CN101178083B - Engineering vehicle walking driving hydraulic system - Google Patents
Engineering vehicle walking driving hydraulic system Download PDFInfo
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- CN101178083B CN101178083B CN2007103022483A CN200710302248A CN101178083B CN 101178083 B CN101178083 B CN 101178083B CN 2007103022483 A CN2007103022483 A CN 2007103022483A CN 200710302248 A CN200710302248 A CN 200710302248A CN 101178083 B CN101178083 B CN 101178083B
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Abstract
The invention discloses an engineering vehicle walking driving hydraulic system, comprising a bidirectional hydraulic pump and a bidirectional hydraulic motor. Two oil nozzles of the bidirectional hydraulic pump are respectively connected with the driving chamber oil nozzle and the backing chamber oil nozzle of the bidirectional hydraulic motor by connecting pipelines. By the connecting pipelines, the bidirectional hydraulic pump supplies oil for the bidirectional hydraulic motor; a driving chamber overflow valve and a backing chamber overflow valve with reverse overflow directions are arranged in parallelism between the two pipelines which connect the bidirectional hydraulic pump with the bidirectional hydraulic motor; wherein, the driving chamber overflow valve provides overflow loop for the bidirectional hydraulic motor driving chamber; the backing chamber overflow valve provides overflow loop for the bidirectional hydraulic motor; furthermore, the overflow pressure valve value of the driving chamber overflow valve is higher than that of the backing chamber overflow valve. Compared with the prior art, when the engineering vehicle walking driving hydraulic system provided by the invention carries out a backing operation, the highest stable working pressure is low, which leads the highest acceleration is low and the driving characteristic is flexible when the vehicle backs.
Description
Technical field
The present invention relates to a kind of engineering vehicle walking drive system, especially a kind of engineering vehicle walking driving hydraulic system.
Background technique
Engineering machinery and engineering vehicle are of a great variety, and form is different, and dissimilar engineering machinery structures have nothing in common with each other, but from view of function, mainly are divided into three parts: main frame, equipment and traveller.The fixed apparatus that is called that only possesses main frame and equipment is as shore container crane, tower crane etc.; Possess main frame, equipment and traveller but need be called the passive type engineering machinery, as concrete hauling pump, towed roller etc. by what external force could be walked; What possess main frame, equipment and walking driving mechanism is called self-propelled engineer machinery or engineering vehicle, as concrete mixer, Mobile crane, fork truck etc.Self-propelled engineer machinery or engineering vehicle have the characteristics of maneuverability, and its rideability is to weigh the important indicator of complete machine performance.
At present, the travel driving system of engineering vehicle mainly adopts modes such as power transmission modes such as hydraulic machine transmission, hydraulic transmission, minority adopt that mechanical transmission and fax are moved.So-called mechanical transmission is meant that the transmission component from the motor to the wheel adopts mechanical part, generally comprises clutch, gearbox, universal joint, transmission shaft, ransaxle, hub reduction device etc.The so-called hydraulic machine kind of drive is meant in the transmission component from the motor to the wheel and comprises the mode that mechanical part and hydraulic element combine, generally comprises clutch, fluid torque converter, gearbox, universal joint, transmission shaft, ransaxle, hub reduction device etc.So-called hydraulic transmission mode is meant that the transmission component from the motor to the wheel adopts hydraulic element substantially, and main hydraulic transmission original paper comprises oil hydraulic pump, hydrovalve, oil hydraulic motor, ransaxle, hub reduction device etc.The moving prime mover that is meant of so-called fax is that motor drives generator or directly uses external power drive wheel driving motor to travel.
In the above-mentioned kind of drive, hydraulic transmission has that transmission power is big, flexible arrangement, be easy to outstanding advantage such as control, is fit to engineering machinery use, thereby has obtained increasingly extensive application, at slow-moving vehicle with the trend of other kinds of drive of replacement mechanically arranged.
