CN104627160A - Hydraulic walking control system for engineering vehicle - Google Patents
Hydraulic walking control system for engineering vehicle Download PDFInfo
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- CN104627160A CN104627160A CN201510078762.8A CN201510078762A CN104627160A CN 104627160 A CN104627160 A CN 104627160A CN 201510078762 A CN201510078762 A CN 201510078762A CN 104627160 A CN104627160 A CN 104627160A
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
- B60K17/10—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of fluid gearing
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K23/00—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for
- B60K23/02—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for main transmission clutches
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K26/00—Arrangements or mounting of propulsion unit control devices in vehicles
- B60K26/04—Arrangements or mounting of propulsion unit control devices in vehicles of means connecting initiating means or elements to propulsion unit
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K26/00—Arrangements or mounting of propulsion unit control devices in vehicles
- B60K26/04—Arrangements or mounting of propulsion unit control devices in vehicles of means connecting initiating means or elements to propulsion unit
- B60K2026/046—Arrangements or mounting of propulsion unit control devices in vehicles of means connecting initiating means or elements to propulsion unit with electrical transmission means
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention provides a hydraulic walking control system for an engineering vehicle. The hydraulic walking control system comprises a hydraulic pump, a liquid-controlled multi-way valve, a hydraulic motor, a solenoid directional valve, a clutch device, an accelerator pedal and a brake pedal, wherein the hydraulic pump is communicated with an oil tank. The liquid-controlled multi-way valve comprises a multi-way valve, a check valve, an oil supplementing check valve and an overflow valve. A pressure limiting overflow valve and a solenoid valve are arranged between the liquid-controlled multi-way valve and the hydraulic motor, the solenoid directional valve is communicated with the multi-way valve, and the clutch device comprises a clutch pedal, a proportional pressure-reducing valve and a clutch sensor. The whole hydraulic walking control system is simple in structure, modular design is achieved, and the hydraulic walking control system is convenient to maintain and manage; and the clutch device in the control system not only has the effect of power cutoff, but also has the effect of parking buffering. Due to the design of the liquid-controlled multi-way valve, the vehicle can be prevented from sliding backwards during the hill start and can be protected from air suction caused by a quick gravity vehicle speed, the maximum pressure of a hydraulic system can be limited, and the running safety of the engineering vehicle is guaranteed.
Description
Technical field
The present invention relates to engineering vehicle walking device field, especially, relate to a kind of engineering truck hydraulic moving control system.
Background technology
The general weight ratio of engineering truck is comparatively large, and the local road environment of traveling is severe, and in order to meet, engineering truck tonnage is large, climbable gradient large, turn to the features such as flexible, and general medium-and-large-sized engineering truck adopts hydraulic moving more.
Existing engineering truck hydraulic moving many employings closed hydraulic loop, direction by changing the inner swash plate of enclosed pump in closed hydraulic loop changes the switching that the direction of pumping oil realizes vehicle advance, retreats, by changing the Angulation changes capacity of pump of the inner swash plate of enclosed pump thus realizing the adjustment of vehicle to run speed, concrete mode is: when pump swash plate rotates forward, and vehicle advances; When pump swash plate angle increases, vehicle speed of advance increases; When pump swash plate angle reduces, vehicle speed of advance reduces; When pump swash plate reverses, vehicle rollback.When under vehicle during large slope, enclosed pump low pressure side hydraulic oil is not the oil inlet being back to fuel tank but getting back to enclosed pump, can play certain brake action like this to equipment, effectively prevents hypervelocity, the slippage pump of enclosed pump inside can carry out repairing to low pressure side oil circuit simultaneously, prevents pump from inhaling empty.
Hydraulic moving adopts closed hydraulic loop, and its inside is integrated with multiple parts, causes its complex structure, expensive, contamination resistance is poor, not easy care.Therefore, design that a kind of structure is simplified, easy care, effectively avoid starting to walk flame-out phenomenon, the speed that vehicle can be made to travel obviously promoted and can ensure that vehicle still has when running at high speed the hydraulic moving control system of the features such as the moment of torsion of abundance significant.
