CN103791129B - The traveling control load valve that a kind of closed type hydraulic system drives - Google Patents
The traveling control load valve that a kind of closed type hydraulic system drives Download PDFInfo
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- CN103791129B CN103791129B CN201410071125.3A CN201410071125A CN103791129B CN 103791129 B CN103791129 B CN 103791129B CN 201410071125 A CN201410071125 A CN 201410071125A CN 103791129 B CN103791129 B CN 103791129B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
- F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
- F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
- F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
- F16K11/07—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides
- F16K11/0716—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides with fluid passages through the valve member
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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
- F15B13/026—Pressure compensating valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
- F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
- F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
- F16K17/048—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded combined with other safety valves, or with pressure control devices
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Safety Valves (AREA)
Abstract
The traveling control load valve that a kind of closed type hydraulic system drives, it comprises valve body (28), this valve body (28) interior setting-in valve plug-in unit (25), this interior setting-in valve pocket of valve plug-in unit (25) (12), embedded sealing ring between this valve pocket (12) left side and valve plug-in unit (25), this valve pocket (12) right side external diameter is less than the internal diameter of valve plug-in unit (25), this valve pocket (12) right hand external suit support spring (11), this support spring (11) outside pocketed springs cap (10), the outward flange of this spring compressor (10) coordinates with valve plug-in unit (25) inner surface, in valve plug-in unit (25), be positioned at the position setting-in main valve plug (26) of valve pocket (12) left end, the left end connecting positioning sleeve (24) of valve plug-in unit (25), the interior setting-in pressure piston of this valve liner (15) (16), this pressure piston (16) left end is equipped with pressure spring (22), this pressure spring (22) left end contacts with the left side of valve base seat (23). the traveling control load valve that closed type hydraulic system provided by the invention drives, it reaches the object of steady control operation traveling speed by the equilibrium relation of the spring force of the hydraulic coupling that forms on main valve plug and pressure piston and pressure spring.
Description
Technical field
The present invention relates to a kind of load valve, particularly a kind of load valve of the traveling control driving for closed type hydraulic system, belongs to engineering equipment technical field.
Background technology
Large-scale Railway road maintainance machinery adopts closed type hydraulic system to drive traveling conventionally, as shown in Figure 1, its operation principle is that diesel internal combustion engine (2) drives hydraulic pressure traveling pump (1) to provide power to hydraulic pressure traveling motor (6), overcome traveling load (7) mobile, fluid pumps shown in oral fluid flow path direction (4) and flow to hydraulic pressure traveling motor (6) by hydraulic pressure traveling pump (1) by traveling, gone out shown in oral fluid flow path direction (5), to flow back to hydraulic pressure traveling pump (1) by traveling motor again, thereby form Closed Hydraulic Driving system, traveling oil-supplementing system (3) carries out repairing to closed type hydraulic system, avoid the interior oil pressure deficiency of system and oil temperature too high.
In actual use, in the situation that three kinds of upward slope, level road or descendings are different, traveling load is different, and in descending process, traveling load is and oppositely puts on traveling hydraulic motor, and hydraulic motor outlet pressure and inlet pressure reduce, and traveling speed increases. Especially under job state, in the time that descending ramp angle is relatively large, load direction is contrary, the outlet pressure Pb of hydraulic motor reduces, and the exchange function of motor and pump, causes traveling speed more and more faster, even out of control, can not control hydraulic motor rotary speed by controlling hydraulic pump flow. Conventionally by artificial braking deceleration, or at automatically controlled counterbalance valve of motor Increasing exports, in the time that Pb is reduced to certain numerical value, in definite value back pressure of Increasing exports of motor, above-mentioned way can effectively prevent the traveling speed even generation of out-of-control condition that increases sharply, and needs but can not solve traveling speed the problem of steadily controlling.
Summary of the invention
The invention provides the traveling control load valve that a kind of closed type hydraulic system drives, it comprises valve body, setting-in valve plug-in unit in this valve body, setting-in valve pocket in this valve plug-in unit, embedded sealing ring between this valve pocket left side and described valve plug-in unit, this valve pocket right side external diameter is less than the internal diameter of described valve plug-in unit, this valve pocket right hand external suit support spring, pocketed springs cap outside this support spring, the outward flange of this spring compressor coordinates with described valve plug-in unit inner surface, in valve plug-in unit, be positioned at the position setting-in main valve plug of described valve pocket left end, the left end connecting positioning sleeve of described valve plug-in unit, setting-in valve base seat between described positioning sleeve and described valve plug-in unit outside and described body cavity, this valve base seat is equipped with valve liner, setting-in pressure piston in this valve liner, this pressure piston left end is equipped with pressure spring, this pressure spring left end contacts with the left side of described valve base seat.
