CN102261354A - Crane hydraulic system and hydraulic balance valve thereof - Google Patents
Crane hydraulic system and hydraulic balance valve thereof Download PDFInfo
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- CN102261354A CN102261354A CN2011100982139A CN201110098213A CN102261354A CN 102261354 A CN102261354 A CN 102261354A CN 2011100982139 A CN2011100982139 A CN 2011100982139A CN 201110098213 A CN201110098213 A CN 201110098213A CN 102261354 A CN102261354 A CN 102261354A
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Abstract
The invention discloses a hydraulic balance valve which comprises a control valve cover and a main valve body, wherein the control valve cover is internally provided with a ladder blind hole which is opposite to and coaxial with the control valve core; the control valve cover is provided with a control oil port which is communicated with the large-diameter section of the blind hole; the small-diameter section of the blind hole is communicated with a containing chamber; the large-diameter section is provided with a plugging component for plugging the small-diameter section; the diameter of the plugging component decreases gradually in the direction towards the small-diameter section, and the plugging fit surface of the plugging component and the small-diameter section is provided with a throttling groove; and the cross section of the throttling groove decreases gradually and axially. In a closing process, control oil enters an oil duct, the flow rate through the throttling groove decreases gradually, and the occurrence of hydraulic impact can be avoided effectively, thus the pressure vibration of control oil liquids which act on the control valve core is less, the opening of a main valve core can be stable, the vibration can be eliminated, and the valve has the advantages of higher comfortableness and safe reliability. The invention also discloses a crane hydraulic system comprising the hydraulic balance valve.
Description
Technical field
The present invention relates to technical field of engineering machinery, particularly a kind of hydraulically balanced valve.The invention still further relates to a kind of crane hydraulic system that comprises above-mentioned hydraulically balanced valve.
Background technique
The safety work performance that improves hoist is the technical problem that these those skilled in the art endeavour to study always.At present in the hoisting of hoist, luffing and the telescopic system, all use equilibrium valve and carry out hydraulic lock, proof load can reliably stop at an arbitrary position, avoids because the internal leakage of hydraulic element brings moving of load.Therefore, adopt equilibrium valve to carry the balance and the safety installations of rate of descent usually as control hoist band.
The trouble free service principle of equilibrium valve is as follows: the equilibrium valve forward is that the one-way valve that hydraulic oil liquid is directly pushed open in the main valve body flows through valve body when opening, when load descends oppositely unlatching, need the commutation of control spool, the control cover plate that enters equilibrium valve by control fluid, and promote spool and move and commutate.
Please refer to Fig. 1, Fig. 1 is a kind of control section sectional view of typical equilibrium valve, and this figure only illustrates the control spool on control end cap and the main valve body, saves conventional structures such as main valve plug on the main valve body and guide's spool.
This equilibrium valve is the main ball type one-way valve that is set up in parallel with the main valve position that adopts in the commutation process of control spool 121.The control end cap 11 and the main valve body 12 of equilibrium valve are set up in parallel vertically, control end cap 11 is provided with control port 111, control oil enters the oil pocket a of control end cap 11 inside from control port 111, oil pocket a ingress is provided with oil purifier and inlet damping, enter the cavity volume b between adjusting screw rod 13 and the control spool 121 again along the gap between push rod 14 and the adjusting screw rod 13, thereby promoting control spool 121 moves right, control spool 121 promotes guide's valve core movement again, after guide's spool operation certain distance, main valve plug moves to right gradually, until opening valve port fully.In this process, push rod 14 is also along with control spool 121 moves to right together, then steel ball 132 also moves right under the effect of spring 131, when control spool 121 continues to move right, when steel ball 132 is sealed duct, adjusting screw rod 13 right side, steel ball 132 has just formed one-way valve structures with adjusting screw rod 13, seals the gap oil duct between push rod 14 and the adjusting screw rod 13, thereby blocks the cavity volume b that control oil enters control spool 121 left sides.
Yet, the moment that steel ball 132 in the control end cap 11 is cutting out, control oil is sealed and stopped suddenly, thereby can produce the hydraulic shock of short time, can't in opening process, control the commutation of spool 121 reposefully, at this moment, can cause the pilot pressure of control spool 121 to produce big ups and downs, because control spool 121 relies on the spring force effect to reset, pressure surge causes spring 131 to follow vibration, finally cause main valve plug about the vibration, make the opening of valve port suddenly big or suddenly small, be that unexpected variation can take place the travelling speed of main valve plug in commutation or moving process, bring hydraulic shock probably, cause creeping of hydraulic actuator, phenomenons such as acceleration suddenly cause the structural member vibration, thereby bring the unstability and the discomfort of operation to the operator, cause operate miss to produce security incident easily.When equilibrium valve being applied in the hoisting system of runabout crane, this fault will show as that oil hydraulic motor takes place to stop suddenly or speed is accelerated suddenly in rotation process, thereby cause the unexpected pause or the lifting suddenly of weight, the dependency structure parts also produce and tremble simultaneously.
