CN102269189B - hydraulic control circuit - Google Patents
hydraulic control circuit Download PDFInfo
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- CN102269189B CN102269189B CN 201110185596 CN201110185596A CN102269189B CN 102269189 B CN102269189 B CN 102269189B CN 201110185596 CN201110185596 CN 201110185596 CN 201110185596 A CN201110185596 A CN 201110185596A CN 102269189 B CN102269189 B CN 102269189B
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- 230000003139 buffering effect Effects 0.000 claims description 138
- 239000010720 hydraulic oil Substances 0.000 claims description 97
- 239000003921 oil Substances 0.000 claims description 48
- 238000013016 damping Methods 0.000 claims description 23
- 230000000694 effects Effects 0.000 abstract description 20
- 239000002828 fuel tank Substances 0.000 description 13
- 239000007788 liquid Substances 0.000 description 11
- 230000003247 decreasing effect Effects 0.000 description 10
- 238000000034 method Methods 0.000 description 10
- 230000009471 action Effects 0.000 description 6
- 230000008569 process Effects 0.000 description 6
- 230000033001 locomotion Effects 0.000 description 5
- 238000001914 filtration Methods 0.000 description 3
- 239000012530 fluid Substances 0.000 description 3
- 230000002411 adverse Effects 0.000 description 2
- 230000002950 deficient Effects 0.000 description 2
- 230000007935 neutral effect Effects 0.000 description 2
- 230000035939 shock Effects 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000011176 pooling Methods 0.000 description 1
- 239000012224 working solution Substances 0.000 description 1
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Abstract
The invention discloses a hydraulic control loop, which comprises an actuating element and a buffer loop connected with the actuating element in parallel, wherein the buffer loop comprises an overflow valve and a buffer control valve connected with the overflow valve in series, when the overflow valve is not communicated, a valve core of the buffer control valve is in an initial position, a valve port of the buffer control valve is opened, when the overflow valve is communicated and the valve core of the buffer control valve is in a limit position, the flow area of the valve port of the buffer control valve is smaller than that when the valve port is opened and is not completely closed, so that a proper buffer effect is still maintained.
Description
Technical field
The present invention relates to the hydraulic control field, particularly, relate to a kind of hydraulic control circuit with buffer loop.
Background technique
In Hydraulic Power Transmission System, Fig. 1 and Fig. 2 are a kind of traditional hydraulic control circuits.As depicted in figs. 1 and 2, this hydraulic control circuit comprises position control valve 10 and the executive component 11(such as the oil hydraulic motor that link to each other with this direction control valve 10), described position control valve 10 comprises the bypass throttle loop with bypass entrance P ' and bypass outlet T ', wherein, bypass entrance P ' communicate with oil inlet P (being oil inlet P and the bypass entrance P ' that the working solution force feed of oil hydraulic pump can be supplied to position control valve 10), bypass outlet T ' communicates with fuel tank, and the passage section in described bypass throttle loop changes with the aperture of position control valve 10.
Figure 1 shows that the working state of described hydraulic control circuit when position control valve 10 is in meta, under this state, the actuator port of position control valve 10 (A mouth and B mouth), oil inlet P and oil return inlet T are all ended, and bypass entrance P ' and bypass outlet T ' connect, and bypass throttle loop (basically) do not produce throttling action to the fluid of bypass entrance P ' and the bypass outlet T ' that flows through.At this moment, executive component 11 is failure to actuate, and the hydraulic oil that comes from the oil hydraulic pump (not shown) flows back to fuel tank by bypass entrance P ' and bypass outlet T '.
When for example position control valve 10 moves to left position shown in Figure 2 from meta shown in Figure 1, the aperture of position control valve 10 increases gradually, oil inlet P communicates with the A mouth, the B mouth communicates with oil return inlet T, and the passage section in the formed bypass throttle of bypass entrance P ' and bypass outlet T ' loop reduces gradually simultaneously.At this moment, the major part that comes from the hydraulic oil of oil hydraulic pump flow through successively oil inlet P, A mouth, through executive component 11 and to after this executive component acting, again from the B mouth through oil return inlet T and flow back to fuel tank.And the hydraulic oil fraction that comes from oil hydraulic pump bypass entrance P ' and the bypass outlet T ' that flows through flows back to fuel tank through after the throttling action.
Yet, the defective of this hydraulic control circuit is, in the working procedure of executive component 11 (especially executive component 11 start and during braking), the load that executive component 11 bears often changes, and in the unexpected or rapid variation of this load meeting appearance of some occasion (running into suddenly larger resistance such as executive component 11), thereby cause the pressure of the hydraulic oil of executive component 11 a certain sides sharply to change (as raising).This can produce serious adverse effect to the stability of a system and reliability.
Therefore, for the situation that system load in the hydraulic control circuit changes suddenly, for the pressure variation of hydraulic oil in the buffering hydraulic control loop, to avoid the adverse effect to hydraulic system, developed a kind of hydraulic control circuit that comprises buffer loop at present.
For example, Figure 3 shows that buffer loop part in traditional hydraulic control circuit.As shown in Figure 3, described buffer loop 100 ' comprising: the first relief valve 51 and the second relief valve 52, the entrance of this first relief valve 51 is connected in described first side of described executive component 11, and the entrance of described the second relief valve 52 is connected in described second side of described executive component 11; The first one-way valve 61 and the second one-way valve 62, the outlet of this first one-way valve 61 is connected in described first side of described executive component 11, the outlet of described the second one-way valve 62 is connected in described second side of described executive component 11, and the entrance of described the first one-way valve 61 and the second one-way valve 62 communicates with each other; With buffering control valve 60 ', the entrance of this buffering control valve 60 ' is connected in the outlet of described the first relief valve 51 and the outlet of the second relief valve 52, and the outlet of described buffering control valve 60 ' is connected on the pipeline between the entrance of the entrance of described the first one-way valve 61 and the second one-way valve 62.
When the pressure of the hydraulic oil of the first side of executive component 11 surpasses predetermined value, the first relief valve 51 is connected, thereby the hydraulic oil that allows this first side flows to the entrance of buffering control valve 60 ', and cushion control valve 60 ' and be in meta this moment, and buffering control valve 60 ' is communicated with.Then, this hydraulic oil flows out from the outlet of buffering control valve 60 ' under the control of this buffering control valve 60 ' again, flow to the second side of executive component 11 and flow back to fuel tank through corresponding one-way valve (i.e. the second one-way valve 62), so a part of hydraulic oil flows back to fuel tank by buffer loop 100 ', avoid it all to supply with executive component 11, thereby play buffer function.Simultaneously, the spool that the hydraulic oil of the first side of executive component 11 act as control oil promotion buffering control valve 60 ' is moved to the left, and the hydraulic oil of the buffering of flowing through control valve 60 ' reduces gradually, when spool moves on to left position, the buffering control valve 60 ' by, hydraulic oil can't continue to flow back to fuel tank.In addition, when the pressure decreased of the hydraulic oil of the first side was following to predetermined value, then the first relief valve 51 cut out, thereby no longer allowed the hydraulic oil of the first side of executive component 11 to flow to the second side of executive component 11 by buffer loop 100 '.
