WO2020257203A1 - Pompes à turbine - Google Patents

Pompes à turbine Download PDF

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Publication number
WO2020257203A1
WO2020257203A1 PCT/US2020/037944 US2020037944W WO2020257203A1 WO 2020257203 A1 WO2020257203 A1 WO 2020257203A1 US 2020037944 W US2020037944 W US 2020037944W WO 2020257203 A1 WO2020257203 A1 WO 2020257203A1
Authority
WO
WIPO (PCT)
Prior art keywords
impeller
pump
assembly
casing
outer housing
Prior art date
Application number
PCT/US2020/037944
Other languages
English (en)
Inventor
Jan STUIVER
Erik Burachinsky
William Parry
Steve Rose
Original Assignee
Ceco Environmental Ip Inc.
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Ceco Environmental Ip Inc. filed Critical Ceco Environmental Ip Inc.
Publication of WO2020257203A1 publication Critical patent/WO2020257203A1/fr

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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
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/0646—Units comprising pumps and their driving means the pump being electrically driven the hollow pump or motor shaft being the conduit for the working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D3/00—Axial-flow pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/5806—Cooling the drive system

Definitions

  • Fluid pumps may include an impeller that is rotated to pressurize a fluid (e.g., a liquid). Typically the impeller is driven by a motor or other suitable driver.
  • a pump may be used to pressurize fluid that is corrosive, particularly to metallic materials. In such a service, metallic components of the pump that come into contact with the fluid may experience corrosion, thereby decreasing the lifespan thereof.
  • the pump includes a casing assembly that includes a central axis, an upstream connector that is configured to engage with a first connector on a fluid line, and a downstream connector that is configured to engage with a second connector on the fluid line.
  • the pump includes an impeller rotatably disposed within the casing assembly.
  • the pump includes a driver assembly coupled to the casing assembly and annularly disposed about the impeller. The driver assembly is configured to rotate the impeller about the central axis.
  • the system includes a first pipe section, a second pipe section, and a pump mounted between the first pipe section and the second pipe section.
  • the pump includes a casing assembly including a central axis.
  • the pump includes an impeller rotatably disposed within the casing assembly.
  • the pump includes a driver assembly coupled to the casing assembly and annularly disposed about the impeller. The driver assembly is configured to rotate the impeller about the central axis to pump fluid from the first pipe section to the second pipe section.
  • the method includes (a) mounting a pump between a pair of pipe sections of the fluid line.
  • the pump includes a casing assembly including a central axis, an impeller rotatably disposed within the casing assembly, and a driver assembly coupled to the casing assembly and annularly disposed about the impeller.
  • the method includes (b) rotating the impeller about the central axis with the driver assembly.
  • the method includes (c) flowing a fluid through the pair of pipe sections and the pump during (b).
  • Embodiments described herein comprise a combination of features and characteristics intended to address various shortcomings associated with certain prior devices, systems, and methods.
  • the foregoing has outlined rather broadly the features and technical characteristics of the disclosed embodiments in order that the detailed description that follows may be better understood.
  • the various characteristics and features described above, as well as others, will be readily apparent to those skilled in the art upon reading the following detailed description, and by referring to the accompanying drawings. It should be appreciated that the conception and the specific embodiments disclosed may be readily utilized as a basis for modifying or designing other structures for carrying out the same purposes as the disclosed embodiments. It should also be realized that such equivalent constructions do not depart from the spirit and scope of the principles disclosed herein.
  • FIG. 1 is a side view of a pump system according to some embodiments
  • FIG. 2 is a side cross-sectional view of a pump for use in the pump system of FIG. 1 according to some embodiments;
  • FIGS. 3 and 4 are side cross-sectional views of a suction casing and a discharge casing, respectively, of the pump of FIG. 2;
  • FIG. 5 is a side cross-sectional view of an impeller of the pump of FIG. 2;
  • FIG. 6 is a side cross-sectional view of a thermal transfer assembly of the pump of FIG. 2;
  • FIG. 7 is a side cross-sectional view of a diffuser of the pump of FIG. 2;
  • FIG. 8 is an exploded assembly view of the pump of FIG. 2;
  • FIGS. 9 and 10 are exploded assembly views of portions of the pump of FIG. 2;
  • FIG. 11 is a cross-sectional view of the pump system of FIG. 1;
  • FIGS. 12 and 13 are schematic side views of embodiments of a thermal transfer system for use with the pump of FIG. 2 according to some embodiments;
  • FIG. 14 is side cross-sectional view of a wax mold core for manufacturing an impeller of the pump of FIG. 2 according to some embodiments;
  • FIGS. 15 and 16 are sequential perspective views of a molding process utilizing the wax mold core of FIG. 14 according to some embodiments.
  • the terms“including” and“comprising” are used in an open-ended fashion, and thus should be interpreted to mean“including, but not limited to. . . ”
  • the term“couple” or“couples” is intended to mean either an indirect or direct connection. Thus, if a first device couples to a second device, that connection may be through a direct connection of the two devices, or through an indirect connection that is established via other devices, components, nodes, and connections.
  • the terms“axial” and“axially” generally mean along or parallel to a given axis (e.g., central axis of a body or a port), while the terms“radial” and“radially” generally mean perpendicular to the given axis.
  • an axial distance refers to a distance measured along or parallel to the axis
  • a radial distance means a distance measured perpendicular to the axis.
  • pumps may include an impeller that is driven or rotated by a separate driver or motor.
  • the motor and/or the pump is supported on separate base or foundation (e.g., a concrete pad). Therefore, the location of pumps within a facility is typically determined by the available floor spacing for the motor foundation.
  • additional lengths or runs of piping (or other conduit) may be called for to fluidly couple the fluid lines to the potentially distally disposed pump.
  • embodiments disclosed herein include pumps (e.g., turbine pumps) including an integrated motor or driver that are configured to be coupled within and along a fluid line or pipe.
  • system 1000 includes turbine pump 800 (or more generally“pump 800”) that is disposed along a fluid line 920.
