A kind of superhigh pressure large flow reciprocating pump fluid end strength test device and method

Abstract

The present application belongs to the technical field of super-high pressure reciprocating pump, and particularly relates to a kind of super-high pressure reciprocating pump liquid end strength test device and method for realizing the strength test of super-high pressure reciprocating pump liquid end under low energy consumption state. The present application comprises a pulsation supercharging part for piston reciprocating stroke action, one end of a test pipeline is connected to the high pressure cavity of the pulsation supercharging part, and the other end of the test pipeline is connected to the liquid outlet of the pump cylinder of the reciprocating pump to be tested. The present application can realize effective simulation of the actual working condition alternating stress of the reciprocating pump liquid end to be tested under the premise of low energy consumption, and finally achieve the purpose of strength test of the liquid end.

Description

TECHNICAL FIELD

[0001] The application belongs to the technical field of super-high pressure reciprocating pumps, and particularly relates to a super-high pressure reciprocating pump liquid end strength test device and method for realizing the strength test of a super-high pressure reciprocating pump liquid end under a low energy consumption state. BACKGROUND

[0002] The super-high pressure reciprocating pump is widely applied in industrial, agricultural, petrochemical and power station production practices, and therefore, it is particularly important to study a series of indexes such as the performance, reliability and service life of the super-high pressure reciprocating pump. The total name of all parts and components in contact with the conveying medium of the reciprocating pump is the liquid end of the reciprocating pump, and usually refers to all parts and components included in the plunger (piston) to the inlet and outlet flanges. The liquid end is an important component of the reciprocating pump, and the strength performance index thereof directly determines the performance and reliability of the pump, which makes the strength detection of the liquid end of the reciprocating pump, especially the super-high pressure reciprocating pump, particularly important.

[0003] The structure of the reciprocating pump includes a crankshaft, the crankshaft drives the plunger to move reciprocally through a connecting rod and a column rod. When the plunger moves from left to right, a negative pressure is formed in the pump cylinder, and then the liquid enters the pump cylinder from the inlet through the inlet. When the plunger moves from right to left, the liquid in the pump cylinder is extruded, the pressure is increased, and the pressurized liquid is discharged from the outlet through the outlet. The plunger reciprocates once, and the liquid is sucked and discharged once, thereby completing a liquid pressurization process, which is called a working cycle. The movement of the plunger from one end to the other end is called a stroke. The distance of one stroke of the plunger is called the stroke of the plunger.

[0004] After the pump liquid end is manufactured, the corresponding strength test should be completed. The existing strength test is mainly the liquid static pressure test of the pump, which refers to the test that the equipment does not appear abnormal phenomena such as leakage and deformation under a certain pressure and for a certain time. As can be seen from the name, this kind of test can only realize the static test purpose under the specified pressure, and cannot completely reflect the actual strength of the equipment under the dynamic working condition for the reciprocating pump and other equipment which generates alternating stress during work. If the actual strength test is carried out by using the pump itself and adjusting the pressure through the pressure regulating valve, the working pressure (or a certain degree of working pressure) of the liquid end is adjusted, and the actual strength test is carried out. Since the power of the super-high pressure reciprocating pump often reaches hundreds of kilowatts or even thousands of kilowatts, a large amount of medium will be sucked and discharged in a single working cycle of the super-high pressure reciprocating pump, and the problem of huge power consumption needs to be solved urgently. SUMMARY

[0005] The application aims to overcome the shortcomings of the prior art, and provides a super-high pressure reciprocating pump liquid end strength test device. The application can effectively simulate the actual working condition alternating stress of the reciprocating pump liquid end under the premise of low energy consumption, and finally achieve the strength test purpose of the liquid end.

[0006] To achieve the above object, the application adopts the following technical solutions:

[0007] An ultrahigh-pressure large-flow reciprocating pump liquid end strength test device is characterized in that it comprises a pulsation pressurizing part capable of piston reciprocating stroke action, one end of a test pipeline is communicated with a high-pressure cavity of the pulsation pressurizing part, and the other end of the test pipeline is communicated with a liquid discharge port of a pump cylinder of a reciprocating pump to be tested.

[0008] Preferably, a filler for filling an inner cavity of the pump cylinder is arranged in the pump cylinder; and a gap is formed between the filler and the cylinder wall of the pump cylinder for allowing the medium to flow between the liquid discharge port and the inner cavity of the pump cylinder.

