CN112303219A - Variable speed control valve with controllable and adjustable dynamic curve - Google Patents
Variable speed control valve with controllable and adjustable dynamic curve Download PDFInfo
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- CN112303219A CN112303219A CN202010635688.6A CN202010635688A CN112303219A CN 112303219 A CN112303219 A CN 112303219A CN 202010635688 A CN202010635688 A CN 202010635688A CN 112303219 A CN112303219 A CN 112303219A
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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
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/0003—Arrangement or mounting of elements of the control apparatus, e.g. valve assemblies or snapfittings of valves; Arrangements of the control unit on or in the transmission gearbox
- F16H61/0009—Hydraulic control units for transmission control, e.g. assembly of valve plates or valve units
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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
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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
- F15B13/025—Pressure reducing 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
- F15B20/007—Overload
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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
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/0021—Generation or control of line pressure
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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
- F16K11/10—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with two or more closure members not moving as a unit
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Control Of Transmission Device (AREA)
Abstract
The invention provides a variable speed control valve with controllable and adjustable dynamic curve, which comprises a valve body, wherein a gear shifting mechanism and a pressure reducing balance mechanism are arranged on the valve body, a brake pressure regulating double-acting mechanism is also arranged on the valve body, the pressure reducing balance mechanism is communicated with the brake and pressure curve regulating double-acting mechanism through a main oil way, and the brake and pressure curve regulating double-acting mechanism is communicated with the gear shifting mechanism through a working oil way. The invention changes the trend of a boosting curve of a traditional design speed change operating valve, prolongs the initial boosting time of main oil pressure during gear switching, simultaneously reduces the inflection point of the boosting curve during gear switching, shortens the time from the main oil pressure rising to the inflection point to set pressure, and solves the technical problem of gear shifting impact of a gear box of a loader by using a method for controlling the boosting curve of the speed change operating valve.
Description
Technical Field
The invention relates to an auxiliary device of a variable speed operating valve of an engineering vehicle, in particular to a variable speed operating valve with controllable and adjustable dynamic curve.
Background
The variable speed control valves of loaders in the market at present mostly use fixed-axis loader hydraulic gear shifting variable speed control valves, although the performance of the variable speed control valves is gradually improved through multiple technical improvements, the breadth of China is wide, the operating environments of the loaders are different, the flow of the existing variable speed control valves is designed in a constant value quantitative control mode, and the real-time controllable and adjustable requirements of various host factories and users on the dynamic curves of the variable speed control valves cannot be met. Utility model discloses utility model special for 2010, 5 months and 19 days, the utility model discloses a variable speed operating valve, especially relates to an electro-hydraulic control variable speed operating valve main oil pressure overload protection device for notice number CN 201475090U. The electro-hydraulic control variable speed control valve mainly solves the technical problems that in the prior art, due to continuous operation in the environment of severe working conditions, the control pressure valve is blocked, the control pressure valve and a control pressure valve spring are blocked, other valve cores are blocked, the oil way of a gearbox is blocked, the oil way of a torque converter is blocked, so that the working oil way is suddenly and infinitely lifted, the pipeline, parts, a box body and the like of the gearbox are damaged, and even the personal injury of operating personnel is influenced. The utility model discloses an including operating valve, connecting plate, oil transportation board, baffle, operating valve is including the valve body, and valve body one end is connected with the case board, and the other end is connected with the housing, is equipped with the solenoid valve in the housing, and solenoid valve and the inside oil circuit intercommunication of oil transportation board, the last oil inlet department of operating valve or oil transportation board is connected with overload protection device. The electro-hydraulic variable speed control valve is used for controlling gears by electricity and liquid, and a mechanical mechanism is used for controlling pressure, and is a combined valve of a mechanical structure and electricity and liquid. But the utility model discloses also can't satisfy the user to the real-time controllable adjustable requirement of variable speed operating valve dynamic curve.
Disclosure of Invention
The invention provides a dynamic curve controllable and adjustable variable speed control valve which is characterized in that a dynamic curve controllable and adjustable mechanism is added on the variable speed control valve to improve the flexibility of gear switching.
