WO2016210119A1 - Système d'entraînement à engrenages et mise en œuvre de ce dernier - Google Patents

Système d'entraînement à engrenages et mise en œuvre de ce dernier Download PDF

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Publication number
WO2016210119A1
WO2016210119A1 PCT/US2016/039001 US2016039001W WO2016210119A1 WO 2016210119 A1 WO2016210119 A1 WO 2016210119A1 US 2016039001 W US2016039001 W US 2016039001W WO 2016210119 A1 WO2016210119 A1 WO 2016210119A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
interface
plate member
displacement device
impeller
Prior art date
Application number
PCT/US2016/039001
Other languages
English (en)
Inventor
David Charles Hokey
Raed Zuhair Hasan
Michael Morgan KRUSZYNSKI
Arun Kumar
Matthew Simmons
Rodney ROBERTS
Original Assignee
Howden Roots Llc
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 Howden Roots Llc filed Critical Howden Roots Llc
Publication of WO2016210119A1 publication Critical patent/WO2016210119A1/fr

Links

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
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
    • F04D29/624—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for elastic fluid pumps

Definitions

  • the subject matter disclosed herein relates generally to fluid displacement devices and, more specifically, to a device having a compressor and motor directly coupled together.
  • Engineers expend great efforts to improve performance of industrial machines that are configured to move and pressurize fluid (e.g., liquids and gasses). These efforts may focus on various areas including structure and control of the machines, wherein the machines may be "fluid displacement devices" such as pumps, compressors (e.g., centrifugal compressors), and blowers. At least one difference between these different types of machinery resides in the operating pressures of the exit flow that discharges from the machines, e.g., to a process line. Examples of process lines may be found in various applications including chemical, water-treatment, petro-chemical, resource recovery and delivery, refinery, and like sectors and industries. Each area may be useful to increase the operating efficiency with little to no cost to operate the machine. Summary of the Disclosure
  • a fluid displacement device in one approach according to the disclosure includes an impeller and a drive system coupled with the impeller.
  • the drive system includes a drive gear directly mounted to a motor shaft, and a pinion gear coupled with the drive gear, wherein the pinion gear is configured to transfer rotation of the drive gear to turn the impeller.
  • a fluid displacement device in another approach according to the disclosure, includes an impeller and a drive system coupled with the impeller.
  • the drive system includes a drive gear directly mounted to a motor shaft of a motive unit, and a pinion gear in mated engagement with the drive gear, wherein the pinion gear is configured to transfer rotation of the drive gear to turn the impeller.
  • a method in another approach according to the disclosure, includes providing an impeller and a drive system coupled with the impeller.
  • the drive system includes a drive gear directly mounted to a motor shaft of a motive unit, and a pinion gear engaged with the drive gear.
  • the method further includes transferring rotation of the drive gear through the pinion gear to turn the impeller.
  • FIG. 1A a perspective view of an exemplary embodiment of a fluid
  • FIG. IB is a side view of the exemplary embodiment of the fluid displacement device of FIG. 1A;
  • FIG. 2 depicts a perspective view of the fluid displacement device of FIG. 1 in exploded form
  • FIG. 3 depicts an elevation view of the side of the fluid displacement device of FIG. 1 in exploded form
  • FIG. 4 depicts a elevation view of the side of the fluid displacement device of FIG. 1 in partially assembled form
  • FIG. 5 depicts a perspective view of the front of an example of a gear housing for use in the fluid displacement device of FIG. 1;
  • FIG. 6 depicts a perspective view of the back of an example of the gear housing of FIG. 5;
  • FIG. 7 depicts an elevation view of the cross-section of an example of the gear housing of FIG. 5;
  • FIG. 8 depicts a perspective view of the front of an example of an interface member for use in the fluid displacement device of FIG. 1;
  • FIG. 9 depicts a perspective view of the back of an example of the interface member of FIG. 8;
  • FIG. 10 depicts an elevation view of the cross-section of an example of the interface member of FIG. 8;
  • FIG. 11 depicts a perspective view of the back of an example of the fluid displacement device of FIG. 1 in partially assembled form
  • FIG. 12 depicts a cross-section of the side of an example of the fluid displacement device of FIG. 1 in partially assembled form
  • FIG. 13 depicts a plan view of the cross-section of the fluid displacement device of FIG. 1 in assembled form.
  • FIG. 14 depicts a cross-section of the side of an example of the fluid displacement device according to embodiments of the disclosure.
  • FIG. 15 depicts a flow diagram of an exemplary embodiment of a method to drive an impeller in a fluid displacement device.