Therefore, how making the pilot pressure of equilibrium valve more stable, control the commutation of main valve plug reposefully, is those skilled in the art's technical issues that need to address.
Summary of the invention
An object of the present invention is to provide a kind of hydraulically balanced valve, have the process of buffering during this hydraulically balanced valve closing control oil, avoid the generation of compression shock, make pilot pressure comparatively stable, thereby can control the spool commutation reposefully.Another object of the present invention provides a kind of crane hydraulic system that comprises above-mentioned hydraulically balanced valve.
For reaching first purpose of the present invention, the invention provides a kind of hydraulically balanced valve, be provided with the control spool in its main valve body, have cavity volume between described control spool and its application valve cover; Have the ladder blind hole relative and coaxial in the described application valve cover with described control spool, and be provided with the control port of the big footpath section that is communicated with described blind hole, the path section of described blind hole is communicated with described cavity volume, and described big footpath section is equipped with the plugging part of elastic member, the described path section of shutoff vertically successively; The diameter of described plugging part is at convergent on the direction of described path section, and the shutoff fitting surface of described plugging part and described path section is provided with throttling groove, and the cross-section area of described throttling groove is cumulative on the direction of described path section.
Preferably, described plugging part is a cone table shape.
Preferably, described path section is a shoulder hole; Described plugging part cooperates with the step surface place shutoff that described path section is joined with the step surface place or the described big footpath section of described path section.
Preferably, the number of described throttling groove is four, and circumferentially evenly distributing along described plugging part.
Preferably, described elastic member is a helical spring, and described plugging part connects guide rod, and described guide rod inserts in the described helical spring helical cavity.
Preferably, also be provided with the passage of direct connection described big footpath section and described cavity volume on the described application valve cover, described passage is provided with fixedly damping; Also be provided with relief valve on the described equilibrium valve, the filler opening of described relief valve is communicated with described cavity volume, and the oil outlet of described relief valve is communicated with return opening.
Preferably, described passage comprises the radially oil pocket that is communicated with described big footpath section, with the axial passage that is communicated with described radially oil pocket and described cavity volume, described fixedly damping comprises first damping and second damping, and described first damping and described second damping are arranged at respectively in described radially oil pocket and the described axial passage.
Preferably, described relief valve is arranged on the described application valve cover.
Preferably, described control spool is provided with the damping cavity that is communicated with described control spool described cavity volume in left side and right side spring chamber, is provided with the 3rd damping in the described damping cavity, and described spring chamber is communicated with the leakage hydraulic fluid port.
The hydraulically balanced valve that this invention provided, the shutoff end face of its plugging part is provided with the throttling groove that radial cross section gradually increases, then control oil enters first oil duct of cavity volume between control spool and the application valve cover in the process of sealing, discharge value through throttling groove is successively decreased lenitively, thereby the pass closed procedure of first oil duct is comparatively relaxed, there is transition stage, can avoid the generation of hydraulic shock effectively, reach the effect of filtering, therefore, the pressure surge that acts on the control fluid on the control spool is less, moving of main valve plug is comparatively steady, and valve port opening can be not suddenly big or suddenly small, and then the control system of this equilibrium valve in the course of the work, can eliminate shake, have higher operation comfort and safety reliability.
For reaching another object of the present invention, the present invention also provides a kind of crane hydraulic system, comprise hydraulic actuator and Hydraulic power units, described Hydraulic power units is provided with hydraulically balanced valve to the path of described hydraulic actuator, and described hydraulically balanced valve is above-mentioned each described hydraulically balanced valve.Because above-mentioned hydraulically balanced valve has above-mentioned technique effect, the crane hydraulic system with this hydraulically balanced valve also has identical technique effect.
Description of drawings
Fig. 1 is a kind of control section sectional view of typical equilibrium valve;
Fig. 2 is the structural representation of a kind of embodiment of hydraulically balanced valve provided by the present invention;
Fig. 3 is the structural representation of ladder blind hole among Fig. 2;
Fig. 4 is the structural representation of plugging part and guide rod among Fig. 2;
Fig. 5 is the schematic representation that cooperates of push rod and adjustable lever integral body among Fig. 2;
Fig. 6 is in the structural representation of sealed condition for plugging part among Fig. 5.
