EP0442070A1 - Sheet metal pump casing - Google Patents
Sheet metal pump casing Download PDFInfo
- Publication number
- EP0442070A1 EP0442070A1 EP90123674A EP90123674A EP0442070A1 EP 0442070 A1 EP0442070 A1 EP 0442070A1 EP 90123674 A EP90123674 A EP 90123674A EP 90123674 A EP90123674 A EP 90123674A EP 0442070 A1 EP0442070 A1 EP 0442070A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- reinforcement element
- wall
- transverse
- main body
- casing according
- 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
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
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
- F04D29/4273—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps suction eyes
-
- 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
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
- F04D29/4266—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps made of sheet metal
Definitions
- the present invention relates to a sheet metal casing with differentiated thickness for centrifugal pumps, of the type comprising a substantially cup-shaped main body formed by a peripheral wall which is continuously joined to a transverse end wall, means for connecting the main body to a transverse sealing plate which is arranged opposite to the end wall so as to define a pressure chamber enclosing an impeller, a substantially tangential delivery port and a substantially axial suction port.
- a further attempt to stiffen the suction inlet and the end wall of the pump body consists in providing some box-like annular structures with a more or less complicated shape which are welded or are integrally formed with the coupling flange so as to give rigidity to the entire assembly.
- These structures are not sufficiently resistant and are also relatively bulky and prevent rusty bolts from being removed owing to the extremely small space available between the flange and the pump body, which is mainly occupied by the reinforcement structures.
- the aim of the present invention is to eliminate the aforementioned disadvantages by providing a sheet metal casing for centrifugal pump which has high characteristics of resistance and reliability as well as considerable constructive simplicity and reduced dimensions.
- a particular object of the present invention is to provide a sheet metal casing with differentiated structure which is capable of easily withstanding, without deformation, both the internal stresses generated by the pressurized fluid and the external ones transmitted through the suction inlet.
- Not least object of the present invention is to provide a sheet metal casing with differentiated thickness for centrifugal pump which can be easily obtained starting from commonly commercially available elements and materials and which is furthermore advantageous from a merely economical point of view.
- a sheet metal casing with differentiated thickness for centrifugal pump of the above described type, characterized in that it comprises a substantially funnel-shaped reinforcement element, said element having a transverse end portion which is at least partially and substantially frusto-conically shaped and is arranged inside said main body and a substantially cylindrical longitudinal end portion extending from said body coaxially to said suction inlet, said transverse end portion of said reinforcement element being at least peripherally superimposed and rigidly coupled to the end wall of said main body by means of a liquid-tight seal to define the transverse wall of the casing adjacent to the suction inlet in contact with the pumped liquid.
- the thickness of the reinforcement element is greater than that of the main body and is such as to integrally withstand, without deformation, both the pressure forces which act inside the chamber in a substantially axial direction and the static and dynamic stresses which act on the suction inlet.
- the sheet metal casing has, at the end wall and at the suction port, a thickness and therefore a resistance which are greater than those of monolithic structures of the prior art, but it preserves the external geometric characteristics thereof, allowing extremely easy and unrestricted assembly and maintenance.
- the casing according to the invention is formed by a main body 2, made of stamped plate, having substantially the shape of a cup, i.e. defined by a substantially cylindrical peripheral side wall 3 and by a transverse end wall 4 which uniformly blends into the wall 3 along the region 5.
- the casing further comprises a suction port 6 which extends axially from the end wall 4 of the pump body and a pressure port 7 which extends tangentially from the peripheral wall 3 of the body 2.
- the peripheral wall 3 of the body 2 preferably has a spiral-shaped volute 8 the end portion of which is joined to the discharge outlet 7.
- a seal-holder plate 9 is provided on the high-pressure side opposite to the suction port 6 and is connected to a flange 10 of the main body 2 by means of a counter-flange 11 and appropriate coupling means, such as bolts, not depicted in the drawings.
- the seal-holder wall 9 centrally supports a sealing pack 12 which seals a pressure chamber 13 within which an impeller 14, driven by a motor shaft 15, can rotate.
- a substantially funnel-shaped reinforcement element is arranged at least partially within the main body 2 and is thicker than said main body.
- the reinforcement element generally indicated by the reference numeral 20, comprises a transverse end portion 21 having at least partially a frusto-conical shape, preferably with a slightly curved cross-section, and a longitudinal end portion 22 having a substantially cylindrical or slightly tapered shape. While the transverse portion 21 is located inside the main body 2, the longitudinal portion 22 protrudes from the main body 2 passing through an axial opening 23 of the end wall thereof which defines a folded edge.