Preferably, described valve base seat is the sealing of right-end openings left end, and the inner cylindrical structure that comprises cavity.
More preferably, the left side of described valve base seat comprises screw, and this screw is communicated with the cavity in described valve base seat.
More preferably, locking nut embeds in the screw of described valve base seat left side, the embedded joint push rod of debuging of described screw.
More preferably, two ends, described pressure spring left and right equal setting-in spring footstock, two equal setting-ins of spring footstock outer side center support steel ball, the support steel ball in the spring footstock outside of pressure spring right-hand member contacts with described pressure piston, the support steel ball in the spring footstock outside of pressure spring left end contacts with described adjusting push rod, and locking nut is screwed into or back-outs, and forces spring-compressed or loosens, thereby regulating spring elastic force, and then reach the object that regulating load sets value.
Preferably, described valve pocket comprises inner chamber I, and this inner chamber I is diameter-changing cavity, and the diameter at this inner chamber I middle part is less than the diameter of the right and left.
Preferably, described valve body comprises axial oil-in I, and described valve body side comprises oil-out I radially and oil return opening I radially, and described valve body side also comprises drain tap I radially.
Preferably, described valve base seat radially comprise drain tap II, this drain tap II is communicated with the drain tap I of described valve body, the drain tap I of described valve body is connected to fuel tank, thereby make the fluid of revealing under high pressure flow back into fuel tank from valve inner via drain tap II and drain tap I, avoid producing back pressure in valve body, the fluid of leakage can be collected into fuel tank, avoid waste and contaminated environment simultaneously.
Preferably, described valve base seat radially comprise oil-out II, this oil-out II is communicated with the oil-out I of described valve body.
More preferably, described valve base seat radially comprise drain tap III, this drain tap III is positioned at sidewall that valve base seat left end pressure spring is corresponding radially, to the fluid that is positioned at pressure piston left end in valve base seat is released, avoids producing back pressure, affects operating efficiency.
Preferably, what valve plug-in unit was positioned at main valve plug and described valve pocket coupling part radially comprises opening, and this opening is communicated with the oil return opening I of described valve body, so that the complete fluid that circulates is back in hydraulic pump.
Preferably, embedded sealing ring between described valve plug-in unit and described valve body.
Preferably, between described valve plug-in unit and spring compressor, flexible collar I is housed.
Preferably, described valve plug-in unit embeds described valve base seat right-hand member, and between described valve plug-in unit and described valve base seat, flexible collar II is housed.
Preferably, described main valve plug left end comprises the cylinder of protrusion, and the cylinder left end of this protrusion comprises groove radially.
Preferably, described positioning sleeve comprises inner chamber II, and this inner chamber II comprises cavity II ' and cavity II 〞, this cavity II ' be communicated with cavity II 〞, cavity II ' diameter be less than the diameter of cavity II 〞, cavity II ' be positioned on the left of cavity II 〞.
Preferably, described positioning sleeve right-hand member embeds in described valve plug-in unit, and described positioning sleeve right-hand member is positioned at described valve plug-in unit inner chamber and main valve plug outside, and described positioning sleeve is limited to described valve plug-in unit the right-hand member of positioning sleeve inside described valve body.
Preferably, described main valve plug embeds in the cavity II 〞 of described positioning sleeve, between the cavity II 〞 of the left end of described main valve plug and described positioning sleeve, form cavity V, the cylinder that described main valve plug left end protrudes through the cavity II of described positioning sleeve ', the cylinder outside that described main valve plug left end protrudes and described cavity II ' between embedded sealing ring.
Preferably, in described main valve plug, comprise inner chamber VI, this inner chamber VI is diameter-changing cavity, the central shaft of this inner chamber VI overlaps with the central shaft of described main valve plug, the diameter of this inner chamber VI left end is d, the diameter of inner chamber VI right-hand member is greater than the diameter of left end, and this inner chamber VI right-hand member connects by ramp way and upper left side, described main valve plug left side, thereby the inner chamber VI of main valve plug is communicated with described cavity V.
Preferably, comprise inner chamber III in described valve liner, this inner chamber III middle part comprises inside protrusion.
Preferably, described valve liner is positioned at described positioning sleeve left side, in the less inner chamber III that is partially submerged into described valve liner of described positioning sleeve left end diameter.
Preferably, setting-in pressure piston in the inner chamber III of described valve liner.
More preferably, described pressure piston comprises left part, middle part and right part three parts, and this left part, middle part and right part are structure as a whole.
More preferably, the external diameter of the left part of described pressure piston, middle part and right part reduces successively.
More preferably, setting-in y-shaped ring between described pressure piston left part and the inner chamber III of described valve liner.
