US3822972A - Multistart helical rotor mechanism - Google Patents

Multistart helical rotor mechanism Download PDF

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Publication number
US3822972A
US3822972A US00308047A US30804772A US3822972A US 3822972 A US3822972 A US 3822972A US 00308047 A US00308047 A US 00308047A US 30804772 A US30804772 A US 30804772A US 3822972 A US3822972 A US 3822972A
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US
United States
Prior art keywords
rotor
stator
helical
circle
rotor mechanism
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US00308047A
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English (en)
Inventor
A Ogly
A Kochney
S Nikomarov
D Baldenko
M Gusman
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VSESOJUZNY NAUCHNO-ISSLEDOVATELSKY INSTITUT BUROVOI TEKHNIKI
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Publication of US3822972A publication Critical patent/US3822972A/en
Assigned to VSESOJUZNY NAUCHNO-ISSLEDOVATELSKY INSTITUT BUROVOI TEKHNIKI reassignment VSESOJUZNY NAUCHNO-ISSLEDOVATELSKY INSTITUT BUROVOI TEKHNIKI ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: BALDENKO, DMITRY F., GUSMAN, MOISEI T., NIKOMAROV, SAMUIL ADMINISTRATOR OF ASAN-NURI ABDULLA OGLY, DEC'D.
Assigned to VSESOJUZNY NAUCHNO-ISSLEDOVATELSKY INSTITUT BUROVOI TEKHNIKI reassignment VSESOJUZNY NAUCHNO-ISSLEDOVATELSKY INSTITUT BUROVOI TEKHNIKI CERTIFICATE OF INHERITANCE Assignors: OGLY, ASAN-NURI A., DEC'D.
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/10—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F01C1/101—Moineau-type
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B4/00—Drives for drilling, used in the borehole
    • E21B4/02—Fluid rotary type drives
    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/107—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth
    • F04C2/1071—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type
    • F04C2/1073—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type where one member is stationary while the other member rotates and orbits

