CN100515818C - Speed limiting system of oil hydraulic running vehicle - Google Patents
Speed limiting system of oil hydraulic running vehicle Download PDFInfo
- Publication number
- CN100515818C CN100515818C CNB200310118054XA CN200310118054A CN100515818C CN 100515818 C CN100515818 C CN 100515818C CN B200310118054X A CNB200310118054X A CN B200310118054XA CN 200310118054 A CN200310118054 A CN 200310118054A CN 100515818 C CN100515818 C CN 100515818C
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- oil
- setting
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- 230000009183 running Effects 0.000 title abstract description 11
- 230000007246 mechanism Effects 0.000 claims description 38
- 230000008859 change Effects 0.000 claims description 28
- 238000006073 displacement reaction Methods 0.000 claims description 8
- 230000008447 perception Effects 0.000 claims description 2
- 230000008878 coupling Effects 0.000 description 9
- 238000010168 coupling process Methods 0.000 description 9
- 238000005859 coupling reaction Methods 0.000 description 9
- 238000001514 detection method Methods 0.000 description 9
- 230000006835 compression Effects 0.000 description 5
- 238000007906 compression Methods 0.000 description 5
- 230000000750 progressive effect Effects 0.000 description 5
- 239000012467 final product Substances 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 230000005540 biological transmission Effects 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 2
- 244000144983 clutch Species 0.000 description 2
- 230000000881 depressing effect Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000004075 alteration Effects 0.000 description 1
- 230000000994 depressogenic effect Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000002828 fuel tank Substances 0.000 description 1
- 230000007274 generation of a signal involved in cell-cell signaling Effects 0.000 description 1
- 239000007921 spray Substances 0.000 description 1
Classifications
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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
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
- F16H61/46—Automatic regulation in accordance with output requirements
- F16H61/47—Automatic regulation in accordance with output requirements for achieving a target output speed
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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
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
- F16H61/42—Control of exclusively fluid gearing hydrostatic involving adjustment of a pump or motor with adjustable output or capacity
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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
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
- F16H61/46—Automatic regulation in accordance with output requirements
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W2720/00—Output or target parameters relating to overall vehicle dynamics
- B60W2720/10—Longitudinal speed
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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
- F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
- F16H59/68—Inputs being a function of gearing status
- F16H2059/6838—Sensing gearing status of hydrostatic transmissions
- F16H2059/6861—Sensing gearing status of hydrostatic transmissions the pressures, e.g. high, low or differential pressures
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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
- F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
- F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
- F16H47/04—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members having orbital motion
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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
- F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
- F16H59/36—Inputs being a function of speed
- F16H59/44—Inputs being a function of speed dependent on machine speed of the machine, e.g. the vehicle
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Control Of Fluid Gearings (AREA)
- Operation Control Of Excavators (AREA)
Abstract
The speed limit system for the hydraulic running vehicle comprises a pump capacity control means controlling capacity of a variable capacity type hydraulic pump for running so that differential pressure between load pressure of a hydraulic motor for running and discharged pressure of the variable capacity type hydraulic pump for running are set to be LS set pressure, a speed detecting means of the hydraulical running vehicle, and a controller changing the LS set pressure when the detected speed exceeds the designated value and lessening capacity of the variable capacity type hydraulic motor for running.
Description
Technical field
The present invention relates to the Speed Limitation Devices of oil pressure driving vehicle.
Background technology
In the past, known a kind of oil pressure driving vehicle, powered vehicle (opening the 2001-235032 communique) with reference to the spy of Japan by the tilt quantity of control hydraulic motor.Wherein, comprising: the speed of a motor vehicle testing agency that is used to detect the speed of a motor vehicle of vehicle; The servovalve of the tilt quantity of control hydraulic motor; When reaching the 1st specified value by the detected speed of a motor vehicle of speed of a motor vehicle testing agency, servovalve is exported in the instruction that increases tilt quantity, during less than the 1st specified value, export to the control mechanism of servovalve in the speed of a motor vehicle with removing the instruction that increases tilt quantity.
