CN101387310A - Hydraulic valve assembly with direction sliding valve and regeneration flow dividing valve with pressure compensation - Google Patents
Hydraulic valve assembly with direction sliding valve and regeneration flow dividing valve with pressure compensation Download PDFInfo
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- CN101387310A CN101387310A CNA2007101929443A CN200710192944A CN101387310A CN 101387310 A CN101387310 A CN 101387310A CN A2007101929443 A CNA2007101929443 A CN A2007101929443A CN 200710192944 A CN200710192944 A CN 200710192944A CN 101387310 A CN101387310 A CN 101387310A
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Abstract
The invention relates to a hydraulic valve component with a directional slide valve for pressure compensation and a regenerating shunt valve. According to the hydraulic valve component, a hydraulic loop controls fluid flow between a first port and a second port of a hydraulic actuator with a cylinder/piston structure and a feeding pipe and a reflowing pipeline of an oil tank. The hydraulic loop operates in a normal power operation mode and power and nonpower regeneration modes. Under the power operation mode, a traditional pressure compensation slide valve determines the speed of the hydraulic actuator. One working port of the slide valve is connected to the first port through a working port blocking valve; and the other working port is connected with the second port. The regenerating shunt valve is directly connected between the first port and the second port of the hydraulic loop. Under the regenerating operation mode or a power and regeneration mixing mode, the combination of the slide valve, the working port blocking valve and the regenerating shunt valve decides the speed of the hydraulic actuator.
Description
Technical field
The present invention relates to the hydraulic system of the actuator of operational example such as cylinder/piston structure, relate more particularly to hydraulic system with power and regeneration mode operate actuator.
Background technique
A large amount of machines are by the hydraulic system operation that has a plurality of hydraulic actuators, and described hydraulic actuator for example is connected to piston on another parts for the cylinder on the parts that are connected to machine with by piston rod.Piston is divided into two internal chamber with cylinder interior, and alternately applies hydraulic fluid under pressure each chamber piston is moved in opposite direction, thereby two parts are relative to each other moved.
In common hydraulic system, manual operation valve control hydraulic fluid flows to cylinder, and wherein operator's mechanically moving is connected to the controlling rod on the spool that is positioned at valve opening, as U.S. Patent No. 5,579, shown in 643.Moving of controlling rod is placed into all places relevant with the hole middle chamber with spool, and described hole and the service that comes self-pumping, the pipeline that leads to the reflow pipe of fluid tank and lead to the associated cylinder chamber are communicated with.Flow to a cylinder chamber along the hydraulic fluid of direction moving valve core control pressurization from pump and allow direction of flow fuel tank in another chamber.This makes piston and the piston rod that is connected thereto drive along a direction.Moving valve core makes fluid with respect to the cylinder chamber reverse flow in opposite direction, thereby produces motion in opposite direction.Change spool and change the size of measuring hole, and therefore change the rate of flow of fluid that flows to the associated cylinder chamber along the amount of movement of suitable direction, thereby with different in proportion speed driving pistons.Pressure compensation mechanism is incorporated in the slide valve assembly usually to provide the cardinal principle of passing measuring hole constant pressure drop.
Exist and break away from the manually-operable hydrovalve, tend to the trend of automatically controlled solenoid valve.U.S. Patent No. 6,637,461 have described by a pair of electro-hydraulic valve and have carried out the pilot operated guiding valve of bidirectional-movement with the control spool.
Utilize manually and electrically operated device, guiding valve is formed the independent main body of so-called valve portion, and the valve portion that is used for multiple machine function connects side by side with formation with bolt and is positioned at valve assembly on the operator workstation of machine.Each valve portion has the working port that is used to be connected to the respective cylinder chamber.Each valve portion also has the passage that is used for service, fuel tank reflux line and load-sensing loop, and wherein these passages are aimed to transmit fluid by whole valve assembly with the channel-like in the adjacent valve part.The end portion of valve assembly has the service of connection and the port of fuel tank pipeline and the hole that pressure-relief valve wherein is installed.
The possibility of guiding valve comprises the Hui Sitong bridge construction that is made of four ratio electro-hydraulic valves, and wherein each electro-hydraulic valve is connected between foursquare two different angles.Two diagonal angles are connected to the working port that is used for two cylinder chamber.A residual angle of bridge is connected to service, and last angle is connected to the fuel tank reflux line.The power of operation cylinder stretch out and the withdrawal pattern under, two valves that are positioned on the bridge opposite side are opened, and make that the fluid from service flows into a cylinder chamber, and flow out all direction of flow fuel tank reflux lines of another cylinder chamber.
Under overload situations, act on external load on the machine or other active force and cause hydraulic actuator to stretch out or withdraw, and need not remarkable pressure from service.Described active force driving fluid flows out a cylinder chamber, and the expansion of another chamber simultaneously sucks fluid from service.In this case, fluid is the effluent gases cylinder under elevated pressures, thereby comprises off-energy when release of fluid is in fuel tank.
Favour stone bridge construction relatively can be more favourable with the guiding valve of regeneration mode operation, the wherein energy recirculation of exhaust fluid, rather than with no release of fluid in fuel tank.In regeneration mode, two adjacent valve at service angle that are connected to the bridge of fuel tank reflux line are opened, and other valve keeps cutting out.Therefore, two from the fluid passing ratio electro-hydraulic valve that a cylinder chamber is discharged flow to another cylinder chamber that enlarges.Therefore, the fluid that flows out from the cylinder chamber of shrinking flows into and is full of the chamber of expansion, thereby reduces or eliminates from the required Fluid Volume of service.This requires and must accurately control two ratio electro-hydraulic valves with suitable metering regenerative fluid.Therefore, apply electric current with two valves be opened to accurately, consistent location.In addition, regenerative fluid all produce power losses in two valves.The amplitude of attempting to reduce energy loss relates to the 5th electro-hydraulic valve directly is connected between two working ports of valve bridge.But the energy loss in the flexible pipe between valve assembly and cylinder still influences the efficient of regeneration mode.
