CN100445576C - Hydraulic loop of building machinery - Google Patents
Hydraulic loop of building machinery Download PDFInfo
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- CN100445576C CN100445576C CNB2005100527167A CN200510052716A CN100445576C CN 100445576 C CN100445576 C CN 100445576C CN B2005100527167 A CNB2005100527167 A CN B2005100527167A CN 200510052716 A CN200510052716 A CN 200510052716A CN 100445576 C CN100445576 C CN 100445576C
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- H—ELECTRICITY
- H04—ELECTRIC COMMUNICATION TECHNIQUE
- H04M—TELEPHONIC COMMUNICATION
- H04M1/00—Substation equipment, e.g. for use by subscribers
- H04M1/02—Constructional features of telephone sets
- H04M1/0202—Portable telephone sets, e.g. cordless phones, mobile phones or bar type handsets
- H04M1/026—Details of the structure or mounting of specific components
- H04M1/0264—Details of the structure or mounting of specific components for a camera module assembly
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- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01R—ELECTRICALLY-CONDUCTIVE CONNECTIONS; STRUCTURAL ASSOCIATIONS OF A PLURALITY OF MUTUALLY-INSULATED ELECTRICAL CONNECTING ELEMENTS; COUPLING DEVICES; CURRENT COLLECTORS
- H01R31/00—Coupling parts supported only by co-operation with counterpart
- H01R31/06—Intermediate parts for linking two coupling parts, e.g. adapter
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- H—ELECTRICITY
- H04—ELECTRIC COMMUNICATION TECHNIQUE
- H04N—PICTORIAL COMMUNICATION, e.g. TELEVISION
- H04N23/00—Cameras or camera modules comprising electronic image sensors; Control thereof
- H04N23/50—Constructional details
- H04N23/51—Housings
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Abstract
The invention efficiently supplys pressure oil from a third pump so as to improve work efficiency of a construction machine by combining it with a first line to which pressure oil from a first pump is supplied, and a second line to which pressure oil from a second pump is supplied. In a first combined flow passage 38, pressure oil from the third pump 13 can be supplied to a first unloading passage 31 in the first line. In a second combined flow passage 39, pressure oil from the third pump 13 can be supplied to a second supply passage 34 in the second line. In a discharge passage 40, a restrictor is formed, and the first combined flow passage 38, the second combined flow passage 39, and a tank are connected.
Description
Technical field
The present invention relates to a kind of oil hydraulic circuit of building machinery, it has: the 1st system comprises the 1st direction switching valve that is supplied to from the pressure oil of the 1st pump; The 2nd system comprises the 2nd direction switching valve that is supplied to from the pressure oil of the 2nd pump; The 3rd system comprises the 3rd direction switching valve that is supplied to from the pressure oil of the 3rd pump.
Background technique
Oil hydraulic circuit as existing building machinery generally has: the 1st system, and described the 1st system comprises: the 1st direction switching valve is supplied to the pressure oil from the 1st pump; The 2nd system, described the 2nd system comprises: the 2nd direction switching valve is supplied to the pressure oil from the 2nd pump; The 3rd system, described the 3rd system comprises: the 3rd direction switching valve is supplied to the pressure oil (with reference to patent documentation 1,2,3) from the 3rd pump.Be recorded in the oil hydraulic circuit in these patent documentations, its 1st system has: the 1st direction switching valve of centre by-pass type; The 1st off-load path is connected on the 1st pump and by the 1st direction switching valve and is communicated with on fuel tank; The 1st supply passage, branch is in the 1st off-load path and to the 1st direction switching valve supply pressure oil.Again, the 2nd system has: the 2nd direction switching valve; The 2nd supply passage is to the pressure oil of the 2nd direction switching valve supply from the 2nd pump; The 3rd system has: the 3rd direction switching valve.
Te Kaiping 10-88627 communique (claims)
Patent documentation 2
The spy opens clear 63-7425 communique (the 5th page, Fig. 1)
Patent documentation 3
The spy opens clear 60-211522 communique (Fig. 2)
In the oil hydraulic circuit that is recorded in patent documentation 1, when pivoted arm drives, with the 1st and the 3rd pump supply pressure oil, when cantilever drives, with the 2nd and the 3rd pump supply pressure oil, that is, optionally collaborate pivoted arm with direction switching valve or cantilever direction switching valve from the pressure oil of the 3rd pump.And (when operating pivoted arm usefulness direction switching valve and cantilever usefulness direction switching valve simultaneously) only preferentially supplied to cantilever direction switching valve from the pressure oil of the 3rd pump when pivoted arm and cantilever drove simultaneously.But, in this oil hydraulic circuit, operate cantilever simultaneously with direction switching valve and pivoted arm during with the direction switching valve, pivoted arm direction switching valve can not be supplied to from the pressure oil of the 3rd pump, thereby pivoted arm can not be quickened to drive.That is, when operating the 2nd direction switching valve of the 1st direction switching valve of the 1st system and the 2nd system simultaneously, can not supply to two direction switching valves simultaneously from the pressure oil of the 3rd pump, thereby cause the low drawback of operating efficiency of building machinery.