More preferably, the right part of described pressure piston comprises inner chamber IV, the diameter of this inner chamber IV right-hand member is less than the diameter of left end, and the radial groove of the cylinder that described main valve plug left end protrudes embeds the less position of described inner chamber IV right-hand member diameter, thereby described main valve plug is connected with described pressure piston.
More preferably, the middle part of described pressure piston is inlaid in the protrusion position at the inner chamber III middle part of described valve liner, and between the protrusion at the inner chamber III of the middle part of described pressure piston and described valve liner middle part, sealing ring is housed.
The traveling control that closed type hydraulic system provided by the invention drives by the working method of load valve is: pressure spring is inlaid between spring footstock, due to the large fastening effect of locking nut, pressure spring is in compressive state, thereby generation elastic force, this elastic force is by the spring footstock on right side, supporting steel ball and pressure piston is applied on main valve plug, main valve plug is moved right and be adjacent to valve pocket, thereby the asphalt channel between oil-in I and oil return opening I is separated, the hydraulic oil at oil-in I place can not enter oil return opening I, but enter into inner chamber I and inner chamber VI through inner chamber I, thereby make oil-in I, be communicated with inner chamber V by inner chamber VI with inner chamber I.
Under action of hydraulic force, the hydraulic action that main valve plug is subject to equals the product of the cross-sectional area that the hydraulic pressures Pb of oil-in I is corresponding with main valve plug inner chamber VI left end diameter d, and direction left; The active force that the hydraulic pressures Ps of oil-out I forms pressure piston equals hydraulic pressures Ps and the product of pressure piston left part with the poor corresponding cross-sectional area of external diameter at middle part, and direction also left; When the hydraulic coupling that hydraulic coupling main valve plug being formed when oil-in I and oil-out I form pressure piston equals spring force left of pressure spring, main valve plug is in poised state, and by oil-in I, the valve port through between main valve plug and valve pocket stably flows to oil return opening I to hydraulic oil. In the situation that locking nut does not regulate, spring force size is constant, and now, as the pressure of crossing oil-out I place reduces, the pressure of oil-in I increases, otherwise the pressure of oil-in I reduces.
The oil-in I of load valve is connected with the outlet of hydraulic motor, the entrance of the oil-out I connecting fluid pressure motor of load valve, the oil return opening I of load valve is connected to the entrance of hydraulic pressure traveling pump, hydraulic pressure traveling pump is supplied with power by internal combustion engine, described hydraulic pressure traveling delivery side of pump is connected with the entrance of described hydraulic motor, described hydraulic motor also connects load, and described hydraulic pressure traveling pump also connects oil-supplementing system, and this form closed type hydraulic system.
In the time of upward slope or level road, the traveling load forward that closed type hydraulic system drives puts on hydraulic motor, the entrance pressure Pa(of hydraulic motor equals Ps) be greater than the pressure Pb at oil-in I place, hydraulic pump provides power drive traveling, by controlling the size of hydraulic pump output flow, can stablize control traveling speed; In the time of descending, traveling laod reversal puts on hydraulic motor, the entrance pressure Pa(of hydraulic motor equals Ps) and back pressure Pb reduction, now, the opening of load valve reduces, the resistance to flow output of hydraulic motor increases, back pressure Pb increases, thereby prevents that hydraulic motor from doing the used time at laod reversal, and the too small hydraulic motor speed that causes of Pb is increased sharply, reach the object of steady control traveling speed, the fluid of revealing in hydraulic oil cyclic process in load valve is back in fuel tank by drain tap I.
By adjusting lock nut and adjusting push rod, thereby the decrement of regulating spring, thereby the hydraulic pressures sum that changes oil-in I and oil-out I, to adapt to the requirement of different loads to hydraulic pressure, thereby makes described load valve can adapt to the traveling control of different loads situation.
More multioperation is all known for those of ordinary skills, repeats no more.
The traveling control that closed type hydraulic system provided by the invention drives comprises any combination of each part mentioned above by the technical scheme of load valve, the simple change of each part mentioned above assembly or combination are still protection scope of the present invention.
The traveling control load valve that closed type hydraulic system provided by the invention drives, it is by the equilibrium relation of the spring force of the hydraulic coupling that forms on main valve plug and pressure piston and pressure spring, reach control overhead valve and open big or small object, once traveling load reduces or oppositely, load valve opening pressure is large, the load applying is large, otherwise, the load applying is little, and regulating spring power can change the setting value of load. Thereby avoid motor load to reduce or oppositely time traveling speed uprush, prevent that the reverse traction phenomena of hydraulic motor from occurring, reaches the object of steady control operation traveling speed.
