CN201581431U - Loader load sensitization hydraulic device - Google Patents

Loader load sensitization hydraulic device Download PDF

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Publication number
CN201581431U
CN201581431U CN2009203178157U CN200920317815U CN201581431U CN 201581431 U CN201581431 U CN 201581431U CN 2009203178157 U CN2009203178157 U CN 2009203178157U CN 200920317815 U CN200920317815 U CN 200920317815U CN 201581431 U CN201581431 U CN 201581431U
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CN
China
Prior art keywords
valve
load
mouth
work
hole
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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.)
Expired - Lifetime
Application number
CN2009203178157U
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Chinese (zh)
Inventor
梁振国
李开亮
黄建兵
谢文菊
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
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Guangxi Liugong Machinery Co Ltd
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Priority to CN2009203178157U priority Critical patent/CN201581431U/en
Application granted granted Critical
Publication of CN201581431U publication Critical patent/CN201581431U/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Abstract

A loader load sensitization hydraulic device is characterized in that a steering system adopts a load sensitization constant pressure variable-volume pump, a work system is provided with a direction change-over valve with an opened middle position, a control valve controls the make-break conversion between an LS oil port and a P oil port of the load sensitization constant pressure variable-volume pump and the LS2 oil port of a converter and controls the conversion of an LS1 oil port of a pilot valve and an LS2 oil port of a steering gear, a liquid control hole of the control valve is communicated with a shuttle valve, and a Pa1 hole, a Pa2 hole, a Pb1 hole and a Pb2 hole of the shuttle valve are respectively communicated with a Pa1 hole, a Pa2 hole, a Pb1 hole and a Pb2 hole of the pilot valve. The loader load sensitization hydraulic device has the advantages that a work system uses the direction change-over valve with the opened middle position to achieve the interflow with the load sensitization constant pressure variable-volume steering system, and no throttle loss and overflow loss are caused when the device is interpedently steered or a steering device and a working device simultaneously work, and the device is simpler than a work system which uses a load sensitization direction change-over valve with a closed middle position and a load sensitization constant pressure variable-volume system, and the cost is low.

