CN202703681U - Preferential variable steering control valve - Google Patents

Preferential variable steering control valve Download PDF

Info

Publication number
CN202703681U
CN202703681U CN 201220325185 CN201220325185U CN202703681U CN 202703681 U CN202703681 U CN 202703681U CN 201220325185 CN201220325185 CN 201220325185 CN 201220325185 U CN201220325185 U CN 201220325185U CN 202703681 U CN202703681 U CN 202703681U
Authority
CN
China
Prior art keywords
oil duct
valve
steering
oil
control
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.)
Expired - Fee Related
Application number
CN 201220325185
Other languages
Chinese (zh)
Inventor
陈莉
王新慧
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.)
ZHEJIANG HERCULES HYDRAULIC CO Ltd
Original Assignee
ZHEJIANG HERCULES HYDRAULIC 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 ZHEJIANG HERCULES HYDRAULIC CO Ltd filed Critical ZHEJIANG HERCULES HYDRAULIC CO Ltd
Priority to CN 201220325185 priority Critical patent/CN202703681U/en
Application granted granted Critical
Publication of CN202703681U publication Critical patent/CN202703681U/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Images

Landscapes

  • Servomotors (AREA)
  • Operation Control Of Excavators (AREA)

Abstract

The utility model provides a preferential variable steering control valve and belongs to the technical field of a hydraulic steering system. The preferential variable steering control valve comprises a valve body, a small end cover arranged on the valve body and the like. An oil pipe L1 is arranged on a preferential valve core, an oil pipe a2 is arranged on a magnification valve core hole, a selection valve core, a steering gear control port a connector and a steering gear control port b connector are arranged in a large end cover, a steering A port overload valve is arranged on the oil pipe A, and a steering A port one-way valve and a steering B port one-way valve are respectively arranged between the oil pipe A and the oil pipe a2 and between an oil pipe B and an oil pipe b2. A pump control load sensing variable steering hydraulic system is formed by the preferential variable steering control valve, a small displacement load sensing steering gear and a variable pump, the preferential variable steering control valve can be used for a bivariate confluence system, selects large pressure signals from the steering gear or a two-way valve, acts on the variable pump, provides necessary flow and pressure required by the system, solves the problem of optimal matching efficiency of the steering hydraulic system of a loader under any working condition, reduces unnecessary energy loss of the system, and has the effect of energy conservation.

