CN103522929B - Quarry tipper determines variable delivery hydraulic system - Google Patents

Quarry tipper determines variable delivery hydraulic system Download PDF

Info

Publication number
CN103522929B
CN103522929B CN201310497282.6A CN201310497282A CN103522929B CN 103522929 B CN103522929 B CN 103522929B CN 201310497282 A CN201310497282 A CN 201310497282A CN 103522929 B CN103522929 B CN 103522929B
Authority
CN
China
Prior art keywords
valve
mouth
lifting
pump
flow
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
CN201310497282.6A
Other languages
Chinese (zh)
Other versions
CN103522929A (en
Inventor
杨胜清
唐绪文
王玉
唐云娟
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Guangxi Liugong Machinery Co Ltd
Original Assignee
Guangxi Liugong Machinery Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Guangxi Liugong Machinery Co Ltd filed Critical Guangxi Liugong Machinery Co Ltd
Priority to CN201310497282.6A priority Critical patent/CN103522929B/en
Publication of CN103522929A publication Critical patent/CN103522929A/en
Application granted granted Critical
Publication of CN103522929B publication Critical patent/CN103522929B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Abstract

The present invention relates to a kind of quarry tipper and determine variable delivery hydraulic system, the quarry tipper of the present invention hydrostatic steering system determined in variable delivery hydraulic system comprises steering cylinder, load-reacting pump, deflector, signal control valve, shuttle valve, flow-controlling gate, and deflector is connected with steering cylinder; The oil circuit control of priority valve is communicated with the left end signal port of flow-controlling gate with the P1 signal port of signal control valve simultaneously; The left position oil outlet of flow-controlling gate is through the P mouth unilaterally connected of check valve to hydraulic control lifting valve, and the right position oil outlet of flow-controlling gate is connected with the P mouth of deflector, and the oil inlet of flow-controlling gate is connected with the pumping hole of load-reacting pump; The pumping hole of load-reacting pump is connected with the P2 mouth of signal control valve, and the P3 mouth of signal control valve is connected with the LS valve in load-reacting pump, and the LS mouth of signal control valve is connected with the LS mouth of deflector.Working stability of the present invention, structure are simple and save energy consumption.

