A kind of anti-shake system applied to load sensitive proportional multi-way valve

Abstract

The application relates to the technical field of hydraulic control, in particular to a jitter prevention system applied to a load-sensitive proportional multi-way valve, which controls the flow supply of a hydraulic system through the opening change of a pressure compensator, the pressure compensator is driven by an initial pressure P1 collected at a load-sensitive signal LS collection point, the initial pressure P1 presents irregular sawtooth fluctuation; the initial pressure P1 is subjected to filtering and voltage stabilizing treatment through an S-shaped damping bridge circuit, the S-shaped damping bridge circuit converts the fluctuating initial pressure P1 into stable target pressure P4, so as to drive the pressure compensator to smoothly act, and realize the continuous and stable supply of system flow.

Description

Technical Field

[0001] This invention relates to the field of hydraulic control technology, and in particular to an anti-shake system for load-sensitive proportional multi-way valves. Background Technology

[0002] Load-sensitive proportional multi-way valves in hydraulic systems are widely used in construction machinery, agricultural machinery, and industrial hydraulic equipment. Their core function is to dynamically adjust flow distribution according to load demand to improve system efficiency and control accuracy. However, in practical applications, the initial pressure acquired by the load-sensitive signal often exhibits irregular sawtooth-like fluctuations.

[0003] In existing technology, the opening degree of the pressure compensator determines the system flow supply. The first pressure fluid is the pressure collected by the load-sensitive signal LS, which serves as the initial pressure P and controls the opening degree of the pressure compensator. The state of the initial pressure P is as follows: Figure 1 One of the ones shown is or is Figure 1 Any combination of the three states shown will exhibit irregular, sawtooth-like fluctuations.

[0004] Therefore, it is evident that existing technologies have at least the following problems:

[0005] The pressure acting on the pressure compensator in an irregular sawtooth-like fluctuation state will cause the pressure compensator to jump irregularly, which in turn leads to unstable flow into the system, and the final phenomenon is continuous shaking during load operation. Summary of the Invention

[0006] In view of this, the purpose of this invention is to propose an anti-shake system for load-sensitive proportional multi-way valves to solve the problem of continuous shaking during load operation.

[0007] To achieve the above objectives, the present invention provides an anti-jitter system for load-sensitive proportional multi-way valves, comprising:

[0008] The load-sensitive signal LS acquisition point is located on the fluid pressure lead-out pipeline of the actuator movement, and is used to acquire the initial pressure P1. The lead-out pipeline is connected in sequence to fixed damper one, fixed damper two, check valve one and pressure compensator to form the first flow channel.

[0009] A pressure compensator is used to control the flow supply of a hydraulic system by changing the opening degree. The pressure compensator is driven by an initial pressure P1 collected at the load-sensitive signal LS acquisition point. The initial pressure P1 fluctuates irregularly in a sawtooth pattern.

[0010] The S-type damping bridge circuit, connected between the fixed damper and the one-way valve, includes a D-type half-bridge circuit and a C-type half-bridge circuit. It is used to filter and stabilize the initial pressure P1. The S-type damping bridge circuit converts the fluctuating initial pressure P1 into a stable target pressure P4 to drive the pressure compensator to operate smoothly and achieve a continuous and stable supply of system flow.

[0011] Optionally, the S-type damping bridge circuit includes a D-type half-bridge circuit and a C-type half-bridge circuit connected in parallel:

[0012] The D-type half-bridge circuit includes fixed damping valve II, fixed damping valve IV, check valve II, and check valve I;

[0013] The C-type half-bridge circuit includes a variable damping valve III, a fixed damping valve IV, a one-way valve II, and a one-way valve I.

[0014] Optionally, the D-type half-bridge circuit includes:

[0015] Fixed damper 2 and fixed damper 4 are used to sequentially allow the second pressure fluid between fixed damper 1 (201) and fixed damper 2 (301) to pass through, and to collect the pressure P3 of the third pressure fluid between fixed damper 2 (301) and fixed damper 4 (701) between fixed damper 2 and fixed damper 4.

