Compact hydraulic amplifier

Abstract

The utility model belongs to the technical field of electro-hydraulic servo valves, and discloses a compact hydraulic amplifier which comprises a pressure reducing valve element assembly, a throttling hole-nozzle-baffle assembly and a power sliding valve assembly, and the pressure reducing valve element assembly comprises a pressure reducing valve element, a spring and a first check ring; the throttling hole-nozzle-baffle assembly comprises a rotating baffle, a main nozzle and a thin-wall throttling hole. The power slide valve assembly comprises a main valve element, a valve sleeve, a shell, a gasket and a second check ring. According to the utility model, the advantages of small driving force, no friction and high sensitivity of a nozzle baffle hydraulic amplifier and the advantages of good linearity and large output flow of a slide valve hydraulic amplifier are combined, the structure is compact, the manufacture is simple, the shearing force of the valve core is large, the anti-pollution capability is strong, and the reliability is high; the influence of oil supply pressure fluctuation on the nozzle-baffle assembly can be restrained, the working stability of the hydraulic amplifier is improved, and the working life of the compact hydraulic amplifier is prolonged.

Description

TECHNICAL FIELD

[0001] The utility model relates to electro-hydraulic servo valve technical field, concretely relates to a compact hydraulic amplifier. BACKGROUND

[0002] Electro-hydraulic servo valve is the core component of hydraulic servo control system, and plays the role of electro-hyydraulic conversion and power amplification in the system, and it directly receives the electric signal from the system transmission when the system works, and converts the electric signal into the signal with corresponding polarity, proportional, load flow or load pressure of the electro-hydraulic servo valve that can control.

[0003] Hydraulic amplifier is the important machine-hydraulic conversion and power amplification device in electro-hydraulic servo valve, and the input of amplifier is the output force or torque of torque motor, and the output of amplifier is load flow and load pressure.

[0004] The nozzle baffle type hydraulic amplifier is composed of fixed throttle hole and variable throttle hole, and works according to the throttle principle, and its characteristics are simple structure, small volume, small inertia of moving parts, small driving force, no friction, high sensitivity and fast response speed, but the mid-position leakage is large, the output flow is small, and it is suitable for small signal work.

[0005] The slide valve type hydraulic amplifier works according to the throttle principle, and its characteristics are that displacement is allowed to be large, output flow is large, working interval linearity is good, flow gain and pressure gain are high, but the structure is complex, axial cooperation is required to be high, liquid power is large, driving force is required to be large, and it is usually directly constituted as single-stage servo valve with moving coil type motor or linear force motor.

[0006] Therefore, in the occasion that the structural size requirement is strict and the driving power is limited, the output flow of the traditional nozzle baffle type hydraulic amplifier is too small, the driving force of the slide valve type hydraulic amplifier is not enough, and the two-stage hydraulic amplifier composed of nozzle baffle type hydraulic amplifier and slide valve type hydraulic amplifier is difficult to meet the requirement of structural size. UTILITY MODEL CONTENT

[0007] The utility model discloses a compact hydraulic amplifier, which combines the advantages of nozzle baffle hydraulic amplifier and slide valve type hydraulic amplifier, and has the advantages of compact structure, small driving force, no friction, large output flow and high reliability.

[0008] Technical solution: In order to achieve the above-mentioned utility model purposes, a compact hydraulic amplifier is provided, comprising a pressure reducing valve core assembly, a throttle hole-nozzle-baffle assembly and a power slide valve assembly, the pressure reducing valve core assembly comprises a pressure reducing valve core, a spring and a first check ring; the throttle hole-nozzle-baffle assembly comprises a rotating baffle, a main nozzle and a thin-wall throttle hole; the power slide valve assembly comprises a main valve core, a valve sleeve, a housing, a gasket and a second check ring.

[0009] Further, the thin-wall throttle hole is fixed in the thin-wall throttle hole mounting hole in the main valve core.

[0010] Further, the rotating baffle and the main nozzle are installed in the inner hole of the housing and can move axially in the inner hole of the housing, and the movement distance of the rotating baffle is limited by the two side end faces of the inner hole of the housing.

[0011] Further, the pressure reducing valve core, the spring and the first check ring are installed in the inner hole of the main valve core and are positioned by the end face of the inner hole of the main valve core and the end face of the check ring mounting groove, and the pressure reducing valve core can move axially in the inner hole.

[0012] Further, the valve sleeve is installed in the inner hole of the housing and is positioned by the gasket and the second check ring.

[0013] Further, the main valve core is installed in the inner holes of the valve sleeve and the housing and can move axially in the inner holes of the housing and the valve sleeve.

