CN111878477A - Flow type non-leakage superposition double-balance valve - Google Patents
Flow type non-leakage superposition double-balance valve Download PDFInfo
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- CN111878477A CN111878477A CN202010771029.5A CN202010771029A CN111878477A CN 111878477 A CN111878477 A CN 111878477A CN 202010771029 A CN202010771029 A CN 202010771029A CN 111878477 A CN111878477 A CN 111878477A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/021—Valves for interconnecting the fluid chambers of an actuator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/023—Excess flow valves, e.g. for locking cylinders in case of hose burst
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/024—Pressure relief valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/027—Check valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/08—Servomotor systems incorporating electrically operated control means
- F15B21/087—Control strategy, e.g. with block diagram
Abstract
The invention discloses a flow type non-leakage superposed double-balance valve, which belongs to a balance valve. Compared with the prior art, the flow type non-leakage superposition double-balance valve has multiple functions of non-leakage pressure maintaining, pressure pre-relief and the like, can enable the oil cylinder to stay at any position for a long time without leakage, has the characteristics of randomly set time length of the pressure pre-relief, reduction of system power consumption and the like, and has good popularization and application values.
Description
Technical Field
The invention relates to a balance valve, in particular to a flow type non-leakage superposition double balance valve.
Background
Balance valves are called load holding valves, load control valves and the like abroad, are usually used in a hydraulic system with an oil cylinder moving in an amplitude manner, control load operation to be stable, prevent the oil cylinder from stalling and prevent the load from reliably staying at any position when the oil cylinder stops operating, but most of the existing hydraulic balance valves are pressure type balance valves which cannot be used for long-time pressure maintaining and have large power loss; although the FD series flow type balance valve in Germany technology can be used for pressure maintaining and power consumption reduction, the problem of creeping when a loaded oil cylinder vertically runs can be solved by matching with a one-way throttle valve under certain working conditions, and the FD series balance valve is difficult to be processed into a stacked double balance valve structure which can be arranged on an integrated oil circuit block below a reversing valve.
Disclosure of Invention
The technical task of the invention is to provide a flow type non-leakage superposed double-balance valve aiming at the defects in the prior art, the flow type non-leakage superposed double-balance valve has multiple functions of non-leakage pressure maintaining, pressure pre-relief and the like, and has the characteristics that an oil cylinder can stay at any position for a long time, the pressure pre-relief time is set at will, and the power consumption of a system is reduced.
The technical scheme adopted by the invention for solving the technical problems is as follows: the balance valve plug-in components are arranged in jacks at the left side and the right side of the valve body respectively, and the control piston is arranged in an inner hole of the valve body in the middle of the two balance valve plug-in components.
The two balance valve plug-ins are respectively a cavity A balance valve plug-in and a cavity B balance valve plug-in, the cavity A balance valve plug-in and the cavity B balance valve plug-in are the same in structure and are symmetrically arranged, and the cavity A plug-in and the cavity B plug-in are respectively arranged in a cavity A jack on the left side of the valve body and a cavity B jack on the right side of the valve body.
The A-cavity balance valve plug-in comprises an adjusting screw, a back nut, a gland, an adjusting rod, a thread pressing sleeve, a spring seat, a balance valve spring, a valve sleeve, a valve core limiting pad, a valve core reset spring, a push rod, a one-way valve steel ball and a steel wire clamping ring, wherein the valve core is arranged in the valve sleeve, the circumferential sharp corner at the right side of the valve core is tightly attached to the inner conical surface of the valve sleeve by the reset force of the valve core reset spring, the valve core reset spring is arranged in a cavity between the valve core and the valve core limiting pad, the one-way valve steel ball is arranged in the one-way valve hole in the radial direction of the valve core, the steel wire clamping ring is arranged in a groove at the position corresponding to the one-way valve hole on the circumference of the valve core, the push rod is arranged in a middle hole of the valve core, make the valve barrel right-hand member face paste tight jack bottom, be provided with the radial A1 oil duct of valve barrel and the radial A oil duct of valve barrel on the valve barrel, the valve barrel left side that the spacing pad of case set up in screw thread pressure cover right side hole, the push rod passes through the spacing pad intermediate hole of case and acts on left spring holder, be provided with the spring holder oil duct on the spring holder, the spring holder sets up in screw thread pressure cover hole, be provided with balanced valve spring between spring holder and the gland, be provided with the regulation pole in the middle of the balanced valve spring, it sets up in the gland to adjust the pole left end, the gland left end is back of the body nut, adjusting screw sets up in.