Definitions

  • Prior art multistart helical rotor mechanism used in a downhole helical hydraulic motor comprises a housing accommodating a. stator having an internal elastic lining. A h'elical groove is made on the surface of the lining. v
  • a rotor is eccentricallyldisposed in the stator, the external surface of the rotor being also provided with a helical groove.
  • the rotor and the stator form a kinematic pair with the permanent contact similarly to-a gearwheel and pinion with internal gearing and define closed chambers.
  • the rotor axis is shifted with respect to the stator axis over the distance of the eccentricity e.
  • the number of teeth of. the helical surfaces of the stator and rotor corresponds to the number of entries of a screw thread.
  • the number of teeth Z, of the stator is one tooth greater than the number' of teeth Z of the rotor.
  • the ratio between the pitches T and t of the stator and rotor respectively is directly proportional to the ratio between the teeth numbers: l
  • the stator circle is assumed to be the starting one.
  • the cross sectional profile of the stator is considered to be the base one, and the rotor profile the conjugated one.
  • the stator profile is equidistant of the cycloidal curve spaced from the latter at thedistance corresponding to the radius r of the stator-tooth.
  • the cycloidal curve proper is formed by rolling without sliding-over a predetermined starting stator circle of another conventional circle, the radius 12 of this circle being equal to the exce ntricity in the c'entroidgearing.
  • the diameter D, of the starting circle of the stator is assumed to be rotor and stator inside of the
  • the conjugated profile of the rotor is formed as an envelope of the base profile of the stator by rolling of the initial circle of the rotor over the initial circle of the stator.
  • a multistart helical rotor mechanism comprising a stator having a helical groove on the internal surface thereof and a rotor eccentrically disposed in the stator and having the external helical surface, the cross sectional-profile of the stator comprising serially arranged circle arcs, each arcbeing conjugated on both sides with portions of a cycloidal curve formed by rolling without sliding over a predetermined starting circle of the stator of another conventional circle, the radius of this circle being selected corresponding to the amount of said eccentricity, whereas the cross sectional profile of therotor comprises an envelope of the stator profile formed by rolling of the initial maximum circle of the rotor selected based upon the condition of continuous contact between the helical surfaces of the predetermined starting circle of the stator.
  • the ratio between the amount of the eccentricity of the mechanism and the radius of the circle arc of the stator cross sectional profile should be within the range from 0.3 to 0.85.
  • the cross sectional profile thereof is formed on the basis of extracentroidal gearing, wherein the radius of the conventional circle used for plotting of cycloidal curve is not equal to the eccentricity.
  • Extracentroidal gearing is characterized by the ratio between the amount of eccentricity and the radius of the above-mentioned conventional circle.
  • the ratio between the amount of eccentricity and the radius of the conventional circle is selected within the range from Due to this fact the smoothness of the helical surfaces of the rotorand the stator is improved, thereby reducing'relative sliding therebetween, and hence, the wear.
  • FIG. 1 shows a general view partially in longitudinal section of the embodiment of a multistart helical rotor mechanism used in a downhole hydraulic motor
  • FIG. 2 is a sectional view taken along the line ll-II in FIG. 1;
  • FIG. 3 shows a diagram of plotting the cross sectional profile of the stator
  • FIG. 4 is a plot showing the relative specific pressure versus a parameter C
  • FIG. 5 shows a general view in longitudinal section of the embodiment of the helical rotor mechanism used in a hydraulic pump
  • FIG. 6 is a sectional view taken along the line VIVI in FIG. 5;
  • FIG. 7 shows a general view in longitudinal section of the embodiment of the helical rotor mechanism used in a compressor
  • FIG. 8 is a sectional view taken along the line VIII- VIII in FIG. 7;
  • FIG. 9 shows a general view in longitudinal section of the embodiment of the helical rotor mechanism used in a reduction gear
  • FIG. 10 is a sectional view taken along the line X-X in FIG. 9.
  • a downhole helical hydraulic motor (FIG. 1) comprises a housing 1 in which there is rigidly mounted an elastic lining 2 provided with a tenthread lielical groove on the internal surface thereof.
  • the housing I with the lining 2 form a stator 3 of the helical rotor mechanism.
  • a rotor 4 is disposed in the stator 3 with an excentricity e," the external surface of the rotor being provided with a ninethread helical groove. Accordingly, the kinematic ratio of the helical rotor mechanism is equal to i 9:10.
  • FIG. 2 shows the cross sectional profile of the helical rotor mechanism, wherein the cross sectional profile of the stator 3 comprises successively alternating portions of a cycloidal curve defining the teeth of the stator 3 and arcs of circles of the radius r defining tooth spaces in the stator cross section.
  • the cycloidal curve which constitutes the basis for the formation of the profile of the stator 3 is formed by rolling without sliding over a predetermined starting circle of the stator 3 of another conventional circle, the diameter of this circle being selected depending upon the amount of eccentricity e.”
  • the predetermined starting circle of the stator is generally determined by the operational conditions of the mechanism and depends upon maximum diameter possible under these conditions.
  • the cross sectional profile of the rotor 4 is conju gated with the profile of the stator 3 and is formed as an envelope of the base profile of the stator 3 by rolling the initial circle of the rotor 4 over the initial circle of the stator 3.
  • M is torque developed by the motor
  • i ZJZ is kinematic ratio of the helical rotor mechanism
  • C e/r is dimensionless geometric parameter of the helical rotor mechanism
  • L is length of the rotor and stator
  • FIG. 4 shows the plot of the relative specific pressure K versus C for helical rotor mechanisms having different kinematic ratios.