Because the walking hydraulic driving system of engineering machinery is made of general hydraulic element often, after so hydraulic transmission replaces other kinds of drive, produced the some shortcomings part, comprised that walking drives, brake control mode, the aspects such as performance of the stopping power of hydraulic system.The approach that addresses these problems comprise the intrinsic parameter of changing general hydraulic element so that its be more suitable for specific engineering machinery usage requirement, adopt more flexibly control mode to improve the coupling flexibility of general hydraulic element.So-called coupling is flexible to be meant under the prerequisite of the hardware unit that does not change hydraulic element, only needs the software parameter numbers such as control electric current of change hydraulic element just can change its usability, makes the different applications that require of its better matching.
At present, a lot of self-propelled engineer machineries such as road roller, grader, bulldozer, container fork truck, harbour wheel mounted crane etc. adopt closed type hydraulic system as the walking transmission scheme, oil hydraulic motor wherein adopts the general two-way hydraulic motor of engineering machinery often, and the usability of the both direction of this motor is identical.And self-propelled engineer machinery advances very not identical with the requirement of the both direction that falls back even differs widely, and causes general oil hydraulic motor can not well adapt to the actual usage requirement of engineering machinery.
For example, generally speaking, when engineering machinery is advanced, there are startup, smooth-ride, three processes of retarding braking quickened.The control performance of operator expectation is, has higher driving force when engineering machinery is quickened to start, and can finish start-up course fast; When engineering machinery is braked, can have lower braking force, realize soft braking.For another example, when engineering machinery is advanced, generally need bigger driving force, and fall back or when adopting the working state that falls back to brake, the action of wishing to travel is softer, the dangerous situation that backward commands falls back at once fast can not occur sending.The hydraulic system of above-mentioned employing two-way hydraulic motor since oil hydraulic motor on two sense of rotation, have identical characteristic, can not satisfy advances in the walking fall back the expectation have different control characteristics requirement.
Summary of the invention
At above-mentioned defective, the technical problem that the present invention solves is, a kind of engineering vehicle walking driving hydraulic system is provided, and this walking driving hydraulic system can make engineering machinery have the different control characteristics of travelling under different working state such as advance, fall back, and satisfies operator's manipulation demand.
Engineering vehicle walking driving hydraulic system provided by the invention, comprise bidirectional hydraulic pump and two-way hydraulic motor, two hydraulic fluid ports of described bidirectional hydraulic pump connect the actuator chamber hydraulic fluid port of described two-way hydraulic motor and the chamber hydraulic fluid port that falls back by connecting pipeline respectively, by above-mentioned connecting pipeline, the bidirectional hydraulic pump is to the two-way hydraulic motor fuel feeding; Between two connecting pipelines of described connection bidirectional hydraulic pump and two-way hydraulic motor, be installed in parallel the opposite actuator chamber relief valve of overflow direction and the chamber relief valve that falls back, wherein, the actuator chamber relief valve is for described two-way hydraulic motor actuator chamber provides skimmer circuit, and the chamber relief valve that falls back provides skimmer circuit for the described two-way hydraulic motor chamber of falling back; And the oil pressure relief threshold values of described actuator chamber relief valve is higher than the oil pressure relief threshold values of the described chamber relief valve that falls back.
Preferably, the described chamber relief valve that falls back has than the littler pressure flow characteristic curve of described actuator chamber relief valve slope.
Preferably, the fall back specified excess flow of chamber relief valve is higher than the specified excess flow of actuator chamber relief valve.
Preferably, connect between two connecting pipelines of bidirectional hydraulic pump and two-way hydraulic motor, also be connected with the first repairing one-way valve and the second repairing one-way valve of series connection; Wherein, what directly be connected with fluid motor-driven chamber hydraulic fluid port by the high voltage terminal of state is the first repairing one-way valve, and the high voltage terminal of cut-off state is direct, and what fall back that the chamber hydraulic fluid port is connected with oil hydraulic motor is the second repairing one-way valve; Interconnecting of the first repairing one-way valve, and the oil outlet of two low voltage terminal connection slippage pumps by the low voltage terminal of state and the low voltage terminal by state of the second repairing one-way valve.
Preferably, described bidirectional hydraulic pump is specially the bidirectional variable hydraulic planger pump.
Preferably, described two-way hydraulic motor is specially the bidirectional ram oil hydraulic motor.