But, this utilization is travelled with the pressure oil of oil pressure pump by engine-driven, drives the oil pressure driving vehicle that travels and travel with hydraulic motor of variable displacement, and maximum speed is travelled to be limited with the oil pressure capacity of pump.And maximum speed is different and different according to the country that the oil pressure driving vehicle travels, and under the situation of the different national output oil pressure driving vehicle of maximum speed, comes corresponding by be equipped with the different vehicle of using oil pressure pump that travels of capacity to different country's output.Yet, if the maximum speed of oil pressure driving vehicle and various countries is arranged in pairs or groups, to prepare different the travelling of various capacity and use oil pressure pump, the kind of travelling with oil pressure pump increases.In addition, the kind of the associated components such as pipe arrangement that making travels cooperates with vehicle with oil pressure pump increases, and causes managing increasing man-hour.And then, before shipment, exist under the situation of change of specification, must transform to travel and use oil pressure pump, produce unnecessary assembling man-hour.
Summary of the invention
The present invention is conceived to the problems referred to above point, and its purpose is, a kind of Speed Limitation Devices that gets final product restricted speed in the oil pressure driving vehicle with simple structure is provided.
In order to achieve the above object, the 1st invention of the present invention is, a kind of have to travel travel with hydraulic motor and variable displacement in the Speed Limitation Devices with the oil pressure driving vehicle of oil pressure pump, constitute and possess: so that the difference of pressure that travels with the ejection pressure of oil pressure pump with the load pressure of hydraulic motor and variable displacement that travels is the mode of load perception setting pressure (hereinafter referred to as the LS setting pressure), the control variable formula is travelled with the pump capacity control mechanism of oil pressure capacity of pump; The speed of a motor vehicle testing agency of above-mentioned oil pressure driving vehicle; With surpassing under the situation of setting value by this detected speed of a motor vehicle of speed of a motor vehicle testing agency, change above-mentioned LS setting pressure, the controller that above-mentioned variable displacement the capacity with hydraulic motor of travelling is reduced.
According to the 1st invention,, the capacity of variable displacement hydraulic motor is reduced, so can realize Speed Limitation Devices with simple formation owing to surpass change LS setting pressure under the situation of setting value in the speed of a motor vehicle.
The 2nd invention of the present invention is, in the 1st invention, above-mentioned controller possesses the LS setting pressure set mechanism of setting above-mentioned LS setting pressure, and this set mechanism can be transformed to the set mechanism that chooses from other multiple LS setting pressure set mechanisms.
According to the 2nd invention,,, can change restricted speed simply so only this set mechanism is transformed to the LS setting pressure set mechanism of selecting from other multiple set mechanisms owing to possess the controller that can exchange LS setting pressure set mechanism.
Description of drawings
Fig. 1 is the formation picture of device of the Speed Limitation Devices of oil pressure driving vehicle of the present invention.
The specific embodiment
With reference to Fig. 1 Speed Limitation Devices of the present invention is at length described.
On driving engine 11, be connected with driving pump 12, drive driving pump 12 ejections by driving engine 11 and press oil.Pass through ride control valve 21 and oil pressure swivel coupling 15 from the pressure oil of driving pump 12 ejections, be sent to driving motors 13.Driving motors 13 is connected with the input shaft of change speed gear box 14, drives change speed gear box 14.
Be provided with moving velocity in the change speed gear box 14 and detect, rotate with the direct ratio ground that is rotated into of the output shaft of change speed gear box 14 with pump 17.The pressure oil that detects with pump 17 ejections from moving velocity is sent to moving velocity detection motor 18 by oil pressure with swivel coupling 15.Driving pump 12 is variable oil pressure pumps, has pump capacity control mechanism 12C.In addition, driving motors 13 is variable hydraulic motors, has motor capacity control mechanism 13C.
And, not shown engineering truck possesses not shown bottom driving body and not shown upper rotating body, on upper rotating body, possess not shown working rig, be provided with oil pressure swivel coupling 15 at the connecting portion place of bottom driving body and upper rotating body.Driving engine 11 is arranged on the not shown upper rotating body, and change speed gear box 14 is arranged on the not shown bottom driving body, and controller 30 is arranged on the not shown upper rotating body.