[0016] One-way valve one is used to allow a third pressure fluid to pass between the fixed damper two (301) and the fixed damper four (701) to form a fourth pressure fluid, which flows to the pressure compensator.

[0017] Optionally, the characteristic of the D-type half-bridge circuit is that the ratio of the third pressure fluid to the second pressure fluid is constant, and the fourth pressure fluid changes linearly proportionally to the second pressure fluid.

[0018] Optionally, the C-type half-bridge circuit includes:

[0019] When the third pressure fluid in the D-type half-bridge circuit is less than the fourth pressure fluid, the one-way valve one is shut off, and the fourth pressure fluid acts in the opposite direction to the third pressure fluid through the variable damper three and the fixed damper four.

[0020] When the third pressure fluid is greater than the fourth pressure fluid, check valve one opens, and the third pressure fluid is output as the fourth pressure fluid through check valve one.

[0021] Optionally, the system pressure relationship is as follows:

[0022]

[0023] Where: P pil Where P is the initial pressure, R is the stability coefficient, and P is the initial pressure. setSet the pressure for the pressure compensator, where P is the system pressure.

[0024] Pressure compensator stability coefficient R when the system is not started Geom =A pilot / A load A pilot A is the projected area of ​​the pressure compensator under the initial pressure. load The projected area of ​​the actuator under load pressure;

[0025] After starting this system, the stability coefficient of the pressure compensator ;

[0026] Adjustment factor λ = (A2) 2 +A4 2 ) / A2 2 ,λ>1, where A2 is the projected area of ​​fixed damper II; A4 is the projected area of ​​fixed damper IV;

[0027] The pressure compensator's action is subject to a time lag compared to the load pressure change, causing the pressure compensator's response to lag behind the initial pressure change.

[0028] Optionally, the S-type damping bridge circuit includes:

[0029] Pressure rise phase: The initial pressure P1 continues to increase, and after being filtered by a fixed damper, it forms a second pressure fluid. Under the action of the D-type half-bridge circuit, the fourth pressure fluid increases linearly, driving the pressure compensator to increase proportionally, and the system flow rate increases proportionally accordingly.

[0030] Pressure drop phase: The initial pressure P1 continues to decrease, and after being filtered by a fixed damper, it forms a second pressure fluid. Under the action of the D-type half-bridge circuit, the fourth pressure fluid decreases linearly, driving the pressure compensator to reduce its opening ratio, and the system flow rate decreases proportionally accordingly.

[0031] Negative pressure fluctuation stage: The initial pressure P1 decreases instantaneously, causing the pressure P3 of the third pressure fluid to be less than the pressure P4 of the fourth pressure fluid. The check valve shuts off, and under the action of the C-type half-bridge circuit, the opening of the pressure compensator is suppressed to reduce suddenly, thus avoiding a sudden drop in system flow.

[0032] During the positive pressure fluctuation phase: The initial pressure P1 increases instantaneously, causing the pressure P3 of the third pressure fluid to be greater than the pressure P4 of the fourth pressure fluid. Once the check valve opens, under the action of the C-type half-bridge circuit, the opening of the pressure compensator is suppressed, thus preventing a sudden increase in the system flow.

[0033] Optionally, the one-way valve one and one-way valve two are used to achieve one-way flow of pressure fluid to prevent the pressure compensator from malfunctioning due to backflow of pressure in the circuit.

[0034] Optionally, the variable damping is used to dynamically adjust the loop damping when the initial pressure P1 fluctuates, thereby extending the response time of the pressure compensator and stabilizing the opening change.

[0035] Optionally, the fixed damper is used for primary filtering of the initial pressure P1 to reduce the high-frequency components of pressure fluctuations and reduce the impact on the control loop.

