CN102330714B - Load feedback control valve - Google Patents
Load feedback control valve Download PDFInfo
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- CN102330714B CN102330714B CN 201110317280 CN201110317280A CN102330714B CN 102330714 B CN102330714 B CN 102330714B CN 201110317280 CN201110317280 CN 201110317280 CN 201110317280 A CN201110317280 A CN 201110317280A CN 102330714 B CN102330714 B CN 102330714B
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- control valve
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Abstract
The invention discloses a load feedback control valve, which comprises a valve body (1) and a flow control valve core (2). The valve body (1) comprises a load feedback channel (11), an oil supply channel (12) and a diversion channel (13) connected near the oil supply channel (12); the flow control valve core (2) is arranged in the diversion channel (13); a control cavity (14) for controlling the movement of the flow control valve core (2) is arranged in the diversion channel (13); the load feedback channel (11) is communicated with the control cavity (14), wherein a first damper (3) and a one-way valve (4) connected in parallel with the first damper (3) are connected in series to the load feedback channel (11); and the one-way valve (4) is used for allowing oil liquid to flow out of the control cavity (14). By adoption of the technical scheme, the load feedback control valve can ensure the stability of the flow control valve core during opening and closing, so that the impact on a system is reduced.
Description
Technical field
The present invention relates to the hydrovalve field, particularly, relate to a kind of load feedback control valve.
Background technique
In the hydraulic control system that adopts metering pump, metering pump can provide hydraulic oil to actuator by load feedback control valve, with control actuator action, and the flow of the hydraulic oil that provides to actuator of the pressure control by load feedback passage feedback.Specifically, existing load feedback control valve generally includes valve body and flow control spool, described valve body has load feedback passage, oil supply gallery and the other split channel that is connected on this oil supply gallery, described flow control spool is arranged in the described split channel, and has the control chamber that the described flow control spool of control moves in the described split channel, described load feedback passage is communicated with described control chamber, is serially connected with damper on the described load feedback passage.
The hydraulic oil of metering pump output flows into from the oil supply gallery of load feedback control valve, and a part of hydraulic oil flows back to fuel tank through split channel, and remaining hydraulic oil offers actuator after the outlet of oil supply gallery is flowed out.With hydraulic oil in the control chamber of load feedback channel connection according to the variation of load so that flow control spool is correspondingly mobile, thereby correspondingly control the flow that flows back to the hydraulic oil of fuel tank from split channel, and then control offers the flow of the hydraulic oil of actuator.The damper that is serially connected on the load feedback passage is used for the hydraulic oil change in flow between load feedback passage and the control chamber is cushioned, thereby so that the motion of flow control spool is steady, to alleviate the impact to whole hydraulic system.And in existing load feedback control valve, the damping value of damper is usually fixing, can't take into account flow control spool stationarity in the opening and closing process.For example, if the damping value of damper is high, in the time of then in main valve stem returns fast, pressure in the load feedback passage raises fast, need to make the flow control spool fast moving and the interior flow of the high split channel of Quick, and this moment damper meeting of high damping value so that the interior flow velocity of split channel can't raise fast, thereby cause system shock; If the damping value of damper is low, then when main valve stem is opened fast, pressure in the load feedback passage raises fast, the damper of low resistance value can make the flow control valve fast moving and the interior flow of fast reducing split channel, and this moment actuator from stopping to rapid movement needing an accelerating process, thereby also can cause system shock.
Summary of the invention
The purpose of this invention is to provide a kind of load feedback control valve, this load feedback control valve can be taken into account flow control spool stationarity in the opening and closing process, thereby reduces system shock.
To achieve these goals, the invention provides a kind of load feedback control valve, this control valve comprises valve body and flow control spool, described valve body has the load feedback passage, oil supply gallery and the other split channel that is connected on this oil supply gallery, described flow control spool is arranged in the described split channel, and has the control chamber that the described flow control spool of control moves in the described split channel, described load feedback passage is communicated with described control chamber, wherein, be serially connected with the first damper and the one-way valve in parallel with this first damper on the described load feedback passage, this one-way valve allows fluid to flow out from described control chamber.