Hope provides a kind of regeneration mode of low energy losses to the hydraulic system of using guiding valve on the operator workstation.This can make existing Machinery Design utilize the regenerative operation pattern to improve.
Summary of the invention
Providing a kind of is used for controlling first port and second port of hydraulic actuator and transmits the service of pressure fluid and oil hydraulic circuit that the fluid of fuel tank reflux line between each flows.This oil hydraulic circuit comprises the guiding valve with the inlet that is connected to the supplying pipe diatom, the outlet that is connected to fuel tank reflow pipe diatom, first working port and second working port.Guiding valve is guided fluid one of into first and second working ports from inlet selectively, and guides fluid another from first and second working ports into outlet.
The working port blocking valve is connected to first working port first port of hydraulic actuator.Regeneration flow dividing valve is connected to hydraulic actuator, and flows between first port and second port by described regeneration flow dividing valve fluid.
In an embodiment of oil hydraulic circuit, working port blocking valve and regeneration flow dividing valve are away from guiding valve and near the hydraulic actuator setting.In another embodiment, regeneration flow dividing valve is away from guiding valve and near the hydraulic actuator setting, and the working port blocking valve is near the guiding valve setting.
In a preferred embodiment, oil hydraulic circuit comprises pressure-compensated valve, and it is connected to the constant pressure drop of cardinal principle between selected in guiding valve and the maintenance inlet and first and second working ports port.In this embodiment's a scheme, the load-sensing loop is connected to guiding valve so that the signal of the force value of wishing in the indication supplying pipe diatom to be provided, thus the operation hydraulic actuator.The load-sensing loop is connected to operationally pilot pressure recuperation valve.
Description of drawings
Fig. 1 is made up of subgraph 1A and 1B, is the schematic representation that comprises hydraulic system of the present invention; With
Fig. 2 is the viewgraph of cross-section of cutting open along the guiding valve of used eletromagnetic-operating in the hydraulic system.
Embodiment
At first with reference to Figure 1A and 1B, the hydraulic system 10 on the machine is controlled five for example hydraulic actuators 11,12,13,14 and 15 of cylinder/piston.Each hydraulic actuator 11-15 comprises the oil hydraulic cylinder 16 that has moveable piston 18, and piston rod 17 is connected on the described piston.Piston 18 has defined hydraulic pressure cavity (head chamber) 19 and rod end chamber 20 in oil hydraulic cylinder, first and second ports that hydraulic pressure respectively is connected to these chambers wherein are set.Should be appreciated that the present invention can use the hydraulic actuator of other type, for example revolution motor.
First and second working ports 46 and 48 are connected in the chamber of main aperture 43 extensions by the first and second working port passages 52,54 respectively.With reference to figure 1, working port 46 is connected to the first relevant hydraulic actuator 11 with 48 by flexible pipe 55 and 56.Particularly, first working port 46 is connected to the hydraulic pressure cavity 19 of oil hydraulic cylinder 16, and second port 48 is connected to the rod end chamber 20 of oil hydraulic cylinder.
Valve piece 42 has a plurality of common-use tunnels, and described common-use tunnel passes perpendicular to the plane of cross section shown in Figure 2 and is connected to common-use tunnel identical among the adjacent portion 32-35.A pair of such passage 58,59 leads to different chamber that extends around main aperture 43 and the fuel tank 22 that is connected to hydraulic system by fuel tank reflux line 28 (Fig. 1).Valve piece 42 also has supply passage 60, the output that it leads to main aperture 43 and is connected to pump 21 by service 24.Another hole 62 that holds traditional pressure-compensated valve 64 in supply passage 60 and the valve piece 42 is communicated with.Pressure-compensated valve 64 control hydraulic fluids are from a pair of supply passage chamber 65,66 that supply passage 60 flows to around main aperture 43, and it links to each other by bridge circuit (bridge passage) 68.This pressure compensation mechanism is described in U.S. Patent No. 4,693, in 272, alternatively, also can use to be described in U.S. Patent No. 5,579 pressure compensation mechanism in 642.
Fig. 2 illustrates and mediates or the spool 44 of middle position, and in this position, fluid is prevented from flowing into or flowing out working port 46 and 48.Spool 44 to the right motion is in the drawings at first opened a path between second working port 48 and the fuel tank path 58 by the first spool recess 61.Spool 44 further moves right opens the first working port passage 52 and the measuring hole between the supply passage chamber 66 of bridge circuit 68 1 ends, thereby provides another path between the supply passage 60 and first working port 46 by pressure-compensated valve 64, supply passage chamber 65, bridge circuit 68 and the second spool recess 63.Notice that from middle position, the first spool recess 61 leads to fuel tank path 58 before the second spool recess 63 leads to bridge circuit 68.Therefore, before the pressurized hydraulic fluid that comes self-pumping 21 imposed on first working port 46, fluid was arranged to fuel tank 22 from second working port 48.With regard to the operation of hydraulic actuator, the significance of this structure will be described subsequently.