[0036] The beneficial effects of this invention are as follows: An anti-shake system applied to a load-sensitive proportional multi-way valve controls the flow supply of the hydraulic system by compensating for changes in opening pressure. The pressure compensator is driven by an initial pressure P1 acquired at the load-sensitive signal LS acquisition point, and the initial pressure P1 fluctuates irregularly in a sawtooth pattern. The initial pressure P1 is filtered and stabilized by an S-type damping bridge circuit, which converts the fluctuating initial pressure P1 into a stable target pressure P4 to drive the pressure compensator to operate smoothly, thereby achieving a continuous and stable supply of system flow. Attached Figure Description

[0037] To more clearly illustrate the technical solutions in this invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only for this invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0038] Figure 1 This is a schematic diagram illustrating the fluctuation of initial pressure over time in the background technology.

[0039] Figure 2 This is a schematic diagram of the prior art in the background section;

[0040] Figure 3 The graph shows the change of initial pressure over time in Stage 1 of the background technology.

[0041] Figure 4 The graph shows the change of initial pressure over time in stage 2 of the background technology.

[0042] Figure 5 The graph shows the change of initial pressure over time in stage 3 of the background technology.

[0043] Figure 6 The graph shows the change of initial pressure over time in stage 4 of the background technology.

[0044] Figure 7 This is a schematic diagram of an anti-shake system applied to a load-sensitive proportional multi-way valve according to a specific embodiment of the present invention;

[0045] Figure 8This is a comparison curve of the pressure response before and after stabilization of an anti-shake system applied to a load-sensitive proportional multi-way valve, according to a specific embodiment of the present invention.

[0046] Figure 9 This is a schematic diagram illustrating the time lag in the response of a pressure compensator to a load-sensitive proportional multi-way valve anti-shake system, as described in a specific embodiment of the present invention, compared to load changes.

[0047] Figure 10 The diagram shows the characteristic curve of a D-type half-bridge circuit in an anti-shake system applied to a load-sensitive proportional multi-way valve, according to a specific embodiment of the present invention.

[0048] Figure 11 The diagram shows the characteristic curve of a C-type half-bridge circuit in an anti-shake system applied to a load-sensitive proportional multi-way valve, according to a specific embodiment of the present invention.

[0049] The diagram is marked as follows:

[0050] 101. Load-sensitive signal LS acquisition point; 201. Fixed damper one; 301. Fixed damper two; 401. Check valve one; 501. Variable damper three; 601. Pressure compensator; 701. Fixed damper four; 801. Check valve two. Detailed Implementation

[0051] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below with reference to specific embodiments.

[0052] It should be noted that, unless otherwise defined, the technical or scientific terms used in this invention should have the ordinary meaning understood by one of ordinary skill in the art to which this invention pertains. The terms "first," "second," and similar terms used in this invention do not indicate any order, quantity, or importance, but are merely used to distinguish different components. Terms such as "comprising" or "including" mean that the element or object preceding the word encompasses the elements or objects listed following the word and their equivalents, without excluding other elements or objects. Terms such as "connected" or "linked" are not limited to physical or mechanical connections, but can include electrical connections, whether direct or indirect. Terms such as "upper," "lower," "left," and "right" are used only to indicate relative positional relationships; when the absolute position of the described object changes, the relative positional relationship may also change accordingly.

[0053] like Figures 7 to 11 As shown in the figure, a specific embodiment of the present invention provides an anti-jitter system applied to a load-sensitive proportional multi-way valve, comprising:

[0054] The load-sensitive signal LS acquisition point 101 is located on the fluid pressure lead-out pipeline of the actuator movement, and is used to acquire the initial pressure P1. The lead-out pipeline is connected in sequence to fixed damper 201, fixed damper 301, check valve 401 and pressure compensator 601 to form the first flow channel.

[0055] Pressure compensator 601 is used to control the flow supply of the hydraulic system by changing the opening degree. The pressure compensator 601 is driven by the initial pressure P1 collected at the load sensitive signal LS acquisition point 101. The initial pressure P1 fluctuates irregularly in a sawtooth pattern.