  • the helical rotor mechanisms have the range of C. values which corresponds to minimum specific pressures. The analysis has shown that for all mechanisms the range of the values of C 0.3 0.85 is optimal for all mechanisms, wherein the specific pressures do not exceed the minimum ones by more than 15-20 percent. In this example the helical rotor mechanism has the parameter C 0.55. This allows the reduction of the specific pressure by about 17 percent as compared to the prior art downhole helical hydraulic motor.
  • h is the radius of the conventional circle used for plotting the cycloidal curve.
  • the extracentroid factor is
  • the rotor 4 of the helical rotor mechanism is connected to the output shaft 6 by means of a doublehinged coupling 5, the actuating tool of the downhole motor (not shown) being secured at the end of the shaft.
  • the output shaft 6 is mounted in a spindle 7 by means of radial bearings 8.
  • Thrust bearings 9 mounted in the spindle 7 take up the axial load during the downhole motor operation.
  • the end of the shaft 6 extends outwards through a gland 10.
  • the housing 1 of the downhole motor is connected to a hydraulic pump by means of a reducer 11 and piping (not shown in the drawing).
  • the downhole motor functions as follows.
  • the hydraulic pump feeds fluid under pressure into a cavity A of the motor to establish the same pressure therein.
  • the cavity A is referred to as the high-pressure cavity.
  • the helical teeth of the rotor 4 and the stator 3 contact each other, thereby defining chambers closed along the pitch T of the helical surface of the stator 3. Therefore, a number of chambers are connected to the high-pressure cavity A, and a number of chambers to a low-pressure cavity B. For that reason an unbalanced force, and hence, torque arises in every cross section of the mechanism.
  • the axis of the rotor 4 performs the translatory motion in the counter clockwise direction, while the rotor itself rotates in the clockwise direction.
  • the rotor 4 imparts rotation to the output shaft via the double-hinged coupling 5, which rotation is then transmitted to the actuating tool of the downhole motor fixed at the end of the shaft.
  • the radial forces determine the amount of contact pressure in the pair rotor-stator."
  • the contactpressure also depends upon the pressure difference between the chambers of the motor in communication with the high-pressure cavity A and the low-pressure cavity B respectively.
  • the helical rotor mechanism according to the invention exhibits higher efficiency and can withstand greater load as compared to a mechanism'of the same size which does not possess the abovedescribed structural features.
  • FIG. 5 shows a hydraulic pump, wherein the helical rotor mechanism according to the invention is used.
  • the pump comprises a housing 12 having suction and discharge nozzles.
  • the housing 12 accommodates an elastic lining 13 provided with a helical surface.
  • housing 12 with the lining 13 forms a stator in which there is eccentrically disposed a rotor 14 connected to a drive (not shown) by means of a universal shaft 15 and an intermediate shaft 16.
  • the helical rotor mechanism has the kinematic ratio i Z /Z 2:3 and the parameter C 0.5.
  • the drive rotates the rotor 14, whereby reduced pressure is established in the zone of the suction nozzle, and fluid is sucked into the cavity of the housing 12.
  • the multiplicity of starts of the helical rotor mechanism ensures rather high output of the pump and small size thereof.
  • the specific contact pressure in the helical rotor mechanism is reduced by about 24 percent as compared to the prior art construction.
  • FIG. 7 shows the example of the use of the helical rotor mechanism according to the invention in a compressor.
  • the compressor comprises a housing 17 having a passage for supply of a liquid coolant, a stator 18 accommodated in the housing 17 and a rotor 19.
  • the rotor is driven via an output shaft 20 and a universal shaft 21.
  • FIG. 9 illustrates the use of the multistart helical rotor mechanism as a reduction gear.
  • a housing 24 of the reduction gear accommodates the helical rotor mechanism comprising a stator 25 and a rotor 26.
  • the length L of the mechanism should be at least equal to the pitch T of the helical surface of the stator', in this case the length of the mechanism is determined based upon the contact pressure and the rigidity of the reduction gear.
  • Mounted in the bore of the rotor 26 are bearings 27 supporting a carrier 28.
  • the latter is made in the form of a crankshaft, the axis of the shank of the shaft being displaced from the axis'of the shaftitself by the amount of eccentricity e' of the helical rotor mechanism.
  • the rotor 26 is connected to the output shaft 29 of the reduction gear by means of a universal shaft 30.
  • Bearings 31 take up axial and radial loads.
  • the torque transmittedby this device is reduced by Z; times, since the multistart helical rotor mechanism kinematically represents a planetary gearing having the gear ratio equal to Z
  • the gear ratio of the helical rotor mechanism various degrees of reduction of speed and torque can be achieved.
  • the helical rotor mechanism used ensures minimum specific pressure in the working parts of the reduction gear.
  • a multistart helical rotor mechanism comprising a stator and a rotor eccentrically disposed in the stator; said stator having a helical groove on the internal surface thereof; said rotor having a helical groove on the external surface thereof; the cross sectional profile of said stator comprising serially conjugated arcs of circle alternating with portions of a cycloidal curve formed by rolling without sliding over a predetermined starting circle of the stator of another conventional circle, the radius of this circle being selected depending upon the amount of said eccentricity; the cross sectional profile of said rotor comprising an envelope of the profile of said stator formed by rolling of the initial maximum cir- Bearings 22 take up axial and radial loads, and a sealing v 23 is adapted to seal the suction chamber of the compressor.
  • This device is similar in operation to well-known r0- tary compressors.
  • the ratio between the amount of said eccentricity and the radius of the arc of circle of the cross sectional profile of said stator being within the range from 0.3 to 0.85.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Fluid Mechanics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Physics & Mathematics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Rotary Pumps (AREA)
  • Transmission Devices (AREA)
US00308047A 1971-11-29 1972-11-20 Multistart helical rotor mechanism Expired - Lifetime US3822972A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
SU1721434A SU436944A1 (de) 1971-11-29 1971-11-29