[0009] Preferably, the pulsation pressurizing part comprises a plunger cylinder and a plunger body fitted in the plunger cylinder, a front end face of the plunger body and a cylinder wall of the plunger cylinder form the high-pressure cavity, an axial columnar rod extends from a rear end face of the plunger body, and a tail end of the columnar rod is coaxially fitted with a piston rod end of a power cylinder.

[0010] Preferably, the pulsation pressurizing part comprises a plunger cylinder and a plunger body fitted in the plunger cylinder, a front end face of the plunger body and a cylinder wall of the plunger cylinder form the high-pressure cavity, an axial columnar rod extends from a rear end face of the plunger body, and the pulsation pressurizing part further comprises a crank slider assembly and a power motor for driving a crank in the crank slider assembly to rotate, and a slider in the crank slider assembly is fixedly connected with the columnar rod.

[0011] Preferably, the device further comprises a water tank arranged on a water supplement pipeline, the medium is discharged through a water outlet of the water tank, sequentially communicated with the liquid discharge port of the pump cylinder through a switch valve V1, a power pump, a first check valve CV1 for preventing medium backflow, a heat exchanger, and then sequentially returned to the water tank through the liquid discharge port of the pump cylinder and a pressure regulating valve RV; the high-pressure cavity of the pulsation pressurizing part is communicated with a liquid inlet branch pipeline and a backflow branch pipeline, the liquid inlet branch pipeline is communicated with a section of the water supplement pipeline between the first check valve CV1 and the heat exchanger through a second check valve CV2 for preventing medium backflow, and the liquid discharge port of the pump cylinder is communicated with the high-pressure cavity of the pulsation pressurizing part through the backflow branch pipeline, and a third check valve CV3 for preventing medium backflow is arranged on the backflow branch pipeline.

[0012] Preferably, a method for applying the ultrahigh-pressure large-flow reciprocating pump liquid end strength test device is characterized by comprising the following steps:

[0013] S1, the following formula is used to obtain the stroke volume V of a single plunger of the pump cylinder of the reciprocating pump to be tested 排单 :

[0014]

[0015] wherein:

[0016] D is the diameter of the plunger in the pump cavity;

[0017] S is the stroke of the plunger in the pump cavity;

[0018] S2, the following formula obtains the total volume V0 of the pump cylinder:

[0019] V0 = n (V 排单 + V 余单 )

[0020] Wherein:

[0021] n is the number of plungers in the pump cavity;

[0022] V 余单 is the residual volume in the single plunger pump cavity;

[0023] S3, the following formula obtains the discharge volume V 脉动 of the pulsation booster:

[0024]

[0025] Wherein:

[0026] k is the compression coefficient;

[0027] S4, the following formula obtains the stroke S 脉动 of the plunger body of the pulsation booster and the diameter d of the plunger body:

[0028]

[0029] S5, the following formula obtains the ratio a of the discharge volume V 脉动 of the pulsation booster and the total stroke volume V 排 of the plunger of the pump cylinder:

[0030]

[0031] Given the ratio a and the power N e待试验泵 of the reciprocating pump to be tested, the driving power N e脉动 of the pulsation booster is obtained by the following formula:

[0032]

[0033] Preferably, in the step S4, the stroke S 脉动 of the plunger body of the pulsation booster is obtained by the following formula:

[0034]

[0035] Preferably, a method for applying the super-high pressure large flow reciprocating pump liquid end strength test device comprises the following steps:

[0036] S1', the following formula is used to obtain the stroke volume V of a single plunger of the reciprocating pump to be tested 排单 :

[0037]

[0038] S2', the following formula is used to obtain the total volume V0 of the pump cylinder:

[0039] V0 = n (V 排单 + V 余单 )

[0040] Wherein:

[0041] n is the number of plungers in the pump cavity;

[0042] V 余单 is the residual volume in the single plunger pump cavity;

[0043] S3', the following formula is used to obtain the volume V0' of the filled pump cylinder:

[0044] V0' = V0 - V 填充

[0045] Wherein:

[0046] V 填充 is the volume of the filling;

[0047] S4', the following formula is used to obtain the discharge volume V of the pulsating booster: 脉动 :

[0048]

[0049] Wherein:

[0050] k is the compression coefficient;

[0051] S5', the following formula is used to obtain the stroke S of the plunger body of the pulsating booster 脉动 and the diameter d of the plunger body:

