WO2019041681A1 - 容积式泵及采油装置 - Google Patents
容积式泵及采油装置 Download PDFInfo
- Publication number
- WO2019041681A1 WO2019041681A1 PCT/CN2017/118171 CN2017118171W WO2019041681A1 WO 2019041681 A1 WO2019041681 A1 WO 2019041681A1 CN 2017118171 W CN2017118171 W CN 2017118171W WO 2019041681 A1 WO2019041681 A1 WO 2019041681A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- plungers
- rotor body
- plunger
- displacement pump
- liquid
- Prior art date
Links
- 238000006073 displacement reaction Methods 0.000 title claims abstract description 45
- 238000004519 manufacturing process Methods 0.000 title abstract description 30
- 239000007788 liquid Substances 0.000 claims abstract description 112
- 230000005540 biological transmission Effects 0.000 claims abstract description 38
- 238000011084 recovery Methods 0.000 claims description 19
- 230000002093 peripheral effect Effects 0.000 claims description 4
- 238000007599 discharging Methods 0.000 abstract description 6
- 238000005086 pumping Methods 0.000 description 27
- 238000005265 energy consumption Methods 0.000 description 9
- 238000011161 development Methods 0.000 description 8
- 230000008901 benefit Effects 0.000 description 5
- 238000000034 method Methods 0.000 description 5
- 230000033001 locomotion Effects 0.000 description 4
- 238000013461 design Methods 0.000 description 3
- 230000005611 electricity Effects 0.000 description 3
- 238000005065 mining Methods 0.000 description 3
- 230000009286 beneficial effect Effects 0.000 description 2
- 239000003638 chemical reducing agent Substances 0.000 description 2
- 238000004891 communication Methods 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
- 230000007246 mechanism Effects 0.000 description 2
- 230000001012 protector Effects 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 238000004458 analytical method Methods 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 239000009096 changqing Substances 0.000 description 1
- 239000000306 component Substances 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 239000008358 core component Substances 0.000 description 1
- 238000007405 data analysis Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000011089 mechanical engineering Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000003129 oil well Substances 0.000 description 1
- 230000035515 penetration Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 239000009671 shengli Substances 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
- 239000002699 waste material Substances 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B47/00—Pumps or pumping installations specially adapted for raising fluids from great depths, e.g. well pumps
- F04B47/06—Pumps or pumping installations specially adapted for raising fluids from great depths, e.g. well pumps having motor-pump units situated at great depth
-
- 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
- E21B43/00—Methods or apparatus for obtaining oil, gas, water, soluble or meltable materials or a slurry of minerals from wells
- E21B43/12—Methods or apparatus for controlling the flow of the obtained fluid to or in wells
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/14—Pistons, piston-rods or piston-rod connections
Definitions
- the invention belongs to the technical field of oil production equipment, and particularly relates to a displacement pump and an oil recovery device for producing the displacement pump.
- Mechanical oil recovery is the use of mechanical energy to extract oil from the ground.
- the main mechanical oil recovery methods are pumping well oil recovery, electric submersible centrifugal pump well production and ground driven screw pump well production.
- the production system of the recreational pumping unit consists of a ground pumping unit system and a downhole pumping system. It is the main oil production equipment of the oil field. It is used in large quantities, consumes a large amount of electricity, and has low system efficiency. It is a typical “large horse”. Car.”
- China's beam pumping unit has more than 200,000 oil production wells, accounting for more than 90% of the total number of production wells. It is the main oil production equipment of the oil field, and the average operating efficiency of the system efficiency is only 26%, which is a typical “large horse-drawn car”. Energy consumption accounts for one-third of the energy consumption of oil fields, and the country consumes more than 10 billion kWh of electricity per year. Since the starting torque of the motor is small, the beam pumping unit needs a large starting torque to drive the balancing block, and the matched motor power is more than 2 levels higher than the power required for normal operation after the pumping unit is started, and the motor is in normal operation.
- the load rate is only about 40%; in addition, due to the alternating load of the underground pumping pump working in conjunction with the pumping unit, the ground system is unbalanced, which exacerbates the reactive power consumption of the power system, resulting in inefficient operation of the pumping system, resulting in A huge waste of energy.
- the power provided by the motor at a balance rate of 100% is only used to lift the 1/2 liquid column weight and overcome friction and the like.
- the pumping unit ground system consists of a motor, a pulley, a reducer and a four-bar linkage.
- the screw pump consists of a stator and a rotor, and the transmission of the medium is realized by the rotational motion of the rotor.
- the screw pump has the advantages of simple structure, small volume, light weight, low power consumption and high efficiency. Due to the rubber stator limitation, the lift is small and cannot be pumped deeply. At present, most field applications are wells with a depth of about 1000m.
- Submersible electric pump also known as submersible electric centrifugal pump
- the main feature is large displacement, which is most suitable for oil production in medium and high water cut period, and easy to manage. .
- Submersible electric pump production system is more and more widely used in oilfields at home and abroad.
- the main disadvantage is that the depth of penetration is limited by the power of the motor.
- the centrifugal pump with a head of 2000 meters is up to 20 meters long. The equipment is expensive and the initial investment is high. The daily maintenance requirements are high. ; used for 4000 meters ultra deep lift is still not working.
- the embodiment of the invention relates to a positive displacement pump and an oil recovery device for producing the positive displacement pump, which can solve at least some defects of the prior art, and provide a volume with simple structure, low equipment cost and low operating cost. Pump and oil production unit.
- Embodiments of the present invention relate to a positive displacement pump including a housing, one end of the housing opening to form a liquid discharge end, the housing having a cylindrical pump chamber, and at least a side wall of the housing is open a liquid inlet connected to the pump chamber, a drain passage formed in a sidewall of the housing, the drain passage being respectively electrically connected to the pump chamber and the drain end;
- a rotor body rotatable about its own axis is coaxially embedded in the housing, and at least one through hole for guiding liquid on the liquid inlet side into the liquid discharge passage is formed in the rotor body.
- a plunger is slidably disposed in the through hole, and each of the plungers is sequentially disposed along an axial direction of the rotor body and an axis is perpendicular to an axis of the rotor body; and is coaxially disposed in the rotor body for a driving crankshaft that drives each of the plungers to reciprocate in a corresponding through hole, the transmission crankshaft has a connecting end fixed to the rotor body and a driving end of a driving device for connecting the peripheral device, each The plungers are each coupled to the drive crankshaft.
- the transmission crankshaft includes a connecting end shaft segment, a transmission end shaft segment and a plurality of eccentric shaft segments, wherein the connecting end shaft segment and the transmission end shaft segment are coaxial with the rotor body, respectively
- the eccentric shaft segments are sequentially disposed between the connecting end shaft segment and the transmission end shaft segment along an axial direction of the rotor body, and an axis of each of the eccentric shaft segments is offset from an axis of the connecting end shaft segment
- Each of the plungers is coupled to one of the eccentric shaft segments.
- each of the plungers is provided with a through hole, and a radius of each of the through holes is greater than a sum of a radius of the corresponding eccentric shaft segment and an eccentric distance of the eccentric shaft segment.
- the plunger sleeve is disposed outside the corresponding eccentric shaft segment.
- each of the plungers includes a plunger body and two thrust members, and each of the through holes is respectively formed on the corresponding plunger body, and each of the thrust members has a curvature.
- An arcuate thrust groove having the same curvature as the corresponding eccentric shaft segment, wherein each of the thrust grooves has a central angle of less than 180° and the notch direction is the same as the axial direction of the corresponding plunger body, and each The two thrust grooves of the plunger are disposed opposite each other and the groove walls abut against the corresponding eccentric shaft segments.