An inner valve core reset spring and an outer valve core reset spring are arranged in a cavity between the valve core and the valve core limiting pad.
The gland is in threaded connection with the threaded gland sleeve.
Check rings and O-shaped sealing rings are arranged between the thread pressing sleeve and the valve body, between the valve sleeve and the thread pressing sleeve, between the thread pressing sleeve and the gland, and between the adjusting rod and the gland, and O-shaped sealing rings are arranged between the valve core and the valve sleeve, between the push rod and the valve core, between the control piston and the valve body and in grooves on the upper end surface of the valve body.
The contact position of the inner conical surface of the valve sleeve and the circumferential sharp angle of the valve core is sealed by a conical surface.
The contact position of the one-way valve steel ball and the inner conical surface of the one-way valve hole is sealed by a spherical surface.
Compared with the prior art, the flow type non-leakage superposition double-balance valve has the following outstanding beneficial effects: the pressure relief function can set the pressure relief duration at will through an electric control system, and reduce hydraulic impact and pipeline vibration during reversing; the oil cylinder can stay at any position for a long time due to the leakage-free pressure maintaining function; when the balance function of the balance valve is in effect, the flow passing through the balance valve is automatically adjusted along with the pressure and the flow on the oil inlet side of the execution element; fourthly, the maximum flow when the balance function of the balance valve is in effect can be set through the adjusting screw, and no one-way throttle valve is additionally added in the pipeline: and fifthly, the oil pressure which acts on the control piston to gradually open the balance valve core is in a certain value interval, and the influence of the load is extremely small and negligible, so that the power consumption of the system can be reduced, and the application field is wider than that of the FD series balance valve. Therefore, the single balance valve or the double balance valve adopting various connection modes (tubular connection, plate connection, flange connection and superposed connection) of the structure can be used as a hydraulic control pressure relief valve, a hydraulic control one-way throttle valve and the like and can be widely applied to hydraulic systems of walking equipment and various fixed equipment in various industries such as loaders of engineering machinery, garbage trucks of cranes and sanitation equipment and the like.
Drawings
FIG. 1 is a schematic structural diagram of a flow type non-leakage superimposed double-balanced valve;
FIG. 2 is an enlarged schematic view of the balanced valve insert of Chamber A;
FIG. 3 is a hydraulic schematic diagram of a typical application of a flow type non-leakage stacked double-balanced valve;
FIG. 4 is a force analysis diagram of valve cores and push rods of the cavity A and the cavity B of the flow type non-leakage superposition double-balance valve in FIG. 3;
description of reference numerals: 1. an adjusting screw, 2, a back-tightening nut, 3, a gland, 4, a retainer ring, 5, an O-shaped sealing ring, 6, a threaded pressing sleeve, 7, a balance valve spring, 8, an adjusting rod, 9, a spring seat, 10, a valve core return spring, 11, a valve core limiting pad, 12, a valve sleeve, 13, a one-way valve hole, 14, a valve sleeve radial A1 oil duct, 15, a one-way valve steel ball, 16, a valve core, 17, a valve sleeve radial A oil duct, 18, a push rod, 19, a push rod axial oil duct, 20, a valve sleeve radial pressure relief hole, 21, a valve core control edge, 22, a steel wire collar, 23, a push rod radial damping hole, 24, an oil duct, 25, a control piston oil duct, 26, a control piston, 27, a valve body, 28, a cavity A balance valve insert, 29, a cavity B balance valve insert, 30, a variable amplitude oil cylinder, 31, a flow type non-leakage superposition double balance valve, 32, 34. hydraulic pump, 35, oscillating load.