Summary of the invention
The object of the invention is to provide that a kind of structure is simplified, easy care, effectively avoid starting to walk flame-out phenomenon, the speed that vehicle can be made to travel obviously are promoted and can ensure that vehicle still has the engineering truck hydraulic moving control system of the moment of torsion of abundance when running at high speed, and concrete technical scheme is as follows:
A kind of engineering truck hydraulic moving control system, comprises the Hydraulic Pump, liquor controlled multipath, HM Hydraulic Motor, solenoid directional control valve, arrangement of clutch and the acceleration pedal that is connected with the driving engine of described engineering truck that are communicated with fuel tank;
Described liquor controlled multipath comprises multiway valve, and described multiway valve comprises main oil inlet P, work oil inlet A, work oil inlet B and oil return inlet T, and when its spool is in meta, described work oil inlet A and described work oil inlet B is in off condition; Described Hydraulic Pump is communicated with described main oil inlet P by the first pipeline, and described first pipeline is provided with the check valve being flowed to main oil inlet P direction by Hydraulic Pump; Described work oil inlet A and described work oil inlet B is communicated with described oil return inlet T respectively respectively by second pipe and the 3rd pipeline, described second pipe is provided with the first repairing check valve being flowed to work oil inlet A direction by oil return inlet T, described 3rd pipeline is parallel with the second repairing check valve and the by pass valve being flowed to work oil inlet B direction by oil return inlet T; Described work oil inlet A is communicated with the first oil inlet of described HM Hydraulic Motor by the 4th pipeline, described work oil inlet B is communicated with the second oil inlet of described HM Hydraulic Motor by the 5th pipeline, is arranged in parallel limited pressurized overflow valve and the electromagnetic valve with electromagnet DT4 between described 4th pipeline and described 5th pipeline;
Described solenoid directional control valve comprises and controls its first outlet opened and closed by electromagnet DT3 and control its second outlet opened and closed by electromagnet DT2, and described first outlet and described second exports and is communicated with the both sides of the spool of described multiway valve respectively;
The clutch sensor that described arrangement of clutch comprises clutch pedal, the proportional pressure-reducing valve be connected with described clutch pedal and is connected with described proportional pressure-reducing valve and described electromagnet DT4 respectively.
Preferred in above technical scheme, described multiway valve is the Changjiang river hydraulic pressure DC20G2-O44U-9L multiway valve; Described electromagnetic valve is U.S. SUN electromagnetic valve DTDA-MCN; Described solenoid directional control valve is U.S. VICKERS solenoid directional control valve DG4V-3-6C-M-U-H7-60.
In order to reach better technique effect, also comprise controller, described electromagnet DT2, electromagnet DT3, electromagnet DT4, clutch sensor and acceleration pedal are all connected with described controller.
Preferred in above technical scheme, described controller is He Siman IFLEX C3E controller.
Preferred in above technical scheme, described Hydraulic Pump is the Variable plunger pump comprising the electromagnet DT1 be connected with described controller, and described acceleration pedal is efp.
Preferred in above technical scheme, described Hydraulic Pump is BOSCH-REXROTH A11VLO130LRDU2 Variable plunger pump, and described acceleration pedal is also connected with described Hydraulic Pump.
Preferred in above technical scheme, described Hydraulic Pump is fix-displacement pump, and described acceleration pedal is bracing wire throttle.
In order to reach better technique effect, described first pipeline is also provided with compression indicator.
Apply technical scheme of the present invention, there is following beneficial effect:
(1) engineering truck hydraulic moving control system of the present invention comprises Hydraulic Pump, liquor controlled multipath, HM Hydraulic Motor, solenoid directional control valve, arrangement of clutch and acceleration pedal, and integral structure is simplified, and realizes modular design, is convenient to maintenance and management; The arrangement of clutch arranged in control system of the present invention not only plays a part to cut off power, also works buffering of stopping; In the present invention, the design of liquor controlled multipath can prevent vehicle vehicle when hill start from slipping, vehicle can be prevented when Xia great Po, and because the gravity speed of a motor vehicle is very fast, empty phenomenon is inhaled in generation and can limit the top pressure of hydraulic efficiency pressure system, ensures the driving safety of engineering truck.
