V-type valve port spool valve structure parameter determination method and system based on flow and vibration suppression cooperation

Abstract

The application discloses a V-shaped valve port spool valve structure parameter determination method and system based on flow and vibration suppression cooperation, and the method comprises the following steps: acquiring the valve cavity tail edge wall surface pressure fluctuation time domain signals of a reference structure scheme and a candidate structure scheme respectively to determine the pressure oscillation amplitude, and acquiring the outlet time average flow under the same preset working condition; constructing a unit flow oscillation cost evaluation index by the ratio of the pressure oscillation amplitude to the flow; establishing a dimensionless relative evaluation result by the ratio of the unit flow oscillation cost of the candidate structure scheme to the reference structure scheme, and determining the target structure parameter scheme with the optimal oscillation suppression effect under the premise of maintaining the linear flow characteristics from the candidate structure scheme. Compared with the prior art, the relative degree of oscillation change and flow change is compared, and a basis is provided for the structure parameter determination of the V-shaped valve port spool valve.

Description

Technical Field

[0001] This invention relates to the field of fluid transmission and control technology, and in particular to a method and system for determining the structural parameters of a V-type valve port slide valve based on the synergy of flow passage and vibration suppression. Background Technology

[0002] Spool valves are key throttling and flow regulation components in hydraulic control systems, widely used in engineering machinery, marine hydraulics, and industrial equipment. Among them, V-type spool valves are widely used for controlling the speed and flow of actuators due to their good linearity and strong flow capacity. During operation, the fluid forms a high-speed jet after being throttled through the V-type valve orifice, and the local pressure drops rapidly. This easily induces cavitation downstream of the valve orifice and inside the valve cavity, resulting in a large number of cavitation bubbles in the liquid. During the formation, development, and collapse of these bubbles, pressure pulsation, wall impact, and flow instability can occur. In severe cases, it can even induce cavitation self-excited oscillations, leading to increased noise, intensified vibration, and affecting the flow stability of the spool valve and the reliability of the system.

[0003] To suppress the aforementioned cavitation self-excited oscillations, existing technologies typically adjust the structural parameters of the valve orifice or valve cavity to improve the local flow field. However, the flow capacity and linear flow characteristics of the V-type valve orifice are also determined by these structural parameters. In practical engineering, the following situation often occurs: while adjusting a certain structural parameter reduces the pressure oscillation amplitude, it also leads to a significant decrease in flow capacity, disrupting the original linear flow regulation characteristics of the valve orifice. This results in a significant reduction in the speed and flow control accuracy of the spool valve. Since existing technologies typically aim to suppress cavitation or reduce the pressure oscillation amplitude, they may misjudge structural solutions that sacrifice flow capacity and control characteristics as the preferred options.

[0004] A search revealed Chinese Patent Publication No. CN120745258A, which discloses a method for designing the valve port structure of a surface-sealed cone valve to suppress cavitation surge. This method simulates and calculates the dominant frequency and amplitude of flow field oscillations caused by cavitation surge under different structural parameters. Based on the dominant frequency and amplitude, it calculates the oscillation energy and analyzes the relationship between the valve port cone angle and sealing length and the oscillation energy. Finally, it determines the optimal cone angle and sealing length by combining the changes in valve port flow resistance and the aspect ratio constraint to suppress cavitation surge. However, this method only uses the flow field oscillation energy as a single optimization objective and does not consider the impact of structural parameter changes on the valve port flow capacity. It cannot determine whether the determined structural design maintains the original flow capacity of the valve port while suppressing oscillations, potentially sacrificing flow capacity for oscillation suppression.

[0005] Therefore, when faced with a variety of candidate structural schemes consisting of variations in valve cavity length, valve port wedge angle, and valve port angle, how to objectively determine the structural parameter scheme that can balance the suppression of cavitation self-excited oscillations with the maintenance of flow capacity is a technical problem that needs to be solved. Summary of the Invention

[0006] The purpose of this invention is to overcome the shortcomings of the prior art by providing a method and system for determining the structural parameters of a V-type valve port slide valve based on the synergy of flow passage and vibration suppression.