[0014] Further, the radial distance between the main valve core and the valve sleeve is less than 0.2mm, which reduces the friction of the main valve core movement and improves the smoothness of the movement.

[0015] Further, the ratio of the nozzle hole diameter of the main nozzle to the diameter of the thin-wall throttle hole is 1.25, which improves the sensitivity of nozzle-baffle control.

[0016] Further, the stiffness of the spring can be changed for adjusting the working pressure of the oil after the pressure reducing valve.

[0017] Further, the distance between the main nozzle and the rotating baffle is less than 0.1mm, which reduces the leakage amount of the control oil and improves the system working efficiency.

[0018] Further, the outflow conical wall angle of the main nozzle is 74°, and the outflow annular wall diameter is less than 1.5mm, which improves the flowability of the oil and enhances the sensitivity of control.

[0019] The beneficial effects of the utility model are as follows:

[0020] 1. The utility model differs from traditional nozzle - baffle hydraulic amplifier and slide valve hydraulic amplifier, this novel structure integrates nozzle - baffle type structure and valve core - valve sleeve type structure on single part, not only realizes the effect that space size is small, compact structure, still has the characteristics that output flow is big, linearity is good, driving force is small.

[0021] 2. The utility model discloses a novel pressure reducing valve core structure for the problem that nozzle cavity oil is easy to be influenced by oil supply pressure fluctuation due to integrated design of compact hydraulic amplifier, reduces oil working pressure through the throttling effect of pressure reducing valve core, suppresses the influence of oil supply pressure fluctuation, improves the reliability of compact hydraulic amplifier. DRAWINGS

[0022] Figure 1 The utility model provides a compact hydraulic amplifier structure schematic drawing for embodiment;

[0023] Figure 2 The utility model provides a main valve core structure schematic drawing for embodiment;

[0024] Figure 3 The utility model provides a main nozzle structure schematic drawing for embodiment;

[0025] Wherein, 1 - rotary baffle, 2-1 - main nozzle, 3 - thin - wall throttling hole, 4 - valve sleeve, 2-2 - main valve core, 5 - shell, 6 - pressure reducing valve core, 7 - spring, 8 - first baffle ring, 9 - valve sleeve gasket, 10 - second baffle ring;

[0026] 2-2.1 - first valve core shoulder, 2-2.2 - second valve core shoulder, 2-2.3 - third valve core shoulder, 2-2.4 - fourth valve core shoulder, 2-2.5 - third valve core oil hole, 2-2.6 - thin - wall throttling hole mounting hole, 2-2.7 - second valve core oil hole, 2-2.8 - first valve core oil hole, 2-2.9 - baffle ring installation groove and 2-2.10 - main valve core inner hole;2-1.1 - nozzle hole, 2-1.2 - conical hole, 2-1.3 - inflow hole, 2-1.4 - outflow annular wall, 2-1.5 - outflow conical wall. DETAILED DESCRIPTION

[0027] In order to more clearly illustrate the technical scheme of the utility model embodiment, the utility model is described in detail below with the description of the drawings or specific implementation examples, it is needful to point out that in the drawing in the disclosed example some (but not all). In fact, many different examples can be described and these examples should not be understood as being limited to the examples set forth herein. On the contrary, these examples are described so that the positive effects of the utility model are more embodied, and the details not described in the text are regarded as known technology or conventional technology means in the art.

[0028] AsFigure 1 As shown, an embodiment of the present invention provides a compact hydraulic amplifier structure, comprising a pressure reducing valve core assembly, a throttle orifice-nozzle-flapper assembly, and a power slide valve assembly. The pressure reducing valve core assembly includes a pressure reducing valve core 6, a spring 7, and a first retaining ring 8; the throttle orifice-nozzle-flapper assembly includes a rotating baffle 1, a main nozzle 2-1, and a thin-walled throttle orifice 3; and the power slide valve assembly includes a main valve core 2-2, a valve sleeve 4, a housing 5, a gasket 9, and a second retaining ring 10.

[0029] like Figure 2 As shown, the main valve core 2-2 includes a first valve core shoulder 2-2.1, a second valve core shoulder 2-2.2, a third valve core shoulder 2-2.3 and a fourth valve core shoulder 2-2.4; also includes a first valve core oil hole 2-2.8, a second valve core oil hole 2-2.7 and a third valve core oil hole 2-2.5; also includes a thin-walled throttle hole mounting hole 2-2.6, a retaining ring mounting groove 2-2.9 and a main valve core inner hole 2-2.10.