When the pressure of the hydraulic oil of the second side of executive component 11 surpasses predetermined value (at this moment, the second side is the high pressure side), then correspondingly the second relief valve 52 is connected, thereby allows the hydraulic oil of this second side to flow to the first side by cushioning control valve 60 '.And when the pressure decreased of the hydraulic oil of the second side was following to predetermined value, the second relief valve 52 cut out.The situation that the pressure of the hydraulic oil of the first side of this process and above-mentioned executive component 11 surpasses predetermined value is similar, therefore is not described in detail.
Although the buffer loop in this traditional hydraulic control circuit can play buffering to a certain extent, but in running, its defective is, when the spool of buffering control valve 60 ' during at meta, the valve port opening of buffering control valve 60 ' is very large, allows the high pressure liquid force feed to pass through fast, and when the spool of buffering control valve 60 ' as the left position of limit position or right the time, then cushion the valve port of control valve 60 ' and close fully, can not continue to play pooling feature.Therefore, the effect of slowing down impact of traditional buffer loop is comparatively limited.
Summary of the invention
The purpose of this invention is to provide a kind of hydraulic control circuit that slows down preferably impact effect that has.
To achieve these goals, the invention provides a kind of hydraulic control circuit, this hydraulic control circuit comprises executive component and the buffer loop in parallel with this executive component, this buffer loop comprises relief valve and the buffering control valve that is connected in series with this relief valve, when described relief valve is disconnected, the spool of described buffering control valve is in initial position, the valve port of this buffering control valve is opened, it is characterized in that, connect and the spool of described buffering control valve when being in limit position the flow area the when flow area of the valve port of this buffering control valve is opened less than valve port and not exclusively closing at described relief valve.
Preferably, described relief valve comprises the first relief valve and the second relief valve, and the entrance of this first relief valve is connected in the first side of described executive component, and the entrance of described the second relief valve is connected in the second side of described executive component; Described buffering control valve is connected in series and is connected to directly or indirectly respectively the first side and second side of described executive component with described the first relief valve and the second relief valve.
Preferably, described buffering control valve has the first entrance, the second entrance and described outlet, the outlet of described the first relief valve is connected with the first entrance of described buffering control valve, the outlet of described the second relief valve is connected with the second entrance of described buffering control valve, wherein, when described the first relief valve and the equal access failure of the second relief valve, the spool of described buffering control valve is positioned at initial position, and described the first entrance, the second entrance and exit are connected; In described the first relief valve and the second relief valve one when connecting, the spool of described buffering control valve moves to corresponding limit position, thereby makes the hydraulic oil of the relief valve of connecting in flow through described the first relief valve and the second relief valve flow to described outlet through throttling.
Preferably, described buffering control valve comprises: buffering valve body, described the first entrance, the second entrance and outlet that this buffering valve body has cavity and communicates with this cavity; Slide core as the spool of described buffering control valve, this slide core has first end, the second end and the joint that is connected this first end and the second end, described slide core is arranged on movably in the described cavity and is limited with in this cavity between described first end and the second end side toward each other and around the through-flow chamber of described joint, this through-flow chamber communicates with described outlet, described the first entrance by be arranged on described first end on the side of the second end the first segment chute and be communicated with described through-flow chamber, described the second entrance can by be arranged on described the second end on the side of first end the second section chute and be communicated with described through-flow chamber, and the stroke L2 of described slide core is less than described first segment chute and the second section chute length L 1 along described slide core longitudinal direction.
Preferably, described buffering control valve is pilot operated directional control valve, described cavity also is divided into first control chamber adjacent with described first end and second control chamber adjacent with described the second end by described slide core, described the first control chamber is connected in described first side of described executive component by the first damping member, and described the second control chamber is connected in described second side of described executive component by the second damping member.
Preferably, described buffering control valve comprises the hydraulic control two position three-way valve, this hydraulic control two position three-way valve has the first entrance, the second entrance, control mouth and outlet, the first entrance of described hydraulic control two position three-way valve is connected in the outlet of described the first relief valve, the second entrance of described hydraulic control two position three-way valve is connected in the outlet of described the second relief valve, and the outlet of described hydraulic control two position three-way valve is connected to the first side and second side of executive component directly or indirectly; Described hydraulic control circuit also comprises shuttle valve, this shuttle valve has the first entrance, the second entrance and exit, the first entrance of described shuttle valve is connected in described first side of described executive component, the second entrance of described shuttle valve is connected in described second side of described executive component, the outlet of described shuttle valve is connected in the described control mouth of described hydraulic control two position three-way valve by the 3rd damping member, wherein, when described the first relief valve and the second relief valve are all disconnected, the spool of described hydraulic control two position three-way valve is positioned at initial position, described first entrance of described hydraulic control two position three-way valve, the second entrance and exit is connected; In described the first relief valve and the second relief valve one when connecting, the spool of described hydraulic control two position three-way valve moves to limit position, thereby the hydraulic oil that makes the relief valve of connecting in flow through described the first relief valve and the second relief valve flows to the outlet of described hydraulic control two position three-way valve through throttling.
Preferably, described buffer loop also comprises the first one-way valve and the second one-way valve, the outlet of this first one-way valve is connected in described first side of described executive component, the outlet of described the second one-way valve is connected in described second side of described executive component, and the entrance of described the first one-way valve and the second one-way valve communicates with each other; The outlet of described buffering control valve is connected on the pipeline between the entrance of the entrance of described the first one-way valve and the second one-way valve.
Preferably, described the first relief valve and for being integrated with the one-way valve of opening opposite direction and the first one-way overflow valve of relief valve, described the second relief valve is to be integrated with the one-way valve of opening opposite direction and the second one-way overflow valve of relief valve, and described buffering control valve is connected between this first one-way overflow valve and the second one-way overflow valve.
Preferably, described buffering control valve is three Twoway valvess of hydraulic control, three Twoway valvess of this hydraulic control have the first working hole and the second working hole and the first control mouth and the second control mouth, described first working hole of three Twoway valvess of described hydraulic control is connected in the outlet of described the first one-way overflow valve, the second working hole of three Twoway valvess of described hydraulic control is connected in the outlet of described the second one-way overflow valve, and the first control mouth of three Twoway valvess of described hydraulic control and the second control mouth are connected respectively to the first side and second side of described executive component; Wherein, when the relief valve of the relief valve of described the first one-way overflow valve and the second one-way overflow valve was all disconnected, the spool of three Twoway valvess of described hydraulic control was positioned at initial position, and described first working hole of described three Twoway valvess and the second working hole are connected; When the relief valve of an one-way overflow valve in described the first one-way overflow valve and the second one-way overflow valve is connected, the spool of three Twoway valvess of described hydraulic control moves to corresponding limit position, thereby makes the hydraulic oil of the relief valve by the one-way overflow valve connected in described the first one-way overflow valve and the second one-way overflow valve flow through the one-way valve of another one-way overflow valve in described the first one-way overflow valve and the second one-way overflow valve through the throttling of three Twoway valvess of described hydraulic control.
