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US20080193309A1 - Screw pump rotor and method of reducing slip flow - Google Patents

Screw pump rotor and method of reducing slip flow Download PDF

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Publication number
US20080193309A1
US20080193309A1 US11/673,148 US67314807A US2008193309A1 US 20080193309 A1 US20080193309 A1 US 20080193309A1 US 67314807 A US67314807 A US 67314807A US 2008193309 A1 US2008193309 A1 US 2008193309A1
Authority
US
United States
Prior art keywords
ring seal
disposed
groove
rotor
pump
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.)
Abandoned
Application number
US11/673,148
Other languages
English (en)
Inventor
Vasanth Srinivasa Kothnur
David Deloyd Anderson
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nuovo Pignone Technologie SRL
Original Assignee
Individual
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
Priority to US11/673,148 priority Critical patent/US20080193309A1/en
Application filed by Individual filed Critical Individual
Assigned to GENERAL ELECTRIC COMPANY reassignment GENERAL ELECTRIC COMPANY ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ANDERSON, DAVID DELOYD, KOTHNUR, VASANTH SRINIVASA
Priority to CA2619195A priority patent/CA2619195C/en
Priority to KR1020080010532A priority patent/KR101420439B1/ko
Priority to JP2008023421A priority patent/JP5469308B2/ja
Priority to CN200810005481XA priority patent/CN101240795B/zh
Priority to EP08101357.5A priority patent/EP1956245A3/en
Priority to RU2008104910/06A priority patent/RU2461736C2/ru
Publication of US20080193309A1 publication Critical patent/US20080193309A1/en
Priority to US13/021,106 priority patent/US8597007B2/en
Assigned to NUOVO PIGNONE TECHNOLOGIE S.R.L. reassignment NUOVO PIGNONE TECHNOLOGIE S.R.L. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: GENERAL ELECTRIC COMPANY
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/001—Radial sealings for working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/24—Fluid mixed, e.g. two-phase fluid