Spool 44 left motion in Fig. 2 at first is connected to first working port 46 by the second spool recess 63 chamber 53 of fuel tank return flow line 59.Along this direction continue move through pressure-compensated valve 64, supply passage chamber 65 and the first spool recess 61 and open supply passage 60 in the path and another measuring hole between second working port 48.Thisly cause from middle position motion left that the second spool recess 63 leads to fuel tank return flow line 59 before the first spool recess 61 leads to supply passage chamber 65.Therefore, before the pressurized hydraulic fluid that comes self-pumping 21 imposed on second working port 48, fluid was arranged to fuel tank 22 from first working port 46.
The motion of spool 44 is produced by the force feedback actuator 70 that is positioned on the spool end relative with spring assembly 50.Force feedback actuator 70 has the end block 78 that attaches to valve piece 42 1 sides, makes that the piston hole 72 in the end block is aimed at main aperture 43.Piston hole 72 holds the valve driven plunger 74 on second end that attaches to spool 44.Perhaps, spool 44 and valve driven plunger 74 can form integral body.In another structure, valve driven plunger 74 and spool 44 move back and forth as common unit.Valve driven plunger 74 has the general hourglass shape of truncated conical end, and truncated conical end concavity place betwixt engages.The first and second piston control chambers 75 and 76 are formed on the piston hole 72 that is arranged on valve driven plunger 74 opposite sides.Although end block 78 separates with valve piece 42, two parts can form integral body, therefore are referred to as main body 73 here.In unitary body, main aperture 43 and piston hole 72 comprise common hole.
First electro-hydraulic valve 80 is installed in first control hole 82, described first control hole extend in the end block 78 and with piston hole 72 with right angle intersection.First electro-hydraulic valve 80 has first solenoid 84, and described first solenoid makes the armature 86 that engages the first valve element 88 selectively produce motion when energising.As described below, make 88 motions of the first valve element by means of the operation of the armature 86 of first solenoid 84, flow into the first and second piston control chambers 75 and 76 thereby control fluid pro rata.Feedback pin 90 has an end that engages with the spring assembly 92 that is arranged in the first valve element 88 and the other end that engages with valve driven plunger 74.
As will be descr, pilot pressure passage 94 is communicated with first control hole 82 and to be used for constant pilot pressure conveyance fluid operating valve driven plunger 74, that regulate.End block 78 also has guide's fuel tank path 93, and its fuel tank return flow line 59 from valve piece 42 extends in the part of first control hole 82.First crosspassage 96 is connected to second control hole 104 with the above-mentioned part of first control hole 82.Branch road 100 leads to first control hole 82 from the first piston control chamber 75 on spool one side of valve driven plunger 74, and second crosspassage 102 forms the continuity of branch road 100 to second control holes 104.The second piston control chamber 76 that is positioned at away from the distally of the valve driven plunger 74 of spool 44 is led in the end of second control hole 104.
Continuation has the second valve element 108 with reference to figure 2, the second electro-hydraulic valves 81, and when second solenoid 106 drove the armature 110 that is connected on the second valve element, the described second valve element was in second control hole, 104 slides within.Second electro-hydraulic valve 81 is the on/off-type valves with two states: energising and outage.When 81 outages of second electro-hydraulic valve, the second valve element 108 is positioned to second crosspassage 102 is connected to the second piston control chamber 76.When 81 energisings of second electro-hydraulic valve, first crosspassage 96 that is communicated with fuel tank return flow line 58 and 59 is connected to the second piston control chamber 76.
First electro-hydraulic valve 80 is proportioning devices, and its metering is from the fluid of pilot pressure passage 94 position with control spool 44, thereby control supplies to the rate of flow of fluid of working port 46 and 48.The two states of second electro-hydraulic valve 81 has determined the moving direction of valve driven plunger 74 and spool 44.The moving direction of spool 44 decision piston rod 17 is that the cylinder 16 from first hydraulic actuator 11 stretches out or withdraws wherein.Details of operation by two electro- hydraulic valves 80 and 81 guiding valves that carry out 40 is described in U.S. Patent No. 6,637, in 461.
Refer again to Figure 1A, the first control valve part 31 has the first anti-cavitation erosion valve 112 and the first working port pressure-relief valve 114, and they are parallel to first working port 46 and lead between the fuel tank return flow line 59 of fuel tank reflux line 28.The first working port pressure-relief valve 114 discharges any excess pressure that results from first working port, 46 places.The same structure of the second anti-cavitation erosion valve 116 and the second working port pressure-relief valve 118 is connected to second working port 48.The second control valve part 32 has the anti-cavitation erosion valve that is connected to its working port and those structures of working port pressure-relief valve equally.
Alternatively, the electronic load induction can be used, in this case, the pressure-compensated valve 64 among load-sensing loop 120 and each valve portion 31-33 can be omitted.As an alternative, pressure transducer 57 provides the signal of the induced pressure of indicative function on corresponding hydraulic actuator to SC system controller 30.The software that SC system controller 30 is carried out is selected the required maximum supply pressure of sensor and is regulated two electro-hydraulic valves 80 of each guiding valve 40 of control and 81 operation, thereby carries out pressure compensation.