The technical scheme of the invention is as follows: a variable speed control valve with controllable and adjustable dynamic curve comprises a valve body, wherein a gear shifting mechanism and a pressure reducing balance mechanism are arranged on the valve body, a double-acting mechanism for regulating and controlling brake pressure is further arranged on the valve body, the pressure reducing balance mechanism is communicated with the double-acting mechanism for regulating and controlling brake and pressure curve through a main oil way, and the double-acting mechanism for regulating and controlling brake and pressure curve is communicated with the gear shifting mechanism through a working oil way. The invention improves the dynamic curve of the variable speed control valve by arranging a braking and pressure curve regulating double-acting mechanism.
Experiments show that the pressure rise curve of the conventional decompression throttling fixed-value quantitative speed change operating valve on a test bed is as follows: flow rate: 60L/min, main pressure: 1.40 MPa. When the neutral gear is switched to the reverse gear, the main oil pressure is instantly reduced to 0.50Mpa, an inflection point appears after the time of about 0.16S is increased to about 0.85Mpa, the time of about 0.70S is increased to 1.40Mpa, and the total gear switching boosting time is 0.86S. By reducing the throttle hole of the dredging needle valve, the boosting time of the rear section of the inflection point can only be prolonged, but the time from initial boosting to the inflection point of gear shifting cannot be changed.
The boosting curve of the dynamic curve controllable and adjustable variable speed control valve for adjusting the length slowly on the test bed position is as follows: flow rate: 60L/min, main pressure: 1.40 MPa. When the neutral gear is switched to the reverse gear, the main oil pressure is instantly reduced to 0.30Mpa, an inflection point appears after the time of about 0.78S is increased to 0.60Mpa, the time of about 0.32S is increased to 1.40Mpa, and the total gear switching boosting time is 1.10S.
The boost curve of the variable speed control valve with controllable and adjustable dynamic curve, which is adjusted quickly and shortened on the test bed position, is as follows: flow rate: 60L/min, main pressure: 1.40 MPa. When the neutral gear is switched to the reverse gear, the main oil pressure is instantly reduced to 0.30Mpa, an inflection point appears after the time of about 0.64S is increased to 0.60Mpa, the time of about 0.26S is increased to 1.40Mpa, and the total gear switching boosting time is 0.90S.
The variable speed control valve with the controllable and adjustable dynamic curve changes the trend of a boosting curve of a variable speed control valve in the traditional design, prolongs the initial boosting time of main oil pressure during gear switching, simultaneously reduces the inflection point of the boosting curve during gear switching, and shortens the time from the main oil pressure rising to the inflection point to set pressure. The pressure curve conforms to the working principle that the gear clutch of the gearbox is flexibly and initially arranged at about 0.30Mpa to 0.60Mpa and then is quickly compressed when the gearbox is shifted. The technical problem of gear shifting impact of a gearbox of the loader is solved by a method for controlling a boosting curve of a variable speed control valve. Meanwhile, the dynamic curve of the variable speed control valve can be adjusted quickly and slowly so as to meet the difference requirements of various loading machine main factories and users on the variable speed control valve, and the boost curve of the variable speed control valve can be adjusted on site in real time according to the requirements of special users.
Preferably, the double-acting mechanism for braking and pressure control comprises a pressure control spring, a double-acting valve for braking and pressure control and a pneumatic and hydraulic brake valve, the double-acting valve for braking and pressure control is connected to the valve body in a sliding mode, the pressure control spring is sleeved on the inner end of the double-acting valve for braking and pressure control and is abutted to the valve body, and the pneumatic and hydraulic brake valve is connected to the valve body in a threaded mode and is connected with the outer end of the double-acting valve for braking and pressure control. The double-acting mechanism for braking and pressure control adopts the structure configuration, so that oil pressure fluctuation can be better regulated, and a boosting curve of the variable speed control valve is controlled, thereby solving the problem of gear shifting impact of the gearbox of the loader.
Preferably, the main oil way and the working oil way are positioned on the bottom surface of the valve body, a main oil way oil inlet, a working oil way oil outlet, a second oil return cavity, an oil inlet, a one-way valve, a dredging needle valve throttling hole and a first oil return cavity are further arranged on the bottom surface of the valve body, the main oil way oil inlet is communicated with the main oil way, the working oil way oil outlet is communicated with the second oil return cavity, the oil inlet is communicated with the main oil way, and the one-way valve and the dredging needle valve throttling hole are communicated. The oil way is arranged on the bottom surface of the valve body, so that oil supply and oil return to each mechanism can be ensured, and the oil way and the valve body are integrated, so that the overall structure of the variable speed control valve is simpler and more compact.