Again, in the oil hydraulic circuit that is recorded in patent documentation 2, operate operation actuator that non-left and right sides travel motor uses with switching valve promptly the 1st direction switching valve of the 1st system and operation actuator that non-left and right sides travel motor is used with switching valve promptly in the 2nd direction switching valve of the 2nd system at least one of them the time, supply to the 1st direction switching valve and the 2nd direction switching valve from the pressure oil of the 3rd pump.But, from the pressure oil of the 3rd pump when the 1st and the 2nd direction switching valve is supplied with, because being communicated with the off-load path (fuel tank of patent documentation 2 is communicated with oil circuit 26) of the 3rd system on fuel tank closes, so under the few situation of the pressure oil of one of them use at least in the 1st and the 2nd direction switching valve, can cause the load on the 3rd pump to become big drawback.Again, in the oil hydraulic circuit that is recorded in patent documentation 3, between the pivoted arm acceleration valve 22 in the downstream side that is positioned at service pump P3 (the 3rd pump) and the control valve 11 that cantilever is used (the 1st direction switching valve), the path that is communicated with on fuel tank is connected with cantilever acceleration stream 23 always.Therefore, even under the abundant situation of the pressure oil that cantilever uses with direction switching valve (the 1st direction switching valve), the drawback that also can cause the pressure oil from the 3rd pump almost can not be supplied to.
Summary of the invention
The present invention considers the problems referred to above and makes, its purpose is to provide a kind of oil hydraulic circuit of building machinery, have the 1st to the 3rd system, described the 1st to the 3rd system is connected on each pump of the 1st to the 3rd, by collaborating efficiently from the pressure oil of the 3rd pump and supplying to the operating efficiency that the 1st system and the 2nd system improve building machinery, aforementioned the 1st system is supplied to the pressure oil from the 1st pump, and aforementioned the 2nd system is supplied to the pressure oil from the 2nd pump.
The oil hydraulic circuit of building machinery of the present invention has: the 1st system, and described the 1st system comprises: the 1st direction switching valve of centre by-pass type is supplied to the pressure oil from the 1st pump; The 1st off-load path is connected on aforementioned the 1st pump, also is communicated with on fuel tank by aforementioned the 1st direction switching valve; The 1st supply passage, branch is in aforementioned the 1st off-load path and to aforementioned the 1st direction switchable pump supply pressure oil; The 2nd system, described the 2nd system comprises: the 2nd direction switching valve is supplied to the pressure oil from the 2nd pump; The 2nd supply passage is to the pressure oil of the 2nd direction switching valve supply from aforementioned the 2nd pump; The 3rd system, described the 3rd system comprises: the 3rd direction switching valve is supplied to the pressure oil from the 3rd pump.
And the oil hydraulic circuit of building machinery of the present invention to achieve these goals, has following several characteristic.That is, oil hydraulic circuit of the present invention has following feature individually, perhaps has to appropriate combination following feature.
To achieve these goals, the 1st feature of the oil hydraulic circuit of building machinery of the present invention is to have: the 1st interflow path, can supply with pressure oil to aforementioned the 1st off-load path of aforementioned the 1st system from aforementioned the 3rd pump; The 2nd interflow path can be supplied with pressure oil from aforementioned the 3rd pump to aforementioned the 2nd supply passage of aforementioned the 2nd system; Drain passageway connects aforementioned the 1st interflow path and aforementioned the 2nd interflow path and fuel tank and is formed with throttle valve; The interflow switching valve, described interflow switching valve has: be communicated with the position, eject pressure oil, restriction site by aforementioned drain passageway to fuel tank, cut off aforementioned drain passageway or compare the discharge flow rate that more limits to fuel tank with aforementioned connection position from aforementioned the 3rd pump; When aforementioned the 2nd direction switching valve of the regulation of aforementioned the 2nd system of operation, aforementioned switching valve switches to the aforementioned limitations position from aforementioned connection position.
According to such formation, during in inoperation the 1st direction switching valve and the 2nd direction switching valve any one, discharge from the 1st off-load path of drain passageway and the 1st system from the pressure oil of the 3rd pump.Therefore, can be suppressed at the high load of generation on the 3rd pump.Again, inoperation the 2nd direction switching valve and when operating the 1st direction switching valve collaborates the 1st system from the pressure oil of the 3rd pump, and in the pressure oil from the 3rd pump, except being fed into the pressure oil of the 1st direction switching valve, remaining pressure oil is discharged from drain passageway.Its result in this case, also can be suppressed at the high load of generation on the 3rd pump.Again, during the 2nd direction switching valve of inoperation the 1st direction switching valve and operating provision, the 2nd system of collaborating regulation from the pressure oil of the 3rd pump, and in pressure oil from the 3rd pump, except the pressure oil of the 2nd direction switching valve that is fed into regulation, remaining pressure oil is all discharged from the 1st off-load path of the 1st system.Its result in this case, also can be suppressed at the high load of generation on the 3rd pump.Again, when operating the 2nd direction switching valve of the 1st direction switching valve and regulation simultaneously, pressure oil from the 3rd pump is cut off on drain passageway or is limited, and is not to discharge from the 1st off-load path, but interflow and supply to the 1st direction switching valve and the 2nd direction switching valve.As mentioned above,, the load of the 3rd pump is increased to more than the admissible value, can collaborate pressure oil efficiently and supply to the 1st system and the 2nd system, thereby improve the operating efficiency of building machinery from the 3rd pump no matter under the sort of situation.