(2) in the present invention, multiway valve is the Changjiang river hydraulic pressure DC20G2-O44U-9L multiway valve, can be used for another loop worked when controlling different from hydraulic moving, practical; Described electromagnetic valve is U.S. SUN electromagnetic valve DTDA-MCN, is the Solenoid ball valve of low discharge, can plays buffer action well when vehicle parking; Solenoid directional control valve is U.S. VICKERS solenoid directional control valve DG4V-3-6C-M-U-H7-60, and precision is high.
(3) also controller is comprised in the present invention, described electromagnet DT2, electromagnet DT3, electromagnet DT4, clutch sensor and acceleration pedal are all connected with described controller, control facilitates and in control system, hydraulic pressure capacity of pump can change according to the output of E-gas, the moment of torsion of driving engine is applied fully, the load reducing driving engine during vehicle start can be made, effectively avoid the flame-out phenomenon that starts to walk; Vehicle can make Vehicle Speed obviously promote in travelling; When driving engine turns raising, when engine output torque diminishes, can ensure that vehicle still has sufficient moment of torsion when running at high speed; Described controller is He Siman IFLEX C3E controller, controls precision high.
(4) Hydraulic Pump described in the present invention is the Variable plunger pump comprising the electromagnet DT1 be connected with described controller, described acceleration pedal is efp or Hydraulic Pump is fix-displacement pump, described acceleration pedal is bracing wire throttle, the mode of control system of the present invention is varied, is applicable to different demands; Described Hydraulic Pump is BOSCH-REXROTH A11VLO130LRDU2 Variable plunger pump, and sensitieness is high, is convenient to control.
(5) the first pipeline described in the present invention is also provided with compression indicator, is convenient to the top pressure knowing hydraulic efficiency pressure system, guarantee the traffic safety of engineering truck further.
Except object described above, feature and advantage, the present invention also has other object, feature and advantage.Below with reference to figure, the present invention is further detailed explanation.
Accompanying drawing explanation
The accompanying drawing forming a application's part is used to provide a further understanding of the present invention, and schematic description and description of the present invention, for explaining the present invention, does not form inappropriate limitation of the present invention.In the accompanying drawings:
Fig. 1 is the integral structure schematic diagram of the engineering truck hydraulic moving control system of the preferred embodiment of the present invention 1;
Fig. 2 is the electric control theory figure in Fig. 1;
Fig. 3 is the graph of a relation in Fig. 1 between E-gas and the rotating speed of driving engine;
Fig. 4 is the graph of a relation in Fig. 1 between E-gas and hydraulic pressure capacity of pump;
Fig. 5 is the graph of a relation between the rotating speed of driving engine in Fig. 1 and moment of torsion;
Fig. 6 is the graph of a relation in the engineering truck hydraulic moving control system of the preferred embodiment of the present invention 2 between E-gas and hydraulic pressure capacity of pump.
Detailed description of the invention
Below in conjunction with accompanying drawing, embodiments of the invention are described in detail, but the multitude of different ways that the present invention can limit according to claim and cover is implemented.
Embodiment 1:
A kind of engineering truck hydraulic moving control system, refer to Fig. 1, specifically comprise the Hydraulic Pump 1, liquor controlled multipath 2, HM Hydraulic Motor 3, solenoid directional control valve 6, arrangement of clutch 7, controller and the acceleration pedal 8 that is connected with the driving engine of described engineering truck respectively that are communicated with fuel tank, integral structure is simplified, and modular design easy-maintaining.
Described Hydraulic Pump 1 is BOSCH-REXROTH A11VLO130LRDU2 Variable plunger pump, and it includes the electromagnet DT1 be connected with controller.
Described liquor controlled multipath 2 comprises multiway valve 2.1, described multiway valve 2.1 adopts the Changjiang river hydraulic pressure DC20G2-O44U-9L multiway valve, comprise main oil inlet P, work oil inlet A, work oil inlet B, oil return inlet T and oil outlet C, main oil inlet P is communicated with oil outlet C, and when its spool is in meta, described work oil inlet A and described work oil inlet B is in off condition.
Described Hydraulic Pump 1 is communicated with described main oil inlet P by the first pipeline 1.1, and described first pipeline 1.1 is provided with the check valve 2.2 being flowed to main oil inlet P direction by Hydraulic Pump 1, for preventing the oil of work oil inlet A or work oil inlet B from flowing backwards, can prevent vehicle vehicle when hill start from slipping.