Description

Quarry tipper determines variable delivery hydraulic system
Technical field
The present invention relates to a kind of quarry tipper hydraulic efficiency pressure system, particularly relate to a kind of quarry tipper and determine variable delivery hydraulic system.
Background technology
Quarry tipper is that mine has been a kind of heavy duty truck of Ore Transportation task in the open, be characterized in that transport distance is short, carrying capacity is strong, often coordinated by large-scale power shovel, large excavator or large-duty loader etc. and load, travel to and fro between digging field and dumping place, be widely used in the cubic metre of earth and stone carriers such as metallurgy, non-metals, chemical industry, coal.Quarry tipper is primarily of compositions such as power system, driving system, vehicle frame, container, suspension, steering swivel system, hydraulic efficiency pressure system, brake system, electric system and cover panels, at present, the tonnage of quarry tipper has from 20 tons to nearly kiloton, generally, the mine car tonnage that mine uses and its output adapt, produce the small mine of megatonnage per year, the vehicle using 25-50 ton more; Medium-sized mine, the mine that yearly output 500-1000 is ten thousand tons, many use load-carryings are the type of 100 tons; The mine that yearly output is more than 1,000 ten thousand tons, the then mine car using more than 200 tonnes more.
The hydraulic efficiency pressure system of quarry tipper generally comprises hydrostatic steering system, hydraulic lifting system etc., has quantitative system at present, also have variable system in these hydraulic efficiency pressure systems, also has quantitatively and hydraulic efficiency pressure system that variable is combined with each other.Hydrostatic steering system is often made up of steering pump, deflector, steering cylinder, energy storage or emergent steering pump etc., quarry tipper generally adopts deflection rubber-tyred to turn to, steering hardware is made up of two steering cylinders and dual rotation pull bar, one steering cylinder large chamber oil-feed and another steering cylinder loculus oil-feed, add the transmission of duplex pull rod power, front tyre can be made to deflect, realize car load turning function.Hydraulic lifting system mainly contains lifting pump, lifting valve, priority valve (electricity or liquid), the compositions such as balance cock, lifting valve spool position is controlled by priority valve, elevating ram can be realized rise, decline, float and the function of meta, vehicle will allow lifting valve be operated in floating position when walking, the large loculus of elevating ram is connected with fuel tank simultaneously, reduce the container upper and lower play of mine car in the process of moving caused by road surface operating mode or goods inertia, the effect of balance cock be when discharging operating mode after goods and container center of gravity cross hinge-point, prevent the too fast upset of container, guarantee discharging is steady.
The hydraulic efficiency pressure system (except brake system) of existing quarry tipper is generally made up of hydraulic lifting system and hydrostatic steering system, hydraulic lifting system is often made up of elements such as fix-displacement pump, lifting valve, balance cock, priority valve (or electromagnetism handle), Multi-stage cylinders, and hydrostatic steering system is often made up of elements such as fix-displacement pump, pressure-gradient control valve, deflector, steering cylinders.At present, most quarry tipper all adopts fixed dilivery hydraulic system, and also have quantitatively and situation that variable delivery hydraulic system is combined with each other, in large-tonnage type, hoisting system and steering swivel system have the hydraulic efficiency pressure system of a lot of use entire variable.
The hydraulic efficiency pressure system operating mode of quarry tipper is relatively simple, fixed dilivery hydraulic system due to its degree of ripeness high, good reliability, cost performance advantages of higher can meet the normal operation requirement of quarry tipper completely, but just these popular at present fixed dilivery hydraulic systems also exist some technical deficiencies:
(1) for the combining hydraulic system adopting pressure-gradient control valve, as shown in Figure 1, there is more degradation of energy through this primary Ioops of pressure-gradient control valve in steering pump always, and the effect of pressure-gradient control valve carries out assignment of traffic and makes to turn to steadily, in view of the factor of quarry tipper operating mode, this pressure-gradient control valve can remove completely.
(2) for the hydraulic efficiency pressure system adopted as shown in Figure 2, although canceled pressure-gradient control valve, but the stationarity of steering swivel system is not guaranteed, and when turning to operation, the flow of steering pump all enters steering swivel system, how many oil masses entering steering cylinder is determined by the rotating speed of driving engine, rotating speed more high flow capacity is larger, make to turn to fluid, the excess traffic of steering pump is all through turning to by pass valve high pressure kicks oil sump tank, degradation of energy is serious, and the frequent unlatching of by pass valve can have a strong impact on component life.
(3) some producer domestic uses the mode of constant pressure variable displacement pump+deflector at steering swivel system, and hydraulic lifting system adopts fix-displacement pump, and two subsystems does not collaborate.Constant pressure variable displacement pump provides a constant pressure source to hydrostatic steering system, and when steering load increases, capacity of pump reduces automatically, when steering load diminishes, capacity of pump strengthens, and the form of meta is closed in deflector, when turning to stopping, because pump intake pressure is suppressed height, make capacity of pump minimum.This hydraulic efficiency pressure system requires that steering pump and lifting pump all need the normal work requirements of enough discharge capacity guarantee machines, steering pump is only devoted oneself to work in steering procedure, steering pump is not utilized when lifting operating mode, when lifting operating mode, only has lifting pump in work, lifting capacity of pump is larger, and meta energy loss is serious.
