Damping type segmented hydraulic slide valve pair structure

Abstract

The invention discloses a damping type segmented hydraulic slide valve pair structure, and relates to the technical field of electro-hydraulic servo valves, damping cavities are introduced into two ends of a valve core, the movement damping of the valve core is changed by adjusting the size of a slender hole, the anti-interference capability of the valve core is improved, and meanwhile, the displacement monitoring and fault diagnosis of the valve core are realized through an embedded flowmeter. The damping type segmented hydraulic slide valve pair structure comprises a first valve element, a second valve element, a third valve element, a valve sleeve, a slender hole and an embedded flow meter.

Description

Technical Field

[0001] The invention relates to the technical field of electro-hydraulic servo valves, and in particular to a damping type segmented hydraulic slide valve auxiliary structure. Background Art

[0002] The electro-hydraulic servo valve is a hydraulic amplification element and also a control element. It is widely used in electro-hydraulic servo control systems in the fields of aviation, aerospace, navigation, etc. The two-stage electro-hydraulic servo valve is mainly composed of a pilot stage and a slide valve stage. The slide valve stage converts the pressure control of the pilot stage into the relative movement between the slide valve pairs, forming a certain flow window, thereby forming a flow or pressure control of the control object. In actual use, the pressure fluctuation of the servo valve pilot stage, the pulsation of the oil inlet pressure of the slide valve stage, the pulsation of the oil return pressure of the slide valve stage, the flow disturbance of the slide valve stage, the extreme vibration environment, the extreme acceleration environment and other disturbances will cause the servo valve core to shake, and then the output curve will shake, which will reduce the control accuracy and increase the control difficulty. In severe cases, howling will occur. At present, there is no relevant slide valve pair structure that can improve the jitter of the slide valve pair. Summary of the invention

[0003] In order to solve the above problems, the purpose of the present invention is to provide a damping type segmented hydraulic sliding valve auxiliary structure, introduce damping cavities at both ends of a valve core, change the valve core movement damping by adjusting the size of the slender hole, and improve the anti-interference ability of the valve core.

[0004] In order to achieve the above-mentioned purpose, the damping type segmented hydraulic slide valve structure provided by the present invention adopts the following technical solutions:

[0005] A damping type segmented hydraulic slide valve auxiliary structure, comprising: a first valve core, a second valve core, a third valve core, a valve sleeve, an elongated hole, and an embedded flow meter;

[0006] The first valve core is symmetrical on the left and right and is a cylindrical structure. The outer circular surface is provided with a first convex shoulder, a second convex shoulder, a third convex shoulder, a fourth convex shoulder, a fifth convex shoulder, a sixth convex shoulder and a seventh convex shoulder. The left and right end surfaces are symmetrically provided with a step blind hole. The second valve core and the third valve core have exactly the same structure and are a T-shaped structure consisting of a first cylinder and a second cylinder. The valve sleeve is a cylindrical structure with a hollow inner hole. The first cylinder of the second valve core and the inner hole of the valve sleeve are gap matched, and the second cylinder of the second valve core and the end face step blind hole of the first valve core are gap matched. The first to seventh convex shoulders on the outer circle of the first valve core are gap matched with the inner hole of the valve sleeve. The matching structure of the third valve core, the first valve core and the valve sleeve is exactly the same as the matching structure of the second valve core. The cavity between the first cylinder of the second valve core and the first convex shoulder of the first valve core constitutes a first damping cavity, and the cavity between the first cylinder of the third valve core and the seventh convex shoulder of the first valve core constitutes a second The damping chamber, the first damping chamber is connected to the second damping chamber, and an elongated hole and an embedded flow meter are connected in series on the connected channel. The first valve core moves to the left to squeeze the fluid in the first damping chamber and increase the pressure of the first damping chamber to PA, releases the fluid in the second damping chamber and reduces the pressure of the second damping chamber to PB, and the fluid Q enters the second damping chamber from the first damping chamber through the elongated hole and the embedded flow meter. Similarly, the first valve core moves to the right to squeeze the fluid in the second damping chamber and increase the pressure of the second damping chamber to PB, releases the fluid in the first damping chamber and reduces the pressure of the first damping chamber to PA, and the fluid Q enters the first damping chamber from the second damping chamber through the elongated hole and the embedded flow meter. The pressures PA and PB are adjusted by changing the aperture d of the elongated hole to achieve the effect of changing the damping of the movement of the first valve core. The pressures PA, PB, fluid Q and the aperture d of the elongated hole satisfy the relationship in formula 1:

[0007]

[0008] In the formula, C is the flow coefficient, ρ is the fluid density;

[0009] Furthermore, the working stroke of the first valve core is determined, and the fluid Q is a constant value. When the aperture d of the elongated hole is smaller, the difference between the pressures PA and PB is larger, and the motion damping of the first valve core is larger. When the aperture d of the elongated hole is larger, the difference between the pressures PA and PB is smaller, and the motion damping of the first valve core is smaller.

[0010] Furthermore, the flow rate Q is obtained by an embedded flow meter, and the displacement X of the first valve core can be calculated according to the outer diameter D of the first valve core, and the relationship in Formula 2 is satisfied:

[0011]

[0012] Further, the cavity between the first convex shoulder and the second convex shoulder of the first valve core constitutes a first control cavity, the cavity between the sixth convex shoulder and the seventh convex shoulder of the first valve core constitutes a second control cavity, the first control cavity and the second control cavity are connected to the pre-stage of the jet tube servo valve or the spray stop servo valve or the deflector plate servo valve, the cavity between the second convex shoulder and the third convex shoulder of the first valve core constitutes a first oil inlet cavity, the cavity between the fifth convex shoulder and the sixth convex shoulder of the first valve core constitutes a second oil inlet cavity, the first oil inlet cavity is communicated with the second oil inlet cavity and connected to the oil inlet port, the cavity between the third convex shoulder and the fourth convex shoulder of the first valve core constitutes a first oil return cavity, the cavity between the fourth convex shoulder and the fifth convex shoulder of the first valve core constitutes a second oil return cavity, the first oil return cavity is communicated with the second oil return cavity and connected to the oil return port, the third convex shoulder of the first valve core is opposite to the first load port, and the fifth convex shoulder of the first valve core is opposite to the second load port;

[0013] Furthermore, a control oil port is provided in the step blind hole of the first valve core, which is connected with the first control chamber and the second control chamber, and the pressure in the first control chamber and the second control chamber acts on the first step surface and the second step surface in the step blind hole, driving the first valve core to move left and right;

[0014] Furthermore, the first step surface in the step blind hole can also be used to limit the stroke of the first valve core. When the first step surface contacts the second cylindrical end surfaces of the second valve core and the third valve core, the first valve core moves to the limit position. At this time, the second step surface can still accept the pressure in the first control chamber and the second control chamber, thereby preventing the first valve core from being sucked to death instantly during movement.

[0015] Compared with the existing sliding valve structure, the present invention has the following advantages:

[0016] (1) Through the design of the segmented sliding valve structure, the damping chamber structure with an elongated hole is introduced to effectively solve the problem of valve core vibration and howling caused by vibration. The diameter of the elongated hole is adjustable, which is suitable for different load conditions.

[0017] (2) By introducing an embedded flow meter structure into the damping chamber structure, the displacement of the valve core can be indirectly obtained, which plays a role in displacement monitoring and fault diagnosis. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Figure 1 Schematic diagram of the substructure of the segmented hydraulic slide valve;

[0019] Figure 2 A schematic diagram of the first valve core structure;

[0020] Figure 3 Schematic diagram of the second valve core structure;

[0021] Figure 4 Schematic diagram of the third valve core structure. DETAILED DESCRIPTION

[0022] In order to more intuitively and clearly describe the structural principles and working methods in the examples of the present invention, the embodiments will be introduced in conjunction with relevant drawings. The drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0023] An embodiment of the present invention provides a damping hydraulic sliding valve auxiliary structure. Through structural innovation and the structure of a segmented sliding valve, a damping control chamber structure is introduced at both ends of the valve core, which can effectively solve the problem of valve core jitter and match different working conditions.

