CN103615421A - Large-drift-diameter balance valve - Google Patents
Large-drift-diameter balance valve Download PDFInfo
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- CN103615421A CN103615421A CN201310627999.8A CN201310627999A CN103615421A CN 103615421 A CN103615421 A CN 103615421A CN 201310627999 A CN201310627999 A CN 201310627999A CN 103615421 A CN103615421 A CN 103615421A
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- latus rectum
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Abstract
The invention discloses a large-drift-diameter balance valve which comprises a valve body, elastic body bases, fixed plugging blocks, first elastic bodies, one-way valves, a sliding valve, second elastic bodies, third elastic bodies, dampers and end covers. The sliding valve is installed in an inner hole of the valve body, the two ends of the sliding valve are sequentially connected with the elastic body bases, the third elastic bodies and the end covers, a hole channel is formed in the sliding valve, the side wall of the sliding valve is provided with first through-flow holes and second through-flow holes, the first through-flow holes and the second through-flow holes are respectively communicated with the hole channel, a first throttling side is arranged on the left side, a second throttling side is arranged on the right side, the one-way valves are installed in the hole channel of the sliding valve, and the side walls of the one-way valves are connected with the first through-flow holes. The drift diameter of the balance valve of the structure can be made to be larger than that of an existing domestic hydraulic steering engine balance valve, the flow can reach 200L/min, the large-drift-diameter balance valve is simple in structure, stable and reliable in operation and capable of being applied to steering engines with the torque larger than 500kNm in a matched mode, and the isolation function, the steering stabilizing function and the negative torque resisting function can be achieved.
Description
Technical field
The present invention relates to a kind of mechanical fitting, relate in particular to a kind of equilibrium valve.
Background technique
Conventionally we are called positive moment steering wheel to the opplied moment of current, and drag force impels the moment of rudder blade quick rotation to be called negative moment to the effect of rudder blade.When very large negative moment acts on rudder blade, make rudder blade quick rotation consistent with former rudder blade sense of rotation, at this moment rudder blade certainly will drive steering wheel plunger fast moving, when the travelling speed of plunger has substantially exceeded the fuel delivery of steering wheel main oil pump, easily cause oil cylinder because being evacuated for shortage of oil, large quantity of air enters oil cylinder.Its consequence is: steering wheel is malfunctioning, the bad phenomenon such as shock and vibration, noise appear in system, creep.In order to address this problem, the hydraulic sterring engine of China's designed, designed was once set up safety check valve, Pilot operated check valve, trimmer valve etc. in system.But all fail to address this problem well.
Existing domestic hydraulic sterring engine equilibrium valve latus rectum is 10-20mm, and flow is less than 120L/min, is generally used for the steering wheel that moment of torsion is less than 450kNm.When exceeding this latus rectum and range of flow, can adopt following two kinds of technological schemes to realize: a. adopts dual hydraulic control one-way valve (referring to Fig. 1); B. adopt numerous valve members such as one-way valve, sequence valve, selector valve and relief valve to be combined to form a kind of hydraulic sterring engine special valve group (referring to patent: notice of authorization CN101954968B) realize.
In technological scheme a, due to for negative moment what overcome employing is the dual hydraulic control one-way valve of cone valve form, cause the flow of system uneven, easily produce very large hydraulic vibration, not only make system produce very large noise, and vibration easily causes the fatigue of spring and fractures for a long time, thereby lose the function of isolation and steady rudder.
Technological scheme b valve member is numerous, and principle too complexity makes valve form this and rate of fault is higher, low-response, and valve packet size is bigger than normal.
Summary of the invention
For solving above-mentioned problems of the prior art and defect, the invention provides a kind of large latus rectum equilibrium valve, its simple in structure, stable and reliable operation, the latus rectum of the equilibrium valve of this structure can be done is greater than existing domestic hydraulic sterring engine equilibrium valve latus rectum at present, flow can reach 200L/min, the steering wheel of moment of torsion more than 500kNm be can be used in, isolation, steady rudder and anti-negative torque function realized.