Summary of the invention
The object of the invention is to determine the above-mentioned shortcoming of variable delivery hydraulic system for existing quarry tipper and provide simple, that energy consumption can the be reduced quarry tipper of a kind of structure to determine variable delivery hydraulic system.
Technical scheme of the present invention is achieved in that provides a kind of quarry tipper to determine variable delivery hydraulic system, comprises hydraulic lifting system and hydrostatic steering system;
Wherein hydraulic lifting system comprises elevating ram, hydraulic control lifting valve, priority valve, balance cock, lifting pump, described lifting pump be connected with the P mouth of hydraulic control lifting valve, priority valve is connected with the control port of hydraulic control lifting valve, the A mouth of hydraulic control lifting valve is connected with elevating ram with B mouth, and balance cock is connected between hydraulic control lifting valve and elevating ram;
Hydrostatic steering system comprises steering cylinder, load-reacting pump, deflector, and deflector is connected with steering cylinder; Also comprise signal control valve, shuttle valve, flow-controlling gate in addition, the oil circuit control of priority valve is communicated with the left end signal port of described flow-controlling gate with the P1 signal port of signal control valve simultaneously;
The left position oil outlet of flow-controlling gate is through the P mouth unilaterally connected of check valve to hydraulic control lifting valve, and the right position oil outlet of flow-controlling gate is connected with the P mouth of deflector, and the oil inlet of flow pilot operated valve device is connected with the pumping hole of load-reacting pump;
The pumping hole of load-reacting pump is connected with the P2 mouth of described signal control valve, and the P3 mouth of signal control valve is connected with the LS valve in load-reacting pump, and the LS mouth of signal control valve is connected with the LS mouth of deflector.
In the present invention, quarry tipper lifting operating mode is separate with walking operating mode, flow-controlling gate controls the direction of the traffic of steering pump, when steering situation, the oil circuit control of priority valve and the conducting of fuel tank loop, signal pressure is not had at signal control valve right-hand member, the left end of flow-controlling gate does not simultaneously have control signal yet, flow-controlling gate is operated in right position under spring force, signal control valve is operated in left position under spring force, the fluid of steering pump all enters steering swivel system, the sufficient flow of steering swivel system when effective guarantee turns to work, now hydrostatic steering system is a typical load sensitive system.When lifting operating mode, the pilot signal taking from hoisting system acts on signal control valve right-hand member, the left end of flow-controlling gate simultaneously is also subject to the control of this pressure signal, flow-controlling gate is operated in left position, signal control valve is operated in right position, the fluid of steering pump all collaborates in the middle of hoisting system, now because signal control valve is operated in right position, the pressure of pumping hole is turned to cause the right-hand member of the LS valve of load-reacting pump through the right position of signal control valve, LS valve is operated in right position, steering pump is now in max.cap., is equivalent to a fix-displacement pump.When lifting operating mode, the fluid of steering pump all collaborates in hoisting system, can reduce lifting capacity of pump on the one hand, on the other hand the flow of steering pump is utilized effectively, reaches energy-conservation object to a certain extent.The fluid of shuttle valve takes from lifting pilot control oil circuit, as long as hoisting system is in the operating mode of lifting or decline, shuttle valve all will obtain pressure oil, and then allow flow-controlling gate and signal control valve be operated in left position and right position respectively, make the fluid of steering pump collaborate in hoisting system; When hoisting system is in meta or floating operating mode, the control presssure of shuttle valve communicates with fuel tank, this insufficient pressure is to overcome the spring force of flow-controlling gate, under spring force, flow-controlling gate is operated in right position, the fluid of steering pump all flows into steering swivel system, ensures that steering swivel system flow is enough.
The beneficial effect that the present invention compared with prior art has:
(1) quarry tipper determines the array mode of hydraulic lifting system and hydrostatic steering system employing steering load sensitivity and lifting quantitative system in variable delivery hydraulic system, turning efficiency can be made greatly to promote on the one hand, hoisting system adopts fix-displacement pump on the other hand, carrying performance-oriented while, cost is not high than quantitative system increase, lower than entire variable system cost, structure is simple.
(2) because hydrostatic steering system adopts load-sensitive loop, steering swivel system does not have excess flow loss, and energy-saving effect is remarkable.
(3) flow of load sensitive system pump is only relevant with the aperture of valve, and have nothing to do with load, the handling of steering swivel system is good.
(4) determine the realization of variable delivery hydraulic system, make full use of capacity of pump, expand the using function of controllable capacity pump.
Accompanying drawing explanation
Fig. 1 is wherein a kind of schematic diagram at existing quarry tipper hydraulic lifting system and hydrostatic steering system interflow.
Fig. 2 is another schematic diagram at existing quarry tipper hydraulic lifting system and hydrostatic steering system interflow.
Fig. 3 is the schematic diagram that quarry tipper of the present invention determines the array mode turning to load-sensitive and lifting quantitative system in variable delivery hydraulic system.
