CN204003700U - Oil cylinder sequentially-operating hydraulic control system and engineering mechanical device - Google Patents
Oil cylinder sequentially-operating hydraulic control system and engineering mechanical device Download PDFInfo
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- CN204003700U CN204003700U CN201420363087.4U CN201420363087U CN204003700U CN 204003700 U CN204003700 U CN 204003700U CN 201420363087 U CN201420363087 U CN 201420363087U CN 204003700 U CN204003700 U CN 204003700U
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Abstract
The utility model relates to a kind of oil cylinder sequentially-operating hydraulic control system and engineering mechanical device, system comprises at least two telescopic oil cylinders and selector valve, the filler opening of selector valve and return opening are communicated with respectively oil-feed oil circuit and oil return circuit, the first actuator port of selector valve is communicated with by large chamber oil circuit successively with the large chamber of telescopic oil cylinder, the second actuator port is communicated with by loculus oil circuit with telescopic oil cylinder loculus respectively, realize the switching of connected relation by selector valve, in large chamber oil circuit and loculus oil circuit, be provided with multiple sequence control structures, realizing the order of telescopic oil cylinder stretches out and order retraction control, on the loculus oil circuit between the second actuator port and the rod chamber of telescopic oil cylinder of selector valve, be also provided with the flow control structure that enters into the fluid flow of the rod chamber of at least two telescopic oil cylinders under the state of controlling telescopic oil cylinder execution retract action.Energy loss when the utility model can reduce the action of hydraulic system execution sequence by flow control structure.
Description
Technical field
The utility model relates to hydraulics and engineering machinery field, relates in particular to a kind of oil cylinder sequentially-operating hydraulic control system and engineering mechanical device.
Background technique
Oil cylinder is the executive component of hydraulic system, and it can convert the pressure energy of liquid to the mechanical energy of operation mechanism, drives corresponding construction parts to carry out linear reciprocation action.Taking truck crane as example, in order to increase the lifting capacity of truck crane, on truck crane, design and can in the time of crane running, regain, the supporting leg of overhanging support complete machine when work, the withdrawal of supporting leg and overhanging action are to have been driven by the oil cylinder in hydraulic system.
As shown in Figure 1A-1C, be respectively existing automobile crane supporting leg and entirely stretching, partly stretching and the structural representation of full reduced state.Be installed on the A point of fixed supporting leg a1 in the one end that is arranged on the cross cylinder a5 in supporting leg, the other end is installed on the B point of movable supporting legs a2, the one end that is arranged on the cross cylinder 6 in supporting leg is installed on the C point of movable supporting legs a2, the other end is installed on the D point of movable supporting legs a3, and Vertical Cylinders a4 is installed on the end of movable supporting legs a3.Utilize the cross cylinder of hoist can make movable supporting legs stretch out and retract, and it is liftoff to utilize Vertical Cylinders can make hoist complete machine support.
In the time that supporting leg is regained, cross cylinder a6 retraction, pulls D point to make movable supporting legs a3 action, has moved as the state of partly stretching of Figure 1B, and then cross cylinder a5 retraction, pulls B point to make movable supporting legs a2 action, has moved final as the full reduced state of Fig. 1 C.Supporting leg stretches out process in contrast, and first cross cylinder a5 stretches out, and rear cross cylinder a6 stretches out, and has moved final as the state of entirely stretching of Figure 1A.According to above-mentioned its supporting leg course of action, need the function of HYDRAULIC CONTROL SYSTEM cross cylinder a5, a6 sequentially-operating.
In order to realize the sequentially-operating of oil cylinder, Fig. 2 shows a kind of oil cylinder sequentially-operating hydraulic control system, system comprise hydraulic oil container b1, oil hydraulic pump b2, relief valve b3, oil cylinder b4, b5, solenoid directional control valve b6, the sequence valve b7 that leaks, in let out sequence valve b9 and one-way valve b8, b10.Solenoid directional control valve b6, the sequence valve b7 that leaks, one-way valve b8 form valve group one, inside let out sequence valve b9 and one-way valve b10 and form valve group two.In the time that solenoid directional control valve b6 commutates to right-hand member, oil hydraulic pump b2 work, pressure oil enters large chamber and the valve group two of oil cylinder b4, owing to letting out in valve group two, sequence valve b9 does not reach its setting pressure, one-way valve b10 oppositely can not open, so oil cylinder b4 stretches out, the loculus fluid of oil cylinder b4 is through one-way valve b8 and solenoid directional control valve b6 oil return.After oil cylinder b4 stretches out completely, the setting pressure of letting out sequence valve b9 in system pressure rising reaches, pressure oil enters the large chamber of oil cylinder b5, and the loculus of oil cylinder b5 is directly through solenoid directional control valve b6 oil return, until oil cylinder b5 stretches out entirely.