- the transverse wall 21 is at least partially superimposed and rigidly coupled to the inner surface of the end wall 4, proximate to the peripheral edge 24 of the element 20 to provide a liquid-tight seal.
- a bead of high-resistance, and perfectly fused welding accomplished for example by means of a laser beam applied by transparency through the wall 4, is executed in peripheral portions 25.
- the coupling between the transverse portion 21 of the reinforcement element 20 and the end wall 4 of the body 2 may optionally be ensured by traditional spot-welding 16, though these latter are not absolutely necessary.
- the longitudinal portion 22 of the reinforcement element 20 may be nested simply into the folded edge 23 of the end wall 4 without any welded connections.
- the folded edge 23 of the apertured end wall 4 might have a diameter which is even greater than the illustrated one, since the wall 4 extends until it completely covers the welding bead 25 to thereby ensure optimum coupling with the transverse wall 21 of the element 20.
- the element 20 defines the transverse wall of the sheet metal casing and is so sized to withstand, without deformation, both the pressure forces exerted by the pumped fluid in an axial direction, and the static and dynamic loads transmitted through the suction port 6.
- the latter loads are generated by the external piping, not illustrated in the drawings, which is connected to the suction port 6 through a stamped plate flange 27 which is welded at 28 to the end of the longitudinal portion 22 of the element 20.
- the transverse portion 21 of the element 20 is connected to the longitudinal portion 22 by means of an intermediate portion 20 including an annular corrugation 31 which forms a sealing ring for the impeller 14.
- the longitudinal portion 22 of the element 20 provides the inlet duct of the suction port 6 and needs no further elements to form the inner wall of the inlet.
- the embodiment illustrated in figure 2 differs from that of figure 1 essentially insofar as the longitudinal portion 22 of the element 20 has a larger diameter than the suction port 6.
- the inlet duct of the latter element is formed by a sleeve 40 having a partially frusto-conical shape and is inserted inside the longitudinal portion 22 coaxially thereto.
- the outer end 41 of the sleeve 40 is welded to the flange 27, whereas the inner end has a more complex geometry, comprising a peripheral edge 42 shaped complementarily to the transverse wall 21 of the element 20 and connected thereto at 43 to provide a liquid-tight seal, also in this case, by laser welding.
- the sleeve 40 has an annular corrugation 44 which forms a sealing ring 45 for the impeller 14.
- the longitudinal end portion 22 of the stiffening element forms an annular flange 46 which is frontally welded at 47 to the central portion 48 of the flange 27.
- hermetical sealing with respect to the pumped fluid is ensured at the welding bead 25 and at the welding bead 43, so that the pressure of the fluid to be pumped is integrally acting upon the transverse wall 21 of the reinforcement element 20 and partially on the strongly stiffened annular corrugation 44 of the sleeve 40.
- the invention achieves the proposed aim and objects, and in particular the fact is stressed that it provides the maximum reliability and resistance of the casing while keeping unchanged the advantages of the prior art regarding easiness of installation and use.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
- Rotary Pumps (AREA)
- Paper (AREA)
- Reciprocating Pumps (AREA)
Abstract
Description
- The present invention relates to a sheet metal casing with differentiated thickness for centrifugal pumps, of the type comprising a substantially cup-shaped main body formed by a peripheral wall which is continuously joined to a transverse end wall, means for connecting the main body to a transverse sealing plate which is arranged opposite to the end wall so as to define a pressure chamber enclosing an impeller, a substantially tangential delivery port and a substantially axial suction port.
- Many pump bodies of the foregoing type are known which are integrally made of sheet metal; in said pump bodies, the basic problem to be solved resides in the limited resistance to static and dynamic loads acting upon the end wall and on the axial suction port defined in the central portion of the end wall of the main body. Many attempts have been made to solve this problem by providing pump body stiffenings arranged in these overloaded regions, for example providing a suction port of considerable thickness,obtained by casting, and subsequently welding it to the end wall of the pump body by circumferential beads. While this solution provides a suction port of considerable rigidity and fatigue resistance, it cannot impart the same mechanical resistance to the coupling region of the inlet port and the end wall of the pump body.