Described work oil inlet A and described work oil inlet B is communicated with described oil return inlet T respectively respectively by second pipe 1.2 and the 3rd pipeline 1.3, described second pipe 1.2 is provided with the first repairing check valve 2.31 being flowed to work oil inlet A direction by oil return inlet T, described 3rd pipeline 1.3 is in series with the second repairing check valve 2.32 and the by pass valve 2.4 that are flowed to work oil inlet B direction by oil return inlet T, second pipe 1.2 and the 3rd pipeline 1.3 are equipped with repairing check valve, when the oil inlet A or work oil inlet B that works occurs to inhale empty, all can carry out correspondingly repairing to it, prevent vehicle when Xia great Po because the gravity speed of a motor vehicle is very fast, multiway valve 2.1 inhales sky because producing for shortage of oil.
Described HM Hydraulic Motor 3 comprises the first oil inlet being set as that driving engineering truck advances and the second oil inlet being set as the retrogressing of driving engineering truck (forward gear and retrogressing shelves are regulated by the walking switch arranged on the controller), described work oil inlet A is communicated with the first oil inlet of described HM Hydraulic Motor 3 by the 4th pipeline 1.4, described work oil inlet B is communicated with the second oil inlet of described HM Hydraulic Motor 3 by the 5th pipeline 1.5, limited pressurized overflow valve 4 and the electromagnetic valve 5 with electromagnet DT4 is arranged in parallel between described 4th pipeline 1.4 and described 5th pipeline 1.5, pressure limiting by pass valve 4 lays respectively at two oil inlets of HM Hydraulic Motor 3, when the vehicle is parked, the spool of multiway valve 2.1 is positioned at meta, described work oil inlet A and described work oil inlet B is in off condition, but due to inertia, vehicle also can move forward, such vehicle can drive HM Hydraulic Motor to rotate, the first oil inlet of HM Hydraulic Motor or the second oil inlet is made to produce high pressure, this pressure limiting by pass valve 4 can limit the top pressure of HM Hydraulic Motor two oil inlets here, protection HM Hydraulic Motor is not damaged, electromagnetic valve 5 adopts U.S. SUN electromagnetic valve DTDA-MCN, it is the Solenoid ball valve of a low discharge, first oil inlet of HM Hydraulic Motor is communicated with the second oil inlet by it, when HM Hydraulic Motor carries out short circle by electromagnetic valve, because electromagnetic valve flow is less, a back pressure can be produced to HM Hydraulic Motor, vehicle is slowly slowed down.
Described solenoid directional control valve 6 adopts U.S. VICKERS solenoid directional control valve DG4V-3-6C-M-U-H7-60, for switching the D Drive of vehicle, neutral gear, retreat shelves, it comprises the second outlet 6.2 being controlled its first outlet 6.1 opened and closed by electromagnet DT3 and controlled its opening and closing by electromagnet DT2, described first outlet 6.1 and described second exports 6.2 and is communicated with the both sides of the spool of described multiway valve 2.1 respectively, setting when vehicle is positioned at neutral gear electromagnet DT2 and electromagnet DT3 herein all must not electricity, when vehicle is positioned at forward gear, electromagnet DT3 obtains electric, when vehicle is positioned at retrogressing shelves, electromagnet DT2 obtains electric, concrete mode is: when vehicle is positioned at neutral gear, electromagnet DT2 in solenoid directional control valve 6 and electromagnet DT3 all must not be electric, the control oil that X makes a slip of the tongue is cut off, multiway valve 2.1 is in meta state, described work oil inlet A and described work oil inlet B is in off condition, when vehicle is positioned at D Drive, electromagnet DT3 obtains electric, the spool of solenoid directional control valve 6 moves and its first outlet is opened, the control oil that X makes a slip of the tongue next is by the first outlet 6.1 of solenoid directional control valve, the spool of multiway valve 2.1 moves and winner's oil inlet P is connected with work oil inlet A, first oil inlet oil-feed of HM Hydraulic Motor 3, drives engineering truck to advance, when engineering truck is positioned at and retreats shelves, electromagnet DT2 obtains electric, the spool of solenoid directional control valve 6 moves and its second outlet is opened, the control oil that X makes a slip of the tongue next is by the second outlet 6.2 of solenoid directional control valve, the spool of multiway valve 2.1 moves and winner's oil inlet P is connected with work oil inlet B, second oil inlet oil-feed of HM Hydraulic Motor 3, drives engineering truck to retreat.