In the time that solenoid directional control valve b6 commutates to left end, oil hydraulic pump b2 work, pressure oil acts on respectively loculus, the sequence valve b7 that leaks, the one-way valve b8 of oil cylinder b5, because the sequence valve b7 that leaks does not reach its setting pressure, one-way valve b8 oppositely can not open, so oil cylinder b5 carries out retract action, the large chamber oil return of oil cylinder b5 is through large chamber, the solenoid directional control valve b6 oil return of one-way valve b10, oil cylinder b4, until full reduced time of oil cylinder b5.After full reduced time of oil cylinder b5, system pressure rises, and reaches after the setting pressure of the sequence valve b7 that leaks, and pressure oil enters the loculus of oil cylinder b4, and the large chamber fluid of oil cylinder b4 is through solenoid directional control valve b6 oil return, until full reduced time of oil cylinder b4.
Above-mentioned oil cylinder one or the two sequential telescopic course of action that are HYDRAULIC CONTROL SYSTEM, its sequentially-operating relies on the sequence valve in hydraulic system to realize, and its sequence valve is opened and relied on system pressure to reach setting value, and need maintain always and be not less than setting value.But above-mentioned oil cylinder sequentially-operating hydraulic control system is in the time carrying out actual oil cylinder expanding-contracting action, and the oil cylinder that often exists formerly retraction is not yet recovered to other oil cylinders of the end just to start to retract, or occurs the synchronous situation of retracting of two oil cylinders.
The principle of probing into this sequence control failure, inventor notices: the oil cylinder in existing hydraulic system exists big or small cavity area ratio, for engineering machinery oil cylinder, general large cavity area be mostly 2 times of little cavity area and more than.Taking the automobile crane supporting leg cross cylinder of Fig. 1 as example, large cavity area is 2 times of little cavity area.Therefore when the large chamber of cross cylinder enters x L oil mass, loculus is discharged x/2L oil mass, enters x L oil mass and work as cross cylinder loculus, and large chamber needs to discharge 2x L oil mass.The oil mass of discharging is hydraulic system oil return, in the time that oil return flow exceedes hydraulic system pipeline, joint, hydrovalve permissible flow, produces return oil pressure resistance.And return oil pressure resistance is exactly the major reason that causes the failure of oil cylinder expanding-contracting action.
For instance, suppose the nominal flow rate 60L/min of solenoid directional control valve b6, in the time of oil cylinder retract action, when the maximum oil-feed flow of its loculus is 60L/min, according to oil cylinder size cavity area than 2, now large chamber oil return flow is 120L/min, and this flow flows out by the road from the large chamber of oil cylinder, oil sump tank joint, solenoid directional control valve b6.In the time flowing through solenoid directional control valve 6, because its flow is far beyond the nominal flow rate of this valve, so can produce the larger pressure loss herein, cause the large chamber of oil cylinder return oil pressure to increase.Because the large chamber of oil cylinder return oil pressure increases, make the also corresponding increase of oil pressure of loculus oil circuit, this just may cause because of the excessive opening sequence valve that shifts to an earlier date of loculus oil circuit oil pressure, and after making, an order oil cylinder moves in advance.In order to overcome this problem, if the pressure set points of sequence valve is set as higher, exceed safety valve setting pressure, can cause again loculus oil circuit oil pressure to be difficult to smooth opening sequence valve, cause retract action failure.
In addition, different oil cylinder loculus oil inlet quantities produce different return oil pressure values, and different flow system flow when this further makes back pressure resistance also can bounce back with oil cylinder carries out corresponding fluctuation variation.
Because of the existence of return oil pressure resistance, in the time that oil cylinder b5 retracts, system pressure need overcome retraction load force and the return oil pressure resistance of oil cylinder b5, and in the time that oil cylinder b4 retracts, system pressure need overcome the setting pressure of retraction load force, return oil pressure resistance and the sequence valve b7 that leaks of oil cylinder b4.For ensureing after oil cylinder b5 in oil cylinder b4 sequentially-operating, the setting pressure of sequence valve b7 of leaking should be higher than the retraction load force of oil cylinder b5 and return oil pressure resistance, the pressure set points of sequence valve b7 of now leaking will be very high, will require like this this sequence valve range of regulation larger, cause element cost higher.The more important thing is, the acting that system overcomes return oil pressure resistance has caused energy dissipation, and makes fluid heating, and Hydraulic System Reliability reduces.