Detailed Description
The flow type leakless stacked double balanced valve of the present invention is described in detail below with reference to the accompanying drawings of the specification 1 to 4.
The flow type non-leakage superposition double-balance valve structurally comprises a cavity A balance valve plug-in 28, a cavity B balance valve plug-in 29, a valve body 27 and a control piston 26; the cavity A balance valve plug-in unit and the cavity B balance valve plug-in unit are identical in structure and are symmetrically arranged, the cavity A balance valve plug-in unit 28 and the cavity B balance valve plug-in unit 29 are respectively arranged in a cavity A jack on the left side of the valve body and a cavity B jack on the right side of the valve body, and the control piston 26 is arranged in a hole 27 in the middle of the two balance valve plug-in units.
The chamber a balanced valve insert comprises: the device comprises an adjusting screw 1, a back nut 2, a gland 3, an adjusting rod 8, a thread pressing sleeve 6, a spring seat 9, a balance valve spring 7, a valve sleeve 12, a valve core 16, a valve core limiting pad 11, a valve core return spring 10, a push rod 18, a one-way valve steel ball 15 and a steel wire retainer ring 22. The following description is made with respect to the cavity a balanced valve insert 28 of fig. 2: the valve core 16 is arranged in the valve sleeve 12, the circumference sharp corner at the right side of the valve core 16 is tightly attached to the inner conical surface of the valve sleeve 12 by the resetting force of the valve core resetting spring 10, the valve core resetting spring 10 is arranged in a cavity between the valve core 16 and the valve core limiting cushion 11, an inner valve core resetting spring 10 and an outer valve core resetting spring 10 are arranged for preventing the springs from being accidentally broken, a one-way valve steel ball 15 is arranged in a one-way valve hole 13 in the radial direction of the valve core 16, a steel wire clamping ring 22 is arranged in a groove at the position corresponding to the one-way valve hole 13 on the circumference of the valve core 16 and used for limiting the moving range of the one-way valve steel ball 15 in the one-way valve hole 13, a push rod 18 is arranged in a middle hole of the valve core 16, a push rod axial oil duct 19 and a push rod radial damping hole 23 are arranged on the push rod 18, be provided with radial A1 oil duct 14 of valve barrel and the radial A oil duct 17 of valve barrel on the valve barrel 12, case spacing pad 11 sets up the valve barrel 12 left side in screw thread press sleeve 6 right side hole, push rod 18 acts on left spring holder 9 through the middle hole of case spacing pad 11, be provided with spring holder oil duct 24 on the spring holder 9, spring holder 9 sets up in screw thread press sleeve 6 hole, be provided with balanced valve spring 7 between spring holder 9 and the gland 3, be provided with in the middle of balanced valve spring 7 and adjust pole 8, it sets up in gland 3 to adjust the pole 8 left end, threaded connection between gland 3 and the screw thread press sleeve 6, gland 3 left end is back-up nut 2, adjusting screw 1 sets up in adjusting pole 8 left sides, with gland 3 and back-up nut 2 threaded connection.
The valve body 27 is provided with an oil cavity A, an oil cavity A1, an oil cavity B and an oil cavity B1, and is also provided with a pressure oil cavity P, an oil return cavity T and a connecting screw hole which are communicated with each other from top to bottom, and a control oil inlet cavity X, a control oil return cavity Y, an oil drainage cavity L and the like which are communicated with each other from top to bottom are also arranged on the valve with a larger drift diameter.
Check rings 4 and O-shaped sealing rings 5 are arranged between the thread pressing sleeve 6 and the valve body 27, between the valve sleeve 12 and the thread pressing sleeve 6, between the thread pressing sleeve 6 and the gland 3 and between the adjusting rod 8 and the gland 3, and O-shaped sealing rings 5 are arranged between the valve core 16 and the valve sleeve 12, between the push rod 18 and the valve core 16, between the control piston 26 and the valve body 27 and in grooves in the upper end face of the valve body 27.
