A kind of jet flow energy absorber and adjustable pressure type ultra-high pressure reciprocating pump test system

Abstract

This invention relates to the field of reciprocating pump testing, specifically a jet energy dissipator and an adjustable pressure ultra-high pressure reciprocating pump testing system. The jet energy dissipator includes an inner sleeve through which the jet passes. One end of the inner sleeve is coaxially connected to a high-pressure water inlet via a throttling nozzle, and the other end is connected to a low-pressure water outlet. Energy dissipation cylinders are evenly spaced along the axial direction within the inner sleeve to divert the fluid. Each energy dissipation cylinder includes a jet cylinder coaxially arranged with the inner sleeve. Diverting blades are evenly arranged circumferentially on the outer wall of the jet cylinder. The inner sleeve, the jet cylinder, and the diverting blades enclose and form multi-component diversion cavities. This invention provides a jet energy dissipator that reduces the velocity of the high-speed water jet during ultra-high pressure reciprocating pump testing, significantly eliminates jet kinetic energy, avoids damage to the experimental system from the high-speed jet, improves experimental measurement accuracy, and ultimately achieves pressure build-up and precise pressure regulation during ultra-high pressure pump testing.

Description

Technical Field

[0001] This invention relates to the field of reciprocating pump testing, specifically a jet energy dissipator and an adjustable pressure ultra-high pressure reciprocating pump testing system. Background Technology

[0002] The volumetric method is a common test method for measuring the flow rate of reciprocating pumps. Its core principle is to introduce all the liquid discharged from the reciprocating pump into a calibrated measuring container of known volume within a specific time period. By measuring the time required to fill the container, the actual average flow rate of the pump can be calculated. By verifying whether the pump's flow rate under rated operating conditions reaches the design value and measuring the change in pump flow rate under different discharge pressures, the performance of the reciprocating pump can be evaluated.

[0003] When testing reciprocating pumps using the volumetric method, it is required to measure the flow rate under different pressure conditions between 0 and rated pressure. Under low-pressure conditions, the pressure can often be directly adjusted by a throttle valve. However, when the maximum test pressure of the reciprocating pump exceeds the maximum pressure within the throttle valve's adjustment range, the pressure cannot be adjusted by the throttle valve. The throttle valve will leak under ultra-high pressure conditions. Therefore, it is urgent to build a new pressure adjustment test system to adapt to the testing of ultra-high pressure reciprocating pumps.

[0004] Furthermore, during the testing of ultra-high pressure reciprocating pumps, the pressure regulation process directly alters the fluid velocity. When the fluid discharged from the ultra-high pressure reciprocating pump forms a high-speed jet, this jet can damage the testing system's containers or pipelines, affecting the measurement accuracy. Therefore, these problems urgently need to be addressed. Summary of the Invention

[0005] To avoid and overcome the technical problems existing in the prior art, this invention provides a jet energy dissipator, which reduces the flow velocity of the high-speed water jet during ultra-high pressure reciprocating pump testing, significantly eliminates the jet's kinetic energy, avoids damage to the experimental system caused by the high-speed jet, and improves the accuracy of experimental measurements. This invention also provides an adjustable pressure ultra-high pressure reciprocating pump testing system, which achieves pressure regulation across the entire pressure range of the ultra-high pressure reciprocating pump within the limited pressure regulation range of the throttle valve.

[0006] To achieve the above objectives, the present invention provides the following technical solution:

[0007] A jet energy dissipator includes an inner sleeve through which the jet passes. One end of the inner sleeve is coaxially connected to a high-pressure water inlet via a throttling nozzle, and the other end of the inner sleeve is connected to a low-pressure water outlet. Energy dissipation cylinders that divide the fluid are uniformly spaced along the axial direction inside the inner sleeve. Each energy dissipation cylinder includes a jet cylinder arranged coaxially with the inner sleeve. Diverting blades are uniformly arranged along the circumferential direction on the outer wall of the jet cylinder. The inner sleeve, the jet cylinder, and each diverting blade enclose and form multiple diverting cavities. The fluid passing through each diverting cavity is guided by the diverting blades to form a swirling flow that is offset from the jet path passing through the jet cylinder. The swirling flow rate through the diverting blades in each energy dissipator is less than the jet flow rate passing through the jet cylinder.

