WO2012097493A1 - Oil-pumping machine - Google Patents

Oil-pumping machine Download PDF

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Publication number
WO2012097493A1
WO2012097493A1 PCT/CN2011/002061 CN2011002061W WO2012097493A1 WO 2012097493 A1 WO2012097493 A1 WO 2012097493A1 CN 2011002061 W CN2011002061 W CN 2011002061W WO 2012097493 A1 WO2012097493 A1 WO 2012097493A1
Authority
WO
WIPO (PCT)
Prior art keywords
wheel
pumping unit
rope
rewinding
sucker rod
Prior art date
Application number
PCT/CN2011/002061
Other languages
French (fr)
Chinese (zh)
Inventor
项援
聂圣成
Original Assignee
北京宝圣得机械有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from CN201110024440.7A external-priority patent/CN102606112B/en
Priority claimed from CN2011202926800U external-priority patent/CN202181881U/en
Application filed by 北京宝圣得机械有限公司 filed Critical 北京宝圣得机械有限公司
Priority to US13/979,847 priority Critical patent/US20140241918A1/en
Publication of WO2012097493A1 publication Critical patent/WO2012097493A1/en

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Classifications

    • EFIXED CONSTRUCTIONS
    • E21EARTH OR ROCK DRILLING; MINING
    • E21BEARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B43/00Methods or apparatus for obtaining oil, gas, water, soluble or meltable materials or a slurry of minerals from wells
    • E21B43/12Methods or apparatus for controlling the flow of the obtained fluid to or in wells
    • E21B43/121Lifting well fluids
    • E21B43/126Adaptations of down-hole pump systems powered by drives outside the borehole, e.g. by a rotary or oscillating drive
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/006Solar operated
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/02Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by wind motors
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B47/00Pumps or pumping installations specially adapted for raising fluids from great depths, e.g. well pumps
    • F04B47/02Pumps or pumping installations specially adapted for raising fluids from great depths, e.g. well pumps the driving mechanisms being situated at ground level
    • F04B47/022Pumps or pumping installations specially adapted for raising fluids from great depths, e.g. well pumps the driving mechanisms being situated at ground level driving of the walking beam
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B47/00Pumps or pumping installations specially adapted for raising fluids from great depths, e.g. well pumps
    • F04B47/14Counterbalancing

Definitions

  • the invention relates to the field of oil pumping machines, and in particular to a wheel pumping unit. Background technique
  • Non-self-injection wells are widely used for beam-type crank balance pumping units.
  • This type of pumping unit has been pumping for a hundred years, with high energy consumption, low working efficiency, strong mechanical impact, and large amounts of cement and steel.
  • energy conservation and emission reduction have become a major issue in the current world oil production industry.
  • Cida 200310100186.X discloses a pumping workover rig including a sun gear shaft, a reducer, a large gear, a pinion gear, an electric motor, a hoist rope, a weight body, a counterweight frame, a guide wire rope, and a pumping machine.
  • a polishing rod a main frame, a support platform, and a sky wheel (traction wheel), wherein the large gear and the balance wheel are fixed to each other, and are mounted on the crown wheel shaft by a sky wheel bearing, and the sun gear shaft is fastened to the bracket platform by a sun gear shaft fastener Upper, or the large gear and the balance wheel and the balance wheel shaft are fixed to each other, the two ends of the balance shaft are fastened to the bracket platform by bearings, and the reducer, the motor, the brake and the overload protector are all mounted on the bracket platform, the bracket platform and the main frame
  • the top of the suspension is connected, the suspension rope is connected to the pumping rod, and the other end is connected to the axle of the skywheel by the suspension rope.
  • the weight is fastened to the balance wheel by the weight frame and the lanyard and the weight body traction rope.
  • the motor is connected to the reducer via a brake and a coupling, and the output shaft of the reducer is connected to the pinion gear, and the pinion gear meshes with the large gear.
  • the new pumping workover rig has a significant improvement in overall efficiency, and it has the function of some workover rigs.
  • a professional workover rig may be required.
  • the balance wheel and the main body member occupying the space above the sucker rod need to be displaced, causing a lot of inconvenience.
  • adaptive changes are required for the electric machine, the transmission, and the like.
  • a double-draw pumping unit is disclosed in Chinese Patent Application No. 03102663.X, in which one or more upper guide wheels are provided at the top of the bracket, and a lower guide wheel is also provided at the bottom of the bracket.
  • the upper guide wheel is fixedly mounted on the bracket, and the upper guide wheel on the side of the bracket occupies the space above the sucker rod, so in the workover work, the upper guide wheel needs to be removed to give up the space above the sucker rod.
  • the disassembly of such a guide wheel is time-consuming and laborious. In some cases, even if the upper guide wheel is removed, it is difficult to give up the space required for workover. Therefore, it is even necessary to move the pumping unit during workover. go.
  • the driving form of the existing pumping unit generally adopts friction type transmission and external tooth meshing transmission, the friction type transmission is easy to slip and the efficiency is low, and the external tooth meshing transmission wears large, the stress per unit area is concentrated and the space is occupied. .
  • One object of the present invention is to provide an improved pumping unit which has the advantages of low oil recovery cost, remarkable energy saving effect, compact structure and convenient maintenance.
  • a pumping unit comprising a main frame, a sucker rod, a weight body, a platform disposed at the top of the main frame, a motor, a guide wheel and a rewinding wheel disposed on the platform, the electric mechanism causing the rewinding to be driven
  • the wheel is rotated about its longitudinal axis, the rewind wheel having a left half and a right half distributed along the axis.
  • the winding wheel is provided with 2n first holes on the circumference of the winding wheel, and is divided into n first holes respectively located on the left half and the right half, and one lead is taken from each of the first holes
  • the weight matching traction rope is connected with the fastener on the weight body to form a counterweight running traction system;
  • the winding wheel is further provided with 2n second holes on the circumference of the winding wheel, which are respectively located in the left half and
  • Each of the n second holes on the right half leads a sucker rod suspension rope from each of the second holes through the guide wheel and is connected with the sucker rod through a tractor to constitute a sucker rod operation a traction system;
  • the rewinding wheel is further provided with a 2m circular spiral groove along the circumferential surface of the wheel, n, m is a natural number and m > n, wherein the m-circle spiral groove is located in the left half, and the m-ring spiral groove is located at the right a half portion, the spiral
  • each of the first apertures and a corresponding second aperture adjacent thereto such that at least a portion of the helical grooves extending therebetween are shared by the sucker rod suspension and the weighted traction ropes from which they are drawn.
  • the rewinding wheel has a small width, and the motor work is only to change the upper and lower directions of the sucker rod and the weight body continuously changing under the action of mutual gravitational field, and overcome the wheel-type rewinding wheel.
  • the friction between the wheel circumference and the coiled surface of the wire rope greatly improves the energy utilization rate, and
  • the reduced width is well adapted to the current weight width.
  • the sucker rod suspension rope and the weight body traction rope can always reverse the torque of the rewinding wheel.
  • the first hole and the second hole are alternately arranged in the axial direction on the left half and/or the right half.
  • the 2n first holes are arranged along a line parallel to the longitudinal axis and/or the 2n second holes are arranged along a line parallel to the longitudinal axis, and 2n first holes and/or 2n
  • the second aperture is bilaterally symmetrical about the transverse centerline.
  • the first aperture and the second aperture are at an angle ⁇ 110 along the circumference of the rewinding wheel. -145. , for example 120. , staggered arrangement.
  • the weight body traction rope is still wound around the spiral groove; at the bottom dead center of the pumping stroke, at least a portion of the pumping stroke
  • the oil rod suspension rope is still wound around the spiral groove.
  • the sucker rod suspension rope and the weight body traction rope are configured, for example, when the sucker rod suspension rope is wound between the first hole and the corresponding one of the second holes. In the case of a spiral groove, the weight body traction rope completely leaves the spiral groove, or vice versa.
  • the four weight body traction ropes extending from the four first holes may be constituted by one mother rope, wherein one end of the female rope is fixed to the four first holes by the adjustable fixing device near the rewinding. a first first hole at one end of the wheel and the other end of the female rope is taken out from the first first hole, and then the other end of the female rope is passed through a second first hole adjacent to the first first hole Inserting into the winding wheel and passing through a third first hole adjacent to the second first hole, and then passing through the fourth first hole adjacent to the third first hole And fixed thereto by an adjustable holder, thereby forming four weight-weight traction ropes of equal length.
  • the weighted tow rope thus configured can easily adjust the tension of each traction rope itself for a long time, and the female rope has a movable pulley and a rope adjuster, and has the function of self-correcting and adjusting the slack.
  • the four sucker rod suspension cords can also be constructed of a single female rope.
  • Other numbers of weight body traction ropes and sucker rod suspension ropes can also be similarly arranged.
  • a plurality of planar scroll springs are mounted at both ends of the rewinding drum body, and the two sets of planar scroll springs are wound in opposite directions, at the highest or lowest stroke of the pumping unit.
  • the central setting is to suppress the inertia when the rewinding wheel is reversed by damping.
  • the planar scroll spring thus configured can eliminate the toothing phenomenon in the mechanical toothed transmission in the internal toothed transmission, and can reduce the double-sided tooth surface wear, and reduce the mechanical commutation of the motor and the rewinding wheel. The effect of inertia and impact force to achieve mechanical smooth commutation.
  • a guide wheel bracket is further provided, the guide wheel bracket is pivotally mounted on the platform at one end, and the other end cantilever extends out of the platform and is mounted with the guide wheel, and the rotation of the rewinding wheel is The guide wheel bracket and the guide wheel are driven to pivot upward relative to the platform in a plane perpendicular to the plane of the platform.
  • connection mechanism for releasably connecting the guide wheel bracket to the rewinding wheel body when the sucker rod suspension rope is disconnected from the sucker rod and the steering wheel is pivoted upwardly
  • the connection mechanism including a first connecting portion disposed on the guide wheel bracket, a second connecting portion disposed on the winding wheel, and a connecting rope releasably connecting the first connecting portion and the second connecting portion, in a rewinding
  • the guide wheel bracket is pulled upward by the connecting rope, thereby pulling the guiding wheel to pivot upward.
  • the connecting mechanism includes a connecting portion disposed on the guide wheel bracket for releasably fixing the sucker rod suspension rope to the guide wheel bracket instead of the connecting rope when the steering wheel needs to be pivoted upward, thereby When the rewinding wheel rotates, the guide rod bracket is pulled upward by the sucker rod suspension rope, and then the guide wheel is pulled upward to pivot.
  • the configuration is such that after the workover is replaced with the work tractor of the workover machine, the rewinding wheel is driven by the motor, and the rewinding wheel drives the guide wheel to pivot upward relative to the platform, the pumping unit
  • the tractor and the sucker rod suspension rope are vertically pulled up and down in the inner groove of the guide wheel, and the guide wheel is located in the workover position, thereby conveniently allowing the workover space without manual manual operation and facilitating safe operation.
  • a workover gear is provided in the control panel of the control system to achieve a highly automated workover.
  • the pumping unit of the present invention further includes a guide wheel adjustment positioning protrusion disposed on the platform adjacent to the sucker rod, configured to cooperate with a recess provided on the guide wheel bracket to fix the guide wheel and Adjust the elevation angle of the guide wheel relative to the platform.
  • the adjustment positioning convex portion is two bolts which are screwed on both sides of the platform, and the concave portion is a groove provided on both sides of the guide wheel bracket, and the elevation angle of the guide wheel can be adjusted by screwing the bolt, thereby facilitating the guide wheel Pivot up.
  • the elevation angle is 6 degrees to 12 degrees, and the adjustment of the elevation angle can also be used to finely adjust the front and rear positions of the guide wheel relative to the wellhead.
  • the guide wheel adjusts the positioning convex portion and is disposed under it The mutual cooperation of the square recesses also prevents the guide wheels from shifting left and right, thereby improving structural stability.
  • the main frame of the pumping unit is configured to form a cylindrical main frame having a vertical cylinder chamber and a door for controlling the electrical control of the motor to be disposed in the vertical chamber, and the weight body and the weight body traction rope Extend into the chamber.
  • the height of the vertical main frame depends on the length of the stroke of the sucker rod during pumping.
  • the thickness of the steel material selected for the vertical main frame should be moderately considered to enhance the rigidity of the derrick.
  • the electrical control is rejected on the back of the main frame opening door, which is an indoor working condition. It has improved the field environment of the existing electronically controlled rejection, and strengthened the anti-theft and security.
  • the electrically controlled control panel is externally placed in a head-up position outside the door to facilitate operator operation.
  • the rewinding wheel has an inner ring gear embedded at at least one end of the inner portion of the cylinder, preferably at one end, the inner ring gear meshing with the output gear shaft of the multi-stage reducer, and the multi-stage reducer
  • the input is connected to the output shaft of the motor via a coupling.
  • the internal tooth meshing transmission between the ring gear and the output gear shaft in the present invention is close to the conventional beam pumping unit in terms of rigidity, strength and reliability, and improves the mechanical structure of the conventional external tooth drive, and the transmission system The working environment is improved and the maintenance is simple.
  • the reel type rewinding wheel is used, so that the motor reversing work control mechanical rotation capability is enhanced, and the overall performance of the motor and the controller is improved, and the matching operation is achieved.
  • the motor can be connected and driven by a shifting mechanism in the form of a planetary gear.
  • a shifting mechanism in the form of a planetary gear.
  • the inner ring gear is similarly arranged, and the sun gear, the planetary gears, the planet carrier, and the like are provided, which eliminates the above-described speed reducer.
  • the meshing gear ratio of the ring gear and the output gear shaft is significantly increased as compared with the conventional outer meshing gear ratio of 1:1, for example, 1:2.5, in the shifting mechanism of the planetary gear transmission type.
  • the number of meshing teeth is even more than 5, which makes the transmission ratio of the transmission system more reasonable.
  • the mechanical torque of the transmission is increased and the rigidity of the transmission mechanism is increased.
  • the input end of the multi-stage reducer is connected to the output shaft of the motor through a coupling, and a power-dissipating brake disc is arranged between the coupling and the input end of the multi-stage reducer to form a mechanical transmission system and Electric drive system.
  • the conventional gearbox and its transmission shaft can be omitted, the transmission mechanism is simplified, and the gearless transmission shaft type transmission is realized.
  • the sun gear, planet gears and planet carrier are housed inside the rewinding drum body, making the transmission system more compact.
  • the motor can even directly connect and drive the rewind wheel.
  • the oil pumping unit of the present invention in order to effectively utilize the wind energy in the natural world, the oil pumping unit is provided with a wind power generation system including a wind turbine generator and a fan controller connected in series. And the battery pack, and the battery pack is connected to the pumping unit control management system via the inverter. Wherein the wind power generator is arranged on a platform at the top of the main frame, and the battery pack is disposed in the weight body.
  • the pumping unit is further provided with a photovoltaic power generation system including a photovoltaic module, a photovoltaic controller and a battery pack connected in series.
  • the battery pack is connected to the pumping unit control management system via an inverter.
  • the oil pumping unit may be provided with both a wind power generation system and a photovoltaic power generation system, wherein the wind power generation system includes a wind power generator, a fan controller, and a battery pack that are sequentially connected, and the battery pack
  • the inverter is connected to the pumping unit control management system
  • the photovoltaic power generation system includes a photovoltaic module connected to the battery pack, and a photovoltaic controller is disposed between the photovoltaic module and the battery pack.
  • the counterweight of the counterweight running traction system is configured to be slightly smaller than the weight of the sucker rod operating traction system.
  • the motor forward and reverse running current difference is preferably between 1-2 amps.
  • the invention also provides a plurality of control systems for the above-mentioned pumping unit, which can realize flexible transitional commutation of mechanical and motor interactions during commutation operation, reduce impact on mechanical mechanism, improve mechanical, motor and control
  • the long-term operating strength of the device is durable.
  • Figure 1 is a side elevational view of one embodiment of a pumping unit in accordance with the present invention showing the guide wheel in a working position and a workover position;
  • Figure 2 is a side view of the pumping unit shown in Figure 1 in a working position
  • FIG 3 is a front view of the pumping unit shown in Figure 1;
  • Figure 4 is a schematic view of a planar scroll spring device disposed in a rewinding wheel
  • Figure 5 is a schematic view showing the sucker rod suspension rope substantially completely wound into the rewinding wheel
  • Figure 6 shows a schematic view of the weight body traction rope substantially completely wound into the rewinding wheel
  • Figure 7 is a plan view of the working platform of the pumping unit shown in Figure 1;
  • Figure 8 is a schematic view showing the positional relationship of the sucker rod suspension rope, the weight body traction rope, the guide wheel and the rewinding wheel;
  • Figures 9a and 9b schematically illustrate a configuration in which a sucker rod suspension rope and a weight body traction rope are wound on a spiral groove in another embodiment of the present invention
  • Figure 9c is a schematic side elevational view of Figures 9a and 9b showing two opposite rewinding directions for the upward and downward strokes of the sucker rod;
  • Figure 10a shows the physical curve of the positive and negative switching movements of the motor output shaft when the induction motor is uncontrolled
  • Figure 10b is a physical curve of the forward and reverse switching motions of the rewinding wheel without being controlled
  • Figure 10c is the internal toothing of the cylinder of the transmission output gear shaft and the rewinding wheel without being controlled Positive and negative switching operation physical characteristic curves
  • Figure 11a is a physical characteristic curve of a planar scroll spring inside the rewinding drum body, wherein the positive and negative forces are simultaneously generated;
  • Figure l ib is the resistance characteristic of the induction motor when the induction motor and the permanent magnet synchronous motor are controlled.
  • Figure 11c is a comparison of the operating conditions of the pumping unit according to the present invention and the existing beam pumping unit;
  • Figure 12 is a schematic view showing the control of the upper VI and the lower V2 of the stroke D of the sucker rod of the control system of the present invention
  • Figure 13 is a side elevational view of another embodiment of a pumping unit in accordance with the present invention showing the guide wheel in a working position and a workover position;
  • Figure 14 is a side elevational view of the pumping unit of Figure 13 in the operating position
  • Figure 15a is a plan view of the working platform of the pumping unit shown in Figure 13;
  • Figures 15b and 15c show the motor and shifting mechanism, respectively
  • Figure 16 is a view showing still another embodiment of the oil pumping unit of Figure 13 equipped with a wind power generation system and a photovoltaic power generation system;
  • Figure 17 is a schematic view showing the arrangement between a wind power generation system and a photovoltaic power generation system equipped with a pumping unit according to the present invention
  • Figure 18 is a schematic view of the shifting mechanism of the planetary gear transmission and the planar scroll spring disposed in the rewinding wheel. List of reference signs
  • the wheeled pumping unit of the present invention mainly comprises a vertical tubular main frame 9, a sucker rod 1, a weight body 11, a platform 8 disposed at the top of the main frame, and a motor disposed on the platform 8. 27.
  • a top platform seal 30 can also be provided on the platform 8 to avoid external influences.
  • the motor is driven by the multi-stage reducer 106 to the rewinding wheel 5 to drive the rewinding wheel, but it is conceivable that the motor can also be indirectly (for example, at light load) or indirectly through other devices.
  • the winding wheel is coupled and driven to rotate about the longitudinal axis of the winding wheel, as described in detail below.
  • the main frame 9 has a vertical cylinder chamber and a door 14 in which a control refusal 12 for controlling the motor is disposed, and the weight body 11 and the weight body traction rope 10 extend into the vertical cylinder chamber. indoor.
  • the height of the vertical tubular main frame 9 depends on the length of the stroke during pumping.
  • the thickness of the steel material selected for the vertical frame main frame 9 should be moderately considered to enhance the rigidity of the derrick, and the control refusal 12 is placed on the back of the door 14 of the main frame, which is an indoor working condition.
  • the control panel of the control panel is placed in a head-up position outside the door 14 to facilitate operational control.
  • a recess is provided in the vertical chamber opposite to the weight body, so that the weight body 11 can be extended during the downward running.