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US3822972A true US3822972A (en) 1974-07-09

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US00308047A Expired - Lifetime US3822972A (en) 1971-11-29 1972-11-20 Multistart helical rotor mechanism

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US (1) US3822972A (de)
CA (1) CA977210A (de)
DD (1) DD100311A1 (de)
DE (1) DE2258135B2 (de)
FR (1) FR2163146A5 (de)
GB (1) GB1407058A (de)
RO (1) RO65171A (de)
SU (1) SU436944A1 (de)

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1980002176A1 (en) * 1979-03-29 1980-10-16 Inst Burovoi Tekhnik Multiple-thread screw-type drive for use in the borehole
WO1981000736A1 (en) * 1979-09-11 1981-03-19 Vsesoyuzny Ins Ni Borehole drive for rock crushing instrument
DE3148746C1 (de) * 1981-12-09 1983-09-29 Vsesojuznyj naučno-issledovatel'skij institut burovoj techniki, Moskva Mehrgängiger Planetenschraubantrieb
US4449953A (en) * 1980-09-12 1984-05-22 Permsky Filial Vsesojuznogo Nauchno-Issledovatelskogo Instituta Burovoi Tekhniki Articulated coupling
US4909337A (en) * 1986-01-31 1990-03-20 Kochnev Anatoly M Rotor of a screw hydraulic downhole motor, method for its production and a device for its production
US5017087A (en) * 1984-07-13 1991-05-21 Sneddon John L Multi-functional rotary hydraulic machine systems
US5171138A (en) * 1990-12-20 1992-12-15 Drilex Systems, Inc. Composite stator construction for downhole drilling motors
US5195882A (en) * 1990-05-12 1993-03-23 Concentric Pumps Limited Gerotor pump having spiral lobes
US6439834B1 (en) * 1998-10-13 2002-08-27 Arthur Whiting Oil field tool
US20050089430A1 (en) * 2003-10-27 2005-04-28 Dyna-Drill Technologies, Inc. Asymmetric contouring of elastomer liner on lobes in a Moineau style power section stator
US20060153724A1 (en) * 2005-01-12 2006-07-13 Dyna-Drill Technologies, Inc. Multiple elastomer layer progressing cavity stators
US9393648B2 (en) 2010-03-30 2016-07-19 Smith International Inc. Undercut stator for a positive displacment motor
US20170059211A1 (en) * 2015-08-27 2017-03-02 Vert Rotors Uk Limited Miniature low-vibration active cooling system with conical rotary compressor
US20170356678A1 (en) * 2015-08-27 2017-12-14 Vert Rotors Uk Limited Miniature low-vibration active cooling system with conical rotary compressor
EA039555B1 (ru) * 2020-10-20 2022-02-10 Борис Иванович Уваров Ротор одновинтового героторного насоса
US20220205445A1 (en) * 2020-12-30 2022-06-30 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
US11988208B2 (en) 2018-09-11 2024-05-21 Rotoliptic Technologies Incorporated Sealing in helical trochoidal rotary machines

Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1980002176A1 (en) * 1979-03-29 1980-10-16 Inst Burovoi Tekhnik Multiple-thread screw-type drive for use in the borehole
WO1981000736A1 (en) * 1979-09-11 1981-03-19 Vsesoyuzny Ins Ni Borehole drive for rock crushing instrument
US4449953A (en) * 1980-09-12 1984-05-22 Permsky Filial Vsesojuznogo Nauchno-Issledovatelskogo Instituta Burovoi Tekhniki Articulated coupling
DE3148746C1 (de) * 1981-12-09 1983-09-29 Vsesojuznyj naučno-issledovatel'skij institut burovoj techniki, Moskva Mehrgängiger Planetenschraubantrieb
US5017087A (en) * 1984-07-13 1991-05-21 Sneddon John L Multi-functional rotary hydraulic machine systems
US4909337A (en) * 1986-01-31 1990-03-20 Kochnev Anatoly M Rotor of a screw hydraulic downhole motor, method for its production and a device for its production
US5195882A (en) * 1990-05-12 1993-03-23 Concentric Pumps Limited Gerotor pump having spiral lobes
US5171138A (en) * 1990-12-20 1992-12-15 Drilex Systems, Inc. Composite stator construction for downhole drilling motors
US6439834B1 (en) * 1998-10-13 2002-08-27 Arthur Whiting Oil field tool
US7083401B2 (en) 2003-10-27 2006-08-01 Dyna-Drill Technologies, Inc. Asymmetric contouring of elastomer liner on lobes in a Moineau style power section stator
US20050089430A1 (en) * 2003-10-27 2005-04-28 Dyna-Drill Technologies, Inc. Asymmetric contouring of elastomer liner on lobes in a Moineau style power section stator
US20060153724A1 (en) * 2005-01-12 2006-07-13 Dyna-Drill Technologies, Inc. Multiple elastomer layer progressing cavity stators
US7517202B2 (en) 2005-01-12 2009-04-14 Smith International, Inc. Multiple elastomer layer progressing cavity stators
US9393648B2 (en) 2010-03-30 2016-07-19 Smith International Inc. Undercut stator for a positive displacment motor
US20170059211A1 (en) * 2015-08-27 2017-03-02 Vert Rotors Uk Limited Miniature low-vibration active cooling system with conical rotary compressor
US9776739B2 (en) * 2015-08-27 2017-10-03 Vert Rotors Uk Limited Miniature low-vibration active cooling system with conical rotary compressor
US20170356678A1 (en) * 2015-08-27 2017-12-14 Vert Rotors Uk Limited Miniature low-vibration active cooling system with conical rotary compressor
US10174973B2 (en) * 2015-08-27 2019-01-08 Vert Rotors Uk Limited Miniature low-vibration active cooling system with conical rotary compressor
US11988208B2 (en) 2018-09-11 2024-05-21 Rotoliptic Technologies Incorporated Sealing in helical trochoidal rotary machines
US11815094B2 (en) 2020-03-10 2023-11-14 Rotoliptic Technologies Incorporated Fixed-eccentricity helical trochoidal rotary machines
EA039555B1 (ru) * 2020-10-20 2022-02-10 Борис Иванович Уваров Ротор одновинтового героторного насоса
US20220205445A1 (en) * 2020-12-30 2022-06-30 Rotoliptic Technologies Incorporated Axial Load In Helical Trochoidal Rotary Machines
US11802558B2 (en) * 2020-12-30 2023-10-31 Rotoliptic Technologies Incorporated Axial load in helical trochoidal rotary machines

Also Published As

Publication number Publication date
DD100311A1 (de) 1973-09-12
DE2258135A1 (de) 1973-06-14
GB1407058A (en) 1975-09-24
CA977210A (en) 1975-11-04
RO65171A (ro) 1980-01-15
SU436944A1 (de) 1974-07-25
DE2258135B2 (de) 1976-07-22
FR2163146A5 (de) 1973-07-20

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