  • pump 800 is coupled between and in-line with a pair of pipe or conduit sections 920a, 920b such that a central or longitudinal axis 805 (“axis 805”) of pump 800 is aligned with a central axis 925 of fluid line 920.
  • pump 800 is configured to induce or drive a flow of fluid along fluid line 920 in a flow direction 950 from pipe section 920a to pipe section 920b.
  • pipe section 920a may be referred to herein as an“upstream pipe section”
  • pipe section 920b may be referred to herein as a“downstream pipe section.”
  • turbine pump 800 comprises a casing assembly 100, an impeller assembly 200, a driver assembly 300, a diffuser 500, and a thermal transfer assembly 400 all concentrically disposed along axis 805.
  • Driver assembly 300 and thermal transfer assembly 400 are mounted to casing assembly 100 and impeller assembly 200 and diffuser 500 are disposed within casing assembly 100.
  • impeller assembly 200 is rotated about axis 805 by driver assembly 300 to pressurize a fluid (e.g., a liquid) within fluid line 920 (see e.g., FIG. 1) so that the fluid is flowed from upstream pipe section 920a toward and through downstream pipe section 920b along flow direction 950 as previously described.
  • a fluid e.g., a liquid
  • pump 800 may be constructed from non-metallic materials so as to decrease the overall weight of pump 800 and to avoid corrosion due to contact with potentially corrosive fluids flowing therethrough (e.g., salt water).
  • casing assembly 100 includes a first or suction casing 102 and a second or discharge casing 120.
  • suction casing 102 includes a first or upstream end 102a, a second or downstream end 102b opposite upstream end 102a, and a throughbore 104 extending axially between ends 102a, 102b.
  • suction casing 102 includes a first or upstream connector 106 at upstream end 102a, a second or downstream connector 108 proximate to downstream end 102b, a cylindrical body 103 extending axially between connectors 106, 108, and a cylindrical projection or lip 107 extending axially from downstream connector 108 to downstream end 102b.
  • a seal gland 114 extends radially inward into bp 107 that receives a sealing member (e.g., O-ring) 150 therein.
  • Connectors 106, 108 may be any suitable device or structure for coupling with a corresponding connector or device on fluid line 920 or within pump 800 (see e.g., FIG.
  • connectors 106, 108 comprise flanges.
  • Upstream connector 106 includes a planar engagement face or surface 106a
  • downstream connector 108 includes a planar engagement face or surface 108a.
  • Engagement surface 108a of downstream connector 108 includes an axially extending circumferential groove or channel 112.
  • a plurality of bolt holes 116 and bolt holes 118 may be provided through upstream connector 106 and downstream connector 108, respectively. Note that only one of the bolt holes 116 and one of the bolt holes 118 are visible in FIGS. 2 and 3 due to the arrangement of the cross-sectional views shown therein.
  • a radially extending downstream facing annular shoulder 109 (“shoulder 109”) is disposed within throughbore 104 such that throughbore 104 includes a first or upstream section 104a extending axially from upstream end 102a to shoulder 109 and second or downstream section 104b extending axially form shoulder 109 to downstream end 102b.
  • Downstream section 104b has a larger inner diameter than upstream section 104a.
  • discharge casing 120 includes a first or upstream end 120a, a second or downstream end 120b opposite upstream end 120a, and a throughbore 124 extending axially between ends 120a, 120b.
  • discharge casing 120 includes a first or upstream connector 128 proximate to upstream end 120a, a second or downstream connector 126 at downstream end 120b, a cylindrical body 123 extending axially between connectors 128, 126, and a cylindrical projection or lip 127 extending axially from upstream connector 128 to upstream end 120a.
  • a seal gland 134 extends radially inward into cylindrical projection 127 that receives a sealing member (e.g., O-ring) 152 therein.
  • Connectors 126, 128 may similar to connectors 106, 108, previously described for suction casing 102 (see e.g., FIGS. 2 and 3). Thus, connector 126, 128 may be any suitable device or structure for coupling with a corresponding connector or device on fluid line 920 or within pump 800. In this embodiment, connectors 126, 128 comprise flanges. Downstream connector 126 includes a planar engagement face or surface 126a, and upstream connector 128 includes a planar engagement face or surface 128a. Engagement surface 128a of upstream connector 128 includes an axially extending circumferential groove or channel 132.
  • a radially extending annular projection 136 (“projection 136”) is disposed within throughbore 124 so that throughbore 124 includes a first or upstream section 124a extending axially from upstream end 120a to projection 136 and second or downstream section 124b extending axially from projection 136 to downstream end 120b.
  • Projection 136 defines a first or upstream facing annular shoulder 137 and a second or downstream facing annular shoulder 139.
  • Upstream section 124a has a larger inner diameter than downstream section 124b.
  • a radially extending annular recess 138 is disposed within downstream section 124b of throughbore 124.
  • impeller assembly 200 generally includes an impeller 202, a pair of impeller wear rings 220a, 220b and a magnet assembly 230.
  • impeller 202 comprises an outer housing 204, a central hub 206 disposed within outer housing 204, and a plurality of impeller vanes 208 (or more simply “vanes 208”) extending between central hub 206 and outer housing 204.
  • outer housing 204 is a cylindrical member that includes a first or upstream end 204a, a second or downstream end 204b opposite upstream end 204a.
  • outer housing 204 includes a radially outer cylindrical surface 201 and a radially inner cylindrical surface 203 both extending axially between ends 204a, 204b.
  • outer housing 204 (or a portion thereof), may be non-cylindrical in shape.
  • central hub 206 is a solid member (non hollow) that is disposed within outer housing 204 along axis 805 and includes a first or upstream end 206a, a second or downstream end 206b opposite upstream end 206a.
  • Upstream end 206a is proximate upstream end 204a of outer housing 204
  • downstream end 206b is disposed at downstream end 204b of outer housing 204.
  • central hub 206 is generally conical in shape and thus includes a varying cross-section between ends 206a, 206b. In particular, the circumference and diameter of central hub 206 progressively increase between ends 206a and 206b.
  • upstream end 206a includes a rounded or hemispherical surface 207.