The contact position of the inner conical surface of the valve sleeve 12 and the circumferential sharp angle of the valve core 16 is sealed by a conical surface. The contact position of the one-way valve steel ball 15 and the inner conical surface of the one-way valve hole 13 is sealed by a spherical surface.
Referring to fig. 1 to 4, the stress and working conditions of the valve core 16 and the push rod 18 of the flow type non-leakage superposition double-balanced valve 31 are analyzed as follows:
setting: the stress areas of the left side and the right side of the A-cavity valve core 16 are equal and are SA (annular area), the stress area of the A-cavity push rod 18 is the circular area of the middle non-section line part of the SA, the left side of PA represents the oil pressure of the left side of the A-cavity valve core 16, and the right side of PA represents the oil pressure of the right side of the A-cavity valve core 16.
The oil thrust of the cavity B on the right side of the control piston 26 is F-controlled B, the reset force F4A of the cavity A balance valve spring 7 and the friction force of the cavity A push rod 18 are ignored.
The right side oil liquid acting force FA of the A cavity valve core 16 is PA right multiplied by SA, the left side oil liquid acting force FA of the A cavity valve core 16 is PA left multiplied by SA, the sum of the reset forces of the A cavity inner and outer valve core reset springs 10 is F1A, the valve core friction force F2A, the A cavity valve port hydraulic force and the like is F3A. The left axial resultant force of the A cavity push rod 18 is F push A, and the left axial resultant force of the A cavity valve core 16 is FA.
Force analysis of the cavity a push rod 18:
in fig. 3, when both coils YV1, YV2 are de-energized: f push A is 0
Energizing YV 2: when PA right is PA left is 0 and delta 1 is 0, F pushes A to F control B-F4A-F1A-F2A-F3A
Energizing YV 1: the design requirement is that the A-cavity push rod 18 can move freely in the axial direction in a specified range in the inner hole of the valve core 16, F4A is greater than F1A, the axial distance between the left end face of the right disc of the push rod 18 and the right end face of the A-cavity valve core 16 is delta 1, PB left is 0, namely F control B is 0, the A-cavity push rod 18 cannot overcome the reset force F4A of the balance valve spring 7 to move leftwards under the action of oil pressure, namely F push A is 0.
Force analysis of the a-chamber spool 16:
f push a is 0, F control B is 0, a cavity valve core 16 is not controlled by the push rod 18, FA right-FA left-F1A-F2A-F3A (PA right-PA left) x SA-F1A-F2A-F3A
When the a-chamber push rod 18 moves left together with the a-chamber valve element 16 by pushing F, FA is pushed F to a
FIG. 3 when both coils YV1, YV2 are de-energized: f equals 0, PA equals 0, and the a-chamber spool 16 is closed by F1A.
Fig. 3 shows that when coil YV2 is energized and Δ 1 is equal to 0: when F control B is greater than F1A + F2A + F3A + F4A, the valve core 16 moves leftwards to be opened, the valve core 16 of the A cavity is opened under the control of the B cavity, and the function of a balance valve is realized.
Fig. 3 coil YV1 is energized: f is 0, PA right > PA left, FA (PA right-PA left) x SA-F1A-F2A-F3A, and when FA > 0, the valve element 16 opens to realize the function of the check valve.
Setting: the left and right stress areas of the B-cavity valve core 16 are equal and are SB (annular area), the stress area of the B-cavity push rod 18 is the circular area of the middle non-section line part of SB, the PB left side represents the oil pressure at the left side of the B-cavity valve core 16, and the PB right side represents the oil pressure at the right side of the B-cavity valve core 16.
The oil thrust of the cavity A on the left side of the control piston 26 is F control A, the reset force F4B of the cavity B balance valve spring 7 is ignored, and the friction force of the cavity B push rod 18 is ignored.