Change speed gear box 14 is connected with speed-change valve 16 as variable speed control mechanism with swivel coupling 15 by oil pressure.Speed-change valve 16 is transported to the pressure of pump 19 oil change speed gear box 1 grade of (speed) power-transfer clutch 14F or 2 grades of power-transfer clutch 14S of change speed gear box 14 through oil pressure swivel coupling 15.The dibit transfer valve that speed-change valve 16 is simple in structure and cost is low switches graphic 1 grade of (speed) position 16A and 2 P PARK Position P 16B according to the signal that comes self-controller 30.
Change speed gear box 14 has sun and planet gear, according to the pressure signal from speed-change valve 16, exerts pressure or hold-off pressure with 2 grades of power-transfer clutch 14S with 1 grade of (speed) power-transfer clutch 14F or high speed to low speed, and close, disconnect, thus the setting speed level.That is, 1 grade of (speed) power-transfer clutch 14F and 2 grades of power-transfer clutch 14S, be execute compressed oil close power-transfer clutch, discharge to press the power-transfer clutch of the mode of oily cut-off clutch.
Change speed gear box 14 has 1 grade (speed) and 2 grade of two velocity stage.Making change speed gear box 14 is under the situation of 1 grade (speed), speed-change valve 16 is positioned at 1 grade of (speed) position 16A, applies pressure oil from speed-change valve 16 to 1 grade of (speed) power-transfer clutch 14F, and 1 grade of (speed) power-transfer clutch closes, and discharge the pressure oil of 2 grades of power-transfer clutch 14S, disconnect 2 grades of power-transfer clutch 14S.In addition, be that speed-change valve 16 is in 2 P PARK Position P 16B under 2 grades the situation making change speed gear box 14, apply pressure oil to 2 grades of power-transfer clutch 14S from speed-change valve 16, the 2 grades of power-transfer clutchs that close, and discharge the pressure oil of 1 grade of (speed) power-transfer clutch 14F, disconnect 1 grade of (speed) power-transfer clutch 14F.
The speed of a motor vehicle detection of gear 35 of vehicle speed signal generation usefulness is set on the output shaft of speed of a motor vehicle detection with motor 18, detects with motor 18 rotations by the speed of a motor vehicle.In the periphery of speed of a motor vehicle detection of gear 35, for example form tooth, the otch and concavo-convex of specified quantity.Speed of a motor vehicle detecting sensor 31, near the periphery setting of speed of a motor vehicle detection of gear 35, the pulse that is taken place during with signal detecting part by speed of a motor vehicle detecting sensor 31 of tooth periphery, for example specified quantity of speed of a motor vehicle detection of gear 35 is as electric signal.
As the speed of a motor vehicle detecting sensor 31 of speed of a motor vehicle testing agency, be connected with controller 30, to the vehicle speed signal of controller 30 transmission as electric signal.This vehicle speed signal of controller 30 calculation process also calculates the speed of a motor vehicle.
Ride control valve 21 switches to progressive position F or the position R that falls back from graphic center position N, and control is carried to driving motors 13 from the direction of the pressure oil of driving pump 12 ejections.Ride control valve 21, the guide pressure that travels by the transfer valve 22 that will fall back from advancing as guide pressure be added in the advance side compression zone 21F of ride control valve 21 or the side compression zone 21R that falls back on, and switch to progressive position F or the position R that falls back from center position N.
The transfer valve 22 that falls back that advances according to the progress signal that comes self-controller 30, switches to graphic progressive position FK, or switches to the position RK that falls back according to the signal that falls back.
Das Gaspedal 23A by being depressed, and makes guide pressure valve 23 runnings of travelling, thereby the guide pressure that travels is produced.As the guide pressure that travels that depresses the amount detection machine structure of Das Gaspedal 23A, change corresponding to the amount of depressing of Das Gaspedal 23A, if the amount of depressing of Das Gaspedal 23A increases, its ratio with regulation is increased.
Be provided with the load pressure sensor 33 that travels on the loop between driving pump 12 and the ride control valve 21, the load pressure sensor 33 that travels will detectedly travel the load pressure signal to controller 30 transmission.
