CN103085865A - Load sensitive turning hydraulic system of loading machine - Google Patents

Load sensitive turning hydraulic system of loading machine Download PDF

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Publication number
CN103085865A
CN103085865A CN2012105026244A CN201210502624A CN103085865A CN 103085865 A CN103085865 A CN 103085865A CN 2012105026244 A CN2012105026244 A CN 2012105026244A CN 201210502624 A CN201210502624 A CN 201210502624A CN 103085865 A CN103085865 A CN 103085865A
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China
Prior art keywords
valve
load
hydraulic
pressure
flux amplification
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CN2012105026244A
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Chinese (zh)
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CN103085865B (en
Inventor
初长祥
李开亮
梁振国
吴军
王允
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Guangxi Liugong Machinery Co Ltd
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Guangxi Liugong Machinery Co Ltd
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Publication of CN103085865A publication Critical patent/CN103085865A/en
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Abstract

The invention discloses a load sensitive turning hydraulic system of a loading machine. The load sensitive turning hydraulic system is characterized in that a load sensitive constant pressure variable plunger pump supplies working oil pressure to a flow enlarging valve and a turning machine; a load feedback pressure signal of the flow enlarging valve controls an LS control valve of a first load sensitive constant pressure variable plunger pump; an oil port L of the turning machine is communicated to the right end of a main valve core L of the flow enlarging valve; an oil port R is communicated to the right end of a main valve core R of the flow enlarging valve; the load sensitive constant pressure variable plunger pump supplies the working oil pressure to a load sensitive turning valve and a pilot valve; and four control ends of the pilot valve are respectively communicated with the load sensitive turning valve. The load sensitive turning hydraulic system of the loading machine also comprises a turning system and convergence systems of other working systems. The load sensitive turning hydraulic system of the loading machine has the advantages that the variable displacement function of the load sensitive constant pressure variable plunger pump is fully used, so that the displacement of a turning pump is increased, and the turning performance is improved; and fuel is saved, and the working efficiency is improved. The flow enlarging valve is simple in structure, and domestication is also realized; the cost of the flow enlarging valve is lower than that of an imported flow enlarging valve; and batch production can be realized.