Technological scheme of the present invention is as follows:
The invention provides a kind of large latus rectum equilibrium valve, described equilibrium valve comprises:
Valve body, elastomer seat, fixedly chock, the first elastomer, one-way valve, guiding valve, the second elastomer, the 3rd elastomer, damper and end cap;
The first filler opening that the pressure oil that described valve body offers endoporus, discharge with oil pump is connected and the second filler opening, the first oil outlet being connected with outer load and the second oil outlet, the first internal control chamber being communicated with the first filler opening, the second internal control chamber being communicated with the second filler opening, the first internal control chamber and the second internal control chamber are applied to respectively the two ends, left and right of guiding valve;
Described guiding valve is arranged in the endoporus of described valve body, and its two ends connect elastomer seat, the 3rd elastomer and end cap successively; Its inside offers duct; Its left and right, duct sidewall symmetry is offered the first through flow hole, the second through flow hole, communicates respectively with its duct; Offer the second throttling limit offering between the first through flow hole in left side and the second through flow hole between first through flow hole on ， right side, first throttle limit and the second through flow hole;
Described one-way valve is symmetrical to be installed, by the second elastomer and fixedly chock be fixed on the both sides, duct of described guiding valve, its sidewall and described the first through flow hole join; ;
Fixedly chock is enclosed within on described damper, and described damper is provided with groove, and described the first elastomer is arranged in described groove and one end is connected and fixed chock, and the other end connects end cap.
Further, described fixedly chock is plug screw; The end in described duct is internal thread duct.
Further, described guiding valve is cylindrical form guiding valve.
Further, described one-way valve is conical surface seal one-way valve.
Further, described the first elastomer, the second elastomer or the 3rd elastomer are spring.
By such scheme of the present invention, can be found out, large latus rectum equilibrium valve provided by the invention comprises the guiding valve being arranged in valve body, and the one-way valve that is arranged on guiding valve duct, its simple in structure, stable and reliable operation, the latus rectum of the equilibrium valve of this spline structure can be done is greater than existing domestic hydraulic sterring engine equilibrium valve latus rectum at present, flow can reach 200L/min, can be used in the steering wheel of moment of torsion more than 500kNm, realizes isolation, steady rudder and anti-negative torque function.
Accompanying drawing explanation
Fig. 1 is the fundamental diagram of dual hydraulic control one-way valve;
Fig. 2 is the three-dimensional section view of large latus rectum equilibrium valve;
Fig. 3 is the structural drawing of large latus rectum equilibrium valve;
Fig. 4 is the three-dimensional profile figure that interface A, B, C, the D of large latus rectum equilibrium valve is placed in the same face;
Fig. 5 is that interface A, the B of large latus rectum equilibrium valve is placed in bottom surface, and interface C, D are placed in the three-dimensional profile schematic diagram of end face;
Fig. 6 is that interface A, the B of large latus rectum equilibrium valve is placed in bottom surface, and interface C, D are placed in the profile schematic diagram of side;
Fig. 7 is the Median Function schematic diagram of large latus rectum equilibrium valve;
Fig. 8 is the left position function schematic diagram of large latus rectum equilibrium valve;
Fig. 9 is the left transition position function schematic diagram of large latus rectum equilibrium valve.
Valve body 1, spring seat 2, plug screw 3, the first spring 4, one-way valve 5, guiding valve 6, the second spring 7, the 3rd spring 8, damper 9, end cap 10, the first through flow hole 21, the second through flow hole 22, first throttle limit 31 and the second throttling limit 32.
Embodiment
For making object, technological scheme and the advantage of patent of the present invention clearer, below in conjunction with accompanying drawing, patent of the present invention is described in further detail.
First embodiment of the invention provides a kind of large latus rectum equilibrium valve, this large latus rectum equilibrium valve adopts hydraulic control guiding valve pattern, respectively as shown in Figures 2 and 3, this equilibrium valve comprises: valve body 1, spring seat 2, plug screw 3, the first spring 4, one-way valve 5, guiding valve 6, the second spring 7, the 3rd spring 8, damper 9 and end cap 10 for its three-dimensional section view and structure.
On valve body 1, offer by endoporus and six oil pockets, these six oil pockets are respectively the first filler opening, the second filler opening, the first oil outlet, the second oil outlet, the first internal control chamber and the second internal control chamber, with A, B, C, D, K1 and K2, represent respectively, the pressure oil that wherein A, B discharge with oil pump is connected, C, D are connected with outer load, and K1 is communicated with the first filler opening A, and K2 is communicated with the second filler opening B, be applied to respectively the two ends, left and right of guiding valve 6, control the movement of guiding valve 6.