[0030] like Figure 3 As shown, the main nozzle 2-1 includes a nozzle hole 2-1.1, a tapered hole 2-1.2, an inlet hole 2-1.3, an outflow annular wall 2-1.4, and an outflow tapered wall 2-1.5.

[0031] The thin-walled throttle hole 3 is fixed in the thin-walled throttle hole mounting hole 2-2.6 in the main valve core.

[0032] The rotating baffle 1 and the main nozzle 2-1 are installed in the inner hole of the shell 5 and can move axially in the inner hole of the shell. The movement distance of the rotating baffle 1 is limited by the end surfaces on both sides of the inner hole of the shell.

[0033] The pressure reducing valve core 6, spring 7 and first retaining ring 8 are installed in the main valve core inner hole 2-2.10. The pressure reducing valve core 6 can move axially in the inner hole through the end face of the main valve core inner hole 2-2.10 and the end face of the retaining ring installation groove 2-2.9.

[0034] The valve sleeve 4 is installed in the inner hole of the housing 5 and is positioned by a gasket 9 and a second retaining ring 10 .

[0035] The main valve core 2-2 is installed in the inner hole of the valve sleeve 4 and the housing 5, wherein the first valve core shoulder 2-2.1 can move in the axial direction in the inner hole of the housing 5, the second valve core shoulder 2-2.2, the third valve core shoulder 2-2.3 and the fourth valve core shoulder 2-2.4 can move in the axial direction in the inner hole of the valve sleeve 4. When the main valve core 2-2 slides to the right, the oil return flow window area formed by the third valve core shoulder 2-2.3 and the valve sleeve 4 gradually increases, and the oil flow from the load port to the oil return port gradually increases. When the main valve core 2-2 slides to the left, the oil inlet flow window area formed by the third valve core shoulder 2-2.3 and the valve sleeve 4 gradually increases, and the oil flow from the oil supply port to the load port gradually increases.

[0036] The following is another embodiment of the utility model.

[0037] The embodiment of the utility model provides a compact hydraulic amplifier structure which is composed of a pressure reducing valve core assembly, a throttle hole-nozzle-baffle assembly and a power spool assembly. The compact configuration of the nozzle-baffle structure and the valve core valve sleeve structure is utilized to realize the effects of hydraulic driving of the main valve core, frictionless movement and large flow output. The two-stage nested structure of the built-in pressure reducing valve core of the main valve core is utilized to realize the effects of high working stability and strong anti-interference capability of the hydraulic amplifier.

[0038] To achieve the above object, the embodiment of the utility model adopts the following technical scheme:

[0039] A compact hydraulic amplifier structure, as shown in Figure 1 The main nozzle 2-1 and the main valve core 2-2 are integrated on the same part, and the pressure difference on both sides of the first valve core shoulder 2-2.1 drives the movement of the main valve core 2-2.

[0040] When the working oil enters the housing 5 from the oil supply port P, it enters the control cavity formed by the valve sleeve 4 and the main valve core 2-2 through the oil passage window on the valve sleeve 4, and the oil in the control cavity enters the inner hole 2-2.10 of the main valve core through the first valve core oil passage hole 2-2.8. The oil in the inner hole flows out through the hole on the pressure reducing valve core 6 and acts on the end face of the pressure reducing valve core, driving the pressure reducing valve core to move to the right. The movement of the pressure reducing valve core can effectively cover the flow area of the first valve core oil passage hole 2-2.8, reduce the oil flow out of the pressure reducing valve core, and thus reduce the oil pressure after the pressure reducing valve core. When the oil pressure and the elastic restoring force of the spring 7 are balanced, the pressure reducing valve core 6 stops moving, and the pressure reducing valve core outputs constant flow and pressure to the thin-wall throttle hole 3.

[0041] The oil liquid from the pressure reducing valve core 6 is discharged through the thin-wall throttle hole 3 at the main nozzle 2-1, the main nozzle 2-1 and the rotary baffle 1 form a variable opening throttle, and the main nozzle works according to the throttle principle, and adjusts the flow of the main nozzle according to the input baffle displacement signal. When the rotary baffle moves to the right, the distance between the baffle and the main nozzle decreases, the flow of the main nozzle decreases, the oil pressure in the main nozzle increases, and acts on the first valve core shoulder 2-2.1 through the third valve core oil hole 2-2.5, drives the valve core to move to the right. When the rotary baffle moves to the left, the distance between the baffle and the main nozzle increases, the flow of the main nozzle increases, the oil pressure in the main nozzle decreases, and acts on the first valve core shoulder 2-2.1 through the third valve core oil hole 2-2.5, drives the valve core to move to the left.