Different flow system flow while retraction with oil cylinder because of back pressure resistance carries out corresponding fluctuation variation, and while causing oil cylinder retraction, systematic order valve pressure setting difficulty and product application debugging efficiency are low.For example, in the time of system small flow, return oil pressure resistance is also little, so the setting pressure of the sequence valve b7 that leaks is also little, in the time of the large flow of system, return oil pressure resistance is also large, so the setting pressure of the sequence valve b7 that leaks is also wanted greatly, retracts like this after guarantee oil cylinder b4 in oil cylinder b5 order.And prior art is in the time that product is applied, flow system flow depends on the engine speed that drives oil hydraulic pump, therefore will produce motor in the time of the slow-speed of revolution, by the leak setting pressure of sequence valve b7 of adjustment, oil cylinder sequentially-operating is set up, but in the time of the high rotating speed of motor, oil cylinder sequentially-operating can not ensure, need again adjust setup pressure value, cause debugging efficiency low.In debugging, can't be directly by too high the design of pressure of the sequence valve b7 that leaks, otherwise can cause compared with macro-energy loss, system reliability and reduce and reduce element working life.
Model utility content
The purpose of this utility model is to propose a kind of oil cylinder sequentially-operating hydraulic control system and engineering mechanical device, can improve the reliability of oil cylinder sequentially-operating, the energy loss while reducing the action of hydraulic system execution sequence.
For achieving the above object, the utility model provides a kind of oil cylinder sequentially-operating hydraulic control system, comprise at least two telescopic oil cylinders and selector valve, the filler opening of described selector valve and return opening are communicated with respectively oil-feed oil circuit and oil return circuit, the first actuator port of described selector valve is communicated with by large chamber oil circuit successively with the rodless cavity of described at least two telescopic oil cylinders, the second actuator port of described selector valve is communicated with by loculus oil circuit with the rod chamber of described at least two telescopic oil cylinders respectively, by described selector valve realize described large chamber oil circuit and loculus oil circuit respectively with the switching of the connected relation of oil-feed oil circuit and oil return circuit, in described large chamber oil circuit and loculus oil circuit, be provided with multiple sequence control structures, described in realization, the order of at least two telescopic oil cylinders is stretched out and order retraction control, wherein, on the loculus oil circuit between the second actuator port and the rod chamber of described at least two telescopic oil cylinders of described selector valve, be also provided with control telescopic oil cylinder carry out under the state of retract action, enter into described in the flow control structure of fluid flow of rod chamber of at least two telescopic oil cylinders.
Further, the setting value of the fluid control flow of described flow control structure is at least determined by two cavity areas ratios of the nominal flow rate of described selector valve and the rodless cavity of telescopic oil cylinder and rod chamber.
Further, the setting value of the fluid control flow of described flow control structure is not higher than the ratio of two cavity area ratios of the nominal flow rate of described selector valve and the rodless cavity of telescopic oil cylinder and rod chamber.
Further, described flow control structure comprises pressure compensated flow valve and with described pressure compensated flow valve, opposite direction is set, and the one-way valve in parallel with described pressure compensated flow valve, the entrance of described pressure compensated flow valve is communicated with the second actuator port of described selector valve, and the outlet of described pressure compensated flow valve is communicated with respectively with the rod chamber of described at least two telescopic oil cylinders.
Further, described flow control structure comprises throttle valve and with described throttle valve, opposite direction is set, and the one-way valve in parallel with described throttle valve, the entrance of described throttle valve is communicated with the second actuator port of described selector valve, and the outlet of described throttle valve is communicated with respectively with the rod chamber of described at least two telescopic oil cylinders.
Further, comprise the first sequence valve and with described the first sequence valve, opposite direction is set at the sequence control structure of described large chamber oil circuit setting, and the one-way valve in parallel with described the first sequence valve, described in described the first sequence valve is arranged at, at least two telescopic oil cylinders, stretch out on the large chamber oil circuit between the rodless cavity of adjacent two telescopic oil cylinders before and after order, and the import of described the first sequence valve and outlet respectively with stretch out order and be communicated with at rodless cavity front and that stretch out the posterior telescopic oil cylinder of order.
Further, described the first sequence valve is off-load sequence valve.
Further, described off-load sequence valve is the formula off-load sequence valve that leaks.
Further, comprise the second sequence valve and with described the second sequence valve, opposite direction is set at the sequence control structure of described loculus oil circuit setting, and the one-way valve in parallel with described the second sequence valve, described the second sequence valve be arranged at described flow control structure respectively and the rod chamber of the non-telescopic oil cylinder at first of retraction order between loculus oil circuit on, and the import of described the second sequence valve and outlet are communicated with the rod chamber of the non-telescopic oil cylinder at first of described flow control structure and retraction order respectively.
Further, described the second sequence valve is off-load sequence valve.
Further, described off-load sequence valve is internal drainage type off-load sequence valve.
Further, described selector valve is solenoid directional control valve.
For achieving the above object, the utility model provides a kind of engineering mechanical device, wherein, comprises aforesaid oil cylinder sequentially-operating hydraulic control system.