The 2nd feature of the oil hydraulic circuit of building machinery of the present invention is, as aforementioned the 1st direction switching valve, has pilot pressure oil to the cantilever of the supply of cantilever pressure cylinder direction switching valve, the 2nd direction switching valve as aforementioned regulation, having pilot pressure oil uses direction switching valve and pilot pressure oil to the piston of the supply of piston pressure cylinder direction switching valve to the pivoted arm of the supply of pivoted arm pressure cylinder, be operated into when drawing position and this piston to be operated on the piston unloaded position one of them with the direction switching valve on the pivoted arm with the direction switching valve being in this pivoted arm, aforementioned interflow switching valve switches to the aforementioned limitations position.
According to such formation, carry out in pulling process on the pivoted arm and the piston off-load operation one of them when operating, because the interflow switching valve switches to restriction site, so can supply to pressure oil efficiently pivoted arm the direction switching valve and the piston direction switching valve of the 2nd system from the 3rd pump.
The 3rd feature of the oil hydraulic circuit of building machinery of the present invention is, aforementioned interflow switching valve is with corresponding to the operation amount of the 2nd direction switching valve of aforementioned regulation and change the mode of stroke proportionally, switch to the aforementioned limitations position, and the valve opening that is connected on the aforementioned drain passageway reduces corresponding to the stroke of aforementioned interflow switching valve, and the valve opening that is connected on aforementioned the 1st interflow path also reduces corresponding to the stroke of aforementioned interflow switching valve.
According to such formation, because can improve the allotment ratio of supplying with to the 2nd system from the pressure oil of the 3rd pump, so can supply to pressure oil efficiently the 2nd direction switching valve from the 3rd pump corresponding to the operation amount of the 2nd direction switching valve of stipulating.
Description of drawings
Fig. 1 is the figure of oil hydraulic circuit of the building machinery of expression embodiments of the present invention.
Fig. 2 is the partial enlarged drawing of oil hydraulic circuit as shown in Figure 1.
Fig. 3 is the operation amount of the 2nd direction switching valve in the oil hydraulic circuit of representing as shown in Figure 1, regulation, and the schematic representation that is equipped with the relation between the valve opening in the stroke of interflow switching valve and the interflow switching valve.
Embodiment
Below, with reference to description of drawings preferred implementation of the present invention.Fig. 1 is the figure of oil hydraulic circuit of the building machinery of expression embodiments of the present invention.The building machinery of using the oil hydraulic circuit 1 (below, be called oil hydraulic circuit 1) of this building machinery is the track-laying vehicle that has various actuators such as pivoted arm or cantilever, and it has each oil hydraulic motor or each pressure cylinder that drives these actuators.And this building machinery has the 1st pump 11 (P1), the 2nd pump 12 (P2) and the 3rd pump 13 (P3), and described the 1st pump 11 (P1), the 2nd pump 12 (P2) and the 3rd pump 13 (P3) supply to pressure oil in the 1st to the 3rd system that oil hydraulic circuit 1 had respectively.
As shown in Figure 1, oil hydraulic circuit 1 has: the 1st system, be connected with a plurality of centre by-pass type the 1st direction switching valves (21,22,23), and described the 1st direction switching valve (21,22,23) is supplied to the pressure oil from the 1st pump 11; The 2nd system is connected with a plurality of the 2nd direction switching valves (24,25,26), and described the 2nd direction switching valve (24,25,26) is supplied to the pressure oil from the 2nd pump 12; The 3rd system is connected with a plurality of the 3rd direction switching valves (27,28,29), and described the 3rd direction switching valve (27,28,29) is supplied to the pressure oil from the 3rd pump 13.22,23 parallel connections of the 1st direction switching valve, the 1st direction switching valve 22,23 is connected with the 1st direction switching valve 21.25,26 parallel connections of the 2nd direction switching valve, the 2nd direction switching valve 25,26 is connected with the 2nd direction switching valve 24.27,28,29 parallel connections of the 3rd direction switching valve.
The 1st system has: the 1st direction switching valve (21,22,23); The 1st off-load path 31 is connected on the 1st pump 11, also is communicated with fuel tank (T1, T2) by the 1st direction switching valve (21,22,23); The 1st supply passage 32, branch is in the 1st off-load path 31, also respectively to the 1st direction switching valve (22,23) supply pressure oil.Again, dispose right lateral and advance with direction switching valve 21, described right lateral advances with direction switching valve 21 to be set at upstream, and the supply of travel motor to the right of pilot pressure oil.The 1st direction switching valve has: cantilever direction switching valve 22, and pilot pressure oil is to the supply of the cantilever pressure cylinder 16 that makes the cantilever action; Auxiliary with direction switching valve 23.