Preferably, described buffering control valve comprises the hydraulic control two position two-way valve, this hydraulic control two position two-way valve has the first working hole, the second working hole and control mouth, the first working hole of described hydraulic control two position two-way valve is connected in the outlet of described the first one-way overflow valve, and the second working hole of described hydraulic control two position two-way valve is connected in the outlet of described the second one-way overflow valve; Described hydraulic control circuit also comprises shuttle valve, this shuttle valve has the first entrance, the second entrance and exit, the first entrance of described shuttle valve is connected in described first side of described executive component, the second entrance of described shuttle valve is connected in described second side of described executive component, the outlet of described shuttle valve is connected in the described control mouth of described hydraulic control two position two-way valve by the 4th damping member, wherein, when the relief valve of the relief valve of described the first one-way overflow valve and the second one-way overflow valve is all disconnected, the spool of described hydraulic control two position two-way valve is positioned at initial position, and described first working hole of described hydraulic control two position two-way valve and the second working hole are connected; When the relief valve of any one-way overflow valve in described the first one-way overflow valve and the second one-way overflow valve is connected, the spool of described hydraulic control two position two-way valve moves to limit position, thereby makes the hydraulic oil of the relief valve by the one-way overflow valve connected in described the first one-way overflow valve and the second one-way overflow valve flow through the one-way valve of another one-way overflow valve in described the first one-way overflow valve and the second one-way overflow valve through the throttling of described hydraulic control two position two-way valve.
Preferably, described executive component is oil hydraulic motor, and this hydraulic control circuit is the revolution control loop.
Pass through technique scheme,, system load causes the unexpected variation of the pressure of hydraulic oil in the in-line of executive component of hydraulic control circuit if changing suddenly (especially start or during braking), then by comprising the buffer loop of relief valve and buffering control valve, the hydraulic oil of this overpressure can be directed in the lower oil circuit of pressure controllably, thereby realizes the buffering to hydraulic oil variation in the hydraulic control circuit.After buffer loop was connected, the spool of buffering control valve can moving along with buffering course.
In the buffer loop in traditional hydraulic control circuit, when the spool of buffering control valve reached the limit of the position, the valve port of this buffering control valve was closed fully, thereby finished buffer function.And in technological scheme provided by the present invention, what is more important, even if the spool of buffering control valve moves to limit position, flow area when the flow area of the valve port of this buffering control valve is opened less than valve port and not exclusively closing, thereby still allow hydraulic oil to flow to the relatively low oil circuit of pressure from the relatively high in-line of pressure, still maintaining suitable buffer function, thereby have with respect to traditional buffer loop and have better cushioning effect.
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 and Fig. 2 are the schematic representation of traditional hydraulic control circuit;
Fig. 3 is the schematic representation of traditional hydraulic control circuit;
Fig. 4 is the schematic representation according to the hydraulic control circuit of one embodiment of the present invention;
Fig. 5 is the schematic representation of the buffering control valve among Fig. 4;
Fig. 6 is the schematic representation of a kind of concrete structure of buffering control valve among Fig. 5;
Fig. 7 is the schematic representation according to the hydraulic control circuit of another embodiment of the present invention;
Fig. 8 is the schematic representation of buffering control valve among Fig. 7;
Fig. 9 and Figure 10 are respectively the schematic representation of the hydraulic control circuit of different mode of executions according to the present invention.
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 shown in Figure 4, hydraulic control circuit provided by the present invention comprises executive component 11.In addition, above-mentioned hydraulic control circuit can comprise that also position control valve 10(is as depicted in figs. 1 and 2), fuel tank (not shown) and oil hydraulic pump (not shown), described oil hydraulic pump is connected with described fuel tank and is connected with described executive component 11 by described position control valve 10.
According to technological scheme of the present invention, in above-mentioned hydraulic control circuit, also be designed with the buffer loop 100 in parallel with executive component 11, such as Fig. 4, Fig. 7, Fig. 9 and shown in Figure 10.Specifically, this buffer loop 100 comprises relief valve 51,52; 81,82 and with this relief valve 51,52; 81, the 82 buffering control valves 60,90,92 that are connected in series, the in-line of the executive component 11 of described hydraulic control circuit is by described relief valve 51,52; 81,82 be connected control valve 60,90,92 and be connected with the oil circuit of the executive component 11 of described hydraulic control circuit, thereby realize the in parallel of buffer loop 100 and executive component 11, at described relief valve 51,52; 81,82 when disconnecting, and described buffering control valve 60,90,92 spool are in initial position, and this buffering control valve 60,90,92 valve port are opened, wherein, and at described relief valve 51,52; 81,82 connect and described buffering control valve 60, when 90,92 spool is in limit position, the flow area the when flow area of this buffering control valve 60,90,92 valve port is opened less than valve port and not exclusively closing.
When executive component 11 normal operation, in hydraulic control circuit, the system liquid force feed enters the executive component 11 from the in-line of executive component 11, and after 11 actings of driving executive component, the oil circuit from executive component 11 flows back to fuel tank again.Therefore, in running, the pressure of hydraulic oil is relatively high in the in-line of executive component 11 usually, and the pressure of hydraulic oil is relatively low in the oil circuit of executive component 11.When system load changes suddenly (for example, when system's startup or braking, when perhaps the load of executive component 11 increases suddenly), unexpected increase also can occur in the pressure of hydraulic oil in the in-line of executive component 11.In this case, if the pressure of hydraulic oil surpasses predetermined pressure, the then relief valve in the buffer loop 51,52 in the in-line; 81,82 can be from being on-state by state-transition, so by with this relief valve 51,52; 81, the 82 buffering control valves 60,90 that connect, 92 and flow to controllably in the oil circuit of executive component 11, thus play the effect of shock absorbing.
Different from traditional hydraulic control circuit is, in technological scheme provided by the present invention, and when the pressure of hydraulic oil in the in-line of executive component 11 surpasses predetermined pressure, described relief valve 51,52; 81,82 connect, thereby the hydraulic oil of overpressure flows to buffering control valve 60,90,92 by the relief valve of connecting in the permission in-line, because cushion control valve 60,90 this moment, 92 spool is in the initial position that valve port is opened, thereby can flow to rapidly the oil circuit of executive component 11.Simultaneously, described buffering control valve 60,90,92 spool move to limit position from initial position, thereby the hydraulic oil of the buffering control valve of flowing through is controlled.When buffering control valve 60,90, when 92 spool is in limit position, the flow area the when flow area of this buffering control valve 60,90,92 valve port is opened less than valve port and not exclusively closing.Therefore, as long as relief valve 51,52; 81,82 not by, even if buffering control valve 60,90,92 spool reach the limit of the position, the excessive hydraulic oil of pressure still can flow in the oil circuit of pressure less by this buffer loop in the in-line of executive component 11, thereby obtains better cushioning effect.
For example, for the executive component of single-action piston cylinder, the in-line of single-action piston cylinder and oil circuit are normally constant.That is to say that the oil circuit that single-action piston cylinder links to each other with oil hydraulic pump is generally in-line, and the oil circuit that links to each other with oil cylinder is generally oil circuit.
But for the executive component of other types, the in-line of executive component and oil circuit then can be changed mutually, for example two-way ram cylinder or the oil hydraulic motor that can drive two sense of rotation.For example, in Fig. 4, Fig. 7, Fig. 9 and Figure 10 of this specification, executive component 11 is oil hydraulic motor, and wherein the A side can be in-line, and then the B side is oil circuit; Perhaps the B side can be in-line, and the A side is oil circuit.
Although mainly described explanation as an example of oil hydraulic motor example in the Figure of description of the present invention, technological scheme of the present invention is all applicable to the application of above-mentioned various executive components.