Brief description of the drawings
Fig. 1 is the traveling schematic diagram that in prior art, closed type hydraulic system drives;
Fig. 2 is according to the structural representation of a preferred embodiment of the traveling control load valve of closed type hydraulic system driving of the present invention;
Fig. 3 is that the traveling control load valve that closed type hydraulic system drives is installed schematic diagram;
Mark in Fig. 1-3 represents respectively:
1, hydraulic pressure traveling pump, 2, diesel internal combustion engine, 3, closed type hydraulic system traveling oil-supplementing system
4, oral fluid flow path direction is pumped in traveling, and 5, traveling motor goes out oral fluid flow path direction
6, hydraulic pressure traveling motor, 7, traveling load, 10, spring compressor, 11, support spring
12, valve pocket, 13, sealing ring, 14, flexible collar, 15, valve liner, 16, pressure piston
17, support steel ball, 18, drain tap, 19, locking nut, 20, regulate push rod
21, spring footstock, 22, pressure spring, 23, valve base seat, 24, positioning sleeve
25, valve plug-in unit, 26, main valve plug, 27, flexible collar, 28, valve body, 30, load valve.
Detailed description of the invention
In order to understand better the present invention, describe respectively the preferred embodiment of the traveling control load valve driving according to a kind of closed type hydraulic system of the present invention in detail below in conjunction with accompanying drawing, Fig. 2, Fig. 3 are structural representation and the installation schematic diagrams of a preferred embodiment of the traveling control load valve of a kind of closed type hydraulic system driving of the present invention.
Embodiment 1.1, the traveling control load valve that the present embodiment provides a kind of closed type hydraulic system to drive, it comprises valve body 28, the interior setting-in valve of this valve body 28 plug-in unit 25, the interior setting-in valve pocket 12 of this valve plug-in unit 25, embedded sealing ring between these valve pocket 12 left sides and valve plug-in unit 25, these valve pocket 12 right side external diameters are less than the internal diameter of valve plug-in unit 25, these valve pocket 12 right hand external suit support springs 11, these support spring 11 outside pocketed springs caps 10, the outward flange of this spring compressor 10 coordinates with valve plug-in unit 25 inner surfaces, in valve plug-in unit 25, be positioned at the position setting-in main valve plug 26 of valve pocket 12 left ends, the left end connecting positioning sleeve 24 of valve plug-in unit 25, setting-in valve base seat 23 between positioning sleeve 24 and valve plug-in unit 25 outsides and valve body 28 inner chambers, this valve base seat 23 is equipped with valve liner 15, the interior setting-in pressure piston 16 of this valve liner 15, these pressure piston 16 left ends are equipped with pressure spring 22.
In the present embodiment, preferably, the left side of valve base seat 23 comprises screw, and this screw is communicated with the cavity in valve base seat 23.
In the present embodiment, preferably, locking nut 19 embeds in the screw of valve base seat 23 left sides, the embedded joint push rod of debuging of described screw.
In the present embodiment preferably, pressure spring 22 two ends, left and right equal setting-in spring footstocks 21, two equal setting-ins of spring footstock 21 outer side center support steel ball, the support steel ball 17 in spring footstock 21 outsides of pressure spring 22 right-hand members contacts with pressure piston 16, the support steel ball in the spring footstock outside of pressure spring 22 left ends contacts with regulating push rod 20, and locking nut 19 is screwed into or back-outs, and forces spring-compressed or loosens, thereby regulating spring elastic force, and then reach the object that regulating load sets value.
In the present embodiment, valve pocket 12 comprises inner chamber I B, and this inner chamber I B is diameter-changing cavity, and the diameter at this inner chamber I B middle part is less than the diameter of the right and left.
In the present embodiment, valve body 28 comprises axial oil-in I, and valve body 28 sides comprise oil-out I radially and oil return opening I radially, and valve body 28 sides also comprise drain tap I L radially.
In the present embodiment, valve base seat 23 radially comprise drain tap II, this drain tap II is communicated with the drain tap I L of valve body 28, the drain tap I L of valve body 28 is connected to fuel tank, thereby make the fluid of revealing under high pressure flow back into fuel tank from valve inner via drain tap II and drain tap I, avoid producing back pressure in valve body, the fluid of leakage can be collected into fuel tank, avoid waste and contaminated environment simultaneously.
In the present embodiment, valve base seat 23 radially comprise oil-out II, this oil-out II is communicated with the oil-out I of valve body 28.
In the present embodiment preferably, valve base seat 23 radially comprise drain tap III 18, the sidewall that this drain tap III is positioned at valve base seat 23 left end pressure spring 22 correspondences radially, to the fluid that is positioned at pressure piston 16 left ends in valve base seat 23 is released, avoid producing back pressure, affect operating efficiency.
In the present embodiment, what valve plug-in unit 25 was positioned at main valve plug 26 and valve pocket 12 coupling parts radially comprises opening, and this opening is communicated with the oil return opening I of valve body 28, so that the complete fluid that circulates is back in hydraulic pump.