- A further attempt to stiffen the suction inlet and the end wall of the pump body consists in providing some box-like annular structures with a more or less complicated shape which are welded or are integrally formed with the coupling flange so as to give rigidity to the entire assembly. These structures, however, are not sufficiently resistant and are also relatively bulky and prevent rusty bolts from being removed owing to the extremely small space available between the flange and the pump body, which is mainly occupied by the reinforcement structures.
- Other attempts have been made to stiffen the suction inlet and the region of coupling to the end wall of the pump body, by using radial ridges welded to said end wall; this solution allows to stiffen the wall of the pump body but does not give the necessary resistance to the suction ducts if said ducts are made of stamped plate.
- The aim of the present invention is to eliminate the aforementioned disadvantages by providing a sheet metal casing for centrifugal pump which has high characteristics of resistance and reliability as well as considerable constructive simplicity and reduced dimensions.
- Within the scope of the above described aim, a particular object of the present invention is to provide a sheet metal casing with differentiated structure which is capable of easily withstanding, without deformation, both the internal stresses generated by the pressurized fluid and the external ones transmitted through the suction inlet.
- Not least object of the present invention is to provide a sheet metal casing with differentiated thickness for centrifugal pump which can be easily obtained starting from commonly commercially available elements and materials and which is furthermore advantageous from a merely economical point of view.
- This aim, the objects mentioned and others which will become apparent hereinafter are achieved by a sheet metal casing with differentiated thickness for centrifugal pump, of the above described type, characterized in that it comprises a substantially funnel-shaped reinforcement element, said element having a transverse end portion which is at least partially and substantially frusto-conically shaped and is arranged inside said main body and a substantially cylindrical longitudinal end portion extending from said body coaxially to said suction inlet, said transverse end portion of said reinforcement element being at least peripherally superimposed and rigidly coupled to the end wall of said main body by means of a liquid-tight seal to define the transverse wall of the casing adjacent to the suction inlet in contact with the pumped liquid.
- In particular, the thickness of the reinforcement element is greater than that of the main body and is such as to integrally withstand, without deformation, both the pressure forces which act inside the chamber in a substantially axial direction and the static and dynamic stresses which act on the suction inlet.
- By this solution, the sheet metal casing has, at the end wall and at the suction port, a thickness and therefore a resistance which are greater than those of monolithic structures of the prior art, but it preserves the external geometric characteristics thereof, allowing extremely easy and unrestricted assembly and maintenance.
- Further characteristics and advantages will become apparent from the description of two preferred but not exclusive embodiments of two sheet metal casings with differentiated thickness for centrifugal pump, according to the invention, illustrated only by way of non-limitative example in the accompanying drawings, wherein:
- Fig. 1 is a partially sectional side view of a first embodiment of the casing according to the invention, taken along an axial vertical plane;
- Fig. 2 is a partially sectional side view of a second embodiment of the casing according to the invention, taken along an axial vertical plane.
- With reference to the cited figures, the same reference numerals have been used for identical or similar elements in the two embodiments. The casing according to the invention, generally indicated by the
reference numeral 1, is formed by amain body 2, made of stamped plate, having substantially the shape of a cup, i.e. defined by a substantially cylindricalperipheral side wall 3 and by atransverse end wall 4 which uniformly blends into thewall 3 along theregion 5. - The casing further comprises a
suction port 6 which extends axially from theend wall 4 of the pump body and apressure port 7 which extends tangentially from theperipheral wall 3 of thebody 2. Theperipheral wall 3 of thebody 2 preferably has a spiral-shaped volute 8 the end portion of which is joined to thedischarge outlet 7. - A seal-
holder plate 9 is provided on the high-pressure side opposite to thesuction port 6 and is connected to aflange 10 of themain body 2 by means of acounter-flange 11 and appropriate coupling means, such as bolts, not depicted in the drawings. The seal-holder wall 9 centrally supports asealing pack 12 which seals apressure chamber 13 within which animpeller 14, driven by amotor shaft 15, can rotate. - Conveniently, according to the invention, a substantially funnel-shaped reinforcement element is arranged at least partially within the
main body 2 and is thicker than said main body. - In particular, the reinforcement element, generally indicated by the
reference numeral 20, comprises atransverse end portion 21 having at least partially a frusto-conical shape, preferably with a slightly curved cross-section, and alongitudinal end portion 22 having a substantially cylindrical or slightly tapered shape. While thetransverse portion 21 is located inside themain body 2, thelongitudinal portion 22 protrudes from themain body 2 passing through anaxial opening 23 of the end wall thereof which defines a folded edge. - Advantageously, the
