WO2016015535A1 - Pendulum type pumping unit with t-shaped walking beam - Google Patents

Abstract

A pendulum type pumping unit with a T-shaped walking beam. The pumping unit comprises a rack (1), a T-shaped walking beam, a horse head, a reduction gearbox (3), a crank (2) and a motor (9). The T-shaped walking beam is mounted on the rack (1) through a main shaft. The central line of an oscillating bar (5) is perpendicular to a main beam (7) to form the T-shaped walking beam in rigid connection, and the transmission angle of the oscillating bar (5) and the main beam (7) during movement is equal to 90° all the time. An output shaft of the reduction gearbox (3) is positioned below the main shaft. The crank (2) is mounted on the output shaft of the reduction gearbox (3) and is provided with a striking gear (13). The striking gear (13) is matched with the oscillating bar (5) to change the rotation movement of the crank (2) into arc movement of the oscillating bar (5) so as to drive the up-down swing of the main beam (7). The pendulum type pumping unit with the T-shaped walking beam has stable counterweight balance moment, the peak torque of the pumping unit can be obviously reduced, the negative torque is eliminated, the stability is enhanced, and the energy saving effect is improved.

Description

Pendulum pumping unit with T-shaped beam Technical field

The invention relates to the field of oil recovery machinery, and in particular to a beam pumping unit.

Background technique

The beam pumping unit is a ground power equipment for underground pumping pumps and is a main mechanical oil recovery equipment. The common pumping unit structure is generally that the frame is located in the middle of the beam. When the pumping unit is working, the load on both ends of the beam is relatively balanced, so that the rack runs smoothly; the crank adopts a conventional strip crank and is connected with a balance block. The crank linkage and the boring head are respectively located on both sides of the frame, and the crank and the beam are connected by a rigid connection or a soft connection to transmit power and torque.

As shown in Figure 1, the soft connection between the crank and the beam can be transmitted through the soft connection of the wire rope. For example, a double-head energy-saving pumping unit disclosed in Chinese invention patent CN202707004 includes a base 1', a frame 2', a beam 3', a rear head 4', a front head 5', a crank 6', The balance block 7', the reduction gear box 8', the wire rope 9' and the motor 10', the two ends of the beam are respectively connected with the front head and the rear head, and the rear head is connected to the crank 6' by the wire rope 9', and the crank is connected with the weight. The balance block 7' and the reduction box 8' are connected to the suspension rod 11'.

As shown in FIG. 2, the conventional conventional beam pumping unit includes a motor 1", a brake device 2", a reduction gear box 3", a crank 4", a weight 5", a connecting rod 6", a beam shaft 7", and a balance. The block 8", the frame shaft 9", the beam 10', the hoe 11", the suspension 12" and the frame 13", the connecting rod 6" is rigidly connected, and the crank 4" is provided with a balancing block 8". The power is transmitted through the four-bar linkage structure, wherein the crankshaft center is located substantially below the tail bearing of the beam, so that when the hammer is at the top dead center (the hammer is raised to the highest point) and the bottom dead point (the hammer is lowered) At the lowest point), the angle between the centerlines of the connecting rods is basically zero. This angle is called the extreme angle of the pumping unit; the center of gravity of the balancing block coincides with the center line of the crankshaft, that is, the clamp formed between the two lines. The angle is zero and this angle is called the equilibrium phase angle of the pumping unit.

The shortcoming of the above pumping unit is that since the balance block is mounted on the crank, the balance block will generate a certain centrifugal force when rotating, and the angle of the crankshaft is rotated when the pumping unit is operated, because the angle of the pole position is approximately zero. Equally, the pumping unit has a higher peak torque throughout the working cycle and there is also a negative torque problem.

Summary of the invention

In order to reduce the peak torque of the pumping unit and eliminate the negative torque and improve the energy saving effect, the present invention provides a novel beam pumping unit.

The technical solution of the present invention is as follows:

A pendulum pumping unit having a T-shaped beam, the pumping unit comprising a frame, a T-shaped beam, a boring head, a reduction gear box, a crank and a motor, wherein the T-shaped beam is mounted on the machine through a spindle a T-shaped beam perpendicular to the main beam to form a rigid connection, the transmission angle of the two is always equal to 90° during the movement; the two ends of the main beam are connected to the taro, An output shaft of the reduction gear box is located below the main shaft; the crank is mounted on an output shaft of the reduction gear box, the crank is provided with a toggle device, and the toggle device cooperates with the swing rod to rotate the crank The rotary motion becomes an arcuate motion of the swing lever to drive the up and down swing of the main beam.