Based on technique scheme, the utility model arranges flow control structure and realizes the control by flow in oil cylinder sequentially-operating hydraulic control system, realize the control of carrying out under the state of retract action the fluid flow to entering into telescopic oil cylinder rod chamber (being loculus) at telescopic oil cylinder, and then the oil return flow of control telescopic oil cylinder rodless cavity (being large chamber), the nominal flow rate of itself and selector valve is matched, reduce or eliminate the return oil pressure resistance in the large chamber of telescopic oil cylinder, reduce or avoid the sequential telescopic that causes because of the return oil pressure resistance in large chamber unsuccessfully, improve the reliability of oil cylinder sequential telescopic action, minimizing system is because overcoming the energy dissipation causing of doing work of return oil pressure resistance, simultaneously also reducing or eliminating the set pressure that has reduced sequence valve because of the return oil pressure resistance in the large chamber of telescopic oil cylinder, reduce the requirement to sequence valve range of regulation, thereby reduce element cost.
In another embodiment, the setting value of the fluid control flow of described flow control structure is at least determined by two cavity areas ratios of the nominal flow rate of described selector valve and the rodless cavity of telescopic oil cylinder and rod chamber.Set the numerical value of fluid control flow of definite flow control structure except reducing or eliminate the return oil pressure resistance of telescopic oil cylinder, can also reduce or eliminate telescopic oil cylinder execution retract action time, the fluctuation of flow system flow changes, to facilitate the setting of pressure set points of sequence valve, improve debugging efficiency.
Brief description of the drawings
Accompanying drawing described herein is used to provide further understanding of the present utility model, forms the application's a part, and schematic description and description of the present utility model is used for explaining the utility model, does not form improper restriction of the present utility model.In the accompanying drawings:
Figure 1A-1C is respectively existing automobile crane supporting leg and is entirely stretching, partly stretching and the structural representation of full reduced state.
Fig. 2 is the hydraulic principle schematic diagram of existing oil cylinder sequentially-operating hydraulic control system.
Fig. 3 A, 3B be respectively in Fig. 2, leak sequence valve and in let out the structural representation of sequence valve.
Fig. 4 is an embodiment's of the utility model oil cylinder sequentially-operating hydraulic control system hydraulic principle schematic diagram.
Fig. 5 is another embodiment's of the utility model oil cylinder sequentially-operating hydraulic control system hydraulic principle schematic diagram.
Fig. 6 is the another embodiment's of the utility model oil cylinder sequentially-operating hydraulic control system hydraulic principle schematic diagram.
Fig. 7 is the structural representation of the formula that the leaks off-load sequence valve that adopts in the utility model oil cylinder sequentially-operating hydraulic control system embodiment.
Embodiment
Below by drawings and Examples, the technical solution of the utility model is described in further detail.
Above, inventor has analyzed why existing oil cylinder sequentially-operating hydraulic control system exists that oil cylinder sequential telescopic action is unreliable, energy consumption is large, sequence valve pressure setting difficulty, debugging efficiency are low and have relatively high expectations and cause the problem that cost is higher, and finds that this serial problem is all how many relevant to flow system flow.Based on this discovery, inventor starts with above-mentioned at least one problem is provided to suitable solution from control flow.
As shown in Figure 4, be an embodiment's of the utility model oil cylinder sequentially-operating hydraulic control system hydraulic principle schematic diagram.In the present embodiment, oil cylinder sequentially-operating hydraulic control system comprises at least two telescopic oil cylinders 4, 5 (shown in Fig. 4 is the situation of two telescopic oil cylinders) and selector valves 6, the filler opening of selector valve 6 and return opening are communicated with respectively oil-feed oil circuit P and oil return circuit T, the first actuator port of selector valve 6 and at least two telescopic oil cylinders 4, 5 rodless cavity (being large chamber) is communicated with successively by large chamber oil circuit, the second actuator port of selector valve 6 respectively with at least two telescopic oil cylinders 4, 5 rod chamber (being loculus) is communicated with by loculus oil circuit, by selector valve 6 just can realize large chamber oil circuit and loculus oil circuit respectively with the switching of the connected relation of oil-feed oil circuit P and oil return circuit T.Selector valve 6 can adopt solenoid directional control valve, also can adopt hand-operated direction valve or other forms, for example, be 3-position 4-way solenoid directional control valve at selector valve 6 employed in figure 4, also can replace to according to actual needs other forms of solenoid directional control valve.
In large chamber oil circuit and loculus oil circuit, be provided with multiple sequence control structures 2,3, can realize the order of at least two telescopic oil cylinders 4,5 and stretch out and order retraction control.Sequence control structure 2,3 can adopt conventional sequence control structure, for example, utilize sequence control mode that sequence valve carries out etc., also will provide in other embodiments hereinafter further way of realization.