  • the hemispherical surface 207 may reduce turbulence for the fluid flowing within outer housing 204 and the generally conical shape of central hub 206 may progressively decrease the flow area within outer housing 204 for fluids flowing from upstream end 204a toward downstream end 204b. This decrease in the flow area may increase the localized flow rate along axis 805 and the pressure of the fluid flowing through impeller 202 during operations.
  • central hub 206 may include non-linear cross-section changes (e.g., a parabolic).
  • Vanes 208 extend generally radially from central hub 206 to radially inner cylindrical surface 203 of outer housing 204.
  • vanes 208 are circumferentially spaced (e.g., uniformly circumferentially spaced) about axis 805.
  • all or some of the vanes 208 may be axially spaced from one another along axis 805.
  • each of the vanes 208 of this embodiment extend generally helically (e.g., along a constant or varying helical pitch) about central hub 206 between ends 206a, 206b.
  • each of the vanes 208 is generally curved between central hub 206 and radially inner cylindrical surface 203 of outer housing 204.
  • each vane 208 generally curves in an upstream direction, or toward upstream ends 206a, 204a of central hub 206 and outer housing 204 when moving radially outward from central hub 206 toward radially inner cylindrical surface 203.
  • vanes 208 may extend generally linearly between central hub 206 and radially inner cylindrical surface 203 in other embodiments.
  • the axial thickness of each vane 208 generally decreases when moving from central hub 206 toward radially inner cylindrical surface 203.
  • the axial thickness of vanes 208 may be generally constant between central hub 206 and radially inner cylindrical surface 203. Further, while not specifically shown it should be appreciated that the axial thickness of each vane 208 may vary (e.g., increase and/or decrease) or may remain generally constant between its corresponding upstream and downstream ends. Still further, in some embodiments local cross-sectional variations may be included along vanes 208 to optimize flow characteristics through impeller 202 during operations.
  • the generally helical configuration of vanes 208 may vary along the axial direction (e.g., along axis 805, between ends 206a, 206b) and/or along the radial direction (e.g., radially between central hub 206 and radially inner cylindrical surface 203 of outer housing 204).
  • vanes 208 may have a varying helical pitch along the axial length between ends 206a, 206b.
  • the helical pitch increases the vanes 208 axially advance a greater distance along axis 805 for a given amount of angular twist about axis 805.
  • the helical pitch of vanes 208 at the first end 206a is different from the helical pitch of vanes 208 at second end 206b.
  • vanes 208 may have helical pitch which varies as a function of radial position between central hub 206 and radially inner cylindrical surface 203.
  • the helical pitch of vanes 208 may increase and/or decrease when moving radially from the attachment central hub 206 and the radially inner cylindrical surface 203.
  • other variations of the helical pitch of vanes 208 are contemplated herein.
  • outer housing 204, central hub 206 and vanes 208 are all formed as a monolithic piece or member (i.e., impeller 202).
  • outer housing 204, central hub 206, and vanes 208 may comprise the same material(s) (e.g., fiberglass).
  • the impeller 202 (including outer housing 204, central hub 206, and vanes 208) generally rotates about axis 805 to increase the pressure and velocity of the fluid flowing therethrough.
  • impeller 202 is symmetrical about axis 805 such that its rotating moment of inertia is concentric about axis 805.
  • vanes 208 are monolithically formed with outer housing 204 and central hub 206 as previously described, fluids flowing through impeller 202 (e.g., between ends 204a, 204b of outer housing 204 are prevented from flowing between outer housing 204 and vanes 208 and between vanes 208 and central hub 206. Accordingly, the fluid is forced to flow in a generally helical or twisting path about axis 805 between vanes 208 as it flows axially between ends 204a, 204b of outer housing 204.
  • each impeller wear ring 220a, 220b includes an annular base 222 including a central aperture 221 extending axially therethrough, and a cylindrical sleeve 223 extending axially from annular base 222.
  • Each of the impeller wear rings 220a, 220b are disposed on outer housing 204 of impeller 202, such that wear ring 220a is disposed over upstream end 204a of outer housing 204, and wear ring 220b is disposed over downstream end 204b of outer housing 204.
  • upstream end 204a of outer housing 204 is received within wear ring 220a such that radially outer cylindrical surface 201 is engaged with the corresponding cylindrical sleeve 223 and upstream end 204a is engaged with the corresponding annular base 222.
  • downstream end 204b of outer housing 204 is received within wear ring 220b such that radially outer cylindrical surface 201 is engaged with the corresponding cylindrical sleeve 223 and downstream end 204b is engaged with the corresponding annular base 222.
  • central apertures 221 in wear rings 220a, 220b are aligned with radially inner surface 203.
  • central apertures 221 are flush with radially inner cylindrical surface 203.
  • magnet assembly 230 comprises a cylindrical ring or sleeve 232, and a plurality of magnets 240 mounted to sleeve 232.
  • sleeve 232 includes an axially extending radially inner cylindrical surface 231 and an axially extending radially outer cylindrical surface 233.
  • the plurality of magnets 240 are mounted to radially outer cylindrical surface 233.
  • magnets 240 are uniformly circumferentially spaced along radially outer cylindrical surface 233 relative to axis 805.
  • magnets 240 are permanent magnets; however, it should be appreciated that in other embodiments magnets 240 may comprise electrically conductive materials (e.g., aluminum bars) such as may found within an induction rotor, or may comprise one or more electro magnetic coils (e.g., conductive coils or windings, such as cooper, surrounding a ferromagnetic or ferromagnetic core, such as iron).
  • electrically conductive materials e.g., aluminum bars
  • electro magnetic coils e.g., conductive coils or windings, such as cooper, surrounding a ferromagnetic or ferromagnetic core, such as iron.
  • magnet assembly 230 is disposed about outer housing 204 of impeller 202 such that radially inner surface 231 of sleeve 232 is engaged with radially outer cylindrical surface 201 of outer housing 204.
  • sleeve 232 is positioned axially between wear rings 220a, 220b such that sleeve 232 is axially spaced from cylindrical sleeves 223 of each ring 220a, 220b.
  • sleeve 232 is generally axially centered between ends 204a, 204b of outer housing 204.