Preferably, described slippage pump is and the integrated guide's gear pump of described bidirectional hydraulic pump that the filler opening of this guide's gear pump directly connects fuel tank.
Compared with prior art, engineering vehicle walking driving hydraulic system provided by the invention is at the actuator chamber hydraulic fluid port of two-way hydraulic motor and fall back two opposite relief valves of overflow direction have been installed between the hydraulic fluid port of chamber, and the oil pressure relief difference of two relief valves, wherein, oil pressure relief when making the normal forward travel state of vehicle is higher, oil pressure relief when vehicle falls back working state is lower, this just makes this hydraulic system when driving and falling back work, its highest stabilizing working pressure also should have difference of height other mutually, during normal forward drive, highest stabilizing working pressure height, accordingly, hydraulic system can provide higher maximum drive ability, vehicle is normally advanced can obtain higher acceleration when travelling; When falling back working state, the highest stabilizing working pressure is low, and is corresponding, and the high driving ability that hydraulic system provides is lower, and high-acceleration was lower when vehicle was fallen back, and ride characteristic is comparatively soft.Above-mentioned ride characteristic can satisfy the job requirement of vehicle preferably, obtains best driving effect.
In a preferred embodiment of the invention,, can make the hydraulic pressure of this hydraulic system be unlikely low, avoid the hydraulic work system that the hydraulic oil loss causes in the system undesired for this hydraulic system provides feed circuit.
The present invention also provides some more excellent schemes for the selection of each hydraulic element in this hydraulic system, uses these hydraulic pressure original papers, can make this hydraulic system have preferable performance.
Description of drawings
Fig. 1 is the hydraulic principle sketch of the engineering vehicle walking driving hydraulic system that provides of first embodiment of the invention;
Fig. 2 is the pressure flow characteristic curve of two relief valves in the first embodiment of the invention;
Fig. 3 be the hydraulic work system that provides in the first embodiment of the invention when the cruising state, the schematic representation of time dependent scope of system pressure and process.
Embodiment
Please referring to Fig. 1, this figure is the hydraulic principle sketch of the engineering vehicle walking driving hydraulic system that provides of first embodiment of the invention.
As shown in the figure, this project vehicle to run drives hydraulic system and comprises bidirectional hydraulic pump 1, two-way hydraulic motor 2, and two hydraulic fluid ports of described bidirectional hydraulic pump 1 connect the actuator chamber hydraulic fluid port A of described two-way hydraulic motor 2 and the chamber hydraulic fluid port B that falls back by connecting pipeline respectively.Described two-way hydraulic motor 2 bidirectional hydraulic pump 1 provide various flows to hydraulic oil the time, can on both direction, rotate respectively.The output characteristics of this two-way hydraulic motor 2 on two sense of rotation is consistent, still, in actual use, the effect difference of two sense of rotation, one of them sense of rotation powered vehicle is advanced, and another sense of rotation falls back vehicle or brakes.In order to distinguish two hydraulic fluid ports of two-way hydraulic motor, when being in the sense of rotation that powered vehicle advances with two-way hydraulic motor 2, its high pressure hydraulic fluid port is called actuator chamber hydraulic fluid port A, and corresponding, the low pressure hydraulic fluid port is called the chamber hydraulic fluid port B that falls back.
Above-mentioned bidirectional hydraulic pump 1 and two-way hydraulic motor 2 interconnective pipelines constitute a simple and easy and complete oil hydraulic circuit, described bidirectional hydraulic pump 1 is under the drive of prime mover, to different direction spinnings, can to described two-way hydraulic motor 2 provide various flows to hydraulic oil, it is rotated to different direction, thereby realize advancing or falling back of vehicle, and braking.But, there is open defect in this easy oil hydraulic circuit, subject matter is that the bidirectional hydraulic pump 1 in this oil hydraulic circuit all has identical performance characteristic with two-way hydraulic motor 2 on two sense of rotation, and actual vehicle then has different control characteristics with the time expectation of falling back advancing.When advancing, hope can provide enough control moments, can quicken rapidly; Fall back or adopt working state when braking of falling back, hope can be softer, can not cause owing to acceleration is excessive and control inconvenience.