On the advancing of control cock 21 of travelling falls back loop between the advance side compression zone 21F of transfer valve 22 and ride control valve 21, the pressure sensor 36 that travels that advances is set.The pressure sensor 37 that travels that falls back is set on the loop between the side compression zone 21R of falling back of transfer valve 22 and ride control valve 21 advancing to fall back.The pressure sensor 36 that travels of advancing will be connected switch inside and the running signal that advances that produce by the guide pressure that travels, the pressure sensor 37 that travels of falling back will be connected internal switch and the running signal that falls back that produce by the guide pressure that travels, and be sent to controller 30 respectively.
Ride control valve 21, is connected with driving motors 13 by the advance side loop 46F and the side loop 46R that falls back with swivel coupling 15 by oil pressure.From at ride control valve 21 and oil pressure with the 47F of the advance side loop 46F branch between the swivel coupling 15 with from the loop 47R of the side loop 46R branch that falls back, connect by reciprocable valve (shuttle valve) 42.The output loop LSM of reciprocable valve 42 is connected with pump capacity control mechanism 12C.From reciprocable valve 42, the high pressure oil of either party pressure of the advance side loop 46F and the side loop 46R that falls back is output as the motor load pressure LS1 of driving motors 13, enters pump capacity control mechanism 12C by output loop LSM.
The ejection loop 41 of driving pump 12 is connected with ride control valve 21.Be connected with pump capacity control mechanism 12C from the pump pressure detection loop LSP of ejection loop 41 branches.The pump ejection pressure LS2 in the ejection loop 41 of driving pump 12 enters pump capacity control mechanism 12C.
Pump capacity control mechanism 12C is connected with controller 30.Pump capacity control mechanism 12C, so that travel with the difference of pressure Δ LS of the motor load pressure LS1 of the pump of pump 12 ejection pressure LS2 and driving motors 13 (=LS2-LS1) become the mode of the LS setting pressure of the cooresponding regulation of pump capacity signal that is transmitted with slave controller 30, control the capacity of driving pump 12.In pump capacity control mechanism 12C, be provided with LS electromagnetic proportional valve 12CLS, can be corresponding with the signal that comes self-controller 30, set the LS setting pressure.
In the both sides of LS electromagnetic proportional valve 12CLS magnet coil 12CS and spring 12CP are set.Corresponding to the signal that comes self-controller 30, magnet coil 12CS applies counter-force to the not shown spool (spool) of LS electromagnetic proportional valve 12CLS.The spool of LS electromagnetic proportional valve 12CLS, power that the counter-force that always move to, magnet coil 12CS produces and the pressing force that the motor load pressure LS1 of driving motors 13 produces add up to and the pump with pump 12 of travelling spray the position of the force balance of the power total that power that pressure LS2 produced and spring 12CP produced.Corresponding to the opening amount of this spool, LS electromagnetic proportional valve 12CLS will be transported to from the pressure oil in the ejection loop 41 of driving pump 12 among the pump capacity control oil cylinder 12CC.That is, pump capacity control mechanism 12C becomes to detect and travels with the pump ejection pressure LS2 of pump 12 and the difference of pressure Δ LS of the motor load pressure LS1 of driving motors 13 (=LS2-LS1) load detection (load sensing) mechanism.According to the setting pressure of the spool of the LS electromagnetic proportional valve 12CLS of this difference of pressure Δ LS balance as the LS setting pressure.
If the power that the motor load pressure LS1 of driving motors 13 is produced increases, then LS electromagnetic proportional valve 12CLS is positioned at graphic position 12A, the pressure oil of pump capacity control oil cylinder 12CC is to fuel tank (not shown) discharging (drain), the swash plate 12a of driving pump 12 tilts to graphic max direction, and the capacity of driving pump 12 increases.On the other hand, if the power that the pump of driving pump 12 ejection pressure LS2 is produced increases, then LS electromagnetic proportional valve 12CLS is positioned at shown position 12B, presses oil to enter pump capacity control oil cylinder 12CC, the swash plate 12a of driving pump 12 tilts to graphic min direction, and the capacity of driving pump 12 reduces.