[0042] The radial distance between the main valve core 2-2 and the valve sleeve 4 is less than 0.2mm, which reduces the friction of the main valve core movement and improves the smoothness of the movement.

[0043] The ratio of the diameter of the nozzle hole 2-1.1 of the main nozzle 2-1 to the diameter of the thin-wall throttle hole 3 is 1.25, which improves the sensitivity of the nozzle-baffle control.

[0044] The stiffness of the spring 7 can be changed to adjust the working pressure of the oil liquid after the pressure reducing valve.

[0045] The distance between the main nozzle 2-1 and the rotary baffle 1 is less than 0.1mm, which reduces the leakage of the control oil liquid and improves the system working efficiency.

[0046] The angle of the outflow conical wall 2-1.5 of the main nozzle 2-1 is 74°, and the diameter of the outflow annular wall 2-1.4 is less than 1.5mm, which improves the flowability of the oil liquid and enhances the sensitivity of the control.

[0047] The utility model differs from traditional nozzle-baffle hydraulic amplifier and spool hydraulic amplifier, the novel amplifier structure integrates nozzle-baffle structure and valve core-valve sleeve structure on single part, not only realizes the effect that space size is small, structure is compact, has the characteristics such as big output flow, good linearity, small driving force.

[0048] The utility model discloses to the problem that nozzle cavity oil liquid is vulnerable to oil supply pressure fluctuation and poor anti-interference ability caused by the integrated design of compact hydraulic amplifier, adopts novel pressure reducing valve core structure, reduces oil liquid working pressure through the throttling effect of pressure reducing valve core, suppresses the influence of oil supply pressure fluctuation, improves the reliability of compact hydraulic amplifier.

[0049] The above specific embodiments or cases are only used to explain and illustrate the technical solutions of the present application, and are not intended to limit the present application, and the parts not described in detail are regarded as conventional technical means or common knowledge in the art; It can be understood by those skilled in the art that: based on the design idea of the present application, the technical solutions recorded in the foregoing embodiments can be modified adaptively, or some or all of the technical features can be replaced by equivalents, and these modified, equivalent, adaptive improved technical solutions do not deviate from the technical essence of the present application, and should be covered within the protection scope of the present application.

Claims

1. A compact hydraulic amplifier characterized by, The pressure reducing valve core assembly, the orifice-nozzle-flapper assembly and the power slide valve assembly are included, the pressure reducing valve core assembly includes a pressure reducing valve core, a spring and a first retainer; the orifice-nozzle-flapper assembly includes a rotating flapper, a main nozzle and a thin wall orifice; the power slide valve assembly includes a main valve core, a valve sleeve, a housing, a gasket and a second retainer.

2. A compact hydraulic amplifier as claimed in claim 1, characterized in that The thin wall orifice is fixed in the thin wall orifice mounting hole in the main valve core.

3. A compact hydraulic amplifier as claimed in claim 1, characterized in that The rotating flapper and the main nozzle are mounted in the inner hole of the housing and can move axially in the inner hole of the housing, the movement distance of the rotating flapper is limited by the two side end faces of the inner hole of the housing.

4. A compact hydraulic amplifier as claimed in claim 1, characterized in that The pressure reducing valve core, the spring and the first retainer are mounted in the inner hole of the main valve core and are positioned by the end face of the inner hole of the main valve core and the end face of the retainer mounting groove, the pressure reducing valve core can move axially in the inner hole.

5. A compact hydraulic amplifier according to claim 1 or 4, characterised in that The main valve core is mounted in the inner holes of the housing and the valve sleeve and can move axially in the inner holes of the housing and the valve sleeve.

6. A compact hydraulic amplifier as claimed in claim 5, characterized in that The valve sleeve is mounted in the inner hole of the housing and is positioned by the gasket and the second retainer.

7. A compact hydraulic amplifier as claimed in claim 1, characterized in that The radial distance between the main valve core and the valve sleeve is less than 0.2mm.

8. A compact hydraulic amplifier as claimed in claim 1, characterized in that The ratio of the nozzle hole diameter of the main nozzle to the diameter of the thin wall orifice is 1.

25.

9. A compact hydraulic amplifier as claimed in claim 8, characterized in that The distance between the main nozzle and the rotating flapper is less than 0.1mm.

10. A compact hydraulic amplifier as claimed in claim 9, characterized in that The angle of the outflow conical wall of the main nozzle is 74° and the diameter of the outflow annular wall is less than 1.5mm.

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