  • spatially relative terms such as “beneath,” “below,” “lower,” “central,” “above,” “upper,” and the like, may be used herein for ease of describing one element's relationship to another element(s) as illustrated in the figures. It will be understood that the spatially relative terms may encompass different orientations of the device in use or operation in addition to the orientation depicted in the figures.
  • Examples of the motive unit include steam turbines, gas turbines, and electric motors.
  • the impeller may have a central body with a plurality of blades disposed thereon. In certain configurations, the blades are exposed. Other configurations enclose the blades on the impeller with a shroud or cover. This shroud secures to the impeller at the top of the blades.
  • rotation of the impeller draws a working fluid into the compressor.
  • the blades are configured to accelerate the working fluid outwardly from the center of rotation, ejecting the working fluid from the impeller under pressure.
  • the compressor directs the working fluid to a discharge.
  • the discharge couples with a pipe that connects the compressor to the process line.
  • Some embodiments include a drive system that is configured to simplify coupling of the drive motor to the impeller.
  • This feature can offer the following benefits: eliminate couplings and guards, eliminate bearings and power loss, eliminate shafts, e.g., low speed shafts, provide compact design, form splash lubricating system to eliminate oil pumps, provide better fits between drive unit and compressor, and modularize design to include components/cartridges that hold support bearings, shafts, gears, etc. At least these benefits as well as other capabilities may be realized in the disclosed subject matter described herein.
  • FIG. 1 illustrates a perspective view of an exemplary embodiment of a fluid displacement device 100 (also "device 100").
  • This embodiment has a front 102 (also, “first end 102) and a back 104 (also, "second end 104").
  • the device 100 may have an inlet 106 that allows working fluid F to enter into a volute casing 108.
  • the volute casing 108 is configured to direct the working fluid F to a nozzle member 110.
  • the working fluid F can exit the nozzle member 110 at a discharge 112 having certain desired flow parameters (e.g., flow rate, pressure, etc.).
  • the nozzle member 110 can mate with one or more collateral members (e.g., piping and/or conduit) to discharge the exit flow into a process line.
  • collateral members e.g., piping and/or conduit
  • this process line may be found in various applications including chemical, water-treatment, petro-chemical, resource recovery and delivery, refinery, and like sectors and industries.
  • FIGS. 2 and 3 illustrate the device 100 in explode form.
  • the device 100 may include an impeller 114 that couples with a shaft member 116 having a pinion gear 118 disposed thereon.
  • the device 100 can also have a bearing member 119 that can support the shaft member 116.
  • a drive gear 120 can couple with the pinion gear 118 as part of a drive system 121.
  • the device 100 can have a gear housing 122 that houses each of the gears 118, 120.
  • the gear housing 122 can mount to the volute casing 108 and with an interface member 124 that secures to a motive unit 126.
  • FIG. 4 illustrates an elevation view of the side of the device 100 in partially assembled view.
  • the device 100 employs a drive system 121 to rotate the impeller 114 at high speeds.
  • the device 100 may realize speeds for the impeller 114 in excess of 25,000 RPM.
  • the drive system 121 can include the gears 118, 120 and the motive unit 126.
  • the drive gear 120 may couple directly to the motive unit 126 at an interface 128 between the drive gear 120 and a motor shaft 130.
  • the interface 128 can form a mechanical connection that prevents (and/or reduces) relative movement between the drive gear 120 and the motor shaft 130.
  • the motor shaft 130 extends through a central opening 123 (FIG. 2) of the drive gear.
  • this mechanical connection may include a key-and-slot formation, a key-and-shrink fit, interferences fits, set screws, and related modalities to secure the drive gear 120 and the motor shaft 130 to one another to prevent relative movement therebetween.
  • FIGS. 5, 6, and 7 illustrate an example of the gear housing 122.
  • FIGS. 5 and 6 depict a perspective view of the example from the front 102 and the back 104, respectively.
  • FIG. 7 illustrates an elevation view of the cross-section of the side of the gear housing 122 taken at line 7-7 of FIG. 5.
  • the gear housing 122 is configured to receive and protect the gears 1 18, 120 (FIG. 1).
  • the gear housing 122 may have a body 132 with a casing side 134 (also, “first side 134") and an interface side 136 (also, "second side 136").
  • the body 132 may feature a plate member 138 with a plate surface 139 and a first aperture 140 that can receive at least part of the bearing member 1 19 (FIGS. 2 and 3).
  • the plate member 138 can be generally annular in shape with a plurality of bolt openings 142 disposed proximate the periphery.
  • the bolt openings 142 may form an array that populates the circumference of the plate member 138. This array may be disposed circumferentially about the central aperture 140 and/or otherwise match corresponding openings on the volute casing 108 (FIG. 1).
  • the bolt openings 142 can penetrate through the plate member 138.
  • This configuration can receive fasteners (e.g., bolts) to couple (or secure or mate) the plate member 138 to the volute casing 108 (FIG. 1).