Further, the dialing device performs a reciprocating motion in a predetermined stroke in the longitudinal rail groove of the swing lever, and the transmission torque transmitted to the beam when the swing lever is swung is variable.

Further, the rail groove is a double-sided track to provide a moving track and load support of the toggle device at different rotation angles.

Further, a center line of the swing rod is located at a center position of the beam, and the head is symmetrically disposed at both ends of the main beam; a connection between the crank and an output shaft of the reduction box is substantially located at the main shaft Directly below.

Further, the main beam is fixedly connected to the swing arm, and the swing rod is fixed on the swing arm.

Further, the swing arm is V-shaped or ladder-shaped.

Further, when the hoe is raised to the highest point or is lowered to the lowest point, an angle α is formed with a horizontal line of the horizontal position of the main beam, and the pendulum swings to a maximum amplitude and a vertical line with the horizontal position of the main beam An angle β is formed, the α = β.

Further, the angle α or β is less than or equal to 22.5°.

Further, the pumping unit removes the balance weight on the crank described in the prior art, and the rotation of the crank is not equal in the angles of the upper stroke and the lower stroke; wherein the crank is turned on the upper stroke The angle γ1>180°, the angle γ2 <180° at the lower stroke.

Further, the pumping unit further includes an electric control system, the input shaft of the speed reducer is provided with an electromagnetic automatic brake, and the electric control system includes the electromagnetic automatic brake for braking under the condition of loss of load. Control circuit.

The invention has the following advantages:

1. The T-shaped beam of the pumping unit adopts the balance structure of the symmetrical double-head balance, and the balance torque and load torque are completely consistent with each other, so that the net torque curve of the pumping unit is ideal, and the balance effect is good, which can be significantly reduced. Pumping unit peak torque, eliminating negative torque, enhancing stability and improving energy saving.

2. The power transmission mechanism is a crank-driven toggle device that swings the swing lever. From the working process, the toggle device reciprocates in the guide groove of the swing lever due to the rotation of the crank, so that the swing lever forms a reciprocating swing, and The power is transmitted to the main beam, so that the hoe on the main beam reciprocates up and down, and the length of the oscillating rod changes when the actual work is done, forming a four-bar mechanism with variable parameters, which saves labor and reduces power consumption. effect.

3. Since the transmission angle of the pendulum and the main beam during the motion is always equal to 90°, the transmission performance is the best in the four-bar mechanism. The working principle is that the parameter of the force transmission performance is the pressure angle or the transmission angle. The smaller the pressure angle (ie, the larger the transmission angle), the higher the force transmission efficiency of the mechanism; conversely, the larger the pressure angle (ie, the smaller the transmission angle), The greater the transmission loss of the mechanism, the lower the transmission efficiency.

4. When the pumping unit is working, the angles of the cranks of the up and down strokes are not equal; the angle of the upper stroke is greater than >180°, and the angle of the lower stroke is <180°, so that the acceleration and dynamic load of the stroke on the suspension point are reduced. Small, the peak torque of the reducer is reduced, and the torque variation is more uniform. The up and down stroke time can be adjusted in real time according to the working conditions of the oil well, which obviously improves the energy saving effect.

5. The balancing block on the crank in the prior art is removed, and the centrifugal force of the rotating balance block can be eliminated, so that the stability of the pumping unit is better.

6. Because the balance of the two ends makes the main load only act on the main shaft of the beam, the friction power loss is low, and the mechanical efficiency of the whole machine is high.

7. Since the electromagnetic automatic brake is installed at the input shaft end of the reducer, in addition to the conventional brake function, it also has the safety control of the automatic brake during the operation of the pumping unit during accidental breakage and off (ie, loss of load). Features.

DRAWINGS

1 and 2 show the structure of a conventional oil pumping unit;

3-5 are schematic structural views of an embodiment of the present invention, respectively showing a state in which the main beam is in a horizontal position, a state in which the main beam is located at an upper hanging point (top dead center), and a lower hanging point (bottom dead center) Shape state.

