CN205349887U - Engineering machine tool speed hydraulic control device - Google Patents
Engineering machine tool speed hydraulic control device Download PDFInfo
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- CN205349887U CN205349887U CN201521073594.5U CN201521073594U CN205349887U CN 205349887 U CN205349887 U CN 205349887U CN 201521073594 U CN201521073594 U CN 201521073594U CN 205349887 U CN205349887 U CN 205349887U
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Abstract
The utility model discloses an engineering machine tool speed hydraulic control device, the control port oil circuit at the main liquid accuse valve both ends that the control hydraulic actuator commutated connects in parallel and installs two throttling arrangement, and one of them throttling arrangement and guide control circuit are connected, and another throttling arrangement is through throttle oil return way connection oil tank, guide control circuit passes through guide brake valve lever and is connected with guide's oil sources, is connected with the shuttle valve between two guide control circuit of main liquid accuse valve, shuttle valve output oil path flows back to the oil tank through an overflow valve, between shuttle valve and the overflow valve and all set up the on -off control valve between throttle oil return way and the oil tank, be equipped with the parallelly connected installation of the throttling arrangement who sets up on a check valve and this oil circuit on guide control circuit, be equipped with the throttling arrangement tandem installation that sets up on another check valve and this oil circuit on throttle oil return way. The utility model discloses the realization lets same platform machine possess two kinds of operation speed control modes, and speed operation mode switch is convenient, and is with low costs.
Description
Technical field
This utility model relates to a kind of engineering machinery speed hydraulic control device, belongs to a kind of pilot control hydraulic circuit or the hydraulic control valve of the engineering machinery application such as excavator.
Background technology
In hydraulic construction machine, such as excavator, operator is when operating machine, and some operating mode wishes machine energy rapid movement, some operating mode (when lifting, level land or some operating mode) then needs to carry out mild microinching, to control actuator motions track exactly.
Manipulation angle in Fig. 1-arrive first shown in secondary pressure curve, wherein curve F is in current excavator hydraulic system, pilot operated " relation curve of stick control angle, θ and guide output pressure P " controlling part, guide output pressure P is used for control bound core stroke, its size is directly proportional to main valve plug stroke, the speed of the more big then actuation means of main valve plug stroke is more fast, and namely guide's output pressure P size then determines machine respective actuators velocity magnitude.In Fig. 1, B curve is under F curve, and its slope and P numerical value are all less, and when θ >=θ 2, pressure P remains unchanged.If removing control bound core stroke with the pressure of B curve, then under identical stick control angle, θ, the speed of respective actuators is obviously slow than by curve F speed and velocity variations is milder, and the stick control angle of two curves is identical to the controlled range of executor's speed, namely effectively to control angle [θ 1-θ 2] identical for handle.
As previously mentioned, as some action on an excavator need quickly, two kinds of control models at a slow speed, when needing quick mode, then go to control with F curve, when needing slow speed mode, then go to control with B curve, and both of which can carry out simple and quick switching, then machine can be made to adapt to various working demand very well.In the current machine for controlling with hydraulic pilot handle, can only go to control with being similar to F curve, also only a kind of fast control mode that its executor is corresponding, and to realize effectively controlling under angle range of condition not changing handle, executor can be allowed to enter mild microinching pattern, namely go to control with being similar to B curve, and allow and quickly can apply on same machine with slow speed mode, then need to increase extra control device to go to realize, relatively costly.
Utility model content
This utility model is based on the defect of above prior art, it is provided that a kind of engineering machinery speed hydraulic control device, adopts the switching of pure hydraulic control quick mode and slow speed mode.
This utility model adopts the following technical scheme that realization:
A kind of engineering machinery speed hydraulic control device, control port oil circuit at the main pilot operated valve device two ends controlling hydraulic actuator commutation has been installed in parallel two throttling arrangements, one of them throttling arrangement is connected with pilot control oil circuit, and another throttling arrangement connects fuel tank by throttling return oil road；Described pilot control oil circuit is connected with pilot control by pilot control handle, it is connected with shuttle valve between two pilot control oil circuits of main pilot operated valve device, described shuttle valve output circuit is back to fuel tank by an overflow valve, is respectively provided with on-off control valve between described shuttle valve and overflow valve and between described throttling return oil road and fuel tank；Guide's oil circuit control is provided with a check valve be installed in parallel with the throttling arrangement of setting on this oil circuit, throttling return oil road is provided with another check valve and installs with the throttling arrangement tandem of setting on this oil circuit.