[0008] As a further aspect of the present invention: the energy dissipation cylinder and the inner wall of the inner sleeve slide in an axial direction, the energy dissipation cylinder and the connecting sleeve are alternately arranged in the inner sleeve, and the cavity of the connecting sleeve forms a channel for the fluid discharged from the energy dissipation cylinder to pass through.

[0009] As a further embodiment of the present invention: a spring is provided axially inside the inner sleeve, one end of the spring abuts against the low-pressure water outlet, and the other end of the spring abuts against the energy dissipation cylinder on the side of the adjacent low-pressure water outlet, and the spring applies an elastic clamping force to each energy dissipation cylinder and the connecting sleeve.

[0010] As a further embodiment of the present invention: an outer sleeve is coaxially arranged outside the inner sleeve, and the outer sleeve and the inner sleeve enclose an annular cooling cavity. A cooling water inlet and a cooling water outlet communicating with the cooling cavity are arranged radially on the outer sleeve; along the axial direction of the outer sleeve, the cooling water inlet and the cooling water outlet are respectively arranged at both ends of the outer sleeve.

[0011] As a further embodiment of the present invention: the inlet of the high-pressure water is fixed to the high-pressure filter by a clamping bolt, and the high-pressure filter is coaxially fixedly connected to the throttling nozzle by a connecting joint.

[0012] An adjustable pressure ultra-high pressure reciprocating pump test system comprises a circulating medium tank, a test reciprocating pump, an air chamber, and an energy dissipation circuit connected sequentially along the medium flow direction. The energy dissipation circuit includes a jet energy dissipator and a cooling sleeve connected in parallel. Throttling valves are installed at the inlets of both the jet energy dissipator and the cooling sleeve to regulate the flow rate. The outlet of the energy dissipation circuit is connected to the inlet of a three-way valve. One outlet of the three-way valve is directly connected to the circulating medium tank, and the other outlet of the three-way valve is connected to the circulating medium tank after passing through a metering container.

[0013] As a further aspect of the present invention: the number of throttling nozzle sets is calculated based on the maximum test pressure of the tested reciprocating pump. a Determine the nozzle orifice diameter for each group of throttling nozzles. d ;

[0014] a = b -1; ;

[0015] ;

[0016] in, b The pressure rating of the tested reciprocating pump. b It is a positive integer;

[0017] The pressure ratings of the tested reciprocating pumps corresponded to different pressure regulation ranges; b The pressure regulation range corresponding to each pressure level is: bPt' ~ ( b -1) Pt' , Pt' The maximum pressure within the regulating range of the two throttle valves in the energy dissipation circuit;

[0018] P 0 The maximum test pressure of the tested reciprocating pump;

[0019] Q The rated flow rate of the tested reciprocating pump;

[0020] μ The flow coefficient of the throttling nozzle;

[0021] P t This represents the maximum pressure within the pressure adjustment range corresponding to the pressure level.

[0022] As a further aspect of the present invention: the distance between the jet outlet of the throttling nozzle and the energy dissipation cylinder at the starting end is equal to the arrangement spacing of the energy dissipation cylinders in the inner sleeve, and the arrangement spacing of the energy dissipation cylinders is... L :

[0023] ;

[0024] in, P This represents the maximum jet pressure of the throttling nozzle;

[0025] d The nozzle orifice diameter of the throttling nozzle is calculated based on the orifice diameter under the highest pressure condition;

[0026] k This is an empirical coefficient;

[0027] x This represents the attenuation ratio of the core area diameter of the throttling nozzle.

[0028] As a further aspect of the present invention: the aperture of the jet tube in the energy dissipation tube is... D :

[0029] .

[0030] As a further embodiment of the present invention: a temperature sensor is installed at the outlet of the energy dissipation circuit, a temperature sensor and a vacuum pressure gauge are installed at the inlet of the tested reciprocating pump, and a throttle valve is installed at the outlet of the circulating medium tank; the outlet of the tested reciprocating pump is connected to the circulating medium tank through a safety valve; a level gauge is installed in both the circulating medium tank and the metering container, and a temperature regulating component for regulating the medium temperature is installed in the circulating medium tank.