- each of the thrust members can be detachably mounted on the corresponding plunger body.
- each of the plungers includes at least one first plunger and at least one second plunger, the axes of the first plungers are parallel to each other, and the axes of the second plungers are mutually Parallel, and the axis of the first plunger is perpendicular to the axis of the second plunger.
- the inner wall of the casing is oppositely provided with a liquid inlet tank and a liquid discharging tank, and each of the liquid inlets communicates with the liquid inlet tank, and the liquid discharging tank and the liquid discharging end Turn on.
- each of the first plungers is disposed to intersect with each of the second plungers in the axial direction of the rotor body.
- Embodiments of the present invention relate to an oil recovery apparatus including a positive displacement pump as described above, to which a drive unit is coupled to a drive end of the drive crankshaft.
- the driving device includes a submersible motor, and an end of the casing remote from the liquid discharge end thereof is fixedly connected with a connection joint of the submersible motor, and the transmission end and the output of the submersible motor are Axis connection.
- the embodiment of the invention has at least the following beneficial effects: the volumetric pump provided by the embodiment has the advantages of simple structure and low equipment cost; and when applied to oil production, since the plunger diameter is small, the liquid displacement is low, and if the rotation speed of the rotor body is lowered, It can further reduce the displacement, so it can meet the requirements of oil recovery and lift in conventional oilfields and low-permeability oil and gas fields, and can better adapt to the demand of onshore oilfields with small liquid production, and solve the prior art using electric submersible centrifugal pumps. There are problems such as high energy consumption, low lift, large initial investment, high oil and gas development cost, and low efficiency, high energy consumption, and high oil and gas development cost in the production system of the cruise pumping unit.
- FIG. 1 is a schematic structural view of a positive displacement pump according to an embodiment of the present invention.
- Figure 2 is a cross-sectional view taken along line A-A of Figure 1;
- FIG. 3 is a schematic structural diagram of an oil recovery device according to an embodiment of the present invention.
- an embodiment of the present invention provides a positive displacement pump 1 including a housing 101 having a cylindrical pump chamber, that is, a pump chamber surrounded by a cylindrical annular inner wall, generally
- the casing 101 is a hollow cylindrical casing 101.
- a casing 101 having a rectangular parallelepiped shape or the like may be used.
- One end of the housing 101 is configured to be a liquid discharge end, and the other end of the housing 101 may be closed or open, and may be designed according to actual needs; in this embodiment, the housing 101 is open at both ends, wherein One end is the drain end, and the other end can be connected to the corresponding equipment as needed.
- At least one liquid inlet 105 that is electrically connected to the pump chamber is defined in a sidewall of the housing 101, and a drain passage 106 is formed in a sidewall of the housing 101.
- the drain passage 106 is electrically connected to the pump chamber and the drain end, respectively.
- a rotor body 102 rotatable about its own axis is coaxially embedded in the housing 101, and at least one liquid for guiding the liquid inlet port 105 side to the drain passage is formed in the rotor body 102.
- a plunger 103 is slidably disposed in each of the through holes, and the plungers 103 are sequentially disposed along the axial direction of the rotor body 102 and the axes are perpendicular to the axis of the rotor body 102.
- Each of the plungers 103 is connected with a driving mechanism that drives the reciprocating slip in the corresponding through holes.
- the number and size specifications of the inlet port 105 described above may be designed according to actual use conditions, such as a single large diameter inlet hole or a plurality of small diameter inlet holes.
- the through hole is used to guide the liquid on the liquid inlet 105 side into the liquid discharge passage 106.
- the through hole may be in at least partially in direct communication with at least one of the liquid inlets 105, and at least partially in direct communication with the liquid discharge channel 106, so that liquid entering through the liquid inlet 105 can enter the through hole and be introduced into the row.
- the distance between each liquid inlet 105 and the liquid discharge port is an interval distance value, and the distance between each through hole and the liquid discharge end Also for an interval distance value, the interval distance value corresponding to each liquid inlet 105 is at least partially overlapped with the interval distance value corresponding to at least one of the through holes (excluding the case where only one end point value is the same);
- the housing 101 is vertically disposed as an example, and the height (or horizontal plane) at which the upper end and/or the lower end of each liquid inlet 105 is located should be between the height (or horizontal plane) at which the upper and lower ends of one of the through holes are located.
- each of the liquid inlets 105 is preferably a liquid inlet hole or a liquid inlet groove (ie, an arc groove having the same curvature as the casing 101) which is opened in the radial direction of the casing 101.
- the through holes are preferably along the rotor.
- the through hole of the body 102 is radially opened, and the axis of the through hole intersects perpendicularly with the axis of the rotor body 102.
- the liquid discharge channel 106 is preferably a corresponding liquid discharge groove on the inner wall of the casing 101, and may be a plurality of liquid discharge channels parallel to the axial direction of the casing 101, or may be a complete curved channel.
- Each of the liquid discharge grooves preferably extends to the liquid discharge end, and a liquid discharge chamber may be formed between each of the liquid discharge grooves and the outer wall of the rotor body 102; of course, the liquid discharge passage 106 may be formed in the wall of the casing 101.
- the liquid flow path correspondingly needs to open at least one liquid discharge hole which is electrically connected to the liquid flow path on the inner wall of the casing 101, and the arrangement of the liquid discharge hole can refer to the setting manner of each liquid inlet 105, such as the liquid inlet. 105 are the same number and are set to face each other. Undoubtedly, the length of each plunger 103 is smaller than the length of the corresponding through hole.
- each of the through holes may be periodically connected to the corresponding liquid inlet 105, and the liquid enters each through hole through the liquid inlet 105, and the space is accommodated by the sliding of the plunger 103 to accommodate the liquid. Then, the rotor body 102 is rotated, so that the liquid storage side of each through hole is electrically connected to the liquid discharge passage 106, and the liquid in the through hole is pushed into the liquid discharge passage 106 by the movement of the plunger 103 to realize liquid pumping. .
- the positive displacement pump 1 provided in this embodiment has a simple structure and low equipment cost; when the oil is used for oil production, since the diameter of the plunger 103 is small, the liquid displacement is low, and if the rotation speed of the rotor body 102 is lowered, the displacement can be further reduced. It can meet the requirements of oil recovery and lift of conventional oilfields and low-permeability oil and gas fields, and can better adapt to the demand of onshore oilfields with small liquid production, and solve the high energy consumption and lift of existing electric submersible centrifugal pumps in the prior art. Problems such as low initial investment, high oil and gas development cost, and low efficiency, high energy consumption, and high oil and gas development cost in the production system of the cruise pumping unit.
- the core components such as the pump cavity, the through hole and the plunger 103 are cylindrical parts, which can achieve high precision matching during processing, small friction between components, high volumetric efficiency and stable operation. , good flow uniformity, low noise, high working pressure and so on.
- the structure of the positive displacement pump 1 is continued.
- the following structure may be adopted: as shown in FIG. 1, coaxially disposed in the rotor body 102 for a driving crankshaft 104 for reciprocatingly sliding the plungers 103 in the corresponding through holes, the transmission crankings 104 having a connecting end fixed to the rotor body 102 and a driving device for connecting peripheral devices At the drive end, each of the plungers 103 is coupled to the drive crankshaft 104.