Fig. 7 is the structural representation of the another kind of embodiment of hydraulically balanced valve provided by the present invention;
Fig. 8 is the working principle schematic representation of hydraulic pressure half-bridge among Fig. 7.
Embodiment
There is the process of buffering in core of the present invention for a kind of hydraulically balanced valve is provided during this hydraulically balanced valve closing control oil, avoid the generation of compression shock, makes pilot pressure comparatively stable, thereby can control the spool commutation reposefully.Another core of the present invention is for providing a kind of crane hydraulic system that comprises above-mentioned hydraulically balanced valve.
In order to make those skilled in the art understand technological scheme of the present invention better, the present invention is described in further detail below in conjunction with the drawings and specific embodiments.
Please refer to Fig. 2 to Fig. 6, Fig. 2 is the structural representation of a kind of embodiment of hydraulically balanced valve provided by the present invention, and this figure only illustrates application valve cover and control valve core segment, saves conventional structure such as main valve plug and guide's spool; Fig. 3 is the structural representation of ladder blind hole among Fig. 2; Fig. 4 is the structural representation of plugging part and guide rod among Fig. 2; Fig. 5 is the schematic representation that cooperates of push rod and adjustable lever integral body among Fig. 2; Fig. 6 is in the structural representation of sealed condition for plugging part among Fig. 5.
Hydraulically balanced valve in this mode of execution comprises application valve cover 3 and main valve body 2, is provided with main valve plug and guide's spool in the main valve chamber of main valve body 2, and when the equilibrium valve forward was opened, hydraulic oil directly promoted main valve plug and moves, and valve port is opened; When equilibrium valve is oppositely opened (when carrying decline) as the hoist band, control oil enters the control oil duct from the control port of controlling on the valve gap 3 32, flow into the left side cavity volume C of guide's valve pocket 21 inner control spools 22, guide's valve pocket 21 is located on the main valve body 2, then control oil promotion control spool 22 moves, control spool 22 is passed guide's spool again, after guide's spool moves to certain distance, main valve plug moves gradually, thereby open valve port lentamente, then the pressure stability of control oil has determined the stability that main valve plug commutates to a certain extent in reverse opening process.
Have ladder blind hole relative with control spool 22 and coaxial setting in the application valve cover 3 of hydraulically balanced valve, promptly the conduction terminal of ladder blind hole is relative with control spool 22, and the path section 316 of ladder blind hole is near controlling spools 22.Ladder blind hole in this mode of execution is positioned on the adjustable lever 31, processes the axial bore coaxial with controlling spool 22 on the main body of application valve cover 3, and the adjustable lever 31 that will have the ladder blind hole inserts in the axial bore of application valve covers 3, and fixing with tightening cover 5.The structural design of adjustable lever 31 is convenient to the processing and the installation of assembly, and can improve cooperate between the component accurate.Certainly, in theory, can be integral structure also with the body design of adjustable lever 31 and application valve cover 3.
Be equipped with elastic member and plugging part 313 vertically successively in the big footpath section 315 of ladder blind hole, plugging part 313 is in order to shutoff ladder blind hole path section 316 and the section 315 step surface places that join, big footpath, in order to realize effective shutoff, plugging part 313 is a variable-diameter structure, its diameter is at convergent on the direction of path section 315, can be taper, spherical, or the cone table shape shown in Fig. 4, when implementing effective shutoff, also have good leading role.When plugging part 313 is cone table shape, the joint of path section 316 and big footpath section 315 can be established the one-level step again, be that path section 316 also is shoulder hole, form path section 316 left side sections and right side section, be convenient to the insertion shutoff of plugging part 313, can further improve plugging effect, the maximum diameter of the plugging part 313 of cone table shape can be greater than the diameter of left side section or right side section, the left side section of the plugging part shutoff path section 316 shown in Fig. 6.The plugging action of plugging part 313 is mainly realized by the reset response of elastic member, during assembling, elastic member is in its pre-compressed state, elastic member can be 311, plugging part 313 can connect guide rod 312, in the helical cavity with guide rod 312 insertions 311, then 311 can stablize and leading role preferably for mobile the playing of plugging part 313, and the processing that the plugging part 313 of cone table shape combines with guide rod 312 is easy to realize on technology.Equilibrium valve also comprises push rod 4, push rod 4 runs through the path section 316 of ladder blind hole, an and end butt plugging part 313 of push rod 4, the other end connects control spool 22, the other end of push rod 4 inserts in the attachment hole of control spool 22 among Fig. 2, the diameter of push rod 4 is slightly less than the diameter of path section 316, promptly has certain clearance between the inner circle wall of push rod 4 and path section 316, and this gap is communicated with control port 32 by big footpath section 315.
