CN101255878A - Energy-saving vibration-reduction type flux amplification valve - Google Patents
Energy-saving vibration-reduction type flux amplification valve Download PDFInfo
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- CN101255878A CN101255878A CNA2007100188241A CN200710018824A CN101255878A CN 101255878 A CN101255878 A CN 101255878A CN A2007100188241 A CNA2007100188241 A CN A2007100188241A CN 200710018824 A CN200710018824 A CN 200710018824A CN 101255878 A CN101255878 A CN 101255878A
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Abstract
The present invention provides an energy-saving damping type amplificative valve. Four throttling groove groups are symmetrical with midline of the main valve core 5, the throttling groove groups on two sides of midline comprise a first oil trough 5a, a second oil trough 5b, a third oil trough 5c and a fourth oil trough 5d in pair respectively, the other two throttling groove groups comprise a first oilreturning groove 5e, a second oilreturning groove 5f, a third oilreturning groove 5g and a fourth oilreturning groove 5h in pair respectively, four throttling groove groups form four main valve port respectively with the first oil intake throttling edge 12a, the second oil intake throttling edge 12b, the first oilreturning throttling edge 12c, the second oilreturning throttling edge 12d, the pilot valve throttling grooves 5i on two ends of the main valve core 5 form two pilot valve port with the first pilot valve throttling edge 12e and the second pilot valve throttling edge 12f on two ends of valve body 12 respectively, the first ring groove 5m and the second ring groove 5n are provided on the left of the main valve core 5, an oil guide ring groove 12k are arranged on the corresponding position of the valve body 12, the first unloading edge 12g and the second unloading edge 12h are provided on the valve body 12 corresponding the position of the first ring groove 5m, seven external connection oil ports are provided on the valve body 12.
Description
Technical field
The present invention relates to the proportional reversing valve that surges, relate in particular to flux amplification valve.
Background technique
The hydraulic flow amplifying valve is widely used in the medium-and-large-sized engineering machinery steering hydraulic system, and its effect is that guide's control flow rate of commutator output is carried out flow and hydraulic power amplification, the motion of control hydraulic actuator according to certain magnification factor.At present, steering hydraulic system exist starting constantly vibrate, creep vibration, stop problem such as moment vibration, cause the work machine operation travelling comfort relatively poor; Simultaneously, there is effectively off-load of steering hydraulic pump, shortcoming such as cause that system energy consumption is big, temperature rise, steering pump life-span are low, the main cause that causes the problems referred to above is exactly the poor-performing of flux amplification valve.Abroad developed the flux amplification valve of some better performances, but its structure more complicated, cost an arm and a leg as Kawasaki Heavy Industries, DANFOSS, card top grade company.
Summary of the invention
The purpose of this invention is to provide a kind of energy-saving vibration-reduction type flux amplification valve.
The present invention is a kind of energy-saving vibration-reduction type flux amplification valve, comprise the proportional reversing valve 2 that surges, safety valve 3, constant difference overflow valve 4, the proportional reversing valve 2 that surges comprises the main valve heart 5, little valve core 13, spring 7, little valve spring 16, valve body 12, right valve gap 10, left side valve gap 11, the main valve heart 5 is by back-up ring 6, spring 7, spring seat 8, hollow screw 9, right valve gap 10 remains on the meta of valve body 12, little valve core 13 in the main valve heart 5 is by little valve guard circle 15, little valve spring 16, screw 17, little valve spring retainer 18, screw plug 19 remains on the meta in the main valve heart 5, there are four throttling groove groups at the middle part of the main valve heart 5, four throttling groove groups are about the center line SS symmetry on the main valve heart 5, the throttling groove group of center line SS both sides is respectively by the first paired oil-feed tank 5a, the second oil-feed tank 5b, the 3rd oil-feed tank 5c, the 4th oil-feed tank 5d forms, two other throttling groove group is respectively by the first paired oil-return groove 5e, the second oil-return groove 5f, the 3rd oil-return groove 5g, the 4th oil-return groove 5h forms, four throttling groove groups respectively with valve body 12 on the first meter in limit 12a, the second meter in limit 12b, the first meter out limit 12c, the second meter out limit 12d has constituted four primary valves, the pilot valve throttling groove 5i at the main valve heart 5 two ends respectively with the first pilot valve throttling limit 12e at valve body 12 two ends, the second pilot valve throttling limit 12f has constituted two pilot valve mouths, there are the first annular groove 5m and the second annular groove 5n in the left side of the main valve heart 5) valve body 12 has lubricating ring groove 12k on the corresponding with it position, on the position of the corresponding first annular groove 5m, the first off-load limit 12g and the second off-load limit 12h are arranged on the valve body 12, seven outer oil-collecting holes are arranged on the valve body 12, hydraulic fluid port P connects the oil hydraulic pump outlet, hydraulic fluid port T connected tank, hydraulic fluid port A and B connect hydraulic actuator, hydraulic fluid port PC connects the spring chamber of constant difference overflow valve 4, and hydraulic fluid port L and R connect the output oil port of commutator.