Two working ports 46 of first valve portion 31 and 48 are connected to the first remote valve assembly 127 near first hydraulic actuator 11 by a pair of flexible pipe 55 and 56.For example, the first remote valve assembly, 127 physics are installed on first hydraulic actuator.A pair of pressure transducer 57 provides the signal of pressure in the chamber 19 and 20 of each oil hydraulic cylinder of indication to SC system controller.Remote valve assembly 127 comprises first regeneration flow dividing valve 126 and the first working port blocking valve 128.Automatically controlled proportional-type first regeneration flow dividing valve 126 directly is connected between the port of the hydraulic pressure cavity 19 that is used for first hydraulic actuator 11 and rod end chamber 20.The term ＂ of Shi Yonging directly connects ＂ and is meant that associated components is without any intermediary element herein, for example valve, hole (orifice) or other device, situation under link together by pipeline, described intermediary element flows at any pipeline interior restriction or control fluid beyond restriction.Under off-position, the fluid between the port of two chambers of first regeneration flow dividing valve, 126 partitions, first hydraulic actuator 11 flows, and when energising, inner one-way valve only allows fluid to flow to rod end chamber from hydraulic pressure cavity 19.Alternatively, can use the outside one-way valve of connecting with two-way regeneration flow dividing valve.By regeneration flow dividing valve 126 being positioned to very close first hydraulic actuator 11, make the fluid energy loss under the regeneration mode minimum.
The load that acts on first hydraulic actuator 11 trends towards making piston rod 17 withdrawals, thereby at the hydraulic pressure cavity 19 inner pressure that produce.Under heavily loaded situation, the flexible pipe 55 that is connected on first working port 46 will break, if there is not working port blocking valve 128, release pressure descends load suddenly.Therefore, in off position down, if defective hose, the first working port blocking valve 128 prevents that load from descending.But the pressure-relief valve 129 in the first remote valve assembly 127 prevents that the pressure in the hydraulic pressure cavity from reaching dangerous values.Notice that in the centre or the central position of spool 44, excess pressure flows to fuel tank reflux line 28.
The oil hydraulic circuit relevant with the working port of the 3rd valve portion 33 among Figure 1B has remote valve assembly 140, and it includes only and the 3rd regeneration flow dividing valve 142 of connecting at the hydraulic pressure cavity port and the one-way valve 144 between the rod end chamber port of the 3rd hydraulic actuator 13.The 3rd working port blocking valve 146 near the 3rd valve portion 33 with control fluid flowing between the guiding valve 40 and first working port 46.For example, the 3rd working port blocking valve is installed on the main body 73 of the 3rd valve portion 33.Therefore, the 3rd working port blocking valve 146 is near operator workstation and SC system controller 30.Pressure transducer 57 is connected to the working port 46 and 48 of the 3rd valve portion 33, but not is positioned at remote valve assembly 140 places.This structure decrease need extend to the number of wires of the remote valve assembly 140 of contiguous the 3rd hydraulic actuator 13.But, the 3rd working port blocking valve 146 is placed on the hose fracture protection that the 3rd valve portion 33 places are not provided to be provided in other valve portion.
The 4th valve portion 34 has the oil hydraulic circuit that is different from other valve portion.The middle position of the guiding valve 40 of the 4th valve portion provides first working port 46 and leads to path between the fuel tank return flow line 59 of fuel tank reflux line 28.This finishes by the spool 44 that changes among Fig. 2, makes the recess relevant with the first working port passage 52 extend in the chamber 53 that is communicated with fuel tank return flow line 59.Therefore, at middle position, the flexible pipe 55 that is attached on first working port 46 is connected to fuel tank 22.Pressure-compensated valve 64 is replaced by proof load one-way valve 115, and described one-way valve prevents that fluid from flowing back to supply passage 60 by valve.The 4th valve portion 34 also has the anti-cavitation erosion valve 160 that only is used for its second working port 48 and the structure of working port pressure-relief valve 162, does not have the similar structure that is connected to first working port 46.
The 4th relevant remote valve assembly 170 comprises the 4th regeneration flow dividing valve 172 of connecting with the 4th one-way valve 174 between the port of the port of the hydraulic pressure cavity 19 of the 4th hydraulic actuator 14 and rod end chamber 20.The 4th one-way valve 174 guarantees when regeneration flow dividing valve 172 is opened, and fluid is only along 20 direction flows from hydraulic pressure cavity 19 to rod end chamber.The 4th working port blocking valve 176 is arranged on the port of hydraulic pressure cavity 19 and is connected between the flexible pipe 55 on first working port 46 of the 4th valve portion 34.Pressure-relief valve 178 is in parallel with the 4th working port blocking valve 176, and opens when excess pressure appears in hydraulic pressure cavity 19.When the guiding valve 40 in the 4th valve portion 34 was in middle position, excess pressure was connected to fuel tank return flow line 59 releases of leading to fuel tank reflux line 28 by first flexible pipe 55 with by guiding valve.
The control of the 5th valve portion 35 is used to make the 5th hydraulic actuator 12 of the load that piston rod 17 is tending towards stretching out.The 5th valve portion 35 is similar to the 4th valve portion 34, and the fuel tank reflux line that just lacks the neutral position connects, and has anti-cavitation erosion valve 164 and the working port pressure-relief valve 166 that is connected to first working port 46.The 5th relevant remote valve assembly 180 is identical with the second remote valve assembly 130 and have an identical functions.Therefore, the same parts of the 5th valve portion 35 and the 5th remote valve assembly 180 has the identical reference number of those parts in the corresponding other parts with control valve assembly 26.
In exemplary control valve assembly 26, second end section 37 includes only the different passages 58/59,60,94,95 that extend through valve portion 31-35 and 122 terminal.