Guiding valve 6 is arranged in the endoporus of valve body 1, and spring seat 2, spring 8 and end cap 10 by two ends position; Guiding valve 6 is cylindrical form guiding valve, and inside is provided with on the sidewall of ，Bing duct, duct left side and offers the first through flow hole 21 and the second through flow hole 22, and in the right sidewall of duct symmetrical the first through flow hole 21 and the second through flow hole 22, the duct inner with it communicates respectively.Between the first through flow hole 21 in left side, duct and the second through flow hole 22, offer first throttle limit 31, between the first through flow hole 21 on right side, duct and the second through flow hole 22, offer the second throttling limit 32.
One-way valve 5 is arranged on the two ends in guiding valve 6 inner ducts, and its sidewall and the first through flow hole 21 join.One-way valve 5 adopts conical surface seal form conducting or cuts off the first through flow hole 21 and the inner duct of guiding valve 6, by the second spring 7 and the plug screw 3 that is tightened in guiding valve 6 ends, positions.
Plug screw 3 is enclosed within on damper 9, and damper 9 is provided with groove, and described the first spring 4 is arranged in described groove and one end connects plug screw 3, and the other end connects end cap 10, damper 9 can be withstood on end cap 10 like this by the first spring 4.
The three-dimensional profile figure of this large latus rectum equilibrium valve as shown in Figure 4, can find out by this figure, and the first filler opening A, the second filler opening B, the first oil outlet C, the second oil outlet D are positioned at the bottom surface of valve body 1, and is furnished with the groove of placing O-ring seals.Valve body 1 can be by six screw mounting hole mounting arrangements on main valve seat.
Certainly, the first filler opening A, the second filler opening B, the first oil outlet C and the second oil outlet D are not limited to and are arranged in same of valve body 1, it can be placed in respectively according to the demand of steering wheel valve group global design the not coplanar of valve body 1, form different oil inlet and outlet combinations, to facilitate, install and valve member coupling.For example, provided the first filler opening A, the second filler opening B are placed in to bottom surface shown in Fig. 5, the first oil outlet C, the second oil outlet D are placed in the schematic diagram of end face; Shown in Fig. 6, provided the first filler opening A, the second filler opening B are placed in to bottom surface, the first oil outlet C, the second oil outlet D are placed in the schematic diagram of side.
In above-described embodiment, plug screw 3 can be also other fixedly chock, and now the duct of guiding valve 6 ends can not arrange internal thread duct, now needs the fixedly duct interference fit of chock and guiding valve 6.
In above-described embodiment, the first spring, the second spring, the 3rd spring also can adopt other elastomer, as thermoplastic elastomer etc.
The working principle of above-mentioned large latus rectum equilibrium valve respectively as shown in Figure 7, Figure 8 and Figure 9.
During not steering, above-mentioned large latus rectum equilibrium valve is in meta state, and its Median Function principle as shown in Figure 7.Guiding valve 6 remains on meta under the effect of the 3rd spring 8, and one-way valve 5 plays non-return effect, cuts off the contact between outer load and oil pump, effectively prevents that oil pump from becoming oil motor, realizes meta lock rudder function.
During steering, above-mentioned large latus rectum equilibrium valve guiding valve 6 can because of both sides oil pressure effect different in valve body 1 left or move right.The guiding valve 6 of large latus rectum equilibrium valve of take is below moved to the left as example and describes, and the left position function principle of large latus rectum equilibrium valve as shown in Figure 8.Suppose that the first filler opening A enters high pressure oil, if disturb without negative torque on rudder blade, pressure oil from oil pump enters behind A chamber, by the first internal control chamber K1, be applied to guiding valve 6 left ends, promote guiding valve 6 and move to right, the position until right-hand member spring seat 2 and the right end cap 10 are collided, now equilibrium valve is in left position function, the pressure oil of the first filler opening A enters the second through flow hole 22 of guiding valve 6, and one-way valve 5 is opened, and then by the first through flow hole 21, outputs to the first oil outlet C and carries out steering; Meanwhile, open completely on guiding valve 6 and valve body 1 the second throttling limit 32 between the second filler opening B and the second oil outlet D, non-resistance oil return.