Preferably, the periphery of the working oil way is provided with an oil leakage prevention groove which is communicated with an oil return cavity on the bottom surface of the valve body. Set up oil leakage prevention groove and time oil return chamber and can collect the backward flow with the oil liquid of oozing out, effectively prevent that fluid from losing.
Preferably, the pressure reducing balance mechanism comprises a pressure reducing valve, a pressure reducing spring, a balance valve and a pair of screw plugs, the two screw plugs are in threaded connection with two ends of the valve body, the pressure reducing valve, the pressure reducing spring, the balance spring and the balance valve are located between the two screw plugs, the pressure reducing valve is in one end of the valve body in a sliding connection mode, the balance valve is in one end of the valve body in a sliding connection mode, the pressure reducing spring is connected between the pressure reducing valve and the balance valve, the balance spring penetrates through the pressure reducing spring, and two ends of the. The pressure reducing balance mechanism regulates the high pressure oil input by the oil pump to the standard range of 1.10 MPa-1.50 MPa of the speed change operating valve.
Preferably, the gear shifting mechanism comprises a gear shifting valve rod and a positioning device, a plurality of gear shifting grooves are formed in the gear shifting valve rod, the gear shifting valve rod is connected to the valve body in a sliding mode, the positioning device comprises a pair of clamping bead grooves, a pair of clamping beads and a pair of clamping bead springs, the two clamping bead grooves are respectively located on two sides of the gear shifting valve rod and are coaxially opposite to each other, the clamping beads are arranged in the clamping bead grooves in a one-to-one correspondence mode, the clamping bead springs are connected between the clamping beads and the bottoms of the clamping bead grooves, and the clamping bead grooves are adaptive to the clamping beads. The shifting valve rod slides axially, the clamping balls are clamped in different stop grooves to finish shifting, and the shifting valve rod conducts the working oil port and the oil return port corresponding to each stop with the working oil circuit and the oil return cavity.
Preferably, the valve body is provided with signal ports or signal devices which correspond to the gears one to one. A signal port or a signal device is arranged for feeding back the gear state after gear shifting, so that an automatic control system can conveniently acquire sampling signals or find abnormal working conditions in time.
Preferably, the main oil path is provided with a main oil pressure overload protection device, the main oil pressure overload protection device comprises a safety valve, a safety valve oil return port, a safety valve spring and a safety valve plug screw, the safety valve is arranged in a safety valve cavity, the safety valve plug screw is connected to a port of the safety valve cavity in a threaded manner, the safety valve abuts against a step structure on the inner wall of the safety valve cavity, the safety valve spring is connected between the safety valve and the safety valve plug screw, and the safety valve oil return port is communicated with the safety valve cavity. When the pressure reducing device fails or the return oil of the gearbox is blocked, and the main oil pressure instantaneously exceeds the set pressure limit, the safety valve automatically opens to release the pressure, the return oil is connected to the transition seat from the safety valve body and flows back into the gearbox, and the safe use of a hydraulic system of the gearbox is ensured.
Preferably, a main pressure signal port is further arranged above the valve body between the pressure reducing balance mechanism and the braking pressure regulating double-acting mechanism. The oil pressure after being decompressed is the main pressure used by each mechanism in the next process, so the pressure parameter obtained after the decompression balancing mechanism is the most accurate parameter, and the main pressure signal port is arranged to be beneficial to obtaining accurate signals.
The invention has the beneficial effects that:
the dynamic curve of the variable speed control valve is improved, so that the gear shifting is more flexible. The invention changes the trend of a boosting curve of a traditional design variable speed control valve, prolongs the initial boosting time of main oil pressure during gear switching, simultaneously reduces the inflection point of the boosting curve during gear switching, shortens the time from the main oil pressure rising to the inflection point to set pressure, and ensures that the gear shifting is more flexible.
The universality is good. The invention optimally designs the local structure in the operating valve body, does not change the connecting installation size of the gearbox and the variable speed operating valve, the appearance size of the variable speed operating valve and the basic function of the original design of the variable speed operating valve, can be conveniently exchanged with the original variable speed operating valve, and has good universality.
