sound transmitted through walls in the vacuum cleaner, due to vibrations transmitted to the walls.
  • In JP-A-59-74396 also, a covering portion of the blower casing is disposed substantially perpendicularly to the shroud plate of the impeller in the vicinity of the inlet of the impeller. Consequently, when the axial direction of the incoming air flow changes to the radial direction in the inlet region of the impeller, the flow breaks away on the side of the shroud, causing a large loss. Since the aerodynamic condition of the flow is bad in the inlet section of the impeller, noise proportional to the product of the number of vanes and the rotational speed of the impeller tends to increase.
  • Additionally, since the length of overlap between the impeller inlet and the blower casing is determined by the thickness of the shroud plate of the impeller, the length of a sealing portion is limited to as small as 1 mm; thus, it is difficult to decrease the leakage flow rate between the shroud plate and the casing.
  • Furthermore, since the leak flow is substantially perpendicular to the main flow at the inlet of the impeller, break-away of the flow is promoted. Since the shroud plate is curved as viewed in the axial plane, the hub plate opposite the shroud plate and the shroud plate tend to be deformed during the fixing of the shroud plate and the vanes together, creating deviation of the impeller from the desired shape. Further, a gap tends to appear at the end surface of the vane inside the impeller, increasing leakage and loss.
  • The object of the present invention is at least partly to avoid the disadvantages described above, and to improve the air flow efficiency through the blower of a vacuum cleaner.
  • The present invention is set out in claim 1, and the impeller of the invention in another aspect is set out in claim 2.
  • Preferably the shroud plate of the impeller is frusto-conical in shape at its region adjacent the impeller vanes. Preferably the extremity of the flange of the shroud plate is at an angle of not more than 30 ° to the axis, as seen in axial cross-section. Best results are obtained when the ratio of (a) the radius of curvature of the shroud plate, at its region of curvature into said flange, to (b) the vane inlet width in the axial direction, is in the range 0.5 to 1.0.
  • Embodiments of the invention will now be described by way of non-limitative example with reference to the accompanying drawings, in which:-
    • Fig. 1 is a side view, partly in cross section, of an electric blower including motor and blower, embodying the present invention;
    • Fig. 2 is an axial sectional view of part of the blower of Fig. 1;
    • Figs. 3 and 4 are diagrams illustrating respectively the air flows in the blower of JP-A-59-74396 and the blower of Fig. 2; and
    • Fig. 5 is an axial sectional view showing another embodiment of the blower according to the present invention;
  • Embodiments of impellers and vacuum cleaner blowers of the invention will now be described. They may be fitted in conventional vacuum cleaners. Examples of vacuum cleaners in which they may be mounted are shown in European Patent Applications 91303152.2 and 91303496.3.
  • The electric vacuum cleaner blower shown in Fig. 1 and 2 is composed of a blower portion 80 and a motor portion 81. Disposed inside a housing 81 a of the motor portion 81 are a rotor 83 secured to a rotating shaft 82 and a stator 85 including coils 84a and 84b. The housing 81 a has a bearing-retaining portion 81 formed at the centre of its end wall, and a bearing 86a for rotatably supporting one end of the rotating shaft 82 is disposed in the bearing-retaining portion 81 b. The housing 81 a also has exhaust ports 81 c in its peripheral surface. The housing 81 a has an end bracket 87 at the opposite end, and this end bracket 87 connects the blower portion 80 and the motor 81 together.
  • The end bracket 87 has a bearing retaining portion 87a at its centre and a flat portion 87b around its circumference. The flat portion 87b is formed with suction ports 88 through which the air from the blower 80 is sent into the motor 81 to cool it. Disposed in the bearing-retaining portion 87a is a bearing 86b for rotatably supporting the other end of the rotating shaft 82. The end bracket 87 carries a diffuser 89, and on the upstream side of the diffuser, a centrifugal impeller 90 is secured to the rotating shaft 82 by means of a nut 91. The centrifugal impeller 90 and the diffuser 89 are covered by a blower casing 92 pressure-fitted to the circumference of the end bracket 87. The blower casing 92 has a suction port 93 formed in its central portion to provide an inlet to the central inlet region of the impeller.
  • The diffuser 89 is composed of a plurality of diffuser vanes 94 arranged radially outside the circumference of the centrifugal impeller 90. A plurality of return guide vanes 95 are arranged on the back of a wall 89a lying adjacent the impeller 90 and supporting the diffuser vanes 94. The wall 89a has a rounded outer peripheral edge to smooth the air flow from the diffuser vanes 94 to the return guide vanes 95, and in conjunction with the wall 89a and the end bracket 87, the return guide vanes 95 define a return guide passage through which the air flow is guided to the suction ports 88.