- the rotor body 102 is coaxial with the transmission crankshaft 104, that is, the rotor body 102 is coaxial with the main shaft of the transmission crankshaft 104, which is well known to those skilled in the art; correspondingly, a cavity is formed in the rotor body 102 for receiving
- the transmission crankshaft 104 is disposed in the axial direction of the rotor body 102, and may be a cylinder-shaped cavity and coaxial with the main shaft of the transmission crankshaft 104.
- the transmission crankshaft 104 is The ends extend out of the two ends of the rotor body 102, respectively, wherein the transmission end is convenient to be connected with the driving device of the peripheral device, and for the structure in which the pump housing 101 of the positive displacement pump 1 is screwed with the connecting joint, the above-mentioned transmission
- the connecting end of the crankshaft 104 extends beyond the corresponding end of the rotor body 102 and is rotatably connected with the corresponding side of the connecting joint by bearing cooperation.
- the rotor body 102 and the pump housing 101 and the rotor body 102 are connected.
- the joints can be matched by bearings to ensure the working stability and reliability of the rotor body 102.
- the plunger 103 is connected to the eccentric member of the transmission crankshaft 104 in order to realize the function of the drive crankshaft 104 to drive the plunger 103 to reciprocate in the corresponding through hole.
- a connecting rod journal or a crank arm, etc. the connection between the plunger 103 and the corresponding eccentric member can be realized by a connecting rod or the like, and the plunger 103 is driven by the eccentric member to perform a linear sliding movement in the corresponding through hole.
- the above-described transmission crankshaft 104 is optimized as follows: the transmission crankshaft 104 includes a connecting end shaft section 1041, a transmission end shaft section 1043, and a plurality of eccentric shaft sections 1042.
- the connecting end shaft segment 1041 and the transmission end shaft segment 1043 are both coaxial with the rotor body 102, and each of the eccentric shaft segments 1042 is sequentially disposed on the connecting end shaft segment 1041 along the axial direction of the rotor body 102.
- the axis of each of the eccentric shaft segments 1042 is offset from the axis of the connecting end shaft segment 1041, and each of the plungers 103 is correspondingly connected with one of the eccentric shaft segments 1042.
- each of the plungers 103 is provided with a through hole 1031, and a radius of each of the through holes 1031 is greater than a sum of a radius of the corresponding eccentric shaft segment 1042 and an eccentric distance of the eccentric shaft segment 1042.
- Each of the plungers 103 is sleeved outside the corresponding eccentric shaft segments 1042, that is, the transmission crankshafts 104 are sequentially passed through the respective plungers 103, and the eccentric shaft segments 1042 are freely rotatable within the corresponding through holes 1031.
- each of the plungers 103 includes a plunger body and two thrust members 1032, and each of the through holes 1031 is respectively formed on the corresponding plunger body.
- Each of the thrust members 1032 has an arcuate thrust groove having the same curvature as the corresponding eccentric shaft segment 1042, and each of the thrust grooves has a central angle of less than 180° and the notch direction is corresponding to the corresponding column.
- the axial direction of the plug body is the same, and the two thrust grooves of each of the plungers 103 are disposed opposite to each other and the groove walls abut against the corresponding eccentric shaft segments 1042; that is, the groove walls of the two bearing push grooves are located On the same cylindrical surface, and the two groove walls cannot be enclosed to form a complete cylindrical surface.
- the diameter of the cylindrical surface is the same as the diameter of the eccentric shaft section 1042, so that the eccentric shaft section 1042 is in the transmission end shaft section 1043, etc.
- the outer wall surface can always fit with the two bearing push grooves of the corresponding plunger 103, and under the eccentric rotation, the two bearing push grooves can be pushed alternately close to or away from the axis of the rotor body 102, that is, the corresponding plunger is driven.
- the sum of the central angles of the groove walls of the two bearing thrust grooves is less than 3 60°, that is, there is a certain letting space between the two bearing thrust grooves, which allows the eccentric shaft segment 1042 to not contact the bearing groove or the through hole wall during the rotation process, thereby avoiding the eccentric shaft segment 1042 to the plunger 103 generates a force in the radial direction of the plunger 103; those skilled in the art can realize the eccentric shaft segment 1042 to continuously drive the plunger 103 during the rotation according to a reasonable design (including the central angle of the two thrust grooves, etc.). Reciprocating slip in the corresponding through hole.
- the conventional crank arm and the connecting rod journal are integrated into an eccentric shaft section 1042, which simplifies the structure of the transmission crankshaft 104, is convenient in design, has high structural precision, and can accurately realize the plunger 103. Drive control.
- the above-mentioned eccentric shaft section 1042 and the plunger 103 are not limited to the above-mentioned driving connection structure, and the driving connection relationship between the two may be realized by a link connection or the like, which is a person skilled in the art. Easy to determine, not detailed here.
- each of the thrust members 1032 can be detachably mounted on the corresponding plunger body, such as by bolts, etc.; the detachable connection structure can facilitate the transmission between the crankshaft 104 and each of the plungers 103.
- the matching connection relationship enables the transmission crankshaft 104 and the plunger 103 to be detached from each other, which is convenient for installation and maintenance.
- each of the pushing members 1032 may be mounted on the hole wall of the insertion hole 1031 of the plunger body; or, one or two mounting grooves (shown, not labeled) may be opened on the outer wall of the plunger body, respectively The groove bottom of the mounting groove is penetrated by the corresponding through hole 1031.
- a mounting groove When a mounting groove is used, it is opened on the connecting end of the plunger body near the rotor body 102 or the outer end of the driving end (the pump housing 101 is vertically placed as
- the mounting groove is correspondingly formed at the top end or the bottom end of the plunger body, and both the pushing members 1032 are installed in the mounting groove and the pushing groove extends to the corresponding through hole 1031 so as to be connected with the eccentric shaft.
- each of the receiving members includes two disassembling members, and the two disassembling members are respectively located in the two mounting grooves).
- each of the plungers 103 includes at least one first plunger and at least one second plunger, each of the first columns.
- the axes of the plugs are parallel to each other, the axes of the respective second plungers are parallel to each other, and the axis of the first plunger is perpendicular to the axis of the second plunger.
- each of the first plungers is arranged to intersect with each of the second plungers, that is, between each adjacent two first plungers.
- the second plunger has a first plunger between each adjacent two second plungers.
- each of the liquid inlets 105 is disposed opposite to the liquid discharge channel 106, wherein each of the liquid inlets 105 is preferably arranged at intervals along the axial direction of the rotor body 102, and the liquid discharge channel 106 is It is preferable to adopt the above-described structure in which the drain groove is provided correspondingly on the inner wall of the casing 101.
- the through holes can transport liquid from the liquid inlet 105 into the liquid discharge passage 106.
- a liquid inlet 109 may be formed in the inner wall of the casing 101, and each of the liquid inlets 105 communicates with the liquid inlet 109 to facilitate the liquid guiding operation of each through hole.
- the number of the above-mentioned plungers 103 can be selected within the range of 2 to 200, and the number of the liquid inlets 105 is between 1 and 6 sets.
- the embodiment of the invention relates to an oil recovery device, comprising the positive displacement pump 1 provided in the first embodiment, wherein the transmission end of the transmission crankshaft 104 is connected with a driving device.
- the driving device comprises a submersible motor 2, an end of the housing 101 remote from the liquid discharge end thereof (the end can be connected to the lower joint 108) and the submersible motor 2
- the connection joint 201 is fixedly connected, and the transmission end is connected to the output shaft 202 of the submersible motor 2.
- the connection structure of the submersible motor 2 and the positive displacement pump 1 is easily designed by those skilled in the art according to the prior art, and will not be further described herein.