On the loculus oil circuit between the second actuator port of selector valve 6 and the rod chamber of at least two telescopic oil cylinders 4,5, be also provided with flow control structure 1, this structure can be controlled telescopic oil cylinder and carry out the fluid flow that enters into the rod chamber of at least two telescopic oil cylinders 4,5 under the state of retract action.When being retracted, oil cylinder enters into the control of the fluid flow of rod chamber, can control accordingly the oil return flow of telescopic oil cylinder rodless cavity, the nominal flow rate of itself and selector valve is matched, so just can reduce or eliminate the return oil pressure resistance in the large chamber of telescopic oil cylinder, reduce or avoid the sequential telescopic that causes because of the return oil pressure resistance in large chamber unsuccessfully, improve the reliability of oil cylinder sequential telescopic action, minimizing system is because overcoming the energy dissipation causing of doing work of return oil pressure resistance, simultaneously also reducing or eliminating the set pressure that has reduced sequence valve because of the return oil pressure resistance in the large chamber of telescopic oil cylinder, reduce the requirement to sequence valve range of regulation, thereby reduce element cost.
The setting value of the fluid control flow of flow control structure 1 can at least be determined by two cavity areas ratios of the nominal flow rate of selector valve 6 and the rodless cavity of telescopic oil cylinder 4,5 and rod chamber.Can calculate the setting value of suitable fluid control flow by these factors.For instance, the nominal flow rate of supposing selector valve 6 is 60L/min, and two cavity area ratios of the rodless cavity of telescopic oil cylinder 4,5 and rod chamber are 2, by the nominal flow rate 60L/min of selector valve 6 is asked for to ratio with the rodless cavity of telescopic oil cylinder 4,5 and two cavity areas of rod chamber than 2, the setting value that can obtain the fluid control flow of flow control structure 1 is 30L/min, also can such as, for being less than the setting value of 30L/min, 28L/min etc.Except adopting above-mentioned calculation method, also can adopt other possible form of calculation, for example increase calculated factor, calculation constant etc., as long as can be convenient to determine the setting value of suitable fluid control flow, repeat no more here.
After having determined the setting value of fluid control flow of flow control structure 1, can learn with reference to figure 4, in the time that telescopic oil cylinder is retracted, the state of rod chamber in oil-feed, limiting after the fluid control flow that enters rod chamber so, make the flow of the hydraulic oil liquid flowing out from rodless cavity be unlikely to exceed the nominal flow rate of selector valve 6, the return oil pressure that this has produced while just having been avoided the existing oil cylinder sequentially-operating hydraulic control system analyzed because of chamber oil return flow supercommutation valve far away nominal flow rate greatly above, even if still there is return oil pressure, also will make this return oil pressure greatly reduce, thereby reduce or avoided the sequential telescopic failure causing because of the return oil pressure resistance in large chamber, also the pressure loss that reduces or avoided large chamber return oil pressure to bring.
On the other hand, limiting after the fluid control flow that enters rod chamber, make large chamber return oil pressure disappear or reduce, so also further eliminate or reduced the fluctuation of the large chamber return oil pressures that cause because loculus oil inlet quantity is different, and the sequence valve that this fluctuation brings sets up that difficulty is high, debug time long and the problem such as the harshness requirement of range of regulation to sequence valve has all obtained overcoming to a certain extent.
In different oil cylinder sequentially-operating hydraulic control system embodiments, provide the implementation example of two kinds of flow control structures below.As shown in Figure 5, be another embodiment's of the utility model oil cylinder sequentially-operating hydraulic control system hydraulic principle schematic diagram.In the present embodiment, the flow control structure 1 that the present embodiment adopts comprises pressure compensated flow valve 11 and with pressure compensated flow valve 11, opposite direction is set, and the one-way valve 12 in parallel with pressure compensated flow valve 11, the entrance of pressure compensated flow valve 11 is communicated with the second actuator port of selector valve 12, and the outlet of pressure compensated flow valve 11 is communicated with respectively with the rod chamber of at least two telescopic oil cylinders 4,5.
Oil pump 8 oil suction from hydraulic oil container 7, and to whole hydraulic control oil circuit fuel feeding, and be arranged on relief valve 9 between oil feeding line and oil return circuit and can play the effect of overload protection.When selector valve 6 switches to the loculus fuel feeding that oil feeding line is telescopic oil cylinder, large chamber oil return, while starting execution sequence retract action, hydraulic oil by selector valve 6 can first pass through pressure compensated flow valve 11, further maintain by the hydraulic oil of sequence control structure 2 and telescopic oil cylinder loculus the traffic level setting with regard to making like this, switch to and work as selector valve 6 large chamber fuel feeding, the loculus oil return that oil feeding line is telescopic oil cylinder, when beginning execution sequence stretches out, oil return is directly by one-way valve 12 hydraulic return fuel tanks 7.
In Fig. 6,1 of flow control structure comprises throttle valve 13 and with throttle valve 13, opposite direction is set, and the one-way valve 12 in parallel with throttle valve 13, the entrance of throttle valve 13 is communicated with the second actuator port of selector valve 6, and the outlet of throttle valve 13 is communicated with respectively with the rod chamber of at least two telescopic oil cylinders 4,5.Throttle valve 13 can be independent device, can be also the function that the damping hole in the valve B being surrounded by double dot dash line is as shown in Figure 6 realized.Its working procedure and pressure compensated flow valve 11 are basic identical, repeat no more here.