In the present embodiment, embedded sealing ring 13 between valve plug-in unit 25 and valve body 28.
In the present embodiment, between valve plug-in unit 25 and spring compressor 10, flexible collar I 27 is housed.
In the present embodiment, valve plug-in unit 25 embeds valve base seat 23 right-hand members, and between valve plug-in unit 25 and valve base seat 23, flexible collar II 14 is housed.
In the present embodiment, main valve plug 26 left ends comprise the cylinder of protrusion, and the cylinder left end of this protrusion comprises groove radially.
In the present embodiment, positioning sleeve 24 comprises inner chamber II, and this inner chamber II comprises cavity II ' and cavity II 〞, this cavity II ' be communicated with cavity II 〞, cavity II ' diameter be less than the diameter of cavity II 〞, cavity II ' be positioned on the left of cavity II 〞.
In the present embodiment, positioning sleeve 24 right-hand members embed in valve plug-in unit 25, and positioning sleeve 24 right-hand members are positioned at valve plug-in unit 25 inner chambers and main valve plug 26 outsides, and positioning sleeve 24 is limited to valve plug-in unit 25 right-hand member of valve body 28 inner side positioning sleeves 24.
In the present embodiment, main valve plug 26 embeds in the cavity II 〞 of positioning sleeve 24, between the cavity II 〞 of the left end of main valve plug and positioning sleeve 24, form cavity V A, the cylinder that main valve plug 26 left ends protrude through the cavity II of positioning sleeve 24 ', the cylinder outside that main valve plug 26 left ends protrude and cavity II ' between embedded sealing ring.
In the present embodiment, in main valve plug 26, comprise inner chamber VI, this inner chamber VI is diameter-changing cavity, the central shaft of this inner chamber VI overlaps with the central shaft of main valve plug 26, the diameter of this inner chamber VI left end is d, the diameter of inner chamber VI right-hand member is greater than the diameter of left end, and this inner chamber VI right-hand member connects by ramp way and main valve plug 26 upper left sides, left side, thereby the inner chamber VI of main valve plug 26 is communicated with cavity V A.
In the present embodiment, comprise inner chamber III in valve liner 15, this inner chamber III middle part comprises inside protrusion.
In the present embodiment, valve liner 15 is positioned at positioning sleeve 24 left sides, and what positioning sleeve 24 left end diameters were less is partially submerged in the inner chamber III of valve liner 15.
In the present embodiment, setting-in pressure piston 16 in the inner chamber III of valve liner 15.
In the present embodiment, preferably, pressure piston 16 comprises left part, middle part and right part three parts, and this left part, middle part and right part are structure as a whole.
In the present embodiment, preferably, the external diameter of the left part of pressure piston 16, middle part and right part reduces successively.
In the present embodiment, the diameter of pressure piston 16 left parts is ds, and the diameter at pressure piston 16 middle parts is do.
In the present embodiment preferably, setting-in y-shaped ring between pressure piston 16 left parts and the inner chamber III of valve liner 15.
In the present embodiment preferably, the right part of pressure piston 16 comprises inner chamber IV, the diameter of this inner chamber IV right-hand member is less than the diameter of left end, and the radial groove of the cylinder that main valve plug 26 left ends protrude embeds the less position of described inner chamber IV right-hand member diameter, thereby main valve plug 26 is connected with pressure piston 16.
In the present embodiment, preferably, the middle part of pressure piston 16 is inlaid in the protrusion position at valve liner 15 inner chamber III middle parts, and between the middle part of pressure piston 16 and the protrusion at valve liner 15 inner chamber III middle parts, sealing ring is housed.
The traveling control that the closed type hydraulic system that the present embodiment provides drives by the working method of load valve is: pressure spring is inlaid between spring footstock, due to the large fastening effect of locking nut, pressure spring is in compressive state, thereby generation elastic force, this elastic force is by the spring footstock on right side, supporting steel ball and pressure piston is applied on main valve plug, main valve plug is moved right and be adjacent to valve pocket, thereby the asphalt channel between oil-in I and oil return opening I is separated, the hydraulic oil at oil-in I place can not enter oil return opening I, but enter into inner chamber I and inner chamber VI through inner chamber I, thereby make oil-in I, be communicated with inner chamber V A by inner chamber VI with inner chamber I B.
