CN2477883Y - Flow switching control valve - Google Patents
Flow switching control valve Download PDFInfo
- Publication number
- CN2477883Y CN2477883Y CN 01236790 CN01236790U CN2477883Y CN 2477883 Y CN2477883 Y CN 2477883Y CN 01236790 CN01236790 CN 01236790 CN 01236790 U CN01236790 U CN 01236790U CN 2477883 Y CN2477883 Y CN 2477883Y
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- valve
- turning
- steering
- control valve
- flow control
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Abstract
The utility model is a new type of turning flow control valve applied to turning hydraulic systems of loaders, which is characterized in that: a mechanical fluid servo turning valve is rationally integrated inside the turning flow control valve; two amplifier chutes are provided symmetrically at corresponding positions at the rod end of the amplifier valve; a bypass throttling and governing device is connected in parallel inside the end cover of the turning pilot oil path. The utility model is characterized in that: the utility model has a compact structure and applies double-pump flow converging and dividing, with improved efficiency of the turning hydraulic system, reduced number of safety turning laps at idle speed, eased operating strength, improved and increased stability of the turning flow control valve, an amplification factor close to a steady valve, and improved turning performances.
Description
The utility model relates to a kind of engineering machinery hydraulic valve, exactly be used for, the applied novel steering flow control valve of large-tonnage loading machine steering hydraulic system.
At present, both at home and abroad in, the large-tonnage wheel loader, steering hydraulic system generally adopts the Constant Pump System form, promptly by steering pump/pioneer pump, the all-hydraulic steering flow amplifying valve that closes heart commutator, wears pressure-gradient control valve, turn to oil cylinder and pipeline etc. to form.
Steering hydraulic system should have following function:
(1) guarantees traffic safety, in the time of should guaranteeing engine idle, also can satisfy steering behaviour and require and turn to full the number of turns 4～5 circles.
Should handle when (2) turning to light, comfortable, steady, anomalies such as non-jitter.
(3) good energy-conserving effect is lacked in system effectiveness height, heating.
In present existing technology, steering safety performance demands when satisfying idling generally adopts bigger gear pump, and as the ZL50D loader that Shandong Engineering Machinery Plant produces, turning to pump delivery is 80ml/r.By turning to 4～5 circles entirely, every circle is 1 a second meter, motor 800 (rev/min) promptly satisfy loader turn to requirement entirely, some producers also adopt the gear pump of bigger specification.When turning to, the hydraulic oil of steering pump is preferentially supplied with steering hydraulic system, to satisfy the requirement of steering hydraulic system.Do not turn to or slow-speed to the time, hydraulic oil is supplied with other hydraulic system.The loader operation need turn to continually, and for boosting productivity, motor is generally worked under middle and high throttle.According to statistics, in turnaround time, the hydraulic pressure of steering pump nearly 40% can fall through the oil hydraulic circuit off-load of other devices owing to surplus, and work not only causes hydraulic oil oil temperature rise, rotten for a long time, cause the fault of other elements, and cause a large amount of energy wastes and environmental pollution.
The steering flow amplifying valve of steering hydraulic system shown in Figure 1 adopts and closes core formula commutator guide control.Because rely on amplifying valve boom end spiral to distribute and gradually the thin-walled aperture of reducing produce back pressure and control the stroke aperture of amplifying valve rod, realize enlarging function, thereby cause and turn to starting performance poor that the fine setting performance is bad.Though it is the magnification factor of steering control valve is approximate curve in whole stroke, widely different in the local magnification factor of curve.It is by turning between outlet plug-in mounting one shuttle valve to control pressure-gradient control valve two that the preferential supply of this valve simultaneously turns to function, and oil duct is Small and Deep Hole Machining, and manufacturability is poor.
The purpose of this utility model provides the steering flow amplifying valve that a kind of simple in structure, steering hydraulic system efficient height, steering behaviour have been stablized, improved.
Order of the present utility model has been achieved in that in the steering flow control valve organic integration mechanical hydraulic servo changing valve of band priority function, it can realize that steering pump and preferential supply of conversion pump double pump turn to according to steering situation, do not turn to or slow-speed to the time, the oil of conversion pump is supplied with other system, and improved the throttle structure of amplifying valve rod port back pressure, and increase turns to the by-pass throttle arrangements for speed regulation of guide's control oil channel, improved and turned to the stability of amplifying valve rod, and made magnification factor near steady state value.
Because use the utility model steering hydraulic system can adopt steering pump, the conversion pump of less discharge capacity to replace original bigger steering pump, when having realized the loader efficiency operation, steering hydraulic system is only by the steering pump fuel feeding, the efficient height of steering hydraulic system.Simultaneously, the hydraulic oil of conversion pump has all been supplied with other equipments, the optional less pump of the working pump of other hydraulic system of working.When idling, owing to steering pump, conversion pump discharge capacity sum are a bit larger tham original steering pump, idling turns to the number of turns few entirely, only is 3.5 circles, and it is low therefore to handle labor intensity.Improved to turn to and amplified the throttle structure that the valve rod flow amplifies groove, and increased the bypass arrangements for speed regulation that turn to guide's control oil channel.Improved and turned to the stability of amplifying valve rod, and made magnification factor, improved the steering stability energy near constant.