[0007] The objective of this invention can be achieved through the following technical solutions: According to a first aspect of the present invention, a method for determining the structural parameters of a V-type valve port slide valve based on the synergy of flow passage and vibration suppression is provided, comprising: The pressure pulsation time-domain signal at the tail edge wall of the valve cavity of the hydraulic slide valve reference structure and at least one candidate structure are obtained respectively, and the pressure oscillation amplitude is determined based on the pressure pulsation time-domain signal. The average outlet flow rate of the baseline structural scheme and each candidate structural scheme under the same preset operating conditions is obtained respectively. A unit flow rate oscillation cost evaluation index is constructed based on the ratio of the pressure oscillation amplitude to the outlet hourly flow rate, which is used to characterize the pressure oscillation level of the corresponding structural scheme under unit flow capacity; A relative evaluation result is established based on the ratio of the unit flow oscillation cost evaluation index of the candidate structural scheme to the unit flow oscillation cost evaluation index of the benchmark structural scheme. Based on the relative evaluation results, a target structural parameter scheme is determined from the candidate structural schemes. The target structural parameter scheme is the scheme with the best oscillation suppression effect while maintaining the linear flow characteristics of the slide valve.

[0008] As a preferred technical solution, the same preset operating conditions include the same oil supply pressure, outlet pressure, fluid medium parameters, and valve opening conditions.

[0009] As a preferred technical solution, the candidate structural solutions include solutions with varying valve cavity length, varying valve port wedge angle, and varying valve port angle. Each candidate structural solution is a solution obtained by changing a single structural parameter relative to the reference structural solution.

[0010] As a preferred technical solution, the pressure oscillation amplitude is obtained by performing time-domain amplitude analysis on the pressure pulsation time-domain signal; the outlet time-averaged flow rate is the time-averaged flow rate flowing through the outlet under the preset same operating conditions.

[0011] As a preferred technical solution, the pressure pulsation time-domain signal is acquired by a pressure sensor installed on the tail edge wall of the valve cavity; the outlet time-averaged flow rate is measured by a flow meter installed at the outlet flow channel.

[0012] As a preferred technical solution, the pressure pulsation time-domain signal and the outlet time-averaged flow rate are obtained through an experimentally verified fluid simulation model.

[0013] As a preferred technical solution, the relative evaluation result is calculated as follows: , in, A 0 and Q 0 represents the pressure oscillation amplitude and the outlet hourly flow rate of the aforementioned benchmark structural scheme, respectively. A 1 and Q 1 represents the pressure oscillation amplitude and the outlet hourly flow rate of the candidate structural scheme, respectively.

[0014] As a preferred technical solution, the relative evaluation result being less than 1 is used as a criterion for determining whether the candidate structural scheme is superior to the benchmark structural scheme; the smaller the relative evaluation result, the better the overall performance of the corresponding candidate structural scheme in terms of oscillation suppression effect and linear flow characteristics maintenance.

[0015] As a preferred technical solution, when there are multiple candidate structural schemes with better overall performance than the benchmark structural scheme, the candidate structural schemes are sorted from smallest to largest by the ratio of the pressure oscillation amplitude ratio to the outlet hourly flow rate ratio, and the candidate structural scheme with the smallest ratio is the optimal target structural parameter scheme.

[0016] According to a second aspect of the present invention, a system is provided for determining the structural parameters of a V-type valve port slide valve based on the synergistic effect of flow passage and vibration suppression, comprising: The data acquisition module is used to acquire the time-domain signal of the valve cavity tail edge wall pressure pulsation and the outlet hourly flow rate of the hydraulic slide valve reference structure and at least one candidate structure under the same preset working conditions. The data processing module determines the pressure oscillation amplitude based on the pressure pulsation time-domain signal, and constructs a unit flow oscillation cost evaluation index based on the ratio of the pressure oscillation amplitude to the outlet hourly flow rate. The scheme output module establishes a relative evaluation result based on the ratio of the unit flow oscillation cost evaluation index of the candidate structural scheme to the unit flow oscillation cost evaluation index of the benchmark structural scheme, and determines the target structural parameter scheme from the candidate structural schemes based on the relative evaluation result. The target structural parameter scheme is the scheme with the best oscillation suppression effect while maintaining the linear flow characteristics of the hydraulic slide valve.

[0017] Compared with the prior art, the present invention has the following advantages: 1. This invention obtains the pressure oscillation amplitude and the time-averaged flow rate at the outlet of the V-type valve port slide valve by acquiring the pressure oscillation amplitude to the flow rate as a benchmark for judging the oscillation cost per unit flow rate. Furthermore, it establishes a dimensionless relative index of the candidate structural scheme relative to the benchmark structural scheme, and incorporates the oscillation suppression benefit and the flow capacity loss into a unified dimensional system for comprehensive consideration. This invention can determine the structural parameter scheme that takes into account both the cavitation self-excited oscillation suppression effect and the maintenance of linear flow capacity in an objective and quantitative way, effectively solving the problem in the prior art that it is difficult to objectively determine the optimal structural parameters due to the lack of comprehensive judgment basis.