Can on the perisporium of big footpath section 315, offer radial direction through hole 314, adjustable lever 31 also has certain clearance with the perisporium of the axial bore of application valve cover 3, then flow to radial direction through hole 314 by this gap from controlling the control oil that hydraulic fluid port 32 enters, flow into the big footpath section 315 of ladder blind hole again, and then enter cavity volume C between control spool 22 and the adjustable lever 31, first oil duct that this is communicated with cavity volume C for realization control port 32 by the gap between path section 316 and the push rod 4.Under the pressure effect of cavity volume C inner control oil, control spool 22 moves to right, at this moment, push rod 4 moves to right synchronously in company with control spool 22, when then plugging part 313 was sealed path section 316 at the step surface place that the reset response of elastic member is displaced downwardly to path section 316, control oil was closed with first oil duct of cavity volume C.
Plugging part 313 is provided with throttling groove 3131 with the shutoff fitting surface of path section 316, the radial cross-section of throttling groove 3131 amasss cumulative on the direction of path section 316, the gradual change trend that is throttling groove 3131 radial dimensions is opposite with the gradual change trend of plugging part 313 overall radial dimension, as shown in Figure 4, the diameter of plugging part 313 is along the direction convergent towards path section 316, and the radial cross-section along this direction of throttling groove 3131 gradually increases.Then first oil duct is when sealing gradually, successively decrease lenitively through the discharge value of throttling groove 3131, promptly first oil duct close the process that relaxes for comparatively, have transition stage, thereby can avoid the generation of hydraulic shock effectively, reach the effect of filtering.Therefore, compare with equilibrium valve of the prior art, the moment that plugging part 313 of the present invention is closed first oil duct can not produce hydraulic shock, the pressure surge that acts on the control fluid on the control spool 22 is less, and therefore, moving of main valve plug is comparatively steady, valve port opening can be not suddenly big or suddenly small, then the control system of this equilibrium valve can be eliminated shake in the course of the work, has higher operation comfort and safety reliability.
Be processed with four throttling grooves 3131 on the plugging part 313 in this mode of execution, preferably make four throttling grooves 3131 and circumferentially uniform along plugging part 313, this scheme can make control fluid flow in each throttling groove 3131 equably, further guarantees the stationarity of main valve plug action.Need to prove that the number of throttling groove 3131 is not limited to four, can determine concrete throttling groove 3131 numbers, satisfy when commutation requires fast, reach throttling stablizing effect preferably according to the parameter request of the equilibrium valve of different model.
Please refer to Fig. 7 and Fig. 8, Fig. 7 is the structural representation of the another kind of embodiment of hydraulically balanced valve provided by the present invention, and identical with Fig. 2, this figure only illustrates application valve cover and control valve core segment, saves conventional structure such as main valve plug and guide's spool; Fig. 8 is the working principle schematic representation of hydraulic pressure half-bridge among Fig. 7.
Cavity volume C and control port 32 also have second oil duct, as shown in Figure 7, application valve cover 3 main bodys are provided with the radially oil pocket B 1 that is communicated with the big footpath of ladder blind hole section 315, big footpath section 315 is provided with first damping 34 with the oil pocket B1 place of connection radially, also be provided with on the application valve cover 3 and be communicated with the radially axial passage B2 of oil pocket B1 and cavity volume C, axial passage B2 is provided with second damping 35 with the place of connection of cavity volume C, processing is convenient in the radially oil pocket B1 at this place and the design of axial passage B2, in fact, as long as the passage that is communicated with big footpath section 315 and cavity volume C is set, because the existence of first damping 34 and second damping 35, when first oil duct is opened, control oil only from first oil duct by entering cavity volume C, when first oil duct is closed, control oil side enters cavity volume C from second oil duct, promptly flow to inlet oil pocket A from controlling hydraulic fluid port 32, then enter the gap between adjustable lever 31 and application valve cover 3 main bodys, enter the radial direction through hole 314 on the adjustable lever 31 again, flow to the big footpath section 315 of ladder blind hole, and enter radially oil pocket B1 and axial passage B2, the left side cavity volume C of final flow direction control valve core 22.In addition, the equilibrium valve in this mode of execution is setting-in relief valve 24 on application valve cover 3, and the filler opening of relief valve 24 is communicated with the cavity volume C in control spool 22 left sides, the oil return circuit of the oil outlet connected system of relief valve 24.Then when the oil pressure of control spool 22 left side cavity volume C was too high, the main valve plug of relief valve 24 was opened, and control oil overflows back fuel tank from relief valve 24.