  • the stroke of the sucker rod can be changed to a certain extent The height of the vertical cylindrical main frame 9 is lowered.
  • the rewinding wheel is constructed and arranged in such a manner, as shown in Figs. 5 and 6, respectively, that the sucker rod suspension rope is completely wound into the reel type rewinding wheel and the counterweight tow rope is completely wound into the rewinding wheel.
  • a very schematic illustration on the top For the sake of clarity, the weight body traction rope is omitted in Fig. 5, and the sucker rod suspension rope is omitted in Fig. 6, and the implementation in Figs. 5 and 6 is correspondingly represented as a suspension rope or a traction rope, and the broken line indicates that it is not The spiral groove occupied by the hanging rope or the traction rope is shown.
  • the second holes 5b arranged in a straight line are symmetrically divided into two left second holes on the left side of the winding wheel and two right second holes on the right side of the winding wheel, from each of the second holes
  • Each of the 5b leads to a sucker rod suspension rope 2, and the sucker rod suspension rope 2 extends through the guide wheel 4 and is connected with the sucker rod 1 through the tractor 3 to form a sucker rod running traction system.
  • the weight body traction rope fasteners 16 on the weight body 11 are connected to form a counterweight running traction system.
  • the four second holes 5b for the sucker rod suspension 2 are closer to the intermediate portion of the winding wheel than the four first holes 5a for the weight pulling rope 10.
  • the four first holes 5a for the weight body traction rope 10 are closer to the intermediate portion of the wheel rewind wheel than the corresponding four second holes for the sucker rod suspension rope 2 also fall in the present invention.
  • the other 8 turns of the spiral groove are located in the right half of the rewinding wheel 5 and are right-handed, and the four first holes 5a are respectively arranged in the 4 turns of the spiral groove in the 16-turn spiral groove, and the 4 second holes are arranged in the The other 4 turns of the spiral groove in the 16-turn spiral groove.
  • each of the first holes and the adjacent one of the corresponding second holes provide a portion of the spiral groove extending therebetween.
  • the sucker rod suspension rope 2 and the weight body traction rope 10 which are taken out from them are shared.
  • the rewinding wheel 5 As the rewinding wheel 5 is fully wound from the sucker rod suspension rope (FIG. 5), it is rotated to the sucker rod suspension rope winding rewinding wheel shown in FIG.
  • the counterweight traction rope is correspondingly wound from the rewinding wheel and reaches the full-winding position of FIG. This winding idea will be described below with reference to Figures 9a-c.
  • the sucker rod suspension rope 2 and the weight body traction rope 10 are designed to wrap one of the sucker rod suspension rope or the weight body traction rope around the first hole and the corresponding one of the second holes during installation.
  • the spiral groove extending therebetween (and preferably substantially equal to or slightly longer than the length of the spiral groove), while the other of the weight body traction rope or the sucker rod suspension rope is correspondingly completely away from the spiral groove. 5 and 6, when the pumping unit is in operation, at the top dead center of the pumping stroke, at least a part of the weight body traction rope is still wound on the spiral groove (such as the weight body traction rope 10 of FIG.
  • the angle between the four first holes 5a and the four second holes 5b along the circumferential direction of the winding wheel is 110 to 145 degrees, preferably 120 degrees, and preferably 60 or less. It is designed such that during operation, the weight pulling rope 10 and the sucker rod suspension 2 do not interfere with each other and the torque relative to the winding pulley 5 is always opposite. It will be understood by those skilled in the art that even numbers of the first or second holes other than 4 are also within the scope of the invention, such as 2, 6, 8, etc.
  • the above configuration greatly improves the operational stability of the sucker rod and the weight body, and does not affect the operation of the weight body or the sucker rod in the case where one of the ropes is slack.
  • a fixed adjuster 24 in the form of a fixed pulley that protrudes inwardly is disposed in the winding wheel 5 to prevent the suspension rope in the form of a wire rope from being bent and adapted to adjust the tension of each rope, and then penetrates into the third
  • the fourth first hole (the rightmost first hole) adjacent to the first hole is fixed thereto by an adjustable holder, thereby forming four equal-length weight body pulling ropes 10.
  • the four sucker rod suspensions extending from a female rope form a connected lower end (free end), whereby two moving pulleys (see Figure 3) can be placed at the lower end of the joint to better balance the pumping
  • the suspension of the oil rod can also be arranged similarly, and a fixed adjuster in the form of a fixed pulley can be similarly arranged, for example, when the mother rope of the weight body traction rope is mounted. Furthermore, for other numbers of first and second holes, the above arrangement is equally applicable.
  • the rewinding wheel is divided into left by a transverse centerline TT perpendicular to the longitudinal axis 00 of the rewinding wheel (where the rewinding wheel portion incorporating the ring gear is not taken into account)
  • the half hole and the right half, the first hole, the second hole, and the spiral groove are symmetrical about the transverse center line, and the spiral groove has a " ⁇ /" shape on the rewinding wheel from a plan view.
  • Figure 9c is a right side view of the schematic rewinding wheel, and shows that the clockwise direction R1 is the direction in which the sucker rod suspension rope 2 is wound out and the weight body traction rope 10 is wound into the rewinding wheel 5; and the counterclockwise direction R2 is drawn The oil rod suspension rope 2 is wound around and the weight body traction rope 10 is wound out of the direction of the winder wheel 5.
  • the sucker rod suspension rope 2 and the weight body traction on the rewinding wheel transitions, for example, from the configuration shown in Figure 9a to the configuration shown in Figure 9b (where the rope is shown in thick solid lines and the spiral grooves not occupied by the rope are shown as dashed lines). It can be understood from this that when the sucker rod suspension rope 2 continuously circulates and leaves the spiral groove with the rotation of the winding wheel, the weight body traction rope 10 continuously winds into the common spiral groove.
  • the degree of penetration of the weight body traction rope 10 always lags behind the sucker rod by a certain distance.
  • the degree of circumvention of the hoisting rope 2 for example, there is an unoccupied spiral groove drawn in a broken line in the drawing.
  • the number of spiral grooves is related to the number of turns of the weight pulling rope or the sucker rod suspension rope, and the number of windings depends on the diameter of the winding wheel. And strokes.
  • the weight body traction rope 10 wound in the spiral groove on the reel type rewinding wheel 5 moves downward due to the gravity of the weight body 11; when the motor is reversed, the wheel type rewinding wheel 5 is driven counterclockwise Rotating, the weighted traction rope 10 is wound around the wheeled rewinding wheel 5 and pulls the weight body 11 upward, and then the gravity of the suspension rope 2 on the circumference of the wheel reel of the wheeled rewinding wheel 5 is on the sucker rod 1 and The resultant force of the reverse rotation of the motor 27 is downward.
  • the forward rotation and reverse rotation of the motor 27 only change the upper and lower directions of the reciprocating up and down movement of the sucker rod 1 and the weight body 11 under the action of the mutual gravitational field, and overcome the wheel circumference of the rewinding wheel 5 and the traction rope and The frictional force of the suspension rope and other factors, the smooth symmetry of the upper and lower moving directions utilizes the gravitational field potential energy generated by the self-weight falling body of the respective system, and reciprocally changes the running direction by the positive and negative electromotive force of the motor 27 and utilizes the natural gravitational force and machinery.
  • the symmetry of the counterweight makes full use of the mutual conversion between potential energy and kinetic energy in the design of mechanical transmission invention.
  • the digital control technology of the motor completes the precision control of the punching and stroke of the pumping unit by the numerical control technology.
  • Torque-following control of load (load) demand between torque and maximum torque.
  • the balance torque is the working condition during normal operation.
  • the maximum torque occurs in the working condition of unloading and loading work during workover, and the maximum torque output by the motor following control when the sandbox is overcome.
  • This torque is 2.5 times the torque of the counterweight 11 on one side. At this time, the downward gravity of the weight body 11 is not counted.
  • a wire rope is used as the fixed guide rope 11, (see Fig. 2), two pairs of upper and lower horizontal pulleys are suspended on the surface of the rope body, and the function is to cooperate with the upward and downward "track" of the weight body 11, The up and down positions of the weight body 11 are too high, and are controlled by the upper and lower stroke limit switches and the alarm is stopped.
  • the counterweight running traction system (see Figure 1) and the sucker rod running traction system (see Figure 2) are in their own dynamic equilibrium.
  • the inner two ends are respectively provided with a set of planar scroll springs 13 (see Fig. 4), and only one set of planes is at the highest or lowest point of the stroke of the pumping unit.
  • the scroll spring 13 is in an energy storage state, and the spring has an extended length greater than the stroke of the sucker rod.
  • the two sets of planar scroll springs are reversibly mounted in the rewinding drum body, see Fig. 11a.
  • one set of springs stores energy, and the other set of springs releases energy, thereby generating action and reaction force. Torque, greatly improving the commutation impact.
  • the arrangement of the planar scroll spring helps the auxiliary motor 27 to smoothly commutate, and the mechanical and electronic control match the flexible follow. The electric loss and the machine loss (coupling) generated by the frequent commutation of the motor 27 are further reduced, and the motor 27, the electronic control components, and the durability of the mechanical components are improved.
  • the plane vortex spring can be installed, for example, by installing a spring at an optional end of the rewinding wheel (the crown wheel) and rotating the rewinding wheel to be in the maximum energy storage state, and rotating the number of turns of the sky wheel and the calculated length of the circumference.
  • the length required for the stroke is greater than the length of the stroke.
  • the other end of the plane vortex spring is fixed to the inside of the crown wheel by a fixing pin. When the fixing pin is installed, the crown wheel cannot be rotated, and then another plane vortex spring is installed at the other end in the released state. After the above work is completed, the day wheel is released.
  • the guide wheel 4 is mounted on the guide wheel bracket 20 by a guide wheel bearing 21 and by which the latter can be pivotally mounted upwardly relative to the platform 8 in a plane perpendicular to the plane of the platform 8.
  • the guide wheel 4 is driven to pivot upward relative to the platform 8 by rotating the rewinding wheel 5.
  • a hanging ring is arranged on the cylinders of the guide wheel bracket 20 and the rewinding wheel 5.
  • This configuration causes the rewinding wheel 5 to be rotated by the motor 27, thereby pulling the guide wheel bracket 20 upward by the lanyard, thereby enabling the guide wheel 5 to be pulled up, thereby conveniently allowing the workover space without manual Dismantling the guide wheel or moving the whole machine greatly saves the cost and time of workover.
  • a guide wheel adjustment positioning dome bolt 22 is further disposed at one end of the platform 8 near the sucker rod, where the positioning dome bolts 22 are respectively mounted on the platform 8. On both sides, it cooperates with the notches or grooves on both sides of the guide wheel bracket 20 to fix the guide wheel 4 in position, and can prevent the guide wheel bracket 20 from being displaced to the left and right, thereby enhancing structural stability.
  • the height of the domed bolt can be adjusted to adjust the elevation angle of the guide wheel 4 relative to the platform 8. Arranging the guide wheels 4 at an elevation angle relative to the platform 8 enables the guide wheels to more easily pivot upward.
  • the elevation angle is, for example, 6 to 12 degrees, preferably 8 to 10 degrees, more preferably 9 degrees. Further, by adjusting the magnitude of the elevation angle, the relative position of the guide wheel and the wellhead can be adjusted.
  • the motor 27 according to the present invention is connected to the rewinding wheel 5 through the speed reducer 106 and drives the rewinding wheel.
  • one end of the inside of the cylinder of the rewinding wheel is embedded with an internal ring gear 7 which meshes with the output shaft 18 of the multi-stage reducer 106 having the first transmission ratio to form The second gear ratio of the ring gear and the gear shaft.
  • This design improves the mechanical mechanism and working environment of the gear transmission, making the conventional system not only compact, but also greatly reduced in cost compared with the conventional internal gear transmission.
  • the number of meshing teeth of the internal tooth drive is increased, the mechanical torque transmission is increased and the wear between the teeth is reduced, and the service life of the gear shaft and the ring gear is prolonged.
  • the input end of the multi-stage reducer 106 is connected to the output shaft of the motor 27 through the coupling 28, and is de-energized on the side (i.e., the outer side) of the multi-stage reducer 106 away from the coupling 28.
  • Brake disc 26 ie, brake
  • the multi-stage reducer 106 is fixedly placed on the vertical frame frame platform, and the motor 27 is fixed on the motor bracket on the platform to be horizontally docked with the multi-stage reducer coupling.
  • the motor is directly coupled to the rewind wheel.
  • the rewinding wheel is also provided with the end ring gear 7 described above, but with the difference that the motor is coupled to the ring gear 7 of the rewinding wheel 5 via the shifting mechanism 106.
  • the pumping unit of the present invention is a wheeled pumping unit, wherein the rewinding wheel 5 is rotatable about a rewinding axle 19 extending along the longitudinal axis of the rewinding wheel, the shifting mechanism 6 including a sun gear 6a, surrounding Four planetary gears 6b of the sun gear 6a arranged equidistantly in the circumferential direction and a planet carrier 6c fixedly mounted on the rewinding axle 19, wherein the output of the motor 27 is connected to the sun gear 6a to drive the sun gear to rotate, the sun gear 6a and Each of the planet gears 6b engages to drive the planetary gears 6b to rotate, and the planetary gears mesh with the ring gears 7 to drive the rewinding wheels 5 to rotate, as shown in Figures 15a-15c. It
  • the motor 27 is a permanent magnet synchronous traction machine 27, the output of which is coupled to the rewinding wheel 5 via a shifting mechanism 6 to drive the rewinding wheel rotation.
  • the permanent magnet synchronous traction machine itself There is an electromagnetic brake 6e, so there is no need to provide an additional electromagnetic brake mechanism.
  • the permanent magnet synchronous traction machine of the present invention may be, for example, a WYJ2-3.00/800 gearless three-phase AC traction machine available from Boma Traction Machine Manufacturing Co., Ltd. located in Xuchang City.
  • suitable permanent magnet synchronous traction machines can also be selected according to specific needs.
  • Permanent magnet synchronous traction machine through direct transmission mechanism including sun gear, planetary gears and planet carrier Coupling to the rewinding wheel eliminates the traditional gearbox and its drive shaft, simplifies the transmission mechanism, realizes the transmission with gearless drive shaft, and makes the transmission system of the pumping unit compact, and because of the inner ring gear The parts are evenly stressed, so the transmission is smooth and the wear is small. Compared with the existing reducer with cylindrical gear reduction, the transmission efficiency is greatly improved and the energy output loss is minimized.
  • the permanent magnet synchronous traction machine is fixed on the motor bracket located on the platform, and the output end thereof is mated with the inner ring gear of the rewinding wheel 5 through the planetary gear 6b. This transmission system is especially suitable for long stroke low stroke pumping units.
  • a planar scroll spring 13 is shown in the rewinding wheel 5 similarly to Fig. 4, but Fig. 18 also shows that a planetary gear transmission type shifting mechanism is coupled to the rewinding wheel 5.
  • Figure 16 shows another embodiment similar to Figures 13-15c, with one difference in that, in order to further reinforce the strength of the vertical tubular main frame, the opposite of the sucker rod 1 of the vertical tubular main frame 9
  • the side is provided with a reinforcing structure, and a control rejection chamber is formed, and the control for rejecting the motor 12 is arranged in the chamber, which is also an indoor working condition, and improves the field environment of the existing control rejection, and strengthens the anti-theft and Safety.
  • the control panel 114 of the control panel is placed in a head-up position outside the door, so that operation control can be performed without entering the chamber.
  • the pumping unit is provided with a wind power generation system including a wind turbine generator 123, a fan controller 125 and a battery pack 116 which are sequentially connected, and the battery Group 116 is coupled via inverter 126 to a pumping control control system for controlling the rotation of motor 27, as shown in FIG.
  • the wind turbine 123 is arranged on the platform 8 at the top of the main frame, and the blade diameter of the wind wheel 124 of the wind turbine 123 depends not only on the desired output power, but also on the wind wheel 124. The operation will not interfere with the normal operation of the pumping unit.
  • a fan horizontal rotation limiting mechanism 118 is further provided for controlling the rotation range of the wind power generator 123 to further prevent the blades of the wind wheel 124 from interfering with the operation of the pumping unit.
  • the battery pack 116 is disposed in the weight body 11 and passes through the cable 115. Connecting the motor not only saves space, but also acts as a counterweight.
  • the pumping unit may be provided with a photovoltaic power generation system including a photovoltaic module 117 connected to the battery pack 116, the photovoltaic module 117 and the battery pack 116.
  • a photovoltaic controller 29 is provided between them.
  • the power curve of the wind power generator is related to the strength of the wind farm wind power
  • the following means are adopted, that is, excess power under strong wind conditions is used for charging, and in the wind farm Under the natural conditions that wind energy is greater than light energy, the energy obtained by the photovoltaic power generation system can be used only for charging.
  • the battery pack 16 functions as a peak shifting.
  • it is also considered to input the meteorological data of the area into the pumping unit control management system 31, and randomly distribute the favorable energy.
  • the present invention also provides a control system for the above pumping unit, the system structure mainly has an oil pumping driving device for driving the upward and downward movements of the sucker rod; the pumping unit control device is used for The pumping drive is controlled.
  • the system may for example be a pumping unit control management system as described above, or other suitable control system.
  • FIG. 10a-12 A control method for controlling the pumping unit and its effects according to the present invention will now be described with reference to Figs. 10a-12.
  • the comprehensive numerical control of the pumping unit control system aims to achieve fine and accurate real-time control of the actual working conditions of the pumping unit in the production, namely, the punching, stroke and reversing, and the best comprehensive efficiency can be obtained. effect.
  • Figure 12 is the control curve of the up and down running speeds VI and V2 of the stroke D of the sucker rod, where CI and C3 are the acceleration sections; El and E2 are the constant speed sections; C2 and C4 are the deceleration sections; Z is the integration time (also See Figure l ib ); D for stroke and T/m for one stroke.
  • the speed adjustment of VI and V2 is actually to control the output frequency and S-characteristic control of the positive and negative speeds of the motor.
  • the motor 27 is positively and reversing to the upper and lower running cycle (T/m) of the sucker rod, and the number of times of the operating cycle per minute per minute is called the number of times. It can be realized by controlling the number of positive and negative reversal of the motor 27 every minute. It is mainly for the forward and reverse speed control of the motor 27 every minute.
  • the positive and reverse rotation speeds determine the speed of the control stroke and the sucker rod 1 up and down,
  • control system provides control of commutation flexibility.
  • the motor 27 is required to control the motor 27 to have an integration time Z of 0.1 s in the forward and reverse directions of the replacement, so as to provide resistance to the commutation of the motor, so that the multi-pole reducer 106 (first transmission ratio) has multiple groups.
  • Gear and rewind wheel inner cog The ring (the second transmission ratio) is flexibly meshed between the positive and negative teeth to prevent the gear from being positively and reversely replaced in the long-term continuous operation during the hard connection process, the toothing phenomenon is caused by the overshoot, and the control device changes the motor 27 To the flexible control function.
  • the mechanical planar scroll spring device has a practical effect in the reversing action, reaction force and energy storage characteristics, and smooth cushioning characteristics.
  • Figure 10a shows the relationship between the pressure P of the positive and negative switching movements of the motor output shaft and the time T under the condition that the induction motor is uncontrolled, and shows the change of the moment of inertia of the motor commutation area ⁇ Fig. 10b
  • the relationship between the pressure of the forward and reverse switching movements of the rewinding wheel and time which shows the change of the moment of inertia of the rewinding zone M 2 ;
  • Figure 11a is the physical characteristic curve of a pair of planar scroll springs inside the rewinding drum body, in which the positive and negative forces are simultaneously generated, as shown in the figure when a plane scroll spring is in the energy storage In the state, the other planar scroll spring is in the energy release state Qo, and vice versa, which may also be referred to as mechanical damping.
  • Figure l ib is the relationship between the speed and time when the induction motor and the permanent magnet synchronous motor are controlled to output the positive/negative switching of the output shaft.
