WO2012034480A1 - Pompe multiphase rotative synchrone - Google Patents

Pompe multiphase rotative synchrone Download PDF

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Publication number
WO2012034480A1
WO2012034480A1 PCT/CN2011/079160 CN2011079160W WO2012034480A1 WO 2012034480 A1 WO2012034480 A1 WO 2012034480A1 CN 2011079160 W CN2011079160 W CN 2011079160W WO 2012034480 A1 WO2012034480 A1 WO 2012034480A1
Authority
WO
WIPO (PCT)
Prior art keywords
cylinder
rotor
oil
main shaft
sliding plate
Prior art date
Application number
PCT/CN2011/079160
Other languages
English (en)
Chinese (zh)
Inventor
侯敏
Original Assignee
Hou Min
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 Hou Min filed Critical Hou Min
Publication of WO2012034480A1 publication Critical patent/WO2012034480A1/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
    • 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
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/32—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members
    • F04C2/332—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members with vanes hinged to the outer member and reciprocating with respect to the inner member

Definitions

  • the present invention relates to a fluid pump, and more particularly to a power unit for the delivery of oil, gas or oil and gas mixtures, and more particularly to a synchronous rotary multiphase mixing pump. Background technique
  • Oil and gas mixing can not only save costs, simplify the process and increase the oil recovery rate, but also greatly reduce the carbon emissions generated by associated gas combustion and recover associated gas, saving energy.
  • the multiphase mixed pump currently used mainly has a twin screw pump.
  • the twin screw mixed pump relies on the mutual engagement of two screw profiles to form a closed working volume to pressurize and transport oil and gas.
  • the working volume of the screw mixing pump relies on the machining accuracy of the profile to seal the oil and gas.
  • the size of the gap directly affects the volumetric efficiency. Therefore, the machining accuracy of the screw profile is put forward, and the machining process is complicated.
  • the characteristics of the characteristics are also high, resulting in higher cost; the water in the crude oil will also emulsifie the lubricating oil, destroying its lubricity and increasing the power loss; the hard particles in the crude oil will also be between the rotor profiles and A leak path is formed between the profile line and the inner surface of the cylinder, which affects the volumetric efficiency; in order to prevent the leakage passage of the profile line, rubber is often added at the end of a rotor profile, but when the gas content in the oil and gas is high The temperature of the compressed one is increased, the aging of the rubber is accelerated, and the service life of the screw mixing pump is reduced; more importantly, the exhaust port of the screw mixing pump is a fixed position, and the pressure of oil and gas in the oil field is continuously generated.
  • the object of the present invention is to design a synchronous rotary multiphase which can be operated at high speed or low speed due to the problem that the mixed pump commonly used in oil and gas transportation is easy to wear due to structural influence, short life and poor reliability.
  • Mixed pump commonly used in oil and gas transportation is easy to wear due to structural influence, short life and poor reliability.
  • a synchronous rotary multiphase mixed pump comprising a body 12, a cylinder 8, a main shaft 1 and a rotor 10, characterized in that the cylinder 8 is mounted in a body 12, and the rotor 10 is mounted on a main shaft 1 that drives its synchronous rotation and Located in the cylinder 8, the main shaft 1 and the cylinder 8 are eccentrically mounted and the rotor 10 on the main shaft 1 is in line contact with the cylinder 8; the rotor 10 is provided with a sliding groove 17, and one end of the sliding plate 15 is located in the sliding groove 17, the sliding plate 15 The other end is hingedly connected to the cylinder 8.
  • the sliding plate 15 divides the crescent-shaped cavity between the cylinder 8 and the rotor 10 into an oil inlet chamber and an oil discharge chamber, and an oil inlet port 21 is disposed on the cylinder 8 opposite to the oil inlet chamber.
  • the oil inlet port 21 communicates with the oil inlet annular volume 20 in the body 12, the oil inlet annular volume 20 communicates with the oil supply port on the body, and the oil discharge port 22 is arranged on the rotor 10 corresponding to the oil discharge chamber.
  • the oil port 22 is discharged from the body 12 through the oil discharge passage 18.
  • the cylinder 8 is fixed by the cylinder upper cover 7 and the cylinder lower cover 11, and the cylinder upper cover 7 and the cylinder lower cover 11 are respectively supported by the frame bearing 4 and the body bearing 13, and the frame bearing 4 is mounted on the eccentric seat 2, eccentric
  • the seat 2 is fixedly coupled to one end of the body 12.
  • One end of the main shaft 1 is supported by a main bearing 3, the main bearing 3 of the main frame is mounted in the eccentric seat 3, and the other end of the main shaft 1 is suspended in the cylinder 8.
  • An end face seal 19 is mounted on both ends of the rotor 10 to prevent oil and gas in the oil discharge passage 18 from entering the oil inlet chamber and the oil discharge chamber from the discharge end surface of the rotor 10, and also preventing oil and gas leakage in the oil discharge chamber.
  • the oil inlet annular volume 20 is mounted on both ends of the rotor 10 to prevent oil and gas in the oil discharge passage 18 from entering the oil inlet chamber and the oil discharge chamber from the discharge end surface of the rotor 10, and also preventing oil and gas leakage in the oil discharge chamber.
  • the cylinder 8 is provided with a circular arc-shaped sliding groove 16.
  • the cylindrical end of the sliding plate 15 is inserted into the circular arc-shaped sliding groove 16 to be hingedly connected.
  • the main body of the oil discharge passage 18 is located on the cylinder lower cover 11, one end of which is connected to the oil discharge port 22 on the rotor, and the other end is connected to the oil outlet on the body 12 at the outlet of the oil discharge passage 18.
  • a check valve 14 is installed.
  • the rotor 10 is provided with an annular cavity 9 for weight reduction.
  • the invention is an ideal equipment for adapting the associated gas in the oil field and carrying out the oil and gas mixed transportation. It is not sensitive to the hard particles in the oil and gas mixed transportation, and has no requirement for the proportion of oil and gas in the oil and gas mixed transportation, and the working pressure is The pressure with the oilfield system can be self-balancing, so any pressure changes in the system will not affect the normal operation of the equipment.
  • the invention has the advantages of stable operation, small leakage, high volumetric efficiency, simple processing technology, and low frictional wear and high work reliability due to the relatively low relative speed of the outer surface of the rotor and the inner surface of the cylinder.
  • the invention has long oil intake time and small loss of oil inlet resistance; no matter how the oil inlet pressure and the system pressure change in the oil field, the working pressure and the system pressure of the mixed pump are always adaptive, and the compression shortage and the never occurring will never occur.
  • the compression problem does not cause liquid hammering, ensuring that the machine is always working under the best working conditions, with low power loss and high efficiency; the rotor 10 and the cylinder 8 only rotate around their own center of rotation, without unbalanced inertial force, The machine runs smoothly; Because of synchronous rotation, it is not sensitive to impurities in oil and gas transportation, adaptability and high reliability;