Parts title and sequence number in figure:
Lifting pump 1, load-reacting pump 2, flow-controlling gate 3, signal control valve 4, shuttle valve 5, priority valve 6, elevating ram 7, steering cylinder 8, hydraulic control lifting valve 9, balance cock 10, deflector 11, check valve 12.
Detailed description of the invention
Below in conjunction with accompanying drawing, specific embodiments is described.
As shown in Figure 3, in the present embodiment, quarry tipper is determined variable delivery hydraulic system and is comprised hydraulic lifting system and hydrostatic steering system; Wherein hydraulic lifting system comprises elevating ram 7, hydraulic control lifting valve 9, priority valve 6, balance cock 10, lifting pump 1, the pumping hole of lifting pump 1 be connected with the P mouth of hydraulic control lifting valve, A, B mouth of priority valve 6 is connected with the control port of hydraulic control lifting valve 9, the A mouth of hydraulic control lifting valve 9 is connected with elevating ram 7 with B mouth, balance cock 10 is connected between hydraulic control lifting valve 9 and elevating ram 7, is namely connected between the loculus hydraulic fluid port of elevating ram and the A mouth of hydraulic control lifting valve; Hydrostatic steering system comprises steering cylinder 8, load-reacting pump 2, deflector 11, signal control valve 4, shuttle valve 5, flow-controlling gate 3, check valve 12, and deflector 11 is connected with steering cylinder 8; The oil circuit control of priority valve is communicated with the left end signal port of flow-controlling gate with the P1 signal port of signal control valve 4 simultaneously; The left position oil outlet of flow-controlling gate 3 is through the pumping hole unilaterally connected of check valve 12 to hydraulic control lifting valve 1, and the right position oil outlet of flow-controlling gate 3 is connected with the P mouth of deflector 11, and the oil inlet of flow pilot operated valve device 3 is connected with the pumping hole of load-reacting pump 2; The pumping hole of load-reacting pump 2 is connected with the P2 mouth of signal control valve 4, and the P3 mouth of signal control valve 4 is connected with the LS valve in load-reacting pump 2, and the LS mouth of signal control valve 4 is connected with the LS mouth of deflector.
In an embodiment, quarry tipper lifting operating mode is separate with walking operating mode, flow-controlling gate 3 controls the direction of the traffic of load-reacting pump 2, when steering situation, priority valve attonity, signal pressure is not had at the right-hand member of signal control valve 4, the left end of flow-controlling gate 3 does not simultaneously have control signal yet, flow-controlling gate 3 is operated in right position under spring force, signal control valve 4 is operated in left position under spring force, the fluid of load-reacting pump all enters steering swivel system, the sufficient flow of steering swivel system when effective guarantee turns to work, now hydrostatic steering system is a typical load sensitive system.When lifting operating mode, the pilot signal taking from hoisting system acts on signal control valve right-hand member, the left end of flow-controlling gate simultaneously is also subject to the control of this pressure signal, flow-controlling gate is operated in left position, signal control valve is operated in right position, the fluid of load-reacting pump all collaborates in the middle of hoisting system, now because signal control valve is operated in right position, the pressure of load-reacting pumping hole causes the right-hand member of pump LS valve through the right position of signal control valve, LS valve is operated in right position, steering pump is now in max.cap., is equivalent to a fix-displacement pump.When lifting operating mode, the fluid of load-reacting pump all collaborates in hoisting system, can reduce lifting capacity of pump on the one hand, on the other hand the flow of load-reacting pump is utilized effectively, reaches energy-conservation object to a certain extent.The fluid of shuttle valve takes from lifting pilot control oil circuit, as long as hoisting system is in the operating mode of lifting or decline, shuttle valve all will obtain pressure oil, and then allow flow-controlling gate and signal control valve be operated in left position and right position respectively, make the fluid of load-reacting pump collaborate in hoisting system; When hoisting system is in meta or floating operating mode, the control presssure of shuttle valve communicates with fuel tank, this insufficient pressure is to overcome the spring force of flow-controlling gate, under spring force, flow-controlling gate is operated in right position, the fluid of load-reacting pump all flows into steering swivel system, ensures that steering swivel system flow is enough.
In the present embodiment, hydrostatic steering system adopts load-reacting system, and ensure that the flow entering hydrostatic steering system is only relevant with the opening of deflector, have nothing to do with extraneous load, load-sensitive technology is very ripe; When comfortable property, flow-controlling gate is operated in right position, and signal control valve is operated in left position, and the LS valve that LS signal guides to load-reacting pump from load end controls right-hand member, realizes the Ioad-sensing control of load-reacting pump.In lifting operating mode, flow-controlling gate is operated in left position, signal control valve is operated in right position, steering swivel system LS signal connects fuel tank, load-reacting pump pump intake pressure signal directly controls steering pump LS valve right-hand member, controllable capacity pump is become a fix-displacement pump, make load-reacting pump collaborate in the middle of hoisting system with max.cap., capacity of pump is fully used.By can realize the switching of load-reacting pumping function easily to the control of signal control valve, effectively expand the using function of controllable capacity pump.Load-reacting capacity of pump is chosen can be relatively large, and lifting capacity of pump can be chosen relatively little, effectively reduces degradation of energy during lifting valve meta.