The 2nd system has: the 2nd direction switching valve (24,25,26); The 2nd off-load path 33 is connected on the 2nd pump 12, also is communicated with on fuel tank (T1, T2) by the 2nd direction switching valve (24,25,26); The 2nd supply passage 34 is to the pressure oil of the 2nd direction switching valve (25,26) supply from the 2nd pump 12.The 2nd supply passage 34 is connected on the 2nd off-load path 33.Again, dispose left lateral and advance with direction switching valve 24, described left lateral advances with direction switching valve 24 to be set at upstream, and the supply of travel motor left of pilot pressure oil.The 2nd direction switching valve has: pivoted arm direction switching valve 25, and pilot pressure oil is to the supply of the pivoted arm pressure cylinder 17 that makes the pivoted arm action; Piston direction switching valve 26, pilot pressure oil is to the supply of the piston pressure cylinder 18 that makes piston action.
The 3rd system has: the 3rd direction switching valve (27,28,29); The 3rd supply passage 36 is to the pressure oil of the 3rd direction switching valve (27,28,29) supply from the 3rd pump 13; Centre by-pass path 37 is communicated with the 3rd direction switching valve (27,28,29).Again, the 3rd direction switching valve (27,28,29) has: the pivoted arm swing is supplied with to the pressure oil of pivoted arm swing (B/ swing) pressure cylinder 14 that the pivoted arm wobbling action is used with direction switching valve 27, control; Blade is supplied with to the pressure oil of the blade pressure cylinder 15 that makes the blade action with direction switching valve 28, control; Rotation is supplied with to the pressure oil of revolution motor with direction switching valve 29, control.
Again, oil hydraulic circuit 1 has the 1st interflow path the 38, the 2nd interflow path 39, drain passageway 40 and interflow switching valve 30.The 1st interflow path 38 can be supplied with pressure oil from the 3rd pump 13 to the 1st off-load path 31 of the 1st system.The 1st interflow path 38 can be communicated with the downstream side of the centre by-pass path 37 of the 3rd system by interflow switching valve 30, and between right lateral advances with direction switching valve 21 and cantilever usefulness direction switching valve 22, is connected with the 1st off-load path 31.The 2nd interflow path 39 can be supplied with pressure oil from the 3rd pump 13 to the 2nd supply passage 34 of the 2nd system.The 2nd interflow path 39 can be communicated with the centre by-pass path 37 of the 3rd system by interflow switching valve 30, and is connected on the supply passage 34.
Drain passageway 40 couples together the downstream side and the fuel tank (T1, T2) of centre by-pass path 37.Fig. 2 be expression interflow switching valve 30 with its near the hydraulic circuit diagram of path, as Fig. 1 and shown in Figure 2, drain passageway 40 by be formed at path in the interflow switching valve 30, with, be connected and collaborate on the switching valve 30 and the path that is communicated with on fuel tank constitutes.In the switching valve 30 of interflow, on drain passageway 40, be formed with throttle valve 41 again.
In Fig. 1 and Fig. 2, interflow switching valve 30 is connected the downstream side of the centre by-pass path 37 of the 3rd system, and is connected on the 1st interflow path 38 and the 2nd interflow path 39.In the switching valve 30 of interflow, form a part of drain passageway 40, and interflow switching valve 30 is connected with the drain passageway 40 that forms outside it.This interflow switching valve 30 has position of connection 42 and restriction site 43 (43a, 43b), and can switch by between.Be communicated with on the position 42, be communicated with the downstream side and the fuel tank (T1, T2) of centre by-pass path 37.And, on restriction site 43 (43a, 43b), cut off the 1st interflow path 38 and the 2nd interflow path 39 and fuel tank (T1, T2), perhaps limit discharge flow rate to fuel tank.When the 2nd direction switching valve of the regulation of operation the 2nd system (pivoted arm with direction switching valve 25 and piston with direction switching valve 26), this interflow switching valve 30 switches to restriction site 43 from being communicated with position 42.
Then, describe formation and its action of switching this interflow switching valve 30 in detail.At first, be under the state that the neutral position promptly is communicated with position 42 at interflow switching valve 30, be in following state: the downstream side of the centre by-pass path 37 of the 3rd system, all be in connected state with the 1st interflow path 38 and the 2nd interflow path 39, drain passageway 40, four from the pressure oil of the 3rd pump 13.Thereby, in this case, to cantilever with direction switching valve 22 and auxiliary with direction switching valve 23 (the 1st direction switching valve), and pivoted arm when not operating with any one of direction switching valve 26 (the 2nd direction switching valve of regulation) with direction switching valve 25 and piston, pressure oil from the 3rd pump 13 is discharged from the 1st off-load path 31 of drain passageway 40 and the 1st system, aforementioned cantilever is connected with the 1st interflow path 38 via the 1st off-load path 31 with direction switching valve 22, and aforementioned pivoted arm is connected with direction switching valve 25 and the 2nd interflow path 39.Therefore, can be suppressed at the high load of generation on the 3rd pump 13.