[0056] The S-type damping bridge circuit is connected between the fixed damper 201 and the one-way valve 401. It includes a D-type half-bridge circuit and a C-type half-bridge circuit. It is used to filter and stabilize the initial pressure P1. The S-type damping bridge circuit converts the fluctuating initial pressure P1 into a stable target pressure P4 to drive the pressure compensator (601) to operate smoothly and achieve a continuous and stable supply of system flow.

[0057] In some optional specific embodiments, such as Figure 6 As shown, the S-type damping bridge circuit includes a D-type half-bridge circuit and a C-type half-bridge circuit connected in parallel:

[0058] The D-type half-bridge circuit includes fixed damper 2 301, fixed damper 4 701, one-way valve 2 801 and one-way valve 1 401;

[0059] The C-type half-bridge circuit includes a variable damping valve 3 (501), a fixed damping valve 4 (701), a one-way valve 2 (801), and a one-way valve 1 (401).

[0060] In some optional specific embodiments, such as Figure 6 As shown, pressure fluid 1 is the first pressure fluid; pressure fluid 2 is the second pressure fluid; pressure fluid 3 is the third pressure fluid; pressure fluid 4 is the fourth pressure fluid; the D-type half-bridge circuit includes:

[0061] Fixed damper 2 301 and fixed damper 4 701 are used to sequentially pass through the second pressure fluid, and the pressure P3 of the third pressure fluid is collected between fixed damper 2 301 and fixed damper 4 701.

[0062] One-way valve 401 is used to allow a third pressure fluid to pass through to form a fourth pressure fluid, which then flows to the pressure compensator 601.

[0063] In some optional specific embodiments, such as Figure 6 As shown, the characteristics of the D-type half-bridge circuit are: the ratio of the third pressure fluid to the second pressure fluid is a constant value, so that the fourth pressure fluid changes in a linear proportion to the second pressure fluid.

[0064] In some optional specific embodiments, such as Figure 6 As shown, the C-type half-bridge circuit includes:

[0065] When the third pressure fluid in the D-type half-bridge circuit is less than the fourth pressure fluid, the one-way valve 401 is shut off, and the fourth pressure fluid acts in the opposite direction to the third pressure fluid through the variable damper 501 and the fixed damper 701.

[0066] When the third pressure fluid is greater than the fourth pressure fluid, check valve 401 opens, and the third pressure fluid is output as the fourth pressure fluid through check valve 401.

[0067] In some optional specific embodiments, the pressure relationship of the image stabilization system is as follows:

[0068]

[0069] Where: P pil Where P is the initial pressure, R is the stability coefficient, and P is the initial pressure. set Set the pressure for the pressure compensator (601), where P is the system pressure.

[0070] The stability coefficient R of the pressure compensator 601 when this system is not used Geom =A pilot / A load A pilot A is the projected area of ​​the pressure compensator 601 under the initial pressure. load The projected area of ​​the actuator under load pressure;

[0071] After starting this system, the stability coefficient of pressure compensator 601 ;

[0072] Adjustment factor λ = (A2) 2 +A4 2 ) / A2 2 λ>1, where A2 is the projected area of ​​fixed damper 2 301; A4 is the projected area of ​​fixed damper 4 701.

[0073] Because of R Real >R Geom Therefore, the stability coefficient of the actual pressure compensator 601 is greatly improved after applying the present invention.

[0074] like Figure 9As shown, Pa is the initial pressure of the pressure compensator 601, Ta is its corresponding response time, Pb is the pressure after compensation by the pressure compensator 601, and Tb is its corresponding response time. Pb > Pa, Tb > Ta. The action of the pressure compensator 601 has a time lag compared with the change in load pressure, causing the action response of the pressure compensator 601 to lag behind the change in initial pressure.

[0075] When the actuator controlled by the hydraulic system moves, the load changes. The fluctuating first pressure fluid taken from the load sensitive signal LS acquisition point 101 is filtered by the fixed damper 201 to form a relatively stable second pressure fluid, thus avoiding excessive impact on the control loop.