The present invention compares with background technique, the useful effect that has is: the main valve interior portion of the proportional reversing valve that surges of this energy-conservation vibration-reduction type flux amplification valve is integrated with three position directional valve (little valve core), when steering hydraulic system did not turn to, this selector valve made the steering pump off-load; When turning to, three position directional valve is incorporated into the spring chamber of constant difference overflow valve to the pressure of oil cylinder hyperbaric chamber, and the effect by constant difference overflow valve makes the pressure reduction substantially constant of oil-feed primary valve.Primary valve has adopted level Four to quicken or the throttling groove that slows down arranges that the meter out groove area makes the oil cylinder oil back chamber have certain back pressure all the time less than the meter in groove area, thereby makes that to turn to starting, operation, stopped process steady; The primary valve throttling groove has adopted shallow U-groove bevel type, utilizes the two-step throttle drag effect of throttling groove itself to make mobile stable, inhibition air pocket in the valve port take place, thereby has reduced the noise of valve; First oil-feed tank is a K shape, and first oil-return groove is a V-arrangement, and the former length is shorter than the latter, makes main valve close into and out of hydraulic fluid port is asynchronous, has avoided the hydraulic shock phenomenon.This flux amplification valve has non-steering situation unloading function, therefore reduced system power consumption, save fuel oil and reduce to discharge, the fluid temperature rise reduces, prolonged working life of steering pump.The present invention has advantages such as effectiveness in vibration suppression is good, energy-saving and emission-reduction, good manufacturability, anti-oil contamination ability is strong, cost is lower, can be widely used in the engineering machinery steering hydraulic system.
Description of drawings
Fig. 1 is a hydraulic schematic diagram of the present invention, Fig. 2 is a structural drawing of the present invention, Fig. 3 is the partial enlarged drawing of Fig. 2, Fig. 4 a is the circumferentially deploying figure of the main valve heart among Fig. 2, Fig. 4 b is that the A-A of the main valve heart among Fig. 4 a is to sectional view, Fig. 4 c be the B-B of the main valve heart among Fig. 4 a to sectional view, Fig. 5 is that the D-D of the main valve heart among Fig. 3 a is to sectional view.