As a kind of preferred version of the present utility model, described on-off control valve is two position and four-way reversing valves, and its external control signal controls the oil circuit break-make between described shuttle valve and overflow valve and between described throttling return oil road and fuel tank simultaneously.
As another kind of preferred version of the present utility model, described on-off control valve is the 2/2-way reversal valve that at least two is independent, and its external control signal controls the oil circuit break-make between described shuttle valve and overflow valve and between described throttling return oil road and fuel tank respectively simultaneously.
In above-mentioned two scheme, the external control signal of described on-off control valve can be hydraulic control, automatically controlled in one.
Further, described overflow valve is adjustable pressure overflow valve, its pressure regulative mode be machinery or hydraulic control, automatically controlled in one.
Further, described throttling arrangement adopts choke valve.
Orifice size between throttling arrangement on described pilot control oil circuit and the throttling arrangement on throttling return oil road can arrange certain proportionate relationship according to the rate request that machinery is concrete.
Further, one independent hydraulic control valve assembly part of described speed hydraulic control device composition is connected with main pilot operated valve device.
This utility model adopts throttling arrangement two groups in parallel to be arranged on the port controlling oil circuit of main pilot operated valve device, the pressure of main pilot operated valve device end can be realized by on-off control valve, realize the operation at a slow speed of work machine, it is possible to realize allowing same machine possess two kinds of operating speed control models.The hydraulic control mode that this utility model all adopts, can Integrated design in the integrated hydraulic system of machine, speed work pattern easy switching, and cost is low.
Below in conjunction with the drawings and specific embodiments, the utility model is described in further detail.
Accompanying drawing explanation
Fig. 1 is the relation curve of stick control angle, θ and guide output pressure P in construction machinery hydraulic system.
Fig. 2 is the hydraulic schematic diagram of embodiment 1.
Fig. 3 is the hydraulic schematic diagram of embodiment 2.
1. first throttle device, 2 second throttling arrangements, 3. the 3rd throttling arrangement, 4. the 4th throttling arrangement, 5. the first check valve 6. second check valve, 7. first controls port oil circuit, 8. second controls port oil circuit, 9. shuttle valve, 10. the second pilot control oil circuit, 11. shuttle valve output circuit, 12. throttling return oil road, 13. the first pilot control oil circuit, 14. the first on-off control valve, 15. overflow valve, 16. the second on-off control valve, 17. the 3rd on-off control valve, 18. pilot control hands handle, 19. main pilot operated valve device, 20. hydraulic actuator, 21. hydraulic oil container, 31. the 3rd check valve, 32. the 4th check valve, 50. pilot control.
Detailed description of the invention
Embodiment 1
Referring to Fig. 2, in the present embodiment, the control port oil circuit at main pilot operated valve device 19 two ends controlling hydraulic actuator commutation has been installed in parallel two throttling arrangements, wherein first control port oil circuit 7 parallel connection be first throttle device 1 and the second throttling arrangement 2, second controls port oil circuit 8 parallel connection is the 3rd throttling arrangement 3 and the 4th throttling arrangement 4.The oil circuit of pilot control 50 is connected with the first pilot control oil circuit 10 and the second pilot control oil circuit 13 respectively by pilot control handle 18, moves the quick of driving hydraulic actuator 20 or microinching for controlling main pilot operated valve device 19 spool.Second pilot control oil circuit 13 is connected with the second throttling arrangement the 2, the 4th throttling arrangement 4 respectively with on the first pilot control oil circuit 10, second throttling arrangement the 2, the 4th throttling arrangement 4 is in parallel with first check valve the 5, second check valve 6 respectively again, and the two check valve is used to eliminate the resistance produced when main its pilot port of pilot operated valve device 19 is fuel-displaced.First throttle device 1 and the second throttling arrangement 2 combined effect control the first control port oil circuit 7 pressure, and the 3rd throttling arrangement 3 and the 4th throttling arrangement 4 combined effect control the second control port oil circuit 8 pressure.First pilot control oil circuit the 10, second pilot control oil circuit 13 is connected with shuttle valve output circuit 11 after shuttle valve 9, and is controlled whether it connects with overflow valve 15 by the 3rd on-off control valve 17.Common threeth check valve 31, fourth check valve 32 in parallel with on the first control port oil circuit 7 and the second control port oil circuit 8 in throttling return oil road 12 is connected, this two check valve is connected with first throttle device the 1, the 3rd throttling arrangement 3 again respectively, and whether throttling return oil road 12 is connected with external hydraulic fuel tank 21, same is controlled by the 3rd on-off control valve 17.X mouth is connected with external pressure signal circuit, and acts on the end of the 3rd on-off control valve 17, for quickly, switching control between two-mode at a slow speed.