Preferably, described the first damper and one-way valve are integrated in the valve piece.
Preferably, described the first damper is the thin-walled throttle orifice.
Preferably, described flow control spool is piston valve core, comprises head and the bar section that is connected with this head, and described head is arranged in the described control chamber, and described bar section extends towards described oil supply gallery.
Preferably, be provided with the spring of pre-pressing in the described control chamber, this spring action is on the head of described flow control spool.
Preferably, be formed with chamber between the inwall of described split channel and the described flow control spool, this chamber and described load feedback channel connection.
Preferably, the contiguous described control chamber of described chamber.
Preferably, described chamber is by the second damper and described load feedback channel connection.
Preferably, described the second damper is the thin-walled throttle orifice.
Preferably, described load feedback control valve also comprises main valve, and the oil-feed port of this main valve is communicated with the outlet of described oil supply gallery.
Preferably, described main valve is throttled directional valve.
Preferably, described load feedback passage is communicated with the load feedback chamber of described throttled directional valve.
Pass through technique scheme, since on the load feedback passage except being serially connected with the first damper, also be serially connected with the one-way valve in parallel with the first damper, this one-way valve allows fluid to flow out from described control chamber, therefore, even the damping value of the first damper is higher, when actuator need to stop fast, pressure in the load feedback passage raises fast, thereby this moment one-way valve opens permissible flow control spool fast moving and flow in the high split channel of Quick, thereby can so that actuator stop fast and can not cause system shock.Therefore can take into account flow control spool stationarity in the opening and closing process, thereby reduce system shock.
Other features and advantages of the present invention will partly be described in detail in embodiment subsequently.
Description of drawings
Accompanying drawing is to be used to provide a further understanding of the present invention, and consists of the part of specification, is used from explanation the present invention with following embodiment one, but is not construed as limiting the invention.In the accompanying drawings:
Fig. 1 is the structural representation according to the load feedback control valve of one embodiment of the present invention;
Fig. 2 is the schematic block diagram of load feedback control valve as shown in Figure 1.
Description of reference numerals
Embodiment
Below in conjunction with accompanying drawing the specific embodiment of the present invention is elaborated.Should be understood that embodiment described herein only is used for description and interpretation the present invention, is not limited to the present invention.
As depicted in figs. 1 and 2, one embodiment of the present invention provide a kind of load feedback control valve, this control valve comprises valve body 1 and flow control spool 2, described valve body 1 has load feedback passage 11, oil supply gallery 12 and the other split channel 13 that is connected on this oil supply gallery 12, described flow control spool 2 is arranged in the described split channel 13, and has the control chamber 14 that the described flow control spool 2 of control moves in the described split channel 13, described load feedback passage 11 is communicated with described control chamber 14, be serially connected with the first damper 3 on the described load feedback passage 11, wherein, also be serially connected with the one-way valve 4 in parallel with the first damper 3 on the described load feedback passage 11, this one-way valve 4 allows fluid to flow out from described control chamber 14.
Pass through technique scheme, since on the load feedback passage 11 except being serially connected with the first damper, also be serially connected with the one-way valve 4 in parallel with the first damper 3, this one-way valve 4 allows fluid to flow out from described control chamber 14, therefore, even the damping value of the first damper 3 is higher, when actuator 7 need to stop fast, pressure in the load feedback passage 11 raises fast, thereby one-way valve 4 overcame cracking pressure and opened permissible flow control spool 2 fast moving and flow in the high split channel 13 of Quick this moment, thus can so that actuator 7 stop fast and can not cause system shock.Therefore can take into account flow control spool 2 stationarity in the opening and closing process, thereby reduce system shock
The first damper 3 and one-way valve 4 can be separate parts, and preferably, the first damper 3 and one-way valve 4 are integrated in the valve piece 34, thus easy disassembly.Described the first damper 3 can be various types of parts that damping can be provided, and for example can be throttle orifice, is preferably the thin-walled throttle orifice, thereby can reduces the temperature of hydraulic oil to the impact of damping value.
