Method for testing strength of liquid end of superhigh pressure and large flow reciprocating pump

Abstract

The application belongs to the technical field of super-high pressure reciprocating pump, and particularly relates to a method for testing the liquid end strength of a super-high pressure large-flow reciprocating pump under low energy consumption. The method comprises a pulsation pressurizing part capable of reciprocating stroke action, a high-pressure cavity of the pulsation pressurizing part connected to one end of a test pipeline, a liquid discharge port of a pump cylinder of a reciprocating pump to be tested connected to the other end of the test pipeline, and a set of optimization algorithms. The method is simple and efficient in calculation, and thus can simulate and restore the actual working state of the reciprocating pump to be tested under low power while matching the reciprocating pump to be tested.

Description

[0001] This invention is a divisional application of application number CN202211715941.4 entitled "A test device and method for hydraulic end strength of an ultra-high pressure and high flow reciprocating pump", with the original application date being December 28, 2022. Technical Field

[0002] This invention belongs to the field of ultra-high pressure reciprocating pump technology, specifically relating to a method for strength testing of the hydraulic end of an ultra-high pressure, high flow rate reciprocating pump under low energy consumption conditions. Background Technology

[0003] Ultra-high pressure reciprocating pumps are widely used in national production practices such as industry, agriculture, petrochemicals, and power plants. Therefore, research on a series of indicators such as performance, reliability, and lifespan of ultra-high pressure reciprocating pumps is particularly important. The hydraulic end of a reciprocating pump refers to all parts and components that come into contact with the pumped medium, typically encompassing everything from the plunger (piston) to the inlet and outlet flanges. The hydraulic end is a crucial component of the reciprocating pump, and its strength performance directly determines the pump's performance and reliability. This makes strength testing of the hydraulic end of reciprocating pumps, especially ultra-high pressure reciprocating pumps, particularly important.

[0004] A reciprocating pump consists of a crankshaft, which drives a plunger to reciprocate via connecting rods and a piston rod. When the plunger moves from left to right, a negative pressure is created inside the pump cylinder, drawing liquid in through the inlet. When the plunger moves from right to left, the liquid inside the pump cylinder is compressed, increasing the pressure, and the pressurized liquid is discharged through the outlet. One reciprocating motion of the plunger, with one intake and one discharge of liquid, completes one liquid pressurization process, called a working cycle. The movement of the plunger from one end to the other is called one stroke. The distance the plunger travels in one stroke is called the plunger's stroke.

[0005] After the hydraulic end of the pump is manufactured, a corresponding strength test should be performed. Current strength tests mostly refer to the pump's hydrostatic pressure test, which tests the equipment to ensure no leakage, deformation, or other abnormalities occur under a certain pressure and within a certain time. As the name suggests, this type of test can only achieve the purpose of a static test under a specified pressure. For equipment such as reciprocating pumps that generate alternating stress during operation, it cannot fully reflect the actual strength of the equipment under dynamic working conditions. Furthermore, if an actual measurement method is used, that is, using the pump itself and adjusting the pressure through a pressure regulating valve to conduct an actual strength test on the hydraulic end at the working pressure (or to a certain extent exceeding the working pressure), the power of ultra-high pressure, high flow reciprocating pumps often reaches hundreds or even thousands of kilowatts. This results in the pump handling a huge amount of media in a single working cycle, leading to enormous power consumption problems that urgently need to be addressed. Summary of the Invention

[0006] The purpose of this invention is to overcome the shortcomings of the prior art and provide a method for testing the hydraulic end strength of an ultra-high pressure, high flow reciprocating pump. This invention is simple and efficient in calculation, thereby simulating and restoring the actual working state of the original reciprocating pump at low power while highly matching the reciprocating pump under test.

[0007] To achieve the above objectives, the present invention adopts the following technical solution:

[0008] A method for testing the hydraulic end strength of an ultra-high pressure, high flow rate reciprocating pump using a testing device is characterized in that: the testing device includes a pulsating booster section capable of reciprocating piston motion; one end of the test pipeline is connected to the high-pressure chamber of the pulsating booster section, and the other end of the test pipeline is connected to the discharge port of the pump cylinder of the reciprocating pump under test; the pump cylinder is filled with a filling material; and a gap exists between the filling material and the cylinder wall to allow the medium to flow between the discharge port and the pump cylinder cavity.