Again, to pivoted arm with direction switching valve 25 and piston with direction switching valve 26 in any one of (the 2nd direction switching valve of regulation) do not operate and when operating in the 1st direction switching valve (22,23) any one, interflow switching valve 30 remains on connection position 42, the 1 off-load paths 31 and is cut off or is limited flow.And, collaborate the 1st system from the pressure oil of the 3rd pump 13, and supply to this operated the 1st direction switching valve (22,23).Again, in the pressure oil from the 3rd pump 13, except being fed into the pressure oil of the 1st direction switching valve (22,23), remaining pressure oil is discharged from drain passageway 40 by throttle valve 41.In addition, be not cut off but under by the state of throttling at the 1st off-load path 31, aforementioned remaining pressure oil is also discharged from the 1st off-load path 31.Its result in this case, collaborates the 2nd system efficiently from the pressure oil of the 3rd pump 13, and can be suppressed at the high load of generation on the 3rd pump 13.
Again, at inoperation the 1st direction switching valve (22,23) and the operation pivoted arm with direction switching valve 25 and piston with in the direction switching valve 26 at least any one the time, collaborate the 2nd system from the pressure oil of the 3rd pump.That is, by the 2nd interflow path 39 and the 2nd supply passage 34, to this operated pivoted arm direction switching valve 25 and the piston pressure oil of direction switching valve 26 supplies from the 3rd pump.Specifically, pivoted arm is operated into when drawing the position on the pivoted arm with direction switching valve 25, and interflow switching valve 30 switches to restriction site 43a, when piston is operated into the piston unloaded position with direction switching valve 26, collaborates switching valve 30 and switches to restriction site 43b.Pivoted arm carries out based on control signal with the switching of direction switching valve 26 with direction switching valve 25 and piston, pivoted arm is operated into when drawing position, this control signal Pa8 that it is sent control on the pivoted arm with direction switching valve 25, this control signal Pa8 also sends control to interflow switching valve 30, thereby interflow switching valve 30 switches to restriction site 43a.On the other hand, when piston was operated into piston unloaded position, this control signal Pb10 it is sent control with direction switching valve 26, this control signal Pb10 also sent control to interflow switching valve 30, thereby interflow switching valve 30 switches to restriction site 43b.Switch to restriction site 43 (43a, 43b) by collaborating switching valve 30, drain passageway 40 just is cut off or is limited the discharge flow rate to fuel tank, thereby in pressure oil from the 3rd pump 13, except the pressure oil of the 2nd direction switching valve (25,26) that is fed into regulation, remaining pressure oil is discharged by the 1st off-load path 31 of the 1st system.Its result in this case, also collaborates the 2nd system efficiently from the pressure oil of the 3rd pump 13, and can be suppressed at the high load of generation on the 3rd pump 13.In addition, at the same time pivoted arm is operated with direction switching valve 25 and drawn the position on the pivoted arm and piston is operated with direction switching valve 26 under the situation of piston unloaded position, interflow switching valve 30 constitutes any one that can switch among restriction site 43a and the restriction site 43b.
Again, operate simultaneously in the 1st direction switching valve (22,23) at least one of them, with the regulation the 2nd direction switching valve (25,26) at least one of them the time, the 1st off-load path 31 is cut off or is limited flow, and operating under the situation of drawing position and piston unloaded position on the pivoted arm, interflow switching valve 30 switches to restriction site 43.Therefore, pressure oil from the 3rd pump 13, on drain passageway 40, be cut off or be limited discharge flow rate, and also on the 1st off-load path 31, be cut off or limit discharge flow rate, thereby collaborate and supply to the 2nd direction switching valve (25,26) of operated the 1st direction switching valve (22,23) and regulation.
Like this, to the 1st direction switching valve (22,23) and the regulation the 2nd direction switching valve (25, when any one 26) do not operated, the 2nd direction switching valve (25 of inoperation regulation, 26) operate the 1st direction switching valve (22,23) time or inoperation the 1st direction switching valve (22,23) and the 2nd direction switching valve of operating provision (25,26) time, to the 1st direction switching valve (22,23) and the regulation the 2nd direction switching valve (25, when 26) all operating, promptly, no matter under which kind of situation, the load on the 3rd pump 13 can not increase to above its admissible value.And, can collaborate pressure oil efficiently and supply to the 1st system and the 2nd system, thereby improve the operating efficiency of the building machinery of using oil hydraulic circuit 1 from the 3rd pump.
Again, in this oil hydraulic circuit 1, be respectively arranged with travel motor with direction switching valve (21,24) in the upstream of the 1st system and the 2nd system, in each system, travel motor is connected with other direction switching valve with direction switching valve (21,24).Therefore, to travel motor with direction switching valve (21,24) when switching, from the 1st pump 11 and the 2nd pump 12 and the pressure oil that comes supplies to each travel motor with direction switching valve (21,24), reduce with other the pressure oil of direction switching valve beyond the direction switching valve thereby supply to travel motor.In this case, as mentioned above, can supply to pressure oil efficiently these other direction switching valve from the 3rd pump 13.