The present embodiment is only with the 3rd on-off control valve 17, and this on-off control valve is two position and four-way reversing valves, and its external control signal controls the oil circuit break-make between described shuttle valve and overflow valve and between described throttling return oil road and fuel tank simultaneously.
In conjunction with Fig. 2, the specific works process of the present embodiment is described in detail:
If 1. requiring that hydraulic actuator 20 carries out retraction movement:, main pilot operated valve device 19 should position work to the right.When X mouth no signal oil pressure, the 3rd on-off control valve 17 is then in cut-off position, left side, makes shuttle valve output circuit 11 and overflow valve 15 obstructed, and throttling return oil road 12 is obstructed with hydraulic oil container 21.Operated pilot handle 18 then supplies the first pilot control oil circuit 13 relevant pressure oil, pressure oil can only supply the first control port oil circuit 7 after the second throttling arrangement 2, and promote main pilot operated valve device 19 spool to overcome spring force to move, main pilot operated valve device position to the right is made to work, the oil return of the left side guide of main pilot operated valve device 19 simultaneously then can be directly over the second check valve 6 oil return, thus the oil return resistance eliminating main valve plug motion and producing.When the spool of main pilot operated valve device 19 is due to the increase of spring force above and during stop motion, at this moment the fluid that the first pilot control oil circuit 13 to the first controls in port oil circuit 7 will remain static, second throttling arrangement 2 can not play expenditure and pressure effect, and at this moment the first pilot control oil circuit 13 is equal with oil liquid pressure in the first control port oil circuit 7.Now pilot control handle 18 handles the angle pressure magnitude relationship with the first control port oil circuit 7 for shown in figure F curve.When the logical external signal oil pressure of X mouth, the 3rd break-make control valve 17 being made to be operated in conducting position, right side, throttling return oil road 12 then connects with fuel tank 21, and shuttle valve output circuit 11 connects with overflow valve 15.Operated pilot joystick 18 then supplies the first pilot control oil circuit 13 relevant pressure oil, and its maximum pressure is controlled by overflow valve 15.Owing to throttling return oil road 12 connects with fuel tank 21, main pilot operated valve device 7 main valve plug is promoted to overcome spring force to move so oil circuit 13 pressure oil supplies the first control port oil circuit 7 through the second throttling arrangement 2 expenditure and pressure rear portion, making main pilot operated valve device position to the right work, another part then returns to hydraulic oil container 21 through first throttle device 1 throttling.When the spool of main pilot operated valve device 19 is due to the increase of spring force above and during stop motion, then all footpath is crossed by the pressure oil after all expenditure and pressures of the second throttling arrangement 2 first throttle device 1 throttling and returns to hydraulic oil container 21, as long as at this moment the manipulation angle of pilot control handle 18 is constant, first controls pressure in port oil circuit 7 then stablizes constant, pressure is consistently less than the pressure in the first pilot control oil circuit 13, and its pressure reduces degree and then depends on two throttling arrangement open area ratios.Now pilot control handle 18 handle angle with first control port oil circuit 7 pressure magnitude relationship be Fig. 1 B curve shown in.As it is shown in figure 1, F curve and B curve are compared, control crank angle is gradually increased, when in θ 1～θ 2 scope, the first pressure controlled in port oil circuit 7 all will increase with handle work angle continuously linear, but under identical θ value, pressure P 2 < P1, and the little F curve of the B slope of curve.When work angle is more than or equal to θ 2, F curve occurs that sudden change increases to P1max, and due to overflow valve effect, it is constant that B curve is then maintained at P2max value.Main pilot operated valve device 19 spool displacement amount is directly proportional to the first pressure size controlling port oil circuit 7, and spool displacement amount then determines hydraulic actuator 20 retraction speed size.So when the first pressure controlling port oil circuit 7 is F curve, then the motion that hastens soon is retracted by hydraulic actuator 20, namely loop enters fast control mode, when the first pressure controlling port oil circuit 7 is B curve, then microinching is retracted by hydraulic actuator 20, namely loop enters slow control mode, and the switching quickly and between at a slow speed is then realized by the signal of X.