Under action of hydraulic force, the hydraulic action that main valve plug is subject to equals the product of the cross-sectional area that the hydraulic pressures Pb of oil-in I is corresponding with main valve plug inner chamber VI left end diameter d, and direction left; The active force that the hydraulic pressures Ps of oil-out I forms pressure piston equals the product of the cross-sectional area that hydraulic pressures Ps is corresponding with pressure piston left part and the diameter at middle part poor (ds-do), and direction also left; When the hydraulic coupling that hydraulic coupling main valve plug being formed when oil-in I and oil-out I form pressure piston equals spring force left of pressure spring, main valve plug is in poised state, and by oil-in I, the valve port through between main valve plug and valve pocket stably flows to oil return opening I to hydraulic oil. In the situation that locking nut does not regulate, spring force size is constant, and now, as the pressure of crossing oil-out I place reduces, the pressure of oil-in I increases, otherwise the pressure of oil-in I reduces.
The oil-in I of load valve 30 is connected with the outlet of hydraulic motor, the entrance of the oil-out I connecting fluid pressure motor of load valve, the oil return opening I of load valve is connected to the entrance of hydraulic pressure traveling pump, hydraulic pressure traveling pump is supplied with power by internal combustion engine, described hydraulic pressure traveling delivery side of pump is connected with the entrance of described hydraulic motor, described hydraulic motor also connects load, and described hydraulic pressure traveling pump also connects oil-supplementing system, and this form closed type hydraulic system.
In the time of upward slope or level road, the traveling load forward that closed type hydraulic system drives puts on hydraulic motor, the entrance pressure Pa(of hydraulic motor equals Ps) be greater than the pressure Pb at oil-in I place, hydraulic pump provides power drive traveling, by controlling the size of hydraulic pump output flow, can stablize control traveling speed; In the time of descending, traveling laod reversal puts on hydraulic motor, the entrance pressure Pa(of hydraulic motor equals Ps) and back pressure Pb reduction, now, the opening of load valve reduces, and increases in the resistance to flow output of hydraulic motor, outlet pressure Pb increases, thereby prevent hydraulic motor speed surge under laod reversal effect, reach the object of steady control traveling speed, the fluid of revealing in hydraulic oil cyclic process in load valve is back in fuel tank by drain tap I L.
By adjusting lock nut 19 and adjusting push rod 20, thereby the decrement of regulating spring, thereby the hydraulic pressures sum that changes oil-in I and oil-out I, to adapt to the requirement of different loads to hydraulic pressure, thereby makes described load valve can adapt to the traveling control of different loads situation.
More multioperation is all known for those of ordinary skills, repeats no more.
The traveling control that the closed type hydraulic system that the present embodiment provides drives comprises any combination of each part mentioned above by the technical scheme of load valve, the simple change of each part mentioned above assembly or combination are still protection scope of the present invention.
The traveling control load valve that the closed type hydraulic system that the present embodiment provides drives, it is by the equilibrium relation of the spring force of the hydraulic coupling that forms on main valve plug and pressure piston and pressure spring, reach control overhead valve and open big or small object, once traveling load reduces or oppositely, load valve opening pressure is large, the load applying is large, otherwise, the load applying is little, and regulating spring power can change the setting value of load. Thereby avoid motor load to reduce or oppositely time traveling speed uprush, prevent that the reverse traction phenomena of hydraulic motor from occurring, reaches the object of steady control operation traveling speed.
Claims (25)
1. the traveling control load valve that closed type hydraulic system drives, it comprises valve body (28), this valve body (28) interior setting-in valve plug-in unit (25), this interior setting-in valve pocket of valve plug-in unit (25) (12), embedded sealing ring between this valve pocket (12) left side and valve plug-in unit (25), this valve pocket (12) right side external diameter is less than the internal diameter of valve plug-in unit (25), this valve pocket (12) right hand external suit support spring (11), this support spring (11) outside pocketed springs cap (10), the outward flange of this spring compressor (10) coordinates with valve plug-in unit (25) inner surface, in valve plug-in unit (25), be positioned at the position setting-in main valve plug (26) of valve pocket (12) left end, the left end connecting positioning sleeve (24) of valve plug-in unit (25), setting-in valve base seat (23) between positioning sleeve (24) and valve plug-in unit (25) outside and valve body (28) inner chamber, this valve base seat (23) is equipped with valve liner (15), the interior setting-in pressure piston of this valve liner (15) (16), it is characterized in that: this pressure piston (16) left end is equipped with pressure spring (22), this pressure spring (22) left end contacts with the left side of valve base seat (23), valve liner comprises inner chamber III in (15), setting-in y-shaped ring between the inner chamber III of pressure piston (16) left part and valve liner (15).
2. the traveling control load valve that a kind of closed type hydraulic system as claimed in claim 1 drives, is characterized in that: valve base seat (23) is the sealing of right-end openings left end, and the inner cylindrical structure that comprises cavity.
3. the traveling control load valve that a kind of closed type hydraulic system as claimed in claim 2 drives, is characterized in that: the left side of valve base seat (23) comprises screw, and this screw is communicated with the cavity in valve base seat (23).