Again, (when driving left and right sides travel motor) carries out the operation of drawing on the pivoted arm if when building machinery is advanced, then because on draw pivoted arm and cause uprising to the load of pivoted arm with the pump of direction switching valve 25 supply pressure oil.But, in this oil hydraulic circuit 1, when carrying out on the pivoted arm pulling process, can switch to restriction site 43a to interflow switching valve 30, close drain passageway 40, and increase and also collaborate pressure oil from of the supply of the 3rd pump 13, so can prevent to spur on the pivoted arm reduction (operating efficiency is low) of the speed of doing to pivoted arm usefulness direction switching valve 25.On the other hand, when carrying out the drop-down action of pivoted arm, because the deadweight of pivoted arm and drop-down, so few with the load of the pump of direction switching valve 25 supply pressure oil to pivoted arm.Therefore, interflow switching valve 30 is not switched to restriction site 43, do not supply with ground, collaborate to supply with from the pressure oil of the 3rd pump thereby do not close drain passageway 40 and do not increase from the pressure oil of the 3rd pump.Again, the situation of carrying out piston off-load action and the drop-down action of pivoted arm simultaneously is a lot, so at this moment need abundant pressure oil.Therefore, piston switches to the piston unloaded position with direction switching valve 26, and interflow switching valve 30 switches to restriction site 43b, thereby can close drain passageway 40, pressure oil from the 3rd pump 13 is supplied to piston direction switching valve 26 efficiently, and use pressure oil efficiently from the 3rd pump 13.Like this, in oil hydraulic circuit 1, carry out in pulling process on the pivoted arm and the piston off-load operation at least one of them the time, because interflow switching valve 30 switches to restriction site 43, so can supply to pressure oil efficiently the pivoted arm of the 2nd system direction switching valve 25 and piston direction switching valve 26 from the 3rd pump 13.
Again, in oil hydraulic circuit 1, the control signal when operating by direction switching valve (25,26) separately carries out interflow switching valve 30 is switched to the timing of restriction site 43.Therefore, for the direction switching valve, needn't be provided with Auxiliary valves, again, because needn't be provided with the control access in addition, so can suppress oil hydraulic circuit and all directions switching valve complicates.
In addition, interflow switching valve 30 switches to restriction site 43 to change the mode of stroke corresponding to the operation amount of the 2nd direction switching valve of stipulating (25,26) proportionally from being communicated with position 42.And in this interflow switching valve 30, the valve opening that is connected on the drain passageway 40 reduces corresponding to the stroke of interflow switching valve 30, and the valve opening that is connected on the 1st interflow path 38 also reduces corresponding to the stroke of interflow switching valve 30.
Fig. 3 be the 2nd direction switching valve (25,26) of expression regulation operation amount, with interior each valve opening (valve opening area) of the stroke of interflow switching valve 30 and interflow switching valve 30 between the schematic representation of relation.As shown in Figure 3, the pulling process quantitative change is big on the pivoted arm, and the stroke and this operation amount that then collaborate switching valve 30 together change pro rata, and interflow switching valve 30 switches to restriction site 43a side, corresponding to the above mentioned facts, the drain passageway side aperture (opening area) that is connected on the drain passageway 40 reduces.Again, under the big situation of piston off-load operation quantitative change, the stroke of interflow switching valve 30 also together changes pro rata with this operation amount, and interflow switching valve 30 switches to restriction site 43b, and corresponding to the above mentioned facts, drain passageway side aperture reduces.And no matter under which kind of situation, if the stroke of interflow switching valve 30 arrives the position of regulation, then drain passageway side aperture is closed, and drain passageway 40 is cut off.Again, similarly, pulling process amount and piston off-load operation amount together change pro rata on the stroke of interflow switching valve 30 and the pivoted arm, and then corresponding to the above mentioned facts, the 1st interflow passage side aperture (opening area) that is connected on the 1st interflow path 38 reduces.On the other hand, in the switching valve 30 of interflow, be connected the 2nd interflow interflow passage side aperture of the 2nd on the path 39 (opening area) and remain unchanged, be in interflow switching valve 30 that to be communicated with position 42 still be that restriction site 43 has nothing to do.
Like this, in oil hydraulic circuit 1, interflow switching valve 30 makes to become following structure: corresponding to pivoted arm on pulling process amount and the piston off-load operation amount stroke of change pro rata together, and reduce drain passageway side aperture and the 1st interflow passage side aperture, and the 2nd interflow passage side aperture is remained unchanged.With this, just can improve the allotment ratio of the 2nd system that flows into from the pressure oil of the 3rd pump 13 corresponding to the operation amount of the 2nd direction switching valve of stipulating (25,26).Therefore, can supply to pressure oil efficiently the 2nd direction switching valve (25,26) from the 3rd pump 13.In addition,, be formed with throttle valve 45 (with reference to Fig. 2), and it is bigger than the 1st interflow passage side aperture always to be set to the 2nd interflow passage side aperture being positioned on the drain passageway 40 that is connected the interflow switching valve 30 on the 1st interflow path 38.With this, even when the cantilever of inoperation the 1st system is used direction switching valve 22, the pressure oil that also can limit from the 3rd pump 13 turns back to the oil mass of fuel tank from the 1st off-load path 31 of the 1st system, and the pressure oil from the 3rd pump 13 is collaborated and supplies to the pivoted arm direction switching valve 25 of the 2nd system efficiently.