Reference character and corresponding name are called: 1. energy-saving vibration-reduction type flux amplification valve, and hydraulic fluid port P connects steering pump, and hydraulic fluid port A and B switch through to oil cylinder, hydraulic fluid port R and L connect commutator, and hydraulic fluid port PC connects surge proportional reversing valve 2 and constant difference overflow valve 4, and proportional reversing valve 2. surges, 3. safety valve, 4. constant difference overflow valve, 5. the main valve heart, 5a. first oil-feed tank, 5b. second inlet channel, 5c. the 3rd oil-feed tank, 5d. the 4th oil-feed tank, 5e. first oil-return groove, 5f. second oil-return groove, 5g. the 3rd oil-return groove, 5h. the 4th oil-return groove, 5i. pilot valve throttling groove, 5j. first radial hole, 5k. through hole, 5l. second radial hole, 5m. first annular groove, 5n. second annular groove, 5o. the 3rd radial hole, 6. back-up ring, 7. spring, 8. spring seat, 9. hollow screw, 10. right valve gap, 11. left valve gaps, 12. valve bodies, 12a. the first meter in limit, 12b. the second meter in limit, the 12c. first meter out limit, the 12d. second meter out limit, 12e. the first pilot valve throttling limit, 12f. the second pilot valve throttling limit, the 12g. first off-load limit, the 12h. second off-load limit, 12i. the first pilot valve runner, 12j. the second pilot valve runner, 12k. lubricating ring groove, 13. little valve cores, 13a. little valve first radial hole, 13b. little valve first convex shoulder, the little valve endoporus of 13c., little valve second convex shoulder of 13d., 13e. little valve collar groove, 13f. little valve second radial hole, 14. balls are stifled, 15. little valve guard circles, 16. little valve spring, 17. screw, 18. little valve spring retainers, the little valve spring retainer of 18a. hole, 19. screw plug, 19a. screw plug hole.
Embodiment
As Fig. 1～shown in Figure 4, energy-saving vibration-reduction type flux amplification valve 1 comprises the proportional reversing valve 2 that surges, safety valve 3, constant difference overflow valve 4, and the proportional reversing valve 2 that surges comprises the main valve heart 5, little valve core 13, spring 7, little valve spring 16, valve body 12, right valve gap 10, left valve gap 11.The main valve heart 5 is by back-up ring 6, spring 7, spring seat 8, hollow screw 9, right valve gap 10 remains on the meta of valve body 12, little valve core 13 in the main valve heart 5 is by little valve guard circle 15, little valve spring 16, screw 17, little valve spring retainer 18, screw plug 19 remains on the meta in the main valve heart 5, there are four throttling groove groups at the middle part of the main valve heart 5, four throttling groove groups are about the SS line symmetry on the main valve heart 5, the throttling groove group of SS line both sides is respectively by the first paired oil-feed tank 5a, the second oil-feed tank 5b, the 3rd oil-feed tank 5c, the 4th oil-feed tank 5d forms, two other throttling groove group is respectively by the first paired oil-return groove 5e, the second oil-return groove 5f, the 3rd oil-return groove 5g, the 4th oil-return groove 5h forms, four throttling groove groups respectively with valve body 12 on the first meter in limit 12a, the second meter in limit 12b, the first meter out limit 12c, the second meter out limit 12d has constituted four primary valves, the pilot valve throttling groove 5i at the main valve heart 5 two ends respectively with the first pilot valve throttling limit 12e at valve body 12 two ends, the second pilot valve throttling limit 12f has constituted two pilot valve mouths, there are the first annular groove 5m and the second annular groove 5n in the left side of the main valve heart 5, valve body 12 has lubricating ring groove 12k on the corresponding with it position, on the position of the corresponding first annular groove 5m, the first off-load limit 12g and the second off-load limit 12h are arranged on the valve body 12, seven outer oil-collecting holes are arranged on the valve body 12, hydraulic fluid port P connects the oil hydraulic pump outlet, hydraulic fluid port T connected tank, hydraulic fluid port A and B connect hydraulic actuator, hydraulic fluid port PC connects the spring chamber of constant difference overflow valve 4, and hydraulic fluid port L and R connect the output oil port of commutator.
The main valve heart 5 is a guiding valve, and the first radial hole 5j, through hole 5k, the second radial hole 5l and the 3rd radial hole 5o are arranged on it.
The little valve first convex shoulder 3b, the little valve second convex shoulder 13d seal the second radial hole 5l, the first radial hole 5j on the main valve heart 5 respectively, and hydraulic fluid port PC connects by lubricating ring groove 12k, the first off-load limit 12g on the valve body 13, the first annular groove 5m, the second off-load limit 12h on the main valve heart 5 and oil return T.