[0052]

[0053] S6', the following formula is used to obtain the ratio a of the discharge volume V of the pulsating booster 脉动 and the total stroke volume V of the plunger of the pump cylinder: 排

[0054]

[0055] Given the ratio a and the power N of the reciprocating pump to be tested e待试验泵 , the driving power N of the pulsating booster is obtained by the following formula: e脉动 : ​

[0056]

[0057] Preferably, in the step S5', the stroke S of the plunger body of the pulsating booster 脉动 is obtained by the following formula:

[0058]

[0059] The present application has the following advantages:

[0060] 1) By the above scheme, the pump cylinder discharge port of the reciprocating pump to be tested is connected to the pulsating booster, and the liquid inlet of the pump cylinder is provided with a one-way valve, so that the medium cannot be discharged from the pump cylinder through the liquid inlet, and the internal space of the pump cylinder is naturally connected to the high-pressure cavity of the pulsating booster.

[0061] During operation, the plunger of the reciprocating pump to be tested does not move, and the plunger body of the pulsating booster reciprocates, so that the pulsating pressure effect of the pulsating booster on the medium in the test pipeline and the pump cavity is utilized to realize the simulation effect of the discharge and intake capacity of the reciprocating pump to be tested. During actual testing, the discharge and intake capacity of the reciprocating pump to be tested accurately reflects the compression amount of the medium in the pump cylinder, and is completely consistent with the effect of the reciprocating pump to be tested under normal working conditions, so that the "four ounces move a thousand catties" effect is realized, and the strength test of the reciprocating pump to be tested with low energy consumption is realized without the need for the reciprocating pump to be tested to work.

[0062] At this point, the present application obtains the real-time change of the medium pressure in the pump cavity by controlling the change of the medium compression amount in the entire device, which not only can simulate the working state of the reciprocating pump to be tested under different working conditions by controlling the pulsating pressure of the pulsating booster, and complete the strength test of the pump liquid end, but also can save a lot of power consumption, realize the low-energy-consumption operation effect of the strength test of the reciprocating pump liquid end, and the effect is extremely significant.

[0063] 2) As a further preferred embodiment of the above scheme, a filler with a reasonable size can be arranged in the liquid end of the reciprocating pump to be tested to reduce the volume of the pump cylinder of the liquid end during testing, so as to further reduce the discharge amount of the pulsating booster by equal proportional compression, and finally further reduce the power consumption of the strength test of the reciprocating pump liquid end.

[0064] 3), further, for pulsating booster, it only needs to realize the reciprocating piston action, the difference lies in the difference of driving mode. According to the actual situation, reciprocating drive structure such as gear rack can be used, cam power driving mode or even worm gear driving pair driving mode can be used. The present application preferably adopts two forms: one is the booster principle type of reciprocating movement of plunger body driven by hydraulic cylinder piston with hydraulic power, the other is the motor-driven reciprocating pump principle type of reciprocating movement of plunger body driven by crankshaft connecting rod mechanism such as motor, diesel engine, etc. Here is not described.

[0065] 4), considering the high efficiency and convenience of test, the present application provides a set of water replenishing circulation system, that is, relying on water tank to form water replenishing kit to ensure that the working pressure of pulsating booster can be adjusted in time according to the demand. At the same time, relying on heat exchanger, the online cooling or even heating purpose of water as medium is realized, so that the medium temperature is kept or tends to the expected working temperature of the medium in the pump cylinder of the reciprocating pump to be tested, and the accuracy of test results is ensured. At this time, the test pipeline mentioned above can be regarded as the combination of water replenishing pipeline, liquid inlet branch pipeline and return branch pipeline.

[0066] 5), as the core part of the present application, the parameters of pulsating booster are designed with strong pertinence, especially the diameter of plunger body, the stroke of plunger body and the driving power. For this, the present application provides an optimization algorithm, so that the above parameters can be obtained simply and efficiently, so that the actual working state of the original reciprocating pump can be simulated and restored at low power while highly matching the reciprocating pump to be tested. BRIEF DESCRIPTION OF DRAWINGS

[0067] Figure 1 is the schematic diagram of pipeline arrangement of the present application;

[0068] Figure 2 and Figure 3 is the structural schematic diagram of two different embodiments of pulsating booster;

[0069] Figure 4 is the arrangement state diagram of filler.