[0009] Includes the following steps:

[0010] S1', the stroke volume V of a single plunger in the pump cylinder of the reciprocating pump under test is obtained by the following formula. 排单 :

[0011]

[0012] S2', The total volume V0 of the pump cylinder is obtained by the following formula:

[0013] V0=n(V 排单 +V 余单 )

[0014] in:

[0015] n is the number of plungers in the pump chamber;

[0016] V 余单 The clearance volume within a single plunger pump chamber;

[0017] S3', The volume V0′ of the pump cylinder after filling is obtained by the following formula: V0′=V0-V 填充

[0018] in:

[0019] V 填充 The volume of the filler;

[0020] S4', The discharge volume V of the pulsating pressurization section is obtained by the following formula. 脉动 :

[0021]

[0022] in:

[0023] k is the compression factor;

[0024] S5', The stroke S of the plunger body of the pulsating booster section is obtained by the following formula. 脉动 and the diameter d of the plunger body:

[0025]

[0026] S6', The discharge volume V of the pulsating pressurization section is obtained by the following formula. 脉动 The total stroke volume V of the pump cylinder plunger 排 The ratio a:

[0027]

[0028] 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 unit is obtained by the following formula. e脉动 :

[0029]

[0030] Preferably, in step S5', the stroke S of the plunger body of the pulsating pressurization section 脉动 Obtained through the following formula:

[0031]

[0032] Preferably, the pulsating booster includes a plunger cylinder and a plunger body fitted inside the plunger cylinder. The front end face of the plunger body and the cylinder wall of the plunger cylinder enclose the high-pressure chamber. A rod extends axially from the rear end face of the plunger body, and the tail end of the rod is coaxially fitted with the piston rod end of the power cylinder.

[0033] Preferably, the pulsating booster includes a plunger cylinder and a plunger body fitted inside the plunger cylinder, the front end face of the plunger body and the cylinder wall of the plunger cylinder forming the high-pressure chamber; a rod extends axially from the rear end face of the plunger body; the pulsating booster also includes a crank-slider assembly and a power motor that drives the crank in the crank-slider assembly to rotate, the slider in the crank-slider assembly and the rod are fixedly connected to each other.

[0034] Preferably, the device further includes a water tank arranged on the water supply pipeline. The medium is discharged through the outlet of the water tank, and sequentially passes through a switching valve, a power pump, a first check valve to prevent backflow of the medium, and a heat exchanger before connecting to the discharge port of the pump cylinder. Then, it returns to the water tank sequentially through the discharge port of the pump cylinder and a pressure regulating valve. The high-pressure chamber of the pulsating pressurization section is connected to an inlet branch pipeline and a return branch pipeline. The inlet branch pipeline is connected to a section of the water supply pipeline between the first check valve and the heat exchanger via a second check valve to prevent backflow of the medium. The medium at the discharge port of the pump cylinder is connected to the high-pressure chamber of the pulsating pressurization section via the return branch pipeline. A third check valve to prevent backflow of the medium is provided on the return branch pipeline.

[0035] The beneficial effects of this invention are as follows:

[0036] 1) By using the above scheme, the pump cylinder discharge port of the hydraulic end of the reciprocating pump to be tested is connected to the pulsating booster section. Since the pump cylinder inlet has a built-in check valve, the medium cannot be discharged from the pump cylinder through the inlet port, thus naturally achieving the unique connection effect between the internal space of the pump cylinder and the high-pressure chamber of the pulsating booster section.

[0037] During operation, the plunger of the reciprocating pump under test does not move, while the plunger of the pulsating pressurization unit reciprocates. This pulsating pressurization unit applies pulsating pressure to the medium in the test pipeline and even the pump chamber, simulating the pump's discharge and inflow rates. In actual testing, the discharge and inflow rates of the reciprocating pump accurately reflect the compression of the medium within the pump cylinder, perfectly matching the effect of normal operation. This achieves a "leveraging effect," ultimately enabling low-energy testing of the reciprocating pump's strength without requiring it to operate.

[0038] Thus, this invention obtains the real-time change of medium pressure in the pump chamber by controlling the change of medium compression in the entire device. It can not only simulate the working state of the reciprocating pump under different working conditions by controlling the pulsating pressure of the pulsating booster, and complete the strength test of the hydraulic end of the pump, but also save a lot of power consumption, achieving a low-energy operation effect for the hydraulic end strength test of ultra-high pressure and high flow reciprocating pumps, with extremely significant results.