  • Sleeve 232 may be secured to radially outer cylindrical surface 201 of outer housing 204 in any suitable fashion.
  • sleeve 232 may be secured to outer housing 204 via a friction fit.
  • sleeve 232 may be welded, brazed, adhered (e.g., with an adhesive) or otherwise secured to outer housing 204.
  • impeller assembly 200 is disposed axially between suction casing 102 and discharge casing 120.
  • a pair of casing wear rings 210a, 210b are disposed within throughbores 104, 124 of casings 102, 120, respectively.
  • Each casing wear ring 210a, 210b includes an annular base 212 including a central aperture 211 extending axially therethrough, and a cylindrical sleeve 213 extending axially from base 212.
  • Casing wear ring 210a is received within downstream section 104b of throughbore 104 of suction casing 102 such that the corresponding annular base 212 is engaged with annular shoulder 109 and the corresponding central aperture 211 is generally aligned and flush with upstream section 104a of throughbore 104.
  • casing wear ring 210b is received within downstream section 124b of throughbore 124 of discharge casing 120 such that the corresponding base 212 is engaged with upstream facing annular shoulder 137.
  • impeller assembly 200 is received within casing assembly 100 such that impeller wear ring 220a is received within casing wear ring 210a and impeller wear ring 220b is received within casing wear ring 210b.
  • cylindrical sleeves 223 of wear rings 220a, 220b may slidingly engage with cylindrical sleeves 213 of casing wear rings 210a, 210b, respectively, and central apertures 221 and 211 of wear rings 220a, 220b, and 210a, 210b, 240a are generally flush with one another along axis 805.
  • impeller assembly 200 rotates about axis 805 within casing assembly 100 such that wear rings 220a, 220b rotate within and relative to casing wear rings 210a, 210b, respectively. Accordingly, direct contact between outer housing 204 of impeller and casings 102, 120 is avoided, and wear rings 210a, 210b, 220a, 220b may be considered wear parts that are replaced at regular intervals.
  • driver assembly 300 is annularly disposed about magnet assembly 230 and is axially positioned between suction casing 102 and discharge casing 120.
  • driver assembly 300 is disposed over the cylindrical projections 107, 127, and is axially disposed between planar engagements faces 108a, 128a of connectors 108, 128 of casings 102, 120, respectively.
  • a sealing sleeve 330 is disposed radially between cylindrical projections 107, 127 of casings 102, 120 and driver assembly 300, such that sealing members 150, 152 are radially compressed within seal glands 114, 134 of casings 102, 120 (see e.g., FIGS. 3 and 4).
  • fluids are prevented (or at least restricted) from flowing between seal sleeve 330 and cylindrical projections 107, 127 during operations.
  • driver assembly 300 defines a plurality of windings or coils 304 of conductive wire (e.g., conductive coils or windings, such as cooper, surrounding a ferromagnetic or ferromagnetic core, such as iron) that are disposed or arranged circumferentially about axis 805.
  • conductive wire e.g., conductive coils or windings, such as cooper, surrounding a ferromagnetic or ferromagnetic core, such as iron
  • electrical current may be routed through the conductive coils 304 so as to induce varying magnetic fields.
  • the induced magnetic fields within driver assembly are configured to drive rotation of impeller assembly 200 about axis 805 within casing assembly 100 during operations.
  • driver assembly 300 may include alternative designs in other embodiments.
  • windings 304 may be replaced with a plurality of permanent magnets arranged circumferentially around axis 805, or a plurality of electrically conductive members (e.g., aluminum bars) such as might be used within an induction motor.
  • thermal transfer assembly 400 includes heat sink or body 402 and a cooling coil 420 circumferentially wrapped around body 402.
  • Body 402 includes a first or upstream end 402a, a second or downstream end 402b opposite upstream end 402a, and a throughbore 401 extending axially between ends 402a, 402b that is defined by a radially inner cylindrical surface 407.
  • body 402 includes a first or upstream connector 404 proximate upstream end 402a, a second or downstream connector 406 proximate downstream end 402b, and a radially outer cylindrical surface 403 extending axially between connectors 404, 406.
  • Connectors 406, 408 may comprise any suitable structure or device for mating with another component or member.
  • connectors 404, 406 comprises flanges that each include a plurality of mounting bores 410 extending axially therein (note: only one of the mounting bores 410 are visible in each of the connectors 404, 406 in FIGS. 2 and 6 due to the arrangement of the cross-sectional views shown therein).
  • body 402 includes a first or upstream lip 409a extending axially upstream connector 404 to upstream end 402a, and a downstream second bp 409b extending axially from downstream connector 406 to downstream end 402b. Lips 409a, 409b may also be generally referred to herein as“axial projections 409a, 409b.”
  • Cooling coil 420 comprises an elongate tube or conduit that is wrapped (e.g., helically) about radially outer surface 403 of body 402.
  • Cooling coil 420 may comprise any suitable material, and in some embodiments may comprise a conductive material (e.g., a metal) so as to conduct thermal energy away from body 402 during operations.
  • a cooling fluid e.g., diverted fluid from fluid line 920, a separate cooling fluid, etc.
  • cooling coil 420 comprises includes a circular cross-section; however, other cross-sections are contemplated (e.g., elliptical, rectangular, square, etc.).
  • Body 402 may be constructed from any suitable material, and in some embodiments may be made of a material having a high thermal conductivity (e.g., having a coefficient of thermal conductivity above 5-W/m°K). In addition, in some embodiments, body 402 may be made from a non-magnetic or possibly a weakly magnetic material (e.g., aluminum, 316 stainless, nickel alloys, alumina filled epoxy, etc.). In some embodiments, there may be intimate contact between cooling coil 420 and radially outer cylindrical surface 403 of body 402 since increased contact areas and compressive forces may increase the heat flow capacity between body 402 and cooling coil 420 during operations.
  • a material having a high thermal conductivity e.g., having a coefficient of thermal conductivity above 5-W/m°K
  • body 402 may be made from a non-magnetic or possibly a weakly magnetic material (e.g., aluminum, 316 stainless, nickel alloys, alumina filled epoxy, etc.).