4. the traveling control load valve that a kind of closed type hydraulic system as claimed in claim 3 drives, is characterized in that: locking nut (19) embeds in the screw of valve base seat (23) left side, the embedded joint push rod of debuging of described screw.
5. the traveling control load valve that a kind of closed type hydraulic system as claimed in claim 4 drives, it is characterized in that: pressure spring (22) two ends, left and right equal setting-in spring footstocks (21), the equal setting-in of two spring footstocks (21) outer side center supports steel ball, the support steel ball (17) in spring footstock (21) outside of pressure spring (22) right-hand member contacts with pressure piston (16), and the support steel ball (17) in the spring footstock outside of pressure spring (22) left end contacts with regulating push rod (20).
6. the traveling control load valve that a kind of closed type hydraulic system as claimed in claim 5 drives, it is characterized in that: valve pocket (12) comprises inner chamber I (B), this inner chamber I (B) is diameter-changing cavity, and the diameter at this inner chamber I (B) middle part is less than the diameter of the right and left.
7. the traveling control load valve that a kind of closed type hydraulic system as claimed in claim 6 drives, it is characterized in that: valve body (28) comprises axial oil-in I, valve body (28) side comprises oil-out I radially and oil return opening I radially, and described valve body (28) side also comprises drain tap I (L) radially.
8. the traveling control load valve that a kind of closed type hydraulic system as claimed in claim 7 drives, it is characterized in that: valve base seat (23) radially comprise drain tap II, this drain tap II is communicated with the drain tap I (L) of described valve body (28), and the drain tap I (L) of described valve body (28) is connected to fuel tank.
9. the traveling control load valve that a kind of closed type hydraulic system as claimed in claim 8 drives, is characterized in that: valve base seat (23) radially comprise oil-out II, this oil-out II is communicated with the oil-out I of described valve body (28).
10. the traveling control load valve that a kind of closed type hydraulic system as claimed in claim 9 drives, it is characterized in that: valve base seat (23) radially comprise drain tap III (18), this drain tap III (18) is positioned at sidewall that valve base seat (23) left end pressure spring (22) is corresponding radially.
The traveling control load valve that 11. a kind of closed type hydraulic systems as claimed in claim 10 drive, it is characterized in that: what valve plug-in unit (25) was positioned at main valve plug (26) and valve pocket (12) coupling part radially comprises opening, and this opening is communicated with the oil return opening I of valve body (28).
The traveling control load valve that 12. a kind of closed type hydraulic systems as claimed in claim 11 drive, is characterized in that: embedded sealing ring (13) between valve plug-in unit (25) and described valve body (28).
The traveling control load valve that 13. a kind of closed type hydraulic systems as claimed in claim 12 drive, is characterized in that: between valve plug-in unit (25) and spring compressor (10), flexible collar I (27) is housed.
The traveling control load valve that 14. a kind of closed type hydraulic systems as claimed in claim 13 drive, it is characterized in that: valve plug-in unit (25) embeds described valve base seat (23) right-hand member, and between described valve plug-in unit (25) and described valve base seat (23), flexible collar II (14) is housed.
The traveling control load valve that 15. a kind of closed type hydraulic systems as claimed in claim 14 drive, is characterized in that: main valve plug (26) left end comprises the cylinder of protrusion, and the cylinder left end of this protrusion comprises groove radially.
The traveling control load valve that 16. a kind of closed type hydraulic systems as claimed in claim 15 drive, it is characterized in that: positioning sleeve (24) comprises inner chamber II, this inner chamber II comprises cavity II ' and cavity II 〞, this cavity II ' be communicated with cavity II 〞, cavity II ' diameter be less than the diameter of cavity II 〞, cavity II ' be positioned at cavity II 〞 left side.
The traveling control load valve that 17. a kind of closed type hydraulic systems as claimed in claim 16 drive, it is characterized in that: positioning sleeve (24) right-hand member embeds in valve plug-in unit (25), positioning sleeve (24) right-hand member is positioned at valve plug-in unit (25) inner chamber and main valve plug (26) outside, and positioning sleeve (24) is limited to valve plug-in unit (25) right-hand member of valve body (28) inner side positioning sleeve (24).
The traveling control load valve that 18. a kind of closed type hydraulic systems as claimed in claim 17 drive, it is characterized in that: main valve plug (26) embeds in the cavity II 〞 of positioning sleeve (24), between the cavity II 〞 of the left end of main valve plug (26) and described positioning sleeve (24), form cavity V (A), the cylinder that main valve plug (26) left end protrudes through the cavity II of positioning sleeve (24) ', the cylinder outside that main valve plug (26) left end protrudes and described cavity II ' between embedded sealing ring.