[0076] The second pressure fluid, through the "D-type half-bridge circuit" composed of fixed damper 2 301, fixed damper 4 701, and check valve 2 801, forms a more stable third pressure fluid. This third pressure fluid splits into two branches. The first branch passes through fixed damper 4 701 and check valve 2 801 into the return oil circuit. The second branch passes through check valve 1 401 to form the fourth pressure fluid, which reaches the pressure compensator 601. According to the characteristic curve of the "D-type half-bridge circuit," as... Figure 9 As shown, P3 / P2 is a constant value, which makes the changes of P4 and P2 linear.

[0077] like Figure 10 As shown, the horizontal axis represents the relative value Y / Y0 of the valve core moving away from the original opening Y0. The zero point of the coordinate is in the middle. The right side is 0 to positive 1, which means the valve core moves to the right, and the left side is 0 to negative 1, which means the valve core moves to the left.

[0078] The vertical axis represents the ratio of the pressure P output from the half-bridge to the controlled oil chamber to the oil source pressure P0, with the zero point on the horizontal axis and the top being 1.

[0079] Vertical downward coordinate: represents the ratio of the flow rate Q from the half-bridge output to the controlled oil chamber to the oil source flow rate Q0, Q / Q0. The zero point is in the middle, the upper half is negative, indicating oil flowing out of the controlled oil chamber, and the lower half is positive, indicating the control oil flowing into the controlled oil chamber.

[0080] Simultaneously, the fourth pressure fluid at pressure compensator 601, through the action of the "C-type half-bridge circuit" formed by the combination of variable damper 3 501, fixed damper 4 701, and one-way valve 2 801, according to the characteristic curve of the "C-type half-bridge circuit", such as Figure 11 As shown, the pressure values ​​P4 and P2 of the fourth pressure fluid form a hysteresis loop, reducing pressure fluctuations and oscillations.

[0081] like Figure 11As shown, the horizontal axis represents the relative value Y / Y0 of the valve core moving away from the original opening Y0. The zero point of the coordinate is in the middle, with 0 to positive 1 on the right, indicating the valve core moving to the right, and 0 to negative 1 on the left, indicating the valve core moving to the left.

[0082] The vertical axis represents the ratio of the pressure P output from the half-bridge to the controlled oil chamber to the oil source pressure P0, with the zero point on the horizontal axis and the top being 1.

[0083] The 45-degree slant coordinate represents the ratio of the flow rate Q from the half-bridge output to the controlled oil chamber to the oil source flow rate Q0, Q / Q0. The zero point is in the middle, the upper half is negative, indicating oil flowing out of the controlled oil chamber, and the lower half is positive, indicating the control oil flowing into the controlled oil chamber.

[0084] The "D-type half-bridge circuit" composed of fixed damper 2 301, fixed damper 4 701, check valve 2 801, and check valve 1 401, combined with the "C-type half-bridge circuit" formed by variable damper 3 501, fixed damper 4 701, check valve 2 801, and check valve 1 401, is connected in parallel to form an S-type damping bridge circuit. This makes the fourth pressure fluid extremely stable. When the fourth pressure fluid is stable, it can stably act on the pressure compensator 601. This allows the pressure compensator 601 to respond quickly, smoothly, and stably to the flow supply demand of the hydraulic system, thereby solving the load jitter problem caused by pilot pressure fluctuations due to load changes.

[0085] In some alternative specific embodiments, such as Figure 7 As shown, the S-type damping bridge circuit includes:

[0086] Pressure rise phase: The initial pressure P1 continues to increase, and after being filtered by the fixed damper 201, it forms the second pressure fluid. Under the action of the D-type half-bridge circuit, the fourth pressure fluid increases linearly, driving the pressure compensator 601 to increase the opening ratio, and the system flow rate increases proportionally accordingly.

[0087] Pressure drop phase: The initial pressure P1 continues to decrease, and after being filtered by the fixed damper 201, it forms the second pressure fluid. Under the action of the D-type half-bridge circuit, the fourth pressure fluid decreases linearly, driving the pressure compensator 601 to reduce the opening ratio, and the system flow rate decreases proportionally accordingly.