[0039] Meanwhile, this invention reduces the volume of the hydraulic end pump cylinder during testing by setting a reasonably sized filler at the hydraulic end of the reciprocating pump under test. This further reduces the discharge volume of the pulsating booster section through proportional compression, ultimately reducing the power consumption of the reciprocating pump's hydraulic end strength test. As the core component of this invention, the parameters of the pulsating booster section are designed with high specificity, especially the core parameters such as the plunger diameter, plunger stroke, and drive power. This invention provides an optimization algorithm to obtain these parameters simply and efficiently, thereby highly matching the reciprocating pump under test while simulating and reproducing the actual working state of the original reciprocating pump at low power.

[0040] 2) Furthermore, for the pulsating booster unit, it only needs to achieve the reciprocating piston action; the difference lies in the driving method. Depending on the actual situation, a reciprocating drive structure such as a gear and rack can be used, or a cam-driven drive or even a worm gear transmission can be employed. This invention preferably adopts two forms: one is a booster principle type where hydraulic power drives a hydraulic cylinder piston to drive the piston body in reciprocating motion; the other is a motorized reciprocating pump principle type where a power motor, such as an electric motor or diesel engine, drives a crankshaft connecting rod mechanism to drive the piston body in reciprocating motion. These will not be elaborated further here.

[0041] 3) Considering the efficiency and convenience of the experiment, this invention simultaneously provides a water replenishment and circulation system, that is, a water replenishment kit formed by a water tank, to ensure that the working pressure of the pulsating pressurization section can be adjusted in a timely manner as needed. At the same time, relying on a heat exchanger, the water used as the medium is cooled or even heated online, thereby maintaining or bringing the medium temperature closer to the expected working temperature of the medium inside the pump cylinder of the reciprocating pump under test, thus ensuring the accuracy of the test results. In this case, the aforementioned test pipeline can be considered as a combination of a water replenishment pipeline, an inlet branch pipeline, and a return branch pipeline. Attached Figure Description

[0042] Figure 1 This is a schematic diagram of the pipeline layout of the present invention;

[0043] Figure 2 and Figure 3 Schematic diagrams of two different embodiments of the pulsating booster unit;

[0044] Figure 4 This is a diagram showing the arrangement of the filling material.

[0045] The actual correspondence between the reference numerals and component names in this invention is as follows:

[0046] V1 - Switch valve; RV - Pressure regulating valve;

[0047] CV1 - First check valve; CV2 - Second check valve; CV3 - Third check valve;

[0048] 10-Pulsating booster section; 11-Plunger cylinder; 12-Plunger body;

[0049] 20 - Reciprocating pump to be tested; 21 - Packing material; 30 - Water tank; 40 - Power pump;

[0050] 50 - Heat exchanger. Detailed Implementation

[0051] For ease of understanding, this section combines... Figure 1-4 The specific structure and operation of the present invention are further described below:

[0052] 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:

[0053] 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.

[0054] 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.

[0055] 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.

[0056] 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.

[0057] 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:

[0058] Option 1:

[0059] 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.

[0060] 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.

[0061] By repeating the above motion at a set frequency, the goal of simulating the working state of the reciprocating pump 20 under test using the pulsating booster unit 10 is achieved. Due to the installation of the third check valve CV3 and the second check valve CV2, the water in the entire device is always kept at a constant... Figure 1 The counterclockwise flow shown can be cooled by heat exchanger 50.

[0062] Option 2:

[0063] The plunger 12 of the pulse booster unit 10 is moved to the beginning, at which point the volume of the high-pressure chamber of the pulse booster unit 10 is at its maximum, and the volume of the entire device is also at its maximum, denoted as V1. Water is pumped from the water tank 30 through the first one-way valve CV1 using the power pump 40 to fill the entire device; the required volume of atmospheric pressure water is V1. When the plunger 12 in the pulse booster unit moves from the beginning to the end, the water in the entire device is pressurized. As the hydraulic end of the test reciprocating pump 20 becomes pressurized, the pressure gradually increases with the movement of the plunger 12, reaching its maximum when the plunger 12 reaches the end. When the plunger 12 in the pulse booster unit moves from the end to the beginning, the pressure in the entire device is released, and the pressure on the hydraulic end of the test reciprocating pump 20 gradually decreases until it reaches an unpressurized state. The pressure regulating valve RV is adjusted so that the water pressure reaches the maximum pressure p0 required for the test when the plunger 12 reaches the end.