The utility model has not only reduced idling safety and has turned to the number of turns entirely, and has reduced hydraulic system power loss, raising steering hydraulic system efficient, has improved the stability of steering system.
Concrete structure of the present utility model is provided by following embodiment and accompanying drawing thereof.
Fig. 1 is the steering flow control valve figure of prior art static state.
Fig. 2 is according to mechanical hydraulic servo changing valve that the utility model proposes the steering flow control valve and the sectional drawing that turns to amplifying valve.
Fig. 3 turns to the flow that amplifies valve rod to amplify the groove partial sectional view.
Fig. 4 turns to amplifying valve and turns to guide's by-pass throttle device sectional drawing.
Fig. 5 is the A-A sectional drawing of Fig. 3.
Describe details and the working condition of using the steering flow control valve of novel proposition according to this in detail below in conjunction with Fig. 2, Fig. 3, Fig. 4.
The details and the working condition of steering flow control valve changing valve.
As shown in Figure 2, the right side, bottom of steering flow control valve is steering system safety valve complement [1], and its left side is a changing valve.The mechanical hydraulic servo changing valve comprises main valve body [2], conversion valve rod [3], spring [4], and conversion valve rod [3] is a Spielpassung with main valve body [2], and relative movement is a straight line motion.Spring [4] lower end acts on the Safety valve body upper end, and the other end acts on conversion valve rod [3] lower end, and under spring force [4] effect, conversion valve rod [3] upper end contacts with plug screw [5].Conversion valve rod [3] lower end spring chamber and Safety valve body form Seal cage II.Conversion valve rod [3] lower end and plug screw [5] form Seal cage I.The B mouth communicates with the A mouth through one-way valve K, and the oil-feed of A mouth communicates with grooving c, and middle oil duct d communicates with turning to amplification valve rod both sides oil duct j, f.Oil input channel L communicates with oil return T through turning to amplifying valve annular groove m.Fig. 2 is the part sectioned view of static steering flow control valve.
The working condition of mechanical hydraulic servo changing valve:
(1) the right side A mouth of steering flow control valve is the filler opening of steering pump, and right side B mouth is the conversion pump filler opening.Work as engine start, turn to amplification valve rod [6] under spring [10] effect, to be in meta, throttle orifice b, the oil duct L of Seal cage II in conversion valve rod [3] annular groove, reach annular groove m and communicate with oil return T, turn to amplification valve rod [6] grooving c to close, the oil pressure at A, B mouth place rises, the damping hole a of pressure on conversion valve rod [3] enters Seal cage I, acts on the right-hand member of conversion valve rod [3].
When hydraulic coupling was greater than spring [4] pressure on the conversion valve rod [3], conversion valve rod [3] moved down, and the grooving f of conversion valve rod [3] opens, the oil of steering pump is through back oil road T oil return, simultaneously, the grooving g of conversion valve rod [3] closes, and the oil of conversion pump flows to other hydraulic system through grooving h.
(2) when low engine speed, the steering dish makes and turns to valve rod [6] to move.Grooving c opens and forms a damping oil duct, and the oil return of conversion valve rod [3] downside Seal cage II is closed, and Seal cage II pressure and spring force sum are during greater than Seal cage I pressure, and conversion valve rod [3] moves up, and closes until the grooving h that changes valve rod.The pressure oil of B mouth is pushed one-way valve K and A mouth pressure oil interflow open, by grooving c through oil duct d, oil duct j and open one-way valve R and enter the S oil duct and lead to steering system.At this moment, the oil pressure before the grooving c is identical with Seal cage I pressure, and the pressure behind the grooving c is identical with the pressure of Seal cage II, and the pressure difference before and after the grooving c is set up by spring [4], and keeps a constant value.
(3) when high engine speeds, the steering dish is because of steering pump, conversion pump have remaining pressure oil, cause that Seal cage I pressure raises, conversion valve rod [3] moves down, and g closes up to grooving, the oil of conversion pump is all supplied with other hydraulic system through grooving g, and steering pump residue fluid is through grooving f oil return.At this moment, entering the hydraulic oil that turns to oil cylinder is all supplied with by steering pump.Because the displacement of steering pump of selecting is chosen by vehicle economic work motor minimum speed, therefore the flow of steering pump off-load at this moment is less, and system effectiveness is higher.
Steering flow amplifier of the present utility model is at amplifying valve boom end corresponding position, and two of symmetric arrangement are amplified skewed slot, and the radial end face of skewed slot is a rectangle, and end face radial dimension y becomes with axial dimension x
Relation.The width D of adjusting constant k or rectangle groove with regard to adjustable turn over to magnification factor.The k value is 0.1～0.8, and the D span is 1～4, and the x value is the running length of valve, is generally less than 10.Owing to adopt steering flow to amplify groove, magnification factor is approximate steady state value in the whole steering travel, therefore turns to the fine setting performance good, and stability is good.