[0031] Compared with the prior art, the beneficial effects of the present invention are:

[0032] 1. This invention utilizes multiple coaxially connected energy dissipation cylinders. As the high-pressure jet flows through each stage of the energy dissipation cylinder, it is guided by diverter blades to form a swirling flow, offset from the central jet path, achieving stage-by-stage, multi-path energy dissipation. By precisely controlling the flow distribution between the diverter blades and the jet cylinders, a stable and controllable pressure reduction can be achieved while ensuring the main propulsion efficiency. This effectively reduces the impact, vibration, and cavitation damage of the high-speed jet on the downstream, lowers the velocity of the high-speed water jet during ultra-high pressure reciprocating pump testing, significantly eliminates jet kinetic energy, avoids damage to the experimental system from the high-speed jet, and improves experimental measurement accuracy. Furthermore, by installing replaceable throttling nozzles at the high-pressure water inlet, nozzles of different diameters can be quickly replaced according to the different outlet pressure ranges and flow requirements of the ultra-high pressure reciprocating pump. Within the limited pressure adjustment range of the throttling valve, pressure regulation of the entire pressure range of the ultra-high pressure reciprocating pump can be achieved.

[0033] 2. The energy dissipation cylinder and inner sleeve of this invention adopt a sliding fit, and the spring applies axial elastic clamping force to each component, which ensures the compactness and stability of the overall structure, prevents the internal components from moving due to water impact, and allows the number or spacing of the internal components of the energy dissipator to be flexibly adjusted according to the actual working pressure. By setting an annular cooling cavity between the outer sleeve and the inner sleeve, and setting cooling water inlet and outlet at both ends along the axial direction, an effective cooling water circulation channel can be formed to remove the heat generated by fluid friction and energy dissipation during the energy dissipation process in a timely manner, thereby improving the operational reliability and service life of the energy dissipator under long-term, high-load conditions.

[0034] 3. The integrated design of the high-pressure filter, connecting joint and clamping bolt of this invention not only prevents nozzle clogging, but also ensures the sealing and firmness of the high-pressure connection. The overall structure is compact, integrating all energy dissipation elements into a coaxial cylindrical structure, resulting in high overall safety and reliability.

[0035] 4. This invention determines the number of throttling nozzle groups based on the pressure range of the tested reciprocating pump and calculates the nozzle orifice diameter of each group of throttling nozzles, thereby adapting to the pressure regulation range of different pressure levels and realizing pressure regulation of the ultra-high pressure reciprocating pump across the entire pressure range. The energy dissipation element is designed based on the nozzle orifice diameter of the throttling nozzle at the highest pressure level, determining the arrangement spacing of the energy dissipation elements and the diameter of the guide holes to ensure that the energy dissipation elements meet the energy dissipation requirements at the highest pressure of the tested reciprocating pump. Attached Figure Description

[0036] Figure 1 This is a schematic diagram of the structure of the present invention.

[0037] Figure 2 This is a schematic diagram of the jet energy dissipator in this invention.

[0038] Figure 3 This is a schematic diagram of the energy dissipation cylinder in this invention.

[0039] In the picture:

[0040] 1. Jet energy dissipator; 11. Inner sleeve; 12. Energy dissipation cylinder;

[0041] 121. Jet tube; 122. Flow divider blade; 13. Connecting sleeve;

[0042] 14. Outer sleeve; 141. Cooling water inlet; 142. Cooling water outlet; 143. Cooling chamber;

[0043] 15. Low-pressure water outlet; 16. Spring; 17. Throttling nozzle;

[0044] 171. Connecting joint; 172. High-pressure filter; 173. Clamping bolt; 18. High-pressure water inlet;

[0045] 2. Cooling sleeve; 3. Air chamber; 4. Test reciprocating pump;

[0046] 5. Circulating medium tank; 51. Temperature control assembly; 6. Three-way valve; 7. Metering container. Detailed Implementation

[0047] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0048] Please see Figures 1-3In this embodiment of the invention, a jet energy dissipator and an adjustable pressure ultra-high pressure reciprocating pump test system are provided. Existing volumetric test systems for reciprocating pumps, as described in Appendix B of GB / T7784 standard, directly adjust the pressure via a throttle valve. This application replaces the throttle valve of the traditional volumetric test system with an energy dissipation circuit. The energy dissipation circuit includes two sets of parallel circuits. One set of circuits contains a jet energy dissipator 1, and the other set contains a cooling sleeve 2. Both the cooling sleeve 2 and the inlet of the jet energy dissipator 1 are equipped with throttle valves of the same type to adjust the pressure.