  • the main processing surfaces are cylindrical, simple in process, good in sealing, small in friction and wear, and high in volumetric efficiency. Save power.
  • Figure 1 is a schematic view of the structure of the present invention.
  • FIG. 2 is a schematic view of the working principle of the present invention. detailed description
  • a synchronous rotary multi-phase mixing pump comprises a body 12, a cylinder 8, a main shaft 1 and a rotor 10.
  • the cylinder 8 is fixed by a cylinder upper cover 7 and a cylinder lower cover 11, and the cylinder upper cover 7 and the cylinder lower cover 11 are respectively framed by a frame
  • the bearing 4 and the body bearing 13 are supported, the frame bearing 4 is mounted on the eccentric seat 2, the eccentric seat 2 is fixedly connected to one end of the body 12, the main frame bearing 1 of the main shaft 1 is supported by the main bearing 3, and the main bearing 3 of the frame is mounted on the eccentric seat 3, the other end of the main shaft 1 is suspended in the cylinder 8; the cylinder 8 is mounted in the body 12, and the rotor 10 is mounted on the main shaft 1 that drives its synchronous rotation and is located in the cylinder 8.
  • the main shaft 1 and the cylinder 8 are eccentrically mounted and the rotor 10 on the main shaft 1 is in line contact with the cylinder 8; the rotor 10 is provided with a sliding groove 17 having a straight plate-shaped structure at one end, which is movably inserted in the sliding groove In the 17th, the other end of the sliding plate 15 has a cylindrical structure, and the cylindrical structure is inserted into the circular arc-shaped sliding plate groove 16 on the cylinder 8, and the two are in cylindrical contact, so that the hinge connection is possible, and the sliding plate 15 acts as the driving cylinder 8 While the rotor 10 rotates synchronously, the crescent-shaped cavity between the cylinder 8 and the rotor 10 is divided into an oil inlet chamber and an oil discharge chamber, and an oil inlet port 21 is disposed on the cylinder 8 opposite to the oil inlet chamber.
  • the oil inlet port 21 communicates with the oil inlet annular volume chamber 20 in the body 12, the oil inlet annular volume 20 communicates with the oil supply port on the body, and the oil discharge port 22 is arranged on the rotor 10 corresponding to the oil discharge chamber.
  • the oil port 22 is discharged through the oil discharge passage 18 to the body 12, and the main body of the oil discharge passage 18 is located on the cylinder lower cover 11, one end of which is connected to the oil discharge port 22 on the rotor, and the other end is connected to the oil outlet on the body 12.
  • a check valve 14 is installed at the outlet of the oil drain passage 18.
  • a plurality of sets of end face seal rings 19 may be installed at both ends of the rotor 10, in order to reduce the weight of the rotor 10,
  • the rotor 10 is provided with an annular cavity 9 for weight reduction. As shown in Figure 1.
  • the eccentric seat 2 is fixed integrally with the body 12 by bolts 5, and the main shaft 1 is supported by the eccentric seat 1 by a set of support bearings 3 of the eccentric seat.
  • the other end of the main shaft 5 is coupled to the rotor 10 by a key and a keyway.
  • the central shaft holes are connected, that is, the rotor 10 is rotated about the central axis of the main shaft 1.
  • the cylinder 8 fixes the cylinder upper cover 7 and the cylinder lower cover 11 as a whole by a connecting bolt 6, wherein the upper and lower covers 7 and 11 are respectively supported by the eccentric seat bearing 4 and the body bearing 13, and the cylinder 8 coincides with the center line of the body, the center
  • the line is the center of rotation of the cylinder 8, which forms an eccentricity with the center of rotation of the rotor 10 such that the outer surface of the rotor 10 and the inner surface of the cylinder 8 are always tangent at point A, forming a crescent-shaped working volume.
  • the cylinder 8 is provided with a semi-circular slide groove 16 for hinged mounting of the slide plate 15, the axial length of the slide groove 16 being the same as the axial length of the rotor 10 and the cylinder 8 and the slide plate 15, and always It is tangent to the semicircle of the head of the sliding plate 15 to prevent oil and gas from leaking from the high pressure chamber to the low pressure chamber.
  • the sliding plate 15 can oscillate with the sliding plate slot 16 and drive the cylinder 8 to rotate synchronously, and reciprocate relative to the sliding plate guiding groove 17 to coordinate Rotational difference due to the different centers of the rotor 10 and the cylinder 8 different.
  • the cylinder 8 is further provided with an oil inlet port 21, which is rotated with the cylinder 8, and communicates with the oil inlet pipe at any angle.
  • the spindle rotation angle is >0°
  • the volume of the oil inlet chamber increases.
  • the pressure is reduced.
  • the rotor 10 is provided with an oil discharge port 22.
  • the volume of the oil inlet chamber is enlarged, the volume of the compression oil discharge chamber is continuously reduced, and the pressure of the oil and gas is continuously increased.
  • the pressure in the chamber is greater than the system pressure, the oil and gas
  • the spindle 1 is rotated one revolution, and at the same time, a working cycle of oil inlet and compression and oil discharge is completed, and the machine has high work efficiency.
  • the rotor 10 rotates synchronously with the cylinder 8, and the hard particles in the oil and gas are difficult to wipe out the leakage passage at the sealing point A, but are discharged together with the rotation of the rotor 10 and the cylinder 8 together, so the patent is in the oil and gas.
  • the impurities are not sensitive and are ideal for transporting oil and gas mixtures with impurities.
  • annular cavity 9 is formed in the rotor 10 to reduce the mass of the rotor 10 and the moment of inertia at the time of starting.
  • the working pressure and the system pressure of the present invention are always adaptive.
  • the problem of insufficient compression and over-compression does not occur in the oil discharge chamber, ensuring that the machine is always Working under the best working conditions, this solves the technical problem that the pressure in the oil and gas mixing often changes and the mixed pump does not work normally.
  • a check valve 14 is arranged in the oil discharge passage 18 to ensure that the synchronous rotary multi-phase mixed pump is stopped or the pressure in the compression chamber is lower than the system pressure when the mixed pump is started, and the oil and gas are recirculated.
  • the utilization rate of the cylinder 8 is obtained.
  • the main shaft 1 can also be supported at both ends of the main shaft 1 through the eccentric bearing 3 and the concentric bearing provided on the body 12 to reduce the bending deformation of the main shaft 1.
  • the rotor Since the cylinder and the rotor of the present invention are connected to the sliding plate by the sliding plate, the rotor realizes a plane rotary motion with respect to the cylinder.
  • the inner surface of the cylinder and the outer surface of the rotor are always tangent at point A, and a gap is formed between them.
  • a crescent-shaped working chamber which is divided into a suction by a skateboard
  • the oil, air chamber and oil drain, air chamber at the same time complete the oil absorption, gas and oil discharge, gas circulation, high work efficiency.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