Described flow control spool 2 can adopt various suitable shapes and set-up mode, for example can be the sliding valve style spool.As a kind of simple and effective mode of execution, as shown in Figure 1, described flow control spool 2 is piston valve core, comprises head 21 and the bar section 22 that is connected with this head 21, described head 21 is arranged in the described control chamber 14, and described bar section 22 extends towards described oil supply gallery 12.
As shown in Figure 1, be provided with the spring 16 of pre-pressing in the described control chamber 14.This spring 16 can act on the head 21 of described flow control spool 2.Thereby the pressure of the biasing force of spring 16 and load feedback passage 11 consists of the pressure in the control chamber 14 jointly, and the difference of the pressure in the pressure in the control chamber 14 and the oil supply gallery 12 has consisted of the power that flow control spool 2 moves that drives.
Because the frequent movement of flow control spool 2 split channel 13 in can cause the wearing and tearing of the inwall of flow control spool 2 and split channel 13, cause the interior hydraulic fluid leak of control chamber 14, thereby so that flow control spool 2 can't accurately move.Therefore preferably, as shown in Figure 1, the inwall of described split channel 13 and described stating are formed with chamber 15 between the flow control spool 2, and this chamber 15 is communicated with described load feedback passage 11.Thereby, go out from control chamber 14 internal leakages with blocking-up hydraulic oil at chamber 15 interior build-up pressures by load feedback passage 11.Preferably, chamber 15 is arranged on the position of contiguous control chamber 14, thereby more effectively prevents the leakage of control chamber 14 interior hydraulic oil.In mode of execution as shown in Figure 1, chamber 15 is arranged between the bar section 22 of the inwall of split channel 13 and flow control spool 2, and certainly, if adopt the flow control spool 2 of other type, the position of chamber 15 can correspondingly be arranged.
Because the buffer function of the first damper 3, when load changes rapidly, pressure in the load feedback passage 11 can immediately not feed back in the control chamber 14, that is to say, the variation of the pressure in the control chamber 14 and the variation of load feedback passage 11 internal pressures are not Complete Synchronizations, but certain hysteresis is arranged.Therefore, more preferably, as shown in Figure 1, described chamber 15 is communicated with described load feedback passage 11 by the second damper 5.Thereby the second damper 5 can be offset the hysteresis effect that produces because of the first damper 3, so that the pressure in the chamber 15 as best one can near the pressure in the control chamber 14, plays the effect of blocking-up control chamber 14 interior hydraulic fluid leaks better.Similarly, the second damper 5 also is preferably the thin-walled throttle orifice, thereby reduces the temperature of hydraulic oil to the impact of damping value.
Above-mentioned load feedback control valve goes for the various valves that need to control by load feedback output flow, can integrate the formation combination brake switch and proporting with various types of main valves.That is to say that as depicted in figs. 1 and 2, described load feedback control valve can also comprise main valve 6, the oil-feed port 61 of this main valve 6 is communicated with the outlet of described oil supply gallery 12.In embodiment as depicted in figs. 1 and 2, main valve 6 is throttled directional valve.At this moment, described load feedback passage 11 can be communicated with the load feedback chamber of described throttled directional valve.Certainly, main valve 6 also can be the valve of other types.
About the more specifically structure of valve body 1, flow control spool 2 and main valve 6 is well known in the art, therefore repeat no more.
The mode of execution of the below take main valve illustrated in figures 1 and 26 as throttled directional valve is example, and the working principle of this load feedback control valve is described simply.
In Fig. 1 and Fig. 2, P and T represent respectively oil-feed port and the return opening of load feedback control valve, are communicated with pump and fuel tank respectively, and A and B represent two actuator ports of load feedback control valve, can be respectively and the 7(of actuator for example oil cylinder, motor) be connected.
When pump no-output or pump export the P mouth to and main valve stem 62 when being in a left side or limit on the right-right-hand limit position, flow control spool 2 under the effect of spring 31 and so that split channel 13 close, POF is all supplied with actuator 7 under this state, and flow control spool 2 is without regulatory function.