  • the integral time Z between the commutations is shown, which can be regarded as the resistance.
  • High power saving rate The structure of the pumping unit of the invention transforms the circular motion of the original conventional beam pumping unit into a straight line, so that the mechanical transmission efficiency is greatly improved, and the power saving rate is between 50 and 70%. This is achieved, for example, by providing a rewind wheel with a small axial dimension, an improved shifting mechanism, and full use of clean energy.
  • the axial size of the rewinding wheel is significantly reduced, so that while reducing energy consumption, it can provide a good torque balance, and can also be well applied to the existing narrower Counterweight.
  • the final effect basically eliminates the loss of the motor generated by the external action itself, and thus the power feedback device can be set to re-feed the force generated by, for example, friction during commutation. To the grid.
  • Optimized oil recovery requires the effect of automatic intermittent pumping.
  • the interval between intermittent pumping can be arbitrarily set and automatically completed by the control management system. This can greatly reduce the cost of doing a variety of useless work, reduce the number of pump wear, increase the life of the original pump body, and achieve power saving.
  • the upper and lower speeds of the oil rod can be adjusted arbitrarily, and the upward speed is fast.
  • the slow down speed is that the speed of the liquid output is increased upward, and the slow down time makes the oil filling time of the oil pump chamber longer. Improve pump efficiency again.
  • the system of the present invention can, for example, adopt an industrial-grade GSM Chinese (English) short message unit, and monitor the time form, that is, report, patrol, check and report monitoring pause content, stroke, stroke, temperature rise, current, voltage, watt-hour meter Degrees, dynamometers, P values, S values, etc.
  • GSM Chinese English
  • control system of the present invention for example, also provides various ways of connecting the motor to the rewind wheel.

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Abstract

Disclosed is an oil-pumping machine, which is characterized in that it is composed of a secondary sheave (5) of a wheel-cylinder type driven by an electric motor. The secondary sheave has a first hole (5a) for extracting a balance weight body traction rope (10) and a second hole (5b) for extracting an oil pumping rod suspension rope (2) respectively arranged in a left-half part and a right-half part of the secondary sheave, and on the secondary sheave there are also provided multiple rounds of a spiral flute (29) in opposite rotating directions respectively on the left and right parts; wherein the first hole (5a) and the second hole (5b) are disposed spaced apart within the corresponding spiral flute in such a manner that at least one part of the spiral flute is shared by both the oil pumping rod suspension rope (2) and the balance weight body traction rope (10) during operation, and the oil pumping rod suspension rope (2) and the balance weight body traction rope (10) wind in opposite directions and they wind into or out of at least part of the spiral flute without interfering with each other.

Description

一种抽油机 技术领域  Pumping unit
本发明涉及抽油机领域, 尤其涉及一种轮筒式抽油机。 背景技术  The invention relates to the field of oil pumping machines, and in particular to a wheel pumping unit. Background technique
非自喷井采油广泛使用游梁式曲柄平衡抽油机。 这种类型的抽油机抽 油方式已有百年历史, 其用电能耗高, 工况效率低, 机械冲击力强,水泥和 钢材用量大。 为了降低采油成本, 节能降耗减排已成为世界采油业当前如 何增效的重大课题。  Non-self-injection wells are widely used for beam-type crank balance pumping units. This type of pumping unit has been pumping for a hundred years, with high energy consumption, low working efficiency, strong mechanical impact, and large amounts of cement and steel. In order to reduce the cost of oil production, energy conservation and emission reduction have become a major issue in the current world oil production industry.
中国专利申请 200310100186.X 号公开了一种抽油修井机, 它包括天 轮轴、 减速器、 大齿轮、 小齿轮、 电动机、 天轮卷扬绳、 配重体、 配重 架、 导向钢丝绳、 抽油光杆、 主框架、 支架平台、 和天轮 (牵引轮), 其中 大齿轮和天轮相互固定, 并通过天轮轴承安装在天轮轴上, 天轮轴用天轮 轴紧固器紧固在支架平台上, 或者大齿轮和天轮与天轮轴相互固定, 天轮 轴的两端通过轴承紧固在支架平台上, 减速器、 电动机、 制动器和过载保 护器都安装在支架平台上, 支架平台与主框架的顶部相连接, 悬绳器一段 连接抽油光杆, 另一端通过悬绳器牵引绳连接在天轮的轮轴上, 配重体通 过配重架和挂绳器及配重体牵引绳紧固在天轮的轮周上, 电动机经过制动 器、 联轴器与减速器连接, 减速器输出轴与小齿轮连接, 小齿轮与大齿轮 啮合。 与游梁式曲柄平衡抽油机相比, 这种新颖的抽油修井机总效率有了 显著的提高, 同时它具有一些修井机的功能。但如果需要复杂的修井作业, 可能需要专业修井机。 在这种情况下, 占据抽油杆上方空间的天轮和主体 构件需要整机移位, 造成诸多不便。 此外, 由于要作修井机之用, 对电动 机、 传动装置等要作适应性的变化。  Chinese Patent Application No. 200310100186.X discloses a pumping workover rig including a sun gear shaft, a reducer, a large gear, a pinion gear, an electric motor, a hoist rope, a weight body, a counterweight frame, a guide wire rope, and a pumping machine. a polishing rod, a main frame, a support platform, and a sky wheel (traction wheel), wherein the large gear and the balance wheel are fixed to each other, and are mounted on the crown wheel shaft by a sky wheel bearing, and the sun gear shaft is fastened to the bracket platform by a sun gear shaft fastener Upper, or the large gear and the balance wheel and the balance wheel shaft are fixed to each other, the two ends of the balance shaft are fastened to the bracket platform by bearings, and the reducer, the motor, the brake and the overload protector are all mounted on the bracket platform, the bracket platform and the main frame The top of the suspension is connected, the suspension rope is connected to the pumping rod, and the other end is connected to the axle of the skywheel by the suspension rope. The weight is fastened to the balance wheel by the weight frame and the lanyard and the weight body traction rope. On the circumference of the wheel, the motor is connected to the reducer via a brake and a coupling, and the output shaft of the reducer is connected to the pinion gear, and the pinion gear meshes with the large gear. Compared to the beam-type crank balance pumping unit, the new pumping workover rig has a significant improvement in overall efficiency, and it has the function of some workover rigs. However, if a complex workover is required, a professional workover rig may be required. In this case, the balance wheel and the main body member occupying the space above the sucker rod need to be displaced, causing a lot of inconvenience. In addition, due to the use of a workover rig, adaptive changes are required for the electric machine, the transmission, and the like.
在中国发明专利申请 03102663.X 中公开了一种双拖动抽油机, 其中 支架顶部设有一个或多个上导向轮, 且在支架的底部还设有下导向轮。 上 导向轮固定安装在支架上, 位于支架侧的上导向轮占据了抽油杆上方的空 间, 因此在进行修井作业时, 需要将上导向轮拆走才让出抽油杆上方的空 间。 而这种导向轮的拆卸费时费力, 在有些情况下, 即使将上导向轮拆走, 也很难让出修井所需的空间, 因此,在修井时甚至需要将抽油机整机移走。  A double-draw pumping unit is disclosed in Chinese Patent Application No. 03102663.X, in which one or more upper guide wheels are provided at the top of the bracket, and a lower guide wheel is also provided at the bottom of the bracket. The upper guide wheel is fixedly mounted on the bracket, and the upper guide wheel on the side of the bracket occupies the space above the sucker rod, so in the workover work, the upper guide wheel needs to be removed to give up the space above the sucker rod. The disassembly of such a guide wheel is time-consuming and laborious. In some cases, even if the upper guide wheel is removed, it is difficult to give up the space required for workover. Therefore, it is even necessary to move the pumping unit during workover. go.
在申请人于 2007年 2月 14曰提交的中国专利申请号 200710063926.5 中公开了一种抽油机, 其具有可分合式导向轮, 在需要修井时, 通过人力 扳动导向轮支架绕平行于抽油杆的轴线转动, 而使导向轮离开油杆上方, 从而让出修井空间。 这种抽油机需要人力扳动导向轮支架。 另外, 这种抽 油机还存在复绕轮体积较大、 换向平稳性不够的缺点。 Chinese patent application number 200710063926.5 submitted by the applicant on February 14, 2007 Disclosed is a pumping unit having a splittable guide wheel. When a workover is required, the guide wheel bracket is manually rotated to rotate parallel to the axis of the sucker rod, thereby causing the guide wheel to move away from the oil rod. Give up the workover space. This type of pumping unit requires manual pulling of the guide wheel bracket. In addition, the pumping unit also has the disadvantage that the rewinding wheel has a large volume and insufficient commutation stability.
另外, 现有的抽油机的驱动形式一般采用摩擦式传动和外齿啮合传 动, 摩擦式传动容易打滑且效率较低, 而外齿啮合传动磨损大、 单位面积 的应力集中并且所占空间大。  In addition, the driving form of the existing pumping unit generally adopts friction type transmission and external tooth meshing transmission, the friction type transmission is easy to slip and the efficiency is low, and the external tooth meshing transmission wears large, the stress per unit area is concentrated and the space is occupied. .
因此, 当前对维护方便、 运行平稳且结构紧凑的抽油机存在需要, 且 还希望该抽油机能够降低能耗以及充分利用清洁能源。  Therefore, there is a need for a pumping unit that is easy to maintain, stable in operation, and compact in structure, and it is also desired that the pumping unit can reduce energy consumption and make full use of clean energy.
发明内容 Summary of the invention
本发明的一个目的提供一种改进的抽油机, 其具有采油成本低、 节能 效果显著、 结构紧凑且方便维护的优点。  SUMMARY OF THE INVENTION One object of the present invention is to provide an improved pumping unit which has the advantages of low oil recovery cost, remarkable energy saving effect, compact structure and convenient maintenance.
一种抽油机, 其包括主框架, 抽油杆, 配重体, 设在该主框架顶部的 平台, 布置在该平台上的电机、 导向轮和复绕轮, 该电机构造成驱动该复 绕轮以使其绕其纵轴线转动, 该复绕轮具有沿该轴线分布的左半部分和右 半部分。 所述复绕轮的轮周上设有 2n个第一孔, 其分为分别位于左半部 分和右半部份上的各 n个第一孔, 从每个所述第一孔各引出一根配重体牵 引绳与该配重体上的紧固器相连接构成配重运行牵引系统; 所述复绕轮的 轮周上还设有 2n个第二孔,其分为分别位于左半部分和右半部份上的各 n 个第二孔, 从每个所述第二孔各引出一根抽油杆悬绳经过该导向轮并通过 牵引器与该抽油杆相连接构成抽油杆运行牵引系统; 所述复绕轮还沿其轮 周表面开设有 2m圈螺旋槽, n,m为自然数且 m > n,其中 m圈螺旋槽位于 该左半部分, 另外 m圈螺旋槽位于该右半部分,位于左半部分和位于右半 部分的螺旋槽的旋向相反, 所述第一孔和所述第二孔如此地在相应的螺旋 槽内间隔布置, 使得至少一部分螺旋槽在运行过程中供所述抽油杆悬绳和 所述配重体牵引绳共用, 所述抽油杆悬绳和所述配重体牵引绳以相反的方 向缠绕且互不干涉地绕进或绕出所述至少一部分螺旋槽。 且最好是, 对于 每一个第一孔与与其相邻的一个相应第二孔使得在它们之间延伸的螺旋 槽的至少一部分供从它们引出的抽油杆悬绳和配重体牵引绳共用。 如此设 计, 使复绕轮具有较小的宽度, 并且电机作功仅是改变抽油杆和配重体不 断在相互重力场作用下往复改变运行的上、 下行方向, 并克服轮筒式复绕 轮轮周与钢丝绳盘绕表面之间的摩擦力, 大大提高了能量利用率, 并且该 减小的宽度能很好适应于当前的配重体宽度。 且抽油杆悬绳和配重体牵引 绳可以对所述复绕轮的力矩始终反向。 A pumping unit comprising a main frame, a sucker rod, a weight body, a platform disposed at the top of the main frame, a motor, a guide wheel and a rewinding wheel disposed on the platform, the electric mechanism causing the rewinding to be driven The wheel is rotated about its longitudinal axis, the rewind wheel having a left half and a right half distributed along the axis. The winding wheel is provided with 2n first holes on the circumference of the winding wheel, and is divided into n first holes respectively located on the left half and the right half, and one lead is taken from each of the first holes The weight matching traction rope is connected with the fastener on the weight body to form a counterweight running traction system; the winding wheel is further provided with 2n second holes on the circumference of the winding wheel, which are respectively located in the left half and Each of the n second holes on the right half leads a sucker rod suspension rope from each of the second holes through the guide wheel and is connected with the sucker rod through a tractor to constitute a sucker rod operation a traction system; the rewinding wheel is further provided with a 2m circular spiral groove along the circumferential surface of the wheel, n, m is a natural number and m > n, wherein the m-circle spiral groove is located in the left half, and the m-ring spiral groove is located at the right a half portion, the spiral groove of the left half and the right half is opposite to each other, and the first hole and the second hole are spaced apart in the corresponding spiral groove such that at least a part of the spiral groove is in operation The sucker rod suspension rope and the weight body traction rope are shared, the sucker rod suspension rope and the Body weight traction rope wound in opposite directions interfere with each other and wound into or unwound at least a portion of said helical groove. And preferably, each of the first apertures and a corresponding second aperture adjacent thereto such that at least a portion of the helical grooves extending therebetween are shared by the sucker rod suspension and the weighted traction ropes from which they are drawn. So designed, the rewinding wheel has a small width, and the motor work is only to change the upper and lower directions of the sucker rod and the weight body continuously changing under the action of mutual gravitational field, and overcome the wheel-type rewinding wheel. The friction between the wheel circumference and the coiled surface of the wire rope greatly improves the energy utilization rate, and The reduced width is well adapted to the current weight width. And the sucker rod suspension rope and the weight body traction rope can always reverse the torque of the rewinding wheel.
按照本发明的一个优选方案, 第一孔和第二孔沿轴向交替布置在所述 左半部分和 /或右半部分上。 有利的是, 这 2n个第一孔沿平行于该纵轴线 的直线间隔排列和 /或 2n个第二孔沿平行于该纵轴线的直线间隔排列, 且 2n个第一孔和 /或 2n个第二孔最好是关于该横向中心线是左右对称的。  According to a preferred embodiment of the invention, the first hole and the second hole are alternately arranged in the axial direction on the left half and/or the right half. Advantageously, the 2n first holes are arranged along a line parallel to the longitudinal axis and/or the 2n second holes are arranged along a line parallel to the longitudinal axis, and 2n first holes and/or 2n Preferably, the second aperture is bilaterally symmetrical about the transverse centerline.
根据进一步优选方案, 第一孔和第二孔沿该复绕轮的周向以夹角 α110。-145。, 例如 120。, 错开布置。 另外, 所述抽油杆悬绳和配重体牵引 绳在所述螺旋槽中的缠绕圈数取决于抽油机的冲程和复绕轮的直径。 例 如, 当抽油机的冲程为 8米时, 可以采用 n=2, m=8 , 即在复绕轮上开设 用于配重体牵引绳的 4个第一孔, 和用于抽油杆悬绳的 4个第二孔, 并在 复绕轮上开设有 16圈螺旋槽, 其中复绕轮轮周的左侧 8圈螺旋槽, 右侧 8 圈螺旋槽, 其中, 左侧 8圈螺旋槽左旋, 右侧 8圈螺旋槽右旋。 然而, 左 侧 8圈螺旋槽右旋, 右侧 8圈螺旋槽左旋也落在本发明的范围内。 抽油杆 悬绳和配重体牵引绳在运行过程中在螺旋槽中的缠绕长度大于抽油机的 冲程。 有利的是, 在抽油机工作过程中, 在抽油机冲程的上止点, 至少一 部分配重体牵引绳仍缠绕在所述螺旋槽上; 在抽油机冲程的下止点, 至少 一部分抽油杆悬绳仍缠绕在所述螺旋槽上。 但对于安装时候而言, 抽油杆 悬绳和配重体牵引绳如此配置是合适的, 例如当抽油杆悬绳绕满在该第一 孔和相应的一个第二孔之间延伸的所述螺旋槽时, 所述配重体牵引绳全离 开所述螺旋槽, 或者反过来。  According to a further preferred embodiment, the first aperture and the second aperture are at an angle α110 along the circumference of the rewinding wheel. -145. , for example 120. , staggered arrangement. Further, the number of windings of the sucker rod suspension rope and the weight body traction rope in the spiral groove depends on the stroke of the pumping unit and the diameter of the rewinding wheel. For example, when the stroke of the pumping unit is 8 meters, n=2, m=8 can be used, that is, four first holes for the weight-bearing traction rope are opened on the rewinding wheel, and used for the sucker rod suspension. 4 second holes of the rope, and 16 spiral grooves are arranged on the rewinding wheel, wherein 8 turns of the spiral groove on the left side of the rewinding wheel and 8 turns of the spiral groove on the right side, wherein the left 8 turns of the spiral groove Left-handed, right-handed 8-turn spiral groove right-handed. However, the left side of the 8 turns of the spiral groove is right-handed, and the right side of the 8 turns of the spiral groove is also within the scope of the present invention. Sucker Rod The length of the wrap and the weighted tow rope in the spiral groove during operation is greater than the stroke of the pumping unit. Advantageously, during the operation of the pumping unit, at the top dead center of the pumping stroke, at least a portion of the weight body traction rope is still wound around the spiral groove; at the bottom dead center of the pumping stroke, at least a portion of the pumping stroke The oil rod suspension rope is still wound around the spiral groove. However, it is suitable for the installation time that the sucker rod suspension rope and the weight body traction rope are configured, for example, when the sucker rod suspension rope is wound between the first hole and the corresponding one of the second holes. In the case of a spiral groove, the weight body traction rope completely leaves the spiral groove, or vice versa.
在上述方案中, 从 4个第一孔延伸出的 4根配重体牵引绳可以由一根 母绳如此构成, 其中母绳的一端通过可调固定器固定在 4个第一孔靠近该 复绕轮一端的第一个第一孔处并且该母绳的另一端从该第一个第一孔引 出, 随后该母绳的另一端经该第一个第一孔相邻的第二个第一孔穿入该复 绕轮内并从与该第二个第一孔相邻的第三个第一孔穿出复绕轮外, 然后再 穿入与该第三个第一孔相邻的第四个第一孔内并通过可调固定器固定于 此处, 从而形成 4根长度相等的配重体牵引绳。 如此配置的配重体牵引绳 在长时间使用中, 可以方便自我调整各牵引绳自身的松紧, 母绳都有动滑 轮顺绳调节器, 具有自我修正调节松弛度的功能。 类似地, 这 4根抽油杆 悬绳也可以如此地由一根母绳构成。 其他数目的配重体牵引绳和抽油杆悬 绳也可类似地设置。 按照本发明的优选方案, 在复绕轮筒体内部的两端各装有一组平面涡 卷弹簧, 这两组平面涡卷弹簧的卷绕方向相反, 在抽油机的冲程处于最高 点或最低点时, 其中仅一组平面涡卷弹簧处于储能状态, 所述弹簧的可伸 展长度大于抽油杆的冲程, 则华中设置是为了通过阻尼抑制复绕轮换向时 的惯性。 采用如此配置的平面涡卷弹簧, 能消除内齿啮合传动中在机械换 向冲击时存在打齿现象, 并能减小双面齿面磨损, 降低电机、 复绕轮轮筒 的同时机械换向惯量和冲击力的作用, 实现机械平滑换向。 In the above solution, the four weight body traction ropes extending from the four first holes may be constituted by one mother rope, wherein one end of the female rope is fixed to the four first holes by the adjustable fixing device near the rewinding. a first first hole at one end of the wheel and the other end of the female rope is taken out from the first first hole, and then the other end of the female rope is passed through a second first hole adjacent to the first first hole Inserting into the winding wheel and passing through a third first hole adjacent to the second first hole, and then passing through the fourth first hole adjacent to the third first hole And fixed thereto by an adjustable holder, thereby forming four weight-weight traction ropes of equal length. The weighted tow rope thus configured can easily adjust the tension of each traction rope itself for a long time, and the female rope has a movable pulley and a rope adjuster, and has the function of self-correcting and adjusting the slack. Similarly, the four sucker rod suspension cords can also be constructed of a single female rope. Other numbers of weight body traction ropes and sucker rod suspension ropes can also be similarly arranged. According to a preferred embodiment of the present invention, a plurality of planar scroll springs are mounted at both ends of the rewinding drum body, and the two sets of planar scroll springs are wound in opposite directions, at the highest or lowest stroke of the pumping unit. At the time of the point, in which only one set of planar scroll springs is in an energy storage state, and the extendable length of the spring is greater than the stroke of the sucker rod, the central setting is to suppress the inertia when the rewinding wheel is reversed by damping. The planar scroll spring thus configured can eliminate the toothing phenomenon in the mechanical toothed transmission in the internal toothed transmission, and can reduce the double-sided tooth surface wear, and reduce the mechanical commutation of the motor and the rewinding wheel. The effect of inertia and impact force to achieve mechanical smooth commutation.