L'invention concerne une pompe multiphase rotative synchrone qui comprend un corps (12), un cylindre (8), un arbre principal (1), et un rotor (10). Le cylindre (8) est installé dans le corps (12), le rotor (10) sur l'arbre principal (1), l'arbre principal (1) et le cylindre (8) étant installés de manière excentrique tandis que le rotor (10) sur l'arbre principal (1) reste en contact en ligne avec le cylindre (8). Une fente de plaque coulissante (17) est disposée sur le rotor (10), une extrémité d'une plaque coulissante (15) est située dans la fente de plaque coulissante (17), l'autre extrémité de ladite plaque coulissante (15) étant reliée par charnière au cylindre (8). La plaque coulissante (15) divise une cavité en croissant entre le cylindre (8) et le rotor (10) en une cavité d'admission d'huile et une cavité d'évacuation d'huile. Une admission d'huile (21) est disposée sur le cylindre (8) correspondant à la cavité d'admission d'huile, et l'admission d'huile (21) communique avec une chambre d'admission d'huile annulaire (20) dans le corps (12). Une sortie d'huile (22) est disposée sur le rotor (10) correspondant à la cavité d'évacuation d'huile, et la sortie d'huile (22) évacue l'huile hors du corps (12) par le biais d'un canal d'évacuation d'huile (18). La pompe, d'une structure simple, fonctionne de manière stable, et son rendement est élevé.
PCT/CN2011/079160 2010-09-14 2011-08-31 Pompe multiphase rotative synchrone WO2012034480A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN2010205283057U CN201786649U (zh) 2010-09-14 2010-09-14 同步回转多相混输泵
CN201020528305.7 2010-09-14