The left oil acting force FB of the B-cavity valve element 16 is PB left × SB, the right oil acting force FB of the B-cavity valve element 16 is PB right × SB, the sum of the return forces of the B-cavity inner and outer valve element return springs 10 is F1B, the valve element friction force is F2B, and the B-cavity valve port hydraulic force is F3B. The resultant axial force of the push rod 18 in the cavity B to the right is F push B, and the resultant axial force of the valve core 16 in the cavity B to the right is FB.
B-cavity push rod 18 force analysis:
in fig. 3, when both coils YV1, YV2 are de-energized: f push B is 0
Energizing YV 1: when PB is 0 and Δ 1 is 0, F pushes B is F controlled a-F4B-F1B-F2B-F3B
Energizing YV 2: the design requirement is that the B-cavity push rod 18 can move freely in the axial direction in a specified range in an inner hole of the valve core 16, F4B is larger than F1B, the axial distance between the right end surface of the left disc of the push rod 18 and the left end surface of the B-cavity valve core 16 is delta 1, when PA is right 0, namely F control A is 0, the B-cavity push rod 18 can not overcome the reset force F4B of the balance valve spring 7 to move right under the action of oil pressure, namely F push B is 0.
B-cavity spool 16 force analysis:
f push B is 0, F control a is 0, B chamber spool 16 is not controlled by push rod 18, FB left-FB right-F1B-F2B-F3B (PB left-PB right) × SB-F1B-F2B-F3B
When the B-chamber push rod 18 moves to the right together with the B-chamber spool 16 by pushing F, FB pushes B together with F
FIG. 3 when both coils YV1, YV2 are de-energized: f push B is 0, PB left is PB right is 0, and the B-chamber spool 16 is closed by F1B.
Fig. 3 shows that when coil YV1 is energized and Δ 1 is equal to 0: and when F control A is greater than F1B + F2B + F3B + F4B, the valve core 16 moves right to be opened, and the valve core 16 of the B cavity is controlled to be opened by the A cavity to realize the function of a balance valve.
Fig. 3 coil YV2 is energized: f push B is 0, PB left > PB right, FB (PB left-PB right) × SB-F1B-F2B-F3B, and when FB > 0, the valve element 16 opens to realize the function of the check valve.
In fig. 3, when the electromagnetic directional valve 32 is in the neutral position (i.e., both YV1 and YV2 are powered off), no pressure exists in the oil chamber a and the oil chamber B in the flow type non-leakage superposition double-balanced valve 31 (the internal structure is shown in fig. 2), and the pressures in the oil chamber a1 and the oil chamber B1 are determined by the stop position of the luffing cylinder 30 and the size of the swing load 35; in the chamber a balanced valve insert 28: the oil cavity A is communicated with a cavity formed between an inner hole of the valve core 16 and an excircle of the push rod 18 and a return spring cavity at the left end of the valve core 16 through a control piston oil duct 25 at the left end of a control piston 26, a push rod axial oil duct 19, a push rod radial damping hole 23, an oil duct formed between the inner hole of the valve core 16 and the excircle of the push rod, and the return spring cavity at the left end of the valve core 16 is communicated with a cavity where the balance valve spring 7 is communicated through an inner hole at the left side of the valve core limiting pad 11, a spring seat oil duct 24, an oil duct formed between an inner hole of the threaded pressing sleeve. Because the inner conical surface of the valve sleeve 12, which is in contact with the sharp corner on the right side of the valve core 16, is formed by one-time clamping and grinding with the inner hole on the left side of the valve sleeve 12, the left and right outer circles of the valve core 16 have the same size, and are also formed by one-time clamping and grinding with the right end surface of the sharp corner, when the pressure of the A1 cavity is greater than the pressure of the A cavity, the steel ball 15 of the check valve is tightly contacted and sealed with the inner conical surface of the check valve hole 13 and is in a reverse cut-off state, the stress areas of the left and right sides of the valve core 16 are SA, the oil pressure PA right is PA and PA left is 0, therefore FA is less than 0, the valve core; the working conditions of the cavity B balance valve insert 29 and the cavity A balance valve insert 28 are completely the same, and oil in the oil cavity B1 cannot enter the oil cavity B; the luffing cylinder 30 is thus in a state of stopping pressure holding.