If 2. requiring that hydraulic actuator 20 carries out stretching out motion:, main pilot operated valve device 19 should position work to the left.When X mouth no signal oil pressure, the 3rd on-off control valve 17 is then in cut-off position, left side, makes shuttle valve output circuit 11 and overflow valve 15 obstructed, and throttling return oil road 12 is obstructed with hydraulic oil container 21.Operated pilot handle 18 then supplies the first pilot control oil circuit 10 relevant pressure oil, pressure oil can only supply the second control port oil circuit 8 after the 4th throttling arrangement 4, and promote main pilot operated valve device 19 spool to overcome spring force to move, main pilot operated valve device position to the left is made to work, the oil return of the right side guide of main pilot operated valve device 19 simultaneously then can be directly over the first check valve 5 oil return, thus the oil return resistance produced when eliminating main valve plug motion.When the spool of main pilot operated valve device 19 is due to the increase of spring force above and during stop motion, at this moment the fluid that the second pilot control oil circuit 10 to the second controls in port oil circuit 8 will remain static, 4th throttling arrangement 4 can not play expenditure and pressure effect, and at this moment the second pilot control oil circuit 10 is equal with the second control port oil circuit 8 oil liquid pressure.Now pilot control handle 18 handles the angle pressure magnitude relationship with the second control port oil circuit 8 for shown in figure F curve.When the logical external signal oil pressure of X mouth, the 3rd break-make control valve 17 being made to be operated in conducting position, right side, throttling return oil road 12 then connects with fuel tank 21, and shuttle valve output circuit 11 connects with overflow valve 15.Operated pilot joystick 18 then supplies the second pilot control oil circuit 10 relevant pressure oil, and its maximum pressure is controlled by overflow valve 15.Owing to throttling return oil road 12 connects with fuel tank 21, main pilot operated valve device 7 main valve plug is promoted to overcome spring force to move so oil circuit 10 pressure oil supplies the second control port oil circuit 8 through the 4th throttling arrangement 4 expenditure and pressure rear portion, making main pilot operated valve device position to the left work, another part then returns to hydraulic oil container 21 through the 3rd throttling arrangement 3 throttling.When the spool of main pilot operated valve device 19 is due to the increase of spring force above and during stop motion, footpath is then all crossed the 3rd throttling by the pressure oil after all expenditure and pressures of the 4th throttling arrangement 4 fill 3 throttlings and return to hydraulic oil container 21, as long as at this moment the manipulation angle of pilot control handle 18 is constant, second controls pressure in port oil circuit 8 then stablizes constant, pressure is consistently less than the pressure in the second pilot control oil circuit 10, and its pressure reduces degree and then depends on two throttling arrangement open area ratios.Now pilot control handle 18 handle angle with second control port oil circuit 8 pressure magnitude relationship be Fig. 1 B curve shown in.As it is shown in figure 1, F curve and B curve are compared, control crank angle is gradually increased, when in θ 1～θ 2 scope, the second pressure controlled in port oil circuit 8 all will increase with handle work angle continuously linear, but under identical θ value, pressure P 2 < P1, and the little F curve of the B slope of curve.When work angle is more than or equal to θ 2, F curve occurs that sudden change increases to P1max, and due to overflow valve effect, it is constant that B curve is then maintained at P2max value.Main pilot operated valve device 19 spool displacement amount is directly proportional to the second pressure size controlling port oil circuit 8, and spool displacement amount then determines hydraulic actuator 20 and stretches out velocity magnitude.So when the second pressure controlling port oil circuit 8 is F curve, then the motion that hastens soon is stretched out by hydraulic actuator 20, namely loop enters fast control mode, when the second pressure controlling port oil circuit 8 is B curve, then microinching is stretched out by hydraulic actuator 20, namely loop enters slow control mode, and the switching quickly and between at a slow speed is then realized by the signal of X.