In the control oil channel of main valve plug commutation, relief valve 24 is equivalent to variable liquid resistance n1, and first damping 34 in second oil duct and second damping 35 are fixer resistance n2, and variable liquid resistance n1 and fixer resistance n2 form a hydraulic pressure half-bridge, working principle schematic representation as shown in Figure 8; Because the coupling of pressure and flow relation, when the variation in pressure of control oil channel is adjusted, the signal of no matter exporting is flow gain or Pressure gain, the excessive steady-state value that arrives that all can be very mild, thereby avoid the generation of moment impact, promptly between pilot stage and power stage the hydraulic pressure half-bridge as the inter-stage feedback loop, thereby can further can improve the precision of equilibrium valve.
Except above-mentioned hydraulically balanced valve, the present invention also provides a kind of crane hydraulic system, comprise hydraulic actuator and Hydraulic power units, described Hydraulic power units is provided with hydraulically balanced valve to the path of described hydraulic actuator, and described hydraulically balanced valve is above-mentioned each described hydraulically balanced valve.Because above-mentioned hydraulically balanced valve has above-mentioned technique effect, the crane hydraulic system with this hydraulically balanced valve also has identical technique effect, does not give unnecessary details at this.
More than a kind of crane hydraulic system provided by the present invention and hydraulically balanced valve thereof are described in detail.Used specific case herein principle of the present invention and mode of execution are set forth, above embodiment's explanation just is used for helping to understand method of the present invention and core concept thereof.Should be pointed out that for those skilled in the art, under the prerequisite that does not break away from the principle of the invention, can also carry out some improvement and modification to the present invention, these improvement and modification also fall in the protection domain of claim of the present invention.
Claims (10)
1. a hydraulically balanced valve is provided with control spool (22) in its main valve body (2), has cavity volume (C) between described control spool (22) and its application valve cover (3); Have the ladder blind hole relative and coaxial in the described application valve cover (3) with described control spool (22), and be provided with the control port (32) of the big footpath section (315) that is communicated with described blind hole, the path section (316) of described blind hole is communicated with described cavity volume (C), it is characterized in that described big footpath section (315) is equipped with the plugging part (313) of elastic member, the described path section of shutoff (316) vertically successively; The diameter of described plugging part (313) is at convergent on the direction of described path section (316), and described plugging part (313) is provided with throttling groove (3131) with the shutoff fitting surface of described path section (316), and the cross-section area of described throttling groove (3131) is cumulative on the direction of described path section (316).
2. hydraulically balanced valve according to claim 1 is characterized in that, described plugging part (313) is a cone table shape.
3. hydraulically balanced valve according to claim 2 is characterized in that, described path section (316) is a shoulder hole; Described plugging part (313) cooperates with the step surface place shutoff that described path section (316) is joined with the step surface place or the described big footpath section (315) of described path section (316).
4. according to each described hydraulically balanced valve of claim 1 to 3, it is characterized in that the number of described throttling groove (3131) is four, and circumferentially evenly distributing along described plugging part (313).
5. hydraulically balanced valve according to claim 4 is characterized in that, described elastic member is helical spring (311), and described plugging part (313) connects guide rod (312), and described guide rod (312) inserts in the helical cavity of described helical spring (311).
6. according to each described hydraulically balanced valve of claim 1 to 3, it is characterized in that also be provided with the passage of the described big footpath of direct connection section (315) and described cavity volume (C) on the described application valve cover (3), described passage is provided with fixedly damping; Also be provided with relief valve (24) on the described equilibrium valve, the filler opening of described relief valve (24) is communicated with described cavity volume (C), and the oil outlet of described relief valve (24) is communicated with return opening.
7. hydraulically balanced valve according to claim 6, it is characterized in that, described passage comprises the radially oil pocket (B1) that is communicated with described big footpath section (315), with the axial passage (B2) that is communicated with described radially oil pocket (B1) and described cavity volume (C), described fixedly damping comprises first damping (34) and second damping (35), and described first damping (34) and described second damping (35) are arranged at respectively in described radially oil pocket (B1) and the described axial passage (B2).