[0024] To achieve the above object, the embodiments of the present invention adopt the following technical solutions:

[0025] A damping type segmented hydraulic slide valve auxiliary structure, such as Figure 1 As shown, it includes: a first valve core 1, a second valve core 2, a third valve core 3, a valve sleeve 4, an elongated hole 6, and an embedded flow meter 5;

[0026] The first valve core 1 is symmetrical and cylindrical in structure. A first convex shoulder 1.1, a second convex shoulder 1.2, a third convex shoulder 1.3, a fourth convex shoulder 1.4, a fifth convex shoulder 1.5, a sixth convex shoulder 1.6 and a seventh convex shoulder 1.7 are arranged on the outer surface. An end face step blind hole 1.8 is symmetrically arranged on the left and right end faces. The second valve core 2 and the third valve core 3 have the same structure and are T-shaped structures, which are composed of a first cylinder 2-3-1 and a second cylinder 2-3-2. The valve sleeve 4 is cylindrical in structure and is provided with a hollow inner hole. The first cylinder 2-3-1 of the second valve core 2 The first to seventh convex shoulders on the outer circle of the first valve core 1 are clearance matched with the inner hole of the valve sleeve 4. The matching structure of the third valve core 3, the first valve core 1 and the valve sleeve 4 is exactly the same as the matching structure of the second valve core 2. The cavity between the first cylinder 2-3-1 of the second valve core 2 and the first convex shoulder 1.1 of the first valve core 1 constitutes a first damping cavity F1. The first cylinder 2-3-1 of the third valve core 3 and the first valve core 1 are clearance matched with the end face step blind hole 1.8 of the first valve core 1. The first to seventh convex shoulders on the outer circle of the first valve core 1 are clearance matched with the inner hole of the valve sleeve 4. The matching structure of the third valve core 3, the first valve core 1 and the valve sleeve 4 is exactly the same as the matching structure of the second valve core 2. The cavity between the first cylinder 2-3-1 of the second valve core 2 and the first convex shoulder 1.1 of the first valve core 1 constitutes a first damping cavity F1. The cavity between the seventh convex shoulder 1.7 of 1 constitutes the second damping chamber F2, the first damping chamber F1 is connected with the second damping chamber F2, and the elongated hole 6 and the embedded flow meter 5 are connected in series on the connected passage, the first valve core 1 moves to the left to squeeze the fluid in the first damping chamber F1 and increase the pressure of the first damping chamber F1 to PA, release the fluid in the second damping chamber F2 and reduce the pressure of the second damping chamber F2 to PB, the fluid Q enters the second damping chamber F2 from the first damping chamber F1 through the elongated hole 6 and the embedded flow meter 5, similarly, the The first valve core 1 moves to the right to squeeze the fluid in the second damping chamber F2 and increase the pressure of the second damping chamber F2 to PB, release the fluid in the first damping chamber F1 and reduce the pressure of the first damping chamber F1 to PA, and the fluid Q enters the first damping chamber F1 from the second damping chamber F2 through the elongated hole 6 and the embedded flow meter 5. The pressures PA and PB are adjusted by changing the aperture d of the elongated hole 6 to achieve the effect of changing the motion damping of the first valve core 1, so that the jitter of the first valve core 1 is controlled, the function of the entire valve is improved, and the valve whistling problem caused by the jitter of the valve core is improved. The pressure PA, PB, fluid Q and the aperture d of the elongated hole 6 satisfy the relationship in formula 1:

[0027]

[0028] In the formula, C is the flow coefficient, ρ is the fluid density;

[0029] Furthermore, the working stroke of the first valve core 1 is determined, and the fluid Q is a constant value. When the aperture d of the elongated hole 6 is smaller, the difference between the pressures PA and PB is larger, and the motion damping of the first valve core 1 is larger. When the aperture d of the elongated hole 6 is larger, the difference between the pressures PA and PB is smaller, and the motion damping of the first valve core 1 is smaller.