[0064] By repeating the above motion at a set frequency, the goal of simulating the working state of the reciprocating pump 20 under test using the pulsating booster 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 device always flows counterclockwise, and can be cooled by heat exchanger 50.

[0065] Based on the above scheme, with the following: Figure 4 Taking the most preferred embodiment of the filler 21 shown as an example, the parameters of the pulsating pressurization section are selected and obtained according to the following steps:

[0066] S1', the stroke volume V of a single plunger in the 20 cylinders of the reciprocating pump under test is obtained by the following formula. 排单 :

[0067]

[0068] in:

[0069] D is the diameter of the plunger inside the pump chamber;

[0070] S represents the stroke of the plunger inside the pump chamber;

[0071] S2', The total volume V0 of the pump cylinder is obtained by the following formula:

[0072] V0=n(V 排单 +V 余单 )

[0073] in:

[0074] n is the number of plungers in the pump chamber;

[0075] V 余单 V is the clearance volume within a single plunger pump chamber, typically given as a known parameter; when the required value is [value], V 余单 The value is 10% to 50% of the pump cylinder volume V0.

[0076] S3', The volume V0′ of the pump cylinder after filling is obtained by the following formula:

[0077] V0′=V0-V 填充

[0078] in:

[0079] V 填充 For the volume of filler 21;

[0080] S4' Since the test pipeline connecting the pulsating booster unit 10 and the reciprocating pump 20 under test is thin and short, its volume can be ignored. Therefore, the volume V1 of the entire device can be equal to the volume V0' of the pump cylinder after filling plus the stroke volume of the plunger body 12 of the pulsating booster unit 10, or the discharge volume V. 脉动 That is, V1 = V0′ + V 脉动 ;

[0081] Simultaneously, during the experiment, the atmospheric pressure water with volume V1, after being compressed by the plunger 12 of the pulsating pressurization section 10 for one stroke, changes its pressure from atmospheric pressure to the discharge pressure p0 of the reciprocating pump 20 under test, and the water volume becomes the pump cylinder volume V0. The volume compression of water under high pressure cannot be ignored. According to literature, its relationship with the total volume V1 of the above-mentioned device is: V 脉动 =kV1.

[0082] Thus, the discharge volume V of the pulsating pressurization unit 10 is obtained. 脉动 :

[0083]

[0084] in:

[0085] k is the compression factor, and its values ​​are shown in Table 1:

[0086] Table 1 shows the values ​​of the compressibility coefficient k of water under partial water pressure.

[0087] k 0.039 0.071 0.084 0.094 0.112 0.132

[0088] S5', The stroke S of the plunger body 12 of the pulsating booster section 10 is obtained by the following formula. 脉动 The diameter d of the plunger body 12:

[0089]

[0090] From the above formula, S 脉动 The value of d must be determined before the value of the other can be determined. It can be seen that S... 脉动 Theoretically, there are countless combinations of d, as long as the ratio is limited to the range of [0.8, 8]; this ratio range is a commonly used empirical range in the industry. In actual calculations, S can also be determined based on the approximate proportional relationship between the plunger stroke S and the plunger diameter D of the reciprocating pump 20 under test. 脉动 The approximate value of d is then rounded up through trial calculations to finally determine S. 脉 The reasonable values ​​for S-pulse / d are as long as S-pulse / d is within the range mentioned above.

[0091] S6' Since the discharge pressure of the pulsating booster 10 is the same as that of the reciprocating pump 20 to be tested, it can be seen from the existing pump effective power calculation formula that the ratio of their power is the ratio of their flow rates.

[0092] Therefore, the discharge volume V of the pulsating pressurization section 10 is obtained by the following formula. 脉动 The total stroke volume V of the pump cylinder plunger 排 The ratio a:

[0093]

[0094] Given the ratio a 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 :

[0095]

[0096] In actual testing, reducing the pump cylinder volume V0 further reduces the driving power of the pulsating booster unit 10. Therefore, suitable filler material 21, such as round steel of the same material as the hydraulic end, can be placed according to different structures within the pump cylinder. During actual installation, it is preferable that the filler material 21 has a gap greater than 3mm between itself and the inner wall of the pump cylinder to ensure free flow of water within the pump cylinder and thus guarantee the accuracy of the experiment. Practice and calculations show that the volume of the filler material 21 can occupy 80% to 90% of the pump cylinder volume V0.