Embodiment 2
Be connected with external pressure signal circuit referring to Fig. 3, X mouth, for quickly, switching control between two-mode at a slow speed.Pilot control handle 18 is connected with oil circuit 13,10, for controlling the motion of hydraulic actuator 20.Oil circuit 13 is connected with the second throttling arrangement the 2, the 4th throttling arrangement 4 respectively with on oil circuit 10, and above-mentioned throttling arrangement is in parallel with first check valve the 5, second check valve 6 respectively again, and this two check valve is used to eliminate the resistance produced when main its pilot port of hydraulic control 19 is fuel-displaced.First throttle device 1 and the second throttling arrangement 2 combined effect control the first control port oil circuit pressure, and the 3rd throttling arrangement 3 and the 4th throttling arrangement 4 combined effect control the second control port oil circuit pressure.Oil circuit 10, oil circuit 13 are connected with shuttle valve output circuit 11 after shuttle valve 9, and are controlled whether it connects with overflow valve 15 by the first break-make control valve 14.Throttling return oil road 12 is common with the 3rd check valve 31,4th check valve 32 connects, this two check valve again respectively with first throttle device 1, the 3rd throttling arrangement 3 is connected, and whether throttling return oil road 12 is connected with external hydraulic fuel tank 21, the second on-off control valve 16 control.
The present embodiment adopts two 2/2-way reversal valves as on-off control valve, and its external control signal controls the oil circuit break-make between described shuttle valve and overflow valve and between described throttling return oil road and fuel tank simultaneously.
In conjunction with Fig. 3, the specific works process of the present embodiment is described in detail:
If 1. requiring that hydraulic actuator 20 carries out retraction movement:, main pilot operated valve device 19 should position work to the right.When X mouth no signal oil pressure, the first on-off control valve 14 is then in cut-off position, makes shuttle valve output circuit 11 and overflow valve 15 obstructed, and the second on-off control valve 15 is in cut-off position, and it is obstructed with hydraulic oil container 21 that envoy flows back to oil circuit 12.Operated pilot handle 18 then supplies the first pilot control oil circuit 13 relevant pressure oil, pressure oil can only supply the first control port oil circuit 7 after the second throttling arrangement 2, and promote main pilot operated valve device 19 spool to overcome spring force to move, main pilot operated valve device position to the right is made to work, the oil return of the left side guide of main pilot operated valve device 19 simultaneously then can be directly over the second check valve oil return, thus the oil return resistance eliminating main valve plug motion and producing.When the spool of main pilot operated valve device 19 is due to the increase of spring force above and during stop motion, at this moment the fluid that the first pilot control oil circuit 13 to the first controls in port oil circuit 7 will remain static, second throttling arrangement 2 can not play expenditure and pressure effect, and at this moment the first pilot control oil circuit 13 is equal with oil liquid pressure in the first control port oil circuit 7.Now pilot control handle 18 handles the angle pressure magnitude relationship with the first control port oil circuit 7 for shown in figure F curve.When the logical external signal oil pressure of X mouth, the second break-make control valve 15 is operated in conducting position, and throttling return oil road 12 then connects with fuel tank 21, and the first on-off control valve 14 is operated in conducting position, and shuttle valve output circuit 11 connects with overflow valve 15.Operated pilot joystick 18 then supplies the first pilot control oil circuit 13 relevant pressure oil, and its maximum pressure is controlled by overflow valve 15.Owing to throttling return oil road 12 connects with fuel tank 21, main pilot operated valve device 7 main valve plug is promoted to overcome spring force to move so oil circuit 13 pressure oil supplies the first control port oil circuit 7 through the second throttling arrangement 2 expenditure and pressure rear portion, making main pilot operated valve device position to the right work, another part then returns to hydraulic oil container 21 through first throttle device 1 throttling.When the spool of main pilot operated valve device 19 is due to the increase of spring force above and during stop motion, then all footpath is crossed by the pressure oil after all expenditure and pressures of the second throttling arrangement 2 first throttle device 1 throttling and returns to hydraulic oil container 21, as long as at this moment the manipulation angle of pilot control handle 18 is constant, first controls pressure in port oil circuit 7 then stablizes constant, pressure is consistently less than the pressure in the first pilot control oil circuit 13, and its pressure reduces degree and then depends on two throttling arrangement open area ratios.Now pilot control handle 18 handle angle with first control port oil circuit 7 pressure magnitude relationship be Fig. 1 B curve shown in.As it is shown in figure 1, F curve and B curve are compared, control crank angle is gradually increased, when in θ 1～θ 2 scope, the first pressure controlled in port oil circuit 7 all will increase with handle work angle continuously linear, but under identical θ value, pressure P 2 < P1, and the little F curve of the B slope of curve.When work angle is more than or equal to θ 2, F curve occurs that sudden change increases to P1max, and due to overflow valve effect, it is constant that B curve is then maintained at P2max value.Main pilot operated valve device 19 spool displacement amount is directly proportional to the first pressure size controlling port oil circuit 7, and spool displacement amount then determines hydraulic actuator 20 retraction speed size.So when the first pressure controlling port oil circuit 7 is F curve, then the motion that hastens soon is retracted by hydraulic actuator 20, namely loop enters fast control mode, when the first pressure controlling port oil circuit 7 is B curve, then microinching is retracted by hydraulic actuator 20, namely loop enters slow control mode, and the switching quickly and between at a slow speed is then realized by the signal of X.