  • The general operation of the electric blower in the embodiment will now be described. When the motor 81 is energized so that the impeller 90 is rotated, air flows as indicated by the arrows in the drawing, through the suction port 93 and into the impeller 90. After discharge from the impeller 90, the air passes between the diffuser vanes 94, and after passing through the return guide passage, goes through the suction ports 88 into the housing 81a. The air flow introduced into the housing 81 a cools the rotor 83, passes through an air passage defined by the stator 85 and the inner surface of the housing 81 a, cools the coils 84a and 84b, and goes through the exhaust ports 81 c formed in the periphery of the housing 81 a to the outside.
  • Fig. 2 shows the configuration of the centrifugal impeller 90 and the diffuser region in more detail. The impeller 90 is composed of a plurality of vanes 96, a shroud plate 97 and hub plate 98. Each vane 96 has on each edge three protrusions which are fitted in holes formed in the shroud plate 97 and the hub plate 98 and then caulked or upset, so that these components are rigidly and tightly secured together at these connection points. As Fig. 6 shows, the vanes 96 are curved as they extend outwardly, but for convenience this is not indicated in Fig. 2.
  • The outer diameter portion of the shroud plate 97 is frusto-conical, i.e. straight as seen in the axial plane, radially outwardly of the innermost point of connection 99 to the vanes 96. Inwardly of the point 99, the shroud plate 97 is shaped as to define a rounded portion 97a ending in an upwardly turned flange 97b whose end portion is at about 20 ° to the impeller axis. The radius of curvature of the rounded portion 87a is 0.7 times the vane inlet width. The blower casing 92 is shaped to provide an inwardly bent flange 92a, and a leakage gap 100 is left between the flange 92a and the flange 97b of the impeller 90. As seen in Fig. 2, the flanges 92a and 97b overlap axially (see also Figs. 4 and 5), with the flange 92a radially inside.
  • By virtue of the pressure difference between the inlet and outlet of the impeller 90, a part of the air flow leaving the impeller 90 passes between the impeller 90 and the blower casing 92 and flows again into the impeller inlet zone. Therefore, the impeller 90 acts on this leak flow too, and if the flow rate of this leakage is large, the performance of the electric blower is considerably degraded; however, since in the illustrated embodiment the length of the gap 100 is larger than the thickness of the shroud plate 97, the friction loss of the leak flow can be increased, thereby decreasing the leak flow rate.
  • Since the direction of the leak flow is parallel to the axis and in this region the main flow is also parallel to the axis, the leak flow does not have bad influence on the main flow, and since the radius of curvature of the rounded portion 97a of the shroud plate is large, the main flow breaks away from the shroud plate 97 at most only slightly.
  • From simulation experiments performed on the blower shown in Fig. 3 and blowers similar to the embodiment of Figs. 1 and 2 and using water flows chosen to be identical in terms of the Reynolds number, it has been found that in the case of the known structure as shown in Fig. 3, the flow breaks away considerably on the side of the shroud plate of the impeller, whereas in the case of the impeller of the present invention in which the ratio of the radius of the rounded portion 97a to the impeller vane inlet width (in the axial direction) was 0.5, the flow lies well along the shroud plate as illustrated by Fig. 4. Consequently, it is possible to suppress noise arising at a frequency corresponding to the product of the rotational speed and the number of vanes. Moreover, the energy loss of the impeller of Figs. 1 and 2 is low.
  • The shroud plate 97 is straight from its outer circumference to the innermost point of connection 99 as viewed in the axial plane, and there is only a small difference in height of the vane 96 between its inlet and outlet. Therefore, although the vane 96 is curved in the circumferential direction in a conventional manner, the force applied in caulking each protrusion of the vane 96 does not vary from one caulking point to another. Accordingly, the deformation of the shroud plate 97 and of the hub plate 98 is minimized even under the force applied to each caulking point. Consequently, hardly any gaps arise between the vanes 96, shroud plate 97 and hub plate 98, and leak flow between the pressure side and suction pressure side of the vane 96 is suppressed. Further, since any face deflection of the shroud plate 97 and of the hub plate 98 is small, unbalance hardly arises; thus, noise based on a frequency corresponding to the rotational speed decreases.
  • Another embodiment of the present invention will be described with reference to Fig. 5 showing a blower in partial sectional view. The shroud plate 97 is straight in its outer diameter portion, as viewed in the axial plane, and has a rounded portion 97a inwardly from the innermost point of connection 99, as in Fig. 2. The shroud plate 97 in this case is provided with a cylindrical portion 97b extending axially from the end of the rounded portion 97a. Furthermore, the blower casing 101 has an inwardly bent flange 101 a at its inner diameter region, so that the gap 100 is left between the flange 101 a and the cylindrical portion 97b of the impeller 90. Since the length of the gap 100 is much larger than the thickness of the shroud plate 97, the friction loss of the leak flow can be made very large, the leak flow can be reduced remarkably, and the efficiency of the electric blower can be improved.
  • A divisional application (94101775.8) has been filed, directed to features of the diffuser 89 of Figs. 1 and 2, such features being disclosed in EP-A-0 467 557.