[0030] Furthermore, the flow rate Q is obtained by an embedded flow meter, and the displacement X of the first valve core 1 can be calculated according to the outer diameter D of the first valve core 1, and the relationship in formula 2 is satisfied:

[0031]

[0032] Further, the cavity between the first convex shoulder 1.1 and the second convex shoulder 1.2 of the first valve core 1 constitutes a first control cavity C1, the cavity between the sixth convex shoulder 1.6 and the seventh convex shoulder 1.7 of the first valve core 1 constitutes a second control cavity C2, the first control cavity C1 and the second control cavity C2 are connected to the pre-stage of the jet tube servo valve or the spray stop servo valve or the deflector plate servo valve, the cavity between the second convex shoulder 1.2 and the third convex shoulder 1.3 of the first valve core 1 constitutes a first oil inlet cavity P1, the cavity between the fifth convex shoulder 1.5 and the sixth convex shoulder 1.6 of the first valve core 1 The first oil inlet chamber P2 is connected to the oil inlet port, the first oil inlet chamber P1 is connected to the second oil inlet chamber P2, and is connected to the oil inlet port. The cavity between the third convex shoulder 1.3 and the fourth convex shoulder 1.4 of the first valve core 1 constitutes the first oil return chamber R1, and the cavity between the fourth convex shoulder 1.4 and the fifth convex shoulder 1.5 of the first valve core 1 constitutes the second oil return chamber R2. The first oil return chamber R1 is connected to the second oil return chamber R2 and is connected to the oil return port. The third convex shoulder 1.3 of the first valve core 1 is opposite to the first load port A, and the fifth convex shoulder 1.5 of the first valve core 1 is opposite to the second load port B.

[0033] Furthermore, a control oil port 1.8.3 is provided in the step blind hole 1.8 of the first valve core 1, which is connected to the first control chamber F1 and the second control chamber F2. The pressure in the first control chamber F1 and the second control chamber F2 acts on the first step surface 1.8.1 and the second step surface 1.8.2 in the step blind hole 1.8, driving the first valve core 1 to move left and right;

[0034] Furthermore, the first step surface 1.8.1 in the step blind hole 1.8 can also be used to limit the stroke of the first valve core 1. When the first step surface 1.8.1 contacts the second cylindrical end surfaces 2-3-2 of the second valve core 2 and the third valve core 3, the first valve core 1 moves to the limit position. At this time, the second step surface 1.8.2 can still accept the pressure in the first control chamber C1 and the second control chamber C2, thereby preventing the first valve core 1 from being sucked to death in an instant when it moves.

[0035] Compared with the existing sliding valve structure, the present invention has the following advantages:

[0036] (1) Through the design of the segmented sliding valve structure, the damping chamber structure with an elongated hole is introduced to effectively solve the problem of valve core vibration and howling caused by vibration. The diameter of the elongated hole is adjustable, which is suitable for different load conditions.

[0037] (2) By introducing an embedded flow meter structure into the damping chamber structure, the displacement of the valve core can be indirectly obtained, which plays a role in displacement monitoring and fault diagnosis.

[0038] The above description is only a preferred embodiment of the present invention. It should be pointed out that a person skilled in the art can make several improvements without departing from the principle of the present invention, and these improvements should also be regarded as within the protection scope of the present invention.

Claims

1. A damping hydraulic slide valve auxiliary structure, characterized in that: The utility model comprises: a first valve core, a second valve core, a third valve core, a valve sleeve, an elongated hole and an embedded flow meter; the first valve core is slidingly arranged in the valve sleeve, the second valve core and the third valve core are arranged at two ends inside the valve sleeve, the outer cylindrical surfaces of the second valve core and the third valve core are gap-matched with the valve sleeve, the end faces of the second valve core and the third valve core are provided with cylindrical sections, which are gap-matched with the step blind holes at two ends of the first valve core respectively, a first damping chamber F1 is formed between the second valve core and the end face of one side of the first valve core, a first damping chamber F2 is formed between the third valve core and the end face of the other side of the first valve core, the first damping chamber F1 is connected with the second damping chamber F2, and the elongated hole and the embedded flow meter are connected in series on the channel connecting the two damping chambers.