[0070] The actual corresponding relationship between the numbers and component names of the present application is as follows:

[0071] 10-pulsating booster; 11-plunger cylinder; 12-plunger body;

[0072] 20-reciprocating pump to be tested; 21-filler; 30-water tank; 40-power pump;

[0073] 50-heat exchanger. DETAILED DESCRIPTION

[0074] For ease of understanding, this section combines... Figures 1-4 The specific structure and operation of the present invention are further described below:

[0075] The specific embodiments of the present invention are as follows: Figure 1 As shown, its main structure includes the test reciprocating pump 20, pressure regulating valve RV, pulsating booster unit 10, water tank 30, power pump 40, first check valve CV1, second check valve CV2, third check valve CV3, on / off valve V1, heat exchanger 50, and packing material 21 located on the test pipeline. Among them:

[0076] During the test, components unrelated to the strength test at the hydraulic end (i.e., the pump cylinder outlet) of the reciprocating pump 20 to be tested were removed, allowing water, the medium, to enter the pump cylinder through the outlet. The pump inlet is a one-way valve, preventing water from exiting, thus creating a naturally open outlet and closed inlet single-pass structure. Therefore, as... Figure 1 After the system is connected as shown, due to the control of the pressure regulating valve RV and the first check valve CV1, the high-pressure chamber of the pulsating booster 10 and the pump cylinder of the reciprocating pump 20 to be tested are connected to the third check valve CV3 and the second check valve CV2 through the test pipeline to form a test system.

[0077] In the aforementioned test system, the pulsating booster unit 10 is the core component of this invention. In actual use, the pulsating booster unit 10 generally takes two forms: one is a booster principle type that uses hydraulic power to drive the piston of a hydraulic cylinder, causing the plunger body 12 of the pulsating booster unit 10 to reciprocate, as described in [reference needed]. Figure 2 As shown. Another type is a motorized reciprocating pump where a power motor, such as an electric motor or diesel engine, drives the crankshaft connecting rod mechanism, and the reciprocating linearly moving slider drives the plunger 12 to produce reciprocating motion. See [reference needed]. Figure 3 As shown.

[0078] When the pulse booster unit 10 is specifically used in a booster principle manner, it includes a hydraulic power system and a booster. For example... Figure 2 As shown, the hydraulic power system mainly consists of a hydraulic oil tank and cooling system, a hydraulic pump, and a reversing valve; the booster mainly consists of a piston and piston cylinder, a plunger body 12 and seals, and a plunger cylinder 11. Figure 2As shown, the hydraulic pump pressurizes and pumps out hydraulic oil. A reversing valve connects pipelines P and A, and T and B. The hydraulic oil enters the piston cylinder through pipeline A, pushing the piston from left to right. The hydraulic oil then returns to the hydraulic tank via pipelines B and T. When the piston reaches the bottom of port B, the reversing valve reverses, connecting pipelines P and B, and T and A. At this time, hydraulic oil enters the piston cylinder through pipeline B, pushing the piston and plunger from right to left. The hydraulic oil then returns to the hydraulic tank via pipelines A and T. This process repeats, achieving the goal of the hydraulic oil pushing the piston in the cylinder, which in turn pushes the plunger body 12 along the plunger cylinder 11 in alternating reciprocating motion, ultimately achieving the effect of cyclic pressurization and depressurization at the hydraulic end of the reciprocating pump 20 under test.

[0079] Correspondingly, such as Figure 3 The pulsating booster unit 10 of the motorized reciprocating pump type shown mainly includes a crankshaft, connecting rod, slider, plunger body 12, plunger cylinder 11, etc. The movement of the crankshaft and connecting rod drives the plunger body 12 to reciprocate within the plunger cylinder 11, thereby achieving the effect of cyclic boosting and depressurization at the hydraulic end of the reciprocating pump 20 under test.

[0080] In actual testing, the end where the plunger 12 pressurizes the medium to its maximum pressure is considered the end point, and the other end is considered the beginning point. Simultaneously, the distance traveled or retracted by the plunger 12 in a single stroke is defined as the stroke of the plunger 12, and the medium is water. Therefore, there are two testing schemes for this invention:

[0081] Option 1:

[0082] The plunger 12 of the pulsating booster 10 is advanced to the end of its stroke, at which point the volume of the high-pressure chamber of the pulsating booster 10 is at its minimum. Water is pumped from the water tank 30 through the first one-way valve CV1 to fill the entire device and pressurize it to the required test pressure p0. The volume of high-pressure water at the test pressure p0 is approximately equal to the volume V0 of the pump cylinder of the reciprocating pump 20 to be tested.