When the coil YV2 in the attached drawing is electrified, the electromagnetic directional valve 32 is switched to the right position, oil enters the superposition double-balance valve 31 from the oil cavity B and returns to the oil tank from the oil cavity A, and the cavity B balance valve plug-in part 29 in the attached drawing 2: the oil entering from the oil cavity B passes through the control piston oil duct 25 on the right side of the control piston 26, the push rod axial oil duct 19, the push rod radial damping hole 23, a cavity between the inner hole of the valve core 16 and the outer circle of the push rod 18 and a spring cavity at the right end of the valve core 16, and simultaneously pushes the check valve steel ball 15 in the check valve hole 13 to flow into the oil duct B1, because the oil passing flow of the push rod radial damping hole 23 is far smaller than that of the oil inlet hole of the check valve hole 13 below the check valve steel ball 15, pressure difference is formed at the left end and the right end of the valve core 16, PB left is larger than PB right, the oil in the oil cavity B pushes the valve core 16 open by overcoming the acting force F1B of the valve. As the chamber B pressure PB rises to the left, the oil force F on the right side of the control piston 26 moves it to the left. Side a balanced valve insert 28: the right end of the push rod 18 is contacted with the control piston 26 pushed by the F control B and then moves leftwards together, and because an axial gap with the distance delta 1 is formed between the left side of a disc at the right end of the push rod 18 and the right end face of a right side step of the valve core 16, the control piston 26 and the push rod 18 continuously move leftwards and move leftwards by the distance delta 1 (namely, delta 1 is equal to 0) through the spring seat 9 by overcoming the acting force F4A of the balance valve spring 7, and then the push rod 18 is contacted with the right end face of the right side step of the valve core 16, so that the valve core 16 is driven; when the pressure PB of the oil chamber B is increased to P1 on the left, the circumferential sharp corner of the right end of the valve core 16 is separated from the inner conical surface of the valve sleeve 12, the oil in the oil chamber a1 flows into the oil chamber a through the valve sleeve radial pressure relief hole 20, pre-pressure relief of the oil chamber a1 is realized, as the PB left side is continuously increased, the valve core 16 continuously moves to the left by delta 2 (delta 2 is the covering amount of the valve core control edge 21 and the valve sleeve radial a1 oil passage 14, namely the oil sealing length), at this moment, the PB left is equal to P2, the valve core control edge 21 opens the valve sleeve radial a1 oil passage 14, the oil in the oil chamber a1 flows into the oil chamber a through the opening formed by the valve sleeve radial a1 oil passage 14 and the valve core control edge 21 and the valve sleeve radial pressure relief hole 20, as the PB left side is continuously increased again, the valve core 16 continuously moves to the left, the opening formed by the valve core control edge 21 and the valve sleeve radial a1 oil passage 14 is gradually increased, the flow rate of the oil chamber a1 is Until the nodal rods 8 touch. From the above analysis it follows that: when PB is not more than P1 and left is less than P2, the oil chamber A1 is in a pressure pre-relief state, the amplitude variation oil cylinder 30 retracts slightly, and the pressure pre-relief time length can be adjusted at will through an electric control system; when PB is not less than P2 and P3, the retraction speed of the luffing cylinder 30 (namely the flow rate of oil flowing from the oil chamber A1 to the oil chamber A) is determined by the opening size of the valve core control edge 21 and the flow rate of oil flowing from the oil chamber B to the luffing cylinder 30, and the maximum flow rate is controlled by the position of the adjusting rod 8 set by the adjusting screw 1.
In the attached figure 3, when the coil YV1 is electrified, the electromagnetic directional valve 32 is switched to the left position, oil enters the flow type non-leakage superposed double-balance valve 31 from the oil chamber A, and the oil chamber B returns to the oil tank, the working principle of the superposed double-balance valve 31 is the same as that when the coil YV2 is electrified, the oil in the oil chamber A can freely flow into the oil chamber A1, the valve core 16 in the B chamber balance valve plug-in piece 29 moves to the right under the action of the control piston 26 and the push rod 18, and the amplitude-variable oil cylinder 30 extends out.