[0088] Negative pressure fluctuation stage: The initial pressure P1 decreases instantaneously, causing the pressure P3 of the third pressure fluid to be less than the pressure P4 of the fourth pressure fluid. One-way valve 401 is shut off. Under the action of the C-type half-bridge circuit, the opening of pressure compensator 601 is suppressed to prevent a sudden drop in system flow.

[0089] During the positive pressure fluctuation stage: The initial pressure P1 increases instantaneously, causing the pressure P3 of the third pressure fluid to be greater than the pressure P4 of the fourth pressure fluid. The one-way valve 401 opens, and under the action of the C-type half-bridge circuit, the opening degree of the pressure compensator 601 is suppressed to prevent a sudden increase in the system flow.

[0090] In some optional specific embodiments, such as Figure 7 As shown, the one-way valve 401 and the one-way valve 801 are used to realize the one-way flow of pressure fluid and prevent the pressure compensator 601 from malfunctioning due to backflow of pressure in the circuit.

[0091] In some optional specific embodiments, such as Figure 7 As shown, the variable damping 501 is used to dynamically adjust the loop damping when the initial pressure P1 fluctuates, thereby extending the response time of the pressure compensator 601 and stabilizing the opening change.

[0092] The following is a detailed description of a de-jittering system applied to a load-sensitive proportional multi-way valve, based on a specific embodiment of the present invention and in conjunction with existing technology.

[0093] like Figures 1 to 6 As shown, in the prior art:

[0094] When the directional valve is in the neutral position, the system load remains unchanged, the initial pressure P1 is 0, the pressure compensator 601 does not operate, and there is no flow supply to the system.

[0095] When the directional valve actuates, the initial pressure P1 changes, to Figure 1 Taking the constant pressure fluctuation form as an example, in stage 1, the initial pressure P1 continues to increase, pressure fluid 1 is collected, and the opening of the control pressure compensator 601 is continuously increased, so that the flow rate entering the system continuously increases.

[0096] In stage 2, the initial pressure P1 fluctuates negatively, and pressure fluid 1 is collected. The opening of the control pressure compensator 601 is reduced, which reduces the flow rate into the system and slows down the load.

[0097] In stage 3, the initial pressure P1 fluctuates positively, pressure fluid 1 is collected, and the opening of the control pressure compensator 601 is increased, which increases the flow rate into the system and accelerates the load.

[0098] The pressure acquisition unit is used to acquire the pressure fluid 1 that is sensitive to the load and obtain the initial pressure P1.

[0099] The S-type damping bridge circuit, including parallel D-type half-bridge circuits and C-type half-bridge circuits, is used to convert the fluctuating initial pressure P1 into a stable pressure fluid 4.

[0100] Subsequently, stages 2 and 3 repeat in a very short cycle, causing the pressure compensator 601 to jump continuously, resulting in unstable system flow supply. This causes the load to continuously "decelerate-accelerate-decelerate-accelerate" within a very short time period, which manifests as load operation jitter.

[0101] The present invention provides an anti-jitter system for load-sensitive proportional multi-way valves, such as... Figure 7 and Figure 11 As shown, its working principle is as follows:

[0102] When the directional valve is in the neutral position, the system load remains unchanged, the initial pressure P1 is 0, the pressure compensator 601 does not operate, and there is no flow supply to the system.

[0103] When the directional valve actuates, the initial pressure P1 changes. In stage 1, the initial pressure P1 continuously increases. The first pressure fluid is filtered by fixed damper 201 to form the second pressure fluid. The second pressure fluid reaches the pressure compensator 601 through the D-type half-bridge circuit. According to the characteristic curve of the D-type half-bridge circuit, the pressure P3 of the third pressure fluid has the following relationship with the pressure P2 of the second pressure fluid: P3 / P2 is a constant value, making the pressure P4 of the fourth pressure fluid linearly related to the change of P2. This controls the proportional change of the opening of the pressure compensator 601 to respond to the increased flow demand of the system. The D-type half-bridge circuit consists of fixed damper 301, check valve 401, fixed damper 701, and check valve 801. The third pressure fluid is taken from between fixed damper 301 and fixed damper 701, and then reaches the pressure compensator 601 through check valve 401.