transverse wall 21 is at least partially superimposed and rigidly coupled to the inner surface of theend wall 4, proximate to theperipheral edge 24 of theelement 20 to provide a liquid-tight seal. To this end, a bead of high-resistance, and perfectly fused welding, accomplished for example by means of a laser beam applied by transparency through thewall 4, is executed inperipheral portions 25. Additionally, the coupling between thetransverse portion 21 of thereinforcement element 20 and theend wall 4 of thebody 2 may optionally be ensured by traditional spot-welding 16, though these latter are not absolutely necessary. It is noted that thelongitudinal portion 22 of thereinforcement element 20 may be nested simply into the foldededge 23 of theend wall 4 without any welded connections. In practice, the foldededge 23 of the aperturedend wall 4 might have a diameter which is even greater than the illustrated one, since thewall 4 extends until it completely covers thewelding bead 25 to thereby ensure optimum coupling with thetransverse wall 21 of theelement 20. - Thus, the
element 20 defines the transverse wall of the sheet metal casing and is so sized to withstand, without deformation, both the pressure forces exerted by the pumped fluid in an axial direction, and the static and dynamic loads transmitted through thesuction port 6. - In particular, the latter loads are generated by the external piping, not illustrated in the drawings, which is connected to the
suction port 6 through a stampedplate flange 27 which is welded at 28 to the end of thelongitudinal portion 22 of theelement 20. - The
transverse portion 21 of theelement 20 is connected to thelongitudinal portion 22 by means of anintermediate portion 20 including an annular corrugation 31 which forms a sealing ring for theimpeller 14. - In the examplified embodiment represented in figure 1, the
longitudinal portion 22 of theelement 20 provides the inlet duct of thesuction port 6 and needs no further elements to form the inner wall of the inlet. - The embodiment illustrated in figure 2 differs from that of figure 1 essentially insofar as the
longitudinal portion 22 of theelement 20 has a larger diameter than thesuction port 6. The inlet duct of the latter element is formed by asleeve 40 having a partially frusto-conical shape and is inserted inside thelongitudinal portion 22 coaxially thereto. Theouter end 41 of thesleeve 40 is welded to theflange 27, whereas the inner end has a more complex geometry, comprising a peripheral edge 42 shaped complementarily to thetransverse wall 21 of theelement 20 and connected thereto at 43 to provide a liquid-tight seal, also in this case, by laser welding. In the vicinity of its inner end, thesleeve 40 has anannular corrugation 44 which forms asealing ring 45 for theimpeller 14. - Advantageously, the
longitudinal end portion 22 of the stiffening element forms an annular flange 46 which is frontally welded at 47 to thecentral portion 48 of theflange 27. - Also in this case, hermetical sealing with respect to the pumped fluid is ensured at the
welding bead 25 and at thewelding bead 43, so that the pressure of the fluid to be pumped is integrally acting upon thetransverse wall 21 of thereinforcement element 20 and partially on the strongly stiffenedannular corrugation 44 of thesleeve 40. - In both cases, the resistance of the transverse wall of the casing, as well as that of the suction inlet, are significantly increased, whereas the outer geometry is not substantially altered to facilitate insertion and removal of cut bolts from the
flange 27. - From the foregoing it can thus be seen that the invention achieves the proposed aim and objects, and in particular the fact is stressed that it provides the maximum reliability and resistance of the casing while keeping unchanged the advantages of the prior art regarding easiness of installation and use.
- The pump casing according to the invention is susceptible to numerous modifications and variations, all of which are within the scope of the inventive concept.
- All the details may furthermore be replaced by other technically equivalent elements: in practice, the materials employed, so long as compatible with the specific use, as well as the contingent shapes and dimensions, may be any according to the requirements.
- Where technical features mentioned in any claim are followed by reference signs, those reference signs have been included for the sole purpose of increasing the intelligibility of the claims and accordingly, such reference signs do not have any limiting effect on the scope of each element identified by way of example by such reference signs.
Claims (11)
- Sheet metal casing (1) with differentiated thickness for centrifugal pump, comprising a substantially cup-shaped main body (2) which is formed by a peripheral wall (3) continuously joined to a transverse end wall (4), means (10) for coupling said main body (2) to a transverse sealing plate (9) opposite to said end wall so as to define a pressure chamber (13) enclosing an impeller (14), a substantially tangential delivery port (7) and a substantially axial suction port (6), characterized in that it comprises a substantially funnel-shaped reinforcement element (20) having a transverse end portion (21) which is at least partially and substantially frusto-conically shaped and is arranged inside said main body (2), and a substantially cylindrical longitudinal end portion (22) which protrudes from said body coaxially to said suction port, said transverse end portion (21) of said reinforcement element (20) being at least peripherally superimposed and rigidly sealingly coupled, with the end wall (4) of said main body (2) at the junction with the side wall (3) thereof, to thereby define the transverse wall of the casing adjacent to said suction port in contact with the pumped liquid.