The second oil-feed tank 5b on the main valve heart 5, the 3rd oil-feed tank 5c, the 4th oil-feed tank 5d, the second oil-return groove 5f, the 3rd oil-return groove 5g, the 4th oil-return groove 5h is U-groove bevel, and U-groove bevel is a shallow trench, the degree of depth that is U-groove bevel is less than width dimensions, the second oil-return groove 5f, the 3rd oil-return groove 5g, the length of the 4th oil-return groove 5h and width respectively with the second oil-feed tank 5b, the 3rd oil-feed tank 5c, the 4th oil-feed tank 5d equates, but the second oil-return groove 5f, the 3rd oil-return groove 5g, the degree of depth of the 4th oil-return groove 5h is respectively than the second oil-feed tank 5b, the 3rd oil-feed tank 5c, the degree of depth of the 4th oil-feed tank 5d is little, the second oil-feed tank 5b, the 3rd oil-feed tank 5c, the axial length of the 4th oil-feed tank 5d reduces one by one, the first oil-feed tank 5a is a K shape groove, and the first oil-return groove 5c is a V-shaped groove.
The first oil-feed tank 5a is shorter than the first oil-return groove 5e in the length of the main valve heart 5 axial directions; Oil sealing length between the first oil-feed tank 5a and the first meter in limit 12a is greater than the oil sealing length between the first oil-return groove 5e and the first meter out limit 12c.
Pilot valve throttling groove 5i is shaped as V-shaped groove, and the oil sealing length between the pilot valve throttling groove 5i and the first pilot valve throttling limit 12e is negative value, and promptly the pilot valve mouth is positive opening form.
Working procedure of the present invention is as follows:
As Fig. 1, Fig. 2 and shown in Figure 3, when non-steering situation, be that hydraulic fluid port L and R do not have fuel feeding, the pilot valve throttling groove 5i at the main valve heart 5 two ends and pilot valve first throttle limit 12e, oil sealing length is for negative between the pilot valve second throttling limit 12f, the main valve heart about 5 two chambeies communicate, pressure equates, the main valve heart 5 is at spring 7, be in meta under the effect of back-up ring 6, hydraulic fluid port P, A, B, T all seals, little valve core 13 pressure at two ends also equate, little valve core 13 is at little valve spring 16, remain on meta under little valve guard circle 15 effects, hydraulic fluid port PC is by lubricating ring groove 12k, the first off-load limit 12g, the first annular groove 5m, the second off-load limit 12h and oil return T connect, the pressure of hydraulic fluid port PC is reduced to oil return low pressure, the pressure of the spring chamber of the constant difference overflow valve 4 that is connected with hydraulic fluid port PC also is oil return low pressure, the inlet pressure of constant difference overflow valve 4 is that the P mouth pressure also is oil return low pressure, and promptly oil hydraulic pump is in unloading condition.
As Fig. 2, Fig. 3 and shown in Figure 4, when turning to, as the L fuel feeding, the R oil return, when passing through pilot valve throttling groove 5i, this pilot flow produces pressure reduction, the main valve heart 5 moves right under the difference force effect, oil-feed tank (5a～5d) and oil-return groove (5e～5h) connect step by step, hydraulic fluid port P and A connect, hydraulic fluid port B and T connect, little valve core 13 also moves right under differential pressure action, the first off-load limit 12g seals the first annular groove 5m, cut off hydraulic fluid port PC and hydraulic fluid port T, the pressure of hydraulic fluid port A is by the second radial hole 5l, the 3rd radial hole 5o, the second annular groove 5n, lubricating ring groove 12k causes the spring chamber of hydraulic fluid port PC and constant difference overflow valve 4, and (pressure reduction of valve port two ends P of 5a～5d) and A mouth keeps substantially constant to the meter in groove immediately.