[0097] Based on this, the ratio 'a' can be calculated when the test pressure is between 100 MPa and 500 MPa, as shown in Table 2.

[0098] Table 2. Ratios a under partial test pressures

[0099] Power ratio % 0.45～1.62 0.85～3.06 1.02～3.67 1.15～4.15 1.40～5.05 1.69～6.08

[0100] Example 1

[0101] Taking a 300MPa ultra-high pressure, high flow rate three-plunger reciprocating pump as an example, the following calculations are performed:

[0102] The pump has a plunger diameter D = 20 mm, a plunger stroke S = 140 mm, and a pump speed n = 440 min. -1 Matching motor power N e =315kW. Its theoretical flow rate q v =58L / min=9.7×10 -4 m 3 / s.

[0103] Obtain the stroke volume V of a single plunger at 20 pump cylinders of the reciprocating pump to be tested. 排单 :

[0104]

[0105] Given the clearance volume V in a single plunger pump chamber 余单 =9.545×10 -6 m 3 ;

[0106] Obtain the total volume V0 of the pump cylinder:

[0107] V0=n(V 排单 +V 余单 )=3×(V 排单 +V 余单 ) = 1.606 × 10 -4 m 3

[0108] Take the corresponding filler 21, and the volume V of filler 21 is known. 填充 =1.32×10 -4 m 3 ;

[0109] Obtain the volume V0′ of the pump cylinder after filling:

[0110] V0′=V0-V 填充 =0.286×10 -4 m 3

[0111] At this time, the discharge volume V of the pulsating pressurization section 10 脉动 for:

[0112]

[0113] At 300 MPa:

[0114] Because the pump speed is the same, S 脉动The proportional relationship between d and the stroke S of the plunger in the reciprocating pump 20 under test is similar to that between the plunger's stroke S and its diameter D, and can be considered equal. In this case, the single plunger cavity of the reciprocating pump 20 under test can be proportionally reduced to the same volume as the high-pressure chamber of the pulsating booster section 10. This allows for the preliminary determination of the stroke and diameter of the plunger body 12 in the pulsating booster section 10. Specifically:

[0115] Let S / D = L, then D = S / L, and so:

[0116]

[0117] Similarly, S 脉动 / d=L, then d=S 脉动 / L, at this time:

[0118]

[0119] Combining the above two equations, we get:

[0120]

[0121] have to: Round it to 60mm.

[0122] Depend on The diameter d of the plunger body 12 is 7.94 mm.

[0123] Therefore, it can be determined that the diameter d of the plunger body 12 is 8mm, and the stroke S of the plunger body 12 is... 脉 The moving part is 60mm, and the reciprocating frequency is the same as that of the reciprocating pump 20 to be tested.

[0124] 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:

[0125]

[0126] Given the ratio a = 2.29% 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 :

[0127] N e脉动 =N e待试验泵 ·α=7.21kW

[0128] Example 2

[0129] To enhance the rigidity of the plunger body 12 in Embodiment 1, a plunger body 12 with a diameter d = 10 mm can also be selected, thus obtaining S 脉动 =37.82mm.

[0130] 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.

[0131] 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:

[0132]

[0133] 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 :

[0134] N e脉动 =N e待试验泵 α = 7.497 kW

[0135] 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.

[0136] 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.

[0137] 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.

[0138] Conclusion

[0139] Through this test device, the present invention can not only simulate the working state of reciprocating pumps under different working conditions and complete the strength test of the hydraulic end of the pump; actual tests have shown that the present invention can also save more than 90% of the power consumption of completing the strength test by pressurizing the pump itself, and realize low-energy operation of hydraulic end strength test of ultra-high pressure and high flow reciprocating pump.

[0140] Of course, those skilled in the art will recognize that the present invention is not limited to the details of the exemplary embodiments described above, 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 invention. Therefore, the embodiments should be considered illustrative and non-limiting in all respects, and the scope of the invention is defined by the appended claims rather than the foregoing description. Thus, all variations falling within the meaning and scope of equivalents of the claims are intended to be included within the present invention. No reference numerals in the claims should be construed as limiting the scope of the claims.

[0141] Furthermore, it should be understood that although this specification describes embodiments, not every embodiment contains only one independent technical solution. This narrative style is merely for clarity. Those skilled in the art should consider the specification as a whole, and the technical solutions in each embodiment can also be appropriately combined to form other embodiments that can be understood by those skilled in the art.