- the liquid discharge end of the casing 101 may be connected to the oil pipe, and the liquid discharge end may be screwed to the upper joint 107 and connected to the oil pipe through the upper joint 107.
- an annular inlet liquid inlet 1071 is opened on the outer wall of the upper joint 107.
- the liquid inlet 1071 is electrically connected to the liquid discharge passage 106 of the pump casing 101, and at least the wall of the upper joint 107 is opened.
- each of the liquid guiding through holes 1072 communicates with the hollow inner cavity of the upper joint 107 and the annular groove type liquid inlet 1071, and the annular groove type liquid inlet 1071 + each liquid guiding through hole 1072
- a liquid flow path constituting the upper joint 107 is used to guide the liquid discharged from the pump casing 101 into the oil pipe.
- Each of the above-mentioned liquid guiding through holes 1072 is preferably designed to be inclined, and is suitable for the requirements of oil recovery and head of conventional oil fields and low-permeability oil and gas fields, and can be better adapted to the demand of onshore oil fields with small liquid production.
- the above oil recovery device has the following advantages:
- the above-mentioned oil production unit displacement range can be controlled from 0.5m 3 /d to 45m 3 /d, which is suitable for the production demand of onshore oilfields in China.
- China's onshore oil wells produce less liquid, and the low-permeability oil field produces less than 1m 3 /d.
- It mainly uses the beam pumping unit to produce oil.
- the number of wells exceeds 200,000, accounting for more than 90% of the total number of production wells.
- the electric submersible centrifugal pump is mainly used in high-yield vertical wells. It is characterized by large displacement (>100m 3 /d) and low lift ( ⁇ 1800m). It has a small application range and cannot replace the beam pumping well.
- the displacement can be further reduced, and the requirements of the oil recovery and the lift of the conventional oil field and the low-permeability oil and gas field can be met, and the system efficiency is low.
- the above-mentioned oil production equipment almost all participate in the lifting of oil and gas, the theoretical efficiency is as high as 95%, compared with the average operating efficiency of the beam pumping unit is only 26%, the total efficiency is increased by 64%.
- China's onshore oilfield beam pumping unit exceeds 200,000, and the annual power consumption exceeds 10 billion kWh.
- the new volumetric pump 1 replaces the recreational pumping unit and is expected to save more than 6.4 billion kWh per year.
- the load of the above oil recovery device is stable and is carried by the oil pipe, without the need for the protector as the main support member, and the working condition is better than that of the electric submersible centrifugal pump.
- the efficiency of the oil recovery device is high, and the power of the required submersible motor is small, further Increased service life.
- the new pump has a service life of more than 9 years, saving a lot of operating costs every year.
- the cost of a single displacement pump 1 is much lower than that of a submersible electric centrifugal pump.
- the above-mentioned positive displacement pump 1 has an efficiency of up to 95%, and the required motor power for lifting the same liquid production amount is 50% smaller than that of the submersible electric centrifugal pump, and the motor length is shorter than half; and the above-mentioned positive displacement pump 1 is not afraid of cavitation, and need not Separator; the above-mentioned positive displacement pump 1 is much shorter than the centrifugal pump, the single-stage positive displacement pump 1 (only one plunger 103) is only 0.5 m in length, and the centrifugal pump length is 20 m;