At the problems referred to above, in the hydraulic system shown in Figure 1, between two connecting pipelines of the actuator chamber hydraulic fluid port A of described bidirectional hydraulic pump 1 hydraulic fluid port and two-way hydraulic motor 2, the chamber hydraulic fluid port B that falls back, be installed in parallel the opposite actuator chamber relief valve 3-1 and the chamber relief valve 3-2 that falls back of overflow direction; Wherein, the overflow direction of actuator chamber relief valve 3-1 is to flow to the chamber hydraulic fluid port B that falls back from actuator chamber hydraulic fluid port A; The overflow direction of chamber relief valve 3-2 of falling back is to flow to actuator chamber hydraulic fluid port A from the chamber hydraulic fluid port B that falls back.The oil pressure relief threshold values difference of above-mentioned relief valve, wherein, the oil pressure relief threshold values P1 of actuator chamber relief valve 3-1 is higher than the oil pressure relief threshold values P2 of the chamber relief valve 3-2 that falls back.A typical numerical value is, the oil pressure relief threshold values P1 of described actuator chamber relief valve 3-1 is 35MPa, and the oil pressure relief threshold values P2 of the described chamber relief valve 3-2 that falls back is 20MPa.
The above-mentioned actuator chamber relief valve 3-1 and the chamber relief valve 3-2 that falls back have determined the maximum pressure of this hydraulic work system when driving working state or falling back working state respectively, because the difference of two relief valve oil pressure relief threshold values, make the highest system pressure of this hydraulic system when driving working state be higher than the highest system pressure under the working state that falling back.Like this, when driving work, this hydraulic system provides bigger high drive by described two-way hydraulic motor 2; When falling back work, this hydraulic system then provides less high drive by described two-way hydraulic motor 2.Accordingly, can obtain bigger high-acceleration when this vehicle advances, and this vehicle then can obtain less high-acceleration when falling back.
Above-mentioned actuator chamber relief valve 3-1 with fall back chamber relief valve 3-2 except the oil pressure relief threshold values is different, also have different pressure flow characteristics autos.Please referring to Fig. 2, this illustrates the pressure flow characteristic curve of two relief valves.The abscissa of this figure is represented flow, and y coordinate is represented pressure.The pressure flow characteristic curve of described actuator chamber relief valve 3-1 is the oblique line D1 among the figure, and the described pressure flow characteristic curve that falls back chamber relief valve 3-2 is figure bend D2.As can be seen, the slope of oblique line D1 is than oblique line D2 height, and its present position on figure also is higher than oblique line D2.This expression, the pressure flow of actuator chamber relief valve 3-1 is than the pressure flow ratio that is higher than the chamber relief valve 3-2 that falls back, under the just identical pressure, the excess flow passing capacity of actuator chamber relief valve 3-1 is less, and the excess flow passing capacity of the chamber relief valve 3-2 that falls back is bigger.The specified excess flow that is called this relief valve corresponding to the excess flow of relief valve oil pressure relief threshold values.For actuator chamber relief valve 3-1, under the pressure corresponding to oil pressure relief threshold values P1, corresponding specified excess flow is Q1; For the chamber relief valve 3-2 that falls back, under the pressure corresponding to oil pressure relief threshold values P2, corresponding specified excess flow is Q2, shown in Fig. 2, Q1＜Q2, typically, actuator chamber relief valve 3-1 specified excess flow Q1 of correspondence when being in oil pressure relief threshold points P1=35MPa is 400L/min; The chamber relief valve 3-2 specified excess flow Q2 of correspondence when being in oil pressure relief threshold points P2=20MPa that falls back is 600L/min.Above-mentioned different specified excess flow makes relief valve reach the oil pressure relief threshold values, and under the situation of beginning overflow, the excess flow difference is also different on high-tension side antihypertensive effect; For the low relief valve of chamber relief valve 3-2 selection pressure flow-rate ratio that falls back, specified excess flow is higher when making it reach the overflow threshold values, can avoid the insufficient reversible drive ability situation really up to the mark that causes of step-down, promptly, falling back or need make this hydraulic work system when the state of falling back is braked, if be higher than the situation of oil pressure relief threshold values, the relief valve 3-2 that falls back will pass through enough excess flows rapidly, system pressure is reduced rapidly, fall back or brake soft.