[0018] 2. This invention uses the ratio of pressure oscillation amplitude to flow rate as the judgment criterion, and establishes a dimensionless relative index based on this criterion with the benchmark scheme as a reference. This gives the results a clear physical meaning and a unified judgment boundary, which can objectively reflect the pressure oscillation level of each candidate structural scheme under unit flow capacity. This avoids the misjudgment caused by the traditional single index judgment method that only focuses on the oscillation amplitude and ignores the change in flow capacity. At the same time, it overcomes the defects of the weighted comprehensive judgment method, which is highly subjective in weight setting and the results are unstable with the change of weight. This improves the consistency and reliability of structural parameter determination.

[0019] 3. This invention establishes a dimensionless relative index by using the unit flow oscillation cost of the benchmark structural scheme as a reference, so that the judgment boundary is naturally determined to be 1 by the normalization relationship. The judgment process is driven by the physical response data of each structural scheme under the same preset working conditions, avoiding the interference of human factors on the results and ensuring objectivity and reproducibility.

[0020] 4. This invention acquires the time-domain signal of pressure pulsation on the tail edge wall of the valve cavity and the outlet flow data through physical hardware such as pressure sensors and flow meters, or obtains the above data through experimentally verified fluid simulation models. It can adapt to the needs of different implementation scenarios and has flexible data acquisition methods. Attached Figure Description

[0021] Figure 1 This is a flowchart of the method of the present invention; Figure 2 This is a schematic diagram of the reference structure of the valve port and valve chamber of a hydraulic spool valve, in which... Figure 2 (a) is the main view. Figure 2 (b) is a sectional view; Figure 3 This is a graph showing the change in pressure on the tail edge wall of the valve cavity over time under different valve cavity lengths in an embodiment of the present invention. Figure 4 This is a graph showing the change in pressure on the valve cavity trailing edge wall over time under different valve port wedge angles in an embodiment of the present invention. Figure 5This is a graph showing the change in pressure on the valve cavity trailing edge wall over time under different valve orifice angles in an embodiment of the present invention. Figure 2 The following are indicated by the numbers: 1. V-groove wedge angle; 2. Valve block; 3. Valve core; 4. Tail edge wall; 5. Valve cavity length; 6. Oil inlet channel; 7. Oil outlet channel; 8. V-groove included angle. Detailed Implementation

[0022] 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, not all, of the embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort should fall within the scope of protection of the present invention.

[0023] Example 1: like Figure 1 As shown, the present invention provides a method for determining the structural parameters of a V-type valve port slide valve based on the synergy of flow passage and vibration suppression, which is used to determine the structural parameter scheme that can take into account both the cavitation self-excited oscillation suppression effect and the maintenance of linear flow passage capacity among multiple candidate structural schemes.

[0024] Among them, such as Figure 2 As shown, the hydraulic spool valve includes a valve block 2, a valve core 3, an oil inlet channel 6, and an oil outlet channel 7. A V-groove is provided at the valve port, and the V-groove has a wedge angle 1 and an included angle 8. The valve cavity has a cavity length 5, and the tail edge wall 4 of the valve cavity serves as the monitoring position for pressure oscillation signals. Among them, the wedge angle 1 is the valve port wedge angle, and the included angle 8 is the valve port angle.

[0025] The method of the present invention includes: Step S1: Obtain the time-domain signal of the pressure pulsation on the valve cavity tail edge wall under the same preset working conditions for the hydraulic slide valve reference structure scheme and at least one candidate structure scheme, and determine the pressure oscillation amplitude based on the pressure pulsation time-domain signal.

[0026] Step S2: Obtain the average outlet flow rate of the baseline structural scheme and each candidate structural scheme under the preset operating conditions.

[0027] Step S3: Construct a unit flow rate oscillation cost evaluation index based on the ratio of the pressure oscillation amplitude to the outlet hourly flow rate. The unit flow rate oscillation cost evaluation index is used to characterize the pressure oscillation level of the corresponding structural scheme under unit flow capacity.

[0028] Step S4: Establish a relative evaluation result based on the ratio of the unit flow oscillation cost evaluation index of the candidate structural scheme to the unit flow oscillation cost evaluation index of the benchmark structural scheme.