- Casing according to claim 1, characterized in that the thickness of said main body (2) is so sized to integrally withstand without deformation the pressure forces acting within said chamber in a substantially radial direction.
- Casing according to claim 1, characterized in that the thickness of said reinforcement element (20) is greater than that of said main body (2) and is so sized to integrally withstand without deformation both the pressure forces acting inside said chamber in a substantially axial direction and the static and dynamic stresses acting upon said suction port (6).
- Casing according to claim 1, characterized in that said substantially cylindrical longitudinal end portion (22) of said reinforcement element is rigidly connected to a sheet metal flange (27) which defines the coupling flange for said suction port (6).
- Casing according to claim 1, characterized in that said transverse end portion (21) of said reinforcement element comprises at least one peripheral edge (24) which is uniformly in contact with the end wall (4) of said body (2) at a region thereof proximate to the connection (5) between said end wall (4) and said side wall (3), in this contact region there being provided circumferential laser or the like weldings (25) providing liquid-tight and rigid coupling between said body (2) and said reinforcement element (20).
- Casing according to claim 5, characterized in that said transverse peripheral portion (21) and said longitudinal portion (22) of said reinforcement element (20) are monolithically connected by an intermediate portion (30) provided with a circumferential corrugation (31) adapted to define a sealing ring for the impeller (14).
- Casing according to claim 5, characterized in that said longitudinal end portion (22) of said reinforcement element defines the inner wall of said suction port (6).
- Casing according to claim 1, characterized in that said longitudinal end portion (22) of said reinforcement element encloses a coaxial tubular sleeve (49) which defines the inner wall of said suction inlet.
- Casing according to claim 8, characterized in that said sleeve (40) has an outer end (41) which is welded to the coupling flange (27) of said delivery port (7) and an inner end (44) which is welded to the intermediate portion (30) of said reinforcement element.
- Casing according to claim 9, characterized in that said inner end (44) of said sleeve is partially corrugated so as to define a sealing ring (45) for said impeller and is rigidly sealingly coupled, to said reinforcement element (20) by means of a circumferential laser or the like welding (42).
- Casing according to claim 10, characterized in that said sleeve (40) is radially spaced from said cylindrical portion (22) of said reinforcement element (20) and has, at its outermost end, a substantially annular radial fold (46) which is welded (48) to said coupling flange.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
IT85524A IT1239829B (en) | 1990-02-13 | 1990-02-13 | DIFFERENTIATED THICKNESS PUMP BODY |
IT8552490 | 1990-02-13 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0442070A1 true EP0442070A1 (en) | 1991-08-21 |
EP0442070B1 EP0442070B1 (en) | 1995-04-12 |
Family
ID=11327493
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP90123674A Expired - Lifetime EP0442070B1 (en) | 1990-02-13 | 1990-12-10 | Sheet metal pump casing |
Country Status (6)
Country | Link |
---|---|
EP (1) | EP0442070B1 (en) |
AT (1) | ATE121167T1 (en) |
DE (1) | DE69018608T2 (en) |
DK (1) | DK0442070T3 (en) |
ES (1) | ES2070984T3 (en) |
IT (1) | IT1239829B (en) |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0494675A2 (en) * | 1991-01-11 | 1992-07-15 | Ebara Corporation | Pump casing made of sheet metal |
DE4101611A1 (en) * | 1991-01-11 | 1992-07-16 | Ebara Corp | Pump casing made of sheet metal |