Claims (1)

1. quarry tipper determines a variable delivery hydraulic system, comprises hydraulic lifting system and hydrostatic steering system;
Described hydraulic lifting system comprises elevating ram, hydraulic control lifting valve, priority valve, balance cock, lifting pump, described lifting pump are connected with the P mouth of hydraulic control lifting valve, priority valve is connected with the control port of hydraulic control lifting valve, the A mouth of described hydraulic control lifting valve is connected with elevating ram with B mouth, and described balance cock is connected between hydraulic control lifting valve and elevating ram;
Described hydrostatic steering system comprises steering cylinder, load-reacting pump, deflector, and described deflector is connected with described steering cylinder;
Characterized by further comprising signal control valve, shuttle valve, flow-controlling gate, check valve, the oil circuit control of described priority valve is communicated with the left end signal port of described flow-controlling gate with the P1 signal port of signal control valve through shuttle valve simultaneously;
The left position oil outlet of described flow-controlling gate is through the P mouth unilaterally connected of check valve to hydraulic control lifting valve, the right position oil outlet of described flow-controlling gate is connected with the P mouth of described deflector, and the oil inlet of described flow-controlling gate is connected with the pumping hole of described load-reacting pump;
The pumping hole of described load-reacting pump is connected with the P2 mouth of described signal control valve, and the P3 mouth of described signal control valve is connected with the LS valve in described load-reacting pump, and the LS mouth of described signal control valve is connected with the LS mouth of described deflector.
CN201310497282.6A 2013-10-22 2013-10-22 Quarry tipper determines variable delivery hydraulic system Active CN103522929B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201310497282.6A CN103522929B (en) 2013-10-22 2013-10-22 Quarry tipper determines variable delivery hydraulic system

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201310497282.6A CN103522929B (en) 2013-10-22 2013-10-22 Quarry tipper determines variable delivery hydraulic system

Publications (2)

Publication Number Publication Date
CN103522929A CN103522929A (en) 2014-01-22
CN103522929B true CN103522929B (en) 2016-04-06

Family

ID=49925418

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201310497282.6A Active CN103522929B (en) 2013-10-22 2013-10-22 Quarry tipper determines variable delivery hydraulic system

Country Status (1)

Country Link
CN (1) CN103522929B (en)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104828135B (en) * 2014-12-22 2017-06-06 北汽福田汽车股份有限公司 Hydraulic control system and the quarry tipper with it
CN105984491B (en) * 2015-02-04 2019-04-02 卡特彼勒(青州)有限公司 Hydraulic system and machine for machine
CN104709151A (en) * 2015-03-19 2015-06-17 句容五星机械制造有限公司 Detection method for lifting difficulty and lifting slowness with displacement fault of compartment of tilting cart
CN106321537B (en) * 2015-06-19 2020-11-13 博世力士乐(北京)液压有限公司 Hydraulic control system and corresponding mobile working device
CN105134695B (en) * 2015-08-26 2017-10-03 徐工集团工程机械股份有限公司科技分公司 A kind of automatically controlled opening and closing core hydraulic system and engineering machinery
CN105298971B (en) 2015-11-13 2018-04-13 上海华测导航技术股份有限公司 The hydraulic control valve group of agricultural machinery automatic steering system
CN106274605B (en) * 2016-08-18 2019-02-19 广西柳工机械股份有限公司 Quarry tipper load-sensitive combining hydraulic system
CN106364552B (en) * 2016-08-30 2018-11-06 广州电力机车有限公司 A kind of six wheel drive self-unloading vehicle hydraulic systems
CN107269633B (en) * 2017-08-09 2019-11-01 中铁四局集团有限公司 A kind of open type variable pump systems of integrated pressure-keeping functions and load-sensitive function
CN107724454B (en) * 2017-11-10 2019-09-17 广西柳工机械股份有限公司 Loading machine determines variable delivery hydraulic system
CN109052255B (en) * 2018-08-28 2019-12-03 江苏建筑职业技术学院 Aerial work platform oscillation system and swing control method
CN112660007B (en) * 2020-12-30 2021-08-10 河南科技大学 Energy-saving heavy dump truck with lifting protection and hydraulic control system thereof