[0049] The jet energy dissipator 1 includes an inner sleeve 11, multiple energy dissipation cylinders 12, and a connecting sleeve 13 arranged in series inside the inner sleeve 11, with the energy dissipation cylinders 12 and the connecting sleeves 13 arranged alternately. The inner sleeve 11 and the outer sleeve 14 are connected by a flange structure. One end of the high-pressure water inlet 18 is connected to a throttle valve, and the other end is fixed to a high-pressure filter 172 by a clamping bolt 173. The high-pressure filter 172 is coaxially connected and fixed to a throttle nozzle 17 via a connecting joint 171. The throttle nozzle 17 is coaxially fixed to the inner sleeve 11, jetting the medium discharged from the high-pressure water inlet 18 into the inner sleeve 11.

[0050] The inner sleeve 11 has a hollow cylindrical structure. One end of it is fixedly connected to the throttling nozzle 17 via a flange, and the throttling nozzle 17 is connected to the high-pressure water inlet 18. The other end of the inner sleeve 11 is open, and a low-pressure water outlet 15 is coaxially arranged at the opening. The low-pressure water outlet 15 has a two-stage stepped columnar structure. The outer sleeve 14 and the inner sleeve 11 clamp and position the low-pressure water outlet 15. A sealing ring is provided at the contact surface between the low-pressure water outlet 15, the outer sleeve 14, and the inner sleeve 11. The outlet flow channel of the low-pressure water outlet 15 is two-stage. The upstream section is a tapered channel that is wider at the front and narrower at the back, and the downstream section is a cylindrical channel that connects to the end of the tapered channel.

[0051] The inner wall of the inner sleeve 11 is smoothly machined. The energy dissipation cylinder 12 and the connecting sleeve 13 are positioned after sliding fit with the wall of the inner sleeve 11. To achieve positioning, a spring 16 is axially arranged inside the inner sleeve 11, near the end of the low-pressure water outlet 15. One end of the spring 16 abuts against the end face of the low-pressure water outlet 15, and the other end abuts against the end face of the energy dissipation cylinder 12 closest to the low-pressure water outlet 15. Under the preload of the spring 16, all the alternately arranged energy dissipation cylinders 12 and the connecting sleeve 13 are pressed together as a whole, forming an elastic compression positioning.

[0052] The energy dissipation cylinder 12 includes a jet cylinder 121 coaxially arranged with the inner sleeve 11. The central through-hole of the jet cylinder 121 forms the main jet channel, allowing a portion of the fluid to pass through at high speed in a relatively concentrated jet state. Four to eight blades are evenly radially distributed along the outer wall of the jet cylinder 121. The radial height of the diverting blades 122 ensures that their outer edges are in close contact with the inner wall of the inner sleeve 11 or leave a very small gap. The diverting blades 122 have a certain helical angle or curved surface shape. Multiple independent diverting cavities are formed by the outer wall of the jet cylinder 121, the two side surfaces of each diverting blade 122, and the inner wall of the inner sleeve 11. The diverting blades 122 guide the fluid flow path through the diverting cavities, changing the flow path and creating a swirling flow around the jet cylinder 121.

[0053] The connecting sleeve 13 is a short cylindrical structure with openings at both ends. Its outer diameter corresponds to the outer diameter of the energy dissipation cylinder 12. It is used to connect two adjacent energy dissipation cylinders 12. Its internal cavity forms a transition channel. All the fluid discharged from the previous energy dissipation cylinder 12 re-converges and collides here before entering the next energy dissipation cylinder 12 for a new round of energy dissipation.

[0054] High-pressure water enters through high-pressure water inlet 18 and first passes through throttling nozzle 17. After throttling and depressurizing the fluid, nozzle 17 accelerates the fluid into a concentrated high-speed jet, which is injected into the inlet of jet tube 121 of the first energy dissipation tube 12. Upon entering the energy dissipation tube 12, the high-speed jet is split. A portion of the fluid passes directly through the central channel of jet tube 121, maintaining a high velocity and concentrated flow state. The other portion, with a smaller flow rate, is intercepted by the splitting blades 122 and guided into the surrounding splitting chambers. Guided by the angled splitting blades 122, this portion of fluid changes direction, generating a strong rotational motion around the axis of jet tube 121, forming a swirling path. This swirling path is spatially offset from the central jet path. In this embodiment, the helical angle of the splitting blades 122 is between 30° and 60°, and the flow rate ratio of the fluid through jet tube 121 to the fluid through the splitting chambers is approximately 8:2.