根据本发明的进一步的方案, 还包括导向轮支架, 该导向轮支架一端 可枢转地安装在该平台上, 另一端悬臂伸出平台外并装有该导向轮, 通过 复绕轮的转动来驱动该导向轮支架和该导向轮在与该平台所在平面垂直 的平面内相对该平台向上枢转。 在一个方案中, 设有用于需要将抽油杆悬 绳与抽油杆断开而向上枢转导向轮时将导向轮支架可松开地连接到复绕 轮主体的连接机构, 该连接机构包括布置在该导向轮支架上的第一连接 部、 设置该复绕轮上的第二连接部, 和将该第一连接部和该第二连接部可 松开地相连的连接绳, 在复绕轮转动时由连接绳拉动导向轮支架向上枢 转, 进而拉动导向轮向上枢转。 作为替代方案, 上述连接机构包括布置在 导向轮支架上连接部, 用于在需要向上枢转导向轮时将抽油杆悬绳可松开 地固定连接到导向轮支架来取代连接绳, 从而在复绕轮转动时由抽油杆悬 绳拉动导向轮支架向上枢转, 进而拉动所述导向轮向上枢转。 如此配置, 使得在修井时, 将抽油杆顶端换上修井机的作业牵引器后, 通过电机驱动 复绕轮, 而复绕轮又带动导向轮相对平台向上枢转, 抽油机的牵引器和抽 油杆悬绳在导向轮内槽中一起被后拉上扬垂立, 导向轮就位于修井位置, 从而便捷地让出修井空间, 而不需人工手动操作, 且便于安全作业。 优选 的是在控制系统的控制面板中设置有修井档, 以实现高自动化的修井。  According to a further aspect of the present invention, a guide wheel bracket is further provided, the guide wheel bracket is pivotally mounted on the platform at one end, and the other end cantilever extends out of the platform and is mounted with the guide wheel, and the rotation of the rewinding wheel is The guide wheel bracket and the guide wheel are driven to pivot upward relative to the platform in a plane perpendicular to the plane of the platform. In one aspect, there is provided a connection mechanism for releasably connecting the guide wheel bracket to the rewinding wheel body when the sucker rod suspension rope is disconnected from the sucker rod and the steering wheel is pivoted upwardly, the connection mechanism including a first connecting portion disposed on the guide wheel bracket, a second connecting portion disposed on the winding wheel, and a connecting rope releasably connecting the first connecting portion and the second connecting portion, in a rewinding When the wheel rotates, the guide wheel bracket is pulled upward by the connecting rope, thereby pulling the guiding wheel to pivot upward. As an alternative, the connecting mechanism includes a connecting portion disposed on the guide wheel bracket for releasably fixing the sucker rod suspension rope to the guide wheel bracket instead of the connecting rope when the steering wheel needs to be pivoted upward, thereby When the rewinding wheel rotates, the guide rod bracket is pulled upward by the sucker rod suspension rope, and then the guide wheel is pulled upward to pivot. The configuration is such that after the workover is replaced with the work tractor of the workover machine, the rewinding wheel is driven by the motor, and the rewinding wheel drives the guide wheel to pivot upward relative to the platform, the pumping unit The tractor and the sucker rod suspension rope are vertically pulled up and down in the inner groove of the guide wheel, and the guide wheel is located in the workover position, thereby conveniently allowing the workover space without manual manual operation and facilitating safe operation. . Preferably, a workover gear is provided in the control panel of the control system to achieve a highly automated workover.
有利的是, 本发明中的抽油机还包括靠近抽油杆布置在平台上的导向 轮调整定位凸部, 其构造成能与设置在导向轮支架上的凹部相配合来固定 该导向轮并调整该导向轮相对该平台的仰角。 由此一来, 在修井完毕后, 可以实现导向轮复位下放位置准确。 在这里, 调整定位凸部是螺纹安装在 平台两侧的两个螺栓, 所述凹部为设置在导向轮支架两侧的凹槽, 通过旋 拧螺栓可以调整导向轮的仰角, 从而有利于导向轮向上枢转。 按照本发明 的一个优选方案, 所述仰角为 6度〜 12度, 通过调整仰角还能起到对导向 轮相对井口前、 后位置的微调。 另外, 导向轮调整定位凸部和设置在其下 方的凹部的相互配合还能防止导向轮左右偏移, 从而提高了结构稳定性。 在本发明中, 抽油机的主框架配置成立筒式主框架, 其具有立筒腔室 和门, 用于控制电机的电控拒布置在立筒腔室内, 并且配重体以及配重体 牵引绳延伸入立筒腔室内。 立筒式主框架的高度取决于抽油时抽油杆冲程 的长度。 立筒式主框架选用的钢材材质厚度应该适度考虑增强井架刚性强 度, 电控拒置于主框架开门的背面, 属室内工况。 改善了现有电控拒的野 外工况环境, 加强了防盗与安全。 有利的是, 电控拒的控制面板外挂布置 在门外平视位置, 从而便于操作人员操作。 Advantageously, the pumping unit of the present invention further includes a guide wheel adjustment positioning protrusion disposed on the platform adjacent to the sucker rod, configured to cooperate with a recess provided on the guide wheel bracket to fix the guide wheel and Adjust the elevation angle of the guide wheel relative to the platform. As a result, after the completion of the workover, the position of the guide wheel resetting and lowering can be achieved accurately. Here, the adjustment positioning convex portion is two bolts which are screwed on both sides of the platform, and the concave portion is a groove provided on both sides of the guide wheel bracket, and the elevation angle of the guide wheel can be adjusted by screwing the bolt, thereby facilitating the guide wheel Pivot up. According to a preferred embodiment of the present invention, the elevation angle is 6 degrees to 12 degrees, and the adjustment of the elevation angle can also be used to finely adjust the front and rear positions of the guide wheel relative to the wellhead. In addition, the guide wheel adjusts the positioning convex portion and is disposed under it The mutual cooperation of the square recesses also prevents the guide wheels from shifting left and right, thereby improving structural stability. In the present invention, the main frame of the pumping unit is configured to form a cylindrical main frame having a vertical cylinder chamber and a door for controlling the electrical control of the motor to be disposed in the vertical chamber, and the weight body and the weight body traction rope Extend into the chamber. The height of the vertical main frame depends on the length of the stroke of the sucker rod during pumping. The thickness of the steel material selected for the vertical main frame should be moderately considered to enhance the rigidity of the derrick. The electrical control is rejected on the back of the main frame opening door, which is an indoor working condition. It has improved the field environment of the existing electronically controlled rejection, and strengthened the anti-theft and security. Advantageously, the electrically controlled control panel is externally placed in a head-up position outside the door to facilitate operator operation.
按照本发明的一个方案, 复绕轮在其筒体内部的至少一端, 优选在一 端嵌有内齿圈, 该内齿圈与多级减速器的输出齿轮轴相啮合, 而该多级减 速器的输入端通过联轴器与电机的输出轴相连接。 本发明中的内齿圈和输 出齿轮轴之间的内齿啮合传动在刚性、 强度、 可靠性方面接近传统的游梁 式抽油机, 改善了传统的外齿传动的力学结构, 并且传动系统的工作环境 得到改善, 并且维护简单。再者, 通过将内齿圈在一端嵌入轮筒式复绕轮, 不仅减小了设备的体积, 转动惯量相应降低, 还大大降低了造价。 另外, 在本发明中采用轮筒式复绕轮, 使得电机换向工作控制机械回转能力加 强, 同时使电机和控制器的综合性能提高, 并且做到匹配运行。  According to an aspect of the invention, the rewinding wheel has an inner ring gear embedded at at least one end of the inner portion of the cylinder, preferably at one end, the inner ring gear meshing with the output gear shaft of the multi-stage reducer, and the multi-stage reducer The input is connected to the output shaft of the motor via a coupling. The internal tooth meshing transmission between the ring gear and the output gear shaft in the present invention is close to the conventional beam pumping unit in terms of rigidity, strength and reliability, and improves the mechanical structure of the conventional external tooth drive, and the transmission system The working environment is improved and the maintenance is simple. Furthermore, by embedding the inner ring gear at one end into the reel type rewinding wheel, not only the volume of the device is reduced, the moment of inertia is correspondingly reduced, but also the cost is greatly reduced. In addition, in the present invention, the reel type rewinding wheel is used, so that the motor reversing work control mechanical rotation capability is enhanced, and the overall performance of the motor and the controller is improved, and the matching operation is achieved.
或者, 电机也可以通过行星齿轮传动形式的变速机构连接并驱动复绕 轮。 例如类似地设置内齿圈, 而且设置太阳轮、 行星齿轮和行星架等, 这 可以省去上述的减速器。  Alternatively, the motor can be connected and driven by a shifting mechanism in the form of a planetary gear. For example, the inner ring gear is similarly arranged, and the sun gear, the planetary gears, the planet carrier, and the like are provided, which eliminates the above-described speed reducer.
通过上述设置, 和传统的外啮合齿数比 1 : 1 相比, 所述内齿圈和所 述输出齿轮轴的啮合齿数比明显增加, 例如为 1 : 2.5 , 在行星齿轮传动形 式的变速机构中啮合齿数甚至为 5以上, 这样使得传动系统的传动比更合 理。 从而使传动的机械力矩增加, 并且使传动机构的刚性增加。 另外, 该 多级减速器的输入端通过联轴器与电机的输出轴相连接, 在联轴器和该多 级减速器的输入端之间配设有失电刹车盘, 形成机械传动系统和电力传动 系统。 而对于变速机构, 还能省去了传统变速箱和其传动轴, 简化了传动 机构, 实现了有齿无传动轴式的传动。 并且太阳轮、 行星齿轮和行星架均 容纳在复绕轮筒体内侧, 使传动系统的结构更紧凑。  With the above arrangement, the meshing gear ratio of the ring gear and the output gear shaft is significantly increased as compared with the conventional outer meshing gear ratio of 1:1, for example, 1:2.5, in the shifting mechanism of the planetary gear transmission type. The number of meshing teeth is even more than 5, which makes the transmission ratio of the transmission system more reasonable. Thereby the mechanical torque of the transmission is increased and the rigidity of the transmission mechanism is increased. In addition, the input end of the multi-stage reducer is connected to the output shaft of the motor through a coupling, and a power-dissipating brake disc is arranged between the coupling and the input end of the multi-stage reducer to form a mechanical transmission system and Electric drive system. For the shifting mechanism, the conventional gearbox and its transmission shaft can be omitted, the transmission mechanism is simplified, and the gearless transmission shaft type transmission is realized. And the sun gear, planet gears and planet carrier are housed inside the rewinding drum body, making the transmission system more compact.
在轻载的环境下, 电机甚至可以直接连接并驱动该复绕轮。  In light load environments, the motor can even directly connect and drive the rewind wheel.
在本发明的抽油机中, 为了有效利用自然界中的风能, 抽油机配设有 风力发电系统, 该风力发电系统包括顺次连接的风力发电机、 风机控制器 和蓄电池组, 而该蓄电池组经逆变器连接到抽油机控制管理系统。 其中风 力发电机布置在该主框架顶部的平台上, 蓄电池组安置在所述配重体中。 In the oil pumping unit of the present invention, in order to effectively utilize the wind energy in the natural world, the oil pumping unit is provided with a wind power generation system including a wind turbine generator and a fan controller connected in series. And the battery pack, and the battery pack is connected to the pumping unit control management system via the inverter. Wherein the wind power generator is arranged on a platform at the top of the main frame, and the battery pack is disposed in the weight body.
在本发明的另一个方案中, 为了有利地利用自然界中的太阳能, 抽油 机还配设有光能发电系统, 该光能发电系统包括顺次连接的光伏组件、 光 伏控制器和蓄电池组, 该蓄电池组经逆变器连接到抽油机控制管理系统。  In another aspect of the present invention, in order to advantageously utilize solar energy in nature, the pumping unit is further provided with a photovoltaic power generation system including a photovoltaic module, a photovoltaic controller and a battery pack connected in series. The battery pack is connected to the pumping unit control management system via an inverter.
在本发明的又一个方案中, 抽油机可同时配设有风力发电系统和光能 发电系统, 其中该风力发电系统包括顺次连接的风力发电机、 风机控制器 和蓄电池组, 而该蓄电池组经逆变器连接到抽油机控制管理系统, 该光能 发电系统包括连接到所述蓄电池组的光伏组件, 该光伏组件和该蓄电池组 之间设有光伏控制器。  In still another aspect of the present invention, the oil pumping unit may be provided with both a wind power generation system and a photovoltaic power generation system, wherein the wind power generation system includes a wind power generator, a fan controller, and a battery pack that are sequentially connected, and the battery pack The inverter is connected to the pumping unit control management system, and the photovoltaic power generation system includes a photovoltaic module connected to the battery pack, and a photovoltaic controller is disposed between the photovoltaic module and the battery pack.
另外, 在本发明中, 配重运行牵引系统的配重配置成略小于抽油杆运 行牵引系统的重量。 当抽油机正常生产工作时所述电机正、 反转运行电流 差优选在 1-2安培之间。  Further, in the present invention, the counterweight of the counterweight running traction system is configured to be slightly smaller than the weight of the sucker rod operating traction system. When the pumping unit is in normal production operation, the motor forward and reverse running current difference is preferably between 1-2 amps.
本发明还提供了多种用于上述抽油机的控制系统, 其可实现换向运行 时的机械、 电机相互配合的柔性过渡换向, 减少对机械机构的冲击力、 提 高机械、 电机和控制器的长期运行强度耐用等级。 附图说明  The invention also provides a plurality of control systems for the above-mentioned pumping unit, which can realize flexible transitional commutation of mechanical and motor interactions during commutation operation, reduce impact on mechanical mechanism, improve mechanical, motor and control The long-term operating strength of the device is durable. DRAWINGS
本发明的完整而能实现的内容, 包括对本领域技术人员来说是最佳的 实施方式, 以下结合附图作了更详细的阐述, 其中:  The complete and achievable content of the present invention includes the best embodiments for those skilled in the art, which are described in more detail below with reference to the accompanying drawings, in which:
图 1为根据本发明抽油机的一个实施例的侧视图, 示出了处于工作位 置和修井位置的导向轮;  Figure 1 is a side elevational view of one embodiment of a pumping unit in accordance with the present invention showing the guide wheel in a working position and a workover position;
图 2为图 1所示的抽油机在工作位置时的侧视图;  Figure 2 is a side view of the pumping unit shown in Figure 1 in a working position;
图 3为图 1所示抽油机的前视图;  Figure 3 is a front view of the pumping unit shown in Figure 1;
图 4为布置在复绕轮中的平面涡卷弹簧装置的示意图;  Figure 4 is a schematic view of a planar scroll spring device disposed in a rewinding wheel;
图 5示出了抽油杆悬绳基本上全绕入复绕轮上的示意图;  Figure 5 is a schematic view showing the sucker rod suspension rope substantially completely wound into the rewinding wheel;
图 6示出了配重体牵引绳基本上全绕入复绕轮上的示意图;  Figure 6 shows a schematic view of the weight body traction rope substantially completely wound into the rewinding wheel;
图 7为图 1所示抽油机的工作平台的俯视图;  Figure 7 is a plan view of the working platform of the pumping unit shown in Figure 1;
图 8为抽油杆悬绳、 配重体牵引绳、 导向轮和复绕轮的位置关系示意 图;  Figure 8 is a schematic view showing the positional relationship of the sucker rod suspension rope, the weight body traction rope, the guide wheel and the rewinding wheel;
图 9a和 9b示意性地示出了本发明的另一个实施例中抽油杆悬绳和配 重体牵引绳缠绕在螺旋槽上的配置; 图 9c是图 9a和 9b的示意性侧视图, 其中显示了用于抽油杆的向上 和向下冲程的两个相反的复绕轮方向; Figures 9a and 9b schematically illustrate a configuration in which a sucker rod suspension rope and a weight body traction rope are wound on a spiral groove in another embodiment of the present invention; Figure 9c is a schematic side elevational view of Figures 9a and 9b showing two opposite rewinding directions for the upward and downward strokes of the sucker rod;
图 10a示出了感应电机在不受控制的情况下, 电机输出轴正、 反切换 运动的物理曲线;  Figure 10a shows the physical curve of the positive and negative switching movements of the motor output shaft when the induction motor is uncontrolled;
图 10b是在不被控制的情况下,复绕轮的正、反切换运动的物理曲线; 图 10c是在不被控制的情况下, 变速器输出齿轮轴与复绕轮的筒体的 内齿啮合正、 反切换运行物理特性曲线;  Figure 10b is a physical curve of the forward and reverse switching motions of the rewinding wheel without being controlled; Figure 10c is the internal toothing of the cylinder of the transmission output gear shaft and the rewinding wheel without being controlled Positive and negative switching operation physical characteristic curves;
图 11a是复绕轮筒体内部的平面涡卷弹簧的物理特性曲线, 其中正反 作用力同时产生;  Figure 11a is a physical characteristic curve of a planar scroll spring inside the rewinding drum body, wherein the positive and negative forces are simultaneously generated;
图 l ib是感应电机、永磁同步电机被控后输出轴正 /反切换时的电阻尼 特性;  Figure l ib is the resistance characteristic of the induction motor when the induction motor and the permanent magnet synchronous motor are controlled.