When pump exports the P mouth to and main valve stem 62 when mediating, P mouth pressure (being the pressure in the oil supply gallery 12) overcomes the power of the spring 16 in the control chamber 14 and makes flow control spool 2 move to full-gear, under this state, POF all flows back to fuel tank through split channel 13 from the T3 mouth that is communicated with oil return inlet T shown in Figure 1, and flow control spool 2 is without regulatory function.
When pump export the P mouth to and main valve stem 62 be in throttle position (main valve stem 62 be in stroke 1/5 to 4/5 interval in) time, produce chock pressure difference on the restriction of main valve stem 62, the power that this pressure reduction overcomes spring 16 moves flow control spool 2, thereby so that split channel 13 is in semi-open state, a POF part is through main valve 6 pushing executing mechanisms 7 under this state; The remaining part flow flows back to fuel tank through split channel 13, and flow control spool 2 has regulatory function.Under this state, the variation of the induced pressure PL of actuator 7 is to comprise in parallel the first damper 3 and one-way valve 4 by valve piece 34() transfer to control chamber 14, when induced pressure PL amplitude of variation is little, the variation of pressure is transmitted by the first damper 3, less by the flow of the first damper 3 turnover control chambers 14 in short time, the amount of movement of three-way flowrate spool is little, and is also less through the variation of three-way flowrate spool oil drain quantity, substantially constant thereby assurance offers the flow of actuator 7.When induced pressure PL amplitude of variation is larger, be divided into boost, two kinds of situations of step-down, when boosting, one-way valve 4 is closed, so the variation of pressure still transmits by the first damper 3, and the amplitude of boosting is weakened; During step-down, when Amplitude of Hypotensive during greater than one-way valve 4 cracking pressure, one-way valve 4 is opened and the fluid in the control chamber 14 is flowed out fast, pressure in the control chamber 14 also fast approaching is the cracking pressure of one-way valve 4 in induced pressure PL but a little more than induced pressure PL(difference), when being step-down, because the effect of one-way valve 4 cracking pressure values reduces Amplitude of Hypotensive, the variation that namely always makes load at this state lower valve block 34 weakens the impact of system, and system is tended towards stability.
When main valve stem 62 during from middle position fast transition to left (right side) limit position, induced pressure PL(is the pressure in the load feedback passage 11) by 0 pressure that rises in the oil supply gallery 12, hydraulic oil slowly enters control chamber 14 under the heavy damping effect of the first damper 3, so that flow control spool 2 slowly moves so that split channel 13 slowly closings, namely the oil drain quantity through split channel 13 has a process that progressively reduces, thereby makes actuator 7 that a starting time be arranged and avoid impacting.
When main valve stem 62 from left (right side) limit position fast transition during to the neutral position, induced pressure PL(is the pressure in the load feedback passage 11) by the Pressure Drop to 0 in the oil supply gallery 12, because one-way valve 4 is opened so that the hydraulic oil in the control chamber 14 discharge fast, thereby so that split channel 13 is opened fast, namely the oil drain quantity through split channel 13 adds ambassador's system decompression fast, thus the system shock of avoiding system to cause because of improper maneuver.
Below describe by reference to the accompanying drawings preferred implementation of the present invention in detail; but; the present invention is not limited to the detail in the above-mentioned mode of execution; in technical conceive scope of the present invention; can carry out multiple simple variant to technological scheme of the present invention, these simple variant all belong to protection scope of the present invention.
Need to prove that in addition each the concrete technical characteristics described in above-mentioned embodiment in reconcilable situation, can make up by any suitable mode.For fear of unnecessary repetition, the present invention is to the no longer separately explanation of various possible compound modes.
In addition, also can carry out combination in any between the various mode of execution of the present invention, as long as it is without prejudice to thought of the present invention, it should be considered as content disclosed in this invention equally.