Here, if reduce the counter-force of the spool that the magnet coil 12CS of LS electromagnetic proportional valve 12CLS produced, then because the power of the power total that will the travel power that produced with the pump of pump 12 ejection pressure LS2 and spring 12CP are produced, the power of the pressing force total that is produced than the motor load pressure LS1 of the counter-force that magnet coil 12CS is produced and driving motors 13 is big, so LS electromagnetic proportional valve 12CLS moves in the mode that becomes position 12B.Thus, press oil to enter pump capacity control oil cylinder 12CC, the swash plate 12a of driving pump 12 tilts to graphic min direction, and the capacity of driving pump 12 is reduced.Therefore, by the LS setting pressure of change as the setting pressure of the load testing agency of pump capacity control mechanism 12C, the swash plate 12a of driving pump 12 tilts to graphic min direction, and the capacity of driving pump 12 is reduced.
The switch 34 that falls back of advancing is connected with controller 30, and advancement commands signal or backward commands signal are transmitted to controller 30.
If controller 30 is accepted the load pressure sensor 33 detected load pressure signals that travel that travel in loop between driving pump 12 and the ride control valve 21, then as the load that resistance to motion produced, the ejection that calculates driving pump 12 presses the pressure of oil whether to surpass specified value.
Controller 30 calculation process speed of a motor vehicle detecting sensors 31 detected vehicle speed signal as electric signal calculate the speed of a motor vehicle, in speed that the speed of a motor vehicle surpasses regulation for example under the situation of 50km/h, the pump capacity that the capacity of driving pump 12 will be reduced reduces signal and is sent to pump capacity control mechanism 12C.Reduce signal if the LS electromagnetic proportional valve 12CLS of pump capacity control mechanism 12C accepts pump capacity, then reduce the counter-force of the spool of the electromagnetic proportional valve 12CLS that produces by magnet coil 12CS.Like this, as mentioned above, the power of the power total that power that will be produced with the pump of pump 12 ejection pressure LS2 owing to will travel and spring 12CP are produced, the power of the pressing force total that is produced than the motor load pressure LS1 of the counter-force that magnet coil 12CS is produced and driving motors 13 is big, so LS electromagnetic proportional valve 12CLS moves in the mode that becomes position 12B, the capacity of driving pump 12 is reduced.
In addition, controller 30 possesses the LS setting pressure setting adapter (adapter) 39 as the LS setting pressure set mechanism that can set the LS setting pressure.The LS setting pressure is set adapter 39, can be loaded and unloaded by not shown adaptor union from the mode of outside exchange with relative controller 30.For example, by be exchanged for maximum speed 50km/h with adapter, maximum speed 60km/h with adapter, maximum speed 70km/h with adapter etc., set multiple LS setting pressure, thereby can set multiple maximum speed.For example under being equipped with as the situation of maximum speed 50km/h with the LS setting pressure setting adapter 39 of adapter, calculation process speed of a motor vehicle detecting sensor 31 detected vehicle speed signal as electric signal are calculated the speed of a motor vehicle, when this speed of a motor vehicle surpasses 50km/h, as mentioned above, the capacity of driving pump 12 is reduced.
The action of Speed Limitation Devices of the present invention then, is described.
Chaufeur, the switch that falls back if will advance switches to advance side, then advances and falls back transfer valve 22 for progressive position FK, depresses Das Gaspedal 23A, the guide pressure that then travels is applied on the advance side compression zone 21F of ride control valve 21, switches to progressive position F from center position N.The pressure sensor 36 that travels that advances is connected internal switch by the guide pressure that travels, and the running signal that will advance transmits to controller 30.
Controller 30, the advancement commands signal of switch 34 and the velocity stage signal of being set by not shown velocity stage control stalk (for example being 2 grades) fall back according to advancing, at first, speed-change valve 16 is switched to 1 grade of (speed) position 16A, 1 grade of (speed) power-transfer clutch 14F then closes, and disconnect 2 grades of power-transfer clutch 14S, change speed gear box 14 speed changes are advance 1 grade (speed).