图 11 c是根据本发明的抽油机与现有的游梁式抽油机的工况曲线的对 比;  Figure 11c is a comparison of the operating conditions of the pumping unit according to the present invention and the existing beam pumping unit;
图 12是本发明的控制系统对抽油杆的冲程 D的上 VI、 下 V2运行控 制示意图;  Figure 12 is a schematic view showing the control of the upper VI and the lower V2 of the stroke D of the sucker rod of the control system of the present invention;
图 13 为根据本发明抽油机的另一个实施例的侧视图, 示出了处于工 作位置和修井位置的导向轮;  Figure 13 is a side elevational view of another embodiment of a pumping unit in accordance with the present invention showing the guide wheel in a working position and a workover position;
图 14为图 13所示的抽油机在工作位置时的侧视图;  Figure 14 is a side elevational view of the pumping unit of Figure 13 in the operating position;
图 15a为图 13所示抽油机的工作平台的俯视图;  Figure 15a is a plan view of the working platform of the pumping unit shown in Figure 13;
图 15b和 15c分别示出了电机与变速机构;  Figures 15b and 15c show the motor and shifting mechanism, respectively;
图 16示出了图 13中的抽油机配设有风力发电系统和光能发电系统的 又一实施例的示意图;  Figure 16 is a view showing still another embodiment of the oil pumping unit of Figure 13 equipped with a wind power generation system and a photovoltaic power generation system;
图 17 为根据本发明的抽油机所配设的风力发电系统和光能发电系统 之间的配置示意图;  Figure 17 is a schematic view showing the arrangement between a wind power generation system and a photovoltaic power generation system equipped with a pumping unit according to the present invention;
图 18 为行星齿轮传动的变速机构以及布置在复绕轮中的平面涡卷弹 簧的示意图。 附图标记一览表  Figure 18 is a schematic view of the shifting mechanism of the planetary gear transmission and the planar scroll spring disposed in the rewinding wheel. List of reference signs
1-抽油杆, 2-抽油杆悬绳, 3-牵引器, 4-导向轮, 5-轮筒式复绕轮 (复绕轮), 5a-第一孔, 5b第二孔, 6-变速机构, 6a-太阳轮, 6b-行星轮, 6c-行星架, 6e-电磁制动器, 7-内齿圈, 8-顶部支架平台, 9-立筒式主框架, 10-配重体 牵引绳, 11-配重体, 1 Γ-固定导向绳, 12-控制拒, 13-平面涡卷弹簧, 14- 电控室门, 15-复绕轮支架, 16-配重体牵引绳紧固器, 17-配重体牵引绳紧 固孔, 18-多级减速器输出轴, 19-复绕轮轴, 20-导向轮支架, 21-导向轮轴 承, 22-导向轮调整定位凸部, 24-固定调节器, 106-多级减速器, 26-制动 器, 27-电机, 28-联轴器, 29-螺旋槽, 30-顶部平台密封罩, 114-控制面板, 115-导缆, 116-蓄电池组, 117-光伏组件, 118-风机水平旋转限位机构, 123- 风力发电机, 124-风轮, 125-风机控制器, 126-逆变器, 128-风机机舱, 129- 光伏控制器, 31 -抽油机控制管理及驱动系统。 具体实施方式 1-sucker rod, 2-sucker rod suspension rope, 3-tractor, 4-guide wheel, 5-wheel rewind wheel (rewinding wheel), 5a-first hole, 5b second hole, 6 -Transmission mechanism, 6a-sun wheel, 6b-planetary wheel, 6c-planet, 6e-electromagnetic brake, 7-ring gear, 8-top bracket platform, 9-cylinder main frame, 10-weight body Traction rope, 11-weighted body, 1 Γ-fixed guide rope, 12-control refuse, 13-planar scroll spring, 14-electric control room door, 15-rewind wheel bracket, 16-weighted traction rope fastener , 17-weighted traction rope fastening hole, 18-multi-stage reducer output shaft, 19-rewinding axle, 20-guide wheel bracket, 21-guide wheel bearing, 22-guide wheel adjustment positioning convex, 24-fixed Regulator, 106-Multi-speed reducer, 26-brake, 27-motor, 28-coupling, 29-spiral groove, 30-top platform seal, 114-control panel, 115-guide cable, 116-battery pack , 117-PV modules, 118-fan horizontal rotation limit mechanism, 123- wind turbine, 124-windwheel, 125-fan controller, 126-inverter, 128-fan cabin, 129- photovoltaic controller, 31 - Pumping unit control management and drive system. detailed description
下文将结合附图描述本发明的实施例。 本领域技术人员将明白, 附图 并不需要精确地按照比例绘制, 其可以示意性示出本发明的一些特征, 甚 至可以在附图中夸张、 剖切、 省略本发明的一些特征以更好地显示或描述 本发明。  Embodiments of the present invention will be described below with reference to the drawings. Those skilled in the art will appreciate that the drawings are not necessarily drawn to scale, which may be shown in the drawings, and may be The invention is shown or described.
图 1至图 3示出了本发明抽油机的一个优选实施例。 参见图 1 , 本发 明中的轮筒式抽油机主要包括立筒式主框架 9, 抽油杆 1 , 配重体 11 , 设 在该主框架顶部的平台 8 , 布置在该平台 8上的电机 27、 多级减速器 106、 悬臂伸出平台外的导向轮 4、 和例如被复绕轮支架 15支撑的复绕轮 5。 优 选地, 还可以在平台 8上设置顶部平台密封罩 30以避免外界影响。 该电 机通过该多级减速器 106与该复绕轮 5相连接来驱动该复绕轮, 但可以想 到的是, 该电机也可以直接 (例如在轻载时)或通过其它装置间接地与复绕 轮相连接并驱动其绕复绕轮的纵轴线转动, 见下文详细描述。 在该实施例 中, 主框架 9具有立筒腔室和门 14, 用于控制电机的控制拒 12布置在该 立筒腔室内, 并且配重体 11以及配重体牵引绳 10延伸入该立筒腔室内。 本领域技术人员应当明白, 立筒式主框架 9的高度取决于抽油时冲程的长 度。立筒式主框架 9选用的钢材材质厚度应该适度考虑增强井架刚性强度, 控制拒 12置于主框架的门 14的背面, 属室内工况。 由此一来, 除改善了 现有控制拒的野外工况环境外, 还加强了防盗与安全。 有利的是, 控制拒 的控制面板外挂布置在门 14外操作人员平视位置, 从而便于操作控制。  1 to 3 show a preferred embodiment of the pumping unit of the present invention. Referring to Figure 1, the wheeled pumping unit of the present invention mainly comprises a vertical tubular main frame 9, a sucker rod 1, a weight body 11, a platform 8 disposed at the top of the main frame, and a motor disposed on the platform 8. 27. A multi-stage reducer 106, a guide wheel 4 which is extended beyond the platform by a cantilever, and a rewinding wheel 5 supported by, for example, a rewinding wheel bracket 15. Preferably, a top platform seal 30 can also be provided on the platform 8 to avoid external influences. The motor is driven by the multi-stage reducer 106 to the rewinding wheel 5 to drive the rewinding wheel, but it is conceivable that the motor can also be indirectly (for example, at light load) or indirectly through other devices. The winding wheel is coupled and driven to rotate about the longitudinal axis of the winding wheel, as described in detail below. In this embodiment, the main frame 9 has a vertical cylinder chamber and a door 14 in which a control refusal 12 for controlling the motor is disposed, and the weight body 11 and the weight body traction rope 10 extend into the vertical cylinder chamber. indoor. Those skilled in the art will appreciate that the height of the vertical tubular main frame 9 depends on the length of the stroke during pumping. The thickness of the steel material selected for the vertical frame main frame 9 should be moderately considered to enhance the rigidity of the derrick, and the control refusal 12 is placed on the back of the door 14 of the main frame, which is an indoor working condition. As a result, in addition to improving the field environment of the existing control rejection, theft and security have been strengthened. Advantageously, the control panel of the control panel is placed in a head-up position outside the door 14 to facilitate operational control.
在一个更优选的实施例中, 为了降低立筒式主框架 9的高度, 在该立 筒腔室内与配重体相对的下方设有凹坑, 使得配重体 11 在向下运行过程 中, 能延伸入凹坑内, 从而在抽油杆冲程不变的情况下, 可以在一定程度 上降低立筒式主框架 9的高度。 In a more preferred embodiment, in order to reduce the height of the vertical column main frame 9, a recess is provided in the vertical chamber opposite to the weight body, so that the weight body 11 can be extended during the downward running. Into the pit, so that the stroke of the sucker rod can be changed to a certain extent The height of the vertical cylindrical main frame 9 is lowered.
在本发明中, 复绕轮如此构造和设置, 参见图 5和图 6, 分别示出了 抽油杆悬绳全绕入轮筒式复绕轮上和配重体牵引绳全绕入复绕轮上的非 常示意的图示。 为了清楚起见, 图 5中省略了配重体牵引绳, 而图 6中省 略了抽油杆悬绳, 则在图 5和 6中的实现相应表示为悬绳或牵引绳, 而虚 线表示为未被所显示的悬绳或牵引绳占用的螺旋槽。 在图 5和 6中为了体 现悬绳或牵引绳是悬垂下来的, 图 5和 6的复绕轮 5例如是从抽油机的正 面或背面看的, 但是本领域技术人员将明白这仅是示意性的示出悬绳和牵 引绳的缠绕, 本发明不应局限于所示实施例, 例如各第一孔或第二孔可以 是处于别的位置, 以及悬绳或牵引绳有更多或更少的缠绕圈数。 在此所述 的全绕入, 是指在抽油杆的冲程的上止点和下止点时, 配重体牵引绳或抽 油杆悬绳相应地绕入复绕轮的最大程度。从图 5中还可以看出,作为示意, 例如复绕轮的直径 D=l米, 冲程为 8米时, 复绕轮 5的轮周上设有 2n=4 个沿平行于复绕轮轴线的直线间隔排列的第二孔 5b,左右对称地分成位于 复绕轮左侧的两个左侧第二孔和位于复绕轮右侧的两个右侧第二孔, 从每 个第二孔 5b各引出一根抽油杆悬绳 2,抽油杆悬绳 2延伸经过导向轮 4并 通过牵引器 3与抽油杆 1相连接构成抽油杆运行牵引系统。 从图 5-7中可 以看出, 轮筒式复绕轮 5的轮周上设有 2n=4个沿平行于复绕轮轴线的直 线间隔排列的第一孔 5a, 类似地分成 2个左侧第一孔和 2个右侧第一孔, 从每个第一孔 5a各引出一根配重体牵引绳 10,配重体牵引绳 10通过配重 体牵引绳紧固孔 17 (图 6 )与该配重体 11上的配重体牵引绳紧固器 16相 连接构成配重运行牵引系统。 在示出的实施例中, 用于抽油杆悬绳 2的 4 个第二孔 5b比用于配重体牵引绳 10的 4个第一孔 5a更靠近复绕轮的中 间部分。 然而, 用于配重体牵引绳 10的 4个第一孔 5a比相应的用于抽油 杆悬绳 2的 4个第二孔更靠近轮筒式复绕轮的中间部分也落在本发明的保 护范围内。  In the present invention, the rewinding wheel is constructed and arranged in such a manner, as shown in Figs. 5 and 6, respectively, that the sucker rod suspension rope is completely wound into the reel type rewinding wheel and the counterweight tow rope is completely wound into the rewinding wheel. A very schematic illustration on the top. For the sake of clarity, the weight body traction rope is omitted in Fig. 5, and the sucker rod suspension rope is omitted in Fig. 6, and the implementation in Figs. 5 and 6 is correspondingly represented as a suspension rope or a traction rope, and the broken line indicates that it is not The spiral groove occupied by the hanging rope or the traction rope is shown. In Figures 5 and 6, in order to show that the suspension rope or the traction rope is suspended, the rewinding wheel 5 of Figures 5 and 6 is for example viewed from the front or the back of the pumping unit, but those skilled in the art will understand that this is only Illustratively showing the winding of the suspension rope and the traction rope, the invention should not be limited to the illustrated embodiment, for example each of the first or second holes may be in another position, and the suspension rope or traction rope has more or Less winding turns. The full wrap as described herein refers to the maximum extent to which the counterweight drawstring or the sucker bar suspension rope is wound into the rewinding wheel at the top dead center and the bottom dead center of the stroke of the sucker rod. It can also be seen from Fig. 5 that, as an example, for example, the diameter of the rewinding wheel is D = 1 m, and when the stroke is 8 m, the circumference of the rewinding wheel 5 is provided with 2n = 4 parallel to the axis of the rewinding wheel. The second holes 5b arranged in a straight line are symmetrically divided into two left second holes on the left side of the winding wheel and two right second holes on the right side of the winding wheel, from each of the second holes Each of the 5b leads to a sucker rod suspension rope 2, and the sucker rod suspension rope 2 extends through the guide wheel 4 and is connected with the sucker rod 1 through the tractor 3 to form a sucker rod running traction system. As can be seen from Figures 5-7, the wheel circumference of the reel-type rewinding wheel 5 is provided with 2n = 4 first holes 5a arranged in a line parallel to the axis of the rewinding wheel, similarly divided into two left a first side hole and two right side first holes, one weight pulling rope 10 is taken out from each of the first holes 5a, and the weight pulling rope 10 passes through the weight pulling rope fastening hole 17 (Fig. 6) The weight body traction rope fasteners 16 on the weight body 11 are connected to form a counterweight running traction system. In the illustrated embodiment, the four second holes 5b for the sucker rod suspension 2 are closer to the intermediate portion of the winding wheel than the four first holes 5a for the weight pulling rope 10. However, the four first holes 5a for the weight body traction rope 10 are closer to the intermediate portion of the wheel rewind wheel than the corresponding four second holes for the sucker rod suspension rope 2 also fall in the present invention. Within the scope of protection.
在图 5和 6所示的实施例中, 复绕轮 5具有沿其周向布置的 2m=16 圈螺旋槽 29, 其中 8圈螺旋槽位于该复绕轮 5的左半部分并且左旋, 而另 外 8圈螺旋槽位于该复绕轮 5的右半部分并且右旋, 四个第一孔 5a分别 布置在 16圈螺旋槽中的 4圈螺旋槽内, 而 4个第二孔布置在所述 16圈螺 旋槽中的另外 4 圈螺旋槽内。 如此设置, 使得从所述第一孔 5a出来的一 组 4根配重体牵引绳 10和从所述第二孔 5b出来的一组 4根抽油杆悬绳 2 中, 即互不干涉地相应绕进或绕出该复绕轮。 也就是说, 一组配重体牵引 绳 10和一组抽油杆悬绳 2共用复绕轮 5上的这些螺旋槽 29, 配重体牵引 绳离开螺旋槽时, 抽油杆悬绳绕进并占据相应的螺旋槽, 从而它们不会出 现相互干涉。 具体而言, 在图 5-7所示的实施例中, 在抽油机的工作过程 中, 为每一个第一孔与相邻的一个相应第二孔使得它们之间延伸的螺旋槽 一部分供从它们引出的抽油杆悬绳 2和配重体牵引绳 10共用。 例如, 从 图 5和图 6可看出, 随着复绕轮 5从抽油杆悬绳全绕入的配置(图 5)转动 到图 6所示的抽油杆悬绳绕出复绕轮的配置, 配重体牵引绳相应地从复绕 轮绕入并到达图 6的全绕入位置。这种缠绕思想将在下文参考图 9a-c描述。 而且, 这些抽油杆悬绳 2和配重体牵引绳 10设计成在安装时, 将抽油杆 悬绳或者配重体牵引绳之一绕满在该第一孔和该相应的一个第二孔之间 延伸的所述螺旋槽 (且优选与该螺旋槽的长度大体相等或稍长), 而此时配 重体牵引绳或者抽油杆悬绳另一个相应地全离开所述螺旋槽。 并且, 参见 图 5和 6, 在抽油机工作时, 在抽油机冲程的上止点, 至少一部分配重体 牵引绳仍缠绕在所述螺旋槽上 (如图 6的配重体牵引绳 10全绕入的视图); 而在抽油机冲程的下止点, 至少一部分抽油杆悬绳仍缠绕在所述螺旋槽上 (如图 5的抽油杆悬绳 2全绕入的视图)。 本发明的 "共用螺旋槽 "的设计使 得复绕轮的宽度大大减小, 从而自身转动惯量大大降低, 同时降低抽油机 的结构体积和用料。 且采用多根抽油悬绳和多根配重体牵引绳, 大大增强 了运行稳定性。 当其中一根绳松弛或出现其它故障时, 不会影响抽油机系 统的正常运行。 In the embodiment shown in Figures 5 and 6, the rewinding wheel 5 has a 2m = 16-turn spiral groove 29 arranged along its circumference, wherein the 8-turn spiral groove is located in the left half of the rewinding wheel 5 and is left-handed. The other 8 turns of the spiral groove are located in the right half of the rewinding wheel 5 and are right-handed, and the four first holes 5a are respectively arranged in the 4 turns of the spiral groove in the 16-turn spiral groove, and the 4 second holes are arranged in the The other 4 turns of the spiral groove in the 16-turn spiral groove. So arranged such that a set of 4 weight body traction ropes 10 coming out of the first hole 5a and a set of 4 sucker rod suspension ropes 2 coming out from the second hole 5b In the middle, that is, the rewinding wheel is independently wound or wound out without interference. That is, a set of weight body traction ropes 10 and a set of sucker rod suspension ropes 2 share these spiral grooves 29 on the rewinding wheel 5, and when the weight body traction rope leaves the spiral groove, the sucker rod suspension rope is wound up and occupied Corresponding spiral grooves so that they do not interfere with each other. Specifically, in the embodiment shown in FIGS. 5-7, during the operation of the pumping unit, each of the first holes and the adjacent one of the corresponding second holes provide a portion of the spiral groove extending therebetween. The sucker rod suspension rope 2 and the weight body traction rope 10 which are taken out from them are shared. For example, as can be seen from FIGS. 5 and 6, as the rewinding wheel 5 is fully wound from the sucker rod suspension rope (FIG. 5), it is rotated to the sucker rod suspension rope winding rewinding wheel shown in FIG. In the configuration, the counterweight traction rope is correspondingly wound from the rewinding wheel and reaches the full-winding position of FIG. This winding idea will be described below with reference to Figures 9a-c. Moreover, the sucker rod suspension rope 2 and the weight body traction rope 10 are designed to wrap one of the sucker rod suspension rope or the weight body traction rope around the first hole and the corresponding one of the second holes during installation. The spiral groove extending therebetween (and preferably substantially equal to or slightly longer than the length of the spiral groove), while the other of the weight body traction rope or the sucker rod suspension rope is correspondingly completely away from the spiral groove. 5 and 6, when the pumping unit is in operation, at the top dead center of the pumping stroke, at least a part of the weight body traction rope is still wound on the spiral groove (such as the weight body traction rope 10 of FIG. 6) At the bottom dead center of the pumping stroke, at least a portion of the sucker rod suspension rope is still wrapped around the spiral groove (see the view of the sucker rod suspension 2 fully wound in FIG. 5). The design of the "common spiral groove" of the present invention makes the width of the rewinding wheel greatly reduced, so that the own moment of inertia is greatly reduced, and at the same time, the structural volume and material of the pumping unit are reduced. The use of multiple pumping suspension ropes and multiple weight-weight traction ropes greatly enhances operational stability. When one of the ropes is slack or other faults occur, it will not affect the normal operation of the pumping unit system.
参见图 8 , 四个第一孔 5a和四个第二孔 5b沿该复绕轮周向的夹角设 计为 110度〜 145度, 优选为 120度, 且最好最小为大于等于 60。, 如此设 计使得在运行过程中, 配重体牵引绳 10和抽油杆悬绳 2的互不干扰并且 相对复绕轮 5的力矩始终相反。 本领域技术人员应当理解, 所述第一孔或 第二孔的数目为除 4之外的偶数也落在本发明的范围内, 例如 2, 6, 8等 等。 上述配置大大提高了抽油杆和配重体的运行稳定性, 在其中一根绳出 现松弛的情况下, 也不影响配重体或抽油杆的运行。  Referring to Fig. 8, the angle between the four first holes 5a and the four second holes 5b along the circumferential direction of the winding wheel is 110 to 145 degrees, preferably 120 degrees, and preferably 60 or less. It is designed such that during operation, the weight pulling rope 10 and the sucker rod suspension 2 do not interfere with each other and the torque relative to the winding pulley 5 is always opposite. It will be understood by those skilled in the art that even numbers of the first or second holes other than 4 are also within the scope of the invention, such as 2, 6, 8, etc. The above configuration greatly improves the operational stability of the sucker rod and the weight body, and does not affect the operation of the weight body or the sucker rod in the case where one of the ropes is slack.