The clutch sensor 7.3 that described arrangement of clutch 7 comprises clutch pedal 7.1, the proportional pressure-reducing valve 7.2 be connected with described clutch pedal 7.1 and is connected with described proportional pressure-reducing valve 7.2 and described electromagnet DT4 respectively, is connected by controller between described electromagnet DT4 with described clutch sensor 7.3.Concrete regulative mode is: when clutch pedal 7.1 is in initial position (namely clutch is not operated), the delivery pressure of described proportional pressure-reducing valve 7.2 is maximum; When clutch pedal 7.1 is operated, proportional pressure-reducing valve 7.2 delivery pressure reduces gradually (when clutch pedal 7.1 is floored, the delivery pressure of proportional pressure-reducing valve is zero), trigger clutch sensor 7.3 sender when the delivery pressure of proportional pressure-reducing valve is zero to controller, the electromagnet DT4 in controller Controlling solenoid valve 5 obtains electric.
Described acceleration pedal 8 is efp, and it is connected with described controller.Described controller adopts He Siman IFLEX C3E controller, its concrete mode refers to Fig. 2, wherein I01, I02 and I03 are on-off model input port, AI01 and AI02 is analog signals input port, DI01 and DI02 is analog signals output port, D01, D02 and D03 are on-off model output port, this controller output end can Direct driver electromagnet and coil DT1, DT2, DT3, DT4, KM, in parallel with electromagnet DT1, DT2, DT3, DT4 is afterflow diode, works the impact reducing reverse induction electric current.B1 is clutch sensor, and when clutch pedal is floored, the closing of contact in clutch sensor B1, controller I01 port obtains electric, and by the control of controller, output port D03 exports high level, and the electromagnet DT4 in electromagnetic valve 5 works.
Bend the throttle 8, engine speed and capacity of pump all can change according to the voltage of E-gas and refer to Fig. 3 and Fig. 4, when driving engine is in idling mode, engine speed is 750rpm, hydraulic pump discharge is 50% of total displacement, the load of driving engine can be reduced like this under the prerequisite ensureing vehicle start speed, effectively can avoid the flame-out phenomenon that starts to walk.E-gas first half term, when exporting as 0-2.5V interval, engine speed rises to 1500rpm by idling 750rpm, engine output torque by minimum rise to maximum, refer to Fig. 5, now pump capacity rises to 100% by 50%, because engine speed is in lifting, capacity of pump is also in lifting, and when at this moment vehicle travels, speed-raising obviously; E-gas the second half, when exporting as 2.5-5V interval, engine speed rises to 2200rpm by 1500rpm, and engine output torque diminishes, and now pump capacity is down to 80% by 100%, can ensure that vehicle still has sufficient moment of torsion when running at high speed like this.
Brake pedal 9 can also be comprised its inside by engineering truck hydraulic moving control system of the present invention according to demand, uses when mainly engineering truck stops.
When engineering truck stops, need release the gas pedal 8, step on clutch pedal 7.1 and brake pedal 9, release the gas pedal 8, engine speed is down to idling, and pump capacity is down to 50% of total displacement.Step on clutch pedal 7.1, proportional pressure-reducing valve 7.2 delivery pressure reduces, and the spool of multiway valve 2.1 is moved to meta, and in multiway valve 2.1, main oil inlet P reduces with the flux of work oil inlet A or the oil inlet B that works, and Vehicle Speed slows down, when clutch pedal 7.1 is floored, the control oil that X makes a slip of the tongue is cut off, proportional pressure-reducing valve 7.2 delivery pressure is zero, the spool of multiway valve 2.1 is in meta state, work oil inlet A and work oil inlet B is in off condition, clutch sensor 7.3 photos and sending messages is to controller simultaneously, electromagnet DT4 in controller Controlling solenoid valve 5 obtains electric, hydraulic pressure first oil inlet is communicated with the second oil inlet by electromagnetic valve 5, now due to inertia, vehicle is still in advance, HM Hydraulic Motor is still in rotation, but the hydraulic oil in HM Hydraulic Motor 3 can only carry out short circle by electromagnetic valve 5, because the flow of electromagnetic valve 5 is less, a back pressure can be produced to HM Hydraulic Motor 3, vehicle is made to enter parking buffer stage.Now step on brake pedal 9, vehicle just can be allowed to stop.