More than, embodiments of the present invention have been described, still, the present invention is not limited to above-mentioned mode of execution, certainly carries out all changes in being recorded in the scope of claims.For example, can carry out following change.
In the present embodiment, the interflow switching valve is connected the downstream side of the 3rd direction switching valve, and to be connected the upstream side of the 3rd direction switching valve also passable but collaborate switching valve.
Again, in the present embodiment, carrying out to the operation of drawing the position on the pivoted arm and in the timing of the operation of piston unloaded position, constituting from being communicated with the position of interflow switching valve switches to restriction site, but in other timing, it is also passable that it switches to restriction site.For example, just carrying out to the operation of drawing the position on the pivoted arm or in the timing of the operation of piston unloaded position, it is also passable that the interflow switching valve switches to restriction site, again, when the 1st direction switching valve is operated into beyond the neutral position, perhaps, when travel motor was operated into beyond the neutral position with the direction switching valve, it switched to all mode of executions such as restriction site and also can.
And then pilot pressure Pb8 and Pb10 constitute from same directive effect also passable in the interflow switching valve.
Claims (3)
1. the oil hydraulic circuit of a building machinery has:
The 1st system, it comprises: the 1st direction switching valve of centre by-pass type is supplied to the pressure oil from the 1st pump; The 1st off-load path is connected on aforementioned the 1st pump, also is communicated with on fuel tank by aforementioned the 1st direction switching valve; The 1st supply passage, branch is in aforementioned the 1st off-load path and to aforementioned the 1st direction switchable pump supply pressure oil;
The 2nd system, it comprises: the 2nd direction switching valve is supplied to the pressure oil from the 2nd pump; The 2nd supply passage is to the pressure oil of the 2nd direction switching valve supply from aforementioned the 2nd pump;
The 3rd system, it comprises: the 3rd direction switching valve is supplied to the pressure oil from the 3rd pump;
It is characterized in that, comprising: the 1st interflow path, can supply with pressure oil to aforementioned the 1st off-load path of aforementioned the 1st system from aforementioned the 3rd pump;
The 2nd interflow path can be supplied with pressure oil from aforementioned the 3rd pump to aforementioned the 2nd supply passage of aforementioned the 2nd system;
Drain passageway is connected with aforementioned the 1st interflow path and aforementioned the 2nd interflow path and fuel tank, and is formed with throttle valve;
The interflow switching valve has: be communicated with the position, eject pressure oil from aforementioned the 3rd pump by aforementioned drain passageway to fuel tank, and be communicated with aforementioned the 1st interflow path and aforementioned the 2nd interflow path; Restriction site cuts off aforementioned drain passageway or compares the discharge flow rate that more limits to fuel tank with aforementioned connection position;
When aforementioned the 2nd direction switching valve of the regulation of not operating aforementioned the 2nd system, the pressure oil of aforementioned the 3rd pump is discharged from aforementioned the 1st off-load path of aforementioned drain passageway and aforementioned the 1st system,
When aforementioned the 2nd direction switching valve of the regulation of aforementioned the 2nd system of operation, aforementioned interflow switching valve switches to the aforementioned limitations position from aforementioned connection position.
2. the oil hydraulic circuit of building machinery as claimed in claim 1 is characterized in that,
Aforementioned interflow switching valve has the 1st restriction site and the 2nd restriction site is used as the aforementioned limitations position,
As aforementioned the 1st direction switching valve, have pilot pressure oil to the cantilever of the supply of cantilever pressure cylinder direction switching valve,
As the 2nd direction switching valve of aforementioned regulation, have pilot pressure oil and use direction switching valve and pilot pressure oil to the piston of the supply of piston pressure cylinder direction switching valve to the pivoted arm of the supply of pivoted arm pressure cylinder,
Be operated into when drawing the position on the pivoted arm with the direction switching valve at aforementioned pivoted arm only, aforementioned interflow switching valve switches to aforementioned the 1st restriction site,
When only aforementioned piston was operated into the piston unloaded position with the direction switching valve, aforementioned interflow switching valve switched to aforementioned the 2nd restriction site,
Carry out at the same time to the operation of drawing the position on the aforementioned pivoted arm with to the operation of aforementioned piston unloaded position the time, aforementioned interflow switching valve switches to the some of aforementioned the 1st restriction site and aforementioned the 2nd restriction site.