- the above-mentioned oil recovery device is used for a new well without huge ground equipment and land occupation fees.
Landscapes
- 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)
- Reciprocating Pumps (AREA)
Abstract
一种容积式泵（1）及采用该容积式泵（1）的采油装置，该容积式泵（1）包括壳体（101），壳体（101）具有排液端及圆柱形泵腔，壳体（101）侧壁上开设有至少一个进液口（105），壳体（101）侧壁内形成有排液通道（106）；壳体（101）内同轴嵌装有可绕自身轴线旋转的转子体（102），转子体（102）内形成有至少一个用于将进液口（105）侧的液体导引至排液通道（106）内的贯通孔，每一贯通孔内滑设有一个柱塞（103），各柱塞（103）沿转子体（102）的轴向依次设置，各柱塞（103）轴线均与转子体（102）的轴线垂直；转子体（102）内同轴设有用于带动各柱塞（103）在对应的贯通孔内往复滑移的传动曲轴（104）。
Description
本发明属于采油设备技术领域，具体涉及一种容积式泵及采油该容积式泵的采油装置。
机械采油是用机械能量把油采出地面的方式。目前，主要的机械采油方式有抽油机井采油、电动潜油离心泵井采油和地面驱动螺杆泵井采油。
(1)游粱式抽油机采油系统
游粱式抽油机采油系统由地面抽油机系统和井下抽汲系统2部分组成，是油田的主要采油设备，使用数量大，耗电量大，系统效率低，属于典型的“大马拉小车”。
我国游梁式抽油机采油井超过20万口，占生产油井总数的90％以上，是油田的主要采油设备，而系统效率平均运行效率仅为26％，属于典型的“大马拉小车”，能耗已占油田能耗的三分之一，全国每年耗电电量逾百亿千瓦时。由于电机启动转矩小，而游梁式抽油机需较大启动转矩带动平衡块，匹配的电机功率比抽油机启动后正常运行所需功率大2个等级以上，而正常运行时电机负载率仅在40％左右；另外，由于与抽油机联合工作的井下抽油泵载荷交替变化造成地面系统工作不平衡，加剧了动力系统的无功消耗，导致抽油系统的低效率运行，造成巨大的能源浪费。在平衡率为100％时电动机提供的动力仅用于提起1/2液柱重量和克服摩擦力等。抽油机地面系统由电机、皮带轮、减速器和四连杆机构组成。查有关的机械工程手册，由于抽油机载荷不均匀，电机最大效率达到80％，皮带轮+减速器效率为82％，四连杆机构效率为95％，地面系统最大效率为62％；盘根盒效率为90％，抽油杆效率为90％，抽油泵效率为80％，油管柱效率为95％，井下抽汲系统最大效率为62％；整个游梁式抽油系统最大效率只有38.4％。目前国内各油田抽油机井系统效率主要分布在20％～30％之间，大庆油田平均为28％，胜利油田平均为25％，长庆油田平均为20％。抽油机能耗已占油田能耗的三分之一。2014年中国石油各油田机采系统数据分析来看，油田机采系统总耗电量占到油田业务总耗电量的50％左右。
(2)螺杆泵举升技术
螺杆泵由定子和转子组成，通过转子的旋转运动实现对介质的传输。螺杆泵结构简单、体积小、重量轻、耗电少、效率高。由于橡胶定子限制，扬程小，无法深抽。目前大多数现场应用是在井深1000m左右的井。
(3)潜油电泵采油系统
潜油电泵又称潜油电动离心泵，主要由多级离心泵、分离器、保护器和潜油电机组成，主要特点是排量大，最适用于中、高含水期采油，并且管理方便。潜油电泵采油系统在国内外油田应用越 来越广泛，主要缺点是下入深度受电机功率的限制，扬程2000米的离心泵长达20米，设备昂贵，初期投资高；日常维护要求高；用于4000米超深举升尚无法正常工作。
2014年下半年，国际油价暴跌，我国油田出现大面积严重亏损，国内各个油田均在想尽办法降本增效，许多低产井无效益而被迫关停。另外，随着油气资源的不断开发，开采油层深度逐年增加，油田含水率的迅速上升，开发经济效益逐年下降，老区块应何时改变采油方式，才能延长油田的经济开采期，新区块应如何选择最佳的举升方式，使油田获得更大的经济效益，是企业面临的重要问题。
综上所述，现有三种主要机采方法均不能满足经济开发的需求，急需让操作成本维持更低水平的新采油方法。
本发明实施例涉及一种容积式泵及采油该容积式泵的采油装置，至少可解决现有技术的部分缺陷，提供一种结构简单、设备成本低廉，能使操作成本维持更低水平的容积式泵及采油装置。
本发明实施例涉及一种容积式泵，包括壳体，所述壳体的其中一端开口构成排液端，所述壳体具有圆柱形的泵腔，所述壳体的侧壁上开设有至少一个与所述泵腔导通的进液口，所述壳体的侧壁内还形成有排液通道，所述排液通道分别与所述泵腔及所述排液端导通；
于所述壳体内同轴嵌装有可绕自身轴线旋转的转子体，所述转子体内形成有至少一个用于将进液口侧的液体导引至所述排液通道内的贯通孔，每一所述贯通孔内滑设有一个柱塞，各所述柱塞沿所述转子体的轴向依次设置且轴线均与所述转子体的轴线垂直；于所述转子体内同轴设有用于带动各所述柱塞在对应的所述贯通孔内往复滑移的传动曲轴，所述传动曲轴具有与所述转子体固连的连接端及用于连接外设的驱动装置的传动端，各所述柱塞均与所述传动曲轴连接。
作为实施例之一，所述传动曲轴包括连接端轴段、传动端轴段以及多个偏心轴段，所述连接端轴段及所述传动端轴段均与所述转子体同轴，各所述偏心轴段沿所述转子体的轴向依次设置于所述连接端轴段与所述传动端轴段之间，各所述偏心轴段的轴线均偏离所述连接端轴段的轴线，每一所述柱塞对应与其中一个所述偏心轴段连接。
作为实施例之一，各所述柱塞均开设有穿设孔，每一所述穿设孔的半径大于对应的所述偏心轴段的半径与该偏心轴段的偏心距之和，各所述柱塞套设在对应的所述偏心轴段外。
作为实施例之一，各所述柱塞均包括柱塞本体和两个承推件，各所述穿设孔分别开设于对应的所述柱塞本体上，各所述承推件均具有曲率与对应的所述偏心轴段曲率相同的弧形承推槽，各所述承推槽的圆心角均小于180°且槽口方向均与对应的所述柱塞本体的轴向相同，每一所述柱塞的 两所述承推槽正对设置且槽壁均与对应的所述偏心轴段贴靠。
作为实施例之一，各所述承推件均可拆卸安装于对应的所述柱塞本体上。
作为实施例之一，各所述柱塞中，包括至少一个第一柱塞和至少一个第二柱塞，各所述第一柱塞的轴线相互平行，各所述第二柱塞的轴线相互平行，且所述第一柱塞的轴线与所述第二柱塞的轴线互为垂直。
作为实施例之一，所述壳体的内壁上相对开设有进液槽和排液槽，各所述进液口均与所述进液槽连通，所述排液槽与所述排液端导通。
作为实施例之一，沿所述转子体的轴向，各所述第一柱塞与各所述第二柱塞交叉布置。
本发明实施例涉及一种采油装置，包括如上所述的容积式泵，所述传动曲轴的传动端连接有驱动装置。
作为实施例之一，所述驱动装置包括潜油电机，所述壳体的远离其排液端的一端与所述潜油电机的连接接头固连，所述传动端与所述潜油电机的输出轴连接。
本发明实施例至少具有如下有益效果：本实施例提供的容积式泵结构简单，设备成本低廉；应用于采油时，由于柱塞直径小，液体排量低，若降低转子体的旋转速度，还可进一步降低排量，因此能够满足常规油田和低渗透油气田的采油排量和扬程的要求，可较好地适应产液量小的陆上油田的需求，解决现有技术中采用电潜离心泵存在的能耗高、扬程低、初期投资大、油气开发成本高等问题以及采用游粱式抽油机采油系统存在的效率低、能耗高、油气开发成本高等问题。
为了更清楚地说明本发明实施例或现有技术中的技术方案，下面将对实施例或现有技术描述中所需要使用的附图作简单地介绍，显而易见地，下面描述中的附图仅仅是本发明的一些实施例，对于本领域普通技术人员来讲，在不付出创造性劳动的前提下，还可以根据这些附图获得其它的附图。
图1为本发明实施例提供的容积式泵的结构示意图；
图2为图1沿A-A的剖视图；
图3为本发明实施例提供的采油装置的结构示意图。
下面将结合本发明实施例中的附图，对本发明实施例中的技术方案进行清楚、完整地描述，显然，所描述的实施例仅仅是本发明一部分实施例，而不是全部的实施例。基于本发明中的实施例，本领域普通技术人员在没有做出创造性劳动前提下所获得的所有其它实施例，都属于本发明保护的范围。
实施例一