The adjustment is convenient, and different requirements of users can be better met. The invention can adjust the speed of the dynamic curve of the variable speed control valve to meet the difference requirements of various loading machine main factories and users on the variable speed control valve.
Drawings
FIG. 1 is a schematic structural diagram of the present invention;
FIG. 2 is a schematic diagram of the oil circuit of each functional mechanism in the present invention;
FIG. 3 is a sectional view of the functional mechanisms of the present invention;
fig. 4 is a partial structural sectional view of the present invention.
In the figure, 1-valve body, 2-gear shifting mechanism, 3-brake pressure regulating double-acting mechanism, 4-pressure reducing balance mechanism, 5-gas-liquid brake valve, 6-F1 gear signal port, 7-F2 gear signal port, 8-R gear signal port, 9-N gear signal device, 10-positioning device, 11-main pressure signal port, 12-screw plug, 13-gear shifting valve rod, 14-N gear, 15-R gear, 16-F1 gear, 17-F2 gear, 18-R gear working oil port, 19-R gear oil return port, 20-F1 gear working oil port, 21-F1 gear oil return port, 22-F2 gear working oil return port, 23-F2 gear oil return port, 24-working oil port, 25-first oil return port, 26-oil inlet, 27-oil return-preventing oil channel, 28-pressure reducing oil return port, 29-main oil path, 30-main oil pressure overload protection device, 31-safety valve oil return port, 32-main oil path inlet, 33-working oil path outlet, 34-regulating oil return port, 35-one-way valve, 36-dredging needle valve throttling hole, 37-combined sealing device, 38-built-in neutral signal block, 39-pressure reducing valve, 40-pressure reducing spring, 41-balance spring, 42-balance valve, 43-pressure control spring, 44-brake pressure control double-acting valve, 45-safety valve plug screw, 46-safety valve, 47-safety valve spring, 48-second oil return cavity, 49-third oil return cavity and 50-gear shifting valve plug screw.
Detailed Description
The invention is further illustrated by the following specific embodiments in conjunction with the accompanying drawings.
Example (b):
as shown in fig. 1 to 4, the variable speed control valve with the controllable and adjustable dynamic curve comprises a valve body 1, a gear shifting mechanism 2 and a pressure reducing balance mechanism 4 are arranged on the valve body 1, a double-acting mechanism 3 for regulating and controlling brake pressure is further arranged on the valve body 1, the pressure reducing balance mechanism 4 is communicated with the double-acting mechanism 3 for regulating and controlling brake and pressure curve through a main oil way 29, and the double-acting mechanism 3 for regulating and controlling brake pressure is communicated with the gear shifting mechanism 2 through a working oil way 24. The double-acting mechanism for braking and pressure control comprises a pressure control spring 43, a double-acting valve 44 for braking and pressure control and a pneumatic-hydraulic brake valve 5, wherein the double-acting valve 44 for braking and pressure control is slidably connected in a brake valve cavity on the valve body 1, the pressure control spring 43 is sleeved on the inner end of the double-acting valve 44 for braking and pressure control and is abutted against the closed end of the brake valve cavity of the valve body 1, the pneumatic-hydraulic brake valve 5 is in threaded connection on the valve body 1, and a valve core of the pneumatic-hydraulic brake valve 5 is connected with the outer end of the double-acting valve 44 for. The main oil way 29 and the working oil way 24 are positioned on the bottom surface of the valve body 1, a main oil way oil inlet 32, a working oil way oil outlet 33, a regulation oil return port 34 and a second oil return cavity 48 are further arranged on the bottom surface of the valve body 1 below the brake pressure regulation double-acting mechanism 3, an oil inlet 26, a pressure reduction oil return port 28, a one-way valve 35, a dredging needle valve throttling hole 36 and a first oil return cavity 25 are further arranged on the bottom surface of the valve body 1 below the pressure reduction balancing mechanism 4, the main oil way oil inlet 32 is communicated with one end of the main oil way 29, the working oil way oil outlet 33 is communicated with the second oil return cavity 48, the oil inlet 26 is communicated with the other end of the. An oil leakage prevention groove 27 is formed in the periphery of the working oil path 24, and the oil leakage prevention groove 27 is communicated with an oil return cavity in the bottom surface of the valve body 1. The pressure reducing balance mechanism 4 comprises a pressure reducing valve 39, a pressure reducing spring 40, a balance spring 41, a balance valve 42 and a pair of screw plugs 12, the two screw plugs 12 are in threaded connection with two ends of a pressure reducing valve cavity