[0029] Step S5: Based on the relative evaluation results, determine the target structural parameter scheme from the candidate structural schemes. The target structural parameter scheme is the scheme with the best oscillation suppression effect while maintaining the linear flow characteristics of the hydraulic slide valve.

[0030] The steps of this invention will be described in detail below.

[0031] Step S101: Acquire the pressure pulsation time domain signal and determine the pressure oscillation amplitude.

[0032] First, the baseline and candidate structural designs for the hydraulic spool valve are determined. The baseline structural design is the V-type valve spool valve structure already used in the prior art, and its specific geometric parameters are determined according to the actual application scenario. The candidate structural designs are obtained by changing local structural parameters based on the baseline structural design. The candidate structural designs include at least one of the following: a structural design with varying valve cavity length, a structural design with varying valve port wedge angle, and a structural design with varying valve port angle. Preferably, each candidate structural design is obtained by changing a single structural parameter relative to the baseline structural design, so as to quantitatively analyze the impact of single parameter changes on oscillation characteristics and flow capacity.

[0033] Specifically, the baseline structural design uses a valve port angle of 90° and a valve port wedge angle of 17°. Candidate structural designs include designs with varying valve cavity length, varying valve port wedge angles, and varying valve port angles. The varying valve port wedge angle design can use 8° and 4° wedge angle structures, while the varying valve port angle design can use 75° and 60° valve port angle structures. These parameters are illustrative examples and can be determined based on the specific valve type and operating conditions in actual applications.

[0034] To ensure the comparability of evaluation results among different structural schemes, the preset operating conditions include the same oil supply pressure, outlet pressure, fluid medium parameters, and valve opening conditions. That is, under the same oil supply pressure, outlet pressure, fluid medium, and valve opening, data are acquired for the benchmark structural scheme and each candidate structural scheme.

[0035] Methods for acquiring time-domain signals of pressure pulsations include: Obtained through physical experiments, such as Figure 2 As shown, pressure sensors are installed at four points on the tail edge wall of the hydraulic spool valve to collect the time-domain signal of the pressure change at these points over time in real time. By directly measuring the wall pressure through the pressure sensors, the pressure pulsation characteristics inside the valve cavity can be accurately reflected. First, a three-dimensional fluid simulation model of the hydraulic spool valve is established using experimentally validated fluid simulation models. This model, based on computational fluid dynamics, numerically simulates the flow field in the valve port and valve cavity regions. To ensure the accuracy of the simulation results, the model needs to be experimentally validated, i.e., calibrated and verified using physical experimental data. Only after the validation results show that the simulation model can accurately reflect the flow characteristics and cavitation oscillation response of the hydraulic spool valve can it be used for subsequent data acquisition. Data obtained through experimentally validated simulation models allows for rapid evaluation of various structural schemes without the need for actual prototype fabrication, reducing the time and material costs of structural optimization.

[0036] After obtaining the time-domain signal of pressure pulsation, time-domain amplitude analysis is performed on the signal to determine the pressure oscillation amplitude. Specifically, for the acquired time-domain signal showing pressure changes over time, the peak and trough values ​​within the steady-state period are extracted, and the peak-to-peak value or the fluctuation amplitude relative to the time-averaged pressure is calculated as the pressure oscillation amplitude A of this structural scheme. The magnitude of the pressure oscillation amplitude directly reflects the strength of cavitation self-excited oscillation; the larger the amplitude, the more intense the wall impact caused by cavitation bubble collapse, and the more unstable the flow.

[0037] The acquired pressure pulsation time-domain signal can be plotted as a pressure-time curve, such as... Figure 3 , Figure 4 , Figure 5 As shown: Figure 3 The time-domain curves of the valve chamber trailing edge wall pressure for different valve chamber lengths are shown. Figure 4 The pressure time-domain curves are for different valve wedge angles. Figure 5 The figures show the pressure-time domain curves corresponding to different valve orifice angles. Multiple curves in each figure represent the pressure fluctuation process under changes in a single structural parameter. By comparing the peak and trough fluctuation amplitudes of the curves, the magnitude of pressure oscillation amplitude under different structural schemes can be intuitively distinguished, allowing for rapid qualitative judgment of the strength of cavitation self-excited oscillation. Figure 3 Different line types represent different valve chamber lengths L; Figure 4 Different line types represent different wedge angles θ; Figure 5 Different line shapes represent different valve orifice angles. The greater the fluctuation range of the curve, the greater the corresponding pressure oscillation amplitude A, and the more intense the cavitation self-excited oscillation.

[0038] Step S201: Obtain the average flow rate at the exit point.

