movement. The middle of the lever is hinged with the roller, one end is hinged with the column base, and the other end is consolidated with the pressurizing mechanism. In this way the plunger also reciprocates inside the pump cylinder. In order to simulate the actual working conditions of the pump barrel and the plunger under the oil well, high-pressure crude oil was injected into the pump barrel and a certain temperature of the crude oil was maintained with circulating hot water. The pressurizing mechanism generates a radial pressure between the pump cylinder and the plunger through the lever. The force sensor can axially fix the pump cylinder and output the friction signal between the pump cylinder and the plunger.

When quantifying the crude oil leaking into the tank, the relationship between the crude oil leakage and the clearance between the pump barrel and the plunger can be observed; when the leakage crude oil is subjected to ferroelectric analysis, it can be between the pump barrel and the plunger. The law of wear is studied. In addition, power consumption, efficiency, and temperature rise analysis can be performed on the pump.

1. Host Structure and Operation The host structure is as shown.

Pump barrel inner diameter 32110mm (there are 8 specifications in the middle) The plunger type has 2 kinds of steel plungers and soft plungers; the inner diameter of the tubing (used as a centralizer test).

Pressure 8MPa temperature 90°C. Plunger reciprocating stroke 300mm, frequency 3Hz The force per unit length in the axial direction between the pump cylinder and the plunger is 10Nmm. 2. The composition and working principle of the pressurizing mechanism In the pumping process, Due to the inclination of the installation of the pump, the deflection of the pulling direction of the sucker rod, and the disturbance of the high-pressure crude oil downhole, a certain lateral pressure may be generated between the pump cylinder and the plunger. At the same time, in order to speed up the frictional wear test process, a certain radial force is applied between the pump cylinder and the plunger.

The design of the pressurization mechanism should pay attention to four issues: 1 In order to maintain the radial force during the test, the pressurizing mechanism should do high-speed reciprocating motion, so the pressurizing mechanism should have a certain impact resistance; 2 the pressurizing mechanism should be simple in structure. , Light weight in order to reduce the inertia force; 3 When the friction test is carried out, the tester can run for a long time without stopping the machine. Therefore, the pressurizing mechanism should work reliably and have a long service life. There are many kinds of diameters of the test pump barrel and plunger. The pressurizing mechanism should have certain versatility.

(1) Composition of the pressurizing mechanism The composition of the pressurizing mechanism is as shown.

The root and the sleeve are in motion and on both sides are the mandrels of the spring. Under the wheel frame there is a roller. The outer surface of the sleeve is welded 90° to one end of the pressure lever.

(2) Working principle When the round nut 2 is turned, the sleeve is ascended and the end of the pressurizing lever is driven upward, so that the radial force is applied between the pump cylinder and the plunger with the axis of the roller as a fulcrum. At this point, the force sensor is pulled. The counterforce is pressed against the backing plate by the frame, the spring, the wheel frame, and the roller. Observe the tension signal in the force sensor through the computer. When it is added to the rated value, disconnect the signal line of the force sensor from the computer, lower the nut 5 to lock the required pressure, and then increase the nut 2 so that the sensor is unloaded during the test. Charge state. Since the deflection of the lever is very small, springs are used to increase the adjustment of the screw. This facilitates observation of force changes and increases resolution when pressurized. When the value of the diameter of the pump cylinder and the plunger exceeds the adjustment limit of the sleeve, the thickness of the pad shall be changed.

The axial section of the pressurizing lever is as shown. The left end of the lever is welded to the sleeve, and the right end is hinged to the plunger. The right part of the flange is the joint part that is replaced due to the different plungers. The figure above shows the joint of the 0110mm plunger and the lower part is the joint of the 038mm plunger.

In the design of the pressurizing lever, the following problems should be noted: 1 The pressurizing lever is a variable cross-section round beam; 2 The deformation deflection of the end of the lever plus the compression of the spring cannot exceed the maximum adjustment amount of the screw; 3 When the lever is When the left end is upturned, it will inevitably cause the vertical deflection of the pressurizing mechanism. Although the roller can adapt to this kind of skew, this skew can not be too large; 4 screw adjustment can not exceed the limit, but too small is not easy to diameter Adjustment of pressure; 5 For thinner plungers, during the reciprocating motion of the connector, avoid friction between the connector and the pump port.

4. The design procedure of the pressurizing lever is set as the axis direction of the lever and y is the bending deformation direction of the lever. According to the force of the lever, draw the shear diagram and bending moment diagram of the lever.

For the n-th section, the moment of inertia of the section is human.

There is one equal-section beam, and the moment of inertia of the section is the equivalent coefficient Pn=n. When the beam is equivalent to the original variable beam of this section, it is in the nth section and the first section of the original variable beam. At the junction of the 1st segment, external forces APn=d1-Pn)Qn and external torque AMn=((1-Pn)锾) should be added. Qn and 锾 are the shear and bending moments of the original variable-section beam at this junction.

According to the initial parameter method, the deflection y(z) and the rotation angle 0(z) at an arbitrary section z on an equal section beam can be obtained.

In combination with the boundary conditions, the deflection and rotation of the lever at one end of the pressurizing mechanism are determined.

According to the deflection of the thickest and finest plunger joints and the maximum adjustment of the screw, two springs with smaller stiffness and larger diameter are selected.

Take the pressurizing lever in the example. For the lever used by the 0110mm plunger, there are 10 beam sections with different sections. The distance from the right end of each beam section to the left end of the lever is: a=25mm, b=382mmc=402mme=477mm / = 497mmg = 559mmh = 588mm, i = 809mm / = 829mm, k = 871. The distance from the fulcrum of the lever to the left end face of the lever is d = 439.5mm. The moment of inertia of the section of each beam segment and the equivalent coefficient are given in Table 12 1 Sectional moment of inertia of each section of beam X104mm4 The equivalent coefficient of the person in Table 2 P 丨 The maximum radial pressure between the pump barrel and the plunger 3000N. So the right end of the lever Pk = 3000N The left end of the lever P. = 2945N Lever The fulcrum force Pd = -5945N. On the equivalent equi-section beam Pk = 21.45X3000 = 64350NP0 = 8.1X2945 = 23 945 = -26455.3N Each of the additional AP and AM values ​​can be calculated from the above existing formula.

Let the displacement of the left end of the lever be y., the angle of rotation is 0. The shear force is the moment M0 because it is the free end, so P0=Q0=23 854.5NM)=Q According to the boundary condition, the deflection is zero at the fulcrum and the right end of the lever. . The initial parameter method can be used to obtain fy0-439. For the 038mm plunger lever, there are nine different cross sections of the smallest pump barrel diameter 32mm diameter of the joint part of 26mm. Calculate the bending deflection y0 = 4. Conclusion Pump is deep in the well and The conditions of use are very poor. At present, simulation tests can only be conducted on the ground. The pump friction and wear tester can basically meet this requirement. The design of the pressurization mechanism is an important part of the mainframe design of the friction and wear tester. This design comprehensively considers various influencing factors, so that the structure of the mechanism is simple, reliable and adaptable. Running tests show that the agency meets design requirements.

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