of the valve body 1, the pressure reducing valve 39, the pressure reducing spring 40, the balance spring 41 and the balance valve 42 are located between the two screw plugs 12, the pressure reducing valve 39 is in sliding connection with one end of the pressure reducing valve cavity on the valve body 1, the balance valve 42 is in sliding connection with the other end of the pressure reducing valve cavity on the valve body 1, the pressure reducing spring 40 is connected with the pressure reducing valve 39, the balance valve 42 is in abutting connection with the pressure reducing valve 39 and the balance valve 42 at two ends respectively, the balance spring 41 is arranged in the pressure. The gear shifting mechanism 2 comprises a gear shifting valve rod 13 and a positioning device 10, a built-in neutral gear positioning block 38 and a built-in neutral gear sealing device 37, the gear shifting valve rod 13 is fixedly sealed by the built-in neutral gear sealing device 37 and a gear shifting valve plug screw 50, a plurality of annular gear shifting grooves are formed in the gear shifting valve rod 13 and respectively correspond to an N gear 14 (neutral gear), an R gear 15 (reverse gear), an F1 gear 16 (front 1 gear) and an F2 gear 17 (front 2 gear), the gear shifting valve rod 13 is connected in a gear shifting valve cavity on the valve body 1 in a sliding mode, the positioning device 10 comprises a pair of ball clamping grooves, a pair of clamping balls and a pair of clamping ball springs, the two ball clamping grooves are respectively located on two sides of the gear shifting valve rod 13 and are coaxially opposite, the ball clamping grooves are perpendicular to the gear shifting valve cavity, the clamping balls are correspondingly arranged in the ball clamping grooves one to one, the clamping ball springs are connected between. The bottom surface of the valve body 1 below the gear shifting mechanism 2 is also provided with an R oil blocking port 18, an R oil blocking return port 19, an F1 oil blocking port 20, an F1 oil blocking return port 21, an F2 oil blocking port 22, an F2 oil blocking return port 23 and a third oil return cavity 49. The valve body 1 above the shift mechanism 2 is provided with an F1 range signal port 6, an F2 range signal port 7, an R range signal port 8, and an N range signal device 9. The main oil path 29 is provided with a main oil pressure overload protection device 30, the main oil pressure overload protection device 30 comprises a safety valve 46, a safety valve oil return port 31, a safety valve spring 47 and a safety valve plug screw 45, the safety valve 46 is arranged in a safety valve cavity, the safety valve plug screw 45 is in threaded connection with a port of the safety valve cavity, the safety valve 46 is spherical and is abutted to a step structure on the inner wall of the safety valve cavity, the safety valve spring 47 is connected between the safety valve 46 and the safety valve plug screw 45, and the safety valve oil return port 31 is communicated with the safety valve cavity. A main pressure signal port 11 is also arranged above the valve body 1 between the pressure reducing balance mechanism 4 and the braking pressure regulating double-acting mechanism 3.
When the shift valve rod 13 is positioned at the R-stop, the working oil path 24 is communicated with the R-stop working oil port 18 arranged at the bottom surface of the valve body 1, and is synchronously communicated with the R-stop signal port 8 above the valve body 1. When the shift valve is positioned at the F1 position, the working oil path is communicated with the bottom surface of the valve body, the F1 position blocking working oil port 20, and the working oil port is synchronously communicated with the signal blocking oil port above the valve, namely, the F1 position blocking oil port. When the shift valve rod 13 is positioned at the F2 position, the working oil path 24 is communicated with the F2 working oil blocking port 22 on the bottom surface of the valve body 1, and is synchronously communicated with the F2 signal blocking port 7 above the valve body. When the shift valve rod 13 is positioned at the N gear, the built-in neutral gear positioning block 38 is communicated with the N gear signal device 9. The variable speed control valve with the controllable and adjustable dynamic curve changes the trend of a boosting curve of a variable speed control valve in the traditional design, prolongs the initial boosting time of main oil pressure during gear switching, simultaneously reduces the inflection point of the boosting curve during gear switching, and shortens the time from the main oil pressure rising to the inflection point to set pressure. The pressure curve conforms to the working principle that the gear clutch of the gearbox is flexibly and initially arranged at about 0.30Mpa to 0.60Mpa and then is quickly compressed when the gearbox is shifted.