[0142] The technologies, shapes, and structures not described in detail in this invention are all known technologies.

Claims

1. A method for testing the hydraulic end strength of an ultra-high pressure, high flow rate reciprocating pump using a testing device, characterized in that: The hydraulic end strength test device for ultra-high pressure and high flow reciprocating pump includes a pulsating booster (10) capable of piston-type reciprocating stroke. One end of the test pipeline is connected to the high pressure chamber of the pulsating booster (10), and the other end of the test pipeline is connected to the discharge port of the pump cylinder of the reciprocating pump (20) to be tested. The pump cylinder is filled with a filler (21) for filling the inner cavity of the pump cylinder. There is a gap between the filler (21) and the cylinder wall for the medium to flow between the discharge port and the inner cavity of the pump cylinder. Includes the following steps: S1', the stroke volume V of a single plunger in the pump cylinder at the reciprocating pump (20) under test is obtained by the following formula. 排单 : S2', The total volume V0 of the pump cylinder is obtained by the following formula: V0=n(V 排单 +V 余单 ) in: n is the number of plungers in the pump chamber; V 余单 The clearance volume within a single plunger pump chamber; S3', The volume V0′ of the pump cylinder after filling is obtained by the following formula: V0′=V0-V 填充 in: V 填充 For the volume of the filler (21); S4', The discharge volume V of the pulsating pressurization section (10) is obtained by the following formula. 脉动 : in: k is the compression factor; S5', the stroke S of the plunger (12) of the pulsating booster section (10) is obtained by the following formula. 脉动 The diameter d of the plunger body (12): S6', The discharge volume V of the pulsating pressurization section (10) is obtained by the following formula. 脉动 The total stroke volume V of the pump cylinder plunger 排 The ratio a: Given the ratio a 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 :

2. The method for testing the hydraulic end strength of an ultra-high pressure, high flow rate reciprocating pump as described in claim 1, characterized in that: In step S5', the stroke S of the plunger (12) of the pulsating booster (10) is... 脉动 Obtained through the following formula:

3. The hydraulic end strength testing device for an ultra-high pressure, high flow rate reciprocating pump according to claim 1 or 2, characterized in that: The pulsating booster unit (10) includes a plunger cylinder (11) and a plunger body (12) fitted inside the plunger cylinder (11). The front end face of the plunger body (12) and the cylinder wall of the plunger cylinder (11) enclose the high-pressure chamber. A rod extends axially from the rear end face of the plunger body (12), and the tail end of the rod is coaxially fitted with the piston rod end of the power cylinder.

4. The hydraulic end strength testing device for an ultra-high pressure, high flow rate reciprocating pump according to claim 1 or 2, characterized in that: The pulsating booster unit (10) includes a plunger cylinder (11) and a plunger body (12) fitted inside the plunger cylinder (11). The front end face of the plunger body (12) and the cylinder wall of the plunger cylinder (11) enclose the high-pressure chamber. A rod extends axially from the rear end face of the plunger body (12). The pulsating booster unit (10) also includes a crank-slider assembly and a power motor that drives the crank in the crank-slider assembly to rotate. The slider in the crank-slider assembly is fixedly connected to the rod.

5. The hydraulic end strength testing device for an ultra-high pressure, high flow rate reciprocating pump according to claim 1 or 2, characterized in that: The device also includes a water tank (30) arranged on the water supply pipeline. The medium is discharged through the outlet of the water tank (30), and sequentially passes through the switch valve (V1), the power pump (40), the first check valve (CV1) to prevent the medium from flowing back, and the heat exchanger (50) before connecting to the discharge port of the pump cylinder. Then, it returns to the water tank (30) sequentially through the discharge port of the pump cylinder and the pressure regulating valve (RV). The high-pressure chamber of the pulsating booster (10) is connected to the inlet branch pipeline and the return branch pipeline. The inlet branch pipeline is connected to a section of the water supply pipeline between the first check valve (CV1) and the heat exchanger (50) via the second check valve (CV2) to prevent the medium from flowing back. The medium at the discharge port of the pump cylinder is connected to the high-pressure chamber of the pulsating booster (10) via the return branch pipeline. A third check valve (CV3) is provided on the return branch pipeline to prevent the medium from flowing back.

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