Figure 6 is a schematic view showing a state of change of the pumping unit of the present invention during operation;

Figure 7 is a graph showing the speed comparison between the pumping unit of the present invention and the prior art pumping unit;

Figure 8 is a graph showing the acceleration comparison between the pumping unit of the present invention and the prior art pumping unit;

Figure 9 is a schematic view showing the comparison of the torque variation of the pumping unit of the present invention and the prior art pumping unit;

Figure 10 is a schematic view showing the comparison of the power variation of the pumping unit of the present invention and the prior art pumping unit.

detailed description

The invention will be further described in detail below with reference to the accompanying drawings, but not to limit the invention.

As shown in FIG. 3-5, the present invention provides a beam pumping unit comprising a frame 1, a crank 2, a swing arm 4, a swing link 5, a main beam 7, a boring head and a driving device. Wherein, the swing arm 4, the swing rod 5 and the main beam 7 constitute a T-shaped beam, wherein, from the positional relationship, the center line of the swing rod 5 is perpendicular to the main beam 7 and is disposed in a T-shaped structure. In the embodiment, specific The connecting structure is: the swinging rod 5 is fixed to the swing arm 4, and the swing arm is fixed to the main beam 7, which are all rigid connections, such as bolting, welding and the like. As a variant, the pendulum can also be fixedly connected directly to the main beam, and the joint is then provided with the necessary reinforcement support.

The main beam 7 adopts a symmetrical double-head balance balance structure, including a front boring head 6 and a counterweight boring head 11, and a counterweight 8 is connected to the counterweight boring head 11. Preferably, the weight 8 is easily adjusted by the wire rope suspension method, so that the load on the ends of the main beam is applied to the frame 1 by the combined force of a plumb, so that the horizontal component of the frame 1 is higher than that of the conventional beam. The machine is much smaller, so that the amount of shaking of the rack 1 is correspondingly smaller.

The load received at both ends of the main beam 7 is symmetrically balanced. The main beam is provided with a main shaft at the center. The main shaft is preferably a bearing 12. The bearing 12 is disposed at the top end of the frame 1, and the main beam 7 is pivoted by the bearing 12. Preferably, a locking device 10 is also provided between the frame 1 and the main beam 7, so that the main beam 7 can be fixed in a horizontal position. It will be understood by those skilled in the art that when the main beam 7 is swung up and down, the T-shaped beam formed by the rigidly connected swing arm 4 and the swing link 5 is integrally swung with the bearing 12. Of course, as an option, the position of the main shaft may not be located at the center point of the main beam 7; as an alternative, the load at both ends of the main beam 7 may also be asymmetrically set.

In the present embodiment, the swing link 5 is rigidly connected under the main beam 7 by the swing arm 4 to form a T-shaped structure, and the swing arm 4 is V-shaped. Of course, other suitable shapes and structures of the swing arm, such as a trapezoid, may be selected. On There are two V-shaped swing arms 4, which are rigidly fixed on both sides of the main beam 7, respectively, and the swinging rod 5 is arranged to be mounted on the two swing arms 4, and the transmission angle of the swinging rod 5 and the main beam 7 is ensured during the movement process. It is always 90°. In the present embodiment, the swing link 5 is rigidly fixed to the swing arm 4 at a plurality of points, thereby further ensuring the firmness and stability of the swing arm 4.

The driving device comprises a motor 9 and a reduction gear box 3, the reduction gear box 3 is located substantially below the bearing 12, and the motor 9 and the reduction gear box 3 are driven by a belt.

The output shaft of the reduction box 3 is provided with a crank 2, and the other end of the crank 2 transmits power to the swing rod 5 through the dialing device 13, and preferably, the dialing device 13 can be a roller or a slider; In the pendulum type reciprocating motion, the swing lever 5 is provided with a longitudinal rail groove 14 which cooperates with the structure of the dialing device 13, and as the crank 2 rotates, the dialing device 13 reciprocates up and down in the rail groove 14. Preferably, a double-sided rail (double-sided rail) is disposed in the rail groove 14 of the swinging rod 5, so that the dialing device 13 is in contact with both sides of the rail slot 14 to accommodate the selection of the dialing device 13 at different rotation angles. One side (one side) rail of the rail groove serves as a point of application to transmit power more efficiently.