As shown in Figure 4, turning to guide's oil circuit to be arranged in parallel by-pass throttle arrangements for speed regulation.The axle sleeve [8] of the interior setting-in band of end cap [7] damping hole t, damping hole t two ends band filter screens [9].End cap [7] is fixed on the main valve body [2].This device working condition is as follows: as shown in Figure 2, k1 advances guide oil as the lower end, and guide oil one tunnel enters inner oil duct P through amplifying groove
TlAnd through the oil return of k2 mouth, another road is through filter screen [9], damping hole t and the inner oil duct P of bypass axle sleeve [8]
tFlow back into valve rod [6] the other end, through the loop oil return of k2 mouth.When upper end k2 entered guide oil, guide oil one tunnel entered inner oil duct P through amplifying groove
T2Flow to the oil return of k1 mouth, another road is through inner oil duct P
t, left end cap axle sleeve [8] filter screen [9], damping hole t, enter left end k1 oil return.Increase by-pass throttle oil circuit in parallel, weaken the inhomogeneous and unstable influence of engine speed of steering wheel rotating speed to steering behaviour, strengthened the stability that turns to guide's control system, and can adjust the size of damping hole t very easily, turn to the number of turns entirely to adjust, satisfy the requirement of full turnaround time.
Claims (4)
1, a kind of novel steering flow control valve that is used for loading machine steering hydraulic system is characterized in that the integrated mechanical hydraulic servo changing valve that is made of conversion valve rod [3], spring [4] in main valve body [2]; Turning to amplification valve rod [6] end corresponding position, two of symmetric arrangement are amplified the steering flow amplifiers that skewed slot constitutes; In the guide oil terminal lid [7] of steering flow control valve, be arranged in parallel by-pass throttle arrangements for speed regulation.
2, steering flow control valve according to claim 1 is characterized in that the mechanical hydraulic servo changing valve by spring [4], conversion valve rod [3] formation, and in the time of in working order, its Seal cage II and Seal cage 1 are connected with oil circuit before and after the grooving c respectively.
3, steering flow control valve according to claim 1 is characterized in that flow amplifier is to amplify skewed slot two of amplifying valve boom end corresponding position symmetric arrangement, and skewed slot radially cutting plane is a rectangle, and section radial dimension y becomes with axial dimension x
Relation, the width D of adjusting constant k or rectangle groove with regard to adjustable turn over to magnification factor.The k value is 0.1～0.8, and the D span is 1～4, and the x value is the running length of valve, is generally less than 10.
4, steering flow control valve according to claim 1 is characterized in that turning to guide's oil circuit that the by-pass throttle arrangements for speed regulation that are made of throttle orifice t and filter screen [9] are set.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 01236790 CN2477883Y (en) | 2001-04-29 | 2001-04-29 | Flow switching control valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 01236790 CN2477883Y (en) | 2001-04-29 | 2001-04-29 | Flow switching control valve |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2477883Y true CN2477883Y (en) | 2002-02-20 |
Family
ID=33649703
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 01236790 Expired - Fee Related CN2477883Y (en) | 2001-04-29 | 2001-04-29 | Flow switching control valve |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2477883Y (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102003426A (en) * | 2010-12-23 | 2011-04-06 | 山东临工工程机械有限公司 | Flow conversion control valve |
| CN108412831A (en) * | 2018-05-09 | 2018-08-17 | 河北华春液压汽配有限公司 | Shunt variable voltage control commutation pile-up valve |
| CN114576228A (en) * | 2022-05-06 | 2022-06-03 | 英轩重工有限公司 | Flow amplifying valve and steering hydraulic control system thereof |
-
2001
- 2001-04-29 CN CN 01236790 patent/CN2477883Y/en not_active Expired - Fee Related
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102003426A (en) * | 2010-12-23 | 2011-04-06 | 山东临工工程机械有限公司 | Flow conversion control valve |
| CN108412831A (en) * | 2018-05-09 | 2018-08-17 | 河北华春液压汽配有限公司 | Shunt variable voltage control commutation pile-up valve |
| CN108412831B (en) * | 2018-05-09 | 2023-07-25 | 河北华春液压汽配有限公司 | Shunt pressure-regulating speed-regulating reversing integrated valve |
| CN114576228A (en) * | 2022-05-06 | 2022-06-03 | 英轩重工有限公司 | Flow amplifying valve and steering hydraulic control system thereof |
| CN114576228B (en) * | 2022-05-06 | 2022-07-22 | 英轩重工有限公司 | Flow amplifying valve and steering hydraulic control system thereof |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C56 | Change in the name or address of the patentee |
Owner name: SHANDONG CONSTRUCTION MACHINERY GROUP CO., LTD. Free format text: FORMER NAME OR ADDRESS: SHANDONG ENGINEERING MACHINERY PLANT |
|
| CP01 | Change in the name or title of a patent holder |
Patentee after: Shandong SEM Machinery Co., Ltd. Patentee before: Shandong Engineering Machiner Factory |
|
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20020220 Termination date: 20100429 |