Definitions

  • the present invention relates in general to screw pumps, and, more particularly, to improved screw pump rotors and methods of reducing slip flow in screw pumps.
  • FIG. 1 illustrates a conventional twin-screw pump 10 .
  • the twin-screw pump 10 has two rotors 12 and 14 that are disposed within a close-fit casing or pump housing 16 .
  • Each rotor has a shaft 18 A and 18 B with one or more outwardly extending sets of screw threads 20 for at least a portion of the length of the shaft.
  • the shafts 18 A and 18 B run axially within two overlapping cylindrical enclosures, collectively, a rotor enclosure, or liner, 19 .
  • Pump 10 will often be driven by a motor (not shown), which rotates rotors 12 and 14 .
  • a drive gear 22 on one of the shafts engages a second gear on the other shaft, such that, when the pump motor turns rotor 12 , rotor 14 is turned at the same rate, but in an opposite direction.
  • wellhead fluids including particulate materials, are drawn into pump 10 at inlet 24 .
  • pump slip flow (illustrated by the arrows in FIG. 2 ) can occur between each rotor and the rotor enclosure 19 .
  • other slip paths include slip between screw tip and adjacent rotor and between faces.
  • pump rotors for screw pumps including a shaft, a first set of threads disposed on a portion of an outer surface of the shaft, at least one thread of the first set of threads comprising a groove disposed on an end portion thereof, and a ring seal disposed on the groove.
  • twin-screw pumps include a casing having an inlet and an outlet, a liner disposed inside of the casing, and two rotors disposed inside of the liner, each rotor having a shaft, a set of threads disposed on a portion of an outer surface of the shaft, at least one thread of the first set of threads comprising a groove disposed on an end portion thereof, and a ring seal disposed on the groove.
  • the screw pump having a casing having a low-pressure inlet and a high-pressure outlet, a liner disposed inside of the casing, and a rotor disposed inside of the liner having a shaft and a first set of threads disposed on a portion of an outer surface of the shaft, such methods including the steps of forming a groove on end portions of at least one thread of the first set of threads, and disposing a ring seal on the groove, the ring seal being configured to protrude outwardly from the groove and to rest against an inner surface of the liner of the screw pump, the groove being sized so as to allow the ring seal to move radially with respect to the at least one thread as the rotor is deflected, and the ring seal being configured to reduce the slip flow from the high-pressure outlet to the low-pressure inlet.
  • FIG. 1 illustrates a conventional twin-screw pump
  • FIG. 2 illustrates the pump slip flow path between rotor tips and the liner.
  • FIG. 3 illustrates a cross section view of a rotor in accordance with an embodiment of the invention
  • FIG. 4 illustrates a close up view of a rotor tip of the rotor of FIG. 3 ;
  • FIG. 5 illustrates a ring seal disposed on the rotor of FIGS. 3 and 4 ;
  • FIG. 6 illustrates a screw tip envelope of a rotor in accordance with the invention with respect to a piston-ring seal mounted on the rotor with the rotor aligned with the liner ( FIG. 6A ) and with the rotor deflected with respect to the liner ( FIG. 6B );
  • FIG. 7 illustrates a perspective view of a rotor in accordance with another embodiment of the disclosed invention.
  • FIG. 8 illustrates a cross sectional view of another rotor seal in accordance with another embodiment of the invention.
  • FIGS. 3-5 illustrate, respectively, a cross section view of a rotor 40 , a cross sectional view of one tip of the screw threads of FIG. 3 , and a ring seal 60 in accordance with an embodiment of the disclosed invention.
  • the terms “ring seal,” “piston-ring seal,” “brush seal,” “inter-stage seal,” “split-ring seal,” or “seal” will be used interchangeably.
  • the rotor 40 includes a shaft 42 , on the periphery of which a plurality of screw threads 44 is disposed. At the tip 46 of the screw threads 44 a groove 48 is provided, inside of which the ring seal 60 is disposed.
  • the ring seal 60 when installed and under normal operation conditions, is designed so as to spring outward, resting against an inside surface 49 of the pump liner 51 .
  • the elimination and/or minimization of pump slip flow is accomplished by an outer surface 50 of the ring seal 60 being pushed against the inside surface 49 of the pump liner 51 by the springing action of the resilient ring seal 60 as well as a centrifugal load on the ring seal 60 caused by the rotation of the rotor 40 while a side surface 52 of the ring seal 60 is pushed against an inner surface 54 of the groove 48 by the pressure difference from one side of the ring seal 60 to the other.
  • the seal is installed on the rotor (unlike conventional applications elsewhere in gas turbine/steam turbines where seals are disposed on the stator), generating a rotating seal between the successive pressure rise stages of a twin-screw pump.
  • the ring seal 60 is helical in structure and may have a length to cover any specific amount of circumferential displacement of the helical threads 44 of the rotor 40 .
  • FIG. 5 illustrates a ring seal 60 covering a complete revolution of the threads 44 .
  • the dimensions of the groove 48 and ring seal 60 are selected such that the contact of the outer surface 50 of the ring seal 60 with the inside surface 49 of the pump liner 51 is accomplished when the rotor is aligned with the pump liner (as illustrated in FIG. 6A by the outer edge of the ring seal 60 ) and with the rotor deflected with respect to the liner ( FIG. 6B ).
  • a screw tip envelope 62 is illustrated with the fully deflected ring seal 60 disposed in the groove 48 at the tip of the screw threads 44 .
  • the pump rotor 40 will minimize and/or eliminate pump slip flow between the rotor and the casing, resulting in a high-pressure differential boost multiphase pump with a compact rotor length.
  • better sealing between the edges of the rotor and the pump casing will also insure a reduction in solid particulate erosion/abrasion of rotor tips as well as providing allowance for thermal expansion mismatch when pumping transport fluids with a high gas-volume fraction, thus also reducing the likelihood of catastrophic seizures.
  • the ride-through operation of the twin screw pump when slugs of high gas volume fraction are present in the well-head flows may be enhanced by using variable speed drives and clearance control logic.
  • FIG. 7 Another embodiment of a rotor 70 of the instant invention is illustrated in FIG. 7 .
  • pins 72 are used to hold the ring seal 60 in place inside and with respect to the grooves 48 when the rotor 70 is rotated, such pins 72 acting as anti-rotation constraints.
  • the ring seals 60 are held in place by pins 72 disposed once per revolution (or any multiple or fraction there of, depending on the circumferential length of the seals).
  • the pins 72 are disposed in the first set of threads 44 at a circumferential location opposite to the circumferential location in which the pins 72 are disposed of the second set of threads 44 or otherwise optimal to insure proper balance when the rotor 70 rotates.
  • a first pin is disposed on a first end of the ring seal and a second one at the second end thereof.
  • the second ring is then disposed against the second pin holding the second end of the first ring and so on.
  • the shaft deflects and rubs against the side surfaces of the piston ring, or ring seal 60 .
  • the outside diameter of the piston ring is in constant contact with the liner bore, thus maintaining the seal. Contact with the liner bore (in spite of seal wear) is maintained by virtue of the ring seal's out-springing effect and/or centrifugal loads on the ring as the rotor rotates.
  • the thermal design of the rotor/liner interface which enables operation of the twin screw pump under wet gas compression conditions by using rotor materials which have low thermal coefficient of expansion compared to the liner bore is also within the scope of the disclosed invention.
  • a specific rotor material such as invar, which has a low thermal coefficient of expansion, enables the pump to ride through a gas slug within a minimum amount of deflection due the thermal heating.
  • a longer mean time between failure, or MTBF is achieved by selecting the material of the ring seal 60 so as to allow the ring seal to be a sacrificial wear component, while simultaneously guaranteeing the rated design pressure/flow rate conditions.
  • the screw pump having a casing having a low-pressure inlet and a high-pressure outlet, a liner disposed inside of the casing, and a rotor disposed inside of the liner having a shaft and a first set of threads disposed on a portion of an outer surface of the shaft.
  • Such methods include the steps of forming a groove on an end portion of at least one thread of the first set of threads, and disposing a ring seal on the groove, the ring seal being configured to protrude outwardly from the groove and to rest against an inner surface of the liner of the screw pump, the groove being sized so as to allow the ring seal to move radially with respect to the at least one thread of the first set of threads as the rotor is deflected, and the ring seal being configured to reduce the slip flow from the high-pressure outlet to the low-pressure inlet.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)
US11/673,148 2007-02-09 2007-02-09 Screw pump rotor and method of reducing slip flow Abandoned US20080193309A1 (en)