[0104] In stage 2, the initial pressure P1 fluctuates negatively, and at the moment P3 < P4, check valve 401 closes, preventing the fourth pressure fluid from flowing backward through check valve 401. The fourth pressure fluid acts in the reverse direction on the third pressure fluid through the C-type half-bridge circuit. When P3 > P4, check valve 401 opens again, and the third pressure fluid becomes the fourth pressure fluid through check valve 401, reaching the pressure compensator 601 and controlling the pressure compensator 601 to respond to the system's flow supply demand. The C-type half-bridge circuit consists of variable damper 501, fixed damper 701, and check valve 801. The third pressure fluid is taken from between variable damper 501 and fixed damper 701, and then reaches the pressure compensator 601 through check valve 401.

[0105] In stage 3, the process of stage 1 is repeated. The D-type half-bridge circuit and the C-type half-bridge circuit are connected in parallel to form an S-type damping bridge circuit, which, combined, acts on the initial pressure P1, transforming the sawtooth initial pressure wave P1 into a highly stable fourth pressure fluid, such as... Figure 7As shown, when the fourth pressure fluid is stable, it can stably act on the valve core of the pressure compensator 601. This allows the pressure compensator 601 to respond quickly, smoothly, and stably to the flow supply requirements of the hydraulic system, thereby solving the problem of vibration during load operation.

[0106] Those skilled in the art should understand that the discussion of any of the above embodiments is merely exemplary and is not intended to imply that the scope of the invention (including the claims) is limited to these examples; within the framework of the invention, the technical features of the above embodiments or different embodiments can also be combined, the steps can be implemented in any order, and there are many other variations of the different aspects of the invention as described above, which are not provided in the details for the sake of brevity.

[0107] This invention is intended to cover all such substitutions, modifications, and variations that fall within the broad scope of the appended claims. Therefore, any omissions, modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this invention should be included within the scope of protection of this invention.

Claims

1. An anti-hunt system for use with a load sensing proportional multi-way valve, the anti-hunt system comprising: The system comprises: a load-sensitive signal LS acquisition point (101) located on a fluid pressure lead-out pipeline of an executing element movement, used for acquiring an initial pressure P1, the lead-out pipeline being sequentially connected to a fixed damper one (201), a fixed damper two (301), a one-way valve one (401) and a pressure compensator (601) to form a first flow channel; the pressure compensator (601) is used for controlling the flow supply of the hydraulic system through opening degree change, the pressure compensator (601) is driven by the initial pressure P1 acquired at the load-sensitive signal LS acquisition point (101), and the initial pressure P1 is irregularly and sawtoothly fluctuated; an S-type damping bridge circuit connected between the fixed damper one (201) and the one-way valve one (401) and comprising a D-type half-bridge circuit and a C-type half-bridge circuit arranged in parallel, used for filtering and stabilizing the initial pressure P1, the S-type damping bridge circuit converts the fluctuated initial pressure P1 into a stable target pressure P4 to drive the pressure compensator (601) to act smoothly and realize continuous and stable supply of system flow; the D-type half-bridge circuit comprises the fixed damper two (301), a fixed damper four (701), a one-way valve two (801) and the one-way valve one (401); the C-type half-bridge circuit comprises a variable damper three (501), the fixed damper four (701), the one-way valve two (801) and the one-way valve one (401).

2. The anti-hunt system for a load-sensing proportional multi-way valve according to claim 1, wherein The D-type half-bridge circuit comprises: the fixed damper two (301) and the fixed damper four (701) are used for sequentially passing the second pressure fluid between the fixed damper one (201) and the fixed damper two (301) and acquiring the pressure P3 of the third pressure fluid between the fixed damper two (301) and the fixed damper four (701); the one-way valve one (401) is used for passing the third pressure fluid between the fixed damper two (301) and the fixed damper four (701), forming the fourth pressure fluid and flowing to the pressure compensator (601).