Description

Loader load-sensitive hydraulic means
Technical field
The utility model relates to a kind of loader load-sensitive hydraulic means that is used for loader.
Background technology
The hydraulic system that present engineering machinery loader is used is made up of steering and work system, all is quantitative system, and steering exists restriction loss and spill losses, and there is spill losses in work system.
The utility model content
The purpose of this utility model just provides the interflow of an a kind of load-sensitive constant pressure variable displacement pump and a constant displacement pump, it when realization turns to load-sensitive constant-pressure variable system, it during work the constant-pressure variable system, the restriction loss and the spill losses of steering have been solved, solved the spill losses of work system, reach energy-conservation and reduction hydraulic system temperature, improve the effect of whole aircraft reliability; Can work as when turning to separately, steering is a load-sensitive constant-pressure variable system that closes meta, does not collaborate with work system; When work system was worked, Variable plunger pump had only the constant voltage function, steering and work system interflow, and steering still is the loader load-sensitive hydraulic means of load-sensitive constant-pressure variable system.
Solution of the present utility model is such: have control valve, shuttle valve, pilot valve and combination valve, described steering is to adopt the load-sensitive constant pressure variable displacement pump, and described work system has out the direction reversal valve of meta; Conversion between the LS2 hydraulic fluid port of the break-make conversion between the LS2 hydraulic fluid port of described control valve control load-sensitive constant pressure variable displacement pump LS hydraulic fluid port, P hydraulic fluid port and steering gear and the LS1 hydraulic fluid port of pressure-gradient control valve and steering gear; The hydraulic control mouth of described control valve is communicated to shuttle valve, and the Pa1 mouth of described shuttle valve, Pa2 mouth, Pb1 mouth, Pb2 mouth are communicated with Pa1 mouth, Pa2 mouth, Pb1 mouth, the Pb2 of pilot valve respectively; The P4 mouth of described pilot valve links to each other with the hydraulic fluid port of combination valve with the T4 mouth.After adopting technique scheme, when turning to separately, steering is a load-sensitive constant-pressure variable system that closes meta, does not collaborate with work system; When work system was worked, Variable plunger pump had only the constant voltage function, steering and work system interflow, and steering still is a load-sensitive constant-pressure variable system, work system is the constant-pressure variable system of a two-stage.
The utility model has the advantages that work system has realized interflow with load-sensitive constant-pressure variable steering with the direction reversal valve of opening meta, and when turning to separately or turn to when working simultaneously, all do not have restriction loss and spill losses with equipment; Reaching under the situation of identical function, simpler with the system of load-sensitive direction reversal valve that closes meta and load-sensitive constant-pressure variable than work system, cost is low.
Description of drawings
Accompanying drawing is embodiment of the present utility model.
Accompanying drawing 1 is a structural representation of the present utility model.
The specific embodiment
Present embodiment includes steering gear 1, pressure-gradient control valve 2, Variable plunger pump 3, turns to oil cylinder 4, shuttle valve 5, control valve 6, drive meta direction reversal valve 7, unloader 8, gear pump 9, hydraulic pressure radiator 10, oil return filter 11, counterbalance valve 12, boom cylinder 13, rotary ink tank 14, one way valve 15, pilot valve 16, combination valve 17, constant voltage stop valve 18, load-sensitive valve 19.
This device includes steering and work system, have control valve 6, shuttle valve 5, pilot valve 16 and combination valve 17, described steering is to adopt the load-sensitive constant pressure variable displacement pump, the load-sensitive constant pressure variable displacement pump includes Variable plunger pump 3, constant voltage stop valve 18 and load-sensitive valve 19, and described work system has out the direction reversal valve 7 of meta; Conversion between the LS2 hydraulic fluid port of the break-make conversion between the LS2 hydraulic fluid port of described control valve 6 control load-sensitive constant pressure variable displacement pump LS hydraulic fluid ports, P hydraulic fluid port and steering gear 1 and the LS1 hydraulic fluid port of pressure-gradient control valve 2 and steering gear 1; The hydraulic control mouth of described control valve 6 is communicated to shuttle valve 5, and the Pa1 mouth of described shuttle valve 5, Pa2 mouth, Pb1 mouth, Pb2 mouth are communicated with Pa1 mouth, Pa2 mouth, Pb1 mouth, the Pb2 of pilot valve 16 respectively; The P4 mouth of described pilot valve 16 links to each other with the hydraulic fluid port of T4 mouth with combination valve 17; The EF hydraulic fluid port of pressure-gradient control valve 2 is communicated with the oil-out of unloader 8.
Operating principle of the present utility model is:
1, when the pilot valve 16 of work system is not worked, the pressure of the hydraulic fluid port 5 of control valve 6 is 0MPa, and control valve 6 is in left function position, and the LS mouth of Variable plunger pump 3 and the LS2 mouth of steering gear 1 communicate, therefore, the load-sensitive valve 19 of Variable plunger pump 3 and constant voltage stop valve 18 all work; In case during pilot valve 16 work of work system, the pressure of the hydraulic fluid port 5 of control valve 6 is 2.5MPa, and control valve 6 is in right function position, and the LS mouth of Variable plunger pump 3 and the P mouth of Variable plunger pump 3 communicate, the load-sensitive valve 19 of Variable plunger pump 3 is inoperative, has only constant voltage stop valve 18 to work.
The LS1 mouth of pressure-gradient control valve 2 is cut off, and pressure-gradient control valve 2 all is in left function position, and steering is closed meta, and with the work system interflow, steering is not a load-sensitive constant-pressure variable system.
When 2, the pilot valve 16 of work system is worked, the pressure of the hydraulic fluid port 5 of control valve 6 is 2.5MPa, control valve 6 is in right function position, the LS1 mouth of pressure-gradient control valve 2 and the LS2 mouth of steering gear 1 are connected, the P mouth of Variable plunger pump 3 and the LS mouth of Variable plunger pump 3 are connected, the load-sensitive valve 19 of Variable plunger pump 3 is inoperative, and Variable plunger pump 3 has only the constant-pressure variable function, and work system is the constant-pressure variable system.
3, when the pilot valve 16 of steering gear 1 and work system is worked, the pressure of the hydraulic fluid port 5 of control valve 6 is 2.5MPa, control valve 6 is in right function position, the LS1 mouth of pressure-gradient control valve 2 and the LS2 mouth of steering gear 1 are connected, the P mouth of Variable plunger pump 3 and the LS mouth of Variable plunger pump 3 are connected, Variable plunger pump 3 has only the constant voltage function, and pressure-gradient control valve 2 is a load-sensitive constant-pressure variable system with the steering that steering gear 1 is formed, and work system is the constant-pressure variable system.

Claims (1)

1. loader load-sensitive hydraulic means, steering and work system are arranged, it is characterized in that having control valve (6), shuttle valve (5), pilot valve (16) and combination valve (17), described steering is to adopt the load-sensitive constant pressure variable displacement pump, and described work system has out the direction reversal valve (7) of meta; Conversion between the LS2 hydraulic fluid port of the break-make conversion between the LS2 hydraulic fluid port of described control valve (6) control load-sensitive constant pressure variable displacement pump LS hydraulic fluid port, P hydraulic fluid port and steering gear (1) and the LS1 hydraulic fluid port of pressure-gradient control valve (2) and steering gear (1); The hydraulic control mouth of described control valve (6) is communicated to shuttle valve (5), and the Pa1 mouth of described shuttle valve (5), Pa2 mouth, Pb1 mouth, Pb2 mouth are communicated with Pa1 mouth, Pa2 mouth, Pb1 mouth, the Pb2 of pilot valve (16) respectively; The P4 mouth of described pilot valve (16) links to each other with the hydraulic fluid port of T4 mouth with combination valve (17).
CN2009203178157U 2009-12-18 2009-12-18 Loader load sensitization hydraulic device Expired - Lifetime CN201581431U (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN2009203178157U CN201581431U (en) 2009-12-18 2009-12-18 Loader load sensitization hydraulic device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN2009203178157U CN201581431U (en) 2009-12-18 2009-12-18 Loader load sensitization hydraulic device