  • ridges, fins or other suitable projections may be disposed along body 402 (particularly along radially outer surface 403) to increase the circumferential contact area between each segment of cooling coil 420 and body 402.
  • increased contact may be achieved between cooling coil 420 and body 402 by tightly wrapping cooling coil 420 around body 402 and/or by applying an external clamp (not shown) around the perimeter of cooling coil 420.
  • thermal transfer assembly 400 is engaged axially between connectors 108, 128 of casings 102, 120, respectively.
  • upstream connector 404 on body 402 is engaged with planar engagement surface 108a on downstream connector 108 of upstream casing and downstream connector 406 on body 402 is engaged with engagement surface 128a on upstream connector 128 of discharge casing 120.
  • upstream bp 409a is received within circumferential groove 112 in planar engagement face 108a
  • downstream bp 409b is received within circumferential groove 132 in planar engagement face 128a.
  • a plurality of fasteners 160 are received within aligned pairs of the bolt holes 118 on connector 108 of suction casing 102 and the mounting bores 410 on upstream connector 404 and within aligned pairs of the bolt holes 140 on upstream connector 128 and the mounting bores 410 on downstream connector 406.
  • the fasteners extend through bolt holes 118, 140 and are threadably engaged with the corresponding mounting holes 410 so as to secure body 402 axially between each of the casings 102, 120.
  • thermal transfer assembly 400 when thermal transfer assembly 400 is mounted between casings 102, 120 as described above, radially inner surface 407 of body 402 may contact (or is closely positioned) to driver assembly 300 (particularly coils 304).
  • driver assembly 300 particularly coils 304.
  • heat which is generated within coils 304 during operations may be transferred (e.g., conducted, radiated, etc.) to body 402 and then further transferred away from pump 800 via cooling coil 420 as noted above.
  • diffuser 500 comprises an outer housing 502, a central hub 506, and a plurality of diffuser vanes 508 (or more simply“vanes 508”) extending between central hub 506 and outer housing 502.
  • outer housing 502 is a cylindrical member that includes a first or upstream end 502a, a second or downstream end 502b opposite upstream end 502a.
  • outer housing 502 includes a radially outer cylindrical surface 504 and a radially inner cylindrical surface 503 both extending axially between ends 502a, 502b.
  • outer housing 502 (or a portion thereol), may be non-cylindrical in shape.
  • central hub 506 is a solid member (non-hollow) disposed within outer housing 502 along axis 805 and includes a first or upstream end 506a, a second or downstream end 506b opposite upstream end 506a.
  • Upstream end 506a extends axially past upstream end 502a of outer housing 502, and downstream end 506b is disposed at downstream end 502b of outer housing 502.
  • central hub 506 includes a first or upstream section 507 extending axially from upstream end 506a, and a second or downstream section 509 extending axially from upstream section 507 to downstream end 506b.
  • Upstream section 507 is generally cylindrical in shape, while downstream section 509 is generally conical in shape.
  • of diffuser 500 may include a varying cross-section between ends 502a, 502b.
  • the circumference and diameter of central hub 506 is generally constant within upstream section 507, and generally decreases when moving axially within downstream section 509 from upstream section 507 to downstream end 506b.
  • downstream end 506b includes a rounded or hemispherical surface 510.
  • the hemispherical surface 510 may reduce turbulence for the fluid flowing within outer housing 502 and the generally conical shape of downstream section 509 of central hub 506 may progressively increase the flow area within outer housing 502 for fluids flowing from upstream end 502a toward downstream end 502b. It should be appreciated that other shapes and profiles are contemplated for central hub 506.
  • central hub 506 may include non-linear cross-section changes (e.g., a parabolic).
  • vanes 508 extend generally radially outward from central hub 506 to radially inner surface 503 of outer housing 502.
  • Each vane 508 includes a first or upstream end 508a and a second or downstream end 508b opposite upstream end 508a.
  • Upstream end 508a is proximate upstream end 502a of outer housing 502 and downstream end 508b is proximate downstream end 502b of housing 502.
  • vanes 508 are circumferentially spaced (e.g., uniformly circumferentially spaced) about axis 805.
  • each of the vanes 508 of this embodiment are configured to generally convert a twisting or helical flow pattern for a fluid (e.g., such as a fluid that has flowed across impeller 202 previously described) into a generally axial or laminar flow pattern. That is, vanes 508 are configured to straighten the fluid flowing from impeller 202.
  • a fluid e.g., such as a fluid that has flowed across impeller 202 previously described
  • vanes 508 are configured to straighten the fluid flowing from impeller 202.
  • each vane 508 extends generally helically at upstream end 508a, but then progressively transitions to a generally axial orientation at downstream end 508b.
  • the upstream end 508a vanes 508 may generally correspond (e.g., having a similar or equal helical angle, pitch, etc.) to the helical direction or shape of vanes 208 of impeller 202 (see e.g., FIGS. 2 and 5) such that fluid flowing past impeller 200 is efficiently captured by diffuser 500, during operations.
  • vanes 508 extend generally helically along portions of central hub 506 proximate to upstream end 508a and couple with radially inner surface 503 of housing 502.
  • the axial thickness of each vane 508 generally decreases when moving from central hub 506 toward radially inner surface 503.
  • the axial thickness of vanes 508 may be generally may be constant between central hub 506 and radially inner surface 503.
  • the axial thickness of each vane 508 may vary (e.g., increase and/or decrease) or may remain generally constant between its corresponding upstream and downstream ends 508a, 508b, respectively.
  • vanes 508 may be included along vanes 508 to optimize flow characteristics through diffuser 500 during operations.
  • the general helical shape of vanes 508 of diffuser 500 e.g., for the portion of vanes 508 proximate upstream end 508a
  • outer housing 502, central hub 506, and vanes 508 are all monolithically formed as a single piece or member (i.e., diffuser 500).
  • outer housing 502, central hub 506, and vanes 508 may comprise the same material(s) (e.g., fiberglass).
  • fluid is flowed over the diffuser 500 (including outer housing 502, central hub 506, and vanes 508) to transition the flow pattern of the fluid from helical or twisting to laminar (or more laminar).