Description

The loader load sensitization steering hydraulic system
Technical field
Of the present inventionly relate to a kind of steering hydraulic system for construction machinery and equipment, be specially adapted to the load-sensitive steering hydraulic system of loader.
Background technology
Common loader is comprised of steering swivel system and work system, steering swivel system and work system or independence, or interflow.In quantitative system, in order both to meet the requirement turn to performance when engine idle and the high speed, meet again the requirement of minimizing steering swivel system degradation of energy simultaneously, steering pump is generally all selected not quite, all little or equal than working barrel in converging system.As take into account 2 top requirements, and the turning efficiency meeting variation of steering swivel system when low speed, subject matter is slow for reaction, and turning velocity is slow, causes turning to efficiency low, and driver's labour intensity is large.This has just affected performance and the investment repayment of whole loader.
Summary of the invention
Purpose of the present invention just be to provide a kind of make turning efficiency engine idle during with high speed performance consistent, and turning velocity (from left-limit to the limit on the right-right-hand limit angle) left and right that can remain on 3 seconds, corresponding bearing circle speed is in 3 circles left and right.The traveling comfort that this has improved the driver operation loader, also improved the load-sensitive steering hydraulic system of the operating efficiency loader use of loader.
Solution of the present invention is such:
The present invention includes:
Steering swivel system: described steering swivel system is mainly by the first load-sensitive constant pressure variable plunger pump, form with flux amplification valve, deflector, the steering cylinder of pressure-gradient control valve function and load signal feedback function, described load-sensitive constant pressure variable plunger pump provides operating oil pressure to flux amplification valve, deflector, and the load feedback pressure signal of flux amplification valve is controlled the LS control cock of the first load-sensitive constant pressure variable plunger pump; Described deflector L hydraulic fluid port is communicated with flux amplification valve main valve plug valve L right-hand member, and the R hydraulic fluid port is communicated with flux amplification valve main valve plug valve R left end;
The converging system of steering swivel system and other work system: described converging system comprises the EF mouth of flux amplification valve and Hydraulic Elements are controlled at the interflow that is connected with flux amplification valve EF mouth, the Hydraulic Elements that described interflow is controlled be used for guaranteeing the hydraulic oil of the EF mouth outflow of flux amplification valve can only one direction to other work system fuel feeding.
System comprises more specifically:
Pressure-gradient control valve in described flux amplification valve is static pressure-gradient control valve, and the open and close signal of pressure-gradient control valve feeds back after by flux amplification valve main valve plug valve.
Advantage of the present invention is to take full advantage of the function that the load-sensitive Variable plunger pump becomes discharge capacity, increases and turns to capacity of pump, reaches the lifting of turning efficiency, and the while is capable of saving fuel oil and raising operating efficiency also.The flux amplification valve adopted is simple in structure, and has also realized production domesticization, and cost is lower than the flux amplification valve that adopts import, can realize producing in enormous quantities.
The accompanying drawing explanation
Accompanying drawing is embodiments of the invention.
Accompanying drawing 1 is steering swivel system hydraulic schematic diagram of the present invention.
The specific embodiment
Below in conjunction with accompanying drawing, the present invention is described in detail.
The present invention includes:
Steering swivel system: described steering swivel system mainly is comprised of the deflector 4 of hydraulic reservoir 1, the first load-sensitive constant pressure variable plunger pump 2, reducing valve 3, small displacement, flux amplification valve 5, left steering oil cylinder 6, right steering oil cylinder 7, check valve 8 and shuttle valve 9 with pressure-gradient control valve function and load signal feedback function, described load-sensitive constant pressure variable plunger pump 2 provides operating oil pressure to flux amplification valve 5, deflector 4, the LS control cock of the responsive constant pressure variable plunger pump 2 of the load feedback pressure signal control overhead of flux amplification valve 5; The L hydraulic fluid port of described deflector 4 is communicated with the main valve plug valve L right-hand member of flux amplification valve 5, and the R hydraulic fluid port is communicated with the main valve plug valve R right-hand member of flux amplification valve 5;
The converging system of steering swivel system and other work system: the interflow control Hydraulic Elements that described converging system comprises the EF mouth of flux amplification valve and is connected with flux amplification valve EF mouth, the hydraulic oil that the Hydraulic Elements that described interflow is controlled flow out for the EF mouth that guarantees flux amplification valve can only one direction to other work system fuel feeding, in the present embodiment, it is to adopt check valve 8 that Hydraulic Elements are controlled at interflow.
The loader hydraulic system of working of other work system of the present embodiment as shown in the accompanying drawing Block Diagrams.
Pressure-gradient control valve in described flux amplification valve 5 is static pressure-gradient control valve, and the open and close signal of pressure-gradient control valve feeds back after by flux amplification valve main valve plug valve.
The present embodiment is that the deflector that adopts the 125cc/r discharge capacity, the first load-sensitive Variable plunger pump and the flux amplification valve with the pressure-gradient control valve function 5 of 100cc/r form.
The LS signal of the first load-sensitive Variable plunger pump 2 of 100cc/r is by flux amplification valve 5 feedbacks with the pressure-gradient control valve function, with the pressure-gradient control valve in the flux amplification valve 5 of pressure-gradient control valve function, it is static pressure-gradient control valve, the open and close signal of pressure-gradient control valve feeds back after by flux amplification valve main valve plug valve, the main valve plug of flux amplification valve is controlled by deflector 4, and deflector 4 is passed through spline joint with bearing circle.
When bearing circle turns left, the L hydraulic fluid port of deflector 4 is fuel-displaced, and towards flux amplification valve main valve plug valve L right-hand member, flux amplification valve 5 main valve plug valves move left under the oil pressure effect of right-hand member, flux amplification valve main valve plug valve feeds back a signal to the spring cavity end of pressure-gradient control valve and the LS mouth of pump, the pressure-gradient control valve spool moves, the LS signal control valve liquid of the first load-sensitive Variable plunger pump 2 moves the discharge capacity of controlling the first load-sensitive Variable plunger pump 2 simultaneously, make the discharge capacity of the first load-sensitive Variable plunger pump 1 proportional with the speed turned to, the discharge capacity of the first load-sensitive Variable plunger pump 2 increases, flow is raised to and turns to the flow needed from 0L/min, the P that is pump by path of oil pumpmouthful to the P1 mouth of pressure-gradient control valve, then by the CF mouth of pressure-gradient control valve the P2 mouth to the Flow amplification spool, the last B mouth that is flow to steering cylinder by the B mouth of Flow amplification spool, flow back to fuel tank by the A mouth of oil cylinder, the T mouth of Flow amplification spool, realized left steering.
When bearing circle is turned right, the R hydraulic fluid port of deflector 4 is fuel-displaced, and towards flux amplification valve main valve plug valve R left end, flux amplification valve 5 main valve plug valves move right under the oil pressure effect of left end, flux amplification valve main valve plug valve feeds back a signal to the spring cavity end of pressure-gradient control valve and the LS mouth of pump, the pressure-gradient control valve spool moves, the LS signal control valve liquid of the first load-sensitive Variable plunger pump 2 moves the discharge capacity of controlling the first load-sensitive Variable plunger pump 2 simultaneously, make the discharge capacity of the first load-sensitive Variable plunger pump 1 proportional with the speed turned to, the discharge capacity of the first load-sensitive Variable plunger pump 2 increases, flow is raised to and turns to the flow needed from 0L/min, the P that is pump by path of oil pumpmouthful to the P1 mouth of pressure-gradient control valve, then by the CF mouth of pressure-gradient control valve the P2 mouth to the Flow amplification spool, the last A mouth that is flow to steering cylinder by the A mouth of Flow amplification spool, flow back to fuel tank by the B mouth of oil cylinder, the T mouth of Flow amplification spool, realized right steering.
When bearing circle does not turn to, the L of deflector 4, R hydraulic fluid port do not have oil to flow out, there is no the effect of pressure oil at the two ends of flux amplification valve 5 main valve plug valves yet, flux amplification valve 5 main valve plug valves are in meta, the LS signal port of flux amplification valve is connected with fuel tank 1, the spring cavity without pressure feedback to pressure-gradient control valve, and the pressure-gradient control valve spool is in left function position, the LS signal port of pump does not have pressure yet simultaneously, the discharge capacity of the first load-sensitive Variable plunger pump 2 is 0, and flow is also 0L/min, makes hydraulic circuit P pumpp1 mouth, the CF mouth of pressure-gradient control valve, the P2 mouth of Flow amplification spool, the A of Flow amplification spool, B mouth, the A of oil cylinder, B mouth to pressure-gradient control valve do not have oil to pass through, and steering hardware is in state of kinematic motion not.
When two hydraulic efficiency pressure systems of need are collaborated work, the hydraulic oil that the EF mouth of flux amplification valve provides passes through check valve 8 one directions to the hydraulic system of working fuel feeding.