如图1和图2，本发明实施例提供一种容积式泵1，包括壳体101，该壳体101具有圆柱形的泵腔，即具有由圆柱环形内壁围设形成的泵腔，一般地，上述壳体101采用中空的圆柱形壳体101，当然，也可以采用长方体等形状的壳体101。该壳体101的其中一端开口构成排液端，其另一端可以是封闭设置的也可以是开口设置的，依据实际需求相应设计即可；本实施例中，该壳体101两端开口，其中一端即为排液端，另一端可根据需要连接相应的设备。如图1和图2，所述壳体101的侧壁上开设有至少一个与所述泵腔导通的进液口105，所述壳体101的侧壁内还形成有排液通道106，所述排液通道106分别与所述泵腔及所述排液端导通。于所述壳体101内同轴嵌装有可绕自身轴线旋转的转子体102，所述转子体102内形成有至少一个用于将进液口105侧的液体导引至所述排液通道106内的贯通孔，每一所述贯通孔内滑设有一个柱塞103，各所述柱塞103沿所述转子体102的轴向依次设置且轴线均与所述转子体102的轴线垂直；各所述柱塞103均连接有驱动其在对应的所述贯通孔内往复滑移的驱动机构。其中，上述的进液口105的数量及尺寸规格等可根据实际使用情况等进行设计，如采用单一的大口径的进液孔或采用多个小口径的进液孔等。上述贯通孔用于将进液口105侧的液体导引至排液通道106内，为实现此功能，贯通孔的数量及位置宜对应设置，在转子体102绕自身轴线旋转过程中，每一贯通孔可与其中至少一个进液口105至少有部分正对连通，且与排液通道106至少有部分正对连通，以便经由进液口105进入的液体可进入贯通孔内，再导入至排液通道106内；体现在结构上，沿转子体102的轴向，每一进液口105与排液端口之间的距离为一区间距离值，每一贯通孔与排液端之间的距离也为一区间距离值，每一进液口105所对应的区间距离值与至少其中一个贯通孔所对应的区间距离值至少有部分重叠(不包含仅有一个端点值相同的情况)；以上述壳体101竖直设置为例，每一进液口105上端和/或下端所在的高度(或者说水平面)应位于其中一个贯通孔的上下两端所在的高度(或者说水平面)之间。本实施例中，上述各进液口105优选为沿壳体101径向开设的进液孔或进液槽(即与壳体101曲率相同的弧形槽)；上述各贯通孔优选为沿转子体102径向开设的通孔，贯通孔的轴线与转子体102的轴线垂直相交。上述的排液通道106优选为是在壳体101内壁上对应开设的排液槽，可以是平行于壳体101轴向的多条排液槽道，也可以是一个完整的弧形槽道，各排液槽优选为延伸开设至排液端，各排液槽与转子体102外壁之间可以围设形成一排液腔；当然，上述排液通道106也可以是形成于壳体101壁内的液体流道，对应需在壳体101内壁上开设至少一个与液体流道导通的排液孔，排液孔的设置则可参考各进液口105的设置方式，如可与进液口105数量相同且一一正对设置等。无疑义地，各柱塞103的长度小于对应的贯通孔的长度。在转子体102转动过程中，各贯通孔可周期性地与对应的进液口105导通，液体经由进液口105进入各贯通孔内，通过柱塞103滑动可让出空间以容纳液体， 再通过转子体102转动使得各贯通孔的储存有液体的一侧与排液通道106导通，通过柱塞103活动将贯通孔内的液体推入至排液通道106内，实现液体的泵出。本实施例提供的容积式泵1结构简单，设备成本低廉；应用于采油时，由于柱塞103直径小，液体排量低，若降低转子体102的旋转速度，还可进一步降低排量，因此能够满足常规油田和低渗透油气田的采油排量和扬程的要求，可较好地适应产液量小的陆上油田的需求，解决现有技术中采用电潜离心泵存在的能耗高、扬程低、初期投资大、油气开发成本高等问题以及采用游粱式抽油机采油系统存在的效率低、能耗高、油气开发成本高等问题。
上述的容积式泵1中，泵腔体、贯通孔、柱塞103等核心部件均是圆柱形零件，加工时可以达到很高的精度配合，部件之间摩擦小，具有容积效率高、运转平稳、流量均匀性好、噪声低、工作压力高等优点。
接续上述容积式泵1的结构，对于上述的用于驱动柱塞103在贯通孔内往复滑移的驱动机构，可以采用如下结构：如图1，于所述转子体102内同轴设有用于带动各所述柱塞103在对应的所述贯通孔内往复滑移的传动曲轴104，所述传动曲轴104具有与所述转子体102固连的连接端及用于连接外设的驱动装置的传动端，各所述柱塞103均与所述传动曲轴104连接。上述转子体102与传动曲轴104同轴，即为转子体102与传动曲轴104的主轴同轴，这对于本领域技术人员是易知地；对应在转子体102内开设容置腔，用以容置该传动曲轴104，该容置腔沿转子体102轴向开设，可以是圆柱体形状的腔室，并与传动曲轴104的主轴同轴；本实施例中，优选地，上述传动曲轴104两端分别伸出于转子体102的两端之外，其中，其传动端便于与外设的驱动装置连接，而对于本容积式泵1的泵壳体101与连接接头螺纹连接的结构，上述传动曲轴104的连接端伸出转子体102的对应端之外且与对应侧的连接接头之间通过轴承配合实现可转动连接，另外，转子体102与泵壳体101之间以及转子体102与连接接头之间均可以通过轴承配合，以保证转子体102的工作稳定性及可靠性。
对于本领域技术人员而言，易于确定的是，为实现传动曲轴104带动各柱塞103在对应的贯通孔内往复滑移的功能，上述的各柱塞103与传动曲轴104的偏心构件连接，如连杆轴颈或曲柄臂等，可以通过连杆等实现柱塞103与对应的偏心构件的之间的连接，并通过该偏心构件驱动柱塞103在对应的贯通孔内作直线滑移运动，这是本领域技术人员根据现有技术易于设计实现的，具体此处不再赘述。请参见图1，作为本实施例的一个优选实施例，对上述的传动曲轴104优化如下：所述传动曲轴104包括连接端轴段1041、传动端轴段1043以及多个偏心轴段1042，所述连接端轴段1041及所述传动端轴段1043均与所述转子体102同轴，各所述偏心轴段1042沿所述转子体102的轴向依次设置于所述连接端轴段1041与所述传动端轴段1043之间，各所述偏心轴段1042的轴 线均偏离所述连接端轴段1041的轴线，每一所述柱塞103对应与其中一个所述偏心轴段1042连接。相应地，各所述柱塞103均开设有穿设孔1031，每一所述穿设孔1031的半径大于对应的所述偏心轴段1042的半径与该偏心轴段1042的偏心距之和，各所述柱塞103套设在对应的所述偏心轴段1042外，即传动曲轴104依次穿过各柱塞103，各偏心轴段1042可在对应的穿设孔1031内自由转动。进一步地，如图1和图2，各所述柱塞103均包括柱塞本体和两个承推件1032，各所述穿设孔1031分别开设于对应的所述柱塞本体上，各所述承推件1032均具有曲率与对应的所述偏心轴段1042曲率相同的弧形承推槽，各所述承推槽的圆心角均小于180°且槽口方向均与对应的所述柱塞本体的轴向相同，每一所述柱塞103的两所述承推槽正对设置且槽壁均与对应的所述偏心轴段1042贴靠；也即两承推槽的槽壁位于同一圆柱面上，而且两槽壁不能围合形成一完整的圆柱面，易知地，该圆柱面的直径与偏心轴段1042的直径相同，从而偏心轴段1042在随传动端轴段1043等转动时，其外壁面可始终与对应柱塞103的两承推槽贴合，在其偏心转动作用下，可推动两承推槽交替地靠近或远离转子体102的轴线，即带动对应柱塞103在贯通孔内往复滑移；由于两承推槽的槽壁的圆心角之和小于360°，即两承推槽之间具有一定的让位空间，容许偏心轴段1042在转动过程中有部分时段不与承推槽或穿设孔壁接触，从而避免偏心轴段1042对柱塞103产生沿柱塞103径向方向的作用力；本领域技术人员可以根据合理地设计(包括两承推槽的圆心角等)，实现偏心轴段1042在转动过程中可连贯地驱动柱塞103在对应的贯通孔内往复滑移。
上述传动曲轴104组成中，将传统的曲柄臂与连杆轴颈集成为一个偏心轴段1042，可以简化该传动曲轴104的结构，便于设计，结构精度高，可精确地实现对柱塞103的驱动控制。需要说明的是，上述的偏心轴段1042与柱塞103之间并不限于上述的驱动连接结构，如也可以采用连杆连接等实现二者之间的驱动连接关系，这是本领域技术人员易于确定的，此处不再详述。
进一步优选地，各所述承推件1032均可拆卸安装于对应的所述柱塞本体上，如可通过螺栓固定等；上述可拆卸连接结构，可方便传动曲轴104与各柱塞103之间的配合连接关系，使得传动曲轴104与柱塞103之间可相互拆离，便于安装维护。其中，各承推件1032可以是安装在柱塞本体的穿设孔1031孔壁上；或者，可以是在柱塞本体外壁上开设一个或两个安装槽(已图示，未标注)，各安装槽的槽底均被对应的穿设孔1031贯通，采用一个安装槽时，其开设于柱塞本体的靠近转子体102的连接端或传动端的外壁上(以泵壳体101竖直放置为例，则在该柱塞本体的顶端或底端对应开设该安装槽)，两承推件1032均安装在该安装槽内且其承推槽伸至对应的穿设孔1031处以便与偏心轴段1042贴合，采用两个安装槽时，两个安装槽沿转子体102的轴向分列于柱塞本体的轴线两侧，可在每个安装槽内对应配置上述的承推件1032(可以理解为每个承托件包括两个分解件，两个分解件分别位于两个安装槽内)。
作为本实施例提供的容积式泵1的一种具体实施方式，如图1，各所述柱塞103中，包括至少一个第一柱塞和至少一个第二柱塞，各所述第一柱塞的轴线相互平行，各所述第二柱塞的轴线相互平行，且所述第一柱塞的轴线与所述第二柱塞的轴线互为垂直。当第一柱塞所在的贯通孔的两端分别与进液通道和排液通道106连通时，第二柱塞所在的贯通孔的两端被泵壳体101内壁所封堵；当第一柱塞所在的贯通孔的两端被泵壳体101内壁封堵时，第二柱塞所在的贯通孔的两端分别与进液通道和排液通道106连通。通过上述结构，可以提高本容积式泵1的工作效率。进一步优选地，如图1，沿所述转子体102的轴向，各所述第一柱塞与各所述第二柱塞交叉布置，即每相邻两个第一柱塞之间有一个第二柱塞，每相邻两个第二柱塞之间有一个第一柱塞。