[0055] Within the same energy dissipation cylinder 12, the central high-speed jet and the peripheral high-speed swirling flow are separated by blades but are adjacent in the flow direction. Momentum exchange occurs between them through viscous shear, with some of the jet's kinetic energy transferred to the swirling flow. The swirling flow itself generates enormous centrifugal force due to its rotational motion, resulting in intense friction and vortex losses within the fluid and between the fluid and the inner sleeve wall, converting a large amount of mechanical energy into heat energy. The two fluids flowing out of the energy dissipation cylinder 12 along different paths then enter the connecting sleeve 13. In the connecting sleeve 13, the central jet collides, mixes, and exchanges momentum with the peripheral swirling flow, generating numerous vortices and turbulence, further dissipating energy. The mixed fluid then enters the second energy dissipation cylinder 12, repeating the aforementioned process of flow splitting, swirling flow generation, and shear dissipation. Through the alternating series connection of multiple energy dissipation cylinders 12 and connecting sleeves 13, the fluid's energy is dissipated stage by stage, repeatedly. After energy dissipation through the final stage of energy dissipation cylinders 12 and connecting sleeves 13, the fluid pressure drops to the target low pressure and is smoothly discharged from the low-pressure water outlet 15.

[0056] The throttling nozzle 17 is a replaceable design, allowing for adaptation to different test pressure ranges and flow rates by replacing nozzles of different diameters.

[0057] The outer sleeve 14 and the inner sleeve 11 enclose an annular cooling cavity 143. Cooling water inlets 141 and cooling water outlets 142 are respectively provided on both sides of the outer sleeve 14. The outer sleeve 14 has a cooling water inlet 141 and a cooling water outlet 142 that communicate with the cooling cavity 143 arranged radially; along the axial direction of the outer sleeve 14, the cooling water inlet 141 and the cooling water outlet 142 are respectively arranged at both ends of the outer sleeve 14.

[0058] The test system for the ultra-high pressure reciprocating pump specifically includes a circulating medium tank 5, a test reciprocating pump 4, an air chamber 3, and an energy dissipation circuit arranged sequentially along the flow direction of the medium. The outlet of the energy dissipation circuit is connected to the inlet of a three-way valve 6. One outlet of the three-way valve 6 is directly connected to the circulating medium tank 5, and the other outlet of the three-way valve 6 is connected to the circulating medium tank via a metering container 7. A temperature sensor is installed at the outlet of the energy dissipation circuit, and a temperature sensor and a vacuum pressure gauge are installed at the inlet of the test reciprocating pump 4. A throttle valve is installed at the outlet of the circulating medium tank 5. The outlet of the test reciprocating pump 4 is connected to the circulating medium tank 5 via a safety valve. Level gauges are installed in both the circulating medium tank 5 and the metering container 7. A temperature regulating component 51 for adjusting the medium temperature is installed in the circulating medium tank.

[0059] When testing the reciprocating pump 4 under test, the number of sets of throttling nozzles 17 is first calculated based on the maximum test pressure of the reciprocating pump 4 under test. a Determine the nozzle orifice diameter corresponding to each group of throttling nozzles 17. d ;

[0060] a = b -1; ;

[0061] , Substituting the values, we get:

[0062] ;

[0063] in, b The pressure rating of the tested reciprocating pump 4 is... b It is a positive integer;

[0064] The pressure rating of the test reciprocating pump 4 corresponds to different pressure regulation ranges; b The pressure regulation range corresponding to each pressure level is: bPt' ~ ( b -1) Pt' , Pt' The maximum pressure within the throttle valve's pressure regulation range in the energy dissipation circuit;

[0065] P 0 The maximum test pressure of the tested reciprocating pump 4 is in MPa;

[0066] Q The rated flow rate of the tested reciprocating pump 4 is L / min;

[0067] μ The flow coefficient of the throttling nozzle 17 is preferably in the range of 0.7 to 0.95;

[0068] P t The maximum pressure within the pressure adjustment range corresponding to the pressure level, in MPa;

[0069] No. a Group throttling nozzle 17 corresponds to b Pressure regulation range at pressure level -1;

[0070] The jet outlet velocity of the throttling nozzle 17;

[0071] Jet fluid density (the density of the water sampled in this embodiment).