[0083] When the plunger 12 in the pulse booster moves from the end to the beginning, the third check valve CV3 opens and the second check valve CV2 closes, releasing the pressure within the entire device. The pressure at the hydraulic end of the test reciprocating pump 20 gradually decreases until it is unpressurized or in a negative pressure state. When the plunger 12 in the pulse booster moves from the beginning to the end, the second check valve CV2 opens and the third check valve CV3 closes, pressurizing the water within the entire device. The hydraulic end of the test reciprocating pump 20 becomes pressurized, and the pressure gradually increases as the plunger 12 moves. When the plunger 12 reaches the end, the pressure reaches the maximum, reaching the test pressure p0.

[0084] The above movement is repeated at a set frequency, i.e. the goal of simulating the working state of the reciprocating pump 20 to be tested by the pulsating pressure unit 10 is achieved. Due to the arrangement of the third check valve CV3 and the second check valve CV2, the water in the entire set always flows in the counterclockwise direction as shown in the figure, and can be cooled by heat exchange in the heat exchanger 50. Figure 1

[0085] Scheme II:

[0086] The plunger body 12 of the pulsating pressure unit 10 is moved to the starting end, at which time the volume of the high-pressure cavity of the pulsating pressure unit 10 is the largest, and the volume of the entire set is also the largest, denoted as V1. The power pump 40 is used to fill the entire set with water from the water tank 30 through the first check valve CV1, and the required volume of water at normal pressure is V1. When the plunger body 12 in the pulsating pressure unit moves from the starting end to the ending end, the water in the entire set is pressurized, and the liquid end of the reciprocating pump 20 to be tested is in a pressurized state, and the pressure gradually increases as the plunger body 12 moves. When the plunger body 12 moves to the ending end, the pressure is the largest. When the plunger body 12 in the pulsating pressure unit moves from the ending end to the starting end, the pressure in the entire set is released, and the pressure on the liquid end of the reciprocating pump 20 to be tested gradually decreases until it is not pressurized. The pressure regulating valve RV is adjusted so that the water pressure reaches the maximum pressure p0 required for the test when the plunger body 12 moves to the ending end.

[0087] The above movement is repeated at a set frequency, i.e. the goal of simulating the working state of the reciprocating pump 20 to be tested by the pulsating pressure unit 10 is achieved. Similarly, due to the control of the third check valve CV3 and the second check valve CV2, the water in the entire set always flows in the counterclockwise direction as shown in the figure, and can be cooled by heat exchange in the heat exchanger 50.

[0088] On the basis of the above scheme, taking the most preferred embodiment with the filler 21 as shown in Figure 4 The parameters of the pulsating pressure unit are selected according to the following steps and obtained:

[0089] S1', the following formula is used to obtain the stroke volume V of a single plunger of the pump cylinder at the reciprocating pump 20 to be tested 排单 :

[0090]

[0091] wherein:

[0092] D is the diameter of the plunger in the pump cavity;

[0093] S is the stroke of the plunger in the pump cavity;

[0094] S2', the following formula is used to obtain the total volume V0 of the pump cylinder:

[0095] V0 = n (V 排单 + V 余单 )​

[0096] wherein:

[0097] n is the number of plungers in the pump chamber;

[0098] V 余单 is the residual volume in the single plunger pump chamber, usually given as a known parameter; when taken as a demand, V 余单 is the volume of the pump cylinder V0 10% ~ 50%.

[0099] S3', the following formula obtains the volume V0' of the filled pump cylinder:

[0100] V0' = V0 - V 填充

[0101] wherein:

[0102] V 填充 is the volume of the filling 21;

[0103] S4', since the test pipeline connecting the pulsating booster 10 and the reciprocating pump 20 to be tested is thin and short, its volume can be ignored, so the volume V1 of the entire device can be equal to the volume V0' of the filled pump cylinder plus the stroke volume or discharge volume V 脉动 of the plunger body 12 of the pulsating booster 10, that is, V1 = V0' + V 脉动 ;

[0104] At the same time, in the test, the atmospheric water in the volume V1, after being compressed by the plunger body 12 of the pulsating booster 10 by one stroke volume, the water pressure changes from atmospheric pressure to the discharge pressure p0 of the reciprocating pump 20 to be tested, and the water volume also changes to the volume V0 of the pump cylinder. The volume compression of water under high pressure cannot be ignored, and according to the literature, the relationship between V 脉动 and V1 is: V 脉动 = kV1.