  • vanes 508 are monolithically formed with outer housing 502 and central hub 506 as previously described, fluids flowing through diffuser 500 (e.g., between ends 502a, 502b of outer housing 502) are prevented from flowing between outer housing 502 and vanes 508 and between vanes 508 and central hub 506. Accordingly, the fluid is forced to flow over vanes 508 as it flows axially between ends 502a, 502b of housing 502.
  • diffuser 500 is inserted within downstream section 124b of throughbore 124 in discharge casing 120 during operations.
  • diffuser 500 is inserted axially into downstream section 124b of throughbore 124 from downstream end 120b of casing 120 until upstream end 502a of outer housing 502 engages with downstream facing annular shoulder 139, and upstream end 506a of central hub 506 approaches downstream end 206b of central hub 206 along axis 805.
  • a retaining ring 520 is inserted within throughbore 124 (particularly downstream section 124b) and is radially expanded into annular recess 138.
  • turbine pump 800 is mounted within a fluid line (e.g., fluid line 920).
  • pump 800 is mounted within pump system 1000 between upstream section 920a and downstream section 920b of fluid line 920 so that axes 805, 925 are generally aligned with one another as previously described.
  • upstream connector 106 on suction casing 102 is engaged with a corresponding connector 910a on upstream section 920a and downstream connector 126 on discharge casing 120 is engaged with a corresponding connector 910b on downstream section 920b.
  • Connectors 910a, 910b include a plurality of bolt holes 912 that are aligned with the plurality of bolt holes 116, 142 on casings 102, 120, respectively.
  • fasteners e.g., bolts
  • Connectors 910a, 910b include a plurality of bolt holes 912 that are aligned with the plurality of bolt holes 116, 142 on casings 102, 120, respectively.
  • a suitable sealing member (e.g., a gasket, O-ring, etc.) may be disposed between the engaged connectors 910a, 116 and 910b, 126 so as to prevent fluids flowing within fluid line 920 and pump 800 from leaking during operations.
  • Upstream section 920a and downstream section 920b of fluid line 920 each include a corresponding flow bore 922a and 922b, respectively.
  • flow bore 922a of upstream section 920a is in fluid communication with flow bore 922b of downstream section 920b through the throughbore 104 of suction casing 102, the outer housings 204, 502 of impeller 202 and diffuser 500, respectively, (as well as the central apertures 211, 221 of wear rings 210, 220 on either side of impeller 202), and the throughbore 124 of discharge casing 120.
  • driver assembly 300 induces a varying magnetic field to thereby rotate impeller 202 about axis 805 within casing assembly 100 as previously described above.
  • turbine pump 800 produces fluid flow through fluid line 920 from upstream section 920a to downstream section 920b in flow direction 950.
  • diffuser 500 remains generally stationary, and serves to transition the fluid flowing from impeller from a helical or twisting flow to a more laminar flow downstream of turbine pump 800 as previously described above.
  • thermal transfer assembly 400 cools driver assembly 300, which may be prone to heating by the electrical current flowing therein.
  • thermal transfer assembly 400 may transfer heat away from driver assembly 300 via body 402 as well as with cooling coil 420.
  • cooling coil 420 may receive a recycle stream of fluid from fluid line 920 and in particular from downstream section 920b during operations.
  • a relatively small amount of the fluid flowing through fluid line 920 is diverted from downstream section 920b and is supplied to cooling coil 420 via a conduit 923 (e.g., tubing).
  • the fluid After flowing through cooling coil 420, the fluid is then recycled back to fluid line 920 via a conduit 924 (e.g., tubing 924), such as at a position upstream of pump 800 (e.g., within upstream section 920a as shown).
  • a conduit 924 e.g., tubing 924
  • the fluid After being emitted from cooling coil 420, the fluid may be at an elevated temperature, and thus, may be routed through a suitable heat exchanger prior to flowing back into fluid line 920 (e.g., upstream section 920a) as previously described above.
  • a separate fluid (that is, a fluid that is not the fluid flowing through fluid line 920) may be flowed through cooling coil 420 to facilitate heat transfer operations.
  • cooling fluid e.g., air, water, ethyl glycol, oil, or two-phase evaporative fluids such as R134a, etc.
  • conduit 1252 e.g., tubing
  • the cooling fluid may be recycled back to cooling unit 1250 via a conduit 1254 (e.g., tubing) (which may include one or more heat exchangers, pumps, etc.).
  • components of turbine pump 800 may be manufactured out of non-metallic materials (e.g., fiberglass, carbon fiber, aramid fiber) such that the pump 800 may be more effectively utilized to pump corrosive fluids (e.g., such as salt water).
  • non-metallic materials e.g., fiberglass, carbon fiber, aramid fiber
  • corrosive fluids e.g., such as salt water
  • an example manufacturing process is described below for manufacturing some or all of the components of pump 800.
  • the manufacturing process described herein is employs a resin transfer molding (RTM) process.
  • RTM molding reinforcing fibers, such as fiberglass, are oriented prior to the injection of resin into the mold, thereby increasing the strength of the molded component in the direction of fiber orientation.
  • the manufacturing process described herein can be applied to other types of molding processes, such as, for example, compression molding.
  • compression molding the orientation of the reinforcing fibers is generally less controlled or uncontrolled, thus causing the compression-molded component to have a greater thickness than a like RTM-molded component having a given strength.
  • a mold core having a shape that is the inverse of the molded component is disposed inside a mold cavity.
  • the mold core may comprise a wax.
  • the wax comprising the core may comprise a "Blue Blend" machinable wax, a wax commercially available from“Machinable Wax.com”, Lake Ann, Mich.
  • the "Blue Blend" wax has a Specific density of approximately 0.035 pounds/cubic inch, a hardness of 50-55 (Shore D scale), a flash point of 575° F., a softening point of 226° F., a drop melting point of 227° F., and a 5% volumetric shrinkage rate.
  • the wax comprising the mold core is carveable.