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4517800A (en) * 1980-10-31 1985-05-21 Kabushiki Kaisha Komatsu Seisakusho Hydraulic control system for off-highway self-propelled work machines
CN201800764U (en) * 2010-08-18 2011-04-20 内蒙古北方重型汽车股份有限公司 Steering control system of heavy duty mine dump truck
CN102363432A (en) * 2011-06-30 2012-02-29 徐工集团工程机械股份有限公司江苏徐州工程机械研究院 Steering control device for electric wheel mining dump trucks
CN202399983U (en) * 2011-12-26 2012-08-29 北京中冀福庆专用车有限公司 Control system for power source shared by hydraulic top cover and container lifting of dreg transporting truck
CN203063751U (en) * 2012-11-07 2013-07-17 秦皇岛天业通联重工股份有限公司 Mining dump truck and hydraulic pressure lifting controlling system of mining dump truck
CN203111003U (en) * 2012-12-29 2013-08-07 徐工集团工程机械股份有限公司江苏徐州工程机械研究院 Converging oil supply system of hinged type dumper lifting hydraulic system

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4517800A (en) * 1980-10-31 1985-05-21 Kabushiki Kaisha Komatsu Seisakusho Hydraulic control system for off-highway self-propelled work machines
CN201800764U (en) * 2010-08-18 2011-04-20 内蒙古北方重型汽车股份有限公司 Steering control system of heavy duty mine dump truck
CN102363432A (en) * 2011-06-30 2012-02-29 徐工集团工程机械股份有限公司江苏徐州工程机械研究院 Steering control device for electric wheel mining dump trucks
CN202399983U (en) * 2011-12-26 2012-08-29 北京中冀福庆专用车有限公司 Control system for power source shared by hydraulic top cover and container lifting of dreg transporting truck
CN203063751U (en) * 2012-11-07 2013-07-17 秦皇岛天业通联重工股份有限公司 Mining dump truck and hydraulic pressure lifting controlling system of mining dump truck
CN203111003U (en) * 2012-12-29 2013-08-07 徐工集团工程机械股份有限公司江苏徐州工程机械研究院 Converging oil supply system of hinged type dumper lifting hydraulic system

Also Published As

Publication number Publication date
CN103522929A (en) 2014-01-22

Similar Documents

Publication Publication Date Title
CN103522929B (en) Quarry tipper determines variable delivery hydraulic system
CN102874704B (en) Hydraulic system, hoisting mechanism and engineering machinery
CN102134047B (en) Energy-saving hydraulic system of electric forklift
CN102536932A (en) Compression refuse collector and hydraulic system thereof
CN103523079B (en) Quarry tipper hydraulic efficiency pressure system
CN202402380U (en) Compression garbage truck and hydraulic system thereof
CN201125403Y (en) Loading apparatus load sensing energy-saving hydraulic system
CN104405006B (en) Loading machine semi-variety hydraulic system
CN110499794B (en) Heavy-load movable arm potential energy recycling system of large hydraulic excavator and control method thereof
CN204491707U (en) Loader semi-variety hydraulic system
CN204432488U (en) A kind of lifting mode framework transport vehicle
CN103775396B (en) A kind of precast concrete piler and energy-recuperation system thereof
CN102384113B (en) Oil supply and energy-saving device for mining dump truck
CN107061430A (en) The hoisting system of minus flow hydraulic circuit control
CN100516558C (en) Rotatary brake valve
CN102059973B (en) Lifting hydraulic integrated system for large-tonnage electric-wheel mining dumper
CN202012522U (en) Balanced valve bank for lifting system of mining dumper
CN201962039U (en) Energy-saving hydraulic system of electronic forklift
CN203063751U (en) Mining dump truck and hydraulic pressure lifting controlling system of mining dump truck
CN203114763U (en) Traveling reversing valve of open-type hydraulic transmission system in telescopic arm forklift truck
CN104029721A (en) Hydraulic steering device for loader
CN203582302U (en) Control valve bank, hydraulic control system and truck crane
CN207513953U (en) Quarry tipper fixed dilivery hydraulic system
CN103591062B (en) Loading machine quantitative pump pressure compensates and automatic deloading hydraulic system
CN201970903U (en) Lifting hydraulic integration system of a large-ton electric-wheel mine dump truck

Legal Events

Date Code Title Description
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