[0105] At this point, the discharge volume V 脉动 of the pulsating booster 10 is obtained:

[0106]

[0107] wherein:

[0108] k is the compression coefficient, the value of which is shown in Table 1:

[0109] Table 1 Values of the compression coefficient k of water under partial water pressure

[0110] pressure P0 / MPa 100 200 250 300 400 500 k 0.039 0.071 0.084 0.094 0.112 0.132

[0111] S5', the following formula obtains the stroke S 脉动 of the plunger body 12 of the pulsating booster 10 and the diameter d of the plunger body 12:

[0112]

[0113] From the above formula, S 脉动 and d must be determined after one of the values is determined. It can be seen that S 脉动 and d have theoretically infinite combinations, but only need to be limited in the ratio range of [0.8, 8], which is a common experience ratio range in the industry. In actual calculation, S 脉动 and d are approximated, and then rounded through trial, so as to finally determine S 脉动 and d are reasonable values, as long as S 脉动 / d is in the above ratio range.

[0114] S6', since the discharge pressure of the pulsation booster 10 is the same as that of the reciprocating pump 20 to be tested, the ratio of the power of the two is the ratio of the flow of the two, which can be obtained from the existing pump effective power calculation formula.

[0115] Therefore, the following formula obtains the ratio a of the discharge volume V 脉动 of the pulsation booster 10 and the total stroke volume V 排 of the pump cylinder:

[0116]

[0117] Given the ratio a and the power N e待试验泵 of the reciprocating pump 20 to be tested, the driving power N e脉动 of the pulsation booster 10 is obtained by the following formula:

[0118]

[0119] In actual testing, it is just because the volume V0 of the pump cylinder is reduced in the test, which can further reduce the driving power of the pulsation booster 10; therefore, appropriate filler 21 can be placed in the pump cylinder according to different structures, such as round steel of the same material as the fluid end. In actual installation, the filler 21 is preferably spaced from the inner wall of the pump cylinder by more than 3 mm, so as to ensure the free flow of water in the pump cylinder, so as to ensure the accuracy of the experiment. Practice and calculation show that the volume of the filler 21 can account for 80% to 90% of the volume V0 of the pump cylinder.

[0120] Accordingly, the ratio a under the test pressure of 100 MPa to 500 MPa can be calculated as shown in Table 2:

[0121] Table 2 Ratio a under part of test pressure

[0122] Test pressure 100 MPa 200 MPa 250 MPa 300 MPa 400 MPa 500 MPa Power ratio in % 0.45～1.62 0.85～3.06 1.02～3.67 1.15～4.15 1.40～5.05 1.69～6.08

[0123] Example 1

[0124] Taking a 300MPa superhigh pressure large flow three-plunger reciprocating pump as an example, the following calculation is carried out:

[0125] The plunger diameter D of the pump is 20mm, the plunger stroke S is 140mm, the pump speed n is 440min -1 , and the matching motor power N e is 315kW. The theoretical flow rate q v is 58L / min=9.7x10 -4 m 3 / s.

[0126] The stroke volume V 排单 of a single plunger of the pump cylinder 20 of the reciprocating pump to be tested is obtained:

[0127]

[0128] The clearance volume V 余单 in the single plunger pump cavity is known to be 9.545x10 -6 m 3 ;

[0129] The total volume V0 of the pump cylinder is obtained:

[0130] V0=n(V 排单 +V 余单 )=3x(V 排单 +V 余单 )=1.606x10 -4 m 3

[0131] Taking the corresponding filler 21, the volume V 填充 of the filler 21 is known to be 1.32x10 -4 m 3 ;

[0132] The volume V0' of the filled pump cylinder is obtained:

[0133] V0'=V0-V 填充 =0.286x10 -4 m 3

[0134] At this time, the discharge volume V 脉动 of the pulsation supercharging part 10 is:

[0135]

[0136] At 300MPa:

[0137] Because the pump speed is the same, S 脉动The ratio of S to D is similar to the ratio of the stroke S of the reciprocating pump 20 to be tested to the diameter D of the reciprocating pump 20, and can be regarded as equal. At this time, the single reciprocating chamber of the reciprocating pump 20 to be tested can be proportionally reduced to the same volume as the high-pressure chamber of the pulsating supercharging part 10, that is, the stroke of the reciprocating body 12 of the pulsating supercharging part 10 and the diameter of the reciprocating body 12 can be initially obtained, and specifically:

[0138] Let S / D=L, then D=S / L, so:

[0139]

[0140] Similarly, S 脉动 / D=L, then d=S 脉动 / L, at this time:

[0141]

[0142] Integrating the above two formulas, we have:

[0143]

[0144] We have: Rounded to 60 mm.

[0145] From we obtain the diameter d of the reciprocating body 12 as 7.94 mm.

[0146] At this time, the diameter d of the reciprocating body 12 is determined as 8 mm, the stroke S of the reciprocating body 12 is 脉动 60 mm, and the reciprocating frequency is the same as that of the reciprocating pump 20 to be tested.

[0147] The ratio a of the discharge volume V 脉动 of the pulsating supercharging part 10 to the total stroke volume V 排 of the pump cylinder is obtained:

[0148]

[0149] Given the ratio a=2.29% and the power N e待试验泵 of the reciprocating pump 20 to be tested, the driving power N e脉动 of the pulsating supercharging part 10 is obtained by the following formula:

[0150] N e脉动 =N e待试验泵 ·a=7.21 kW

[0151] Example 2

[0152] To strengthen the stiffness of the reciprocating body 12 of Example 1, the diameter d of the reciprocating body 12 can also be selected as 10 mm, and S 脉动 =37.82 mm is obtained.

[0153] It can be determined that the diameter d of the selected plunger body 12 is 10mm, and the stroke S of the rounded plunger body 12 is... 脉动 =40mm, and the reciprocating frequency is the same as that of the reciprocating pump 20 to be tested.

[0154] The discharge volume V of the pulsating pressurization unit 10 is obtained. 脉动 The total stroke volume V of the pump cylinder plunger 排 The ratio a:

[0155]

[0156] Given the ratio a = 2.38% and the power N of the reciprocating pump 20 to be tested. e待试验泵 The driving power N of the pulsating booster unit 10 is obtained by the following formula. e脉动 :

[0157] N e脉动 =N e待试验泵 α = 7.497 kW

[0158] Therefore, for the aforementioned 300MPa ultra-high pressure, high flow rate three-plunger reciprocating pump, the pulsating booster section 10 can be determined to have a plunger body 12 with a diameter d = 8mm and a plunger body 12 stroke S. 脉动 =60mm; or, considering the strength of the plunger body 12, select a plunger body 12 diameter d = 10mm, and a plunger body 12 stroke S. 脉动 =37.82mm; the driving power of the power motor or hydraulic pump of the hydraulic cylinder matched with the pulsating booster 10 is 7.5kW, which can achieve the purpose of strength test of the reciprocating pump 20 under 315kW.

[0159] After the experiment has been running for a period of time, even though the heat exchanger 50 cools the water used as the medium in the entire device, the water in the entire device will still slowly heat up due to repeated pressurization, affecting the test results. At this time, the power pump 40 can be used to displace the high-temperature water in the pump cylinder from the water tank 30 by using the first one-way valve CV1 and the pressure regulating valve RV. If any form of leakage occurs during the experiment, causing a drop in the test pressure, this method can also be used to replenish water to the pump cylinder. If the experiment is interrupted, the operation of the initial experiment should be repeated.

[0160] Finally, the stress and strain data of key components of the hydraulic end are read using testing instruments, thus completing the strength test of the hydraulic end. The setup, reading, and recording of this testing instrument are standard operating procedures in the industry and will not be elaborated upon here.

[0161] Conclusion

[0162] Through the test device, the working state of the reciprocating pump under different working conditions can be simulated, and the strength test of the liquid end of the pump can be completed.

[0163] Of course, the present application is not limited to the details of the above-described exemplary embodiments, but also includes the same or similar structures that can be implemented in other specific forms without departing from the spirit or essential characteristics of the present application. Therefore, the embodiments should be regarded as exemplary and non-limiting, and the scope of the present application is defined by the appended claims rather than the above description, and thus all changes falling within the meaning and scope of the equivalent elements of the claims are intended to be included in the present application. Any reference signs in the claims should not be regarded as limiting the claims involved.