[0072] The distance between the jet outlet of the throttling nozzle 17 and the energy dissipation cylinder 12 at the starting end S Spacing between the energy dissipation cylinder 12 and the inner sleeve 11 L The spacing between the energy dissipation cylinders 12 in the inner sleeve 11 is equal to the spacing between the cylinders 12 in the inner sleeve 11. L :

[0073] The core jet diameter of the throttling nozzle 17 is ;

[0074] ,in It is the confining pressure of the jet. ;

[0075] but ;

[0076] ;

[0077] Solve the above equations simultaneously, and substitute the values ​​into the equations. S=L ,but:

[0078] ;

[0079] in, P The maximum jet pressure of the throttling nozzle 17 is MPa;

[0080] d The nozzle orifice diameter of the throttling nozzle 17 is in mm;

[0081] k This is an empirical coefficient, and its preferred value range is 1.2 to 1.6;

[0082] x The attenuation ratio is the diameter reduction ratio of the core area of ​​the throttling nozzle 17; in this embodiment, the attenuation ratio is preferably 80%.

[0083] The radial velocity distribution of the jet at section 12 of the energy dissipation cylinder is as follows:

[0084] ;

[0085] h = 0.11 S + 0.145 d ;

[0086] in: The radial position inside section 12 of the energy dissipation cylinder r Axial velocity at the location;

[0087] The maximum axial velocity within the section of the energy dissipation cylinder 12 (located on the jet axis) r =0);

[0088] h For the jet half-width (velocity reduced to) radial distance at time ≈2.718);

[0089] With speed 80% U maxThe diameter of the jet tube 121 is used as the diameter of the jet tube.

[0090] The aperture of the jet tube 121 is D :

[0091] ;

[0092] To achieve a thorough energy dissipation effect, the high-speed water jet flow velocity is gradually reduced to a low-speed (below 5m / s) pipe flow. The number of energy dissipation cylinders 12 is set to 5 to 10 levels according to the pressure and flow rate of the test pump, with more levels for higher pressure and larger flow rate. The spacing design of the subsequent energy dissipation cylinders 12 is as follows: L is set at equal intervals within 100mm, and the spacing can be gradually reduced for levels above 100mm.

[0093] The diameter of the area impacting the energy dissipation cylinder 12, i.e., the jet expansion diameter, is obtained from S. B :

[0094] ;

[0095] The jet diffusion angle is preferably 15°.

[0096] The jet expansion diameter is equal to the outer diameter of the energy dissipation cylinder 12. .

[0097] In a specific case, let's take an experiment with a pump that has an upper limit of 300 MPa and a flow rate of 50 L / min as an example:

[0098] First, based on the pressure regulation upper limit requirement of 300MPa, it was calculated that three pressure levels and two sets of throttling nozzles are needed.

[0099] The pressure ranges corresponding to the three pressure levels are 0~100MPa, 100MPa~200MPa, and 200MPa~300MPa, respectively.

[0100] First, calculate the orifice diameter of the first set of throttling nozzles 17:

[0101] ;

[0102] The first set of throttling nozzles 17 allows the tested reciprocating pump 4 to be throttled and pressurized to approximately 100 MPa when the throttling valve at the front end of the jet energy dissipator 1 is fully open and the throttling valve at the front end of the cooling sleeve 2 is fully closed. At this time, opening the throttling valve at the front end of the cooling sleeve 2 allows some fluid to flow out through it, reducing the pump outlet pressure. When the throttling valve at the front end of the cooling sleeve 2 is fully open, the relative pressure at the pump outlet drops to 0. Therefore, by adjusting the opening of the throttling valve at the front end of the cooling sleeve 2, the pump's test pressure can be infinitely adjusted from 0 to 100 MPa, enabling performance testing under different pressure conditions from 0 to 100 MPa.

[0103] When the throttle valve at the front end of cooling jacket 2 is completely closed, all the pump flow first passes through the throttle valve at the front end of jet energy dissipator 1 and then flows out through jet energy dissipator 1. As mentioned earlier, the pump pressure at this time is approximately 100 MPa. Gradually closing the throttle valve at the front end of jet energy dissipator 1 reduces the valve opening, allowing it to perform its throttling and pressure regulating function. The pump pressure then gradually increases until the opening of the throttle valve at the front end of jet energy dissipator 1 is adjusted to the minimum opening within its effective pressure regulating range (0~100 MPa). At this point, the pump pressure gradually reaches 200 MPa. Therefore, by adjusting the opening of the throttle valve at the front end of jet energy dissipator 1, stepless adjustment of the pump's test pressure from 100 to 200 MPa can be achieved, i.e., performance testing of the pump under different pressure conditions from 100 to 200 MPa can be realized. Through the coordinated adjustment of the two sets of throttle valves, the pressure regulation of the pump's performance test under different pressure conditions from 0 to 200 MPa was experimentally demonstrated.