Publications (1)

Publication Number Publication Date
CN201581431U true CN201581431U (en) 2010-09-15

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Family Applications (1)

Application Number Title Priority Date Filing Date
CN2009203178157U Expired - Lifetime CN201581431U (en) 2009-12-18 2009-12-18 Loader load sensitization hydraulic device

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CN (1) CN201581431U (en)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102251996A (en) * 2011-07-05 2011-11-23 天津柳工机械有限公司 Engineering mechanical load sensing hydraulic system
CN102296665A (en) * 2011-06-23 2011-12-28 上海三一重机有限公司 Excavator hydraulic system carrying load sensing main valve and positive flow pump
CN102653948A (en) * 2011-03-03 2012-09-05 北汽福田汽车股份有限公司 Hydraulic system of loader
CN102927088A (en) * 2012-11-16 2013-02-13 无锡汇虹机械制造有限公司 Pressure control method of hydraulic pump system
CN103085865A (en) * 2012-11-30 2013-05-08 广西柳工机械股份有限公司 Load sensitive turning hydraulic system of loading machine
CN103452961A (en) * 2012-05-29 2013-12-18 罗伯特·博世有限公司 Open central control unit with constant and regulating pump
CN103807240A (en) * 2012-11-14 2014-05-21 柳州柳工挖掘机有限公司 Priority system and priority device on pilot hydraulic control oil circuit
CN104015798A (en) * 2014-01-09 2014-09-03 广西柳工机械股份有限公司 Hydraulic steering system for engineering machinery
CN104061197A (en) * 2014-06-05 2014-09-24 安徽博一流体传动股份有限公司 Hydraulic system for loading machine
CN104061196A (en) * 2014-06-05 2014-09-24 安徽博一流体传动股份有限公司 Novel hydraulic system for loader
CN105952700A (en) * 2016-06-29 2016-09-21 徐工集团工程机械股份有限公司科技分公司 Loader variable multi-stage power control module and hydraulic system
CN106321537A (en) * 2015-06-19 2017-01-11 博世力士乐(北京)液压有限公司 Hydraulic control system and corresponding movable working equipment
CN106836363A (en) * 2016-12-30 2017-06-13 山东临工工程机械有限公司 Loader hydraulic system
CN107882798A (en) * 2017-11-10 2018-04-06 广西柳工机械股份有限公司 Load simulation valve and loading machine variable system

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102653948A (en) * 2011-03-03 2012-09-05 北汽福田汽车股份有限公司 Hydraulic system of loader
CN102296665A (en) * 2011-06-23 2011-12-28 上海三一重机有限公司 Excavator hydraulic system carrying load sensing main valve and positive flow pump
CN102296665B (en) * 2011-06-23 2013-04-24 上海三一重机有限公司 Excavator hydraulic system carrying load sensing main valve and positive flow pump
CN102251996A (en) * 2011-07-05 2011-11-23 天津柳工机械有限公司 Engineering mechanical load sensing hydraulic system
CN103452961A (en) * 2012-05-29 2013-12-18 罗伯特·博世有限公司 Open central control unit with constant and regulating pump
CN103452961B (en) * 2012-05-29 2017-04-19 罗伯特·博世有限公司 Open central control unit with constant and regulating pump
CN103807240A (en) * 2012-11-14 2014-05-21 柳州柳工挖掘机有限公司 Priority system and priority device on pilot hydraulic control oil circuit
CN102927088A (en) * 2012-11-16 2013-02-13 无锡汇虹机械制造有限公司 Pressure control method of hydraulic pump system
CN103085865A (en) * 2012-11-30 2013-05-08 广西柳工机械股份有限公司 Load sensitive turning hydraulic system of loading machine
CN103085865B (en) * 2012-11-30 2016-05-25 广西柳工机械股份有限公司 Loader load sensitization steering hydraulic system
CN104015798A (en) * 2014-01-09 2014-09-03 广西柳工机械股份有限公司 Hydraulic steering system for engineering machinery
CN104061196A (en) * 2014-06-05 2014-09-24 安徽博一流体传动股份有限公司 Novel hydraulic system for loader
CN104061196B (en) * 2014-06-05 2017-05-03 安徽博一流体传动股份有限公司 Novel hydraulic system for loader
CN104061197A (en) * 2014-06-05 2014-09-24 安徽博一流体传动股份有限公司 Hydraulic system for loading machine
CN106321537A (en) * 2015-06-19 2017-01-11 博世力士乐(北京)液压有限公司 Hydraulic control system and corresponding movable working equipment
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
CN105952700A (en) * 2016-06-29 2016-09-21 徐工集团工程机械股份有限公司科技分公司 Loader variable multi-stage power control module and hydraulic system
CN106836363A (en) * 2016-12-30 2017-06-13 山东临工工程机械有限公司 Loader hydraulic system
CN107882798A (en) * 2017-11-10 2018-04-06 广西柳工机械股份有限公司 Load simulation valve and loading machine variable system

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Granted publication date: 20100915

CX01 Expiry of patent term