  • the body 132 may also have a gear member 144 that couples with the plate member 138.
  • the gear member 144 may be cast from one of various materials (e.g., metal) for cost-efficient manufacture.
  • such casting may form the members 138, 144 integrally with one another, although this disclosure does contemplate fabrication of the gear housing 122 from one or more separate pieces (e.g., the members 138, 144) that affix to one another as a weldment and/or using like fastening techniques.
  • the body 132 may also incorporate a support member 146 interposed between the members 138, 142.
  • the support member 146 may include a generally annular member 148 that aligns with the central aperture 140.
  • One or more leg members 150 can radiate from proximate the annular member 148 outwardly toward the periphery of the plate member 138.
  • the leg members 150 may be spaced annularly apart from one another to form an array that at least partially circumscribes the annular member 148.
  • the gear member 144 can have a second aperture 152, which may be larger than the first aperture 140 to receive the drive gear 120.
  • the gear member 144 can also form an interface surface 154 with one or more threaded openings 156 disposed circumferentially about the second aperture 152.
  • the surfaces 139, 154 may be machined and/or result from secondary operation to ensure certain dimensional tolerances (e.g., flatness). This feature can ensure proper fit-up and function of interface member 124, as noted more below.
  • FIG. 7 depicts the interior of the gear member 144.
  • the interior may be configured to receive each of the gears 118, 120 (FIG. 1). These configurations can protect the gears 118, 120 from contaminants that can frustrate operation of the device 100.
  • the interior of the gear member 144 may form a chamber 158 or hollow space (or void). This hollow space may be sized to allow the gears 118, 120 (FIG. 1) to mesh and rotate during operation of the device 100.
  • the apertures 140, 152 can penetrate the material of the body 132.
  • the first aperture 140 may have a pair of bores (e.g., a first bore 160 and a second bore 162) in a counter-bore arrangement.
  • the larger of the two bores (e.g., the first bore 160) can reside proximate the casing side 134.
  • the smaller of the two bores (e.g., the second bore 162) can reside proximate the chamber 158, terminating at an opening that communicates with the chamber 158.
  • the second aperture 152 can have a third bore 164 that also terminates at an opening that communicates with the chamber 136.
  • some embodiments may include a transitory mount 165 to facilitate movement of the gear housing 122.
  • the transitory mount 165 may include rollers, casters, and like friction-reducing members. In this way, an end user can translate the gear housing 122 relative to (e.g., away from) the volute casing 108 (FIG. 1) to perform certain maintenance and/or repair tasks, as necessary.
  • FIGS. 8, 9, and 10 illustrate an example of the interface member 124.
  • FIGS. 8 and 9 depict a perspective view of the example from the front 102 and the back 104, respectively.
  • FIG. 10 illustrates an elevation view of the cross-section of the side of the interface member 124 taken at line 10-10 of FIG. 8.
  • the interface member 124 is configured to mate with the gear housing 122 (FIG. 1) and the motive unit 126 (FIG. 1).
  • This example has a body 166 with an interface side 168 and a motor side 170.
  • the body 166 may also be cast, although it is possible to consider use of a weldment and/or like fabricating technique to integrate one or more of the features of the interface member 124 considered herein.
  • the body 166 can comprise a pair of plate members (e.g., a first plate member 172 and a second plate member 174).
  • the plate members 172, 174 can be generally annular and/or circular, although this disclosure does contemplate that the geometry of adjacent components (e.g., the gear member 144 (FIG. 6) and/or the motive unit 126 (FIG. 1)) may dictate the form factor for the body 166.
  • the first plate member 172 can have a mating surface 175 with a first aperture 176 that penetrates into the body 166.
  • a plurality of bolt openings 178 may form an array that populates the mating surface 175 of the first plate member 172. This array can at least partially circumscribe the first aperture 176 and can match, at least partially, the array of bolt openings 142 (FIG. 6) on the gear member 144 (FIG. 6) mentioned above.
  • the body 166 can include a frame member 180 that couples the frame members 172, 174.
  • the frame member 180 may form one or more ribs 182 that interpose between the plate members 172, 174, extending radially away from the central aperture 176.
  • the ribs 182 can be annularly spaced apart from one another to form an array that at least partially circumscribes the central aperture 176.
  • FIGS. 9 and 10 provide some additional exemplary features that may be found on the interface member 124.
  • the second plate member 174 may have a mating surface 175 with a second aperture 184 that penetrates the body 166.
  • the surfaces 154, 175 may be machine-finished where necessary to hold certain dimension with acceptable tolerances (e.g., flatness).
  • the diagram of FIG. 10 shows that the apertures 176, 184 may form a counter-bore arrangement with a first bore 186 and a second bore 188.