根据本发明的更优选的实施例, 是这多根抽油杆悬绳和配重体牵引绳 是分别由一根母绳形成的。 仍以上述 n=2的图 5-图 7为例, 由一根母绳构 成 4根配重体牵引绳如此设置, 其中该母绳的一端通过可调固定器固定在 所述 4个第一孔 5a中靠近该复绕轮 5—端的第一个第一孔 (例如最左边第 一孔)处并且该母绳的另一端从该第一个第一孔引出,随后该母绳的另一端 经该第一个第一孔相邻的第二个第一孔穿入该复绕轮 5内并从与该第二个 第一孔相邻的第三个第一孔引出(在复绕轮 5 内安置有呈朝内凸起的定滑 轮形式的固定调节器 24 以防钢丝绳形式的悬绳弯折并适于调节各根绳的 拉紧程度), 然后再穿入与该第三个第一孔相邻的第四个第一孔 (最右边第 一孔)并通过可调的固定器固定于此处,从而形成 4根等长的配重体牵引绳 10。从由一条母绳伸出来的 4根抽油杆悬绳会形成相连接的下端(自由端), 由此可在该连接的下端放置两个动滑轮 (见图 3)以更好地平衡对抽油杆的 悬挂。 由一根母绳构成 4根配重体牵引绳也可以类似地如此设置, 而且例 如在安装配重体牵引绳的母绳时也可以类似地设置呈定滑轮形式的固定 调节器。 此外, 对于其他数目的第一孔和第二孔, 上述的设置也同样适用。 According to a more preferred embodiment of the invention, the plurality of sucker rod suspension ropes and the weight body traction ropes are each formed by a single female rope. Still taking the above-mentioned n=2 of FIG. 5 to FIG. 7 as an example, four weighting body traction ropes are constituted by one mother rope, wherein one end of the female rope is fixed by an adjustable fixing device. a first first hole (for example, the leftmost first hole) of the four first holes 5a adjacent to the end 5 of the winding wheel, and the other end of the mother rope is taken out from the first first hole, and then The other end of the female rope passes through the second first hole adjacent to the first first hole and penetrates into the winding wheel 5 and is taken out from the third first hole adjacent to the second first hole (in the complex A fixed adjuster 24 in the form of a fixed pulley that protrudes inwardly is disposed in the winding wheel 5 to prevent the suspension rope in the form of a wire rope from being bent and adapted to adjust the tension of each rope, and then penetrates into the third The fourth first hole (the rightmost first hole) adjacent to the first hole is fixed thereto by an adjustable holder, thereby forming four equal-length weight body pulling ropes 10. The four sucker rod suspensions extending from a female rope form a connected lower end (free end), whereby two moving pulleys (see Figure 3) can be placed at the lower end of the joint to better balance the pumping The suspension of the oil rod. The four weight body traction ropes formed by one mother rope can also be arranged similarly, and a fixed adjuster in the form of a fixed pulley can be similarly arranged, for example, when the mother rope of the weight body traction rope is mounted. Furthermore, for other numbers of first and second holes, the above arrangement is equally applicable.
下面结合图 9a-9c所示的另一实施例的非常示意性的视图来描述配重 体牵引绳和抽油杆悬绳共用它们之间的螺旋槽的配置以说明本发明的思 想。 在该实施例中, 螺旋槽的倾角被夸张示出, 且仅示意性地示出 n=l , m=8的情形,在此第二孔 5b比第一孔 5a更靠近中间。如图 9a和 9b所示, 通过垂直于复绕轮纵轴线 00,的横向中心线 TT,(在此未将嵌有内齿圈的 复绕轮部分考虑在内)将该复绕轮分成左半部分和右半部份, 第一孔、第二 孔、 以及螺旋槽关于该横向中心线对称, 且从俯视角度看, 螺旋槽在复绕 轮上呈" \ / "形。 图 9c是示意性的复绕轮右视图, 并画出顺时针方向 R1是 抽油杆悬绳 2绕出而配重体牵引绳 10绕入复绕轮 5的方向; 而逆时针方 向 R2是抽油杆悬绳 2绕入而配重体牵引绳 10绕出复绕轮 5的方向。由此, 当复绕轮 5朝方向 R1旋转以使得抽油杆从冲程上止点处或附近朝下止点 处或附近运动时, 复绕轮上的抽油杆悬绳 2和配重体牵引绳 10例如从图 9a所示配置转变到图 9b所示配置 (其中绳以粗实线示出, 未被绳占据的螺 旋槽示出为虚线)。 由此可以明白, 当抽油杆悬绳 2随复绕轮的转动不断绕 出并离开螺旋槽时, 配重体牵引绳 10则持续地绕入该共用的螺旋槽。 而 且, 例如由于上述提到的第一孔 5a和四个第二孔 5b沿该复绕轮周向的夹 角设计, 配重体牵引绳 10 的绕入程度始终会以一定距离落后于抽油杆悬 绳 2的绕出程度, 例如存在图中以虚线画出的未被占用的螺旋槽。 对于复 抽油杆悬绳 2和配重体牵引绳 10则相应地相反动作。 在本发明中, 在孔数一定的情况下, 螺旋槽的数目和配重体牵引绳或 抽油杆悬绳要卷绕的圈数有关, 而卷绕圈数又取决于复绕轮的直径和冲 程。 本领域技术人员应当明白, 为了使抽油机系统正常运行, 配重体牵引 绳或抽油杆悬绳在复绕轮上的缠绕长度大于抽油机的冲程。 The configuration of the helical groove between the weight body traction rope and the sucker rod suspension rope to share the spiral groove is described below in conjunction with a very schematic view of another embodiment shown in Figures 9a-9c to illustrate the idea of the present invention. In this embodiment, the inclination of the spiral groove is shown exaggeratedly, and only the case where n = 1, m = 8, is schematically shown, where the second hole 5b is closer to the middle than the first hole 5a. As shown in Figures 9a and 9b, the rewinding wheel is divided into left by a transverse centerline TT perpendicular to the longitudinal axis 00 of the rewinding wheel (where the rewinding wheel portion incorporating the ring gear is not taken into account) The half hole and the right half, the first hole, the second hole, and the spiral groove are symmetrical about the transverse center line, and the spiral groove has a "\ /" shape on the rewinding wheel from a plan view. Figure 9c is a right side view of the schematic rewinding wheel, and shows that the clockwise direction R1 is the direction in which the sucker rod suspension rope 2 is wound out and the weight body traction rope 10 is wound into the rewinding wheel 5; and the counterclockwise direction R2 is drawn The oil rod suspension rope 2 is wound around and the weight body traction rope 10 is wound out of the direction of the winder wheel 5. Thus, when the rewinding wheel 5 is rotated in the direction R1 such that the sucker rod moves from or near the stroke top dead center or near the bottom dead center, the sucker rod suspension rope 2 and the weight body traction on the rewinding wheel The rope 10 transitions, for example, from the configuration shown in Figure 9a to the configuration shown in Figure 9b (where the rope is shown in thick solid lines and the spiral grooves not occupied by the rope are shown as dashed lines). It can be understood from this that when the sucker rod suspension rope 2 continuously circulates and leaves the spiral groove with the rotation of the winding wheel, the weight body traction rope 10 continuously winds into the common spiral groove. Moreover, for example, due to the above-mentioned angle of the first hole 5a and the four second holes 5b along the circumferential direction of the winding wheel, the degree of penetration of the weight body traction rope 10 always lags behind the sucker rod by a certain distance. The degree of circumvention of the hoisting rope 2, for example, there is an unoccupied spiral groove drawn in a broken line in the drawing. For the double sucker rod suspension 2 and the weight body traction rope 10, the corresponding action is reversed. In the present invention, in the case where the number of holes is constant, the number of spiral grooves is related to the number of turns of the weight pulling rope or the sucker rod suspension rope, and the number of windings depends on the diameter of the winding wheel. And strokes. Those skilled in the art will appreciate that in order for the pumping unit system to function properly, the length of the weight of the weighted drawstring or the sucker rod suspension on the winder is greater than the stroke of the pump.
在抽油机运行时, 例如电机正转时带动轮筒式复绕轮 5顺时针转动, 四根抽油杆悬绳 2盘绕到轮筒复绕轮上, 由此拉动抽油杆 1向上运动, 此 时盘绕在轮筒式复绕轮 5上的螺旋槽内的配重体牵引绳 10因配重体 11的 重力作用向下运动; 在电机反转时, 带动轮筒式复绕轮 5逆时针转动, 配 重体牵引绳 10盘绕到轮筒式复绕轮 5并拉动配重体 11上行, 而这时盘绕 在轮筒式复绕轮 5轮周上的悬绳 2在抽油杆 1的重力和电机 27反转的合 力作用而向下。  When the pumping unit is running, for example, when the motor rotates forward, the wheel-type rewinding wheel 5 is rotated clockwise, and the four sucker rod suspension ropes 2 are wound onto the rewinding wheel of the drum, thereby pulling the sucker rod 1 upward. At this time, the weight body traction rope 10 wound in the spiral groove on the reel type rewinding wheel 5 moves downward due to the gravity of the weight body 11; when the motor is reversed, the wheel type rewinding wheel 5 is driven counterclockwise Rotating, the weighted traction rope 10 is wound around the wheeled rewinding wheel 5 and pulls the weight body 11 upward, and then the gravity of the suspension rope 2 on the circumference of the wheel reel of the wheeled rewinding wheel 5 is on the sucker rod 1 and The resultant force of the reverse rotation of the motor 27 is downward.
电机 27的正转、 反转作功仅是改变抽油杆 1与配重体 11在相互重力 场的作用下往复上下运动的上、 下行方向, 克服轮筒复绕轮 5轮周与牵引 绳和悬绳的摩擦力等因素, 上、 下行运动方向中的相互平稳对称均利用各 自系统的自重落体产生的重力场势能, 往复改变运行方向靠电机 27的正、 反电动势并利用自然引力作用和机械配重的对称性, 在机械传动发明设计 上充分利用势能与动能之间的互为转换紧密配合, 加之电机数字化控制技 术完成了数控技术对抽油机的冲次和冲程的精确度控制, 平衡转矩与最大 转矩之间的对负载 (载荷)需求的转矩跟随控制。 平衡转矩是常态工作时的 工况, 最大转矩出现在修井时卸载和装载工作的工况, 及井下沙卡时克服 沙卡而由电机跟随控制输出的最大转矩。 这个转矩为配重体 11 单边被提 起到装载位的 2.5倍转矩。 此时, 配重体 11方向向下的重力还未计在内。  The forward rotation and reverse rotation of the motor 27 only change the upper and lower directions of the reciprocating up and down movement of the sucker rod 1 and the weight body 11 under the action of the mutual gravitational field, and overcome the wheel circumference of the rewinding wheel 5 and the traction rope and The frictional force of the suspension rope and other factors, the smooth symmetry of the upper and lower moving directions utilizes the gravitational field potential energy generated by the self-weight falling body of the respective system, and reciprocally changes the running direction by the positive and negative electromotive force of the motor 27 and utilizes the natural gravitational force and machinery. The symmetry of the counterweight makes full use of the mutual conversion between potential energy and kinetic energy in the design of mechanical transmission invention. In addition, the digital control technology of the motor completes the precision control of the punching and stroke of the pumping unit by the numerical control technology. Torque-following control of load (load) demand between torque and maximum torque. The balance torque is the working condition during normal operation. The maximum torque occurs in the working condition of unloading and loading work during workover, and the maximum torque output by the motor following control when the sandbox is overcome. This torque is 2.5 times the torque of the counterweight 11 on one side. At this time, the downward gravity of the weight body 11 is not counted.
在轮筒复绕轮内部分别有配重体悬绳和抽油杆牵引钢丝绳的可调固 定器及过渡定滑轮 (图 6)。 配重体 11 中间由一根钢丝绳作为固定导向绳 11, (参见图 2), 两对上、 下水平的滑轮浮悬于绳体的表面, 作用是配合配 重体 11的上行、 下行"轨迹", 配重体 11的上行、 下行位置过超, 受上、 下行程限位开关控制和报警停车。  Inside the rewinding wheel, there are adjustable weights and transitional pulleys for the weighted suspension rope and the sucker rod traction wire rope (Fig. 6). In the middle of the weight body 11, a wire rope is used as the fixed guide rope 11, (see Fig. 2), two pairs of upper and lower horizontal pulleys are suspended on the surface of the rope body, and the function is to cooperate with the upward and downward "track" of the weight body 11, The up and down positions of the weight body 11 are too high, and are controlled by the upper and lower stroke limit switches and the alarm is stopped.
在抽油机的运行过程中, 配重体运行牵引系统 (参见图 1)与抽油杆运 行牵引系统 (参见图 2)呈自身动平衡态势。 为了使多级减速器 106和轮筒 式复绕轮 5的内嵌齿圈的第一传动和第二传动在运行与换向时, 有更加平 稳运行效果, 在轮筒复绕轮 5筒体内部的两端分别装有一组平面涡卷弹簧 13(参见图 4) , 在抽油机的冲程处于最高点或最低点时, 其中仅一组平面 涡卷弹簧 13处于储能状态, 并且所述弹簧的伸展长度大于抽油杆的冲程。 在复绕轮筒体内的两组平面涡卷弹簧反向安装, 参见图 11a, 在电机正向 转动时, 其中一组弹簧储能, 而另一组弹簧释能, 从而产生作用与反作用 力的力矩, 大大改善换向冲击。 平面涡卷弹簧的设置有助于辅助电机 27 平滑换向, 机械与电控相配柔性跟随。 更加减少电机 27 频繁换向所产生 的电损和机损 (联轴器)效果更加节电, 同时提高电机 27、 电控元件、 机械 部件耐用度等。 该平面涡面弹簧的安装例如可以在复绕轮(天轮) 的任选 一端装设一个弹簧并转动复绕轮使其处于最大储能态, 转动天轮的圈数与 周长的计算长度大于冲程所需长度, 此时通过固定销固定安装平面涡面弹 簧另一端在天轮内侧。 安装固定销时天轮不能让其转动, 然后以释放态在 另一端安装另一平面涡面弹簧。 上述工作完成后释放天轮筒。 During the operation of the pumping unit, the counterweight running traction system (see Figure 1) and the sucker rod running traction system (see Figure 2) are in their own dynamic equilibrium. In order to make the first transmission and the second transmission of the inner ring gear of the multi-stage reducer 106 and the roller rewinding wheel 5 in operation and reversal, there is a smoother running effect, and the reeling wheel 5 is in the cylinder The inner two ends are respectively provided with a set of planar scroll springs 13 (see Fig. 4), and only one set of planes is at the highest or lowest point of the stroke of the pumping unit. The scroll spring 13 is in an energy storage state, and the spring has an extended length greater than the stroke of the sucker rod. The two sets of planar scroll springs are reversibly mounted in the rewinding drum body, see Fig. 11a. When the motor rotates in the forward direction, one set of springs stores energy, and the other set of springs releases energy, thereby generating action and reaction force. Torque, greatly improving the commutation impact. The arrangement of the planar scroll spring helps the auxiliary motor 27 to smoothly commutate, and the mechanical and electronic control match the flexible follow. The electric loss and the machine loss (coupling) generated by the frequent commutation of the motor 27 are further reduced, and the motor 27, the electronic control components, and the durability of the mechanical components are improved. The plane vortex spring can be installed, for example, by installing a spring at an optional end of the rewinding wheel (the crown wheel) and rotating the rewinding wheel to be in the maximum energy storage state, and rotating the number of turns of the sky wheel and the calculated length of the circumference. The length required for the stroke is greater than the length of the stroke. At this time, the other end of the plane vortex spring is fixed to the inside of the crown wheel by a fixing pin. When the fixing pin is installed, the crown wheel cannot be rotated, and then another plane vortex spring is installed at the other end in the released state. After the above work is completed, the day wheel is released.
在本发明中, 有利的是, 导向轮 4通过导向轮轴承 21安装在导向轮 支架 20上并通过后者可在与平台 8所在平面垂直的平面内相对该平台 8 向上枢转地安装在该平台 8上, 并且, 该导向轮 4通过转动复绕轮 5被驱 动相对平台 8向上枢转。 具体来说, 在导向轮支架 20和复绕轮 5的筒体 上设有挂环, 在修井过程中, 断开抽油杆和抽油杆悬绳, 需要而向上向后 扬起导向轮时, 将挂绳分别挂在导向轮支架和复绕轮筒体上, 从而将两者 可松开地相连接。 这种配置使得通过电机 27驱动复绕轮 5转动, 从而通 过挂绳拉动导向轮支架 20向上枢转, 进而使导向轮 5能被后拉上扬, 从 而便捷地让出修井空间, 而无需人工拆移导向轮或者移动整机, 大大节省 了修井的费用和时间。 在向上枢转导向轮 5的过程中, 优选通过点动控制 电机驱动复绕轮转动。 另外, 还优选在平台上设有挡板 (未示出), 用于限 定导向轮的向上枢转的角度。  In the present invention, it is advantageous if the guide wheel 4 is mounted on the guide wheel bracket 20 by a guide wheel bearing 21 and by which the latter can be pivotally mounted upwardly relative to the platform 8 in a plane perpendicular to the plane of the platform 8. On the platform 8, and, the guide wheel 4 is driven to pivot upward relative to the platform 8 by rotating the rewinding wheel 5. Specifically, a hanging ring is arranged on the cylinders of the guide wheel bracket 20 and the rewinding wheel 5. During the workover process, the sucker rod and the sucker rod suspension rope are disconnected, and the guide wheel is raised upward and backward as needed. When the lanyard is hung on the guide wheel bracket and the rewinding drum body, the two are releasably connected. This configuration causes the rewinding wheel 5 to be rotated by the motor 27, thereby pulling the guide wheel bracket 20 upward by the lanyard, thereby enabling the guide wheel 5 to be pulled up, thereby conveniently allowing the workover space without manual Dismantling the guide wheel or moving the whole machine greatly saves the cost and time of workover. In the process of pivoting the guide wheel 5 upward, it is preferable to drive the rewinding wheel rotation by the jog control motor. In addition, it is also preferred to provide a baffle (not shown) on the platform for limiting the angle of upward pivoting of the guide wheels.
另外, 按照本发明的优选方案, 还参见图 2, 在平台 8的靠近抽油杆 的一端还布有导向轮调整定位圓顶螺栓 22, 在这里该定位圓顶螺栓 22是 分别安装在平台 8两侧, 其与导向轮支架 20两侧上的凹口或凹槽相配合 将导向轮 4 固定就位, 并能防止导向轮支架 20左右偏移, 增强了结构稳 定性。 通过旋拧圓顶螺栓, 可以调整圓顶螺栓的高度, 从而调整导向轮 4 相对平台 8的仰角。 将导向轮 4布置成相对平台 8成一定的仰角, 能使导 向轮更容易地向上枢转。在本发明中,仰角例如为 6度〜 12度,优选为 8〜10 度, 更优选为 9度, 另外通过调整仰角的大小, 还可以调整导向轮与井口 的相对位置。 如上文所述, 根据本发明的电机 27通过减速器 106与复绕轮 5相连 并驱动复绕轮。 按照本发明的一个优选实施例, 复绕轮的筒体内部的一端 嵌有内齿圈 7 , 该内齿圈 7与具有第一传动比的多级减速器 106的输出轴 18相啮合, 形成齿圈和齿轮轴的第二传动比。 这种设计, 改善了齿轮传动 的力学机构和工作环境, 使得传统系统不仅结构紧凑, 并且和传统的内齿 传动相比, 造价大大降低。 另外, 这种内齿传动齿啮合数增加, 增大了机 械力矩传递并且使齿间的磨损减小, 延长了齿轮轴和内齿圈的使用寿命。 In addition, according to a preferred embodiment of the present invention, referring also to FIG. 2, a guide wheel adjustment positioning dome bolt 22 is further disposed at one end of the platform 8 near the sucker rod, where the positioning dome bolts 22 are respectively mounted on the platform 8. On both sides, it cooperates with the notches or grooves on both sides of the guide wheel bracket 20 to fix the guide wheel 4 in position, and can prevent the guide wheel bracket 20 from being displaced to the left and right, thereby enhancing structural stability. By screwing the domed bolt, the height of the domed bolt can be adjusted to adjust the elevation angle of the guide wheel 4 relative to the platform 8. Arranging the guide wheels 4 at an elevation angle relative to the platform 8 enables the guide wheels to more easily pivot upward. In the present invention, the elevation angle is, for example, 6 to 12 degrees, preferably 8 to 10 degrees, more preferably 9 degrees. Further, by adjusting the magnitude of the elevation angle, the relative position of the guide wheel and the wellhead can be adjusted. As described above, the motor 27 according to the present invention is connected to the rewinding wheel 5 through the speed reducer 106 and drives the rewinding wheel. According to a preferred embodiment of the present invention, one end of the inside of the cylinder of the rewinding wheel is embedded with an internal ring gear 7 which meshes with the output shaft 18 of the multi-stage reducer 106 having the first transmission ratio to form The second gear ratio of the ring gear and the gear shaft. This design improves the mechanical mechanism and working environment of the gear transmission, making the conventional system not only compact, but also greatly reduced in cost compared with the conventional internal gear transmission. In addition, the number of meshing teeth of the internal tooth drive is increased, the mechanical torque transmission is increased and the wear between the teeth is reduced, and the service life of the gear shaft and the ring gear is prolonged.