Priority Applications (8)

Application Number Priority Date Filing Date Title
US11/673,148 US20080193309A1 (en) 2007-02-09 2007-02-09 Screw pump rotor and method of reducing slip flow
CA2619195A CA2619195C (en) 2007-02-09 2008-01-31 Screw pump rotor and method of reducing slip flow
KR1020080010532A KR101420439B1 (ko) 2007-02-09 2008-02-01 스크류 펌프 로터 및 슬립 유동을 감소시키는 방법
JP2008023421A JP5469308B2 (ja) 2007-02-09 2008-02-04 スクリューポンプロータ及び滑り流を減少させる方法
CN200810005481XA CN101240795B (zh) 2007-02-09 2008-02-05 螺杆泵转子和减小滑流的方法
EP08101357.5A EP1956245A3 (en) 2007-02-09 2008-02-07 Screw pump rotor and method of reducing slip flow
RU2008104910/06A RU2461736C2 (ru) 2007-02-09 2008-02-08 Ротор винтового насоса и способ уменьшения скользящего течения в винтовом насосе
US13/021,106 US8597007B2 (en) 2007-02-09 2011-02-04 Screw pump rotor and method of reducing slip flow

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US11/673,148 US20080193309A1 (en) 2007-02-09 2007-02-09 Screw pump rotor and method of reducing slip flow

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US13/021,106 Division US8597007B2 (en) 2007-02-09 2011-02-04 Screw pump rotor and method of reducing slip flow

Publications (1)

Publication Number Publication Date
US20080193309A1 true US20080193309A1 (en) 2008-08-14

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ID=39356693

Family Applications (2)

Application Number Title Priority Date Filing Date
US11/673,148 Abandoned US20080193309A1 (en) 2007-02-09 2007-02-09 Screw pump rotor and method of reducing slip flow
US13/021,106 Active 2027-08-04 US8597007B2 (en) 2007-02-09 2011-02-04 Screw pump rotor and method of reducing slip flow

Family Applications After (1)

Application Number Title Priority Date Filing Date
US13/021,106 Active 2027-08-04 US8597007B2 (en) 2007-02-09 2011-02-04 Screw pump rotor and method of reducing slip flow

Country Status (7)