[0104] If the pump's test pressure exceeds 200 MPa, a smaller orifice nozzle needs to be used. In this case, the orifice diameter of the second set of orifice nozzles 17 is:

[0105] .

[0106] Similar to the above operation method, the throttle valve at the front end of the jet energy dissipator 1 is fully closed, and the opening of the throttle valve at the front end of the cooling sleeve 2 is adjusted to achieve stepless adjustment of the pressure from 0 to 100 MPa. The throttle valve at the front end of the cooling sleeve 2 is closed, and the throttle valve at the front end of the jet energy dissipator 1 is adjusted to achieve stepless adjustment of the pressure from 200 to 300 MPa.

[0107] The design of the jet energy dissipator 1 is calculated based on the highest pressure condition and the last set of throttling nozzles 17. Taking the above calculation as an example, under the conditions of 200MPa and an orifice diameter of 1.45mm, the spacing L of the energy dissipation cylinder 12 is calculated as follows:

[0108] ;

[0109] The aperture of the jet tube 121 of the energy dissipation tube 12 D for:

[0110] ;

[0111] outer diameter =tan 15 °× 46 ＝ 12.3 mm ;

[0112] All calculated values ​​are approximate. In this embodiment, the energy dissipation cylinder 12 is designed with 6 stages, spaced at equal intervals. The arrangement of the outer casing 14 is sufficient to ensure that the discharge water temperature at the low-pressure water outlet is below 45℃.

[0113] The basic principles of this application have been described above with reference to specific embodiments. However, it should be noted that the advantages, benefits, and effects mentioned in this application are merely examples and not limitations, and should not be considered as essential features of each embodiment of this application. Furthermore, the specific details disclosed above are for illustrative and facilitative purposes only, and are not limitations. These details do not limit the application to the necessity of employing the aforementioned specific details for implementation.

[0114] The block diagrams of devices, apparatuses, devices, and systems involved in this application are merely illustrative examples and are not intended to require or imply that they must be connected, arranged, or configured in the manner shown in the block diagrams. As those skilled in the art will recognize, these devices, apparatuses, devices, and systems can be connected, arranged, and configured in any manner. Words such as “comprising,” “including,” “having,” etc., are open-ended terms meaning “including but not limited to,” and are used interchangeably with them. The terms “or” and “and” as used herein refer to the terms “and / or,” and are used interchangeably with them unless the context clearly indicates otherwise. The term “such as” as used herein refers to the phrase “such as but not limited to,” and is used interchangeably with it.

Claims

1. A jet energy dissipator, characterized in that, The jet energy dissipator (1) includes an inner sleeve (11) through which the jet passes. One end of the inner sleeve (11) is coaxially connected to a high-pressure water inlet (18) via a throttling nozzle (17), and the other end of the inner sleeve (11) is connected to a low-pressure water outlet (15). Energy dissipation cylinders (12) for diverting fluid are evenly spaced along the axial direction inside the inner sleeve (11). The energy dissipation cylinder (12) includes a jet cylinder (121) arranged coaxially with the inner sleeve (11). 1) The outer wall is uniformly provided with flow divider blades (122) along the circumference. The inner sleeve (11) and the jet tube (121) are surrounded by each flow divider blade (122) to form a multi-component flow chamber. The fluid passing through each flow divider chamber is guided by the flow divider blades (122) to form a swirling flow that is offset from the jet path passing through the jet tube (121). The swirling flow rate passing through the flow divider blades (122) in each energy dissipation tube (12) is less than the jet flow rate passing through the jet tube (121).

2. The jet energy dissipator according to claim 1, characterized in that, The energy dissipation cylinder (12) and the inner wall of the inner sleeve (11) slide together axially. The energy dissipation cylinder (12) and the connecting sleeve (13) are arranged alternately in the inner sleeve (11). The cavity of the connecting sleeve (13) forms a channel for the fluid discharged from the energy dissipation cylinder (12) to pass through.