参见图 7 , 多级减速器 106的输入端与通过联轴器 28与电机 27的输 出轴相连,并且在多级减速器 106远离联轴器 28的一侧(即外侧)配设有失 电刹车盘 26(即制动器), 形成机械传动系统和电力传动系统。 在这里, 多 级减速器 106 固定放置在立筒框架平台上, 而电机 27 固定在位于平台上 的电机支架上, 与多级减速器联轴器水平对接锁定。  Referring to Fig. 7, the input end of the multi-stage reducer 106 is connected to the output shaft of the motor 27 through the coupling 28, and is de-energized on the side (i.e., the outer side) of the multi-stage reducer 106 away from the coupling 28. Brake disc 26 (ie, brake) forms a mechanical transmission system and an electric drive system. Here, the multi-stage reducer 106 is fixedly placed on the vertical frame frame platform, and the motor 27 is fixed on the motor bracket on the platform to be horizontally docked with the multi-stage reducer coupling.
但是本领域技术人员可以想到在轻载场合, 电机直接与复绕轮相连。 或者在如图 13-16所示的其它优选方案, 复绕轮同样设置有上述的端部内 齿圈 7 , 但区别在于电机通过变速机构 106与复绕轮 5的内齿圈 7相连。  However, those skilled in the art will appreciate that in light load applications, the motor is directly coupled to the rewind wheel. Alternatively, in other preferred embodiments as shown in Figures 13-16, the rewinding wheel is also provided with the end ring gear 7 described above, but with the difference that the motor is coupled to the ring gear 7 of the rewinding wheel 5 via the shifting mechanism 106.
图 13至图 15c所示的实施例基本上类似于图 1所显示的实施例, 但 有一个主要不同之处在于提供了呈行星传动形式的变速机构 106。 参见图 13 , 本发明中的抽油机为轮筒式抽油机, 其中复绕轮 5可绕沿复绕轮纵轴 线延伸的复绕轮轴 19转动, 该变速机构 6包括太阳轮 6a、 围绕太阳轮 6a 的周向等间距布置的四个行星齿轮 6b和固定安装在复绕轮轴 19上的行星 架 6c, 其中电机 27输出端连接到太阳轮 6a而带动该太阳轮转动, 太阳轮 6a与每个行星齿轮 6b啮合进而带动各行星齿轮 6b转动,而各行星齿轮与 内齿圈 7啮合以驱动复绕轮 5转动, 如图 15a-15c所示。 本领域技术人员 应当理解, 虽然本实施例中行星齿轮 6b 的数目设置为四个, 但是根据具 体需要, 设置两个、 三个或更多数目的行星齿轮也落在本发明的范围内。  The embodiment shown in Figures 13 through 15c is substantially similar to the embodiment shown in Figure 1, but with one major difference in that a shifting mechanism 106 in the form of a planetary transmission is provided. Referring to Figure 13, the pumping unit of the present invention is a wheeled pumping unit, wherein the rewinding wheel 5 is rotatable about a rewinding axle 19 extending along the longitudinal axis of the rewinding wheel, the shifting mechanism 6 including a sun gear 6a, surrounding Four planetary gears 6b of the sun gear 6a arranged equidistantly in the circumferential direction and a planet carrier 6c fixedly mounted on the rewinding axle 19, wherein the output of the motor 27 is connected to the sun gear 6a to drive the sun gear to rotate, the sun gear 6a and Each of the planet gears 6b engages to drive the planetary gears 6b to rotate, and the planetary gears mesh with the ring gears 7 to drive the rewinding wheels 5 to rotate, as shown in Figures 15a-15c. It will be understood by those skilled in the art that although the number of the planetary gears 6b is set to four in the present embodiment, it is within the scope of the present invention to provide two, three or more numbers of planetary gears according to specific needs.
有利的是, 电机 27为永磁同步曳引机 27 , 其输出端通过变速机构 6 联接到复绕轮 5以驱动该复绕轮转动本领域技术人员应当明白, 永磁同步 曳引机自身带有电磁制动器 6e, 因此不需要配设额外的电磁制动机构。 本 发明中的永磁同步曳引机例如可以是购自位于许昌市的博玛曳引机制造 有限公司的 WYJ2-3.00/800无齿轮三相交流曳引机。 但本领域技术人员应 当明白, 根据具体需要, 也可以选择其它合适的永磁同步曳引机。  Advantageously, the motor 27 is a permanent magnet synchronous traction machine 27, the output of which is coupled to the rewinding wheel 5 via a shifting mechanism 6 to drive the rewinding wheel rotation. It will be understood by those skilled in the art that the permanent magnet synchronous traction machine itself There is an electromagnetic brake 6e, so there is no need to provide an additional electromagnetic brake mechanism. The permanent magnet synchronous traction machine of the present invention may be, for example, a WYJ2-3.00/800 gearless three-phase AC traction machine available from Boma Traction Machine Manufacturing Co., Ltd. located in Xuchang City. However, those skilled in the art should understand that other suitable permanent magnet synchronous traction machines can also be selected according to specific needs.
将永磁同步曳引机通过包括太阳轮、 行星齿轮和行星架变速机构直接 联接到复绕轮, 省去了传统的变速箱和其传动轴, 简化了传动机构, 实现 了有齿无传动轴式的传动, 并使抽油机的传动系统结构紧凑, 且由于内齿 圈的各部分受力均匀, 因此传动平稳, 磨损小。 与现有的采用圓柱齿轮减 速的减速器相比, 大大提高了传动效率, 并将能量输出损耗降至最低。 在 这里, 永磁同步曳引机固定在位于平台上的电机支架上, 其输出端通过行 星齿轮 6b与复绕轮 5的内齿圈对接啮合。 这种传动系统尤其适用于长冲 程低冲次的抽油机。 Permanent magnet synchronous traction machine through direct transmission mechanism including sun gear, planetary gears and planet carrier Coupling to the rewinding wheel eliminates the traditional gearbox and its drive shaft, simplifies the transmission mechanism, realizes the transmission with gearless drive shaft, and makes the transmission system of the pumping unit compact, and because of the inner ring gear The parts are evenly stressed, so the transmission is smooth and the wear is small. Compared with the existing reducer with cylindrical gear reduction, the transmission efficiency is greatly improved and the energy output loss is minimized. Here, the permanent magnet synchronous traction machine is fixed on the motor bracket located on the platform, and the output end thereof is mated with the inner ring gear of the rewinding wheel 5 through the planetary gear 6b. This transmission system is especially suitable for long stroke low stroke pumping units.
在图 18中,类似于图 4地示出了平面涡卷弹簧 13布置在复绕轮 5中, 但图 18还示出行星齿轮传动型的变速机构连接到该复绕轮 5。  In Fig. 18, a planar scroll spring 13 is shown in the rewinding wheel 5 similarly to Fig. 4, but Fig. 18 also shows that a planetary gear transmission type shifting mechanism is coupled to the rewinding wheel 5.
图 16示出了类似于图 13-15c的另一个实施例, 一个不同之处在于, 为了进一步加强立筒式主框架的强度, 在立筒式主框架 9的与抽油杆 1相 反的一侧设置加强结构, 并形成控制拒用腔室, 用于控制电机的控制拒 12 布置在该腔室内, 同样属室内工况,并改善了现有控制拒的野外工况环境, 加强了防盗与安全。 同样地, 控制拒的控制面板 114外挂布置在门外操作 人员平视位置, 从而不需要进入立筒腔室内就能进行操作控制。  Figure 16 shows another embodiment similar to Figures 13-15c, with one difference in that, in order to further reinforce the strength of the vertical tubular main frame, the opposite of the sucker rod 1 of the vertical tubular main frame 9 The side is provided with a reinforcing structure, and a control rejection chamber is formed, and the control for rejecting the motor 12 is arranged in the chamber, which is also an indoor working condition, and improves the field environment of the existing control rejection, and strengthens the anti-theft and Safety. Similarly, the control panel 114 of the control panel is placed in a head-up position outside the door, so that operation control can be performed without entering the chamber.
另外, 考虑到目前海上风能单机发电功率最大已经达到 5000KW, 并 且陆地风力发电机的输出功率也达到 2000KW到 3000KW之间,并且随着 风力发电技术的日渐成熟, 性能提高, 价格下降。 对于图 1至图 3中示出 的抽油机来说,传动功率的常态工况是 10KW左右,在井深 1000m ~ 1200m 提配重、 卸配重时的功率在 20KW到 25KW之间, 属于瞬时功率, 这很大 一部分取决于电机的转矩或转速。 因此, 一般的风力发电机和光能发电机 可以满足这种抽油机的供电需要。在深井情况下,可以考虑加大功率和光、 风能的储备功率。  In addition, considering that the current power generation capacity of offshore wind power has reached 5000 KW, and the output power of land wind turbines has reached 2000 KW to 3000 KW, and with the maturity of wind power technology, performance has increased and prices have fallen. For the pumping unit shown in Fig. 1 to Fig. 3, the normal working condition of the transmission power is about 10KW, and the power when the weight is 1000m ~ 1200m and the weight is unloaded is between 20KW and 25KW. Power, a large part of this depends on the torque or speed of the motor. Therefore, general wind turbines and light energy generators can meet the power supply needs of such pumping units. In the case of deep wells, it is possible to consider increasing the power and the reserve power of light and wind energy.
为此, 在图 16所示的该实施例中, 抽油机配设有风力发电系统, 该 风力发电系统包括顺次连接的风力发电机 123、 风机控制器 125和蓄电池 组 116, 而该蓄电池组 116经逆变器 126连接到至少用于控制电机 27的转 动的抽油机控制管理系统, 如图 17 所示。 从图中可以看出, 风力发电机 123布置在该主框架顶部的平台 8上, 并且风力发电机 123的风轮 124的 叶片直径不仅取决于期望的输出功率, 并且还要考虑到风轮 124的运转不 会干涉抽油机的正常运行。 另外, 还设有风机水平旋转限位机构 118 , 用 于控制风力发电机 123的转动范围, 进一步防止风轮 124的叶片干涉抽油 机的运行。 有利的是, 蓄电池组 116安置在配重体 11 中并通过导缆 115 连接电机, 这样不仅节约了空间, 还能起到配重的作用。 To this end, in the embodiment shown in FIG. 16, the pumping unit is provided with a wind power generation system including a wind turbine generator 123, a fan controller 125 and a battery pack 116 which are sequentially connected, and the battery Group 116 is coupled via inverter 126 to a pumping control control system for controlling the rotation of motor 27, as shown in FIG. As can be seen from the figure, the wind turbine 123 is arranged on the platform 8 at the top of the main frame, and the blade diameter of the wind wheel 124 of the wind turbine 123 depends not only on the desired output power, but also on the wind wheel 124. The operation will not interfere with the normal operation of the pumping unit. In addition, a fan horizontal rotation limiting mechanism 118 is further provided for controlling the rotation range of the wind power generator 123 to further prevent the blades of the wind wheel 124 from interfering with the operation of the pumping unit. Advantageously, the battery pack 116 is disposed in the weight body 11 and passes through the cable 115. Connecting the motor not only saves space, but also acts as a counterweight.
另外, 除了风力发电系统之外, 抽油机还可配设有光能发电系统, 该 光能发电系统包括连接到所述蓄电池组 116的光伏组件 117, 该光伏组件 117和该蓄电池组 116之间设有光伏控制器 29。  In addition, in addition to the wind power generation system, the pumping unit may be provided with a photovoltaic power generation system including a photovoltaic module 117 connected to the battery pack 116, the photovoltaic module 117 and the battery pack 116. A photovoltaic controller 29 is provided between them.
在本发明中, 考虑到风力发电机的功率曲线与风场风力的强弱有关, 为了合理的分配风力发电功率, 采取了以下手段, 即强风条件下的多余功 率用于充电, 并且在风场风能大于光能的自然条件下, 光能发电系统获得 的能量可仅用于充电。 在这里, 蓄电池组 16起到调峰的作用。 在本发明 中, 还考虑到将区域的气象资料输入至抽油机控制管理系统中 31 , 随机处 理分配有利能量。 此外, 本发明还提供一种用于上述抽油机的控制系统, 该系统结构主要具有抽油驱动装置,其用来驱动抽油杆上行、下行的动作; 抽油机控制装置, 其用来控制所述抽油驱动装置。 该系统例如可以是如上 文所述的抽油机控制管理系统, 或其它合适的控制系统。  In the present invention, considering that the power curve of the wind power generator is related to the strength of the wind farm wind power, in order to reasonably distribute the wind power generation power, the following means are adopted, that is, excess power under strong wind conditions is used for charging, and in the wind farm Under the natural conditions that wind energy is greater than light energy, the energy obtained by the photovoltaic power generation system can be used only for charging. Here, the battery pack 16 functions as a peak shifting. In the present invention, it is also considered to input the meteorological data of the area into the pumping unit control management system 31, and randomly distribute the favorable energy. In addition, the present invention also provides a control system for the above pumping unit, the system structure mainly has an oil pumping driving device for driving the upward and downward movements of the sucker rod; the pumping unit control device is used for The pumping drive is controlled. The system may for example be a pumping unit control management system as described above, or other suitable control system.
下面结合图 10a-12 描述根据本发明的控制抽油机的一种控制方法及 其效果。 其中, 抽油机控制系统的综合数控目的是针对抽油机在生产中实 际的工况, 即冲次、 冲程、 换向三大要素实现精细、 精确的实时控制, 可 获取综合效率的最佳效果。  A control method for controlling the pumping unit and its effects according to the present invention will now be described with reference to Figs. 10a-12. Among them, the comprehensive numerical control of the pumping unit control system aims to achieve fine and accurate real-time control of the actual working conditions of the pumping unit in the production, namely, the punching, stroke and reversing, and the best comprehensive efficiency can be obtained. effect.
图 12为对抽油杆的冲程行程 D的上下运行速度 VI、 V2的控制曲线, 其中 CI , C3为加速段; El , E2为匀速段; C2, C4为减速段; Z为积分 时间(还可以参见图 l ib ); D为冲程及 T/m代表一个冲次。 首先确认设定 最终冲程值 9(冲程值可小数点位细分), 再设定上行速度 VI 和下行速度 V2的速度值; 下行速度 V2慢于上行速度 VI , 以加长油泵内液量聚集的 填充时间, 提高产液量, 此种上、 下行分速度运行功能是传统式抽油机无 法实现的。 VI、 V2 的速度可调实际是对电机正、 反转速分别设定输出频 率与 S字特性控制。 关于控制系统对冲次的控制, 电机 27正、 反转为抽 油杆上行、下行的一次运行周期 (T/m),每分钟单位时间内运行周期的次数 多少即冲次。 可通过对电机 27每分钟换向的正、 反转不同转速控制多少 回实现。 主要是针对电机 27每分钟转换的正转、 反转的转速控制。 正、 反转不同转速决定了控制冲次和抽油杆 1上行和下行的速度,  Figure 12 is the control curve of the up and down running speeds VI and V2 of the stroke D of the sucker rod, where CI and C3 are the acceleration sections; El and E2 are the constant speed sections; C2 and C4 are the deceleration sections; Z is the integration time (also See Figure l ib ); D for stroke and T/m for one stroke. First confirm that the final stroke value is set to 9 (the stroke value can be subdivided), and then the speed value of the up speed VI and the down speed V2 is set; the down speed V2 is slower than the up speed VI to increase the filling of the liquid volume in the oil pump. Time, increase the liquid production, this up and down speed operation function is not realized by the traditional pumping unit. The speed adjustment of VI and V2 is actually to control the output frequency and S-characteristic control of the positive and negative speeds of the motor. Regarding the control of the control system's hedging times, the motor 27 is positively and reversing to the upper and lower running cycle (T/m) of the sucker rod, and the number of times of the operating cycle per minute per minute is called the number of times. It can be realized by controlling the number of positive and negative reversal of the motor 27 every minute. It is mainly for the forward and reverse speed control of the motor 27 every minute. The positive and reverse rotation speeds determine the speed of the control stroke and the sucker rod 1 up and down,
此外, 控制系统提供了换向柔性的控制。 电机 27在正、 反向的交替 换向瞬间, 要求控制器控制电机 27有 0.1s的积分时间 Z以为电机的换向 提供电阻尼, 使多极减速器 106(第一传动比)内多组齿轮及复绕轮内嵌齿 圈(第二传动比)在正、 反的齿间柔性啮合, 以防齿轮正、 反交替换向长期 连续运行在硬连接过程中, 因过冲力造成打齿现象, 控制装置对电机 27 的换向柔性控制功能。 另外, 加之机械平面涡卷弹簧装置在换向时起到作 用与反作用力和储能特性、 平滑緩冲特征均收到实用效果。 In addition, the control system provides control of commutation flexibility. The motor 27 is required to control the motor 27 to have an integration time Z of 0.1 s in the forward and reverse directions of the replacement, so as to provide resistance to the commutation of the motor, so that the multi-pole reducer 106 (first transmission ratio) has multiple groups. Gear and rewind wheel inner cog The ring (the second transmission ratio) is flexibly meshed between the positive and negative teeth to prevent the gear from being positively and reversely replaced in the long-term continuous operation during the hard connection process, the toothing phenomenon is caused by the overshoot, and the control device changes the motor 27 To the flexible control function. In addition, the mechanical planar scroll spring device has a practical effect in the reversing action, reaction force and energy storage characteristics, and smooth cushioning characteristics.
图 10a示出了感应电机在不受控制的情况下, 电机输出轴正、 反切换 运动的压力 P与时间 T的关系曲线,其中显示了电机换向区域^^的转动惯量 变化; 图 10b是在复绕轮不被控制的情况下, 复绕轮的正、 反向切换运动 的压力与时间的关系曲线, 其中显示了复绕轮换向区域 M2的转动惯量变 化; 图 10c是在电机和复绕轮不被控制的情况下, 变速机构输出齿轮轴与 复绕轮的筒体的内齿啮合正、 反向切换运行的压力与时间的关系曲线, 其 中显示在换向区域 M3中的转动惯量和冲量的刚性叠加; 图 11a是复绕轮筒 体内部的一对平面涡卷弹簧的物理特性曲线, 其中正反作用力同时产生, 如图所显示当一平面涡卷弹簧处于储能状态 时, 另一平面涡卷弹簧处于 释能状态 Qo, 反之则反, 这也可称作机械阻尼。 图 l ib是感应电机、 永磁 同步电机被控后输出轴正 /反切换时的转速和时间的关系,其中示出了在换 向之间的积分时间 Z, 这可以被视为电阻尼。 通过本发明的控制系统对本 发明抽油机的电阻尼控制, 最后能够使本发明的轮筒式抽油机获得图 11c 所示的根据本发明的滚筒式抽油机工况曲线 P 这相比于现有的游梁式抽 油机工况曲线 P2显著地改善了换向时的性能, 例如避免了图 11c中阴影所 显示的过冲区域8。 Figure 10a shows the relationship between the pressure P of the positive and negative switching movements of the motor output shaft and the time T under the condition that the induction motor is uncontrolled, and shows the change of the moment of inertia of the motor commutation area ^ Fig. 10b In the case where the rewinding wheel is not controlled, the relationship between the pressure of the forward and reverse switching movements of the rewinding wheel and time, which shows the change of the moment of inertia of the rewinding zone M 2 ; Fig. 10c is in the motor and When the rewinding wheel is not controlled, the output gear shaft of the shifting mechanism and the internal teeth of the cylinder of the rewinding wheel mesh with the pressure of the forward and reverse switching operation, which is displayed in the reversing area M 3 The rigid superposition of the moment of inertia and the impulse; Figure 11a is the physical characteristic curve of a pair of planar scroll springs inside the rewinding drum body, in which the positive and negative forces are simultaneously generated, as shown in the figure when a plane scroll spring is in the energy storage In the state, the other planar scroll spring is in the energy release state Qo, and vice versa, which may also be referred to as mechanical damping. Figure l ib is the relationship between the speed and time when the induction motor and the permanent magnet synchronous motor are controlled to output the positive/negative switching of the output shaft. The integral time Z between the commutations is shown, which can be regarded as the resistance. By controlling the resistance of the pumping unit of the present invention by the control system of the present invention, finally, the wheeled pumping unit of the present invention can obtain the drum type pumping unit operating condition curve P according to the present invention as shown in Fig. 11c. The existing beam pumping condition curve P 2 significantly improves the performance at the time of commutation, for example avoiding the overshoot region 8 shown by the shading in Fig. 11c.