Compared with the prior art, the pumping unit directly removes the balance block that cooperates with the crank 2 to better improve the stability.

Further, in order to achieve the technical effect of eliminating the negative torque, it is preferable that the connection of the crank 2 to the output shaft of the reduction gear box 3 is substantially directly below the bearing 12 of the main beam 7. The toggle device 13 on the crank 2 is moved up and down within the guide groove 14 of the swing lever 5 within a predetermined stroke so that the transmission torque transmitted to the main beam 7 by the swing lever 5 during the swing is variable. Particularly preferably, as shown in FIG. 6, the angle at which the crank 2 is rotated by the upper stroke and the lower stroke is not equal, wherein the rotation of the crank 2 is rotated by the angle γ1>180° in the upper stroke and the angle γ2 rotated in the lower stroke. <180°. When the steamed head rises to the highest point or falls to the lowest point, it forms an angle α with the horizontal line of the horizontal position of the main beam, and when the track swings to the maximum amplitude, it forms an angle β with the vertical line of the horizontal position of the main beam, preferably, the clamp Angle α = β. In order to achieve a good energy saving effect, the angle α or β is preferably less than or equal to 22.5°, such as 22°.

The above pumping unit is controlled by an electric control system, including necessary power control, servo drive, etc., and the electric control system can be controlled by any one of the prior art control systems to ensure the pumping unit. jobs. As an option, an electromagnetic automatic brake (not shown) is mounted on the input shaft of the reduction gear box 3, and the electromagnetic brake can realize the basic braking function, and the sucker rod can be unexpected during the operation of the pumping unit. Safety control function for automatic braking when disconnected or off (ie, lost load); accordingly, the above electrical control system includes control for The control circuit of the electromagnetic automatic brake. The invention is not limited to the construction of an electromagnetic automatic brake, nor does it limit the specific implementation of the electrical control system. As an implementable solution, the electromagnetic automatic brake described in the Chinese invention patent CN202326846U and the technical solution of the electrical control system involved therein are incorporated herein by reference.

In use, the motor 9 drives the reduction gearbox 3 through the belt and transmits it to the crank 2. The toggle device 13 at the front end of the crank reciprocates in the guide rail groove 14, so that the swing lever 5 forms a left and right arc swing, and then the T-shaped beam The driving boring head 6 and the weight boring head 11 also form a reciprocating swing up and down. The vertical reciprocating motion of the hanging point is formed by the hoe 6 and the raccoon 15 to drive the rod pump to work.

The pumping unit of the present invention is tested and compared with a conventional pumping unit in part to further illustrate the superior performance of the pumping unit provided by the present invention. The general beam pumping unit involved below, the general structure and working principle is shown in Fig. 2. The shaft connection between the crank and the reduction box is basically located directly below the tail bearing of the beam, and the connecting rod is rigidly connected.

1, speed comparison

As shown in Fig. 7, the horizontal axis is the number of angular changes, the angular coordinates are 1, 3, 5, ..., 37, the vertical axis is the speed, C1 is the speed curve of the pumping unit of the present invention, and C2 is The speed curve of a conventional pumping unit.

It can be seen from the curve of the speed in the figure that the upper stroke speed is lower than that of the conventional pumping unit, so that the frictional resistance is reduced, which is advantageous for reducing the upstroke suspension point load.

2, suspension point acceleration comparison

As shown in Fig. 8, the horizontal axis is the number of angular changes, the angular coordinates are 1, 3, 5, ..., 37, the vertical axis is the acceleration, C1 is the acceleration curve of the pumping unit of the present invention, and C2 is The acceleration curve of the existing pumping unit.

It can be seen from the variation curve of the acceleration in the figure that the acceleration of the first half of the stroke of the pumping unit of the present invention is lower than that of the conventional pumping unit, and the acceleration of the second half of the upper stroke is higher than that of the conventional pumping unit, which is advantageous for reducing the dynamic load and lowering the upper load. Fluctuation of the stroke load of the stroke.

3, crank torque comparison

As shown in Fig. 9, the horizontal axis is the number of angular changes, the angular coordinates are 1, 3, 5, ..., 37, the vertical axis is the crank torque, and C1 is the crank torque curve of the pumping unit of the present invention. C2 is the crank torque curve of the existing pumping unit.