[0039] The average time-of-flow rate at the outlet of the baseline structural design and each candidate structural design is obtained under the preset operating conditions. The average time-of-flow rate at the outlet is the time-averaged flow rate through the outlet channel 7 under the preset operating conditions. That is, under the same oil supply pressure, outlet pressure, and valve opening, after the flow reaches a steady state, the average time-of-flow rate of the outlet is taken over a preset time period to obtain the effective flow capacity Q of the structural design under that operating condition. A larger average time-of-flow rate at the outlet indicates a stronger flow capacity of the structural design.

[0040] The method for obtaining flow data corresponds to the method for obtaining pressure data in step S101: in the physical experiment method, it is obtained by measuring with a flow meter set at the outlet flow channel; in the simulation method, the volumetric flow rate is obtained by integrating the flow velocity at the outlet section in the simulation model and then taking the time average.

[0041] Step S301: Construct an evaluation index for the unit flow oscillation cost.

[0042] A unit flow rate oscillation cost evaluation index R is constructed based on the ratio of the pressure oscillation amplitude to the average outlet flow rate. , The unit flow oscillation cost evaluation index R is used to characterize the pressure oscillation level of the corresponding structural scheme under unit flow capacity.

[0043] Since the goal of optimizing the V-type valve orifice slide valve structure is not simply to reduce the pressure oscillation amplitude A, but to reduce cavitation self-excited oscillation while maintaining the valve orifice flow capacity and linear flow regulation capability, if A and Q are considered separately, a pseudo-optimization situation may occur where the amplitude is reduced but the flow rate is reduced even more. Therefore, this invention defines the ratio of A to Q as the unit flow oscillation cost. The larger A is, the stronger the oscillation (the greater the cost), and the larger Q is, the stronger the flow capacity (the greater the benefit). Dividing A by Q can directly characterize how much pressure oscillation needs to be withstood to obtain 1 unit flow capacity. The smaller this ratio is, the more the structural scheme obtains a larger flow capacity with a smaller oscillation cost, and the better the overall performance.

[0044] This step uses a ratio instead of addition, subtraction, or empirical weighting for the following reasons: A and Q correspond to the cost and benefit terms in structural optimization, respectively. Dividing A by Q aligns with the physical evaluation logic of obtaining greater flow capacity with less oscillation cost. If A and Q are directly added or subtracted, their dimensions and physical meanings differ, lacking a clear physical interpretation. If a weighted sum is used, weights need to be manually set, and the ranking of candidate structural schemes may change with weight variations, resulting in a lack of objectivity in the evaluation results. Therefore, the A / Q ratio reduces the influence of subjective weights and more objectively reflects the comprehensive performance of each structural scheme.

[0045] Step S401: Establish relative evaluation results.

[0046] A relative evaluation result is established based on the ratio of the unit flow oscillation cost evaluation index of the candidate structural scheme to that of the benchmark structural scheme. : , in, A 0 and Q 0 represents the pressure oscillation amplitude and the average outlet flow rate of the baseline structural scheme, respectively. A 1 and Q 1 represents the pressure oscillation amplitude and the outlet hourly flow rate of the candidate structural schemes, respectively.

[0047] Under the same preset operating conditions, the absolute value of A / Q can be used directly to rank the various structural schemes. However, the magnitude of this absolute value is affected by the dimensions, units of measurement, and specific operating parameters, making it difficult to establish a unified boundary of absolute superiority or inferiority. This embodiment uses the unit flow oscillation cost of the benchmark structural scheme. As a normalization reference, the candidate structural schemes Converting to a dimensionless relative evaluation index, this normalization process does not change the relative ranking of each candidate structural scheme according to the unit flow oscillation cost, but enables the evaluation results to directly represent the change multiple of the candidate structural scheme relative to the benchmark structural scheme, thereby improving the interpretability of the evaluation results and the convenience of comparison between schemes with different structural parameters.

[0048] Step S501: Determine the target structural parameter scheme.

[0049] Since the ratio of the baseline structural scheme to its own unit flow oscillation cost is always equal to 1, it constitutes an equivalent criterion boundary naturally determined by the normalization relation, rather than a threshold artificially set based on experience. A value less than 1 is used as a criterion for determining whether a candidate structural scheme is superior to the baseline structural scheme, and The smaller the value, the better the overall performance of the corresponding candidate structure in terms of oscillation suppression and preservation of linear flow characteristics. When = 1, it indicates that the candidate structural scheme and the benchmark structural scheme have the same unit flow oscillation cost, and their effects are comparable in this evaluation dimension; when When the value is greater than 1, it indicates that the unit flow oscillation cost of the candidate structural scheme is higher than that of the benchmark structural scheme, and its overall effect is not better than that of the benchmark structural scheme.