综合以上描述说明本发明的抽油机在生产过程的一些有益效果:  The above description explains some of the beneficial effects of the pumping unit of the present invention in the production process:
1、 节电率高: 本发明的抽油机结构将原有传统的游梁式抽油机的圓 周运动变直线做功使机械传动效率大大提高, 节电率在 50— 70%之间, 这 例如是通过提供轴向尺寸较小的复绕轮、 改善的变速机构以及充分利用清 洁能源实现的。  1. High power saving rate: The structure of the pumping unit of the invention transforms the circular motion of the original conventional beam pumping unit into a straight line, so that the mechanical transmission efficiency is greatly improved, and the power saving rate is between 50 and 70%. This is achieved, for example, by providing a rewind wheel with a small axial dimension, an improved shifting mechanism, and full use of clean energy.
2、 通过共用螺旋槽的思想,使得复绕轮的轴向尺寸显著降低, 因此在 减少能耗的同时, 能够提供良好的转矩平衡, 而也能很好地适用于现有的 较窄的配重。  2, through the idea of sharing the spiral groove, the axial size of the rewinding wheel is significantly reduced, so that while reducing energy consumption, it can provide a good torque balance, and can also be well applied to the existing narrower Counterweight.
3、 高精度调节配重, 省时、 省力, 最终实效基本消除了电动机因外 作用自身产生电动势再生发电的耗损, 并因而可以设置电能回馈装置以将 例如换向时摩擦所产生的力再回馈到电网。  3. Adjusting the weight with high precision, saving time and effort, the final effect basically eliminates the loss of the motor generated by the external action itself, and thus the power feedback device can be set to re-feed the force generated by, for example, friction during commutation. To the grid.
4、 方便调整配重、 冲次、 冲程, 实行抽油生产的优化管理, 收到对 优化采油需要自动间歇抽油的效果。 间歇抽油的间隔时间可任意设定, 由 控制管理系统自动完成。 这样可以大量减少做多种无用功的耗费, 减少泵 体磨损次数, 增加原有泵体的使用寿命, 同时达到节电效果。 4. It is convenient to adjust the weight, stroke and stroke, and implement the optimal management of pumping production. Optimized oil recovery requires the effect of automatic intermittent pumping. The interval between intermittent pumping can be arbitrarily set and automatically completed by the control management system. This can greatly reduce the cost of doing a variety of useless work, reduce the number of pump wear, increase the life of the original pump body, and achieve power saving.
5、 可任意调节油杆的上、 下行的速度, 调上行速度快, 下行速度慢 的结果是, 上行加快出液量的速度, 下行慢使油泵腔体内充油液的时间加 长。 再次提高泵效。  5. The upper and lower speeds of the oil rod can be adjusted arbitrarily, and the upward speed is fast. The slow down speed is that the speed of the liquid output is increased upward, and the slow down time makes the oil filling time of the oil pump chamber longer. Improve pump efficiency again.
6、 本发明的系统例如能够采用工业级 GSM中文(英文)短信单元, 监控时间形式, 即报、 巡报、 查报监控暂停内容、 冲程、 冲次、 温升、 电 流、 电压、 电度表度数、 示功图、 P值、 S值等。  6. The system of the present invention can, for example, adopt an industrial-grade GSM Chinese (English) short message unit, and monitor the time form, that is, report, patrol, check and report monitoring pause content, stroke, stroke, temperature rise, current, voltage, watt-hour meter Degrees, dynamometers, P values, S values, etc.
7、 本发明的控制系统例如还提供了电机与复绕轮的多种连接方式。 7. The control system of the present invention, for example, also provides various ways of connecting the motor to the rewind wheel.
8、 根据本发明的复绕轮的缠绕方式结合本发明的抽油机其余部件能 够很好地控制根据本发明的抽油机工作过程中的动平衡。 虽然上文中已经 在一定程度上详细地对本发明的多个实施例进行了描述, 应当理解, 以上 描述是示范性而非限制性的。 在不背离本发明的精神或范围的情况下, 本 技术领域内的普通技术人员可以对这些公开的实施例做出多种改变。 8. The winding method of the rewinding wheel according to the present invention, in combination with the remaining components of the pumping unit of the present invention, can well control the dynamic balance during operation of the pumping unit according to the present invention. While the invention has been described in detail with reference to the preferred embodiments embodiments Various changes to these disclosed embodiments can be made by those skilled in the art without departing from the spirit and scope of the invention.

Claims

权 利 要 求 Rights request
1. 一种抽油机, 其包括主框架 (9) , 抽油杆(1) , 配重体(11) , 设在该 主框架顶部的平台(8) , 布置在该平台(8)上的电机 (27)、 导向轮 (4)和复绕轮 (5), 该电机构造成驱动该复绕轮以使其绕其轴线转动, 该复绕轮具有沿该 轴线分布的左半部分和右半部分, 其特征是, 所述复绕轮 (5)的轮周上设有 2n个第一孔 (5a),其分为分别位于左半部分和右半部份上的各 n个第一孔, 从每个所述第一孔 (5a)各引出一根配重体牵引绳(10)与该配重体(11)上的 紧固器(16)相连接构成配重运行牵引系统; 所述复绕轮 (5)的轮周上还设有 2n个第二孔 (5b),其分为分别位于左半部分和右半部份上的各 n个第二孔, 从每个所述第二孔 (5b)各引出一根抽油杆悬绳 (2)经过该导向轮 (4)并通过 牵引器 (3)与该抽油杆(1)相连接构成抽油杆运行牵引系统; 所述复绕轮 (5) 还沿其轮周表面开设有 2m圈螺旋槽, n为自然数且111 > 1 , 其中 m圈螺旋 槽位于该左半部分, 另外 m圈螺旋槽位于该右半部分,位于左半部分和位 于右半部分的螺旋槽的旋向相反,所述第一孔 (5a)和所述第二孔 (5b)如此地 在螺旋槽内间隔布置, 使得至少一部分螺旋槽在运行过程中供所述抽油杆 悬绳 (2)和所述配重体牵引绳(10)共用, 所述抽油杆悬绳 (2)和所述配重体牵 槽。 ' 、 ^ '、  A pumping unit comprising a main frame (9), a sucker rod (1), a weight body (11), a platform (8) disposed at the top of the main frame, disposed on the platform (8) a motor (27), a guide wheel (4) and a rewinding wheel (5), the electric mechanism causing the rewinding wheel to be rotated about its axis, the rewinding wheel having a left half and a right distribution along the axis a half portion, wherein the winding wheel (5) is provided with 2n first holes (5a) on the circumference of the winding wheel (5), which are divided into n firsts respectively located on the left half and the right half a hole, from each of the first holes (5a), a weight body traction rope (10) is connected with a fastener (16) on the weight body (11) to form a counterweight running traction system; There are also 2n second holes (5b) on the circumference of the rewinding wheel (5), which are divided into n second holes respectively located on the left half and the right half, from each of the above Two holes (5b) each lead a sucker rod suspension rope (2) through the guide wheel (4) and connected to the sucker rod (1) through a tractor (3) to form a sucker rod running traction system; The rewinding wheel (5) is also provided along the circumferential surface of the wheel 2m circle spiral groove, n is a natural number and 111 > 1 , wherein the m-circle spiral groove is located in the left half, and the m-ring spiral groove is located in the right half, and the spiral groove of the left half and the right half is rotated. Conversely, the first hole (5a) and the second hole (5b) are spaced apart in the spiral groove such that at least a portion of the spiral groove is supplied to the sucker rod suspension rope (2) and the machine during operation. The heavy-duty traction rope (10) is shared, and the sucker rod suspension rope (2) and the weight body are grooved. ' , ^ ',
2. 根据权利要求 1所述的抽油机, 其特征是, 所述 2n个第一孔沿平 行于该纵轴线的直线间隔排列和 /或所述 2n个第二孔沿平行于该纵轴线的 直线间隔排列。 2. The pumping unit according to claim 1, wherein the 2n first holes are arranged at a line spacing parallel to the longitudinal axis and/or the 2n second holes are parallel to the longitudinal axis The lines are arranged at intervals.
3. 根据权利要求 2所述的抽油机, 其特征是, 所述第一孔 (5a)和所述 第二孔 (5b)沿该复绕轮的周向以夹角 110。-145。错开布置。  The pumping unit according to claim 2, wherein the first hole (5a) and the second hole (5b) are at an angle 110 along a circumferential direction of the winding wheel. -145. Staggered arrangement.
4. 根据权利要求 1 所述的抽油机, 其特征是, 所述抽油杆悬绳 (2)和 配重体牵引绳(10)在所述螺旋槽中的缠绕圈数取决于抽油机的冲程和复绕 轮的直径, 并且所述抽油杆悬绳 (2)和配重体牵引绳(10)在所述螺旋槽中的 最大缠绕长度大于抽油机的冲程。  4. The pumping unit according to claim 1, wherein the number of windings of the sucker rod suspension rope (2) and the weight body traction rope (10) in the spiral groove depends on the pumping unit The stroke and the diameter of the rewinding wheel, and the maximum winding length of the sucker rod suspension rope (2) and the weight body traction rope (10) in the spiral groove is greater than the stroke of the pumping unit.
5. 根据权利要求 4所述的抽油机,其特征是,在抽油机冲程的上止点, 至少一部分配重体牵引绳仍缠绕在所述螺旋槽上; 在抽油机冲程的下止 点, 至少一部分抽油杆悬绳仍缠绕在所述螺旋槽上。  5. The pumping unit according to claim 4, wherein at the top dead center of the pumping stroke, at least a portion of the weight body traction rope is still wound around the spiral groove; at the end of the pumping stroke At least a portion of the sucker rod suspension rope is still wrapped around the spiral groove.
6. 根据权利要求 1 所述的抽油机, 其特征是, 所述抽油杆悬绳 (2)和 配重体牵引绳(10)的长度设计成当抽油杆悬绳绕满在一个所述第一孔和相 应的一个第二孔之间延伸的所述螺旋槽时, 所述配重体牵引绳全离开所述 螺旋槽。 6. The pumping unit according to claim 1, wherein the sucker rod suspension rope (2) and The length of the weighted traction rope (10) is designed such that when the sucker rod suspension rope is wound around the spiral groove extending between one of the first holes and the corresponding one of the second holes, the weight body traction rope is full Leave the spiral groove.
7. 根据权利要求 1所述的抽油机, 其特征是, n=2, m=8。  7. The pumping unit according to claim 1, wherein n = 2 and m = 8.
8. 根据权利要求 1所述的抽油机, 其特征是, 由该 2n个第一孔引出 的配重体牵引绳 (10)由一根母绳如此构成, 该母绳以其一端固定在最靠近 复绕轮一个纵向端的第一孔中, 且其另一端朝复绕轮的另一纵向端方向逐 个地从相邻的第一孔交替地穿入该复绕轮内部或穿出复绕轮外且最终穿 入并固定到最靠近该另一纵向端的第一孔中, 从而形成相连的 2n根配重 体牵引绳(10)。  8. The oil pumping unit according to claim 1, wherein the weight body traction rope (10) led out by the 2n first holes is constituted by a mother rope, the mother rope being fixed at one end thereof at the most Adjacent to the first hole of one longitudinal end of the rewinding wheel, and the other end thereof alternately penetrates the inside of the rewinding wheel or the rewinding wheel from the adjacent first hole one by one toward the other longitudinal end of the rewinding wheel. The outer hole is finally penetrated and fixed into the first hole closest to the other longitudinal end to form a connected 2n weight body traction rope (10).
9. 根据权利要求 1所述的抽油机, 其特征是, 由该 2n个第二孔引出 的抽油杆悬绳 (2)由一根母绳如此构成,该母绳以其一端固定在最靠近复绕 轮一个纵向端的第二孔中, 且其另一端朝复绕轮的另一纵向端方向逐个地 从相邻的第二孔交替地穿入该复绕轮内部或穿出复绕轮外且最终穿入并 固定到最靠近该另一纵向端的第二孔中, 从而形成相连的 2n根抽油杆悬 绳 (2)。  9. The pumping unit according to claim 1, wherein the sucker rod suspension rope (2) led out by the 2n second holes is constituted by a mother rope which is fixed at one end thereof The second hole closest to one longitudinal end of the rewinding wheel, and the other end of which alternately penetrates the inside of the rewinding wheel or the rewinding from the adjacent second hole one by one toward the other longitudinal end of the rewinding wheel The wheel is externally and finally penetrated and secured into the second hole closest to the other longitudinal end to form a continuous 2n sucker rod suspension (2).
10. 根据权利要求 1至 9中任一项所述的抽油机, 其特征是, 在该复 绕轮 (5)筒体内部装有两组卷绕方向相反的平面涡卷弹簧(13) , 这两组平面 涡卷弹簧 (13)在抽油机的冲程处于最高点或最低点时, 其中仅一组平面涡 卷弹簧处于储能状态, 所述弹簧的可伸展长度大于抽油杆的冲程。  The pumping unit according to any one of claims 1 to 9, characterized in that two sets of planar scroll springs (13) having opposite winding directions are arranged inside the cylinder of the rewinding wheel (5). The two sets of planar scroll springs (13) are at a highest or lowest point when the stroke of the pumping unit is at a highest point or a lowest point, wherein only one set of planar scroll springs is in an energy storage state, and the extendable length of the spring is greater than that of the sucker rod stroke.
11. 根据权利要求 1至 9中任一项所述的抽油机, 其特征是, 还包括 导向轮支架 (20) ,该导向轮支架 (20)—端可枢转地安装在该平台上, 另一端 悬臂伸出该平台(8)外并装有该导向轮,通过所述复绕轮 (5)的转动来驱动该 导向轮支架 (20)和该导向轮 (4)在与该平台(8)所在平面垂直的平面内相对 该平台(8)向上枢转。  The pumping unit according to any one of claims 1 to 9, further comprising a guide wheel bracket (20), the guide wheel bracket (20) being pivotally mounted on the platform The other end cantilever extends out of the platform (8) and is mounted with the guide wheel, and the guide wheel bracket (20) and the guide wheel (4) are driven by the rotation of the rewinding wheel (5) (8) The plane in which the plane lies is pivoted upward relative to the platform (8).
12. 根据权利要求 11所述的抽油机, 其特征是, 还包括布置在该平台 (8)上的导向轮调整定位凸部 (22) , 其位于导向轮支架之下且构造成能与设 置在导向轮支架下侧的凹部相配合来定位该导向轮 (4)并调整该导向轮 (4) 相对该平台(8)的仰角, 该仰角为 6度〜 12度。  12. The pumping unit according to claim 11, further comprising a guide wheel adjusting positioning protrusion (22) disposed on the platform (8), located under the guide wheel bracket and configured to be The recess provided on the underside of the guide wheel bracket cooperates to position the guide wheel (4) and adjust the elevation angle of the guide wheel (4) relative to the platform (8), the elevation angle being 6 degrees to 12 degrees.
13. 根据权利要求 1至 9中任一项所述的抽油机, 其特征是, 所述电 机 (27)直接地或者通过减速器(106)连接并驱动该复绕轮 (5)。  The pumping unit according to any one of claims 1 to 9, characterized in that the motor (27) is connected to and drives the rewinding wheel (5) directly or through a speed reducer (106).
14. 根据权利要求 1至 9中任一项所述的抽油机, 其特征是, 所述电 机 (27)通过变速机构 (6)连接并驱动该复绕轮 (5),所述复绕轮 (5)在其一端设 有内齿圈(7)且可转动地安装在沿其纵轴线布置的复绕轮轴 (19)上, 该变速 机构 (6)包括与所述电机的输出端连接的太阳轮 (6a) , 固定安装在该复绕轮 轴(19)上的行星架(6c)和可转动地安装在行星架上的至少两个行星齿轮 (6b), 所述行星齿轮与该内齿圈(7)和太阳轮 (6a)啮合。 The pumping unit according to any one of claims 1 to 9, wherein the electric pump The machine (27) connects and drives the rewinding wheel (5) through a shifting mechanism (6), the rewinding wheel (5) is provided at one end thereof with an internal ring gear (7) and rotatably mounted along its longitudinal axis On the rewinding axle (19), the shifting mechanism (6) includes a sun gear (6a) coupled to the output of the motor, a planet carrier (6c) fixedly mounted on the rewinding axle (19), and At least two planet gears (6b) rotatably mounted on the planet carrier, the planet gears meshing with the ring gear (7) and the sun gear (6a).
15. 根据权利要求 1至 9中任一项所述的抽油机, 其特征是, 该电机 (27)为永磁同步曳引机。  The pumping unit according to any one of claims 1 to 9, characterized in that the motor (27) is a permanent magnet synchronous traction machine.
16. 根据权利要求 1至 9中任一项所述的抽油机, 其特征是, 该抽油 机配设有风力发电系统, 该风力发电系统包括顺次连接的风力发电机 (123)、风机控制器(125)和蓄电池组(116),而该蓄电池组(116)经逆变器(126) 连接到构造成能管理和驱动所述电机的抽油机控制管理及驱动系统 (31)。  The oil pumping unit according to any one of claims 1 to 9, wherein the oil pumping unit is provided with a wind power generation system, the wind power generation system comprising a wind power generator (123) connected in series, a fan controller (125) and a battery pack (116), and the battery pack (116) is coupled via an inverter (126) to a pumping unit control management and drive system configured to manage and drive the motor (31) .
17. 根据权利要求 16 所述的抽油机, 其特征是, 该风力发电机 (23) 布置在该主框架顶部的平台(8)上, 该蓄电池组(16)安置在该配重体(11)中。  17. The oil pumping unit according to claim 16, wherein the wind power generator (23) is arranged on a platform (8) at the top of the main frame, and the battery pack (16) is disposed on the weight body (11) )in.
18. 根据权利要求 1至 9中任一项所述的抽油机, 其特征是, 该抽油 机配设有光能发电系统, 该光能发电系统包括顺次连接的光伏组件(117)、 光伏控制器(129)和蓄电池组(116) , 而该蓄电池组(116)经逆变器(126)连接 到构造成能管理和驱动所述电机的抽油机控制管理及驱动系统 (31)。  The oil pumping unit according to any one of claims 1 to 9, wherein the oil pumping unit is provided with a photovoltaic power generation system, and the photovoltaic power generation system comprises a photovoltaic module (117) connected in series. a photovoltaic controller (129) and a battery pack (116), and the battery pack (116) is coupled via an inverter (126) to a pumping unit control management and drive system configured to manage and drive the motor (31) ).
PCT/CN2011/002061 2011-01-21 2011-12-09 Oil-pumping machine WO2012097493A1 (en)

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