  • the first bore 186 may be generally larger than the second bore 188 so as to potentially receive any protrusions, bosses, and like features that may protrude from the housing of the motive unit 126 (FIG. 1).
  • the second boss 188 may be sized to receive the shaft 130 (FIG. 4) of the motive unit 126 (FIG. 4).
  • the bosses 186, 188 may be configured to receive and support bearings that are useful to support the shaft 130 (FIG. 4), as necessary.
  • FIG. 11 depicts a perspective view of the back of the device 100 in exploded form and with certain members absent for clarity.
  • the interface member 124 can mount to the gear member 144, preferably with mating surfaces 154, 175 in contact with one another.
  • Bolts can insert through bolt openings 178. The bolts can be received in the threaded openings 156 to tighten and retain the members 124, 144 in contact with one another.
  • FIGs. 12-13 show cross-sectional views of the side of the device 100.
  • the interface member 124 is in position on the interface side 134 of the gear housing 122.
  • the shaft member 116 can insert into the first aperture 140 to position the pinion gear 118 in the top portion of the chamber 158.
  • the bearing member 119 can fit into the bores 160, 162 to provide support to the shaft member 116.
  • the assembly may include one or more additional bearings 171 to properly distribute the loading of the shaft member 116 by the pinion gear 118.
  • the drive gear 120 can insert into the third aperture 152. When coupled with the motor shaft 130, the drive gear 120 can reside in the chamber 158 to engage the pinion gear 118.
  • the members 122, 124 can form a reservoir 192 to retain a volume of fluid 192, preferably lubricant and like viscous fluids sufficient to cover at least part of the drive gear 120.
  • the lubricant can help prolong the life of mechanical components.
  • the device 100 may incorporate a seal that interposes between the surfaces 154, 175. This seal can retain fluid inside of the chamber 158. Another seal may be useful between the plate surface 139 and the corresponding surface on the volute casing 108. Examples of the seals may comprise a compressible unit (e.g., an o-ring, a gasket, etc.) that fits into a groove (or like feature) in one of the mating surfaces 139, 154, and 175. In some implementations, the mating surfaces 139, 154, 175 may be configured to form a metal-to-metal or otherwise forgo use of the seal. As shown in FIG. 13, the device 100 includes a motor shaft bearing member 196 to support the motor shaft 130.
  • a motor shaft bearing member 196 to support the motor shaft 130.
  • FIG. 14 shows a cross-sectional partial view of the side of the device 100 according to another embodiment of the disclosure.
  • the interface member 124 is in position on the interface side 134 of the gear housing 122.
  • the shaft member 116 positions the pinion gear 118 in the top portion of the chamber 158.
  • the bearing member 119 can fit into bores to provide support to the shaft member 116.
  • the assembly may include one or more additional bearings 171 to properly distribute the loading of the shaft member 116 by the pinion gear 118.
  • the bearings 171 are located along the shaft member 116 on both sides of the pinion gear 118.
  • the method 200 includes providing an impeller and a drive system coupled with the impeller, as shown at block 201.
  • the drive system includes a gear housing covering the drive gear and the pinion gear, the gear housing including a gear housing plate member, and a central aperture of the gear housing plate member for receiving the shaft member.
  • the gear housing cover further includes a gear member coupled to the gear housing plate member, wherein the gear member includes an interface surface surrounding a gear opening, the gear opening receiving the drive gear.
  • the drive system further includes an interface member coupled to the motive unit and the gear housing, the interface member including a body and a first interface plate member and a second interface plate member coupled to the body, wherein the first interface plate member has a first mating surface surrounding a first aperture, and wherein the second interface plate member has a second mating surface surrounding a second aperture.
  • the method further includes coupling the first mating surface directly to the interface surface of the gear member and coupling the second mating surface directly to the motive unit.
  • the method 200 further includes directly coupling/mounting a drive gear to a motor shaft of a motive unit, as shown at block 203.
  • the method 200 further includes transferring rotation of the drive gear through the pinion gear to turn the impeller, as shown at block 205.
  • This written description uses examples to disclose embodiments of the disclosure, including the best mode, and also to enable any person skilled in the art to practice the disclosure, including making and using any devices or systems and performing any incorporated methods.
  • the patentable scope of the disclosure is defined by the claims, and may include other examples that occur to those skilled in the art. Such other examples are intended to be within the scope of the claims if they have structural elements that do not differ from the literal language of the claims, or if they include equivalent structural elements with insubstantial differences from the literal language of the claims.