Ride control valve 21 will be transported to the advance side spout 13F of driving motors 13 by oil pressure from the pressure oil of driving pump 12 ejections with swivel coupling 15.The rotation of driving motors 13 forward direction drives change speed gear box 14, engineering truck is advanced travel.
If the speed of a motor vehicle increases, surpass for example speed of a motor vehicle 50km/h of the maximum speed set from the vehicle speed signal of speed of a motor vehicle detecting sensor 31, then controller 30 transmits the pump capacity that the capacity that makes driving pump 12 reduces to pump capacity control mechanism 12C and reduces signal.
Reduce signal if the LS electromagnetic proportional valve 12CLS of pump capacity control mechanism 12C accepts pump capacity, then reduce the counter-force of the spool that magnet coil 12CS produced.Like this, the power of the power total that power that is produced with the pump of pump 12 ejection pressure LS2 owing to travel and spring 12CP are produced, the power of the pressing force total that is produced than the motor load pressure LS1 of the counter-force that magnet coil 12CS is produced and driving motors 13 is big, so LS electromagnetic proportional valve 12CLS moves in the mode that becomes position 12B.Press oil to enter pump capacity control oil cylinder 12CC, the swash plate 12a of driving pump 12 tilts to graphic min direction, and the capacity of driving pump 12 is reduced.
And if the speed of engineering truck descends, the maximum speed that becomes setting is for example below the speed of a motor vehicle 50km/h, and then controller 30 transmits the pump capacity signal that the capacity that makes driving pump 12 increases to pump capacity control mechanism 12C.
Like this, the present invention only reduces signal to the LS electromagnetic proportional valve 12CLS of pump capacity control mechanism 12C transfer pump capacity, reduces the counter-force of the spool that magnet coil 12CS produced, and gets final product restricted speed.Therefore, under the situation of working load testing agency, can use existing pump capacity control mechanism 12C in the pump capacity control mechanism 12C of oil pressure driving vehicle, also can not need to append new parts, the Control Software of an alteration control unit 30 gets final product.With this simple structure, as the oil pressure driving vehicle of engineering truck just can be no more than as the maximum speed of restricted speed travel.
Have again, under the situation of change maximum speed, only exchange be LS setting pressure set mechanism also be that the LS setting pressure of maximum speed set mechanism is set adapter 39, can change simply as the maximum speed that limits the speed of a motor vehicle.
In addition, the oil pressure driving vehicle also can be the vehicle with upper rotating body.For example, also go for wheel type loader, fork truck or Other Engineering vehicle.Using under the situation of Speed Limitation Devices of the present invention on the vehicle that does not have upper rotating body, can omit oil pressure swivel coupling 15.
And 2 grades of power-transfer clutch 14S of low speed is used in the change speed gear box 14 1 grade of (speed) power-transfer clutch 14F and high speed usefulness are executing the compressed oil power-transfer clutch that closes, and the power-transfer clutch that discharges the mode of pressing oily cut-off clutch is that example describes.
In contrast, can make on 2 grades of power-transfer clutch 14S of 1 grade of (speed) power-transfer clutch 14F using at low speed and high speed usefulness the spring that power-transfer clutch connects usefulness is set, discharge press oil close power-transfer clutch, execute the mode of compressed oil cut-off clutch.Promptly, can be under the situation of 1 grade (speed) making change speed gear box 14 also, to the pressure oil of 1 grade of (speed) power-transfer clutch 14F release from speed-change valve 16,1 grade of (speed) power-transfer clutch closes, execute compressed oil to 2 grades of power-transfer clutch 14S and disconnect 2 grades of power-transfer clutch 14S, change speed gear box 14 is 1 grade (speed).Making change speed gear box 14 is under 2 grades the situation, discharges pressure oil from speed-change valve 16 to 2 grades of power-transfer clutch 14S, and the 2 grades of power-transfer clutchs that close are executed compressed oil to 1 grade of (speed) power-transfer clutch 14F and disconnected 1 grade of (speed) power-transfer clutch 14F, and change speed gear box 14 is 2 grades.