Refer again to Figure 1A, first end section 36 has makes pump and fuel tank pipeline 24 and 28 be connected to the port of control valve assembly 26.First end section 36 also comprises several pressure responsive valve, and it is used for the interior pressure of different passages of adjusting control valve assembly.Especially, when the pressure in the service surpassed predetermined first threshold, first pressure-relief valve 150 was connected to service 24 the fuel tank reflux line that is used for fuel tank 22.When the pressure in the load-sensing passage 95 surpassed second threshold value, second pressure-relief valve 152 provided the path that leads to fuel tank reflux line 28.First end section 36 provides a port, is connected to the control input of pump 21 by described port load-sensing passage 95.Pressure regulator valve 154 is connected to five pilot pressure passages 94 among the valve portion 31-35 with service 24, and these passages are remained under the constant pilot pressure of the cardinal principle that is used for operating valve driven plunger 74.
Industrial applicibility
Each hydraulic actuator 11-15 on control valve assembly 26 is operated machines in a similar fashion.For example, the operation of first hydraulic actuator 11 is moved relevant operating handle 29 expressions by the machine worker along operating corresponding direction with hope.This sends signal to SC system controller 30, and described SC system controller responds by applying electric current to the valve in first valve portion 31 and the first remote valve assembly 127, thus the motion that produces associated piston bar 17.The oil hydraulic circuit that is used for first hydraulic actuator 11 and other actuator 12-14 can be operated with different quantitative models, comprise that power stretches out, power retraction, unpowered from regeneration and power regenerating pattern, the selection of making in response to joystick signal and existing situation as controller.Except operating with isolated quantitative model, the quantitative model that the loop of hydraulic actuator can be made up is operated, thereby level and smooth, continuous control to associated actuator are provided.
Stretch out pattern at the power that is used for first hydraulic actuator 11, SC system controller 30 activates first and second electro- hydraulic valves 80 and 81 in first valve portion 31, thereby will impose on the second piston control chamber 76 among Fig. 2 from the pressure fluid of pilot pressure passage 94, simultaneously the pressure in the first piston control chamber 75 will be discharged in the fuel tank 22.This applies the power that makes spool 44 move to a position on valve driven plunger 74, in this position, impose on first working port 46 from the pressure fluid of service 24, and second working port 48 is connected to fuel tank reflux line 28.Especially, spool 44 is positioned to make fluid to flow to first working port 46 from service 24 and supply passage 60 by pressure-compensated valve 64, bridge circuit 68 and the first working port passage 52.Spool position also provides another path that leads to fuel tank reflux line 28 from second working port 48 by the second working port passage 54 and fuel tank path 58.When this happens, the working port blocking valve 128 in the first remote valve assembly 127 among Fig. 1 is also switched on and is opened.This configuration will impose on the hydraulic pressure cavity 19 of first cylinder 16 from the pressure fluid of first working port 46, discharge fluid from rod end chamber 20 simultaneously, thereby make piston rod 17 stretch out cylinder 16 further.
When machine industry control system piston rod 17 was withdrawn in the cylinder 16 of first hydraulic actuator 11, hydraulic system 10 had working power withdrawal pattern or unpowered selection from the withdrawal pattern of regenerating.Under the power retraction pattern, SC system controller 30 activates pressure fluid is imposed on first piston control chamber 75 first and second electro- hydraulic valves 80 and 81, thereby promote valve driven plunger 74 so that second working port 48 of first valve portion 31 is given in spool 44 location therefore from the FLUID TRANSPORTATION of service 24, first working port 46 is connected to fuel tank reflux line 28 by fuel tank return flow line 59 simultaneously.Under this power retraction pattern, the first working port blocking valve 128 is also switched on and is in open mode.In this configuration, pressure fluid imposes on rod end chamber 20, and the release of fluid in the hydraulic pressure cavity is in fuel tank 22.This causes piston rod 17 to be withdrawn in the cylinder 16.
As mentioned previously, the load that the machine part that attaches on first hydraulic actuator 11 is worked is for example owing to the gravity reason applies active force, and it makes piston rod 17 be tending towards being withdrawn in the cylinder 16.Therefore, when wishing piston rod when withdrawal, the active force that can use the outside to apply replaces owing to will impose on the active force that cylinder causes or make its increase from the pressure fluid of supplying with pipeline.
Opposite with the dynamic mode of withdrawal first hydraulic actuator 11, in response to from supplying with and reflux line sensor 25,27 and be connected to the sensor 57 of cylinder chamber 19 and 20, SC system controller 30 is made and is utilized this external force and use unpowered oneself regenerate decision of withdrawal pattern.When these pressure sensor device indication fluids will flow into rod end chamber 20, SC system controller 30 was opened the first working port blocking valve 128 and the regeneration flow dividing valve 126 in the first remote valve assembly 127.This flows directly in the rod end chamber 20 fluid in the hydraulic pressure cavity 19, thereby piston 18 can be moved along the direction of withdrawal piston rod 17.This motion need be from the fluid of service 24, so this is unpowered pattern.
But hydraulic pressure cavity 19 has the volume greater than rod end chamber 20, and this is owing to there is the part of piston rod 17 in a back chamber.Therefore, the excess fluid that flows out hydraulic pressure cavity 19 must be discharged by direction sliding valve 40, at the described direction sliding valve in the neutral position of central authorities first working port 46 is connected to loop 58,59 and reflow pipe 28.Therefore, control the first working port blocking valve 128 flows to fuel tank 22 by direction sliding valve 40 with metering excess fluid.