The left transition position function principle of above-mentioned large latus rectum equilibrium valve as shown in Figure 9.When boats and ships are in storm navigation, rudder blade is often subject to stormy waves, the impact of ice cube, or because adopting certain special rudder blade, on rudder stock, sometimes will be subject to like this effect of negative torque, and consistent with turning to of rudder, now pushing away rudder cylinder piston motion accelerates, by the first filler opening A, flow into the pressure oil of the first oil outlet C and cause that pressure reduces rapidly because have little time to supplement, this pressure that just means equilibrium valve left end the first internal control chamber K1 reduces rapidly, and the second oil outlet D accelerates because of flow velocity to the oil return of the second filler opening B, resistance increment and cause that the pressure of the second internal control chamber K2 raises, add the effect of compressed the 3rd spring 8 of right-hand member, like this when the right-hand member of guiding valve 6 makes a concerted effort to be greater than left end oil pressure, guiding valve 6 will disequilibrium and is moved to the left, until arrive new equilibrium position.And guiding valve 6 and valve body 1 the second throttling limit 32 between the second filler opening B and the second oil outlet D diminishes owing to moving to left and plays throttling action, make cylinder piston motion Speed Reduction evenly mobile, not steady thereby the rudder speed that opposing negative torque is brought is accelerated operation.
Technological scheme by the invention described above can be found out, equilibrium valve provided by the invention comprises the guiding valve being arranged in valve body, and the one-way valve that is arranged on guiding valve duct, its simple in structure, stable and reliable operation, the latus rectum of the equilibrium valve of this spline structure can be done is greater than existing domestic hydraulic sterring engine equilibrium valve latus rectum at present, flow can reach 200L/min, can be used in the steering wheel of moment of torsion more than 500kNm, realizes isolation, steady rudder and anti-negative torque function.
Although the present invention with preferred embodiment openly as above, embodiment is not of the present invention for limiting.Without departing from the spirit and scope of the invention, any equivalence of doing changes or retouching, belongs to equally the present invention's protection domain.Therefore should to take the application's the content that claim was defined be standard to protection scope of the present invention.
Claims (5)
1. a large latus rectum equilibrium valve, is characterized in that, described large latus rectum equilibrium valve comprises:
Valve body, elastomer seat, fixedly chock, the first elastomer, one-way valve, guiding valve, the second elastomer, the 3rd elastomer, damper and end cap;
The first filler opening that the pressure oil that described valve body offers endoporus, discharge with oil pump is connected and the second filler opening, the first oil outlet being connected with outer load and the second oil outlet, the first internal control chamber being communicated with the first filler opening, the second internal control chamber being communicated with the second filler opening, the first internal control chamber and the second internal control chamber are applied to respectively the two ends, left and right of guiding valve;
Described guiding valve is arranged in the endoporus of described valve body, and its two ends connect elastomer seat, the 3rd elastomer and end cap successively; Its inside offers duct; Its left and right, duct sidewall symmetry is offered the first through flow hole, the second through flow hole, communicates respectively with its duct; Offer the second throttling limit offering between the first through flow hole in left side and the second through flow hole between first through flow hole on ， right side, first throttle limit and the second through flow hole;
Described one-way valve is symmetrical to be installed, by the second elastomer and fixedly chock be fixed on the both sides, duct of described guiding valve, its sidewall and described the first through flow hole join;
Fixedly chock is enclosed within on described damper, and described damper is provided with groove, and described the first elastomer is arranged in described groove and one end is connected and fixed chock, and the other end connects end cap.
2. large latus rectum equilibrium valve according to claim 1, is characterized in that, described fixedly chock is plug screw; The end in described duct is internal thread duct.
3. large latus rectum equilibrium valve according to claim 1 and 2, is characterized in that, described guiding valve 6 is cylindrical form guiding valve.
4. large latus rectum equilibrium valve according to claim 3, is characterized in that, described one-way valve 5 is conical surface seal one-way valve.