Claims (12)
1. load feedback control valve, this control valve comprises valve body (1) and flow control spool (2), described valve body (1) has load feedback passage (11), oil supply gallery (12) and side are connected on the split channel (13) on this oil supply gallery (12), described flow control spool (2) is arranged in the described split channel (13), and has the mobile control chamber (14) of the described flow control spool of control (2) in the described split channel (13), described load feedback passage (11) is communicated with described control chamber (14), it is characterized in that, be serially connected with the first damper (3) and the one-way valve (4) in parallel with this first damper (3) on the described load feedback passage (11), this one-way valve (4) allows fluid to flow out from described control chamber (14).
2. load feedback control valve according to claim 1 is characterized in that, described the first damper (3) and one-way valve (4) are integrated in the valve piece (34).
3. load feedback control valve according to claim 1 is characterized in that, described the first damper (3) is the thin-walled throttle orifice.
4. load feedback control valve according to claim 1, it is characterized in that, described flow control spool (2) is piston valve core, comprise head (21) and the bar section (22) that is connected with this head (21), described head (21) is arranged in the described control chamber (14), and described bar section (22) extends towards described oil supply gallery (12).
5. load feedback control valve according to claim 4 is characterized in that, is provided with the spring (16) of pre-pressing in the described control chamber (14), and this spring (16) acts on the head (21) of described flow control spool (2).
6. load feedback control valve according to claim 1 is characterized in that, is formed with chamber (15) between the inwall of described split channel (13) and the described flow control spool (2), and this chamber (15) is communicated with described load feedback passage (11).
7. load feedback control valve according to claim 6 is characterized in that, the contiguous described control chamber (14) of described chamber (15).
8. load feedback control valve according to claim 6 is characterized in that, described chamber (15) is communicated with described load feedback passage (11) by the second damper (5).
9. load feedback control valve according to claim 8 is characterized in that, described the second damper (5) is the thin-walled throttle orifice.
10. load feedback control valve according to claim 1 is characterized in that, described load feedback control valve also comprises main valve (6), and the oil-feed port (61) of this main valve (6) is communicated with the outlet of described oil supply gallery (12).
11. load feedback control valve according to claim 10 is characterized in that, described main valve (6) is throttled directional valve.
12. load feedback control valve according to claim 11 is characterized in that, described load feedback passage (11) is communicated with the load feedback chamber of described throttled directional valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201110317280 CN102330714B (en) | 2011-10-18 | 2011-10-18 | Load feedback control valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201110317280 CN102330714B (en) | 2011-10-18 | 2011-10-18 | Load feedback control valve |
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| Publication Number | Publication Date |
|---|---|
| CN102330714A CN102330714A (en) | 2012-01-25 |
| CN102330714B true CN102330714B (en) | 2013-03-13 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN 201110317280 Active CN102330714B (en) | 2011-10-18 | 2011-10-18 | Load feedback control valve |
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| CN (1) | CN102330714B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107795279A (en) * | 2017-12-06 | 2018-03-13 | 徐工集团工程机械有限公司 | Trepan and engineering truck |
| CN112555213B (en) * | 2020-11-20 | 2023-04-11 | 常德中联重科液压有限公司 | Hydraulic control loop, valve group unit and engineering machinery |
| CN113915188B (en) * | 2021-10-18 | 2024-05-07 | 山东泰丰智能控制股份有限公司 | Self-adaptive hydraulic control system |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4362087A (en) * | 1981-03-26 | 1982-12-07 | Tadeusz Budzich | Fully compensated fluid control valve |
| DE3141143A1 (en) * | 1981-10-16 | 1983-04-28 | Robert Bosch Gmbh, 7000 Stuttgart | Hydraulic control device |
| JP3658434B2 (en) * | 1994-09-30 | 2005-06-08 | 豊興工業株式会社 | Liquid control device |
| CN2890448Y (en) * | 2005-12-08 | 2007-04-18 | 常德信诚液压有限公司 | Hydraulic combined control valve |
| CN202251197U (en) * | 2011-10-18 | 2012-05-30 | 常德中联重科液压有限公司 | Loading feedback control valve |
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| CN102330714A (en) | 2012-01-25 |
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