In the oil cylinder sequentially-operating hydraulic control system embodiment shown in Fig. 5 and Fig. 6, sequence control structure 3 in large chamber oil circuit setting can comprise the first sequence valve 31 and with the first sequence valve 31, opposite direction is set, and the one-way valve 32 in parallel with the first sequence valve 31, the first sequence valve 31 is arranged on the large chamber oil circuit between the rodless cavity that stretches out two telescopic oil cylinders adjacent before and after order at least two telescopic oil cylinders 4,5, and the import of the first sequence valve 31 and outlet respectively with stretch out order and be communicated with at rodless cavity front and that stretch out the posterior telescopic oil cylinder of order.If have three telescopic oil cylinder Y1, Y2, Y3, sequence control structure 3 is separately positioned on Y1 and Y2, and between Y2 and Y3, if there is more telescopic oil cylinder, the rest may be inferred for the set-up mode of sequence control structure 3.Wherein, sequence control structure 3 can be realized in valve A.
Fig. 3 A, 3B be respectively existing leak sequence valve b7 and in let out the structural representation of sequence valve b9.The present invention, in the first sequence valve 31 and the selection of the second sequence valve 21 below, still can adopt this existing structure.But for this existing sequence valve structure, inventor notices: exceed spring force (pressure set points) when the inlet pressure of sequence valve reaches, and maintain for a long time, just can maintain being communicated with of P1 mouth and P2 mouth, visible sequence valve P1 mouth and P2 mouth must have the pressure that overcomes spring force to maintain while being connected.This just makes in this sequence control system, need to rely on system pressure to complete to leak sequence valve 7 and in let out the unlatching of sequence valve 9 and maintain opening.And in the time that oil cylinder b4 carries out retract action, system pressure should be greater than the retraction load force sum of spring force and the oil cylinder b4 of the sequence valve b7 that leaks, and in system, this pressure acting that maintains sequence valve unlatching will make fluid heating, and Hydraulic System Reliability is reduced.
Therefore, in order further to improve the reliability of hydraulic system, in the selection of the first sequence valve 31, can adopt the formula that the leaks off-load sequence valve shown in Fig. 7, than existing sequence valve, the spool of the formula that leaks off-load sequence valve is provided with damping hole S1 and escape orifice X1, in the time that the oil inlet P 1 of the valve body of the formula off-load sequence valve that leaks reaches preset pressure, spool moves upward, order mouth P3 and the escape orifice X1 of valve body are connected, the pressure oil that enters into oil inlet P 1 flows out from order mouthful P3 through damping hole S1 and escape orifice X1, enter next stage system, when spool moves to final position, the top completely, sequence valve is opened completely, oil inlet P 1 is connected with oil outlet P2, pressure oil enters into next stage system by oil inlet P 1 and oil outlet P2, and partial pressure oil will keep flowing by damping hole S1 and escape orifice X1, mobile hydraulic oil produces pressure difference in the front and back of damping hole S1, utilize this pressure difference just can keep the opening state of spool, until flowing, fluid stops.
Utilize the off-load sequence valve of this structure, open when reaching after default system pressure, then just can rely on fluid to flow to be held open state, what need to overcome is only the spring force of main spring on spool, and main spring power can be set to very little spring force, therefore adopt the pressure loss that the off-load sequence valve of this structure occurs in the time of hydraulic work system much smaller than prior art, make the energy loss of system still less.
In oil cylinder sequentially-operating hydraulic control system of the present utility model, the corresponding off-load sequence valve of the first sequence valve 31 can be straight moving form, also can adopt the pilot control form shown in Fig. 7, in Fig. 7, valve body middle part is also provided with a damping hole S2, spheroid (can be also cone etc.) and the pilot stage spring that stops damping hole S2 at the other end of damping hole S2, under certain pressure, back down spheroid by this structured liquid force feed, damping hole S2 is opened, spool just moves afterwards, and escape orifice X1 just can be communicated with an order mouthful P3.Than the off-load sequence valve of straight moving form, the off-load sequence valve of pilot control form has higher control accuracy and larger nominal flow rate.
In the selection of the draining mode of the corresponding off-load sequence valve of the first sequence valve 31, the formula that preferably leaks, carries out draining by drain tap Y, and than internal drainage type structure, the formula that leaks structure back pressure is less, makes the longer service life of valve body and Sealing.