3. A jet energy dissipator according to claim 2, characterized in that, A spring (16) is provided axially inside the inner sleeve (11). One end of the spring (16) abuts against the low-pressure water outlet (15), and the other end of the spring (16) abuts against the energy dissipation cylinder (12) on the side of the adjacent low-pressure water outlet (15). The spring (16) applies an elastic clamping force to each energy dissipation cylinder (12) and the connecting sleeve (13).

4. A jet energy dissipator according to claim 1, characterized in that, An outer sleeve (14) is coaxially arranged outside the inner sleeve (11). The outer sleeve (14) and the inner sleeve (11) enclose an annular cooling cavity (143). A cooling water inlet (141) and a cooling water outlet (142) communicating with the cooling cavity (143) are arranged radially on the outer sleeve (14). Along the axial direction of the outer sleeve (14), the cooling water inlet (141) and the cooling water outlet (142) are respectively arranged at both ends of the outer sleeve (14).

5. A jet energy dissipator according to claim 1, characterized in that, The port of the high-pressure water inlet (18) is fixed to the high-pressure filter (172) by a clamping bolt (173), and the high-pressure filter (172) is coaxially fixedly connected to the throttling nozzle (17) through a connecting joint (171).

6. A test system for an adjustable pressure ultra-high pressure reciprocating pump, characterized in that, Along the direction of medium flow, the circulating medium tank (5), the test reciprocating pump (4), the air chamber (3), and the energy dissipation circuit are connected in sequence. The energy dissipation circuit includes a jet energy dissipator (1) and a cooling sleeve (2) as described in any one of claims 1 to 5, which are connected in parallel. Throttling valves are provided at the inlets of the jet energy dissipator (1) and the cooling sleeve (2) to regulate the flow rate. The outlet of the energy dissipation circuit is connected to the inlet of the three-way valve (6). One outlet of the three-way valve (6) is directly connected to the circulating medium tank (5), and the other outlet of the three-way valve (6) is connected to the circulating medium tank (5) after passing through the metering container (7).

7. The adjustable pressure ultra-high pressure reciprocating pump test system according to claim 6, characterized in that, Based on the maximum test pressure of the tested reciprocating pump (4), calculate the number of sets of throttling nozzles (17). a Determine the nozzle orifice diameter of each group of throttling nozzles (17). d ; a = b -1； ； ； in, b The pressure rating of the tested reciprocating pump (4) b It is a positive integer; The pressure ratings of the tested reciprocating pump (4) correspond to different pressure regulation ranges; b The pressure regulation range corresponding to each pressure level is: bPt' ~ ( b -1) Pt' , Pt' The maximum pressure within the regulating range of the two throttle valves in the energy dissipation circuit; P 0 The maximum test pressure of the tested reciprocating pump (4); Q The rated flow rate of the tested reciprocating pump (4); μ The flow coefficient of the throttling nozzle (17); P t This represents the maximum pressure within the pressure adjustment range corresponding to the pressure level.

8. The adjustable pressure ultra-high pressure reciprocating pump test system according to claim 7, characterized in that, The distance between the jet outlet of the throttling nozzle (17) and the energy dissipation cylinder (12) at the starting end is equal to the arrangement spacing of the energy dissipation cylinders (12) in the inner sleeve (11). The arrangement spacing of the energy dissipation cylinders (12) is... L : in, P The maximum jet pressure of the throttling nozzle (17); d The nozzle orifice diameter of the throttling nozzle (17) is calculated based on the orifice diameter under the highest pressure condition; k This is an empirical coefficient; x The core area diameter attenuation ratio of the throttling nozzle (17).

9. The adjustable pressure ultra-high pressure reciprocating pump test system according to claim 8, characterized in that, The aperture of the jet tube (121) in the energy dissipation tube (12) is D : 。 10. The adjustable pressure ultra-high pressure reciprocating pump test system according to claim 6, characterized in that, A temperature sensor is installed at the outlet of the energy dissipation circuit, a temperature sensor and a vacuum pressure gauge are installed at the inlet of the tested reciprocating pump (4), and a throttle valve is installed at the outlet of the circulating medium tank (5). The outlet of the tested reciprocating pump (4) is connected to the circulating medium tank (5) through a safety valve. A level gauge is installed in both the circulating medium tank (5) and the metering container (7). A temperature regulating component (51) for regulating the medium temperature is installed in the circulating medium tank (5).

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