Because the application of double-acting hydraulic cylinder and oil hydraulic motor is more extensive, therefore, in the preferred case, when the pressure of the hydraulic oil of first side (A side) of described executive component 11 surpassed scheduled pressure value, this buffer loop 100 can allow the hydraulic oil of this first side to flow to controllably second side (B side) of described executive component 11.Here the first side of said executive component 11 and the second side only are used for the both sides of difference executive component 11, and wherein the first side can refer to any side of executive component 11, and the second side then refers to the opposite side relative with described the first side of executive component 11.In other words, when the first side was the oil-feed side of in-line, then the second side was the oil return side of oil circuit; When the first side was the oil return side of oil circuit, the second side was the oil-feed side of in-line.
Utilize this buffer loop 100, when the pressure of the hydraulic oil of the first side of executive component 11 is excessive, when namely surpassing scheduled pressure value, then in order to cushion the pressure of this larger hydraulic oil, allow the hydraulic oil of this first side to flow to controllably the opposite side (i.e. the second side) of executive component 11, thereby play the effect of buffering elevated pressures, avoid the safe operation of hydraulic control circuit is caused damage.Simultaneously, the implication of so-called " controllably " is that buffer loop can not always keep the first side of executive component 11 and being connected of the second side, but when executive component 11 certain side pressure surpass scheduled pressure value, buffer loop allows the first side and second side of executive component 11 to be connected, thereby part hydraulic oil is flowed between the first side and the second side by buffer loop 100, and after making elevated pressures drop to predetermined value, the first side and the second side with executive component 11 disconnects again, thereby makes executive component 11 have enough driving load capacity.
Therefore, utilize technological scheme provided by the present invention, if cause the unexpected variation of pressure of the hydraulic oil of executive component 11 a certain sides owing to the unexpected variation of system load, then by buffer loop 100 can be with the pressure of executive component 11 hydraulic oil of a higher side controllably be directed to the low side of pressure, thereby realize buffering that hydraulic fluid pressure in the hydraulic control circuit is changed.
As mentioned above, the buffering control valve 60 ' valve port when spool is in limit position in the buffer loop 100 ' of traditional hydraulic control circuit is closed fully.And in technological scheme provided by the present invention, even if the spool of buffering control valve 60 moves to limit position, the valve port of buffering control valve 60 is not to close fully, but remain with predetermined passage section, thereby still allow hydraulic oil from the relatively high effluent of pressure to the relatively low side of pressure, still to maintain suitable buffer function, therefore in movement process, also can play a role in filtering to pressure peak, have with respect to the better cushioning effect of traditional buffer loop.
Preferably, in order to control better the hydraulic oil of this buffer loop 100 of flowing through, such as Fig. 4, shown in Figure 7, described buffer loop 100 comprises: the first relief valve 51 and the second relief valve 52, the entrance of this first relief valve 51 is connected in described first side of described executive component 11, and the entrance of described the second relief valve 52 is connected in described second side of described executive component 11; Described buffering control valve 60 is connected in series with described the first relief valve 51 and the second relief valve 52 respectively, and is connected to directly or indirectly the first side and second side of executive component 11.
In order to be adapted to executive component 11 in the situation of both direction operation, described relief valve comprises the first relief valve 51 and the second relief valve 52, and be connected to the first side and second side of executive component 11, thereby when executive component 11 as the either side of in-line in the pressure of hydraulic oil when surpassing predetermined pressure, corresponding relief valve opens that (when the hydraulic fluid pressure of the first side surpassed predetermined pressure, the first relief valve 51 was opened; When the pressure of the hydraulic oil of the second side surpassed predetermined pressure, the second relief valve 52 was opened), then the excessive hydraulic oil of pressure flows in the opposite side as oil circuit by buffering control valve 60 again, thereby plays the effect that slows down impact.
As mentioned above, when the spool of buffering control valve 60 reaches the limit of the position, still allow hydraulic oil with relatively little traffic flow mistake, thereby obtain better cushioning effect.
Preferably, as shown in Figure 4 and Figure 5, described buffering control valve 60 has the first entrance 601, the second entrance 602 and described outlet 603, the outlet of described the first relief valve 51 is connected with the first entrance 601 of buffering control valve 60, the outlet of described the second relief valve 52 is connected with the second entrance 602 of described buffering control valve 60, wherein, when described the first relief valve 51 and the second relief valve 52 equal access failure, described buffering control valve 60 is positioned at initial position, described the first entrance 601, the second entrance 602 and export 603 and connect; In described the first relief valve 51 and the second relief valve 52 one when connecting, described buffering control valve 60 moves to corresponding limit position (spool that is buffering control valve 60 among Fig. 4 moves to left position or right position), thereby makes the hydraulic oil of the relief valve of connecting in flow through described the first relief valve 51 and the second relief valve 52 flow to described outlet 603 through throttling.
With reference to figure 4, the difference of buffer loop 100 ' mainly is to cushion principle and the structure of control valve 60 among the buffer loop 100 shown in Fig. 4 and Fig. 3.
As mentioned above, mode of execution for Fig. 3, when the hydraulic oil that surpasses scheduled pressure value when the pressure of the first side that for example comes from executive component 11 acts on the spool of buffering control valve 60 ' and makes spool be in left position, buffering control valve 60 ' disconnects fully, thereby no longer allows the hydraulic oil of the first side of executive component 11 to flow to the second side.
Yet, mode of execution for Fig. 4, when the high pressure liquid force feed of the first side that for example comes from executive component 11 makes the spool of buffering control valve 60 be positioned at right position, disconnect different fully from the buffering control valve 60 ' in the mode of execution of Fig. 3, in the mode of execution of Fig. 4, buffering control valve 60 still allows to flow through the hydraulic oil of the first relief valve 51 by this buffering control valve 60, thereby obtains better cushioning effect.Preferably, as shown in Figure 4 and Figure 5, when the spool of buffering control valve 60 is positioned at left position and right position, the first entrance 601 of buffering control valve 60 and export valve port between 603 and the second entrance 602 and the valve port that exports between 603 are not closed fully, but allow hydraulic oil to flow through corresponding valve port by throttling groove.
Mode of execution according to Fig. 4, because when the spool of buffering control valve 60 still has passage section in left position or during right limit position, allow hydraulic oil under throttling action, to flow through, therefore not only in startup and braking process, can cushion the impact of the elevated pressures of executive component 11 both sides hydraulic oil when executive component 11, can also cushion the compression shock that executive component 11 produces in running, thereby obtain than the better cushioning effect of buffer loop in traditional hydraulic control circuit.
Specifically, as shown in Figure 4, when the pressure of the hydraulic oil of the first side of executive component 11 surpasses predetermined value, the first relief valve 51 is connected, thereby the hydraulic oil that allows this first side flows to the entrance of buffering control valve 60, cushion control valve 60 and still be in initial position this moment, and buffering control valve 60 is communicated with.Then, this hydraulic oil flows out from the outlet of buffering control valve 60 under the control of this buffering control valve 60 again, and flow to the second side of executive component 11 and flow back to fuel tank, so a part of hydraulic oil flows back to fuel tank by buffer loop 100, avoid it all to supply with executive component 11, thereby play buffer function.Simultaneously, the spool that the hydraulic oil of the first side of executive component 11 act as control oil promotion buffering control valve 60 is moved to the left, the hydraulic oil of the buffering of flowing through control valve 60 reduces gradually, when spool moves on to left position, buffering control valve 60 still remains with the flow area that dwindles, thereby continue to allow a small amount of hydraulic oil to flow back to fuel tank, play buffer function.In addition, when the pressure decreased of the hydraulic oil of the first side was following to predetermined value, then the first relief valve 51 cut out, thereby no longer allowed the hydraulic oil of the first side of executive component 11 to flow to the second side of executive component 11 by buffer loop 100.