If 2. requiring that hydraulic actuator 20 carries out stretching out motion:, main pilot operated valve device 19 should position work to the left.When X mouth no signal oil pressure, the first on-off control valve 14 is then in cut-off position, makes shuttle valve output circuit 11 and overflow valve 15 obstructed, and the second on-off control valve 15 is in cut-off position, and it is obstructed with hydraulic oil container 21 that envoy flows back to oil circuit 12.Operated pilot handle 18 then supplies the first pilot control oil circuit 10 relevant pressure oil, pressure oil can only supply the second control port oil circuit 8 after the 4th throttling arrangement 4, and promote main pilot operated valve device 19 spool to overcome spring force to move, main pilot operated valve device position to the left is made to work, the oil return of the right side guide of main pilot operated valve device 19 simultaneously then can be directly over the first check valve 5 oil return, thus the oil return resistance produced when eliminating main valve plug motion.When the spool of main pilot operated valve device 19 is due to the increase of spring force above and during stop motion, at this moment the fluid that the second pilot control oil circuit 10 to the second controls in port oil circuit 8 will remain static, 4th throttling arrangement 4 can not play expenditure and pressure effect, and at this moment the second pilot control oil circuit 10 is equal with the second control port oil circuit 8 oil liquid pressure.Now pilot control handle 18 handles the angle pressure magnitude relationship with the second control port oil circuit 8 for shown in figure F curve.When the logical external signal oil pressure of X mouth, the second break-make control valve 15 is operated in conducting position, and throttling return oil road 12 then connects with fuel tank 21, and the first on-off control valve 14 is operated in conducting position, and shuttle valve output circuit 11 connects with overflow valve 15.Operated pilot joystick 18 then supplies the second pilot control oil circuit 10 relevant pressure oil, and its maximum pressure is controlled by overflow valve 15.Owing to throttling return oil road 12 connects with fuel tank 21, so oil circuit 10
Pressure oil supplies the second control port oil circuit 8 through the 4th throttling arrangement 4 expenditure and pressure rear portion and promotes main pilot operated valve device 7 main valve plug to overcome spring force to move, making main pilot operated valve device position to the left work, another part then returns to hydraulic oil container 21 through the 3rd throttling arrangement 3 throttling.When the spool of main pilot operated valve device 19 is due to the increase of spring force above and during stop motion, footpath is then all crossed the 3rd throttling by the pressure oil after all expenditure and pressures of the 4th throttling arrangement 4 fill 3 throttlings and return to hydraulic oil container 21, as long as at this moment the manipulation angle of pilot control handle 18 is constant, second controls pressure in port oil circuit 8 then stablizes constant, pressure is consistently less than the pressure in the second pilot control oil circuit 10, and its pressure reduces degree and then depends on two throttling arrangement open area ratios.Now pilot control handle 18 handle angle with second control port oil circuit 8 pressure magnitude relationship be Fig. 1 B curve shown in.As it is shown in figure 1, F curve and B curve are compared, control crank angle is gradually increased, when in θ 1～θ 2 scope, the second pressure controlled in port oil circuit 8 all will increase with handle work angle continuously linear, but under identical θ value, pressure P 2 < P1, and the little F curve of the B slope of curve.When work angle is more than or equal to θ 2, F curve occurs that sudden change increases to P1max, and due to overflow valve effect, it is constant that B curve is then maintained at P2max value.Main pilot operated valve device 19 spool displacement amount is directly proportional to the second pressure size controlling port oil circuit 8, and spool displacement amount then determines hydraulic actuator 20 and stretches out velocity magnitude.So when the second pressure controlling port oil circuit 8 is F curve, then the motion that hastens soon is stretched out by hydraulic actuator 20, namely loop enters fast control mode, when the second pressure controlling port oil circuit 8 is B curve, then microinching is stretched out by hydraulic actuator 20, namely loop enters slow control mode, and the switching quickly and between at a slow speed is then realized by the signal of X.