Publications (1)

Publication Number Publication Date
WO2012034480A1 true WO2012034480A1 (fr) 2012-03-22

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Application Number Title Priority Date Filing Date
PCT/CN2011/079160 WO2012034480A1 (fr) 2010-09-14 2011-08-31 Pompe multiphase rotative synchrone

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CN (1) CN201786649U (fr)
WO (1) WO2012034480A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021178497A1 (fr) * 2020-03-04 2021-09-10 Solar Turbines Incorporated Compresseur de gaz intégré

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN201786649U (zh) * 2010-09-14 2011-04-06 侯敏 同步回转多相混输泵
CN113623200A (zh) * 2021-09-13 2021-11-09 江苏丰泰流体机械科技有限公司 一种同步回转式多相多级潜油混输泵

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1352107A (en) * 1915-08-11 1920-09-07 James H Wagenhorst Pump or compressor
US1719954A (en) * 1925-12-26 1929-07-09 Nat Pump And Compressor Compan Rotary compressor
US1915097A (en) * 1928-11-27 1933-06-20 Gen Electric Rotary pump
US3298331A (en) * 1965-04-15 1967-01-17 James L Butler Rotary heat engine
US3697203A (en) * 1970-06-22 1972-10-10 James L Butler Rotary engine
US4773836A (en) * 1984-04-13 1988-09-27 J. C. Moore Research Inc. Rotary vane pump
CN1607331A (zh) * 2003-10-15 2005-04-20 徐衡 全运动式压缩机
CN201568302U (zh) * 2009-11-23 2010-09-01 侯敏 带有旋转进排气口和排气阀的同步回转压缩机械
CN201568303U (zh) * 2009-11-23 2010-09-01 侯敏 对称平衡式同步旋转压缩机械
CN201786649U (zh) * 2010-09-14 2011-04-06 侯敏 同步回转多相混输泵

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1352107A (en) * 1915-08-11 1920-09-07 James H Wagenhorst Pump or compressor
US1719954A (en) * 1925-12-26 1929-07-09 Nat Pump And Compressor Compan Rotary compressor
US1915097A (en) * 1928-11-27 1933-06-20 Gen Electric Rotary pump
US3298331A (en) * 1965-04-15 1967-01-17 James L Butler Rotary heat engine
US3697203A (en) * 1970-06-22 1972-10-10 James L Butler Rotary engine
US4773836A (en) * 1984-04-13 1988-09-27 J. C. Moore Research Inc. Rotary vane pump
CN1607331A (zh) * 2003-10-15 2005-04-20 徐衡 全运动式压缩机
CN201568302U (zh) * 2009-11-23 2010-09-01 侯敏 带有旋转进排气口和排气阀的同步回转压缩机械
CN201568303U (zh) * 2009-11-23 2010-09-01 侯敏 对称平衡式同步旋转压缩机械
CN201786649U (zh) * 2010-09-14 2011-04-06 侯敏 同步回转多相混输泵

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021178497A1 (fr) * 2020-03-04 2021-09-10 Solar Turbines Incorporated Compresseur de gaz intégré
US11371513B2 (en) 2020-03-04 2022-06-28 Solar Turbined Incorporated Integrated gas compressor

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