[0050] It should be pointed out that when When the value is greater than 1, the pressure oscillation amplitude and the outlet hourly average flow rate of the candidate structural scheme are both lower than those of the benchmark structural scheme (i.e., A 1< A 0 andQ 1< Q 0), In this case, if only the pressure oscillation amplitude is used as the evaluation index, it would be concluded that this scheme is superior to the benchmark scheme, but the present invention Able to correctly reveal, when When the value is greater than 1, it indicates that the relative reduction in flow capacity is greater than the relative reduction in pressure oscillation amplitude. In other words, this scheme sacrifices flow capacity excessively in exchange for oscillation suppression, and therefore should not be selected as the target structural parameter scheme.

[0051] The method of the present invention described above will be explained in conjunction with specific embodiments below.

[0052] Combination Figure 4 , Figure 5 The pressure pulsation time-domain curves allow for a direct observation of the difference in pressure fluctuation amplitude between the two schemes, which can then be quantitatively calculated. The comprehensive evaluation was completed, and the specific values ​​are as follows: In one embodiment, the candidate structural scheme with the valve port angle maintained at 90° and the valve port wedge angle reduced from 17° to 4° has a pressure oscillation amplitude of 21.43% of the benchmark structural scheme, i.e., a pressure oscillation amplitude reduction of 78.57%, and an outlet hourly average flow rate of 6.62% of the benchmark structural scheme, i.e., an outlet hourly average flow rate reduction of 93.38%. Substituting... Calculation formula: =0.2143×1 / 0.0662=3.2357>1. This result indicates that although the pressure oscillation amplitude of this scheme is significantly reduced, the relative reduction in its flow capacity is far greater than the relative reduction in the oscillation amplitude. Sacrificing most of the flow capacity for oscillation suppression should not be considered as the preferred scheme.

[0053] In another embodiment, a candidate structural design where the valve port wedge angle is maintained at 17° and the valve port angle is reduced from 90° to 60° has a pressure oscillation amplitude of 29.47% of the baseline structural design, a reduction of 70.53%, and an outlet hourly average flow rate of 55.33% of the baseline structural design, a reduction of 44.67%. Calculation formula: =0.2947×1 / 0.5533=0.5326<1. This result shows that the relative reduction in pressure oscillation amplitude of the proposed scheme is greater than the relative reduction in outlet average flow rate (44.67%). It achieves significant oscillation suppression while maintaining most of the flow capacity. Its overall performance is better than the benchmark structural scheme and can be used as the preferred target structural parameter scheme.

[0054] Using the above methods, we can analyze the influence of changes in valve cavity length, valve port wedge angle, and valve port angle on the suppression effect and flow capacity of cavitation self-excited oscillation of hydraulic spool valves. Based on this, we can sort and screen different candidate structural schemes and finally determine the target structural parameter scheme with the best oscillation suppression effect while maintaining linear flow characteristics.

[0055] In a weighted two-factor evaluation method, the pressure oscillation amplitude retention rate and the outlet hourly average flow loss rate are weighted and summed. The weighted two-factor evaluation value is defined. : , in, Assign weights to the pressure oscillation indicator. The smaller the value, the better the evaluation result.

[0056] when At this point, the weighted evaluation values ​​for the valve orifice wedge angle reduction scheme and the valve orifice angle reduction scheme are 0.5741 and 0.3707, respectively, indicating that the valve orifice angle reduction scheme has a better evaluation result. At this point, the weighted evaluation values ​​for the two schemes are 0.2863 and 0.3099, respectively, indicating that the scheme with reduced valve wedge angle has a better evaluation result. This demonstrates that the ranking of schemes in the weighted two-factor evaluation method may change depending on the weight values.

[0057] The method of this invention integrates the gains from oscillation suppression and the loss of flow capacity into a unified physical dimension system for comprehensive analysis. This effectively identifies pseudo-optimal schemes that sacrifice flow capacity excessively to achieve oscillation suppression, overcoming the misjudgment defects of traditional single-index evaluation or subjective weighted evaluation methods. It provides an objective and quantitative basis for determining the structural parameters of V-type valve slide valves under linear flow characteristic constraints.