The maximum working pressure of the flow type non-leakage superposition double-balance valve can reach 40 MPa.
In the hydraulic schematic diagram of fig. 3, YV2 is powered on, when the pressure PB left of the oil chamber B is greater than P1 and 2.5MPa, the control piston 26 drives the push rod 18 in the a chamber balance valve plug 28 to push the valve element 16 to move left, after Δ 2 is moved left, PB left is P2 and 3.7MPa, the oil chamber a1 realizes pressure relief through the valve sleeve radial pressure relief hole 20 in the process that P1 is greater than or equal to PB left and less than P2, when PB left is greater than or equal to P2 and 3.7MPa, the valve element control edge 21 gradually opens the passage from the oil chamber a1 to the oil chamber a, the oil flow rate in this section is approximately linearly increased, PB left is greater than P3 and 6MPa, and the valve element 16 is fully opened when the adjusting rod 8 is at the leftmost position without throttling. The control pressure PB of the oil chamber B required by the valve core 16 to move leftwards in the cavity A balance valve plug-in 28 is a constant value between 2.5MPa and 6MPa, theoretically, the pressure interval value is not influenced by load, and the pressure interval value can be changed by replacing the balance valve spring 7. The three-stage electromagnetic overflow valve 33 can realize three pressure regulation through the on-off states of the coils YV3 and YV4, can regulate the pressure of a pilot overflow valve to be 3MPa when the YV3 is electrified, can set the pressure relief time of the oil cavity A1 or the oil cavity B1 by controlling the electrifying time length of the YV3, can set the pressure of the pilot overflow valve to be a fixed value between 3.7MPa and 6MPa when the YV4 is electrified according to the needs of a system to control the operation speed of the amplitude cylinder 30 at a certain stage, and can set the main pressure when the YV3 and the YV4 are both powered off to be the maximum working pressure or the safe pressure of the system.
The above-mentioned embodiments are only for understanding the present invention, and are not intended to limit the technical solutions of the present invention, and those skilled in the art can make various changes or modifications based on the technical solutions described in the claims, and all equivalent changes or modifications should be covered by the scope of the claims of the present invention. The present invention is not described in detail, but is known to those skilled in the art.
Claims (8)
1. Flow type does not have two balanced valves of leakage stack, characterized by: the balance valve plug-in components are arranged in jacks at the left side and the right side of the valve body respectively, and the control piston is arranged in an inner hole of the valve body in the middle of the two balance valve plug-in components.
2. The flow-type no-leak stacked double balanced valve of claim 1, wherein: the two balance valve plug-ins are respectively a cavity A balance valve plug-in and a cavity B balance valve plug-in, the cavity A balance valve plug-in and the cavity B balance valve plug-in are the same in structure and are symmetrically arranged, and the cavity A plug-in and the cavity B plug-in are respectively arranged in a cavity A jack on the left side of the valve body and a cavity B jack on the right side of the valve body.
3. The flow-type no-leak stacked double balanced valve of claim 2, wherein: the A-cavity balance valve plug-in comprises an adjusting screw, a back nut, a gland, an adjusting rod, a thread pressing sleeve, a spring seat, a balance valve spring, a valve sleeve, a valve core limiting pad, a valve core reset spring, a push rod, a one-way valve steel ball and a steel wire clamping ring, wherein the valve core is arranged in the valve sleeve, the circumferential sharp corner at the right side of the valve core is tightly attached to the inner conical surface of the valve sleeve by the reset force of the valve core reset spring, the valve core reset spring is arranged in a cavity between the valve core and the valve core limiting pad, the one-way valve steel ball is arranged in the one-way valve hole in the radial direction of the valve core, the steel wire clamping ring is arranged in a groove at the position corresponding to the one-way valve hole on the circumference of the valve core, the push rod is arranged in a middle hole of the valve core, make the valve barrel right-hand member face paste tight jack bottom, be provided with the radial A1 oil duct of valve barrel and the radial A oil duct of valve barrel on the valve barrel, the valve barrel left side that the spacing pad of case set up in screw thread pressure cover right side hole, the push rod passes through the spacing pad intermediate hole of case and acts on left spring holder, be provided with the spring holder oil duct on the spring holder, the spring holder sets up in screw thread pressure cover hole, be provided with balanced valve spring between spring holder and the gland, be provided with the regulation pole in the middle of the balanced valve spring, it sets up in the gland to adjust the pole left end, the gland left end is back of the body nut, adjusting screw sets up in.