Country Link
US (2) US20080193309A1 (ru)
EP (1) EP1956245A3 (ru)
JP (1) JP5469308B2 (ru)
KR (1) KR101420439B1 (ru)
CN (1) CN101240795B (ru)
CA (1) CA2619195C (ru)
RU (1) RU2461736C2 (ru)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100040499A1 (en) * 2008-08-14 2010-02-18 General Electric Company Screw pump rotors and ring seals for screw pump rotors
US20100270747A1 (en) * 2009-04-24 2010-10-28 General Electric Company Non-metallic brush seal
DE102010000576A1 (de) 2010-02-26 2011-09-01 G+R Technology Group Ag Anlage und Verfahren zur hydrothermalen Karbonisierung von Biomasse
WO2012138522A3 (en) * 2011-04-07 2013-12-12 Imo Industries Inc System and method for monitoring pump lining wear
US10837444B2 (en) 2018-09-11 2020-11-17 Rotoliptic Technologies Incorporated Helical trochoidal rotary machines with offset
US10844720B2 (en) 2013-06-05 2020-11-24 Rotoliptic Technologies Incorporated Rotary machine with pressure relief mechanism
US20210270265A1 (en) * 2020-02-27 2021-09-02 Gardner Denver, Inc. Low coefficient of expansion rotors for vacuum boosters
US11746782B2 (en) 2020-04-03 2023-09-05 Gardner Denver, Inc. Low coefficient of expansion rotors for blowers
US11802558B2 (en) 2020-12-30 2023-10-31 Rotoliptic Technologies Incorporated Axial load in helical trochoidal rotary machines
US11815094B2 (en) 2020-03-10 2023-11-14 Rotoliptic Technologies Incorporated Fixed-eccentricity helical trochoidal rotary machines
US12146492B2 (en) 2021-01-08 2024-11-19 Rotoliptic Technologies Incorporated Helical trochoidal rotary machines with improved solids handling
US12352268B2 (en) 2021-01-08 2025-07-08 Rotoliptic Technologies Incorporated Pumps, compressors, and expanders with a teardrop-shaped rotor

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US8591181B2 (en) 2010-10-18 2013-11-26 General Electric Company Turbomachine seal assembly
WO2014167503A1 (en) * 2013-04-09 2014-10-16 Indian Institute Of Technology Madras Apparatus for measuring rheological parameters and methods for its operation
US9506366B2 (en) 2013-08-06 2016-11-29 General Electric Company Helical seal system for a turbomachine
US9863860B2 (en) 2013-08-26 2018-01-09 Indian Institute Of Technology Madras Methods and apparatus for measuring rheological properties of multi-phase fluids
CN106151027A (zh) * 2016-08-31 2016-11-23 程巍 金属复合螺杆泵转子
CN112780554A (zh) * 2021-02-26 2021-05-11 珠海格力电器股份有限公司 压缩机和空调
CN114215748B (zh) * 2021-11-26 2024-11-19 珠海格力电器股份有限公司 压缩机和空调
CN114432588B (zh) * 2022-01-18 2023-11-10 江苏大学 一种折边叶片结构的主动脉穿刺型轴流式血泵
CN114562457A (zh) * 2022-04-11 2022-05-31 浙江创为真空设备股份有限公司 一种等螺距变压缩的螺杆转子

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US7401655B2 (en) * 2005-07-07 2008-07-22 Baker Hughes Incorporated Downhole gas compressor
US20100040499A1 (en) * 2008-08-14 2010-02-18 General Electric Company Screw pump rotors and ring seals for screw pump rotors

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US5738505A (en) * 1995-09-05 1998-04-14 Nuovo Pignone S.P.A. Perfected twin-screw pump, particularly suitable for the pumping of biphase fluids in a submerged environment
US6406281B1 (en) * 1999-09-23 2002-06-18 Nuovo Pignone Holding S.P.A. Screw-type pumping unit for treatment of fluids in several phases
US7401655B2 (en) * 2005-07-07 2008-07-22 Baker Hughes Incorporated Downhole gas compressor
US20100040499A1 (en) * 2008-08-14 2010-02-18 General Electric Company Screw pump rotors and ring seals for screw pump rotors