[0058] Example 2: This invention provides an optimized system for suppressing oscillations in a V-type valve orifice slide valve that also considers linear flow characteristics, used to execute the method described in Example 1. The system includes: The data acquisition module is used to acquire the time-domain signal of the pressure pulsation on the tail edge wall of the hydraulic slide valve and at least one candidate structural scheme under the same preset working conditions, as well as the outlet hourly flow rate.

[0059] Preferably, the data acquisition module includes a pressure sensor disposed on the tail edge wall of the valve cavity and a flow meter disposed on the outlet flow channel, which are used to acquire the pressure pulsation time-domain signal and measure the outlet flow rate in real time, respectively. The data acquisition module can also be an experimentally verified fluid simulation model, which can obtain the corresponding pressure pulsation time-domain signal and the outlet time-averaged flow rate by performing numerical simulation on the benchmark structural scheme and each candidate structural scheme. The above two implementation methods can be used in one of them or can be mutually verified.

[0060] The same preset operating conditions include the same oil supply pressure, outlet pressure, fluid medium parameters, and valve opening conditions.

[0061] The data processing module determines the pressure oscillation amplitude based on the pressure pulsation time-domain signal, and constructs a unit flow oscillation cost evaluation index based on the ratio of the pressure oscillation amplitude to the outlet hourly average flow rate.

[0062] Specifically, the data processing module performs time-domain amplitude analysis on the received pressure pulsation time-domain signal, extracting the pressure fluctuation amplitude within the steady-state time period as the pressure oscillation amplitude A for this structural scheme; simultaneously, the data processing module records or calculates the received outlet hourly average flow rate data Q. Then, the data processing module calculates the ratio of A to Q to obtain the unit flow oscillation cost evaluation index R=A / Q for each structural scheme.

[0063] The design principle of the data processing module for constructing the A / Q ratio evaluation index is explained in detail in step S3 of Example 1, and will not be repeated here.

[0064] The scheme output module is used to establish a relative evaluation result based on the ratio of the unit flow oscillation cost evaluation index of the candidate structural scheme to the unit flow oscillation cost evaluation index of the benchmark structural scheme, and to determine the target structural parameter scheme from the candidate structural schemes based on the relative evaluation result. The target structural parameter scheme is the scheme with the best oscillation suppression effect while maintaining the linear flow characteristics of the hydraulic slide valve.

[0065] Specifically, the scheme output module evaluates the unit flow oscillation cost of each candidate structural scheme. R 1 Evaluation index of unit flow oscillation cost compared with the benchmark structural scheme R 0 Dividing them yields the dimensionless relative evaluation index. R norm Then, the solution output module, based on... R norm The candidate structural schemes are filtered based on whether the value is less than 1: R normCandidate structural schemes with a value less than 1 and smaller values ​​indicate that they have better overall performance in terms of oscillation suppression and preservation of linear flow characteristics. These schemes are determined as the target structural parameter schemes and output. R norm Candidate structural schemes with a value greater than 1 were excluded.

[0066] Preferably, the scheme output module further includes a display unit, which is used to visualize the pressure oscillation amplitude, outlet hourly flow rate, unit flow oscillation cost evaluation index and relative evaluation results of each candidate structural scheme in the form of a list or chart, so that engineering technicians can intuitively compare the comprehensive performance of different structural schemes.

[0067] In actual physical implementation, the above modules can be integrated into the same computing device or distributed across different computing devices to work together via wired or wireless communication.

[0068] The system of this invention provides an objective and efficient systematic tool for the structural optimization design of V-type valve port slide valves, avoiding the problems of low efficiency and easy misjudgment of traditional manual experience judgment or simulation trial and error methods, while effectively avoiding the technical defects of unstable evaluation results due to weight setting.

[0069] The above description is merely a specific embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any person skilled in the art can easily conceive of various equivalent modifications or substitutions within the technical scope disclosed in the present invention, and these modifications or substitutions should all be covered within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be determined by the scope of the claims.

Claims

1. A method for determining the structural parameters of a V-type valve orifice slide valve based on the synergy of flow passage and vibration suppression, characterized in that, include: The pressure pulsation time-domain signal at the tail edge wall of the valve cavity of the hydraulic slide valve reference structure and at least one candidate structure are obtained respectively, and the pressure oscillation amplitude is determined based on the pressure pulsation time-domain signal. The average outlet flow rate of the baseline structural scheme and each candidate structural scheme under the same preset operating conditions is obtained respectively. A unit flow rate oscillation cost evaluation index is constructed based on the ratio of the pressure oscillation amplitude to the outlet hourly flow rate, which is used to characterize the pressure oscillation level of the corresponding structural scheme under unit flow capacity; A relative evaluation result is established based on the ratio of the unit flow oscillation cost evaluation index of the candidate structural scheme to the unit flow oscillation cost evaluation index of the benchmark structural scheme. Based on the relative evaluation results, a target structural parameter scheme is determined from the candidate structural schemes. The target structural parameter scheme is the scheme with the best oscillation suppression effect while maintaining the linear flow characteristics of the slide valve.