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

Abstract

L'invention concerne un dispositif de déplacement de fluide, lequel dispositif intègre un système d'entraînement avec un engrenage d'entraînement qui se couple directement à un arbre moteur. Le système d'entraînement peut comprendre un pignon qui se couple à l'engrenage d'entraînement. Le pignon peut être conçu pour transférer la rotation de l'arbre moteur pour faire tourner l'hélice. Dans un mode de réalisation, le dispositif de déplacement de fluide peut comprendre un compresseur centrifuge qui nécessite que l'hélice tourne à des vitesses élevées supérieures à 25.000 t/min.
PCT/US2016/039001 2015-06-23 2016-06-23 Système d'entraînement à engrenages et mise en œuvre de ce dernier WO2016210119A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201562183270P 2015-06-23 2015-06-23
US62/183,270 2015-06-23

Publications (1)

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WO2016210119A1 true WO2016210119A1 (fr) 2016-12-29

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109827802A (zh) * 2019-03-12 2019-05-31 北京铁城信诺工程检测有限公司 灌砂法测量压实度用取土设备

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3619086A (en) * 1970-02-26 1971-11-09 Westinghouse Electric Corp Self-contained centrifugal refrigerant gas compressor and electric motor
US4687411A (en) * 1985-03-25 1987-08-18 Ebara Corporation Speed increasing gear for a centrifugal compressor
US4688989A (en) * 1983-09-22 1987-08-25 Ebara Corporation Gas rotary machine
US5425345A (en) * 1994-10-31 1995-06-20 Chrysler Corporation Mechanically driven centrifugal air compressor with hydrodynamic thrust load transfer
US20120107099A1 (en) * 2008-06-09 2012-05-03 Airzen Co., Ltd Turbo blower and high speed rotating body used in same
WO2014077310A1 (fr) * 2012-11-15 2014-05-22 三菱重工業株式会社 Compresseur centrifuge

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3619086A (en) * 1970-02-26 1971-11-09 Westinghouse Electric Corp Self-contained centrifugal refrigerant gas compressor and electric motor
US4688989A (en) * 1983-09-22 1987-08-25 Ebara Corporation Gas rotary machine
US4687411A (en) * 1985-03-25 1987-08-18 Ebara Corporation Speed increasing gear for a centrifugal compressor
US5425345A (en) * 1994-10-31 1995-06-20 Chrysler Corporation Mechanically driven centrifugal air compressor with hydrodynamic thrust load transfer
US20120107099A1 (en) * 2008-06-09 2012-05-03 Airzen Co., Ltd Turbo blower and high speed rotating body used in same
WO2014077310A1 (fr) * 2012-11-15 2014-05-22 三菱重工業株式会社 Compresseur centrifuge

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109827802A (zh) * 2019-03-12 2019-05-31 北京铁城信诺工程检测有限公司 灌砂法测量压实度用取土设备

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