Utilize the similar operation pattern to be operationally connected to second hydraulic actuator 12 on the second remote valve assembly 130 and second valve portion 32.But the load that acts on this hydraulic actuator is tending towards making its piston rod 17 to stretch out from cylinder 15.Therefore, the second working port blocking valve 134 is connected to the flexible pipe 56 that extends to rod end chamber 20 from second working port 48.Power stretches out with the withdrawal pattern to be operated in the mode identical with first valve portion 31.But, when the pressure in the rod end chamber 20 surpasses the pressure of hydraulic pressure cavity, by being used to can working power to stretch out piston rod from regeneration mode from the active force of load.Under this pattern, open regeneration flow dividing valve 132 so that fluid directly flows to the hydraulic pressure cavity 19 of cylinder 16 from rod end chamber 20.Because rod end chamber 20 less than hydraulic pressure cavity 19, needs additive fluid to fill a back chamber, and this fluid is from service 24.Therefore, stretch out under the pattern from regeneration at power, the direction sliding valve 40 in second valve portion 32 is in the position that makes first working port 46 be connected to service 24 by supply passage 60.When this happens, the second working port blocking valve 134 keeps cutting out to prevent that the fluid in the second remote valve assembly 130 from flowing to fuel tank reflux line 28 by direction sliding valve 40.This pattern is owing to a certain amount of fluid that it consumes from service 24 is called power from regeneration mode.
Because the load active force is tending towards the piston rod of withdrawing, so the 3rd valve portion 33 is to operate with first valve portion, 31 similar modes.But the 3rd valve portion 33 difference structurally is that the 3rd working port blocking valve 146 is near on the 3rd valve portion 33, and is for example mounted thereto, rather than is positioned on the 3rd remote valve assembly 140.Required noticing, the 3rd working port blocking valve 146 is placed on not to be provided near the 3rd valve portion 33 by this valve being placed on the hose fracture protection that flexible pipe actuator end place provides.
Another difference with respect to the 3rd valve portion 33 is that its guiding valve 40 that is in middle position does not provide the path that leads to fuel tank reflux line 28 from first working port 46.Now, for the unpowered excess fluid that flows out from hydraulic pressure cavity 19 from the regeneration mode discharging, except that the 3rd working port blocking valve 146, must activate guiding valve 40.The actuating of guiding valve 40 realizes by making first and second electro- hydraulic valves 80 and 81 energisings, thereby pressure fluid is imposed on the second piston control chamber 76.This motion makes valve driven plunger 74 a small amount of moving with location spool 44 in Fig. 2 left, thereby produces flow passage by the second spool recess 63 and chamber 53 between first working port 46 and fuel tank return flow line 59.Spool 44 moves a short distance, makes the spool recess 61 of winning not lead to the supply passage chamber 65 that is connected with the outlet of pressure-compensated valve 64 yet.Therefore, enter fuel tank 22, and do not impose on hydraulic actuator from the pressure fluid of service 24 from the excess fluid of the hydraulic pressure cavity 19 of the 3rd hydraulic actuator 13.Like this, guiding valve can be used the regenerative operation pattern on as the oil hydraulic circuit of telegoniometer metered valve.
The load that imposes on the 4th hydraulic actuator 14 applies the active force that makes piston rod 17 withdrawals thereon.Therefore, the 4th valve portion 34 equally can with the same way as of before having described with respect to first hydraulic actuator 11 with power stretch out, power retraction and the operation of dynamic measurement pattern.But, be used for oil hydraulic circuit function difference under dead status of the 4th hydraulic actuator 14, be in middle position at this valve 40 of sliding in state, as shown in the figure.This valve element position is closed second working port 48, provides at first working port 46 simultaneously and leads to path between the fuel tank return flow line 59 of fuel tank reflux line 28, thereby the path from the first working port flexible pipe 55 to fuel tank 22 is provided.But during this time, valve 172,176 in the 4th remote valve assembly 170 and 178 closed condition stop the hydraulic pressure cavity of direction of flow the 4th hydraulic actuator 14 and by its outflow.Pressure in hydraulic pressure cavity 19 surpasses pressure-relief valve 178 threshold values to be set, and the guiding valve 40 in the 4th valve portion 34 is under the situation of middle position simultaneously, and pressure-relief valve is opened so that fluid is discharged into return passage and pipeline 59/60 and 28 and fuel tank 22 by guiding valve.
The description of front relates generally to the preferred embodiments of the present invention.Although be concerned about the plurality of optional scheme within the scope of the invention, can expect that those of ordinary skill in the art might realize other possibility, it becomes apparent by disclosing of the embodiment of the invention.For example, the particular valve assembly can have the valve portion of varying number, and all these valve portions are identical or different combinations of five types of 31-35 disclosed herein.Those of ordinary skill in the art can research and develop other valve portion that comprises notion of the present invention.Therefore, scope of the present invention should be determined by following claim, and can't help above-mentioned open the qualification.
Claims (30)
1. oil hydraulic circuit, described oil hydraulic circuit are used for controlling hydraulic actuator with first port and second port and service and the fuel tank reflux line fluid between each and flow, and described oil hydraulic circuit comprises:
Guiding valve, it has the inlet that is connected to service, the outlet that is connected to the fuel tank reflux line, first working port and second working port, wherein guiding valve is guided fluid into first and second working ports one from inlet selectively, and guides fluid another from first and second working ports into outlet selectively;
The working port blocking valve, it is connected to first working port first port of hydraulic actuator; With
Regeneration flow dividing valve, it is connected to hydraulic actuator, and flows between first port and second port by described regeneration flow dividing valve fluid.