3. The anti-hunt system for use in a load-sensing proportional multi-way valve according to claim 1, wherein The system pressure relationship is: where: P pil is the initial pressure, R is the stability coefficient, P set is the pressure set by the pressure compensator (601), P is the system pressure; Stabilizing factor R of the pressure compensator (601) when the system is not activated Geom = A pilot / A load where A pilot is the projected area of the initial pressure acting on the pressure compensator (601), and A load is the projected area of the load pressure acting on the actuator After starting the system, the pressure compensator (601) stabilizes the coefficient ; Adjustment factor λ = (A2 2 +A4 2 ) / A2 2 , λ > 1, where A2 is the projected area of the fixed damper two (301); A4 is the projected area of the fixed damper four (701); the action of the pressure compensator (601) lags behind the change of the load pressure by a time hysteresis, so that the action of the pressure compensator (601) lags behind the change of the initial pressure.

4. The anti-hunt system for use in a load-sensing proportional multi-way valve according to claim 1, wherein The C-type half-bridge circuit comprises: when the pressure P3 of the third pressure fluid in the D-type half-bridge circuit is less than the pressure P4 of the fourth pressure fluid, the one-way valve one (401) is closed, the fourth pressure fluid acts on the third pressure fluid in a reverse direction through the variable damper three (501) and the fixed damper four (701); when the pressure P3 of the third pressure fluid is greater than the pressure P4 of the fourth pressure fluid, the one-way valve one (401) is opened, and the third pressure fluid is output as the fourth pressure fluid through the one-way valve one (401).

5. The anti-hunt system for use in a load sensing proportional multi-way valve according to claim 1, wherein The S-type damping bridge circuit comprises: a pressure rising stage: the initial pressure P1 continuously increases, the second pressure fluid is formed after filtering through the fixed damper one (201), the pressure P4 of the fourth pressure fluid is linearly increased under the action of the D-type half-bridge circuit, the opening degree of the pressure compensator (601) is proportionally increased, and the system flow is proportionally increased; Pressure drop stage: the initial pressure P1 continuously decreases, the second pressure fluid is formed after filtering by the fixed damping one (201), the pressure P4 of the fourth pressure fluid linearly decreases under the action of the D-type half-bridge circuit, the opening of the pressure compensator (601) proportionally decreases, and the system flow proportionally decreases; Pressure negative fluctuation stage: the initial pressure P1 instantaneously decreases, the pressure P3 of the third pressure fluid is less than the pressure P4 of the fourth pressure fluid, the one-way valve one (401) is cut off, the opening of the pressure compensator (601) is inhibited from suddenly decreasing under the action of the C-type half-bridge circuit, and sudden drop of the system flow is avoided; Pressure positive fluctuation stage: the initial pressure P1 instantaneously increases, the pressure P3 of the third pressure fluid is greater than the pressure P4 of the fourth pressure fluid, the one-way valve one (401) is opened, and the opening of the pressure compensator (601) is inhibited from suddenly increasing under the action of the C-type half-bridge circuit, so as to avoid sudden increase of the system flow.

6. The anti-hunt system for use in a load sensing proportional multi-way valve according to claim 1, wherein The one-way valve one (401) and the one-way valve two (801) are used to realize one-way conduction of the pressure fluid, and prevent misoperation of the pressure compensator (601) caused by pressure backflow in the circuit.

7. The anti-hunt system for use in a load sensing proportional multi-way valve according to claim 1, wherein The variable damping three (501) is used to dynamically adjust the damping of the circuit when the initial pressure P1 fluctuates, prolong the response time of the pressure compensator (601), and stabilize the opening change.

8. The anti-hunt system for use in a load sensing proportional multi-way valve of claim 1, wherein, The fixed damping one (201) is used to perform primary filtering on the initial pressure P1, reduce high-frequency components of pressure fluctuation, and reduce the impact on the control circuit.

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