Description

A kind of type of priority variable turns the control valve
Technical field
The utility model belongs to the hydrostatic steering system technical field of construction machinery and equipment, and the type of priority variable that is specifically related to a kind of pump control Load Sensing Steering Hydraulic System turns the control valve.
Background technology
Domestic current construction machinery and equipment such as loader, the development experience of its hydrostatic steering system servo steering system, load sensing all hydraulic pressure steering-gear, Steering system with flow amplification, although through improving several times, energy-saving effect is more and more obvious, but what generally adopt is quantitative system, because steering pump is fix-displacement pump, discharge capacity is immutable, and the loader working changes greatly, and the unnecessary flow of steering pump certainly exists high pressure or low pressurized overflow, has larger degradation of energy.And adopting on a small quantity variable system, it is the Hydraulic Elements that adopt external import basically, so that the cost of loader improves.Pump control Load Sensing Steering Hydraulic System is development tendency because of its superior energy-saving effect application on loader, it also is at present domestic demand place to the modern projects such as the loader machinery green revolution, but at present domestic also do not have more energy-conservation, more the failure-free variable that is applied to pump control Load Sensing Steering Hydraulic System turns the control valve, especially the type of priority variable turns the control valve.
The utility model content
For the above-mentioned problems in the prior art, the purpose of this utility model is to provide a kind of type of priority variable of pump control Load Sensing Steering Hydraulic System to turn the control valve.
Described a kind of type of priority variable turns the control valve, comprise valve body, be arranged on the small end cover on the valve body, amplify spool, priority spool, Ls control mouthful plug screw and large end cap, described priority spool hole is provided with oil duct L1, oil duct EF, oil duct P, oil duct P1 and oil duct L2, described amplification spool bore is provided with oil duct a2, back oil road T1, oil duct A, oil duct P1, oil duct B, back oil road T2 and oil duct b2, it is characterized in that on the described Ls control mouthful plug screw orifice plug I being set, described priority spool two ends are equipped with respectively orifice plug II and orifice plug III, in the described large end cap selection spool is set, deflector control mouthful a joint, deflector control mouthful b joint, the upper setting of described oil duct A turns to A mouth bypass control, arrange between oil duct A and the oil duct a2 and turn to A mouth check valve, arrange between oil duct B and the oil duct b2 and turn to B mouth check valve, the upper setting of oil duct B turns to B mouth bypass control, and the Ls safety valve is set on the oil duct L1.
Described a kind of type of priority variable turns the control valve, it is characterized in that hydraulic fluid port a, oil duct a1, oil duct a4, oil duct b4, oil duct b, hydraulic fluid port b are set on the described selection spool bore, and oil duct a4 communicates with oil duct a2, and oil duct b2 communicates with oil duct b4.
Described a kind of type of priority variable turns the control valve, it is characterized in that a described deflector control mouthful a joint is arranged between hydraulic fluid port a and the oil duct a1, and control port a is communicated with oil duct a1, oil duct a3.
Described a kind of type of priority variable turns the control valve, it is characterized in that a described deflector control mouthful b joint is arranged between hydraulic fluid port b and the oil duct b1, and control port b is communicated with oil duct b1, oil duct b3.
Described a kind of type of priority variable turns the control valve, it is characterized in that described oil duct EF is connected with work system multiway valve oil inlet.
Described a kind of type of priority variable turns the control valve, it is characterized in that described oil duct P1 is connected with the amplification spool bore.
Described a kind of type of priority variable turns the control valve, it is characterized in that described oil duct P is steering pump oil inlet oil duct, and described oil duct A, oil duct B are and turn to a mouthful oil duct, described oil duct P1 oil inlet oil duct.
The utility model turns the control valve by the type of priority variable that adopts above-mentioned technology and obtain, it is simple in structure, compact, with the deflector of small displacement load sensing, controllable capacity pump forms pump control load sensing variable steering hydraulic system together, can be directly used in the bivariate converging system, select from the deflector of small displacement load sensing or both large pressure signals of multiway valve by shuttle valve, and act on controllable capacity pump, make pump do corresponding adjusting to delivery rate, the flow of system requirements necessity is provided, solve the efficient optimum matching problem of the steering hydraulic system of loader under any operating mode, reduce to greatest extent the unnecessary degradation of energy of system, reduce oil temperature, actv. plays energy-conserving action.
Description of drawings
Fig. 1 is front view structural representation of the present utility model;
Fig. 2 is the vertical cutaway view structural representation of looking of Fig. 1;
Fig. 3 is the A-A cutaway view structural representation of Fig. 2;
Fig. 4 is the B-B cutaway view structural representation of Fig. 3;
Fig. 5 is the C-C cutaway view structural representation of Fig. 3;
Fig. 6 is hydraulic system principle figure of the present utility model.
Among the figure: the 1-valve body, the 2-small end cover, 3-amplifies spool, the 4-priority spool, 5-Ls control mouthful plug screw, 6-orifice plug I, 7-orifice plug II, 8-orifice plug III, the large end cap of 9-, 10-turn to A mouth check valve, and 11-turns to B mouth check valve, 12-selects spool, 13-deflector control mouthful a joint, 14-deflector control mouthful b joint, 15-turns to A mouth bypass control, 16-turns to B mouth bypass control, the 17-Ls safety valve, 18-type of priority variable turns the control valve, the deflector of 19-small displacement load sensing, the 20-controllable capacity pump, the 21-multiway valve.
The specific embodiment
Below in conjunction with Figure of description the utility model is further described:
Shown in Fig. 1-6, a kind of type of priority variable turns the control valve, comprise valve body 1, small end cover 2, amplify spool 3, priority spool 4, Ls control mouthful plug screw 5, large end cap 9, turn to A mouth check valve 10, turn to B mouth check valve 11, select spool 12, deflector control mouthful a joint 13, deflector control mouthful b joint 14, turn to A mouth bypass control 15, turn to B mouth bypass control 16, Ls safety valve 17, priority spool 4 holes are provided with 5 oil ducts: from left to right be followed successively by oil duct L1, the oil duct EF that is connected with work system multiway valve oil inlet, steering pump oil inlet oil duct P, the oil duct P1 that is connected with amplification spool 3 holes, oil duct L2, amplify spool 3 holes and be provided with 7 oil ducts: from left to right be followed successively by oil duct a2, back oil road T1, turn to a mouthful oil duct A, oil inlet oil duct P1, turn to a mouthful oil duct B, back oil road T2, oil duct b2, on the described Ls control mouthful plug screw 5 orifice plug I 6 is housed, orifice plug II 7 respectively is equipped with at described priority spool 4 two ends, orifice plug III 8; 9 li of described large end caps are equipped with selects spool 12, a deflector control mouthful a joint 13, a deflector control mouthful b joint 14, a deflector control mouthful a joint 13 is arranged between hydraulic fluid port a and the oil duct a1, control port a is communicated with oil duct a1, oil duct a3, a deflector control mouthful b joint 14 is arranged between hydraulic fluid port b and the oil duct b1, and control port b is communicated with oil duct b1, oil duct b3; The described A of turning to mouth check valve 10 is contained in and turns between mouthful oil duct A and oil duct a2, turns to B mouth check valve 11 to be contained in to turn between mouthful oil duct B and oil duct b2, and oil duct a2 communicates with oil duct a4, oil duct b2 communicates with oil duct b4; Describedly turn to mouthful oil duct A to arrange to turn to A mouth bypass control 15, turn to mouthful oil duct B to arrange and turn to B mouth bypass control 16, described Ls safety valve 17 is arranged on the oil duct L1.