Claims (2)
1. the Speed Limitation Devices of an oil pressure driving vehicle, it has to travel and travels with oil pressure pump (12) with hydraulic motor (13) and variable displacement, it is characterized in that: comprise
Is the mode of LS setting pressure with the difference of pressure that travels with the ejection pressure of oil pressure pump with the load pressure of hydraulic motor (13) and variable displacement that will travel as load perception setting pressure, and the control variable formula is travelled with the pump capacity control mechanism (12C) of the capacity of oil pressure pump (12);
The speed of a motor vehicle testing agency (31) of above-mentioned oil pressure driving vehicle; And
Surpassing under the situation of setting value, change above-mentioned LS setting pressure, the controller (30) that above-mentioned variable displacement the capacity with hydraulic motor (13) of travelling is reduced by this detected speed of a motor vehicle of speed of a motor vehicle testing agency (31).
2. the Speed Limitation Devices of oil pressure driving vehicle according to claim 1 is characterized in that: above-mentioned controller (30) possesses the LS setting pressure set mechanism (39) of setting above-mentioned LS setting pressure,
This set mechanism is to select from multiple LS setting pressure set mechanism.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB0227633A GB2395768B (en) | 2002-11-27 | 2002-11-27 | Vehicle speed limiting system of hydraulic travelling vehicle |
| GB0227633.5 | 2002-11-27 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1509917A CN1509917A (en) | 2004-07-07 |
| CN100515818C true CN100515818C (en) | 2009-07-22 |
Family
ID=9948587
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB200310118054XA Expired - Fee Related CN100515818C (en) | 2002-11-27 | 2003-11-24 | Speed limiting system of oil hydraulic running vehicle |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JP2004176919A (en) |
| CN (1) | CN100515818C (en) |
| DE (1) | DE10354198B4 (en) |
| FR (1) | FR2847524B1 (en) |
| GB (1) | GB2395768B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104495626B (en) * | 2014-12-30 | 2017-01-04 | 中联重科股份有限公司 | Crane control method, device and system and crane |
| US11242672B2 (en) | 2017-09-29 | 2022-02-08 | Hitachi Construction Machinery Co., Ltd. | Wheel loader |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4474104A (en) * | 1983-04-11 | 1984-10-02 | Double A Products Co. | Control system for variable displacement pumps and motors |
| DE3914904C2 (en) * | 1989-05-05 | 1995-06-29 | Rexroth Mannesmann Gmbh | Regulation for a variable displacement pump that works depending on the load |
| DE4226453A1 (en) * | 1992-08-10 | 1994-02-17 | Sauer Sundstrand Gmbh & Co | Hydraulic transmission for fork lift truck - has variable pump and electronic control of transmission ratio |
| JPH08135789A (en) * | 1994-11-09 | 1996-05-31 | Komatsu Ltd | Transmission for vehicular hydraulic drive device and control method for the transmission |
| US6381529B1 (en) * | 2001-06-07 | 2002-04-30 | Deere & Company | Control system for hydrostatic transmission |
-
2002
- 2002-11-27 GB GB0227633A patent/GB2395768B/en not_active Expired - Fee Related
-
2003
- 2003-11-14 JP JP2003385170A patent/JP2004176919A/en active Pending
- 2003-11-20 DE DE10354198A patent/DE10354198B4/en not_active Expired - Fee Related
- 2003-11-20 FR FR0313605A patent/FR2847524B1/en not_active Expired - Fee Related
- 2003-11-24 CN CNB200310118054XA patent/CN100515818C/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| GB0227633D0 (en) | 2003-01-08 |
| GB2395768B (en) | 2006-01-25 |
| FR2847524A1 (en) | 2004-05-28 |
| FR2847524B1 (en) | 2009-03-06 |
| GB2395768A (en) | 2004-06-02 |
| JP2004176919A (en) | 2004-06-24 |
| CN1509917A (en) | 2004-07-07 |
| DE10354198A1 (en) | 2004-06-09 |
| DE10354198B4 (en) | 2008-09-04 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| CP02 | Change in the address of a patent holder |
Address after: Tokyo, Japan, Japan Applicant after: Komatsu Mfg Co., Ltd. Address before: Durham, England Applicant before: British Komatsu Co. Ltd. |
|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20090722 Termination date: 20201124 |