Claims (7)
1, energy-saving vibration-reduction type flux amplification valve, comprise the proportional reversing valve that surges (2), safety valve (3), constant difference overflow valve (4), the proportional reversing valve (2) that surges comprises the main valve heart (5), little valve core (13), spring (7), little valve spring (16), valve body (12), right valve gap (10), left side valve gap (11), the main valve heart (5) is by back-up ring (6), spring (7), spring seat (8), hollow screw (9), right valve gap (10) remains on the meta of valve body (12), little valve core (13) in the main valve heart (5) is by little valve guard circle (15), little valve spring (16), screw (17), little valve spring retainer (18), screw plug (19) remains on the meta in the main valve heart (5), there are four throttling groove groups at the middle part that it is characterized in that the main valve heart (5), four throttling groove groups are about center line (SS) symmetry on the main valve heart (5), the throttling groove group of center line (SS) both sides is respectively by paired first oil-feed tank (5a), second oil-feed tank (5b), the 3rd oil-feed tank (5c), the 4th oil-feed tank (5d) is formed, two other throttling groove group is respectively by paired first oil-return groove (5e), second oil-return groove (5f), the 3rd oil-return groove (5g), the 4th oil-return groove (5h) is formed, four throttling groove groups respectively with valve body (12) on the first meter in limit (12a), the second meter in limit (12b), the first meter out limit (12c), the second meter out limit (12d) has constituted four primary valves, the pilot valve throttling groove (5i) at the main valve heart (5) two ends respectively with the first pilot valve throttling limit (12e) at valve body (12) two ends, the second pilot valve throttling limit (12f) has constituted two pilot valve mouths, there are first annular groove (5m) and second annular groove (5n) in the left side of the main valve heart (5), valve body (12) has lubricating ring groove (12k) on the corresponding with it position, on the position of corresponding first annular groove (5m), the first off-load limit (12g) and the second off-load limit (12h) are arranged on the valve body (12), seven outer oil-collecting holes are arranged on the valve body (12), hydraulic fluid port P connects the oil hydraulic pump outlet, hydraulic fluid port T connected tank, hydraulic fluid port A and B connect hydraulic actuator, hydraulic fluid port PC connects the spring chamber of constant difference overflow valve (4), and hydraulic fluid port L and R connect the output oil port of commutator.
2, energy-saving vibration-reduction type flux amplification valve according to claim 1 is characterized in that the main valve heart (5) is a guiding valve, has first radial hole (5j), through hole (5k), second radial hole (5l) and the 3rd radial hole (5o) on it.
3, energy-saving vibration-reduction type flux amplification valve according to claim 1, it is characterized in that little valve core (13) is a guiding valve, little valve first radial hole (13a), little valve second convex shoulder (13b), little valve endoporus (13c), little valve second convex shoulder (13d), little valve collar groove (13e), little valve second radial hole (13f) are arranged on it, and the right-hand member of little valve endoporus (13c) is by ball stifled (14) sealing.
4, energy-saving vibration-reduction type flux amplification valve according to claim 1, it is characterized in that little valve first convex shoulder (13b), little valve second convex shoulder (13d) seal second radial hole (5l), first radial hole (5j) on the main valve heart (5) respectively, hydraulic fluid port PC connects with oil return T by first annular groove (5m) on the lubricating ring groove (12k) on the valve body (13), the first off-load limit (12g), the main valve heart (5), the second off-load limit (12h).
5, energy-saving vibration-reduction type flux amplification valve according to claim 1, it is characterized in that second oil-feed tank (5b) on the main valve heart (5), the 3rd oil-feed tank (5c), the 4th oil-feed tank (5d), second oil-return groove (5f), the 3rd oil-return groove (5g), the 4th oil-return groove (5h) is U-groove bevel, and U-groove bevel is a shallow trench, the degree of depth that is U-groove bevel is less than width dimensions, second oil-return groove (5f), the 3rd oil-return groove (5g), the length of the 4th oil-return groove (5h) and width respectively with second oil-feed tank (5b), the 3rd oil-feed tank (5c), the 4th oil-feed tank (5d) equates, but second oil-return groove (5f), the 3rd oil-return groove (5g), the degree of depth of the 4th oil-return groove (5h) is respectively than second oil-feed tank (5b), the 3rd oil-feed tank (5c), the degree of depth of the 4th oil-feed tank (5d) is little, second oil-feed tank (5b), the 3rd oil-feed tank (5c), the axial length of the 4th oil-feed tank (5d) reduces one by one, first oil-feed tank (5a) is a K shape groove, and first oil-return groove (5c) is a V-shaped groove.