In the oil cylinder sequentially-operating hydraulic control system embodiment shown in Fig. 5 and Fig. 6, comprise the second sequence valve 21 and with the second sequence valve 21, opposite direction is set at the sequence control structure 2 of loculus oil circuit setting, and the one-way valve 22 in parallel with the second sequence valve 21, the second sequence valve 21 be arranged at flow control structure 2 respectively and the rod chamber of the non-telescopic oil cylinder 5 at first of retraction order between loculus oil circuit on, and the import of the second sequence valve 21 and outlet are communicated with the rod chamber of the non-telescopic oil cylinder 5 at first of flow control structure 1 and retraction order respectively.If have three telescopic oil cylinder Y1, Y2, Y3, sequence control structure 2 is separately positioned on flow control structure 1 respectively and between Y1 and Y2, and be not arranged between the telescopic oil cylinder Y3 of flow control structure 1 and first retraction, if there is more telescopic oil cylinder, the rest may be inferred for the set-up mode of sequence control structure 2.Wherein, sequence control structure 2 can realized with selector valve 6 and flow control mechanism 1 in valve B, also can be with respect to selector valve 6 and the independent setting of flow control mechanism 1.
In the selection of the second sequence valve 21, can still continue to use that sequence valve structure of mentioning in background technique, also can adopt off-load sequence valve, concrete structure can be with reference to the formula that the leaks off-load sequence valve introduced above.Utilize off-load sequence valve, open when reaching after default system pressure, then just can rely on fluid to flow to be held open state, what need to overcome is only the spring force of main spring on spool, and main spring power can be set to very little spring force, therefore adopt the pressure loss that the off-load sequence valve of this structure occurs in the time of hydraulic work system much smaller than prior art, make the energy loss of system still less.
The corresponding off-load sequence valve of the second sequence valve 21 that oil cylinder sequentially-operating hydraulic control system of the present utility model adopts can, for straight moving form, also can adopt pilot control form, owing to this there being detailed explanation above, has just no longer described in detail here.In the selection of the draining mode of the corresponding off-load sequence valve of the second sequence valve 21, preferably internal drainage type, by special drain tap is not set, but carry out draining by oil outlet, than the formula of leaking, internal drainage type structure not only can reduce relevant pipeline, also compacter aspect arrangement space.
After each embodiment of the utility model oil cylinder sequentially-operating hydraulic control system is described, be appreciated that the engineering mechanical device that has comprised above-mentioned any oil cylinder sequentially-operating hydraulic control system embodiment, energy loss can reduce the action of hydraulic system execution sequence time, the reliability of raising system.
Finally should be noted that: above embodiment is only in order to illustrate that the technical solution of the utility model is not intended to limit; Although the utility model is had been described in detail with reference to preferred embodiment, those of ordinary skill in the field are to be understood that: still can modify or part technical characteristics is equal to replacement embodiment of the present utility model; And not departing from the spirit of technical solutions of the utility model, it all should be encompassed in the middle of the technological scheme scope of the utility model request protection.
Claims (13)
1. an oil cylinder sequentially-operating hydraulic control system, comprise at least two telescopic oil cylinders and selector valve, the filler opening of described selector valve and return opening are communicated with respectively oil-feed oil circuit and oil return circuit, the first actuator port of described selector valve is communicated with by large chamber oil circuit successively with the rodless cavity of described at least two telescopic oil cylinders, the second actuator port of described selector valve is communicated with by loculus oil circuit with the rod chamber of described at least two telescopic oil cylinders respectively, by described selector valve realize described large chamber oil circuit and loculus oil circuit respectively with the switching of the connected relation of oil-feed oil circuit and oil return circuit, in described large chamber oil circuit and loculus oil circuit, be provided with multiple sequence control structures, described in realization, the order of at least two telescopic oil cylinders is stretched out and order retraction control, it is characterized in that, on the loculus oil circuit between the second actuator port and the rod chamber of described at least two telescopic oil cylinders of described selector valve, be also provided with control telescopic oil cylinder carry out under the state of retract action, enter into described in the flow control structure of fluid flow of rod chamber of at least two telescopic oil cylinders.
2. oil cylinder sequentially-operating hydraulic control system according to claim 1, it is characterized in that, the setting value of the fluid control flow of described flow control structure is at least determined by two cavity areas ratios of the nominal flow rate of described selector valve and the rodless cavity of telescopic oil cylinder and rod chamber.
3. oil cylinder sequentially-operating hydraulic control system according to claim 2, it is characterized in that, the setting value of the fluid control flow of described flow control structure is not higher than the ratio of two cavity area ratios of the nominal flow rate of described selector valve and the rodless cavity of telescopic oil cylinder and rod chamber.
4. oil cylinder sequentially-operating hydraulic control system according to claim 1, it is characterized in that, described flow control structure comprises pressure compensated flow valve and with described pressure compensated flow valve, opposite direction is set, and the one-way valve in parallel with described pressure compensated flow valve, the entrance of described pressure compensated flow valve is communicated with the second actuator port of described selector valve, and the outlet of described pressure compensated flow valve is communicated with respectively with the rod chamber of described at least two telescopic oil cylinders.