  • wax structure 60 which may be used to produce impeller 202 (see e.g., FIG. 5), yet a similar procedure may be used for diffuser 500 (see e.g., FIG. 7) as well as other components of pump 800. More particularly, wax structure 60 has a shape suitable to provide a mold core 62 that is disposed inside a mold cavity so as to facilitate fabrication of a RTM-fabricated impeller 202. Thus, the size of mold core 62 may be defined by the geometry of the desired wax structure 60.
  • mold core 62 defines an inverse structure of impeller 202, such that solid regions of mold core 62 defines open regions or air pockets along impeller 202 that are material-free, while open regions or air pockets defined by mold core 62 defines solid structures along impeller 202.
  • mold dies that define the shape of wax structure 60 may be made of silicon rubber. Silicon rubber minimizes the dissipation of heat as wax structure 60 hardens during fabrication of wax structure 60. Additionally, heat lamps may be selectively used during the fabrication of wax structure 60 to prevent local hardening of the wax, for example at the open end of the mold which is exposed to ambient air temperatures.
  • Multi-axis computer numerical control (CNC) machines can mill or otherwise machine cutouts 64 in wax structure 60 that are in the shape of impeller vanes 208.
  • reinforcing fibers such as fiberglass fibers
  • the fiberglass carrying core 62 is placed into a mold cavity 72 that is defined between a pair of mold dies 74, and a resin is injected into the mold cavity 72 to form impeller 202. Once the resin hardens, mold dies 74 may be separated to reveal impeller 202.
  • the injected resin may be any suitable resin, such as, for example a non-corrosive resin (e.g., as a vinyl-ester or epoxy).
  • the injected and cured resin has a melting point of greater than 350° F, and greater than that of wax mold core 62, such that wax mold core 62 may be melted away without damaging impeller 202.
  • the resin may heated to facilitate the curing thereof, and thus it may be possible to select a mold curing temperature that concurrently cures and removes mold core 62.
  • 267° F may provide a suitable curing temperature in some embodiments which may melt away a wax mold core 62 made of Blue Blend wax (e.g., above 221 F) without melting the cured resin at 350° F.
  • any residual wax which may remain on impeller 202 after wax core 62 is melted, may be flushed out of turbine pump 800 during operations. Without being limited to this or any other theory, the residual wax may be soft enough such that it may pass through turbine pump 800 and fluid line 920 during normal operations.
  • both the molded impeller 202 and diffuser 500 are homogeneous one piece solid components when produced by the methods described herein above. More particularly the elements of each component are fabricated as a single integral structure, free of joints in the form of glue, non-molded resin, bolts, fasteners, or other discrete connections.
  • impeller vanes 208 are integrally connected to both outer housing 204 and central hub 206.
  • diffuser vanes 508 are integrally connected to outer surface 502 and central hub 506.
  • embodiments disclosed herein include turbine pumps with integrated motor or drive units (e.g., pump 800), which may allow the pumps to be installed and supported within segments of a fluid line (e.g., fluid line 920). As a result, a separate support base or foundation for the motor or drive unit of the pump may be omitted.
  • some embodiments of the turbine pumps disclosed herein are constructed (wholly or partially) of non-metallic materials, such that they may be used to pump corrosive fluids (e.g., salt water).
  • magnet assembly 230 that is separately secured to impeller 202
  • magnet assembly 230 (or portions thereol) are integrated or monolithically formed with impeller 202.
  • magnets 240 of magnet assembly 230 may be molded onto and/or within outer housing 204 of impeller 202 during an embodiment of the above described manufacturing process. That is, the magnets 240 may be placed within the mold cavity along with core 62 (see FIGS. 15 and 16) so that the resulting impeller 202 may have magnets embedded therein.
  • some of the embodiments of pump 800 may supplement or replace cooling coils 420, with other thermal transfer devices.
  • thermal transfer assembly 400 may include a so-called cooling jacket to channel or flow a volume of cooling fluid about body 402.
  • body 402 may define or include a channel or annulus that may receive a flow of cooling fluid therethrough during operations (e.g., such as cooling fluids discussed above with respect to FIGS. 12 and 13).
  • the channel or annulus may be subdivided using fins, baffles, etc.
  • other heat transfer components or devices may be used within pump either in lieu of or in addition to those described above (e.g., fins, blowers, fluid baths, etc.).
  • a pump comprises: a casing assembly, wherein the casing assembly includes a central axis and comprises: an upstream connector that is configured to engage with a first connector on a fluid line; and a downstream connector that is configured to engage with a second connector on the fluid line; an impeller rotatably disposed within the casing assembly; and a driver assembly coupled to the casing assembly and annularly disposed about the impeller; wherein the driver assembly is configured to rotate the impeller about the central axis.
  • a second embodiment can include the pump of the first embodiment, wherein the impeller comprises an outer housing, a central hub, and a plurality of vanes engaged with and extending between the central hub and the outer housing.
  • a third embodiment can include the pump of the second embodiment, wherein the outer housing is cylindrical in shape and includes a radially inner cylindrical surface and a radially outer cylindrical surface, and wherein each of the plurality of vanes is engaged with the radially inner cylindrical surface.
  • a fourth embodiment can include the pump of the third embodiment, wherein the casing assembly comprises a suction casing and a discharge casing, wherein the suction casing comprises a throughbore that is flush with the radially inner cylindrical surface of the outer housing of the impeller.
  • a fifth embodiment can include the pump of the third or fourth embodiment, wherein the central hub includes a first end and a second end opposite the first end, wherein the first end of the central hub includes a hemispherical surface.
  • a sixth embodiment can include the pump of any one of the third to fifth embodiments, comprising a plurality of magnets coupled to the radially outer cylindrical surface of the outer housing of the impeller, wherein the driver assembly is configured to induce a varying magnetic field to rotate the impeller and the plurality of magnets about the central axis.
  • a seventh embodiment can include the pump of any one of the second to sixth embodiments, wherein the outer housing, the central hub, and the plurality of vanes of the impeller are formed as a monolithic member.
  • An eighth embodiment can include the pump of the seventh embodiment, wherein the impeller comprises fiberglass.