The utility model has following several operating mode when work:
When 1, not turning to
Shown in Fig. 1-6, when deflector is not worked, bearing circle is placed in the middle, the LS mouth is zero by deflector and oil return cut-in pressure, amplify spool 3, select spool 12 to be in the center, the P1 oil duct with turn to the A mouth, turn between the B mouth and be in closed state, this variations per hour steering pump P comes oily orifice plug 7 by priority spool 4 two ends, orifice plug 8 oil-feeds, action of hydraulic force is at priority spool 4 right-hand members, overcome the precompressed compression of priority spool 4 springs, priority spool is moved to the left, the oil duct EF that this moment, steering pump oil inlet oil duct P was connected with work system multiway valve oil inlet is communicated with, and steering pump oil all collaborates in work system, thereby realizes Dual-pump flow-converging, controllable capacity pump is done corresponding adjusting according to the pressure signal of multiway valve to delivery rate, and the flow of work system demand necessity is provided.
2, only turn to when not working
Shown in Fig. 1-6, when bearing circle turns left (right-hand rotation), controllable capacity pump comes the oil content two-way: lead up to deflector pilot control oil out and joint 13(14) a control mouthful a(b) connect, the LS control signal oil of shunting out by deflector is connected with controllable capacity pump, Ls control mouthful plug screw 5, another road through priority spool 4, amplify spool 3 all to steering cylinder.
When bearing circle turns left (right-hand rotation), joint 13 (14) the controls mouthful a (b) of deflector pilot control oil out on large end cap 9 is communicated with oil duct a1 (b1), act on the end of selecting spool 12, promote to select spool 12 downward (making progress) mobile, oil duct b2(a2) by oil duct b4 (a4), oil duct b1 (a1) and oil duct b3 (a3) connect, select spool 12 other end hydraulic oil by the joint 14(13 on the large end cap 9) control mouthful b(a) connect with the deflector oil return, pilot control oil is through oil duct a1 (b1), oil duct a3 (b3) acts on the end of amplifying spool 3, promotion amplification spool 3 left (to the right) is mobile, simultaneously turn to B (A) mouthful of check valve 11 (12) to turning to a mouthful oil duct B (A) through amplifying aperture on the spool 3 to oil duct b2 (a2) and pushing open, amplify simultaneously oil that spool 3 other end oil duct b3 (a3) extrude and push open by oil duct b2 (a2) and turn to B (A) mouth check valve
11 (12) also to turning to a mouthful oil duct B (A), the amount of movement that amplifies spool 3 this moment is subjected to the control of bearing circle rotating speed, the bearing circle rotating speed is faster, enter the pilot control flow that amplifies spool 3 certain end larger, the amount of movement that amplifies spool is larger, then the opening amount is just larger, requirement enters steering cylinder fluid, and more multi-steering is faster, and act on controllable capacity pump by the LS control signal that deflector shunts out, Displacement Regulation, make it to adapt with the demand of steering cylinder, the LS control signal that simultaneously deflector shunts out acts on the left end of priority spool 4 by throttling pore on the orifice plug 6, because the pressure reduction △ P between oil duct L1 chamber, two ends, priority spool 4 left and right sides and the oil duct L2 chamber and the effect of controlling spring power, so that priority spool moves right, oil inlet oil duct P1 opening increases, the oil duct EF opening that is connected with work system multiway valve oil inlet is gradually reduced to closes, priority spool is in right position, steering pump oil inlet oil duct P, the oil duct P1 UNICOM that is connected with the amplification valve opening, the variable steering pump comes oily all through oil inlet oil duct P, the oil duct P1 that is connected with the amplification valve opening, throttling channel and a (b) mouthful of pilot control oil of amplifying on the spool 3 enter steering cylinder B (A) together, the hydraulic oil of steering cylinder A (B) is through turning to a mouthful oil duct A (B), amplify the throttling channel on the spool 3, back oil road T2 oil return realizes that vehicle left (right side) turns to.Controllable capacity pump is done corresponding adjusting according to the pressure signal of load sensing deflector to delivery rate at this moment, and the flow of steering swivel system demand necessity is provided.
When 3, working while turning to
Shown in Fig. 1-6, when working while turning to, the LS control signal that deflector shunts out acts on the left end of priority spool 4 by throttling pore on the orifice plug 6, the fluid of oil inlet oil duct P1 moves to steering cylinder with amplifying spool 3, fluid produces pressure reduction △ P between oil duct L1 chamber and oil duct L2 chamber, the spring force of this pressure reduction and pressure-gradient control valve balances each other, when pressure reduction during less than the spring force of pressure-gradient control valve, priority spool 4 is in right position, the fluid of steering pump is all supplied steering swivel system, when pressure reduction during greater than the pressure-gradient control valve spring force, promoting priority spool 4 moves to left, the oil duct EF opening that oil inlet oil duct P is connected with work system multiway valve oil inlet increases gradually, the unnecessary fluid of variable steering pump changes the oil duct EF that is connected with work system multiway valve oil inlet over to, thereby preferentially guarantee steering swivel system, unnecessary fluid collaborates hydraulic system of working, select from deflector or multiway valve both large pressure signals by shuttle valve this moment, act on controllable capacity pump, make pump do corresponding adjusting to delivery rate, provide and turn to, the flow of work system demand necessity reduces the unnecessary degradation of energy of system to greatest extent.
When steering-load surpassed Ls safety valve 17 rated value, safety valve was opened, the release of LS mouth, the damage that protection system causes because of hypertonia.
When steering cylinder surpasses when turning to A mouth bypass control 15 or turning to the setting pressure of B mouth bypass control 16 owing to the external intervention reason causes load, this moment, bypass control was opened off-load, and the protection steering cylinder is avoided pressure and gone out the damage that causes.
Type of priority variable of the present utility model turns control valve 18, with small displacement load sensing deflector 19, controllable capacity pump 20 forms pump control load sensing variable steering hydraulic system together, can be directly used in the bivariate converging system, select from the deflector 19 of small displacement load sensing or multiway valve 21 both large pressure signals by shuttle valve, and act on controllable capacity pump 20, make pump do corresponding adjusting to delivery rate, the flow of system requirements necessity is provided, solve the efficient optimum matching problem of the steering hydraulic system of loader under any operating mode, reduce to greatest extent the unnecessary degradation of energy of system, reduce oil temperature, actv. plays energy-conserving action.