8. hydraulically balanced valve according to claim 7 is characterized in that, described relief valve (24) is arranged on the described application valve cover (3).
9. hydraulically balanced valve according to claim 8, it is characterized in that, described control spool (22) is provided with the damping cavity that is communicated with described control spool (22) left side described cavity volume (C) and right side spring chamber, be provided with the 3rd damping (36) in the described damping cavity, and described spring chamber is communicated with the leakage hydraulic fluid port.
10. crane hydraulic system, comprise hydraulic actuator and Hydraulic power units, described Hydraulic power units to the path of described hydraulic actuator is provided with hydraulically balanced valve, it is characterized in that described hydraulically balanced valve is each described hydraulically balanced valve of claim 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011100982139A CN102261354A (en) | 2011-04-19 | 2011-04-19 | Crane hydraulic system and hydraulic balance valve thereof |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011100982139A CN102261354A (en) | 2011-04-19 | 2011-04-19 | Crane hydraulic system and hydraulic balance valve thereof |
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| CN102261354A true CN102261354A (en) | 2011-11-30 |
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| CN2011100982139A Pending CN102261354A (en) | 2011-04-19 | 2011-04-19 | Crane hydraulic system and hydraulic balance valve thereof |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102889261A (en) * | 2012-10-15 | 2013-01-23 | 常德中联重科液压有限公司 | Balancing valve, hydraulic cylinder telescoping control loop and hydraulic device |
| CN103498824A (en) * | 2013-10-14 | 2014-01-08 | 徐州重型机械有限公司 | Balance valve device |
| CN103727245A (en) * | 2013-12-23 | 2014-04-16 | 三一汽车起重机械有限公司 | Hydraulic valve, hydraulic system and engineering machinery |
| CN108223493A (en) * | 2018-03-01 | 2018-06-29 | 徐州重型机械有限公司 | A kind of variable balanced valve of pilot ratio |
| CN110848196A (en) * | 2019-11-28 | 2020-02-28 | 河南航天液压气动技术有限公司 | Hydraulic control valve |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101734566A (en) * | 2008-11-25 | 2010-06-16 | 徐州重型机械有限公司 | Crane |
| CN101852222A (en) * | 2009-03-31 | 2010-10-06 | 徐州重型机械有限公司 | Balanced valve and crane using same |
| CN202040137U (en) * | 2011-04-19 | 2011-11-16 | 徐州重型机械有限公司 | Crane hydraulic system and hydraulic balance valve thereof |
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2011
- 2011-04-19 CN CN2011100982139A patent/CN102261354A/en active Pending
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101734566A (en) * | 2008-11-25 | 2010-06-16 | 徐州重型机械有限公司 | Crane |
| CN101852222A (en) * | 2009-03-31 | 2010-10-06 | 徐州重型机械有限公司 | Balanced valve and crane using same |
| CN202040137U (en) * | 2011-04-19 | 2011-11-16 | 徐州重型机械有限公司 | Crane hydraulic system and hydraulic balance valve thereof |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102889261A (en) * | 2012-10-15 | 2013-01-23 | 常德中联重科液压有限公司 | Balancing valve, hydraulic cylinder telescoping control loop and hydraulic device |
| CN102889261B (en) * | 2012-10-15 | 2015-02-04 | 常德中联重科液压有限公司 | Balancing valve, hydraulic cylinder telescoping control loop and hydraulic device |
| CN103498824A (en) * | 2013-10-14 | 2014-01-08 | 徐州重型机械有限公司 | Balance valve device |
| CN103498824B (en) * | 2013-10-14 | 2015-11-25 | 徐州重型机械有限公司 | A kind of balancing valve apparatus |
| CN103727245A (en) * | 2013-12-23 | 2014-04-16 | 三一汽车起重机械有限公司 | Hydraulic valve, hydraulic system and engineering machinery |
| CN103727245B (en) * | 2013-12-23 | 2016-01-20 | 三一汽车起重机械有限公司 | Hydrovalve, hydraulic system and engineering machinery |
| CN108223493A (en) * | 2018-03-01 | 2018-06-29 | 徐州重型机械有限公司 | A kind of variable balanced valve of pilot ratio |
| CN110848196A (en) * | 2019-11-28 | 2020-02-28 | 河南航天液压气动技术有限公司 | Hydraulic control valve |
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Application publication date: 20111130 |