When the pressure of the hydraulic oil of the second side of executive component 11 surpasses predetermined value (at this moment, the second side is the high pressure side), then correspondingly the second relief valve 52 is connected, thereby allows the hydraulic oil of this second side to flow to the first side by buffering control valve 60.And when the pressure decreased of the hydraulic oil of the second side was following to predetermined value, the second relief valve 52 cut out.The situation that the pressure of the hydraulic oil of the first side of this process and above-mentioned executive component 11 surpasses predetermined value is similar, therefore is not described in detail.
The buffering control valve 60 that is used for the mode of execution of Fig. 4 can have the various structures form.Preferably, as shown in Figure 5 and Figure 6, described buffering control valve 60 comprises: buffering valve body 200, this buffering valve body 200 have cavity 201 and described the first entrance 601, the second entrance 602 that communicate with this cavity 201 and export 603; Slide core 604 as the spool of described buffering control valve 60, this slide core 604 has first end 605, the second end 606 and the joint 607 that is connected this first end and the second end, described slide core 604 is arranged on movably in the described cavity 201 and is limited with in this cavity 201 between described first end 605 and the second end 606 side toward each other and around the through-flow chamber 608 of described joint 607, this is through-flow, and chamber 608 communicates with described outlet 603, described the first entrance 601 by be arranged on described first end on the side of the second end first segment chute 611 and be communicated with described through-flow chamber 608, described the second entrance 602 can by be arranged on described the second end on the side of first end second section chute 612 and be communicated with described through-flow chamber 608, and the stroke L2 of described slide core 604 is less than described first segment chute 611 and second section chute 612 length L 1 along described slide core longitudinal direction.
As shown in Figure 6, the first entrance 601 of buffering control valve 60 is communicated with outlet 603 by first segment chute 611, through-flow chamber 608, and by first segment chute 611 realization throttling actions.Similarly, the second entrance 602 of buffering control valve 60 is communicated with outlet 603 by second section chute 612, through-flow chamber 608, and by second section chute 612 realization throttling actions.
In addition, in the concrete structure of buffering control valve 60 shown in Figure 6, the stroke L2(of described slide core 604 is namely from the neutral position of slide core 604 to the displacement distance of left position or right position) less than described first segment chute 611 and second section chute 612 length L 1 along described slide core longitudinal direction.Therefore, no matter when the slide core (being spool) of buffering control valve 60 during from middle position movement to left position or right position, first segment chute 611 and second section chute 612 can not sealed by slide core 604, but reserve part passage section still, thereby continue to allow hydraulic oil being subject to flowing through this buffering control valve 60 under the throttling action.Therefore, in system's running, not only can play a role in filtering to pressure peak, and by being supplied to executive component 11 less flows just can set up higher pressure.
The stroke L2 of slide core 604, first segment chute 611 and second section chute 612 along the length L 1 of described slide core longitudinal direction and the difference between L2 and the L1 usually according to concrete application operating mode and design alternative.Described first segment chute 611 and second section chute 612 can have one or more respectively.Preferably, described first segment chute 611 and second section chute 612 include many throttling grooves.
In addition, the structure that is applied to the buffering control valve 60 in the mode of execution of Fig. 4 is not limited to concrete structure shown in Figure 6.For example, although the buffering control valve 60 shown in Fig. 6 is hydraulic control valve, should cushion control valve 60 still can be for electrically-controlled valve or hand control valve etc., as long as can realize cushioning the above-mentioned functions of control valve 60.
Preferably, such as Fig. 4 and shown in Figure 6, described buffering control valve 60 is pilot operated directional control valve, described cavity 201 also is divided into first control chamber 613 adjacent with described first end 605 and second control chamber 614 adjacent with described the second end 606 by described slide core, described the first control chamber 613 is connected in described first side of described executive component 11 by the first damping member 615, and described the second control chamber 614 is connected in described second side of described executive component 11 by the second damping member 616.
According to this structure, for example when the pressure of the hydraulic oil of the first side of executive component 11 is higher than predetermined value, the first relief valve 51 can move and connect on the one hand, the high pressure liquid force feed of this first side can be by the first damping member 615(such as damping plug simultaneously) flow in the first control chamber 613, slide to the right thereby drive slide core 604, until the power that acts on the slide core 604 is in the equilibrium position again.When the pressure decreased of the hydraulic oil of the first side was following to predetermined value, then slide core 604 can return to the neutral position again.Hence one can see that, utilizes the buffering control valve 60 of pilot operated directional control valve can realize comparatively compact and succinct structure, thereby improve the reliability of hydraulic system.
Described the first damping member 615 and the second damping member 616 can be various damping plugs.
Except mode of execution shown in Figure 4, the present invention also provides multiple substitute mode.For example, as shown in Figure 7 and Figure 8, described buffering control valve 60 can comprise: hydraulic control two position three-way valve 69, this hydraulic control two position three-way valve 69 has the first entrance 621, the second entrance 622, control mouth 623 and exports 624, the first entrance 621 of described hydraulic control two position three-way valve is connected in the outlet of described the first relief valve 51, the second entrance 622 of described hydraulic control two position three-way valve is connected in the outlet of described the second relief valve 52, and the outlet 624 of described hydraulic control two position three-way valve is connected to the first side and second side of executive component 11 directly or indirectly; Described hydraulic control circuit also comprises shuttle valve 70, this shuttle valve has the first entrance 701, the second entrance 702 and outlet 703, the first entrance 701 of described shuttle valve is connected in described first side of described executive component 11, the second entrance 702 of described shuttle valve is connected in described second side of described executive component 11, the outlet 703 of described shuttle valve is connected in the described control mouth 623 of described hydraulic control two position three-way valve by the 3rd damping member 704, wherein, when described the first relief valve 51 and the second relief valve 52 are all disconnected, the spool of described hydraulic control two position three-way valve 69 is positioned at initial position (the right position shown in Fig. 7 and Fig. 8), at this initial position, described first entrance 621 of described hydraulic control two position three-way valve 69, the second entrance 622 and outlet 624 are connected; In described the first relief valve 51 and the second relief valve 52 one when connecting, the spool of described hydraulic control two position three-way valve 69 moves to limit position (shown in Fig. 7 and Fig. 8 left position), thereby makes the hydraulic oil of the relief valve of connecting in flow through described the first relief valve 51 and the second relief valve 52 flow to the outlet 624 of described hydraulic control two position three-way valve through throttling.
As shown in Figure 7 and Figure 8, shuttle valve 70 provides control signal to hydraulic control two position three-way valve 69.