  • a ninth embodiment can include the pump of any one of the first to eighth embodiments, further comprising a thermal transfer assembly comprising: a body annularly disposed about the driver assembly; and a cooling coil disposed about the body, wherein the cooling coil comprises an elongate tube that is configured to receive a flow of cooling fluid therethrough.
  • a tenth embodiment can include the pump of the ninth embodiment, wherein the casing assembly comprises a suction casing and a discharge casing, wherein the body of the thermal transfer assembly is disposed axially between the suction casing and the discharge casing.
  • a system comprises: a first pipe section; a second pipe section; and a pump mounted between the first pipe section and the second pipe section, wherein the pump comprises: a casing assembly including a central axis; an impeller rotatably disposed within the casing assembly; and a driver assembly coupled to the casing assembly and annularly disposed about the impeller; wherein the driver assembly is configured to rotate the impeller about the central axis to pump fluid from the first pipe section to the second pipe section.
  • a twelfth embodiment can include the system of the eleventh embodiment, wherein the impeller comprises: a cylindrical outer housing; a central hub disposed within the outer housing; and a plurality of impeller vanes engaged with and extending between the central hub and the outer housing.
  • a thirteenth embodiment can include the system of the twelfth embodiment, further comprising: a diffuser disposed within the casing assembly, axially adjacent the impeller, wherein the diffuser is configured to straighten a flow of fluid flowing from the impeller; and wherein the diffuser comprises: a cylindrical outer housing; a central hub disposed within the outer housing of the diffuser; and a plurality of diffuser vanes engaged with and extending between the central hub of the diffuser and the outer housing of the diffuser.
  • a fourteenth embodiment can include the system of any one of the eleventh to thirteenth embodiments, further comprising a thermal transfer assembly comprising: a body mounted to the casing assembly and disposed annularly about the driver assembly; and a cooling coil disposed about the body, wherein the cooling coil comprises an elongate tube that is configured to receive a flow of cooling fluid therethrough.
  • a fifteenth embodiment can include the system of the fourteenth embodiment, wherein the cooling coil is fluidly coupled to the first pipe section and the second pipe section.
  • a method of pumping a fluid through a fluid line comprises: mounting a pump between a pair of pipe sections of the fluid line, wherein the pump comprises: a casing assembly including a central axis; an impeller rotatably disposed within the casing assembly; and a driver assembly coupled to the casing assembly and annularly disposed about the impeller; rotating the impeller about the central axis with the driver assembly; and flowing a fluid through the pair of pipe sections and the pump while rotating the impeller.
  • a seventeenth embodiment can include the method of the sixteenth embodiment, further comprising: straightening a flow of the fluid with a diffuser disposed axially adjacent the impeller.
  • An eighteenth embodiment can include the method of the sixteenth or seventeenth embodiment, wherein rotating the impeller comprises: inducing a varying magnetic field with the driver assembly; and attracting a plurality of magnets with the varying magnetic field.
  • a nineteenth embodiment can include the method of any one of the sixteenth to eighteenth embodiments, further comprising: flowing a cooling fluid through a coil that is wrapped about a body of a thermal transfer assembly, wherein the body is mounted to the casing assembly and is disposed annularly about the driver assembly.
  • a twentieth embodiment can include the method of the nineteenth embodiment, wherein flowing the cooling fluid through the coil comprises: flowing a stream of fluid from a downstream section of the pair of pipe sections to the coil; and flowing the stream of fluid through the coil after; and flowing the stream of fluid from the coil to an upstream section of the pair of pipe section after flowing the stream through the coil.

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

Abstract

Selon des modes de réalisation, l'invention concerne des pompes, ainsi que des systèmes et des procédés s'y rapportant. Dans un mode de réalisation, la pompe comprend un carter (100) qui comprend un axe central, un connecteur en amont (106) qui est conçu pour s'engager avec un premier connecteur sur une conduite de fluide, et un connecteur en aval (108) qui est conçu pour s'engager avec un second connecteur sur la conduite de fluide. De plus, la pompe comprend une turbine (200) disposée de manière à pouvoir tourner à l'intérieur du carter. En outre, la pompe comprend un ensemble d'entraînement (300) accouplé au carter et disposé de manière annulaire autour de la turbine. L'ensemble d'entraînement est conçu pour faire tourner la turbine autour de l'axe central.
PCT/US2020/037944 2019-06-17 2020-06-16 Pompes à turbine WO2020257203A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US16/443,034 2019-06-17
US16/443,034 US20200392960A1 (en) 2019-06-17 2019-06-17 Turbine pumps

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Publication number Priority date Publication date Assignee Title
US11808265B2 (en) * 2019-12-06 2023-11-07 Kinetic Technology Systems, Llc Energy-conserving fluid pump
US20240175339A1 (en) * 2022-11-30 2024-05-30 Halliburton Energy Services, Inc. High volume axial flow electric submersible pump (esp) pump stage

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0657654A1 (fr) * 1993-12-09 1995-06-14 Westinghouse Electric Corporation Pompe pour fluides
DE29920437U1 (de) * 1999-11-22 2001-02-22 Taube GmbH, 52249 Eschweiler Pumpengehäuse aus glasfaserverstärktem Kunststoff
US20030143093A1 (en) * 2002-01-25 2003-07-31 Mabe William J. Liquid cooled integrated rotordynamic motor/generator station with sealed power electronic controls
EP1840026A2 (fr) * 2006-03-31 2007-10-03 Goriziane S.p.A. Système de traction électrique utilisant une volute

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0657654A1 (fr) * 1993-12-09 1995-06-14 Westinghouse Electric Corporation Pompe pour fluides
DE29920437U1 (de) * 1999-11-22 2001-02-22 Taube GmbH, 52249 Eschweiler Pumpengehäuse aus glasfaserverstärktem Kunststoff
US20030143093A1 (en) * 2002-01-25 2003-07-31 Mabe William J. Liquid cooled integrated rotordynamic motor/generator station with sealed power electronic controls
EP1840026A2 (fr) * 2006-03-31 2007-10-03 Goriziane S.p.A. Système de traction électrique utilisant une volute

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