2. The method for determining the structural parameters of a V-type valve port slide valve based on the synergy of flow passage and vibration suppression as described in claim 1, characterized in that, The same preset operating conditions include the same oil supply pressure, outlet pressure, fluid medium parameters, and valve opening conditions.

3. The method for determining the structural parameters of a V-type valve port slide valve based on the synergy of flow passage and vibration suppression as described in claim 1, characterized in that, The candidate structural schemes include schemes with varying valve cavity length, schemes with varying valve port wedge angle, and schemes with varying valve port angle. Each candidate structural scheme is a scheme obtained by changing a single structural parameter relative to the reference structural scheme.

4. The method for determining the structural parameters of a V-type valve port slide valve based on the synergy of flow passage and vibration suppression as described in claim 1, characterized in that, The pressure oscillation amplitude is obtained by performing time-domain amplitude analysis on the pressure pulsation time-domain signal; The time-averaged flow rate at the outlet is the average flow rate over time under the same preset operating conditions.

5. The method for determining the structural parameters of a V-type valve port slide valve based on the synergy of flow passage and vibration suppression as described in claim 1, characterized in that, The pressure pulsation time-domain signal is acquired by a pressure sensor installed on the tail edge wall of the valve cavity; the outlet time-averaged flow rate is measured by a flow meter installed at the outlet flow channel.

6. The method for determining the structural parameters of a V-type valve port slide valve based on the synergy of flow passage and vibration suppression as described in claim 1, characterized in that, The pressure pulsation time-domain signal and the outlet time-averaged flow rate were obtained through an experimentally verified fluid simulation model.

7. The method for determining the structural parameters of a V-type valve port slide valve based on the synergy of flow passage and vibration suppression as described in claim 1, characterized in that, The relative evaluation result is calculated as follows: ， in, A 0 and Q 0 represents the pressure oscillation amplitude and the outlet hourly flow rate of the aforementioned benchmark structural scheme, respectively. A 1 and Q 1 represents the pressure oscillation amplitude and the outlet hourly flow rate of the candidate structural scheme, respectively.

8. The method for determining the structural parameters of a V-type valve port slide valve based on the synergy of flow passage and vibration suppression as described in claim 7, characterized in that, The relative evaluation result being less than 1 is used as the criterion for determining whether the candidate structural scheme is superior to the benchmark structural scheme; The smaller the relative evaluation result, the better the overall performance of the corresponding candidate structure scheme in terms of oscillation suppression effect and preservation of linear flow characteristics.

9. The method for determining the structural parameters of a V-type valve port slide valve based on the synergy of flow passage and vibration suppression as described in claim 1, characterized in that, When there are multiple candidate structural schemes with better overall performance than the benchmark structural scheme, they are sorted from smallest to largest by the ratio of the pressure oscillation amplitude ratio to the outlet hourly flow rate ratio of each candidate structural scheme, and the candidate structural scheme with the smallest ratio is the optimal target structural parameter scheme.

10. A system for implementing the method for determining the structural parameters of a V-type valve port slide valve based on the synergy of flow passage and vibration suppression as described in any one of claims 1-9, characterized in that, include: The data acquisition module is used to acquire the time-domain signal of the valve cavity tail edge wall pressure pulsation and the outlet hourly flow rate of the hydraulic slide valve reference structure and at least one candidate structure under the same preset working conditions. The data processing module determines the pressure oscillation amplitude based on the pressure pulsation time-domain signal, and constructs a unit flow oscillation cost evaluation index based on the ratio of the pressure oscillation amplitude to the outlet hourly flow rate. The scheme output module establishes a relative evaluation result based on the ratio of the unit flow oscillation cost evaluation index of the candidate structural scheme to the unit flow oscillation cost evaluation index of the benchmark structural scheme, and determines the target structural parameter scheme from the candidate structural schemes based on the relative evaluation result. The target structural parameter scheme is the scheme with the best oscillation suppression effect while maintaining the linear flow characteristics of the hydraulic slide valve.

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