Claims (9)
1. The variable speed control valve with the controllable and adjustable dynamic curve comprises a valve body (1), wherein a gear shifting mechanism (2) and a pressure reducing balance mechanism (4) are arranged on the valve body (1), and the variable speed control valve is characterized in that a braking pressure regulating double-acting mechanism (3) is further arranged on the valve body (1), the pressure reducing balance mechanism (4) is communicated with the braking and pressure curve regulating double-acting mechanism (3) through a main oil way (29), and the braking pressure regulating double-acting mechanism (3) is communicated with the gear shifting mechanism (2) through a working oil way (24).
2. The variable speed control valve with the controllable and adjustable dynamic curve as claimed in claim 1, wherein the double-acting mechanism for braking and pressure control comprises a pressure control spring (43), a double-acting valve (44) for braking and pressure control and a pneumatic and hydraulic brake valve (5), the double-acting valve (44) for braking and pressure control is slidably connected to the valve body (1), the pressure control spring (43) is sleeved on the inner end of the double-acting valve (44) for braking and pressure control and is abutted against the valve body (1), and the pneumatic and hydraulic brake valve (5) is in threaded connection with the valve body (1) and is connected with the outer end of the double-acting valve (44) for braking and pressure control.
3. The variable speed control valve with the controllable and adjustable dynamic curve as claimed in claim 1, wherein the main oil path (29) and the working oil path (24) are located on the bottom surface of the valve body (1), a main oil path oil inlet (32), a working oil path oil outlet (33), a second oil return cavity (48), an oil inlet (26), a one-way valve (35), a dredging needle valve orifice (36) and a first oil return cavity (25) are further arranged on the bottom surface of the valve body (1), the main oil path oil inlet (32) is communicated with the main oil path (29), the working oil path oil outlet (33) is communicated with the second oil return cavity (48), the oil inlet (26) is communicated with the main oil path (29), and the one-way valve (35) and the dredging needle valve orifice (36) are communicated with the working.
4. The variable speed control valve with controllable and adjustable dynamic curves according to claim 3 is characterized in that the periphery of the working oil path (24) is provided with an oil leakage prevention groove (27), and the oil leakage prevention groove (27) is communicated with an oil return cavity on the bottom surface of the valve body (1).
5. The variable-speed control valve with the controllable and adjustable dynamic curve as claimed in claim 1, wherein the pressure-reducing balance mechanism (4) comprises a pressure-reducing valve (39), a pressure-reducing spring (40), a balance spring (41), a balance valve (42) and a pair of screw plugs (12), the two screw plugs (12) are in threaded connection with two ends of the valve body (1), the pressure-reducing valve (39), the pressure-reducing spring (40), the balance spring (41) and the balance valve (42) are located between the two screw plugs (12), the pressure-reducing valve (39) is in sliding connection with one end of the valve body (1), the balance valve (42) is in sliding connection with the other end of the valve body (1), the pressure-reducing spring (40) is connected between the pressure-reducing valve (39) and the balance valve (42), the balance spring (41) is arranged in the pressure-reducing spring (40) in a penetrating manner.
6. The dynamic curve controllable adjustable variable speed operating valve according to claim 1, characterized in that the shift mechanism (2) comprises a shift valve rod (13) and a positioning device (10), a plurality of gear grooves are arranged on the shift valve rod (13), the shift valve rod (13) is slidably connected to the valve body (1), the positioning device (10) comprises a pair of ball clamping grooves, a pair of ball clamping springs and a pair of ball clamping springs, the two ball clamping grooves are respectively positioned on two sides of the shift valve rod (13) and are coaxially opposite, the ball clamping grooves are correspondingly arranged in the ball clamping grooves, the ball clamping springs are connected between the ball clamping grooves and the bottoms of the ball clamping grooves, and the ball clamping grooves are matched and clamped in the gear grooves.