Claims (7)

1. a type of priority variable turns the control valve, comprise valve body (1), be arranged on the small end cover (2) on the valve body (1), amplify spool (3), priority spool (4), Ls control mouthful plug screw (5) and large end cap (9), described priority spool (4) hole is provided with oil duct L1, oil duct EF, oil duct P, oil duct P1 and oil duct L2, described amplification spool (3) hole is provided with oil duct a2, back oil road T1, oil duct A, oil duct P1, oil duct B, back oil road T2 and oil duct b2, it is characterized in that on the described Ls control mouthful plug screw (5) orifice plug I (6) being set, described priority spool (4) two ends are equipped with respectively orifice plug II (7) and orifice plug III (8), arrange in the described large end cap (9) and select spool (12), deflector control mouthful a joint (13), deflector control mouthful b joint (14), the upper setting of described oil duct A turns to A mouth bypass control (15), arrange between oil duct A and the oil duct a2 and turn to A mouth check valve (10), arrange between oil duct B and the oil duct b2 and turn to B mouth check valve (11), the upper setting of oil duct B turns to B mouth bypass control (16), and Ls safety valve (17) is set on the oil duct L1.
2. a kind of type of priority variable according to claim 1 turns the control valve, it is characterized in that on described selection spool (12) hole hydraulic fluid port a, oil duct a1, oil duct a4, oil duct b4, oil duct b, hydraulic fluid port b being set, oil duct a4 communicates with oil duct a2, and oil duct b2 communicates with oil duct b4.
3. a kind of type of priority variable according to claim 2 turns the control valve, it is characterized in that a described deflector control mouthful a joint (13) is arranged between hydraulic fluid port a and the oil duct a1.
4. a kind of type of priority variable according to claim 2 turns the control valve, it is characterized in that a described deflector control mouthful b joint (14) is arranged between hydraulic fluid port b and the oil duct b1.
5. a kind of type of priority variable according to claim 1 turns the control valve, it is characterized in that described oil duct EF is connected with work system multiway valve oil inlet.
6. a kind of type of priority variable according to claim 1 turns the control valve, it is characterized in that described oil duct P1 is connected with amplification spool (3) hole.
7. a kind of type of priority variable according to claim 1 turns the control valve, it is characterized in that described oil duct P is steering pump oil inlet oil duct, and described oil duct A, oil duct B are and turn to a mouthful oil duct, described oil duct P1 oil inlet oil duct.
CN 201220325185 2012-07-06 2012-07-06 Preferential variable steering control valve Expired - Fee Related CN202703681U (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN 201220325185 CN202703681U (en) 2012-07-06 2012-07-06 Preferential variable steering control valve