The traveling control load valve that 19. a kind of closed type hydraulic systems as claimed in claim 18 drive, it is characterized in that: main valve plug comprises inner chamber VI in (26), this inner chamber VI is diameter-changing cavity, the central shaft of this inner chamber VI overlaps with the central shaft of described main valve plug (26), the diameter of inner chamber VI right-hand member is greater than the diameter of left end, and this inner chamber VI right-hand member connects by ramp way and upper left side, described main valve plug left side.
The traveling control load valve that 20. a kind of closed type hydraulic systems as claimed in claim 19 drive, is characterized in that: the inner chamber III middle part of valve liner (15) comprises inside protrusion.
The traveling control load valve that 21. a kind of closed type hydraulic systems as claimed in claim 20 drive, it is characterized in that: valve liner (15) is positioned at positioning sleeve (24) left side, what positioning sleeve (24) left end diameter was less is partially submerged in the inner chamber III of valve liner (15), setting-in pressure piston (16) in the inner chamber III of valve liner (15).
The traveling control load valve that 22. a kind of closed type hydraulic systems as claimed in claim 21 drive, is characterized in that: pressure piston (16) comprises left part, middle part and right part three parts, and this left part, middle part and right part are structure as a whole.
The traveling control load valve that 23. a kind of closed type hydraulic systems as claimed in claim 22 drive, is characterized in that: the external diameter of left part, middle part and the right part of pressure piston (16) reduces successively.
The traveling control load valve that 24. a kind of closed type hydraulic systems as claimed in claim 23 drive, it is characterized in that: the right part of pressure piston (16) comprises inner chamber IV, the diameter of this inner chamber IV right-hand member is less than the diameter of left end, the radial groove of the cylinder that main valve plug (26) left end protrudes embeds the less position of described inner chamber IV right-hand member diameter, thereby main valve plug (26) is connected with described pressure piston.
The traveling control load valve that 25. a kind of closed type hydraulic systems as claimed in claim 24 drive, it is characterized in that: the middle part of pressure piston (16) is inlaid in the protrusion position at valve liner (15) inner chamber III middle part, and between the middle part of pressure piston (16) and the protrusion at valve liner (15) inner chamber III middle part, sealing ring is housed.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201410071125.3A CN103791129B (en) | 2014-02-28 | 2014-02-28 | The traveling control load valve that a kind of closed type hydraulic system drives |
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| CN201410071125.3A CN103791129B (en) | 2014-02-28 | 2014-02-28 | The traveling control load valve that a kind of closed type hydraulic system drives |
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| CN103791129A CN103791129A (en) | 2014-05-14 |
| CN103791129B true CN103791129B (en) | 2016-05-11 |
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| CN201410071125.3A Active CN103791129B (en) | 2014-02-28 | 2014-02-28 | The traveling control load valve that a kind of closed type hydraulic system drives |
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Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN104153419B (en) * | 2014-07-22 | 2016-05-25 | 广西柳工机械股份有限公司 | Power control valve and loading machine are determined variable delivery hydraulic system |
| EP3309643B1 (en) * | 2016-10-14 | 2020-10-14 | Honeywell Technologies Sarl | Pressure independent control valve |
| CN109185498B (en) * | 2018-11-23 | 2020-04-17 | 玉环信得利阀业股份有限公司 | Proportional balance valve |
| CN112648251B (en) * | 2020-12-22 | 2023-04-28 | 天水锻压机床(集团)有限公司 | Automatic fluid infusion hydraulic valve of accumulator for large bending machine |
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| KR20110038224A (en) * | 2009-10-08 | 2011-04-14 | 볼보 컨스트럭션 이큅먼트 에이비 | Pressure control valve |
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| DE3011196A1 (en) * | 1979-03-26 | 1980-10-09 | Sperry Corp | HYDRAULIC VARIOUS FUNCTION VALVE ARRANGEMENT |
| DE19536725A1 (en) * | 1995-10-02 | 1997-04-03 | Rexroth Mannesmann Gmbh | Pressure cut=off valve with adjustment system |
| DE102005011138A1 (en) * | 2005-03-10 | 2006-09-14 | Bosch Rexroth Aktiengesellschaft | Pilot pressure switching fluid valve has spring loaded main piston which opens tank connection above set system pressure |
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| CN103791129A (en) | 2014-05-14 |
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Address after: 650215 Kunming City, Yunnan sheep sheep Wang Fang No. 384 Patentee after: CHINA RAILWAY CONSTRUCTION HIGH-TECH EQUIPMENT CO., LTD. Address before: 650215 Kunming City, Yunnan sheep sheep Wang Fang No. 384 Patentee before: Zhongtie Giant Road Maintenance Machinery Group Co., Ltd., Kunming |