US6082960A (en) * | 1995-08-30 | 2000-07-04 | Sterling Fluid Systems Gmbh | Regenerative pump |
DE19838798C2 (en) * | 1998-08-26 | 2002-08-29 | Ind Tech Res Inst | Pump housing made of a sheet metal and process for its manufacture |
FR2958324A1 (en) * | 2010-03-30 | 2011-10-07 | Snecma | RIGIDIFIED TURBOMACHINE HOUSING |
JP2014177881A (en) * | 2013-03-14 | 2014-09-25 | Nippon Densan Corp | Pump |
CN109196230A (en) * | 2016-03-30 | 2019-01-11 | 三菱重工发动机和增压器株式会社 | Impeller, rotating machinery, turbocharger |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3059582A (en) * | 1959-04-24 | 1962-10-23 | Bell & Gossett Co | Motor pump unit |
DE3517828A1 (en) * | 1985-05-17 | 1986-11-20 | Klein, Schanzlin & Becker Ag, 6710 Frankenthal | Pump casing |
US4775295A (en) * | 1985-05-17 | 1988-10-04 | Klein, Schanzlin & Becker Aktiengesellschaft | Centrifugal pump casing |
-
1990
- 1990-02-13 IT IT85524A patent/IT1239829B/en active IP Right Grant
- 1990-12-10 DK DK90123674.5T patent/DK0442070T3/en active
- 1990-12-10 EP EP90123674A patent/EP0442070B1/en not_active Expired - Lifetime
- 1990-12-10 DE DE69018608T patent/DE69018608T2/en not_active Expired - Fee Related
- 1990-12-10 ES ES90123674T patent/ES2070984T3/en not_active Expired - Lifetime
- 1990-12-10 AT AT90123674T patent/ATE121167T1/en not_active IP Right Cessation
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3059582A (en) * | 1959-04-24 | 1962-10-23 | Bell & Gossett Co | Motor pump unit |
DE3517828A1 (en) * | 1985-05-17 | 1986-11-20 | Klein, Schanzlin & Becker Ag, 6710 Frankenthal | Pump casing |
US4775295A (en) * | 1985-05-17 | 1988-10-04 | Klein, Schanzlin & Becker Aktiengesellschaft | Centrifugal pump casing |
Non-Patent Citations (1)
Title |
---|
PATENT ABSTRACTS OF JAPAN vol. 12, no. 41 (M-666)(2888) 06 February 1988, & JP-A-62 195496 (HITACHI LTD) 28 August 1987, * |
Cited By (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0494675A2 (en) * | 1991-01-11 | 1992-07-15 | Ebara Corporation | Pump casing made of sheet metal |
DE4101611A1 (en) * | 1991-01-11 | 1992-07-16 | Ebara Corp | Pump casing made of sheet metal |
EP0494675A3 (en) * | 1991-01-11 | 1992-09-02 | Ebara Corp | Pump casing made of sheet metal |
US5310310A (en) * | 1991-01-11 | 1994-05-10 | Ebara Corporation | Pump casing made of sheet metal |
US5358380A (en) * | 1991-01-11 | 1994-10-25 | Ebara Corporation | Pump casing made of sheet metal |
US6082960A (en) * | 1995-08-30 | 2000-07-04 | Sterling Fluid Systems Gmbh | Regenerative pump |
DE19838798C2 (en) * | 1998-08-26 | 2002-08-29 | Ind Tech Res Inst | Pump housing made of a sheet metal and process for its manufacture |
FR2958324A1 (en) * | 2010-03-30 | 2011-10-07 | Snecma | RIGIDIFIED TURBOMACHINE HOUSING |
EP2375006A1 (en) * | 2010-03-30 | 2011-10-12 | Snecma | Stiffened turbo pump casing |
JP2014177881A (en) * | 2013-03-14 | 2014-09-25 | Nippon Densan Corp | Pump |
CN109196230A (en) * | 2016-03-30 | 2019-01-11 | 三菱重工发动机和增压器株式会社 | Impeller, rotating machinery, turbocharger |
JPWO2017168642A1 (en) * | 2016-03-30 | 2019-02-14 | 三菱重工エンジン&ターボチャージャ株式会社 | Impeller, rotating machine, turbocharger |
EP3434908A4 (en) * | 2016-03-30 | 2019-04-03 | Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. | Impeller, rotary machine, and turbocharger |
US10883513B2 (en) | 2016-03-30 | 2021-01-05 | Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. | Impeller, rotary machine, and turbocharger |
Also Published As
Publication number | Publication date |
---|---|
ES2070984T3 (en) | 1995-06-16 |
IT1239829B (en) | 1993-11-15 |
DK0442070T3 (en) | 1995-07-03 |
EP0442070B1 (en) | 1995-04-12 |
ATE121167T1 (en) | 1995-04-15 |
IT9085524A1 (en) | 1991-08-13 |
DE69018608D1 (en) | 1995-05-18 |
DE69018608T2 (en) | 1995-10-12 |
IT9085524A0 (en) | 1990-02-13 |
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