Apply engineering truck hydraulic moving control system of the present invention, have the following advantages:
(1) control system integral structure is simplified, and it realizes modularization, for ease of maintenaince etc.
(2) setting of arrangement of clutch not only plays a part to cut off power, can also work buffering of stopping.
(3) hydraulic pressure capacity of pump can change according to the output of E-gas, the moment of torsion of driving engine is applied fully, can make the load reducing driving engine during vehicle start, effectively avoids the flame-out phenomenon that starts to walk; Vehicle can make Vehicle Speed obviously promote in travelling; When driving engine turns raising, when engine output torque diminishes, can ensure that vehicle still has sufficient moment of torsion when running at high speed.
(4) setting of check valve in liquor controlled multipath, for preventing the oil of main oil inlet P from flowing backwards, can prevent vehicle vehicle when hill start from slipping; The setting of repairing check valve 2.3, when suction sky occurs the oil inlet A or work oil inlet B that works in multiway valve, all can carry out correspondingly repairing to it, prevent vehicle when Xia great Po because the gravity speed of a motor vehicle is very fast, multiway valve 2.1 inhales sky because producing for shortage of oil.
(5) design of pressure limiting by pass valve can limit the top pressure of HM Hydraulic Motor two oil inlets, and protection HM Hydraulic Motor is not damaged.
(6) design of electromagnetic valve can produce a back pressure to HM Hydraulic Motor, and vehicle is slowly slowed down.
(7) D Drive, neutral gear, the retrogressing shelves that switch vehicle are convenient in the design of solenoid directional control valve, easy to operate.
Multiway valve 2.1 described in the present embodiment also comprises work oil outlet C, and the entrance point of the fuel-displaced C of described work is communicated with described work oil inlet A, another loop worked when its exit end is different with hydraulic moving from the external world, practical.
Embodiment 2:
A kind of engineering truck hydraulic moving control system, the difference of the present embodiment and embodiment is only: Hydraulic Pump keeps certain discharge capacity to export, refer to Fig. 6, Hydraulic Pump adopts the discharge capacity work (can, according to actual conditions, be also 10%-100% between variable piston capacity of pump setting district) 80% herein.
Specific works principle is as follows: when switch of walking is beaten in " D Drive " or " retrogressing shelves " position, controller can give electromagnet DT1 electric current, makes Hydraulic Pump keep certain discharge capacity to export.Other principles are with embodiment 1.
Embodiment 3:
A kind of engineering truck hydraulic moving control system, the difference of the present embodiment and embodiment 1 is: described acceleration pedal 8 adopts bracing wire throttle, and described Hydraulic Pump 1 adopts fix-displacement pump.
The difference of concrete mode is: the rotating speed directly adopting bracing wire engine throttle control, do not have electric elements in this mode, simple and reliable for structure, cost is low.
The foregoing is only the preferred embodiments of the present invention, be not limited to the present invention, for a person skilled in the art, the present invention can have various modifications and variations.Within the spirit and principles in the present invention all, any amendment done, equivalent replacement, improvement etc., all should be included within protection scope of the present invention.