For example when the pressure of the hydraulic oil of the first side of executive component 11 surpassed predetermined value, the first relief valve 51 was connected.Simultaneously, shuttle valve 70 with this high pressure liquid force feed through the 3rd damping member 704(such as damping plug) guide to hydraulic control two position three-way valve 69, thereby make the spool of hydraulic control two position three-way valve 69 move to limit position from initial position, the high pressure liquid force feed that allows to come from the first relief valve 51 flows to the second side of executive component 11 through the throttle effect of this hydraulic control two position three-way valve 69.When the pressure decreased of the hydraulic oil of the first side of executive component 11 is following to predetermined value, 51 cut-offs of the first relief valve, simultaneously hydraulic control two position three-way valve 69 returns to initial position from limit position.
As mentioned above, the described buffering control valve 60 that is connected in series with described the first relief valve 51 and the second relief valve 52 is connected to the first side and second side of described executive component 11 directly or indirectly.Specifically, the outlet of buffering control valve 60 can be directly connected in the first side and second side of executive component 11, perhaps, preferably, described buffer loop also comprises the first one-way valve 61 and the second one-way valve 62, the outlet of this first one-way valve 61 is connected in described first side of described executive component 11, and the outlet of described the second one-way valve 62 is connected in described second side of described executive component 11, and the entrance of described the first one-way valve 61 and the second one-way valve 62 communicates with each other; The outlet of described buffering control valve 60 is connected on the pipeline between the entrance of the entrance of described the first one-way valve 61 and the second one-way valve 62, such as Fig. 4 and shown in Figure 7.
In addition, as shown in Figure 9 and Figure 10, the hydraulic control circuit of other mode of executions is provided according to the present invention, wherein said the first relief valve 81 and for being integrated with the one-way valve of opening opposite direction and the first one-way overflow valve of relief valve, described the second relief valve 82 is for being integrated with the one-way valve of opening opposite direction and the second one-way overflow valve of relief valve, described buffering control valve 90,92 is connected between this first one-way overflow valve and the second one-way overflow valve.
Be connected on two pipelines between the one-way valve different from the outlet of buffering control valve 60 in the mode of execution of Fig. 4 and Fig. 7, in Fig. 9 and mode of execution shown in Figure 10, because the first relief valve 81 and the second relief valve 82 are the one-way overflow valve that is integrated with one-way valve and relief valve, therefore from when the pressure of the hydraulic oil of executive component 11 1 sides during above predetermined pressure, this hydraulic oil can from successively by with the direct-connected one-way overflow valve of this side, buffering control valve 90 or 92 and the opposite side that flows to executive component 11 with direct-connected another one-way overflow valve of opposite side.
Specifically, as shown in Figure 9, described buffering control valve 90 is three Twoway valvess of hydraulic control, three Twoway valvess of this hydraulic control have the first working hole 901 and the second working hole 902 and the first control mouthful the 903 and second control mouth 904, described first working hole 901 of three Twoway valvess of described hydraulic control is connected in the outlet of described the first one-way overflow valve, the second working hole 902 of three Twoway valvess of described hydraulic control is connected in the outlet of described the second one-way overflow valve, and the first control of three Twoway valvess of described hydraulic control mouthful the 903 and second control mouth 904 is connected respectively to the first side and second side of described executive component 11;
Wherein, when the relief valve of the relief valve of described the first one-way overflow valve and the second one-way overflow valve was all disconnected, the spool of three Twoway valvess of described hydraulic control was positioned at initial position, and described first working hole 901 of described three Twoway valvess and the second working hole 902 are connected;
When the relief valve of an one-way overflow valve in described the first one-way overflow valve and the second one-way overflow valve is connected, the spool of three Twoway valvess of described hydraulic control moves to corresponding limit position, thereby makes the hydraulic oil of the relief valve by the one-way overflow valve connected in described the first one-way overflow valve and the second one-way overflow valve flow through the one-way valve of another one-way overflow valve in described the first one-way overflow valve and the second one-way overflow valve through the throttling of three Twoway valvess of described hydraulic control.
When the pressure of the hydraulic oil of the first side of executive component 11 surpasses predetermined value, then the relief valve of the first one-way overflow valve is connected, simultaneously the high pressure liquid force feed of the first side moves to spool as three Twoway valvess of hydraulic control of buffering control valve 90 to make valve port that the limit position of certain flow area be arranged, thereby the hydraulic oil that allows the first side flows to the second side of executive component 11 successively through the one-way valve in the first one-way overflow valve (in relief valve), three Twoway valvess of hydraulic control and the second one-way overflow valve, to realize the effect of compensator or trimmer pressure.When the pressure decreased of the hydraulic oil of the first side of executive component 11 is following to predetermined value, the cut-off of the first one-way overflow valve, and the spool of three Twoway valvess of hydraulic control returns to initial position, thus no longer allow the hydraulic oil of the first side to flow to the second side.
When the pressure of the hydraulic oil of the second side of executive component 11 surpasses predetermined pressure, then the relief valve of the second one-way valve is connected, thereby make the spool as three Twoway valvess of hydraulic control that cushion control valve move to limit position, thereby the hydraulic oil that allows the second side flows to the first side of executive component 11 successively through the one-way valve in the relief valve in the second one-way overflow valve, three Twoway valvess of hydraulic control and the first one-way overflow valve, to realize the effect of compensator or trimmer pressure.When the pressure decreased of the hydraulic oil of the second side of executive component 11 is following to predetermined value, the cut-off of the second one-way overflow valve, and the spool of three Twoway valvess of hydraulic control returns to initial position, thus no longer allow the hydraulic oil of the second side to flow to the first side.
In addition, as shown in figure 10, described buffering control valve 92 comprises the hydraulic control two position two-way valve, this hydraulic control two position two-way valve has the first working hole 921, the second working hole 922 and control mouth 923, the first working hole 921 of described hydraulic control two position two-way valve is connected in the outlet of described the first one-way overflow valve, and the second entrance 922 of described hydraulic control two position two-way valve is connected in the outlet of described the second one-way overflow valve;
Described hydraulic control circuit also comprises shuttle valve 91, this shuttle valve has the first working hole 911, the second entrance 912 and exports 913, the first working hole 911 of described shuttle valve is connected in described first side of described executive component 11, the second entrance 912 of described shuttle valve is connected in described second side of described executive component 11, the outlet 913 of described shuttle valve is connected in the described control mouth 923 of described hydraulic control two position two-way valve by the 4th damping member 914
Wherein, when the relief valve of the relief valve of described the first one-way overflow valve and the second one-way overflow valve is all disconnected, the spool of described hydraulic control two position two-way valve is positioned at initial position, and described first working hole 921 of described hydraulic control two position two-way valve and the second working hole 922 are connected;
When the relief valve of any one-way overflow valve in described the first one-way overflow valve and the second one-way overflow valve is connected, the spool of described hydraulic control two position two-way valve moves to limit position, thereby makes the hydraulic oil of the relief valve by the one-way overflow valve connected in described the first one-way overflow valve and the second one-way overflow valve flow through the one-way valve of another one-way overflow valve in described the first one-way overflow valve and the second one-way overflow valve through the throttling of described hydraulic control two position two-way valve.