Please continue referring to Fig. 1, drive in the hydraulic system, connect between two connecting pipelines of bidirectional hydraulic pump 1 and two-way hydraulic motor 2, also be connected with the first repairing one-way valve 4-1 and the second repairing one-way valve 4-2 of series connection at this project vehicle to run; Wherein, the first repairing one-way valve 4-1 directly is connected with the actuator chamber hydraulic fluid port A of described two-way hydraulic motor 2 at the high voltage terminal by state, and the high voltage terminal of the described second repairing one-way valve 4-2 cut-off state directly is connected with the chamber hydraulic fluid port B that falls back of described two-way hydraulic motor 2; The low voltage terminal by state of two one-way valves interconnects, and forms both common port C; This common port C connects the oil outlet of a slippage pump 5 by pipeline; This slippage pump 5 be one with the integrated guide's gear pump of described bidirectional hydraulic pump 1, its oil outlet provides pressure to the common port C of the first repairing one-way valve 4-1 and the second repairing one-way valve 4-2 as mentioned above, its filler opening connects fuel tank 6.The effect of this slippage pump 5 is repairing in this hydraulic system.When described bidirectional hydraulic pump 1 was worked, this slippage pump 5 was also worked simultaneously, and regardless of described bidirectional hydraulic pump 1 sense of rotation, slippage pump 5 is that the hydraulic oil in the fuel tank 6 is extracted out all the time, and pumps from oil outlet with certain pressure.The above-mentioned slippage pump 5 and the first repairing one-way valve 4-1, the second repairing one-way valve 4-2 constitute the feed circuit of this hydraulic system jointly.
Need the reason of above-mentioned feed circuit to be, the major loop of this hydraulic system is a closed system, in theory, hydraulic oil in this hydraulic system can circulate, but because the seepage of each link etc., can cause the loss of hydraulic oil, if do not replenish all the time, this system can finally can't normally move owing to the hydraulic oil quantity not sufficient.Because hydraulic oil reduces and at first shows as low voltage terminal because low on fuel and hypotony can to this hydraulic system repairing, remedy the loss of hydraulic oil as standard in the system.
In this system, it is the delivery pressure of 2.5MPa that the oil outlet of described slippage pump 5 provides a typical pressure value, this delivery pressure is added on the common port C of the described first repairing one-way valve 4-1 and the second repairing one-way valve 4-2, this common port C is because two lateral lines all are provided with one-way valve, therefore, no matter which kind of working state is this hydraulic system be in, the pressure ratio of the 2.5MPa that the pressure of its low voltage side at first obtains from slippage pump 5 with this common port C, since this common port C be in two one-way valves by the time low voltage side, therefore, as long as the pressure of system low-voltage side is higher than 2.5MPa, all not conductings of then above-mentioned one-way valve; When the pressure of system low-voltage side is lower than 2.5MPa, lead to one-way valve conducting under the effect of the pressure of the 2.5MPa that slippage pump 5 provides of this low voltage side, to this hydraulic system low voltage side repairing.Through after the repairing, the hydraulic oil of loss is replenished in this system, and the pressure of hydraulic system low voltage side is recovered, and is final, and the one-way valve that this pressure will make described conducting is again by, the normal working state of system recovery.
The effect of above-mentioned repairing oil circuit and above-mentioned overflow oil circuit combine, and the effect that reaches is that whole system is operated under the suitable pressure range.Please referring to Fig. 3, this illustrates this hydraulic work system when the cruising state, the excursion of system pressure and process, as can be seen, when system pressure is higher than the oil pressure relief 35MPa that drives relief valve 3-1, its pressure meeting very fast reduction owing to the action that drives relief valve 3-1; Equally, when system pressure was lower than the outlet pressure 2.5MPa of slippage pump 5, system pressure can recover rapidly owing to the effect of feed circuit.Like this, the pressure of this hydraulic system generally will be under normal state between two ultimate pressures.
In above-mentioned hydraulic system, the described bidirectional hydraulic pump 1 concrete preferred bidirectional variable hydraulic planger pump that adopts.