Claims (6)

1. A vacuum cleaner blower assembly having a blower motor (81), a vaned centrifugal impeller (90) driven by the blower motor (81) to rotate about an axis and an air diffuser (89) radially beyond the periphery of the impeller, the impeller having a shroud plate (97) at one axial side of the vanes (96) of the impeller, characterised in that, to improve air flow efficiency at the impeller inlet as seen in axial section the shroud plate (97) extends from the inlet ends of the vanes (96) to an inner edge (97b) which is spaced radially and axially from the inlet ends of the vanes, and between the inlet ends of the vanes (96) and said inner edge (97b) the shroud plate curves with a convex face facing the regions of air flow to the vanes (96).
2. An impeller (90) for a vacuum cleaner having a central air inlet region around its axis of rotation, a plurality of vanes (96) extending outwardly from said inlet region and a shroud plate (97) covering said vanes (96) at one axial side thereof and attached to said vanes, characterised in that said shroud plate (97) extends substantially straight, as seen in axial cross-section, from an innermost point of connection (99) to each said vane to the outer peripheral ends of the vanes, and radially inwardly from said innermost point of connection (99), said shroud plate (97) is curved as seen in axial section, to provide a flange (97b) surrounding said inlet region and directed away from said vanes.
3. An impeller according to claim 2 wherein said shroud plate (97) is frusto-conical in shape at its region adjacent said vanes (96).
4. An impeller according to claim 2 or claim 3 wherein the extremity of said flange (97b) of said shroud plate is at an angle of not more than 30 ° to the axis, as seen in axial cross-section.
5. An impeller according to any one of claims 2 to 4 wherein the ratio of (a) the radius of curvature of the shroud plate (97), at its region (97a) of curvature into said flange (97b), to (b) the vane inlet width in the axial direction, is in the range 0.5 to 1.0.
6. A vacuum cleaner having an impeller (90) according to any one of claims 2 to 5, a blower motor (81) coupled to said impeller (90) and a casing (92) covering said impeller, the casing (92) having an air inlet passage (93) for flow of air to said inlet region of said impeller, said air inlet passage being provided by an inward annular wall (92a) of said casing which, as seen in axial cross-section, overlaps said flange (97b) of said shroud plate at the radially inner side thereof.
EP91306038A 1990-07-20 1991-07-03 Blower assembly with impeller for vacuum cleaner Expired - Lifetime EP0467557B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP94101775A EP0602007B1 (en) 1990-07-20 1991-07-03 Vacuum cleaner having an impeller and diffuser

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP190540/90 1990-07-20
JP2190540A JP2852106B2 (en) 1990-07-20 1990-07-20 Vacuum cleaner and electric blower
JP19054090 1990-07-20

Related Child Applications (2)

Application Number Title Priority Date Filing Date
EP94101775A Division EP0602007B1 (en) 1990-07-20 1991-07-03 Vacuum cleaner having an impeller and diffuser
EP94101775.8 Division-Into 1994-02-07

Publications (3)

Publication Number Publication Date
EP0467557A1 EP0467557A1 (en) 1992-01-22
EP0467557B1 true EP0467557B1 (en) 1994-12-14
EP0467557B2 EP0467557B2 (en) 2001-09-26

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ID=16259788

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Application Number Title Priority Date Filing Date
EP91306038A Expired - Lifetime EP0467557B2 (en) 1990-07-20 1991-07-03 Blower assembly with impeller for vacuum cleaner
EP94101775A Expired - Lifetime EP0602007B1 (en) 1990-07-20 1991-07-03 Vacuum cleaner having an impeller and diffuser

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP94101775A Expired - Lifetime EP0602007B1 (en) 1990-07-20 1991-07-03 Vacuum cleaner having an impeller and diffuser

Country Status (4)

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EP (2) EP0467557B2 (en)
JP (1) JP2852106B2 (en)
KR (1) KR0180742B1 (en)
DE (2) DE69127832T2 (en)

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JPH02156920A (en) * 1988-12-09 1990-06-15 Hitachi Ltd Vacuum cleaner

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0874160A2 (en) 1997-04-23 1998-10-28 BSH Bosch und Siemens Hausgeräte GmbH Fan device
DE19855905B4 (en) * 1998-12-03 2013-02-21 BSH Bosch und Siemens Hausgeräte GmbH blower assembly

Also Published As

Publication number Publication date
EP0467557B2 (en) 2001-09-26
KR920002084A (en) 1992-02-28
EP0602007B1 (en) 1997-10-01
DE69127832D1 (en) 1997-11-06
EP0467557A1 (en) 1992-01-22
EP0602007A2 (en) 1994-06-15
JPH0481600A (en) 1992-03-16
EP0602007A3 (en) 1994-12-28
DE69105845D1 (en) 1995-01-26
DE69127832T2 (en) 1998-04-30
KR0180742B1 (en) 1999-02-01
DE69105845T2 (en) 1995-04-27
JP2852106B2 (en) 1999-01-27

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