When the pressure of the hydraulic oil of the first side of executive component 11 surpassed predetermined pressure, the relief valve of the first one-way overflow valve was connected.Simultaneously, shuttle valve 91 with the high pressure liquid force feed of the first side of executive component 11 through the 4th damping member 914(such as damping plug) guide to the hydraulic control two position two-way valve as described in control mouthfuls 923, thereby make the spool of hydraulic control two position two-way valve move to limit position from initial position, the high pressure liquid force feed that allows to come from the relief valve of the first one-way overflow valve flows to the one-way valve of the second one-way overflow valve through the throttle effect of this hydraulic control two position two-way valve, and then flows to the second side of executive component 11.When the pressure decreased of the hydraulic oil of the first side of executive component 11 is following to predetermined value, the relief valve cut-off of the first one-way overflow valve, simultaneously hydraulic control two position two-way valve 69 returns to initial position again from limit position.
When the hydraulic oil of the second side of executive component 11 surpassed predetermined pressure, the relief valve of the second one-way overflow valve was connected.Simultaneously, shuttle valve 91 with the high pressure liquid force feed of the second side of executive component 11 through the 4th damping member 914(such as damping plug) guide to the hydraulic control two position two-way valve as described in control mouthfuls 923, thereby make the spool of hydraulic control two position two-way valve move to limit position from initial position, the high pressure liquid force feed that allows to come from the relief valve of the second one-way overflow valve flows to the one-way valve of the first one-way overflow valve through the throttle effect of this hydraulic control two position two-way valve, and then flows to the first side of executive component 11.When the pressure decreased of the hydraulic oil of the second side of executive component 11 is following to predetermined value, the relief valve cut-off of the second one-way overflow valve, simultaneously hydraulic control two position two-way valve 69 returns to initial position again from limit position.
In above-mentioned Fig. 4, Fig. 7, Fig. 9 and embodiment shown in Figure 10, in the rotation motion process, valve port still had certain flow area when the spool of the hydraulic control position control valve 90 of the buffering control valve 60 of Fig. 4, the hydraulic control two position three-way valve 69 of Fig. 7, Fig. 9, the hydraulic control position control valve 92 of Figure 10 was in limit position, therefore each relief valve also can play a role in filtering to pressure peak in movement process, but this area is very little, just can set up higher pressure by less flow, therefore little on the impact of the movement velocity under system's upbuild voltage capacity and the standard load.
In the application's specification, although mostly be that pressure take the hydraulic oil of the first side of executive component 11 surpasses predetermined value and describes as example, but what those skilled in the art should understand that is, surpass the situation of predetermined value for the pressure of the hydraulic oil of the second side of executive component 11, also applicable same principle and can realize same useful technique effect.Therefore, the situation that no longer pressure of the hydraulic oil of the second side of executive component 11 is surpassed predetermined value here is described in detail.
As mentioned above, preferably, described executive component 11 can be oil hydraulic motor, and this hydraulic control circuit is the revolution control loop.
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, and be not limited to the adduction relationship between every claim in claims.
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 (11)
1. hydraulic control circuit, this hydraulic control circuit comprises executive component (11) and the buffer loop (100) in parallel with this executive component (11), this buffer loop (100) comprises relief valve (51,52; 81,82) and with this relief valve (51,52; 81, the buffering control valve that 82) is connected in series (60,90,92) is at described relief valve (51,52; 81,82) when disconnecting, the spool of described buffering control valve (60,90,92) is in initial position, and the valve port of this buffering control valve (60,90,92) is opened, and it is characterized in that, at described relief valve (51,52; 81,82) connect and the spool of described buffering control valve (60,90,92) when being in limit position the flow area the when flow area of the valve port of this buffering control valve (60,90,92) is opened less than valve port and not exclusively closing.
2. hydraulic control circuit according to claim 1, it is characterized in that, described relief valve comprises the first relief valve (51,81) and the second relief valve (52,82), the entrance of this first relief valve (51,81) is connected in the first side of described executive component (11), the entrance of described the second relief valve (52,82) is connected in the second side of described executive component (11); Described buffering control valve (60,90,92) is connected in series and is connected to directly or indirectly respectively the first side and second side of described executive component (11) with described the first relief valve (51,81) and the second relief valve (52,82).
3. hydraulic control circuit according to claim 2, it is characterized in that, described buffering control valve (60) has the first entrance (601), the second entrance (602) and outlet (603), the outlet of described the first relief valve (51) is connected with first entrance (601) of described buffering control valve (60), the outlet of described the second relief valve (52) is connected with second entrance (602) of described buffering control valve (60)
Wherein, when described the first relief valve (51) and the equal access failure of the second relief valve (52), the spool of described buffering control valve (60) is positioned at initial position, and described the first entrance (601), the second entrance (602) and outlet (603) are connected;
In described the first relief valve (51) and the second relief valve (52) one when connecting, the spool of described buffering control valve (60) moves to corresponding limit position, thereby makes the hydraulic oil of the relief valve of connecting in flow through described the first relief valve (51) and the second relief valve (52) flow to described outlet (603) through throttling.
4. hydraulic control circuit according to claim 3 is characterized in that, described buffering control valve (60) comprising:
Buffering valve body (200), this buffering valve body (200) have cavity (201) and described the first entrance (601) that communicates with this cavity (201), the second entrance (602) and outlet (603);
Slide core (604) as the spool of described buffering control valve (60), this slide core (604) has first end (605), the second end (606) and the joint that is connected this first end and the second end (607), described slide core (604) is arranged on movably in the described cavity (201) and is limited with through-flow chamber (608) in this cavity (201), this through-flow chamber (608) is positioned between described first end (605) and the second end (606) side toward each other and centers on described joint (607), this through-flow chamber (608) communicates with described outlet (603), described the first entrance (601) by be arranged on described first end on the side of the second end first segment chute (611) and be communicated with described through-flow chamber (608), described the second entrance (602) can by be arranged on described the second end on the side of first end second section chute (612) and be communicated with described through-flow chamber (608), and the stroke (L2) of described slide core (604) is less than described first segment chute (611) and second section chute (612) length (L1) along described slide core longitudinal direction.
5. hydraulic control circuit according to claim 4, it is characterized in that, described buffering control valve (60) is pilot operated directional control valve, described cavity (201) also is divided into first control chamber (613) adjacent with described first end (605) and second control chamber (614) adjacent with described the second end (606) by described slide core, described the first control chamber (613) is connected in described first side of described executive component (11) by the first damping member (615), and described the second control chamber (614) is connected in described second side of described executive component (11) by the second damping member (616).
6. hydraulic control circuit according to claim 2, it is characterized in that, described buffering control valve (60) comprises hydraulic control two position three-way valve (69), this hydraulic control two position three-way valve (69) has the first entrance (621), the second entrance (622), control mouthful (623) and outlet (624), first entrance (621) of described hydraulic control two position three-way valve is connected in the outlet of described the first relief valve (51), second entrance (622) of described hydraulic control two position three-way valve is connected in the outlet of described the second relief valve (52), and the outlet of described hydraulic control two position three-way valve (624) is connected to the first side and second side of executive component (11) directly or indirectly;
Described hydraulic control circuit also comprises shuttle valve (70), this shuttle valve (70) has the first entrance (701), the second entrance (702) and outlet (703), first entrance (701) of described shuttle valve is connected in described first side of described executive component (11), second entrance (702) of described shuttle valve is connected in described second side of described executive component (11), the outlet of described shuttle valve (703) is connected in the described control mouthful (623) of described hydraulic control two position three-way valve by the 3rd damping element (704)
Wherein, at described the first relief valve (51) and the second relief valve (52) when all disconnecting, the spool of described hydraulic control two position three-way valve (69) is positioned at initial position, and described first entrance (621) of described hydraulic control two position three-way valve (69), the second entrance (622) and outlet (624) are connected;
In described the first relief valve (51) and the second relief valve (52) one when connecting, the spool of described hydraulic control two position three-way valve (69) moves to limit position, thereby makes the hydraulic oil of the relief valve of connecting in flow through described the first relief valve (51) and the second relief valve (52) flow to the outlet (624) of described hydraulic control two position three-way valve through throttling.