进一步优选地，如图1-图2，各进液口105均与排液通道106相对设置，其中，各进液口105优选为沿转子体102轴向依次间隔设置，而排液通道106则优选为采用上述的在壳体101内壁上对应开设排液槽的结构。通过合理的设计，基于转子体102的转动及各柱塞103的直线往复滑移之间的相对运动，使得各贯通孔可将液体由进液口105转运至排液通道106内。进一步可在壳体101的内壁上开设进液槽109，各进液口105均与进液槽109连通，便于各贯通孔的导液操作。
本实施例中，上述的柱塞103数量可以在2～200范围内选择，进液口105的数量在1～6组之间。
实施例二
本发明实施例涉及一种采油装置，包括上述实施例一所提供的容积式泵1，所述传动曲轴104的传动端连接有驱动装置。
如图3，作为实施例之一，所述驱动装置包括潜油电机2，所述壳体101的远离其排液端的一端(该端可连接一下部接头108)与所述潜油电机2的连接接头201固连，所述传动端与所述潜油电机2的输出轴202连接。上述潜油电机2与容积式泵1的连接结构是本领域技术人员根据现有技术易于设计的，此处不再一一赘述。
上述壳体101的排液端可连接油管，该排液端可螺纹连接上部接头107，并通过该上部接头107连接油管。如图1，在该上部接头107的外壁上开设有环形槽式的液体入口1071，该液体入口1071与泵壳体101的排液通道106导通，在该上部接头107的壁内开设有至少一个导液通孔1072，各导液通孔1072均与该上部接头107的中空内腔及上述的环形槽式的液体入口1071连通，则环形槽式的液体入口1071+各导液通孔1072构成该上部接头107的液体流通道，用于将泵壳体101内排出的液体导引至油管内。上述各导液通孔1072优选为是倾斜设计的，适用于常规油田和低渗透油气田的采油排量和扬程的要求，可较好地适应产液量小的陆上油田的需求。
对于上述采油装置，与现有机采方法相比，具有如下优点：
(1)排量范围好，覆盖现有的游梁式抽油机井采油
上述采油装置排量范围可控制在0.5m
3/d～45m
3/d，适应我国陆上油田生产需求。我国陆上油井产液量较小，低渗透油田的产液量甚至不足1m
3/d，主要应用游梁式抽油机采油，井数超过20万口，占生产油井总数的90％以上。而电潜离心泵主要应用于高产直井，特点是大排量(＞100m
3/d)、低扬程(＜1800m)，应用范围较小，不能替代游梁式抽油机井。
本实施例中，通过减小柱塞103直径，降低柱塞103腔体的旋转速度，可进一步降低排量，满足常规油田和低渗透油气田的采油排量和扬程的要求，解决系统效率低、能耗高，初期投资大等油气开发成本高的问题。
(2)大幅度节能
上述采油装置电能几乎全部参与举升油气，理论效率高达95％，与游梁式抽油机平均运行效率仅为26％相比，总效率提高64％。我国陆上油田游梁式抽油机超过20万口，年耗电量逾百亿千瓦时，新型容积式泵1替代游粱式抽油机采油有望每年节省电能超过64亿千瓦时。
(3)使用寿命长
上述采油装置的载荷稳定，且均由油管承载，而不需要保护器作为主要支撑件，工作工况比电潜离心泵还要好，另外，采油装置效率高，所需潜油电机功率小，进一步提高了使用寿命。通过理论对比分析，新型泵的寿命长达9年以上，每年节约大量作业费。
(4)成本低，节约地面建设费和设备费
容积式泵1单台成本远远低于潜油电动离心泵。潜油电动离心泵的排量越小，系统效率越低，例如排量为50m
3/d的电潜泵效率仅为42％。而应用上述容积式泵1，效率高达95％，举升相同产液量的所需电机功率比潜油电动离心泵小50％，电机长度短一半；而且上述容积式泵1不怕气蚀，无需分离器；上述容积式泵1长度远比离心泵短，单级容积式泵1(仅一个柱塞103)长度仅0.5m，而离心泵长度达到20m；
上述采油装置用于一口新井无需庞大的地面设备和占地费。
以上所述仅为本发明的较佳实施例而已，并不用以限制本发明，凡在本发明的精神和原则之内，所作的任何修改、等同替换、改进等，均应包含在本发明的保护范围之内。
Claims (10)
- 一种容积式泵，其特征在于：包括壳体，所述壳体的其中一端开口构成排液端，所述壳体具有圆柱形的泵腔，所述壳体的侧壁上开设有至少一个与所述泵腔导通的进液口，所述壳体的侧壁内还形成有排液通道，所述排液通道分别与所述泵腔及所述排液端导通；于所述壳体内同轴嵌装有可绕自身轴线旋转的转子体，所述转子体内形成有至少一个用于将进液口侧的液体导引至所述排液通道内的贯通孔，每一所述贯通孔内滑设有一个柱塞，各所述柱塞沿所述转子体的轴向依次设置且轴线均与所述转子体的轴线垂直；于所述转子体内同轴设有用于带动各所述柱塞在对应的所述贯通孔内往复滑移的传动曲轴，所述传动曲轴具有与所述转子体固连的连接端及用于连接外设的驱动装置的传动端，各所述柱塞均与所述传动曲轴连接。
- 如权利要求1所述的容积式泵，其特征在于：所述传动曲轴包括连接端轴段、传动端轴段以及多个偏心轴段，所述连接端轴段及所述传动端轴段均与所述转子体同轴，各所述偏心轴段沿所述转子体的轴向依次设置于所述连接端轴段与所述传动端轴段之间，各所述偏心轴段的轴线均偏离所述连接端轴段的轴线，每一所述柱塞对应与其中一个所述偏心轴段连接。
- 如权利要求2所述的容积式泵，其特征在于：各所述柱塞均开设有穿设孔，每一所述穿设孔的半径大于对应的所述偏心轴段的半径与该偏心轴段的偏心距之和，各所述柱塞套设在对应的所述偏心轴段外。
- 如权利要求3所述的容积式泵，其特征在于：各所述柱塞均包括柱塞本体和两个承推件，各所述穿设孔分别开设于对应的所述柱塞本体上，各所述承推件均具有曲率与对应的所述偏心轴段曲率相同的弧形承推槽，各所述承推槽的圆心角均小于180°且槽口方向均与对应的所述柱塞本体的轴向相同，每一所述柱塞的两所述承推槽正对设置且槽壁均与对应的所述偏心轴段贴靠。
- 如权利要求4所述的容积式泵，其特征在于：各所述承推件均可拆卸安装于对应的所述柱塞本体上。
- 如权利要求1至5中任一项所述的容积式泵，其特征在于：各所述柱塞中，包括至少一个第一柱塞和至少一个第二柱塞，各所述第一柱塞的轴线相互平行，各所述第二柱塞的轴线相互平行，且所述第一柱塞的轴线与所述第二柱塞的轴线互为垂直。
- 如权利要求6所述的容积式泵，其特征在于：所述壳体的内壁上相对开设有进液槽和排液槽，各所述进液口均与所述进液槽连通，所述排液槽与所述排液端导通。
- 如权利要求6所述的容积式泵，其特征在于：沿所述转子体的轴向，各所述第一柱塞与各所述第二柱塞交叉布置。
- 一种采油装置，其特征在于：包括如权利要求1至8中任一项所述的容积式泵，所述传动曲轴的传动端连接有驱动装置。
- 如权利要求9所述的采油装置，其特征在于：所述驱动装置包括潜油电机，所述壳体的远离其排液端的一端与所述潜油电机的连接接头固连，所述传动端与所述潜油电机的输出轴连接。
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710755744.8 | 2017-08-29 | ||
| CN201710755744.8A CN107461320B (zh) | 2017-08-29 | 2017-08-29 | 容积式泵及采油装置 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| WO2019041681A1 true WO2019041681A1 (zh) | 2019-03-07 |
Family
ID=60550689
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| PCT/CN2017/118171 WO2019041681A1 (zh) | 2017-08-29 | 2017-12-25 | 容积式泵及采油装置 |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN107461320B (zh) |
| WO (1) | WO2019041681A1 (zh) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US11867176B1 (en) * | 2021-04-16 | 2024-01-09 | Lex Submersible Pumps FZE Company | Method and apparatus for a submersible multistage labyrinth-screw pump |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107461320B (zh) * | 2017-08-29 | 2018-10-26 | 海斯比得（武汉）石油科技有限公司 | 容积式泵及采油装置 |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2189217Y (zh) * | 1992-06-06 | 1995-02-08 | 翟金涛 | 新型转子柱塞泵 |