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN 201220325185 CN202703681U (en) 2012-07-06 2012-07-06 Preferential variable steering control valve

Publications (1)

Publication Number Publication Date
CN202703681U true CN202703681U (en) 2013-01-30

Family

ID=47584009

Family Applications (1)

Application Number Title Priority Date Filing Date
CN 201220325185 Expired - Fee Related CN202703681U (en) 2012-07-06 2012-07-06 Preferential variable steering control valve

Country Status (1)

Country Link
CN (1) CN202703681U (en)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102734245A (en) * 2012-07-06 2012-10-17 浙江海克力液压有限公司 Preferential-type variable steering control valve
CN103148038A (en) * 2013-03-20 2013-06-12 镇江华瑞液压机械有限公司 Dual-energy saving combined hydraulic valve
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
CN114263644A (en) * 2021-12-27 2022-04-01 徐工集团工程机械股份有限公司道路机械分公司 Oil supply control valve group for steering gear

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102734245A (en) * 2012-07-06 2012-10-17 浙江海克力液压有限公司 Preferential-type variable steering control valve
CN102734245B (en) * 2012-07-06 2015-05-27 浙江海克力液压有限公司 Preferential-type variable steering control valve
CN103148038A (en) * 2013-03-20 2013-06-12 镇江华瑞液压机械有限公司 Dual-energy saving combined hydraulic valve
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
CN114263644A (en) * 2021-12-27 2022-04-01 徐工集团工程机械股份有限公司道路机械分公司 Oil supply control valve group for steering gear
CN114263644B (en) * 2021-12-27 2024-02-27 徐工集团工程机械股份有限公司道路机械分公司 Oil supply control valve group for steering gear

Similar Documents

Publication Publication Date Title
CN201962040U (en) Forklift hydraulic system with functions of priority and unloading
CN201963534U (en) Hydraulic control device for concrete pump
CN201180705Y (en) High-pressure high-volume hydraulic loop device
CN202703681U (en) Preferential variable steering control valve
CN201501119U (en) A continuous pressurizing hydraulic control system of cubic press pressurizer
CN202833008U (en) Concrete pump and hydraulic system thereof
CN105350598A (en) Hydraulic control system for improving energy saving performance of loader and control method of hydraulic control system
CN201531483U (en) Single-acting fast closing/double-acting boosting hydraulic cylinder
CN201125403Y (en) Loading apparatus load sensing energy-saving hydraulic system
CN108545612A (en) A kind of closed system integrates switching valve and control method
CN201902384U (en) Multi-way reversing valve of multifunctional fork truck
CN109306976B (en) Load sensitive control system
CN201169289Y (en) Forklift load sensing priority steering hydraulic system
CN102734245B (en) Preferential-type variable steering control valve
CN102674210B (en) Lift converging multiway valve
CN205207311U (en) Meso position burden flow valve, swing arm energy -saving control system and excavator
CN104192201A (en) Hydraulic steering control valve and hydraulic steering control system
CN205190386U (en) Improve hydraulic control system of loader energy -conservation nature
CN202790680U (en) Electronic controlled proportional multi-way valve
CN103711172B (en) The quantitative combining hydraulic system of loader four pump
CN201944036U (en) Energy-conservation hydraulic system for loader
CN205689505U (en) A kind of force control hydraulic pressure energy saving of system device
CN202730562U (en) A hydraulic system device for track layer traveling power matching
CN204704187U (en) Overload unloading valve
CN208686686U (en) The energy-saving hydraulic system of large-tonnage storage battery forktruck

Legal Events

Date Code Title Description
C14 Grant of patent or utility model
GR01 Patent grant
CF01 Termination of patent right due to non-payment of annual fee

Granted publication date: 20130130

Termination date: 20160706

CF01 Termination of patent right due to non-payment of annual fee