It can be seen from the variation curve of the torque in the figure that the peak torque of the present invention is much lower than that of the conventional pumping unit, and there is no negative torque in the whole working cycle, and the peak torques of the upper and lower strokes are close, and the torque fluctuations of the upper and lower strokes are all compared. The conventional pumping unit is even, the motor load changes more evenly, and the operation is smoother than that of the conventional pumping unit.

4, motor power comparison

As shown in FIG. 10, the horizontal axis is the number of angular changes, the angular coordinates are sequentially 1, 3, 5, ... 37, the vertical axis is the motor power, and C1 is the crank torque curve of the pumping unit of the present invention. C2 is the crank torque curve of a conventional pumping unit.

When the crank rotates at a constant speed, the motor power variation law is the same as the crank torque. The motor power peak of the pendulum pumping unit of the present invention is much smaller than that of the conventional pumping unit, so that a smaller power motor can be selected to reduce the loss of the motor itself. And circuit losses, improve power factor, improve the power quality of the grid.

5. The main parameters of the same type 10 pumping unit are compared:

Pumping unit of the invention Conventional beam pumping unit Maximum hanging point load kN 61 64.84 Minimum hanging point load kN 30.49 55.62 Maximum stroke speed m/s 0.68 1.01 Maximum stroke acceleration m/s ² 0.64 0.91 Upper stroke minimum acceleration m/s ² -0.25 -0.55 Upper stroke maximum torque kN.m 14.72 33.31 Upper stroke minimum torque kN.m 0 -10.89 Motor maximum power kW 9.24 20.92 Motor minimum power kW 0 -6.84

It should be noted that the above description is only a preferred embodiment of the present invention, and is not limited thereto. The scope of patent protection of the invention can also be equivalently improved by the structure of the above various components. Therefore, equivalent structural changes made by the description and the illustration of the present invention, or directly or indirectly applied to other related technical fields, are included in the scope of the present invention.

Claims (10)

A pendulum pumping unit with a T-shaped beam, characterized in that the pumping unit comprises a frame, a T-shaped beam, a boring head, a reduction gear box, a crank and a motor. The T-shaped beam is mounted on the frame by a spindle; The center line of the swinging rod is perpendicular to the main beam to form the rigidly connected T-shaped beam, and the transmission angle of the two is always equal to 90° during the movement; the two ends of the main beam are connected to the hammer, the deceleration The output shaft of the box is located below the main shaft; The crank is mounted on an output shaft of the reduction gear box, the crank is provided with a dialing device, and the toggle device cooperates with the swing rod to change the rotary motion of the crank into an arc motion of the swing rod, The upper and lower swings of the main beam are driven. A pumping unit according to claim 1, wherein said dialing means performs a reciprocating motion within a predetermined stroke in a longitudinal rail groove of said rocker, said rocker being transmitted to said swim when swinging The drive torque of the beam is variable. A pumping unit according to claim 2, wherein said rail groove is a double-sided track to provide a moving track and load support of said dialing device at different angles of rotation. The pumping unit according to claim 3, wherein a center line of the swing rod is located at a center position of the beam, and the head is symmetrically disposed at both ends of the main beam; the crank and the reduction box The connection of the output shaft is located substantially directly below the main shaft. A pumping unit according to claim 4, wherein said main beam is fixedly coupled to the swing arm, and said swing link is fixed to said swing arm. A pumping unit according to claim 5, wherein said swing arm is V-shaped or ladder-shaped. A pumping unit according to claim 6, wherein said ram swings to a maximum when said hoe is raised to a highest point or lowered to a minimum point at an angle α with a horizontal line of said main beam horizontal position. The amplitude forms an angle β with the vertical line of the horizontal position of the main beam, and the α=β. A pumping unit according to claim 7, wherein said angle α or β is less than or equal to 22.5°. A pumping unit according to any one of claims 1 to 8, wherein the balance weight on the crank of the prior art is removed, and the rotation of the crank is not rotated at the upper and lower strokes. Equivalent; wherein the crank is rotated by an angle γ1>180° on the upper stroke and γ2<180° on the lower stroke. A pumping unit according to claim 9, wherein said pumping unit further comprises an electric control system, said input shaft of said speed reducer being provided with an electromagnetic automatic brake, said electric control system comprising said The electromagnetic automatic brake realizes the braking control circuit under the condition of no load.

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