Claims (8)
1. an engineering truck hydraulic moving control system, is characterized in that: comprise the Hydraulic Pump (1), liquor controlled multipath (2), HM Hydraulic Motor (3), solenoid directional control valve (6), arrangement of clutch (7) and the acceleration pedal (8) that is connected with the driving engine of described engineering truck that are communicated with fuel tank;
Described liquor controlled multipath (2) comprises multiway valve (2.1), described multiway valve (2.1) comprises main oil inlet P, work oil inlet A, work oil inlet B and oil return inlet T, and when its spool is in meta, described work oil inlet A and described work oil inlet B is in off condition; Described Hydraulic Pump (1) is communicated with described main oil inlet P by the first pipeline (1.1), and described first pipeline (1.1) is provided with the check valve (2.2) being flowed to main oil inlet P direction by Hydraulic Pump (1); Described work oil inlet A and described work oil inlet B is communicated with described oil return inlet T respectively respectively by second pipe (1.2) and the 3rd pipeline (1.3), described second pipe (1.2) is provided with the first repairing check valve (2.31) being flowed to work oil inlet A direction by oil return inlet T, described 3rd pipeline (1.3) is parallel with the second repairing check valve (2.32) and the by pass valve (2.4) that are flowed to work oil inlet B direction by oil return inlet T; Described work oil inlet A is communicated with the first oil inlet of described HM Hydraulic Motor (3) by the 4th pipeline (1.4), described work oil inlet B is communicated with the second oil inlet of described HM Hydraulic Motor (3) by the 5th pipeline (1.5), is arranged in parallel limited pressurized overflow valve (4) and the electromagnetic valve (5) with electromagnet DT4 between described 4th pipeline (1.4) and described 5th pipeline (1.5);
Described solenoid directional control valve (6) comprises and controls its first outlet (6.1) opened and closed by electromagnet DT3 and control its second outlet (6.2) opened and closed by electromagnet DT2, and described first outlet (6.1) exports (6.2) and is communicated with the both sides of the spool of described multiway valve (2.1) respectively with described second;
The clutch sensor (7.3) that described arrangement of clutch (7) comprises clutch pedal (7.1), the proportional pressure-reducing valve (7.2) be connected with described clutch pedal (7.1) and is connected with described proportional pressure-reducing valve (7.2) and described electromagnet DT4 respectively.
2. engineering truck hydraulic moving control system according to claim 1, is characterized in that: described multiway valve (2.1) is the Changjiang river hydraulic pressure DC20G2-O44U-9L multiway valve; Described electromagnetic valve (5) is U.S. SUN electromagnetic valve DTDA-MCN; Described solenoid directional control valve (6) is U.S. VICKERS solenoid directional control valve DG4V-3-6C-M-U-H7-60.
3. engineering truck hydraulic moving control system according to claim 2, it is characterized in that: also comprise controller, described electromagnet DT2, electromagnet DT3, electromagnet DT4, clutch sensor (7.3) and acceleration pedal (8) are all connected with described controller.
4. engineering truck hydraulic moving control system according to claim 3, is characterized in that: described controller is He Siman IFLEX C3E controller.
5. engineering truck hydraulic moving control system according to claim 3, it is characterized in that: described Hydraulic Pump (1) is for comprising the Variable plunger pump of the electromagnet DT1 be connected with described controller, and described acceleration pedal (8) is efp.
6. engineering truck hydraulic moving control system according to claim 5, it is characterized in that: described Hydraulic Pump (1) is also connected with described Hydraulic Pump (1) for BOSCH-REXROTH A11VLO130LRDU2 Variable plunger pump, described acceleration pedal (8).
7. engineering truck hydraulic moving control system according to claim 3, is characterized in that: described Hydraulic Pump (1) is fix-displacement pump, described acceleration pedal (8) is bracing wire throttle.
8. engineering truck hydraulic moving control system according to claim 3, is characterized in that: described first pipeline (1.1) is also provided with compression indicator (2.5).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510078762.8A CN104627160A (en) | 2015-02-13 | 2015-02-13 | Hydraulic walking control system for engineering vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510078762.8A CN104627160A (en) | 2015-02-13 | 2015-02-13 | Hydraulic walking control system for engineering vehicle |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN104627160A true CN104627160A (en) | 2015-05-20 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201510078762.8A Pending CN104627160A (en) | 2015-02-13 | 2015-02-13 | Hydraulic walking control system for engineering vehicle |
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| Country | Link |
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| CN (1) | CN104627160A (en) |
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| CN104929999A (en) * | 2015-06-29 | 2015-09-23 | 宁波精垦液压有限公司 | Full-hydraulic driving control system |
| CN106627136A (en) * | 2016-08-31 | 2017-05-10 | 泉州鑫豪工程机械科技有限公司 | Electromagnetic valve for controlling traveling direction |
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