[0164] Furthermore, it should be understood that, although the present specification is described in terms of embodiments, not every embodiment contains only one independent technical solution, and the description of the specification is only for the sake of clarity, and those skilled in the art should consider the specification as a whole, and the technical solutions in each embodiment can be properly combined to form other embodiments that those skilled in the art can understand.

[0165] The technologies, shapes, and structural parts not described in detail in the present application are well-known technologies.

Claims

1. A method for testing the strength of a liquid end of a super-high pressure and large flow reciprocating pump, characterized in that: the testing device comprises a pulsating pressure boosting part (10) capable of reciprocating stroke action as a piston, one end of a test pipeline is connected to a high pressure cavity of the pulsating pressure boosting part (10), and the other end of the test pipeline is connected to a liquid discharge port of a pump cylinder of a reciprocating pump (20) to be tested; the pulsating pressure boosting part (10) comprises a plunger cylinder (11) and a plunger body (12) fitted in the plunger cylinder (11), a front end surface of the plunger body (12) and a cylinder wall of the plunger cylinder (11) form the high pressure cavity; and the method further comprises the following steps: wherein: D is the diameter of the plunger in the pump cavity; S is the stroke of the plunger in the pump cavity; S2 is the total volume V0 of the pump cylinder obtained by the following formula: wherein: n is the number of plungers in the pump cavity; wherein: k is the compression coefficient; the rear end surface of the plunger body (12) extends axially with a columnar rod, and the tail end of the columnar rod is coaxially fitted with the piston rod end of a power cylinder. The rear end surface of the plunger body (12) extends axially with a columnar rod; the pulsating pressure boosting part (10) further comprises a crank slider assembly and a power motor driving a crank of the crank slider assembly to rotate, and a slider of the crank slider assembly is fixedly connected with the columnar rod. The device further comprises a water tank (30) arranged on a water supplement pipeline, the medium is discharged through a water outlet of the water tank (30), sequentially passes through a switch valve V1, a power pump (40), a first check valve CV1 for preventing medium backflow, a heat exchanger (50), and then is connected to the liquid discharge port of the pump cylinder, and then sequentially passes through the liquid discharge port of the pump cylinder and a pressure regulating valve RV, and then returns to the water tank (30); the high pressure cavity of the pulsating pressure boosting part (10) is connected with a liquid inlet branch pipeline and a backflow branch pipeline, the liquid inlet branch pipeline is connected to a section of the water supplement pipeline between the first check valve CV1 and the heat exchanger (50) through a second check valve CV2 for preventing medium backflow, the liquid discharge port of the pump cylinder is connected to the high pressure cavity of the pulsating pressure boosting part (10) through the backflow branch pipeline, and a third check valve CV3 for preventing medium backflow is arranged on the backflow branch pipeline. ​ S1, the following formula obtains the stroke volume V of the single plunger of the pump cylinder of the reciprocating pump (20) to be tested 排单 : ​ ​ ​ ​ V0 = n(V 排单 + V 余单 ) ​ ​ V 余单 Vr is the residual volume in the single plunger pump chamber; S3, the following formula obtains the discharge volume V of the pulsation supercharger (10) 脉动 : ​ ​ S4, the stroke S of the plunger body (12) of the pulsation supercharger (10) is obtained from the following formula 脉动 and the diameter d of the plunger body (12): S5, the ratio a of the volume V of the delivery of the pulsation supercharger (10) obtained from the following formula 脉动 and the total stroke volume V of the plunger of the pump cylinder 排 ​ The known ratio a and the power N of the reciprocating pump (20) to be tested e The drive power N of the pulsation booster (10) is obtained for the pump to be tested by e脉动 :

2. The method of claim 1, wherein the device is used for testing the strength of a liquid end of a super-high-pressure and high-flow reciprocating pump. ​ 3. The method of claim 1, wherein the device is used for testing the strength of a liquid end of a super-high-pressure large-flow reciprocating pump. ​ 4. The method of claim 1, wherein the device is used for strength test of a liquid end of a super-high pressure and high flow reciprocating pump. ​ 5. The method of claim 1, wherein the method further comprises: determining the strength of the liquid end of the super-high pressure large flow reciprocating pump. In the step S4, the stroke S of the plunger body (12) of the pulsation supercharger (10) 脉动 is obtained by the following formula:

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