Embodiment above describes ultimate principle of the present utility model and principal character and advantage of the present utility model, skilled person will appreciate that of the industry, this utility model is not restricted to the described embodiments, described in above-described embodiment and description is that specific works principle of the present utility model is described, under the premise without departing from this utility model spirit and scope, this utility model also has various changes and modifications, these changes and improvements both fall within the scope of claimed this utility model, this utility model claims scope and is defined by appending claims and equivalent thereof.
Claims (7)
1. an engineering machinery speed hydraulic control device, it is characterised in that:
Control port oil circuit at the main pilot operated valve device two ends controlling hydraulic actuator commutation has been installed in parallel two throttling arrangements, and one of them throttling arrangement is connected with pilot control oil circuit, and another throttling arrangement connects fuel tank by throttling return oil road；
Described pilot control oil circuit is connected with pilot control by pilot control handle, it is connected with shuttle valve between two pilot control oil circuits of main pilot operated valve device, described shuttle valve output circuit is back to fuel tank by an overflow valve, is respectively provided with on-off control valve between described shuttle valve and overflow valve and between described throttling return oil road and fuel tank；
Guide's oil circuit control is provided with a check valve be installed in parallel with the throttling arrangement of setting on this oil circuit, throttling return oil road is provided with another check valve and installs with the throttling arrangement tandem of setting on this oil circuit.
2. a kind of engineering machinery speed hydraulic control device according to claim 1, described on-off control valve is two position and four-way reversing valves, and its external control signal controls the oil circuit break-make between described shuttle valve and overflow valve and between described throttling return oil road and fuel tank simultaneously.
3. a kind of engineering machinery speed hydraulic control device according to claim 1, described on-off control valve is the 2/2-way reversal valve that at least two is independent, and its external control signal controls the oil circuit break-make between described shuttle valve and overflow valve and between described throttling return oil road and fuel tank respectively simultaneously.
4. a kind of engineering machinery speed hydraulic control device according to Claims 2 or 3, the external control signal of described on-off control valve be hydraulic control, automatically controlled in one.
5. a kind of engineering machinery speed hydraulic control device according to claim 1, described overflow valve is adjustable pressure overflow valve, its pressure regulative mode be machinery or hydraulic control, automatically controlled in one.
6. a kind of engineering machinery speed hydraulic control device according to claim 1, described throttling arrangement adopts choke valve.
7. a kind of engineering machinery speed hydraulic control device according to claim 1, described speed hydraulic control device one independent hydraulic control valve assembly part of composition is connected with main pilot operated valve device.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201521073594.5U CN205349887U (en) | 2015-12-21 | 2015-12-21 | Engineering machine tool speed hydraulic control device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201521073594.5U CN205349887U (en) | 2015-12-21 | 2015-12-21 | Engineering machine tool speed hydraulic control device |
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| Publication Number | Publication Date |
|---|---|
| CN205349887U true CN205349887U (en) | 2016-06-29 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201521073594.5U Withdrawn - After Issue CN205349887U (en) | 2015-12-21 | 2015-12-21 | Engineering machine tool speed hydraulic control device |
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| CN (1) | CN205349887U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105443469A (en) * | 2015-12-21 | 2016-03-30 | 山河智能装备股份有限公司 | Hydraulic control device for speed of engineering machine |
-
2015
- 2015-12-21 CN CN201521073594.5U patent/CN205349887U/en not_active Withdrawn - After Issue
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105443469A (en) * | 2015-12-21 | 2016-03-30 | 山河智能装备股份有限公司 | Hydraulic control device for speed of engineering machine |
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