In above-mentioned hydraulic system, the described two-way hydraulic motor 2 preferred bidirectional ram oil hydraulic motors that adopt.
In above-mentioned hydraulic system, described slippage pump 5 uses gear pump.
In above-mentioned hydraulic system, described relief valve can adopt the adjustable relief valve of electric proportional control, perhaps the adjustable relief valve of hydraulic proportional control.Above-mentioned adjustable relief valve can adjust the Maximum operating pressure of this hydraulic system as required by providing electric current or pressure to adjust the oil pressure relief threshold values of relief valve as required.
During above-mentioned hydraulic work system, when two-way hydraulic motor 2 is in when driving working state, the upper limit pressure of hydraulic system is the oil pressure relief threshold values of actuator chamber relief valve 3-1.In case system pressure is higher than this oil pressure relief threshold values, the hydraulic oil that then is on high-tension side actuator chamber hydraulic fluid port A one side will flow to the chamber hydraulic fluid port B that falls back of low voltage side by this actuator chamber relief valve 3-1, system pressure is reduced, when the oil pressure relief threshold values of actuator chamber relief valve 3-1 was 35MPa, the highest stable operation pressure of this hydraulic system can not surpass 35MPa.Same reason, when hydraulic work system at the state of falling back, comprise that vehicle falls back or vehicle because braking and need being operated in when falling back state, the stable operation upper pressure limit of hydraulic system be decided by the to fall back oil pressure relief threshold values of chamber relief valve 3-2 is 20MPa.Because the driving force that oil hydraulic motor outwards provides is directly proportional with the pressure of hydraulic system, therefore, when driving working state, its maximum driving force makes this vehicle can obtain higher acceleration because system's highest stabilizing working pressure is higher and higher at this hydraulic work system.On the contrary, when this hydraulic work system when falling back working state, its maximum driving force is because the highest stabilizing working pressure of this hydraulic system is lower, the high-acceleration that vehicle can obtain is lower, it is softer that the dynamic property of vehicle is shown as, the speed that can not produce when falling back raise suddenly cause out of control.
Need to prove, the vehicle that uses this hydraulic system is when braking, can only increase the discharge capacity of two-way hydraulic motor 2, but this mode of braking possibly can't reach required braking effect, when if brake request is higher, just need be with two-way hydraulic motor 2 counter-rotatings, like this, this hydraulic system just is operated in the state of falling back.Under this braking state, because the high drive of hydraulic system is less, then action can be not really up to the mark during this car brakeing, can obtain soft braking effect.
Above embodiment only provides the concise and to the point working principle of this hydraulic system, and actual work system also can be equipped with other relevant accessory in order to obtain better work effect in this hydraulic system.Related domain staff can need not creative work according to existing related known technology under the guidance of the foregoing description, can carry out above-mentioned work, will not describe in detail at this.
The above only is a preferred implementation of the present invention; should be pointed out that for those skilled in the art, under the prerequisite that does not break away from the principle of the invention; can also make some improvements and modifications, these improvements and modifications also should be considered as protection scope of the present invention.
Claims (7)
1. engineering vehicle walking driving hydraulic system, comprise bidirectional hydraulic pump and two-way hydraulic motor, two hydraulic fluid ports of described bidirectional hydraulic pump connect the actuator chamber hydraulic fluid port of described two-way hydraulic motor and the chamber hydraulic fluid port that falls back by connecting pipeline respectively, by above-mentioned connecting pipeline, the bidirectional hydraulic pump is to the two-way hydraulic motor fuel feeding; It is characterized in that, between two connecting pipelines of described connection bidirectional hydraulic pump and two-way hydraulic motor, be installed in parallel the opposite actuator chamber relief valve of overflow direction and the chamber relief valve that falls back, wherein, the actuator chamber relief valve is for described two-way hydraulic motor actuator chamber provides skimmer circuit, and the chamber relief valve that falls back provides skimmer circuit for the described two-way hydraulic motor chamber of falling back; And the oil pressure relief threshold values of described actuator chamber relief valve is higher than the oil pressure relief threshold values of the described chamber relief valve that falls back.