2. oil hydraulic circuit as claimed in claim 1 is characterized in that, also comprises the one-way valve of connecting with the regeneration flow dividing valve between first port and second port.
3. oil hydraulic circuit as claimed in claim 1 is characterized in that, also comprises a mechanism, and described mechanism only allows fluid to flow through regeneration flow dividing valve between first port and second port along a direction.
4. oil hydraulic circuit as claimed in claim 1 is characterized in that, described working port blocking valve and regeneration flow dividing valve are away from guiding valve and near the hydraulic actuator setting.
5. oil hydraulic circuit as claimed in claim 1 is characterized in that, described regeneration flow dividing valve is away from guiding valve and near the hydraulic actuator setting; And described working port blocking valve is near the guiding valve setting.
6. oil hydraulic circuit as claimed in claim 1 is characterized in that, described working port blocking valve and regeneration flow dividing valve all are electro-hydraulic valve.
7. oil hydraulic circuit as claimed in claim 1 is characterized in that, described working port blocking valve is a guide operating valve.
8. oil hydraulic circuit as claimed in claim 1 is characterized in that, also comprises the pressure-relief valve that is connected between first working port and the fuel tank reflux line, and opens when the pressure at the first working port place surpasses predetermined value.
9. oil hydraulic circuit as claimed in claim 1 is characterized in that, also comprises first port that is connected hydraulic actuator and the pressure-relief valve between second port, and the pressure in first port is opened when surpassing predetermined value.
10. oil hydraulic circuit as claimed in claim 1 is characterized in that, also comprises the anti-cavitation erosion valve that is connected between first working port and the fuel tank reflux line, and opens in response to the cavitation effect in the hydraulic actuator.
11. oil hydraulic circuit as claimed in claim 1 is characterized in that, also comprises:
First pressure-relief valve, it is connected between first working port and the fuel tank reflux line, and opens when the pressure at the first working port place surpasses predetermined value;
The first anti-cavitation erosion valve, it is connected between first working port and the fuel tank reflux line, and opens in response to the cavitation effect in the hydraulic actuator;
Second pressure-relief valve, it is connected between second working port and the fuel tank reflux line, and opens when the pressure at the second working port place surpasses predetermined value; With
The second anti-cavitation erosion valve, it is connected between second working port and the fuel tank reflux line, and opens in response to the cavitation effect in the hydraulic actuator.
12. oil hydraulic circuit as claimed in claim 1 is characterized in that, also comprises a pressure-compensated valve, it is connected to guiding valve and keeps inlet and the constant pressure drop of cardinal principle between the selected port in first and second working ports.
13. oil hydraulic circuit as claimed in claim 12 is characterized in that, also comprises a load-sensing loop, it is connected to guiding valve and the signal of the force value of wishing in the indication service is provided; And the load-sensing loop is connected to operationally pilot pressure recuperation valve.
14. oil hydraulic circuit as claimed in claim 1 is characterized in that, wherein guiding valve has a state, and wherein first working port is connected to outlet, and stops fluid to flow through second working port; And comprise a pressure-relief valve, when surpassing predetermined value, opens its pressure in parallel with the working port blocking valve and in first port of hydraulic actuator.
15. oil hydraulic circuit as claimed in claim 1 is characterized in that, described guiding valve was connected to the fuel tank reflux line with first working port before second working port is connected to service simultaneously.
16. an oil hydraulic circuit, described oil hydraulic circuit are used for controlling first port and second port of hydraulic actuator and transmit the service of pressure fluid and the fluid of fuel tank reflux line between each flows, described oil hydraulic circuit comprises:
Guiding valve, it has the inlet that is connected to service, the outlet that is connected to the fuel tank reflux line, first working port and second working port, and have fluid and flow to first working port and flow to the primary importance of outlet by measuring hole, and have the second place that fluid flows to second working port and flows to outlet from first working port by measuring hole from inlet from second working port from inlet;
Pressure-compensated valve, the constant pressure drop of cardinal principle that it is connected to guiding valve and keeps passing through measuring hole;
The working port blocking valve, it is connected to first port of hydraulic actuator with first working port, and the fluid of controlling therebetween flows; With
Regeneration flow dividing valve, it is connected to hydraulic actuator, and flows between first port and second port by described regeneration flow dividing valve fluid.
17. oil hydraulic circuit as claimed in claim 16 is characterized in that, described guiding valve has the 3rd position, stops fluid to flow through first working port and second working port in this position.
18. oil hydraulic circuit as claimed in claim 16 is characterized in that, described guiding valve has the 3rd position, is connected to outlet at this position first working port, and stops fluid to flow through second working port; And comprise a pressure-relief valve, when surpassing predetermined value, opens its pressure in parallel with the working port blocking valve and in first port of hydraulic actuator.
19. oil hydraulic circuit as claimed in claim 16 is characterized in that, also comprises the one-way valve of connecting with the regeneration flow dividing valve between first port and second port.
20. oil hydraulic circuit as claimed in claim 16 is characterized in that, also comprises a mechanism, described mechanism only allows fluid to flow through regeneration flow dividing valve between first port and second port along a direction.
21. oil hydraulic circuit as claimed in claim 16 is characterized in that, described working port blocking valve and regeneration flow dividing valve are away from guiding valve and near the hydraulic actuator setting.
22. oil hydraulic circuit as claimed in claim 16 is characterized in that, described regeneration flow dividing valve is away from guiding valve and near the hydraulic actuator setting; And described working port blocking valve is near the guiding valve setting.