7. the described hydraulic control circuit of any one according to claim 2-6, wherein, described buffer loop also comprises the first one-way valve (61) and the second one-way valve (62), the outlet of this first one-way valve (61) is connected in described first side of described executive component (11), the outlet of described the second one-way valve (62) is connected in described second side of described executive component (11), and the entrance of described the first one-way valve (61) and the second one-way valve (62) communicates with each other; The outlet of described buffering control valve (60) is connected on the pipeline between the entrance of the entrance of described the first one-way valve (61) and the second one-way valve (62).
8. hydraulic control circuit according to claim 2, wherein, described the first relief valve (81) is for being integrated with the one-way valve of opening opposite direction and the first one-way overflow valve of relief valve, described the second relief valve (82) is for being integrated with the one-way valve of opening opposite direction and the second one-way overflow valve of relief valve, described buffering control valve (90,92) is connected between this first one-way overflow valve and the second one-way overflow valve.
9. hydraulic control circuit according to claim 8, wherein, described buffering control valve (90) is three Twoway valvess of hydraulic control, three Twoway valvess of this hydraulic control have the first working hole (901) and the second working hole (902) and the first control mouthful (903) and the second control mouthful (904), described first working hole (901) of three Twoway valvess of described hydraulic control is connected in the outlet of described the first one-way overflow valve, second working hole (902) of three Twoway valvess of described hydraulic control is connected in the outlet of described the second one-way overflow valve, and the first control mouthful (903) of three Twoway valvess of described hydraulic control and the second control mouthful (904) are connected respectively to the first side and second side of described executive component (11);
Wherein, when the relief valve of the relief valve of described the first one-way overflow valve and the second one-way overflow valve is all disconnected, the spool of three Twoway valvess of described hydraulic control is positioned at initial position, and described first working hole (901) of described three Twoway valvess and the second working hole (902) are connected;
When the relief valve of an one-way overflow valve in described the first one-way overflow valve and the second one-way overflow valve is connected, the spool of three Twoway valvess of described hydraulic control moves to corresponding limit position, thereby makes the hydraulic oil of the relief valve by the one-way overflow valve connected in described the first one-way overflow valve and the second one-way overflow valve flow through the one-way valve of another one-way overflow valve in described the first one-way overflow valve and the second one-way overflow valve through the throttling of three Twoway valvess of described hydraulic control.
10. hydraulic control circuit according to claim 8, it is characterized in that, described buffering control valve (92) comprises the hydraulic control two position two-way valve, this hydraulic control two position two-way valve has the first working hole (921), the second working hole (922) and control mouthful (923), first working hole (921) of described hydraulic control two position two-way valve is connected in the outlet of described the first one-way overflow valve, and second working hole (922) of described hydraulic control two position two-way valve is connected in the outlet of described the second one-way overflow valve;
Described hydraulic control circuit also comprises shuttle valve (91), this shuttle valve has the first entrance (911), the second entrance (912) and outlet (913), first entrance (911) of described shuttle valve is connected in described first side of described executive component (11), second entrance (912) of described shuttle valve is connected in described second side of described executive component (11), the outlet of described shuttle valve (913) is connected in the described control mouthful (923) of described hydraulic control two position two-way valve by the 4th damping element (914)
Wherein, when the relief valve of the relief valve of described the first one-way overflow valve and the second one-way overflow valve is all disconnected, the spool of described hydraulic control two position two-way valve is positioned at initial position, and described first entrance (921) of described hydraulic control two position two-way valve and the second entrance (922) are connected;
When the relief valve of any one-way overflow valve in described the first one-way overflow valve and the second one-way overflow valve is connected, the spool of described hydraulic control two position two-way valve moves to limit position, thereby makes the hydraulic oil of the relief valve by the one-way overflow valve connected in described the first one-way overflow valve and the second one-way overflow valve flow through the one-way valve of another one-way overflow valve in described the first one-way overflow valve and the second one-way overflow valve through the throttling of described hydraulic control two position two-way valve.
11. the described hydraulic control circuit of any one according to claim 1-6 and among the 8-10, described executive component (11) is oil hydraulic motor, and this hydraulic control circuit is the revolution control loop.
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| CN 201110185596 CN102269189B (en) | 2011-07-04 | 2011-07-04 | hydraulic control circuit |
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| CN 201110185596 CN102269189B (en) | 2011-07-04 | 2011-07-04 | hydraulic control circuit |
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| CN103010980B (en) * | 2012-12-10 | 2015-05-13 | 徐州重型机械有限公司 | Rotary control hydraulic system and crane |
| CN106870499B (en) * | 2017-04-28 | 2018-12-21 | 太原科技大学 | A kind of damping buffering valve |
| CN114457866A (en) * | 2022-02-09 | 2022-05-10 | 徐工消防安全装备有限公司 | Cutting device and rescue vehicle |
| CN114623114B (en) * | 2022-05-17 | 2022-08-09 | 中海油能源发展股份有限公司采油服务分公司 | Hydraulic rotation control system of marine hose crane |
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| US6167701B1 (en) * | 1998-07-06 | 2001-01-02 | Caterpillar Inc. | Variable rate ride control |
| JP2004132461A (en) * | 2002-10-10 | 2004-04-30 | Kioritz Corp | Boom device for spreader and buffer mechanism |
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| CN201671899U (en) * | 2010-05-19 | 2010-12-15 | 西安邮电学院 | Hydraulic overflow buffer circuit for mechanical arm |
| CN102022393A (en) * | 2010-12-30 | 2011-04-20 | 常德中联重科液压有限公司 | Rotary valve and rotary control loop using same |
| CN201884349U (en) * | 2010-09-15 | 2011-06-29 | 杭州骐瑞机电设备有限公司 | Cushioning device of revolving arm support |
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|---|---|---|---|---|
| US6167701B1 (en) * | 1998-07-06 | 2001-01-02 | Caterpillar Inc. | Variable rate ride control |
| JP2004132461A (en) * | 2002-10-10 | 2004-04-30 | Kioritz Corp | Boom device for spreader and buffer mechanism |
| CN201198850Y (en) * | 2008-05-16 | 2009-02-25 | 宁波中意液压马达有限公司 | Delaying and buffering brake mechanism of hydraulic reversing device |
| CN201671899U (en) * | 2010-05-19 | 2010-12-15 | 西安邮电学院 | Hydraulic overflow buffer circuit for mechanical arm |
| CN201884349U (en) * | 2010-09-15 | 2011-06-29 | 杭州骐瑞机电设备有限公司 | Cushioning device of revolving arm support |
| CN102022393A (en) * | 2010-12-30 | 2011-04-20 | 常德中联重科液压有限公司 | Rotary valve and rotary control loop using same |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102269189A (en) | 2011-12-07 |
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