6, energy-saving vibration-reduction type flux amplification valve according to claim 1 is characterized in that first oil-feed tank (5a) is shorter than first oil-return groove (5e) in the length of the main valve heart (5) axial direction; Oil sealing length between first oil-feed tank (5a) and the first meter in limit (12a) is greater than the oil sealing length between first oil-return groove (5e) and the first meter out limit (12c).
7, energy-saving vibration-reduction type flux amplification valve according to claim 1, the V-shaped groove that is shaped as that it is characterized in that pilot valve throttling groove (5i), oil sealing length between the pilot valve throttling groove (5i) and the first pilot valve throttling limit (12e) is negative value, and promptly the pilot valve mouth is positive opening form.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNA2007100188241A CN101255878A (en) | 2007-09-21 | 2007-09-21 | Energy-saving vibration-reduction type flux amplification valve |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNA2007100188241A CN101255878A (en) | 2007-09-21 | 2007-09-21 | Energy-saving vibration-reduction type flux amplification valve |
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| CN101255878A true CN101255878A (en) | 2008-09-03 |
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| Application Number | Title | Priority Date | Filing Date |
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| CNA2007100188241A Pending CN101255878A (en) | 2007-09-21 | 2007-09-21 | Energy-saving vibration-reduction type flux amplification valve |
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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102267627A (en) * | 2011-07-25 | 2011-12-07 | 武汉钢铁(集团)公司 | Method for reducing discharging quantity of standard part star discharge valve |
| CN102829012A (en) * | 2012-09-18 | 2012-12-19 | 兰州理工大学 | Hydraulic damping device |
| CN106678104A (en) * | 2015-11-06 | 2017-05-17 | 中国航空工业第六八研究所 | Anti-pollution retaining logic control valve |
| CN107128362A (en) * | 2017-05-23 | 2017-09-05 | 吉林大学 | A kind of small-sized narrow-track tractor four-wheel steering synchronization system and rotating direction control method |
| CN110285104A (en) * | 2019-06-04 | 2019-09-27 | 常德中联重科液压有限公司 | Constant difference overflow valve and engineering machinery |
| CN110878778A (en) * | 2019-11-28 | 2020-03-13 | 宁波文泽机电技术开发有限公司 | Engineering machinery vibration damper |
| 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 |
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2007
- 2007-09-21 CN CNA2007100188241A patent/CN101255878A/en active Pending
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102267627A (en) * | 2011-07-25 | 2011-12-07 | 武汉钢铁(集团)公司 | Method for reducing discharging quantity of standard part star discharge valve |
| CN102267627B (en) * | 2011-07-25 | 2012-11-28 | 武汉钢铁(集团)公司 | Method for reducing discharging quantity of standard part star discharge valve |
| CN102829012A (en) * | 2012-09-18 | 2012-12-19 | 兰州理工大学 | Hydraulic damping device |
| CN106678104A (en) * | 2015-11-06 | 2017-05-17 | 中国航空工业第六八研究所 | Anti-pollution retaining logic control valve |
| CN107128362A (en) * | 2017-05-23 | 2017-09-05 | 吉林大学 | A kind of small-sized narrow-track tractor four-wheel steering synchronization system and rotating direction control method |
| CN107128362B (en) * | 2017-05-23 | 2023-03-28 | 吉林大学 | Four-wheel steering synchronous system and steering control method for small narrow-track tractor |
| CN110285104A (en) * | 2019-06-04 | 2019-09-27 | 常德中联重科液压有限公司 | Constant difference overflow valve and engineering machinery |
| CN110285104B (en) * | 2019-06-04 | 2020-12-01 | 常德中联重科液压有限公司 | Fixed-difference overflow valve and engineering machinery |
| CN110878778A (en) * | 2019-11-28 | 2020-03-13 | 宁波文泽机电技术开发有限公司 | Engineering machinery vibration damper |
| CN110878778B (en) * | 2019-11-28 | 2021-07-09 | 山东金利液压科技有限公司 | Engineering machinery vibration damper |
| 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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Open date: 20080903 |