5. oil cylinder sequentially-operating hydraulic control system according to claim 1, it is characterized in that, described flow control structure comprises throttle valve and with described throttle valve, opposite direction is set, and the one-way valve in parallel with described throttle valve, the entrance of described throttle valve is communicated with the second actuator port of described selector valve, and the outlet of described throttle valve is communicated with respectively with the rod chamber of described at least two telescopic oil cylinders.
6. oil cylinder sequentially-operating hydraulic control system according to claim 1, it is characterized in that, comprise the first sequence valve and with described the first sequence valve, opposite direction is set at the sequence control structure of described large chamber oil circuit setting, and the one-way valve in parallel with described the first sequence valve, on large chamber oil circuit before and after stretching out sequentially described in described the first sequence valve is arranged at least two telescopic oil cylinders between the rodless cavity of two adjacent telescopic oil cylinders, and the import of described the first sequence valve and outlet respectively with stretch out order front and stretch out order posterior telescopic oil cylinder rodless cavity be communicated with.
7. oil cylinder sequentially-operating hydraulic control system according to claim 6, is characterized in that, described the first sequence valve is off-load sequence valve.
8. oil cylinder sequentially-operating hydraulic control system according to claim 7, is characterized in that, described off-load sequence valve is the formula off-load sequence valve that leaks.
9. oil cylinder sequentially-operating hydraulic control system according to claim 1, it is characterized in that, comprise the second sequence valve and with described the second sequence valve, opposite direction is set at the sequence control structure of described loculus oil circuit setting, and the one-way valve in parallel with described the second sequence valve, described the second sequence valve be arranged at described flow control structure respectively and the rod chamber of the non-telescopic oil cylinder at first of retraction order between loculus oil circuit on, and the import of described the second sequence valve and outlet are communicated with the rod chamber of described flow control structure and the non-telescopic oil cylinder at first of retraction order respectively.
10. oil cylinder sequentially-operating hydraulic control system according to claim 9, is characterized in that, described the second sequence valve is off-load sequence valve.
11. oil cylinder sequentially-operating hydraulic control systems according to claim 10, is characterized in that, described off-load sequence valve is internal drainage type off-load sequence valve.
12. oil cylinder sequentially-operating hydraulic control systems according to claim 1, is characterized in that, described selector valve is solenoid directional control valve.
13. 1 kinds of engineering mechanical devices, is characterized in that, comprise the arbitrary described oil cylinder sequentially-operating hydraulic control system of claim 1～12.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420363087.4U CN204003700U (en) | 2014-07-02 | 2014-07-02 | Oil cylinder sequentially-operating hydraulic control system and engineering mechanical device |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201420363087.4U CN204003700U (en) | 2014-07-02 | 2014-07-02 | Oil cylinder sequentially-operating hydraulic control system and engineering mechanical device |
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| CN204003700U true CN204003700U (en) | 2014-12-10 |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104088837A (en) * | 2014-07-02 | 2014-10-08 | 徐州重型机械有限公司 | Oil cylinder sequential action hydraulic control system and engineering machinery device |
| CN106337846A (en) * | 2016-10-12 | 2017-01-18 | 中南大学 | Piling machine pile clamping hydraulic system and control method capable of achieving sequential pile clamping and pile clamping sequence control valve |
| CN107178542A (en) * | 2017-04-28 | 2017-09-19 | 防城港市海河堤管理站 | Telescoping mechanism and the hydrologic monitoring device with the telescoping mechanism |
| CN107255092A (en) * | 2017-04-28 | 2017-10-17 | 防城港市海河堤管理站 | Hydrologic monitoring device |
| CN109693348A (en) * | 2019-02-18 | 2019-04-30 | 天津银宝山新科技有限公司 | Double-ejection order controller, mold and control method |
-
2014
- 2014-07-02 CN CN201420363087.4U patent/CN204003700U/en not_active Withdrawn - After Issue
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104088837A (en) * | 2014-07-02 | 2014-10-08 | 徐州重型机械有限公司 | Oil cylinder sequential action hydraulic control system and engineering machinery device |
| CN106337846A (en) * | 2016-10-12 | 2017-01-18 | 中南大学 | Piling machine pile clamping hydraulic system and control method capable of achieving sequential pile clamping and pile clamping sequence control valve |
| CN107178542A (en) * | 2017-04-28 | 2017-09-19 | 防城港市海河堤管理站 | Telescoping mechanism and the hydrologic monitoring device with the telescoping mechanism |
| CN107255092A (en) * | 2017-04-28 | 2017-10-17 | 防城港市海河堤管理站 | Hydrologic monitoring device |
| CN109693348A (en) * | 2019-02-18 | 2019-04-30 | 天津银宝山新科技有限公司 | Double-ejection order controller, mold and control method |
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