4. A flow-type no-leak stacked double balanced valve as claimed in claim 3, wherein: an inner valve core reset spring and an outer valve core reset spring are arranged in a cavity between the valve core and the valve core limiting pad.
5. A flow-type no-leak stacked double balanced valve as claimed in claim 3, wherein: the gland is in threaded connection with the threaded gland sleeve.
6. A flow-type no-leak stacked double balanced valve as claimed in claim 3, wherein: check rings and O-shaped sealing rings are arranged between the thread pressing sleeve and the valve body, between the valve sleeve and the thread pressing sleeve, between the thread pressing sleeve and the gland, and between the adjusting rod and the gland, and O-shaped sealing rings are arranged between the valve core and the valve sleeve, between the push rod and the valve core, between the control piston and the valve body and in grooves on the upper end surface of the valve body.
7. A flow-type no-leak stacked double balanced valve as claimed in claim 3, wherein: the contact position of the inner conical surface of the valve sleeve and the circumferential sharp angle of the valve core is sealed by a conical surface.
8. A flow-type no-leak stacked double balanced valve as claimed in claim 3, wherein: the contact position of the one-way valve steel ball and the inner conical surface of the one-way valve hole is sealed by a spherical surface.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010771029.5A CN111878477A (en) | 2020-08-04 | 2020-08-04 | Flow type non-leakage superposition double-balance valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010771029.5A CN111878477A (en) | 2020-08-04 | 2020-08-04 | Flow type non-leakage superposition double-balance valve |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN111878477A true CN111878477A (en) | 2020-11-03 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010771029.5A Pending CN111878477A (en) | 2020-08-04 | 2020-08-04 | Flow type non-leakage superposition double-balance valve |
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| Country | Link |
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| CN (1) | CN111878477A (en) |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201496335U (en) * | 2009-09-09 | 2010-06-02 | 四川神坤装备股份有限公司 | Automatic balancing valve |
| CN202023780U (en) * | 2011-03-21 | 2011-11-02 | 蒋晓军 | Pressure-reducing type balance hydraulic lock |
| CN206111712U (en) * | 2016-09-08 | 2017-04-19 | 上海圣克赛斯液压机械有限公司 | Two balanced valve valvess of stack formula |
| CN208565121U (en) * | 2018-07-12 | 2019-03-01 | 宁波善研液压有限公司 | Balanced valve |
| CN210637304U (en) * | 2019-08-16 | 2020-05-29 | 石家庄市液压有限责任公司 | Balance valve with double-flow control |
-
2020
- 2020-08-04 CN CN202010771029.5A patent/CN111878477A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201496335U (en) * | 2009-09-09 | 2010-06-02 | 四川神坤装备股份有限公司 | Automatic balancing valve |
| CN202023780U (en) * | 2011-03-21 | 2011-11-02 | 蒋晓军 | Pressure-reducing type balance hydraulic lock |
| CN206111712U (en) * | 2016-09-08 | 2017-04-19 | 上海圣克赛斯液压机械有限公司 | Two balanced valve valvess of stack formula |
| CN208565121U (en) * | 2018-07-12 | 2019-03-01 | 宁波善研液压有限公司 | Balanced valve |
| CN210637304U (en) * | 2019-08-16 | 2020-05-29 | 石家庄市液压有限责任公司 | Balance valve with double-flow control |
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