2. A damping type hydraulic slide valve auxiliary structure according to claim 1, characterized in that: The first valve core is symmetrical and cylindrical in structure, and a first convex shoulder, a second convex shoulder, a third convex shoulder, a fourth convex shoulder, a fifth convex shoulder, a sixth convex shoulder and a seventh convex shoulder are arranged on the outer circumferential surface, and an end face step blind hole is symmetrically arranged on the left and right end faces.

3. A damping type hydraulic slide valve auxiliary structure according to claim 2, characterized in that: The second valve core and the third valve core have the same structure, which is a T-shaped structure and consists of a first cylinder and a second cylinder.

4. A damping type hydraulic slide valve auxiliary structure according to claim 3, characterized in that: The valve sleeve is a cylindrical structure with a hollow inner hole. The first cylinder of the second valve core is gapped with the inner hole of the valve sleeve, the second cylinder of the second valve core is gapped with the left end face step blind hole of the first valve core, the first to seventh shoulders on the outer circle of the first valve core are gapped with the inner hole of the valve sleeve, the first cylinder of the third valve core is gapped with the inner hole of the valve sleeve, the second cylinder of the third valve core is gapped with the right end face step blind hole of the first valve core, and the first to seventh shoulders on the outer circle of the first valve core are gapped with the inner hole of the valve sleeve.

5. A damping type hydraulic slide valve auxiliary structure according to claim 4, characterized in that: The cavity between the first cylinder of the second valve core and the first convex shoulder of the first valve core constitutes a first damping chamber F1, and the cavity between the first cylinder of the third valve core and the seventh convex shoulder of the first valve core constitutes a second damping chamber F2.

6. A damping type hydraulic slide valve auxiliary structure according to claim 4, characterized in that: The diameter d of the elongated hole and the flow rate Q of the fluid between the first damping chamber F1 and the second damping chamber F2 satisfy the following relationship: Wherein, C is the flow coefficient, ρ is the fluid density, PA is the pressure of the first damping chamber F1 after the first valve core moves; PB is the pressure of the second damping chamber F2 after the first valve core moves.

7. A damping type hydraulic slide valve auxiliary structure according to claim 6, characterized in that: The flow rate Q is obtained by an embedded flow meter, and the displacement X of the first valve core can be calculated according to the outer diameter D of the first valve core 1 by the following formula, namely:

8. A damping type hydraulic slide valve auxiliary structure according to claim 6, characterized in that: The cavity between the first shoulder and the second shoulder of the first valve core constitutes the first control cavity C1, the cavity between the sixth shoulder and the seventh shoulder of the first valve core constitutes the second control cavity C2, the first control cavity C1 and the second control cavity C2 are connected to the pre-stage of the jet tube servo valve or the spray stop servo valve or the deflector plate servo valve, the cavity between the second shoulder and the third shoulder of the first valve core constitutes the first oil inlet cavity P1, the cavity between the fifth shoulder and the sixth shoulder of the first valve core constitutes the second oil inlet cavity P2, the first oil inlet cavity P1 is communicated with the second oil inlet cavity P2 and is connected to the oil inlet port, the cavity between the third shoulder and the fourth shoulder of the first valve core constitutes the first oil return cavity R1, the cavity between the fourth shoulder and the fifth shoulder of the first valve core constitutes the second oil return cavity R2, the first oil return cavity R1 is communicated with the second oil return cavity R2 and is connected to the oil return port, the third shoulder of the first valve core is opposite to the first load port A, and the fifth shoulder of the first valve core is opposite to the second load port B.

9. A damping type hydraulic slide valve auxiliary structure according to claim 8, characterized in that: Control oil ports are respectively arranged at both ends of the first valve core, wherein the control oil port at one end is respectively connected to the corresponding step blind hole and the first control chamber C1, and the control oil port at the other end is respectively connected to the corresponding step blind hole and the second control chamber C2.

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