5. large latus rectum equilibrium valve according to claim 4, is characterized in that, described the first elastomer, the second elastomer or the 3rd elastomer are spring.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310627999.8A CN103615421B (en) | 2013-11-28 | 2013-11-28 | A kind of Large-drift-diameterbalance balance valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310627999.8A CN103615421B (en) | 2013-11-28 | 2013-11-28 | A kind of Large-drift-diameterbalance balance valve |
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| Publication Number | Publication Date |
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| CN103615421A true CN103615421A (en) | 2014-03-05 |
| CN103615421B CN103615421B (en) | 2016-03-02 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201310627999.8A Active CN103615421B (en) | 2013-11-28 | 2013-11-28 | A kind of Large-drift-diameterbalance balance valve |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108177754A (en) * | 2017-12-28 | 2018-06-19 | 赛克思液压科技股份有限公司 | A kind of compact profile shaft flow hydraulic axial plunger pump |
| CN111094762A (en) * | 2017-09-26 | 2020-05-01 | 川崎重工业株式会社 | Anti-swing device |
| CN113309749A (en) * | 2021-05-21 | 2021-08-27 | 杭州诺祥科技有限公司 | Digital control type hydraulic triode |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201125893Y (en) * | 2007-11-29 | 2008-10-01 | 贵州枫阳液压有限责任公司 | Bidirectional balanced valve |
| DE102007054135A1 (en) * | 2007-11-14 | 2009-05-20 | Hydac Filtertechnik Gmbh | Hydraulic valve device |
| CN201770000U (en) * | 2010-07-27 | 2011-03-23 | 南京中船绿洲机器有限公司 | Rotary vane type steering engine high-flow anti-surging negative torque valve |
| CN202040134U (en) * | 2011-03-18 | 2011-11-16 | 宁波克泰液压有限公司 | Cartridge balanced valve |
| CN202946467U (en) * | 2012-11-23 | 2013-05-22 | 上海立新液压有限公司 | Electric hydraulic control one-way valve |
-
2013
- 2013-11-28 CN CN201310627999.8A patent/CN103615421B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102007054135A1 (en) * | 2007-11-14 | 2009-05-20 | Hydac Filtertechnik Gmbh | Hydraulic valve device |
| CN201125893Y (en) * | 2007-11-29 | 2008-10-01 | 贵州枫阳液压有限责任公司 | Bidirectional balanced valve |
| CN201770000U (en) * | 2010-07-27 | 2011-03-23 | 南京中船绿洲机器有限公司 | Rotary vane type steering engine high-flow anti-surging negative torque valve |
| CN202040134U (en) * | 2011-03-18 | 2011-11-16 | 宁波克泰液压有限公司 | Cartridge balanced valve |
| CN202946467U (en) * | 2012-11-23 | 2013-05-22 | 上海立新液压有限公司 | Electric hydraulic control one-way valve |
Non-Patent Citations (1)
| Title |
|---|
| 刘德宽: "《船舶辅机》", 28 February 2006, 大连海事大学出版社 * |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111094762A (en) * | 2017-09-26 | 2020-05-01 | 川崎重工业株式会社 | Anti-swing device |
| CN111094762B (en) * | 2017-09-26 | 2022-02-18 | 川崎重工业株式会社 | Anti-swing device |
| CN108177754A (en) * | 2017-12-28 | 2018-06-19 | 赛克思液压科技股份有限公司 | A kind of compact profile shaft flow hydraulic axial plunger pump |
| CN108177754B (en) * | 2017-12-28 | 2019-09-20 | 赛克思液压科技股份有限公司 | A kind of compact profile shaft flow hydraulic axial plunger pump |
| CN113309749A (en) * | 2021-05-21 | 2021-08-27 | 杭州诺祥科技有限公司 | Digital control type hydraulic triode |
| CN113309749B (en) * | 2021-05-21 | 2022-03-11 | 杭州诺祥科技有限公司 | Digital control type hydraulic triode |
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| CN103615421B (en) | 2016-03-02 |
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Effective date of registration: 20160722 Address after: 200031 room 43, building 10, No. 105, Xuhui District, Shanghai, Hengshan Road Patentee after: Shanghai Dake hydraulic Electromechanical Engineering Co., Ltd. Address before: 200031 Xuhui District, Hengshan Road, No. 10, Patentee before: No.704 Institute of China Shipbuilding Industry Corporation |