Claims (2)

1. the load-sensitive steering hydraulic system that a loader is used is characterized in that comprising:
Steering swivel system: described steering swivel system is mainly by the first load-sensitive constant pressure variable plunger pump, form with flux amplification valve, deflector, the steering cylinder of pressure-gradient control valve function and load signal feedback function, described load-sensitive constant pressure variable plunger pump provides operating oil pressure to flux amplification valve, deflector, and the load feedback pressure signal of flux amplification valve is controlled the LS control cock of the first load-sensitive constant pressure variable plunger pump; Described deflector L hydraulic fluid port is communicated with flux amplification valve main valve plug valve L right-hand member, and the R hydraulic fluid port is communicated with flux amplification valve main valve plug valve R right-hand member;
The converging system of steering swivel system and other work system: described converging system comprises the EF mouth of flux amplification valve and Hydraulic Elements are controlled at the interflow that is connected with flux amplification valve EF mouth, the Hydraulic Elements that described interflow is controlled be used for guaranteeing the hydraulic oil of the EF mouth outflow of flux amplification valve can only one direction to other work system fuel feeding.
2. the load-sensitive steering hydraulic system that loader according to claim 1 is used, is characterized in that the pressure-gradient control valve in described flux amplification valve is static pressure-gradient control valve, and the open and close signal of pressure-gradient control valve feeds back after by flux amplification valve main valve plug valve.
CN201210502624.4A 2012-11-30 2012-11-30 Loader load sensitization steering hydraulic system Active CN103085865B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201210502624.4A CN103085865B (en) 2012-11-30 2012-11-30 Loader load sensitization steering hydraulic system

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Application Number Priority Date Filing Date Title
CN201210502624.4A CN103085865B (en) 2012-11-30 2012-11-30 Loader load sensitization steering hydraulic system

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CN103085865A true CN103085865A (en) 2013-05-08
CN103085865B CN103085865B (en) 2016-05-25