| CN2291510Y (zh) * | 1996-09-03 | 1998-09-16 | 莱芜市钢城企业集团公司 | 双缸双作用转子活塞泵 |
| WO2001036789A1 (de) * | 1999-11-12 | 2001-05-25 | Corporate Decision Gmbh | Drehkolbenvorrichtung |
| CN200996365Y (zh) * | 2007-01-09 | 2007-12-26 | 陕西理工学院 | 油泵 |
| CN107461320A (zh) * | 2017-08-29 | 2017-12-12 | 海斯比得（武汉）石油科技有限公司 | 容积式泵及采油装置 |
Family Cites Families (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SU544768A1 (ru) * | 1975-06-10 | 1977-01-30 | Насос дл подъема жидкости из скважин | |
| US4291588A (en) * | 1976-12-06 | 1981-09-29 | Camact Pump Corp. | Transmission |
| SU1211454A1 (ru) * | 1984-06-07 | 1986-02-15 | Башкирский государственный научно-исследовательский и проектный институт нефтяной промышленности | Скважинный штанговый насос |
| SU1315654A1 (ru) * | 1985-01-07 | 1987-06-07 | Азербайджанский Институт Нефти И Химии Им.М.Азизбекова | Привод скважинного насоса |
| CN2929317Y (zh) * | 2006-07-18 | 2007-08-01 | 中国石油天然气股份有限公司 | 一种承压式偏心联轴器 |
| GB0701061D0 (en) * | 2007-01-19 | 2007-02-28 | Head Phillip | Wireline or coiled tubing deployed electric submersible pump |
| CN201218174Y (zh) * | 2008-06-13 | 2009-04-08 | 台州市压缩机制造有限公司 | 旋转气缸压缩机 |
| CN101718273A (zh) * | 2009-11-12 | 2010-06-02 | 陕西关中压缩机制造有限公司 | 旋缸活塞液泵 |
| CN101871450B (zh) * | 2010-06-08 | 2012-08-22 | 余文凌 | 小流量高扬程径向活塞泵 |
| CN207454228U (zh) * | 2017-08-29 | 2018-06-05 | 海斯比得（武汉）石油科技有限公司 | 容积式泵及采油装置 |
-
2017
- 2017-08-29 CN CN201710755744.8A patent/CN107461320B/zh active Active
- 2017-12-25 WO PCT/CN2017/118171 patent/WO2019041681A1/zh active Application Filing
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2189217Y (zh) * | 1992-06-06 | 1995-02-08 | 翟金涛 | 新型转子柱塞泵 |
| CN2291510Y (zh) * | 1996-09-03 | 1998-09-16 | 莱芜市钢城企业集团公司 | 双缸双作用转子活塞泵 |
| WO2001036789A1 (de) * | 1999-11-12 | 2001-05-25 | Corporate Decision Gmbh | Drehkolbenvorrichtung |
| CN200996365Y (zh) * | 2007-01-09 | 2007-12-26 | 陕西理工学院 | 油泵 |
| CN107461320A (zh) * | 2017-08-29 | 2017-12-12 | 海斯比得（武汉）石油科技有限公司 | 容积式泵及采油装置 |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US11867176B1 (en) * | 2021-04-16 | 2024-01-09 | Lex Submersible Pumps FZE Company | Method and apparatus for a submersible multistage labyrinth-screw pump |
Also Published As
| Publication number | Publication date |
|---|---|
| CN107461320A (zh) | 2017-12-12 |
| CN107461320B (zh) | 2018-10-26 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102536807B (zh) | 原油举升系统和利用滑片泵输送流体的方法 | |
| CN107620703B (zh) | 机泵一体潜油直驱螺杆泵采油装置及方法 | |
| AU772668B2 (en) | Improved pump | |
| WO2016037449A1 (zh) | 一种带井下驱动转换装置的潜没式抽油泵机组 | |
| WO2019041681A1 (zh) | 容积式泵及采油装置 | |
| CN107387379B (zh) | 柱塞泵及采油装置 | |
| CN203783910U (zh) | 一种水力潜油泵 | |
| CN201943926U (zh) | 一种新型电动潜油升举柱塞抽油泵 | |
| CN202768405U (zh) | 深井用全金属螺杆式抽油泵 | |
| CN104329233B (zh) | 螺旋往复式井下采油装置 | |
| CN205189836U (zh) | 液驱螺杆泵采油设备 | |
| CN202467779U (zh) | 原油举升系统 | |
| CN201606228U (zh) | 潜油电机柱塞式隔膜泵 | |
| CN204126864U (zh) | 一种带井下驱动转换装置的潜没式抽油泵机组 | |
| CN208169072U (zh) | 一种矿井排水用抽水泵 | |
| CN207454228U (zh) | 容积式泵及采油装置 | |
| CN102828939B (zh) | 带有缓冲器的电潜双向管式抽油泵 | |
| CN108708851A (zh) | 一种稠油热采多级超长潜油螺杆泵系统 | |
| CN207539007U (zh) | 容积式泵、动力装置及采油系统 | |
| CN107917063B (zh) | 动力装置及采油系统 | |
| CN204984366U (zh) | 井下往复增效举升装置 | |
| CN201255097Y (zh) | 电潜螺杆泵采油装置 | |
| CN203499650U (zh) | 磁悬浮机泵一体化井下采油装置 | |
| CN102094797A (zh) | 无杆电潜液力驱动柱塞式深井抽油泵 | |
| CN207033700U (zh) | 柱塞泵及采油装置 |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| 121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 17923637 Country of ref document: EP Kind code of ref document: A1 |
|
| NENP | Non-entry into the national phase |
Ref country code: DE |
|
| 122 | Ep: pct application non-entry in european phase |
Ref document number: 17923637 Country of ref document: EP Kind code of ref document: A1 |