2. engineering vehicle walking driving hydraulic system according to claim 1 is characterized in that, the described chamber relief valve that falls back has than the littler pressure flow characteristic curve of described actuator chamber relief valve slope.
3. engineering vehicle walking driving hydraulic system according to claim 2 is characterized in that, the specified excess flow of the chamber relief valve that falls back is higher than the specified excess flow of actuator chamber relief valve.
4. engineering vehicle walking driving hydraulic system according to claim 3 is characterized in that, connects between two connecting pipelines of bidirectional hydraulic pump and two-way hydraulic motor, also is connected with the first repairing one-way valve and the second repairing one-way valve of series connection; Wherein, what directly be connected with fluid motor-driven chamber hydraulic fluid port by the high voltage terminal of state is the first repairing one-way valve, and the high voltage terminal of cut-off state is direct, and what fall back that the chamber hydraulic fluid port is connected with oil hydraulic motor is the second repairing one-way valve; Interconnecting of the first repairing one-way valve, and the oil outlet of two low voltage terminal connection slippage pumps by the low voltage terminal of state and the low voltage terminal by state of the second repairing one-way valve.
5. according to each described engineering vehicle walking driving hydraulic system of claim 1-4, it is characterized in that described bidirectional hydraulic pump is specially the bidirectional variable hydraulic planger pump.
6. engineering vehicle walking driving hydraulic system according to claim 5 is characterized in that described two-way hydraulic motor is specially the bidirectional ram oil hydraulic motor.
7. engineering vehicle walking driving hydraulic system according to claim 4 is characterized in that, described slippage pump is and the integrated guide's gear pump of described bidirectional hydraulic pump that the filler opening of this guide's gear pump directly connects fuel tank.
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| CN2007103022483A CN101178083B (en) | 2007-12-20 | 2007-12-20 | Engineering vehicle walking driving hydraulic system |
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| CN2007103022483A CN101178083B (en) | 2007-12-20 | 2007-12-20 | Engineering vehicle walking driving hydraulic system |
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| CN101178083A CN101178083A (en) | 2008-05-14 |
| CN101178083B true CN101178083B (en) | 2010-06-02 |
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| CN2007103022483A Expired - Fee Related CN101178083B (en) | 2007-12-20 | 2007-12-20 | Engineering vehicle walking driving hydraulic system |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN103088167B (en) * | 2013-01-30 | 2015-11-04 | 扬州扬宝机械有限公司 | A kind of water squeezing striking-out machine rubber roll felt roll rotates synchronization hydraulic system |
| CN104791311B (en) * | 2015-04-28 | 2017-01-04 | 湖南五新隧道智能装备股份有限公司 | A kind of engineering truck hydraulic moving control system |
| CN106827648A (en) * | 2017-04-18 | 2017-06-13 | 河海大学常州校区 | A kind of hydraulic/mechanical combination drive servo-press transmission system |
| US20190011046A1 (en) * | 2017-07-05 | 2019-01-10 | GM Global Technology Operations LLC | Hydraulic circuit to enable unidirectional flow under forward and reverse positive displacement pump rotation |
| CN107725197A (en) * | 2017-11-02 | 2018-02-23 | 江苏金通灵流体机械科技股份有限公司 | A kind of gas turbine dislocation generation vehicle electric hydraulic activating system |
| CN108860305B (en) * | 2018-04-17 | 2021-03-23 | 万向钱潮传动轴有限公司 | EPS of large vehicle |
| CN109139588A (en) * | 2018-11-09 | 2019-01-04 | 徐工集团工程机械有限公司 | Hydraulic power system and the dual-purpose working truck of rail |
| CN109792889A (en) * | 2019-03-19 | 2019-05-24 | 河北宗申戈梅利农业机械制造有限公司 | A kind of ensilage machine feeding unit Quick-speed braking arrangement |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN85108834A (en) * | 1985-12-10 | 1987-06-24 | 株式会社小松制作所 | Control device for hydraulic motor |
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2007
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Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN85108834A (en) * | 1985-12-10 | 1987-06-24 | 株式会社小松制作所 | Control device for hydraulic motor |
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