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103359594A (en) * 2013-07-30 2013-10-23 西安煤矿机械有限公司 Cage locking swing deck
CN103696997A (en) * 2013-12-18 2014-04-02 柳州柳工挖掘机有限公司 Hydraulic system with priority function
CN104029721A (en) * 2014-01-23 2014-09-10 广西柳工机械股份有限公司 Hydraulic steering device for loader
CN104192201A (en) * 2014-08-18 2014-12-10 柳州柳工液压件有限公司 Hydraulic steering control valve and hydraulic steering control system
CN104481948A (en) * 2014-10-28 2015-04-01 广西柳工机械股份有限公司 Stabilized pressure flow control valve and load sensitive analog valve
CN105201944A (en) * 2015-09-25 2015-12-30 广西柳工机械股份有限公司 Flow enlarging valve and hydraulic steering system
CN105387032A (en) * 2015-12-22 2016-03-09 江苏师范大学 Liquid energy feedback energy-saving device for load-sensitive proportion control system
CN106762928A (en) * 2017-01-17 2017-05-31 徐工集团工程机械有限公司 Automobile hydraulic system and the engineering truck with it

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2589425Y (en) * 2002-10-29 2003-12-03 柯坚 Load sensitive confluent hydraulic system for loader
CN201357777Y (en) * 2009-02-24 2009-12-09 宝山钢铁股份有限公司 Two-way hydraulic system of transporting rack car
CN201581431U (en) * 2009-12-18 2010-09-15 广西柳工机械股份有限公司 Loader load sensitization hydraulic device
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
KR20120054680A (en) * 2010-11-20 2012-05-31 두산산업차량 주식회사 Steering load sensing system for a heavy equipment

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2589425Y (en) * 2002-10-29 2003-12-03 柯坚 Load sensitive confluent hydraulic system for loader
CN201357777Y (en) * 2009-02-24 2009-12-09 宝山钢铁股份有限公司 Two-way hydraulic system of transporting rack car
CN201581431U (en) * 2009-12-18 2010-09-15 广西柳工机械股份有限公司 Loader load sensitization hydraulic device
KR20120054680A (en) * 2010-11-20 2012-05-31 두산산업차량 주식회사 Steering load sensing system for a heavy equipment
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

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103359594B (en) * 2013-07-30 2016-01-20 西安煤矿机械有限公司 A kind of lock tank cage chair
CN103359594A (en) * 2013-07-30 2013-10-23 西安煤矿机械有限公司 Cage locking swing deck
CN103696997B (en) * 2013-12-18 2015-12-30 柳州柳工挖掘机有限公司 There is the hydraulic system of priority function
CN103696997A (en) * 2013-12-18 2014-04-02 柳州柳工挖掘机有限公司 Hydraulic system with priority function
CN104029721A (en) * 2014-01-23 2014-09-10 广西柳工机械股份有限公司 Hydraulic steering device for loader
CN104029721B (en) * 2014-01-23 2016-09-07 广西柳工机械股份有限公司 Loader hydraulic transfer
CN104192201A (en) * 2014-08-18 2014-12-10 柳州柳工液压件有限公司 Hydraulic steering control valve and hydraulic steering control system
CN104192201B (en) * 2014-08-18 2016-06-29 柳州柳工液压件有限公司 Hydraulic steering control valve and hydraulic steering system
CN104481948B (en) * 2014-10-28 2017-01-11 广西柳工机械股份有限公司 Stabilized pressure flow control valve and load sensitive analog valve
CN104481948A (en) * 2014-10-28 2015-04-01 广西柳工机械股份有限公司 Stabilized pressure flow control valve and load sensitive analog valve
CN105201944A (en) * 2015-09-25 2015-12-30 广西柳工机械股份有限公司 Flow enlarging valve and hydraulic steering system
CN105387032A (en) * 2015-12-22 2016-03-09 江苏师范大学 Liquid energy feedback energy-saving device for load-sensitive proportion control system
CN105387032B (en) * 2015-12-22 2017-11-03 江苏师范大学 A kind of liquid energy feedback energy-saving device for load-sensitive ratio control system
CN106762928A (en) * 2017-01-17 2017-05-31 徐工集团工程机械有限公司 Automobile hydraulic system and the engineering truck with it
CN106762928B (en) * 2017-01-17 2018-10-16 徐工集团工程机械有限公司 Automobile hydraulic system and engineering truck with it

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