7. A dynamic curve controllable and adjustable variable speed operating valve according to claim 1, characterized in that the valve body (1) is provided with signal ports or signal devices corresponding to each gear one to one.
8. The variable speed control valve with the controllable and adjustable dynamic curve as claimed in claim 1, wherein a main oil pressure overload protection device (30) is arranged on the main oil path (29), the main oil pressure overload protection device (30) comprises a safety valve (46), a safety valve oil return port (31), a safety valve spring (47) and a safety valve plug (45), the safety valve (46) is arranged in a safety valve cavity, the safety valve plug (45) is in threaded connection with a port of the safety valve cavity, the safety valve (46) abuts against a step structure on the inner wall of the safety valve cavity, the safety valve spring (47) is connected between the safety valve (46) and the safety valve plug (45), and the safety valve oil return port (31) is communicated with the safety valve cavity.
9. A dynamic curve controllable and adjustable variable speed operating valve as claimed in any one of claims 1 to 8, characterized in that a main pressure signal port (11) is further provided above the valve body (1) between the pressure reducing balancing mechanism (4) and the brake pressure regulating double-acting mechanism (3).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010635688.6A CN112303219A (en) | 2020-07-03 | 2020-07-03 | Variable speed control valve with controllable and adjustable dynamic curve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010635688.6A CN112303219A (en) | 2020-07-03 | 2020-07-03 | Variable speed control valve with controllable and adjustable dynamic curve |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN112303219A true CN112303219A (en) | 2021-02-02 |
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| CN201433958Y (en) * | 2009-04-10 | 2010-03-31 | 杭州萧山叉车配件有限公司 | Speed-variable control valve primary oil pressure protective device |
| CN201475302U (en) * | 2009-07-21 | 2010-05-19 | 杭州萧山叉车配件有限公司 | Variable speed operating valve with hydraulic brake device |
| CN201696374U (en) * | 2010-04-27 | 2011-01-05 | 厦门厦工机械股份有限公司 | Improved structure of variable speed control valve for loader |
| CN201772053U (en) * | 2010-07-13 | 2011-03-23 | 杭州萧山叉车配件有限公司 | Speed-changing operation valve for blocking oil-impregnation structure on the junction surface |
| CN208281487U (en) * | 2018-04-20 | 2018-12-25 | 杭州萧山叉车配件有限公司 | The speed change operating valve of the built-in neutral signal device of loading machine |
| CN110081164A (en) * | 2019-04-17 | 2019-08-02 | 杭州萧山叉车配件有限公司 | Loading machine gearbox shifting amortization multi-function variable-speed manipulates valve and its control method |
| CN210218658U (en) * | 2019-04-17 | 2020-03-31 | 杭州萧山叉车配件有限公司 | Multifunctional gear-shifting buffering variable-speed control valve of loader gearbox |
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2020
- 2020-07-03 CN CN202010635688.6A patent/CN112303219A/en active Pending
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201433958Y (en) * | 2009-04-10 | 2010-03-31 | 杭州萧山叉车配件有限公司 | Speed-variable control valve primary oil pressure protective device |
| CN201475302U (en) * | 2009-07-21 | 2010-05-19 | 杭州萧山叉车配件有限公司 | Variable speed operating valve with hydraulic brake device |
| CN201696374U (en) * | 2010-04-27 | 2011-01-05 | 厦门厦工机械股份有限公司 | Improved structure of variable speed control valve for loader |
| CN201772053U (en) * | 2010-07-13 | 2011-03-23 | 杭州萧山叉车配件有限公司 | Speed-changing operation valve for blocking oil-impregnation structure on the junction surface |
| CN208281487U (en) * | 2018-04-20 | 2018-12-25 | 杭州萧山叉车配件有限公司 | The speed change operating valve of the built-in neutral signal device of loading machine |
| CN110081164A (en) * | 2019-04-17 | 2019-08-02 | 杭州萧山叉车配件有限公司 | Loading machine gearbox shifting amortization multi-function variable-speed manipulates valve and its control method |
| CN210218658U (en) * | 2019-04-17 | 2020-03-31 | 杭州萧山叉车配件有限公司 | Multifunctional gear-shifting buffering variable-speed control valve of loader gearbox |
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