23. oil hydraulic circuit as claimed in claim 16 is characterized in that, described working port blocking valve and regeneration flow dividing valve all are electro-hydraulic valve.
24. oil hydraulic circuit as claimed in claim 16 is characterized in that, described working port blocking valve is a guide operating valve.
25. oil hydraulic circuit as claimed in claim 16 is characterized in that, also comprises a pressure-relief valve, it is connected between first working port and the fuel tank reflux line, and opens when the pressure at the first working port place surpasses predetermined value.
26. oil hydraulic circuit as claimed in claim 16 is characterized in that, also comprises a pressure-relief valve, it is connected between first port and second port of hydraulic actuator, and opens when the pressure of first port surpasses predetermined value.
27. oil hydraulic circuit as claimed in claim 16 is characterized in that, also comprises an anti-cavitation erosion valve, it is connected between first working port and the fuel tank reflux line, and opens in response to the cavitation effect in the hydraulic actuator.
28. oil hydraulic circuit as claimed in claim 16 is characterized in that, also comprises:
First pressure-relief valve, it is connected between first working port and the fuel tank reflux line, and opens when the pressure at the first working port place surpasses predetermined value;
The first anti-cavitation erosion valve, it is connected between first working port and the fuel tank reflux line, and opens in response to the cavitation effect in the hydraulic actuator;
Second pressure-relief valve, it is connected between second working port and the fuel tank reflux line, and opens when the pressure at the second working port place surpasses predetermined value; With
The second anti-cavitation erosion valve, it is connected between second working port and the fuel tank reflux line, and opens in response to the cavitation effect in the hydraulic actuator.
29. oil hydraulic circuit as claimed in claim 16 is characterized in that, also comprises a load-sensing loop, it is connected to guiding valve and the signal of required pressure value in the indication service is provided; And pilot pressure recuperation valve.
30. oil hydraulic circuit as claimed in claim 16 is characterized in that, described guiding valve was connected to the fuel tank reflux line with first working port before second working port is connected to service simultaneously.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNA2007101929443A CN101387310A (en) | 2007-09-12 | 2007-09-12 | Hydraulic valve assembly with direction sliding valve and regeneration flow dividing valve with pressure compensation |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNA2007101929443A CN101387310A (en) | 2007-09-12 | 2007-09-12 | Hydraulic valve assembly with direction sliding valve and regeneration flow dividing valve with pressure compensation |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101387310A true CN101387310A (en) | 2009-03-18 |
Family
ID=40476896
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2007101929443A Pending CN101387310A (en) | 2007-09-12 | 2007-09-12 | Hydraulic valve assembly with direction sliding valve and regeneration flow dividing valve with pressure compensation |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN101387310A (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102141062A (en) * | 2011-02-25 | 2011-08-03 | 江苏国瑞液压机械有限公司 | Proportion distribution dual induction and dual damping pressure compensator |
| CN102498320A (en) * | 2009-09-22 | 2012-06-13 | 伊顿公司 | Spool valve |
| CN102864798A (en) * | 2012-10-22 | 2013-01-09 | 三一重机有限公司 | Bucket rod regeneration structure and excavator |
| CN106762900A (en) * | 2016-11-25 | 2017-05-31 | 合肥协力液压科技有限公司 | A kind of hydraulic valve |
| CN110477999A (en) * | 2019-08-29 | 2019-11-22 | 湖南瀚德微创医疗科技有限公司 | A kind of surgical clamp exporting constant clamping force |
| CN110552928A (en) * | 2019-09-24 | 2019-12-10 | 江苏徐工工程机械研究院有限公司 | Integrated valve and floating hydraulic system |
| CN111226046A (en) * | 2018-03-09 | 2020-06-02 | Ｋｙｂ株式会社 | Control valve |
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2007
- 2007-09-12 CN CNA2007101929443A patent/CN101387310A/en active Pending
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102498320A (en) * | 2009-09-22 | 2012-06-13 | 伊顿公司 | Spool valve |
| US8464756B2 (en) | 2009-09-22 | 2013-06-18 | Eaton Corporation | Spool valve |
| CN102498320B (en) * | 2009-09-22 | 2013-10-23 | 伊顿公司 | Spool valve |
| CN102141062A (en) * | 2011-02-25 | 2011-08-03 | 江苏国瑞液压机械有限公司 | Proportion distribution dual induction and dual damping pressure compensator |
| CN102864798A (en) * | 2012-10-22 | 2013-01-09 | 三一重机有限公司 | Bucket rod regeneration structure and excavator |
| CN102864798B (en) * | 2012-10-22 | 2015-01-14 | 三一重机有限公司 | Bucket rod regeneration structure and excavator |
| CN106762900A (en) * | 2016-11-25 | 2017-05-31 | 合肥协力液压科技有限公司 | A kind of hydraulic valve |
| CN111226046A (en) * | 2018-03-09 | 2020-06-02 | Ｋｙｂ株式会社 | Control valve |
| CN111226046B (en) * | 2018-03-09 | 2022-03-15 | Ｋｙｂ株式会社 | Control valve |
| CN110477999A (en) * | 2019-08-29 | 2019-11-22 | 湖南瀚德微创医疗科技有限公司 | A kind of surgical clamp exporting constant clamping force |
| CN110552928A (en) * | 2019-09-24 | 2019-12-10 | 江苏徐工工程机械研究院有限公司 | Integrated valve and floating hydraulic system |
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Application publication date: 20090318 |