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100040499A1 (en) * 2008-08-14 2010-02-18 General Electric Company Screw pump rotors and ring seals for screw pump rotors
US20100270747A1 (en) * 2009-04-24 2010-10-28 General Electric Company Non-metallic brush seal
DE102010000576A1 (de) 2010-02-26 2011-09-01 G+R Technology Group Ag Anlage und Verfahren zur hydrothermalen Karbonisierung von Biomasse
WO2012138522A3 (en) * 2011-04-07 2013-12-12 Imo Industries Inc System and method for monitoring pump lining wear
US9243631B2 (en) 2011-04-07 2016-01-26 Imo Industries, Inc. System and method for monitoring pump lining wear
US11506056B2 (en) 2013-06-05 2022-11-22 Rotoliptic Technologies Incorporated Rotary machine
US10844720B2 (en) 2013-06-05 2020-11-24 Rotoliptic Technologies Incorporated Rotary machine with pressure relief mechanism
US11608827B2 (en) 2018-09-11 2023-03-21 Rotoliptic Technologies Incorporated Helical trochoidal rotary machines with offset
US11988208B2 (en) * 2018-09-11 2024-05-21 Rotoliptic Technologies Incorporated Sealing in helical trochoidal rotary machines
US11306720B2 (en) 2018-09-11 2022-04-19 Rotoliptic Technologies Incorporated Helical trochoidal rotary machines
US11499550B2 (en) 2018-09-11 2022-11-15 Rotoliptic Technologies Incorporated Sealing in helical trochoidal rotary machines
US10844859B2 (en) * 2018-09-11 2020-11-24 Rotoliptic Technologies Incorporated Sealing in helical trochoidal rotary machines
US10837444B2 (en) 2018-09-11 2020-11-17 Rotoliptic Technologies Incorporated Helical trochoidal rotary machines with offset
US20230098259A1 (en) * 2018-09-11 2023-03-30 Rotoliptic Technologies Incorporated Sealing In Helical Trochoidal Rotary Machines
US11668304B2 (en) * 2020-02-27 2023-06-06 Gardner Denver, Inc. Low coefficient of expansion rotors for vacuum boosters
US20210270265A1 (en) * 2020-02-27 2021-09-02 Gardner Denver, Inc. Low coefficient of expansion rotors for vacuum boosters
US12158146B2 (en) 2020-02-27 2024-12-03 Industrial Technologies And Services, Llc Low coefficient of expansion rotors for vacuum boosters
US11815094B2 (en) 2020-03-10 2023-11-14 Rotoliptic Technologies Incorporated Fixed-eccentricity helical trochoidal rotary machines
US11746782B2 (en) 2020-04-03 2023-09-05 Gardner Denver, Inc. Low coefficient of expansion rotors for blowers
US12085078B2 (en) 2020-04-03 2024-09-10 Industrial Technologies And Services, Llc Low coefficient of expansion rotors for blowers
US12448968B2 (en) 2020-04-03 2025-10-21 Industrial Technologies And Services, Llc Low coefficient of expansion rotors for blowers
US11802558B2 (en) 2020-12-30 2023-10-31 Rotoliptic Technologies Incorporated Axial load in helical trochoidal rotary machines
US12473912B2 (en) 2020-12-30 2025-11-18 Rotoliptic Technologies Incorporated Axial load in helical trochoidal rotary machines
US12352268B2 (en) 2021-01-08 2025-07-08 Rotoliptic Technologies Incorporated Pumps, compressors, and expanders with a teardrop-shaped rotor
US12146492B2 (en) 2021-01-08 2024-11-19 Rotoliptic Technologies Incorporated Helical trochoidal rotary machines with improved solids handling

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EP1956245A2 (en) 2008-08-13
CN101240795A (zh) 2008-08-13
KR20080074745A (ko) 2008-08-13
JP5469308B2 (ja) 2014-04-16
US20110123378A1 (en) 2011-05-26
US8597007B2 (en) 2013-12-03
RU2461736C2 (ru) 2012-09-20
KR101420439B1 (ko) 2014-07-16
JP2008196487A (ja) 2008-08-28
CA2619195A1 (en) 2008-08-09
CA2619195C (en) 2015-08-11
RU2008104910A (ru) 2009-08-20
EP1956245A3 (en) 2014-07-30
CN101240795B (zh) 2013-08-21

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