3. the oil hydraulic circuit of building machinery as claimed in claim 1, it is characterized in that, aforementioned interflow switching valve is with corresponding to the operation amount of the 2nd direction switching valve of aforementioned regulation and change the mode of stroke proportionally, switch to the aforementioned limitations position, the valve opening that is connected on the aforementioned drain passageway reduces corresponding to the stroke of aforementioned interflow switching valve, and the valve opening that is connected on aforementioned the 1st interflow path also reduces corresponding to the stroke of aforementioned interflow switching valve.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2004066589A JP4223421B2 (en) | 2004-03-10 | 2004-03-10 | Hydraulic circuit for construction machinery |
| JP66589/04 | 2004-03-10 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1693718A CN1693718A (en) | 2005-11-09 |
| CN100445576C true CN100445576C (en) | 2008-12-24 |
Family
ID=35082818
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005100527167A Active CN100445576C (en) | 2004-03-10 | 2005-03-10 | Hydraulic loop of building machinery |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP4223421B2 (en) |
| KR (1) | KR100627627B1 (en) |
| CN (1) | CN100445576C (en) |
| IT (1) | ITTO20050150A1 (en) |
Families Citing this family (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4926627B2 (en) * | 2006-09-21 | 2012-05-09 | ナブテスコ株式会社 | Electric oil system |
| KR101324355B1 (en) | 2006-12-05 | 2013-11-01 | 두산인프라코어 주식회사 | Hydraulic system for small-sized excavator to improve bucket speed |
| DE202007005232U1 (en) * | 2007-04-11 | 2008-08-14 | Liebherr Mining Equipment Co. | tipper |
| CN101886405B (en) * | 2010-07-21 | 2012-01-11 | 山河智能装备股份有限公司 | Main valve of small type hydraulic excavator with energy-saving excavation and high-efficient land leveling |
| JP5803587B2 (en) * | 2011-11-09 | 2015-11-04 | コベルコ建機株式会社 | Hydraulic circuit for construction machinery |
| JP5859857B2 (en) * | 2012-01-20 | 2016-02-16 | コベルコ建機株式会社 | Hydraulic circuit for construction machinery |
| CN103256266B (en) * | 2012-02-21 | 2015-06-17 | 湖南三一港口设备有限公司 | Construction machinery supporting leg synchronous control device and construction machinery |
| KR101728596B1 (en) | 2012-03-29 | 2017-04-19 | 케이와이비 가부시키가이샤 | Control valve device for power shovel |
| JP6004900B2 (en) * | 2012-11-07 | 2016-10-12 | Ｋｙｂ株式会社 | Hydraulic pressure control device for power shovel |
| JP6196499B2 (en) * | 2013-08-20 | 2017-09-13 | ナブテスコ株式会社 | Multiple directional valve for construction machinery |
| JP6324825B2 (en) * | 2014-07-03 | 2018-05-16 | ナブテスコ株式会社 | Hydraulic circuit for construction machinery |
| JP6639130B2 (en) * | 2015-07-15 | 2020-02-05 | ナブテスコ株式会社 | Hydraulic circuit for construction machinery and construction machinery |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3922855A (en) * | 1971-12-13 | 1975-12-02 | Caterpillar Tractor Co | Hydraulic circuitry for an excavator |
| US4030623A (en) * | 1971-12-13 | 1977-06-21 | Caterpillar Tractor Co. | Hydraulic circuitry for an excavator |
| CN1160823A (en) * | 1996-03-30 | 1997-10-01 | 三星重工业株式会社 | Flow confluence apparatus for heavy equipment |
| JP2002089512A (en) * | 2000-09-14 | 2002-03-27 | Hitachi Constr Mach Co Ltd | Hydraulic drive device for construction equipment |
| JP2002206256A (en) * | 2001-01-05 | 2002-07-26 | Kubota Corp | Hydraulic device for backhoe |
| US20030089106A1 (en) * | 2001-11-09 | 2003-05-15 | Nabco, Ltd. | Hydraulic circuit |
-
2004
- 2004-03-10 JP JP2004066589A patent/JP4223421B2/en not_active Expired - Lifetime
-
2005
- 2005-03-08 KR KR1020050018996A patent/KR100627627B1/en active IP Right Grant
- 2005-03-09 IT IT000150A patent/ITTO20050150A1/en unknown
- 2005-03-10 CN CNB2005100527167A patent/CN100445576C/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3922855A (en) * | 1971-12-13 | 1975-12-02 | Caterpillar Tractor Co | Hydraulic circuitry for an excavator |
| US4030623A (en) * | 1971-12-13 | 1977-06-21 | Caterpillar Tractor Co. | Hydraulic circuitry for an excavator |
| CN1160823A (en) * | 1996-03-30 | 1997-10-01 | 三星重工业株式会社 | Flow confluence apparatus for heavy equipment |
| JP2002089512A (en) * | 2000-09-14 | 2002-03-27 | Hitachi Constr Mach Co Ltd | Hydraulic drive device for construction equipment |
| JP2002206256A (en) * | 2001-01-05 | 2002-07-26 | Kubota Corp | Hydraulic device for backhoe |
| US20030089106A1 (en) * | 2001-11-09 | 2003-05-15 | Nabco, Ltd. | Hydraulic circuit |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1693718A (en) | 2005-11-09 |
| KR20060043497A (en) | 2006-05-15 |
| JP4223421B2 (en) | 2009-02-12 |
| ITTO20050150A1 (en) | 2005-09-11 |
| JP2005256881A (en) | 2005-09-22 |
| KR100627627B1 (en) | 2006-09-25 |
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