CN102042273A - Hydraulic control loop and method - Google Patents
Hydraulic control loop and method Download PDFInfo
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- CN102042273A CN102042273A CN 201010255962 CN201010255962A CN102042273A CN 102042273 A CN102042273 A CN 102042273A CN 201010255962 CN201010255962 CN 201010255962 CN 201010255962 A CN201010255962 A CN 201010255962A CN 102042273 A CN102042273 A CN 102042273A
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- valve
- executive component
- hydraulic
- resistance element
- hydraulic control
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
- F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
- F15B11/0423—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in" by controlling pump output or bypass, other than to maintain constant speed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/505—Pressure control characterised by the type of pressure control means
- F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
- F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
Abstract
The invention discloses a hydraulic control loop which comprises a main oil path (1), a hydraulic resistance element (2) and an oil box (3), wherein the hydraulic resistance element (2) is connected in series with the oil box (3) and bypassed on the main oil path (1). The invention also discloses a hydraulic control method, wherein the hydraulic resistance element (2) is bypassed on the main oil path (1), and the hydraulic resistance element (2) is connected back to the oil box (3), so that the pressure of the main oil path (1) can be controlled by controlling the flow of the main oil path (1). Therefore, according to the technical scheme of the invention, the pressure of the main oil path (1) can be controlled by controlling the flow of the main oil path (1) so that the pressure is not easily influenced, and a hydraulic system is simplified.
Description
Technical field
The present invention relates to the hydraulic control field, particularly, relate to a kind of hydraulic control circuit and method.
Background technique
Often relate to the pressure control in hydraulic system or the oil hydraulic circuit in the hydraulic control field.The for example Pilot operated check valve in the hydraulic system, pilot operated directional control valve, equilibrium valve etc., its control port is communicated with a certain oil circuit (hereinafter referred to as working connection) in the hydraulic system, to control the action of parts such as this Pilot operated check valve, pilot operated directional control valve, equilibrium valve.And the pressure of working connection can be subjected to the influence of other parts in the hydraulic system usually, thereby makes the action of parts such as above-mentioned Pilot operated check valve, pilot operated directional control valve, equilibrium valve undesirably be affected.Perhaps the pressure of this working connection is controlled by extra pressure valve (for example solenoid-operated proportional reduction valve etc.), thereby make the control mode of parts such as above-mentioned Pilot operated check valve, pilot operated directional control valve, equilibrium valve become complicated, and even increased the complexity of whole hydraulic system.
Be that example illustrates the shortcoming that pressure controling mode exists in the existing hydraulic system with a kind of load hydraulic control circuit that descends below.
In the engineering machinery, the decline load is common enforcement operation operating mode, generally all adopts the equilibrium valve loop to the weight speed limit that descends, to guarantee the Security of operation process.Can regulate for the assurance equilibrium valve, make weight to transfer according to different speed when different operating mode, equilibrium valve need have internal control signal or external control signal to control.What application was more at present is automatical control system or hydraulic control system, automatical control system is owing to each side such as cost, impact is former thereby limited on application area, therefore, in the construction plant that some need be controlled cost and job requirements is very not strict, all adopt hydraulic control system.The hydraulic control guide pilot pressure of general hydraulic system is lower, and output value is single, and equilibrium valve is at the different loads operating mode time, and its pilot pressure is not quite similar, and therefore, the hydraulic control signal of equilibrium valve all picks up from system itself, but not guide's control pressure signal.
As shown in Figure 1, traditional decline load hydraulic control circuit generally includes main valve 8 ', equilibrium valve 9 ', oil hydraulic cylinder 71 ' and relief valve 10 ', the first actuator port A8 ' of main valve 8 ' is connected with for example rodless cavity 711 ' of oil hydraulic cylinder 71 ' by equilibrium valve 9 ', the second actuator port B8 ' of main valve 8 ' is connected with the rod chamber 712 ' of oil hydraulic cylinder 71 ', and the control port 91 ' of relief valve 10 ' and equilibrium valve 9 ' all is connected on the pipeline between the second actuator port B8 ' of the rod chamber 712 ' of oil hydraulic cylinder 71 ' and main valve 8 '.
In load decline process, main valve 8 ' works in right position, and the oil-feed port P8 ' of system flows to second chamber 712 ' of oil hydraulic cylinder 71 ' by the second actuator port B8 '; The oil of the rodless cavity 711 ' of oil hydraulic cylinder 71 ' is by equilibrium valve 9 ', and the first actuator port A8 ' and the oil return inlet T 8 ' by main valve 8 ' flows back to fuel tank again.In this process, the pilot pressure of equilibrium valve 9 ' (dotted portion of equilibrium valve 9 ' among the figure) is from the pressure of rod chamber 712 ', and promptly by the pressure of load generation, its highest pilot pressure is the setup pressure value of relief valve 10 '.Therefore this pilot pressure is produced by load, is subjected to the influence of load all the time, fluctuates because of the variation of load easily.In actual conditions, for making pilot pressure more stable, tend to make relief valve 10 ' to be in opening state all the time, this just requires system's fuel supply flow rate must satisfy simultaneously when the main valve 8 ' traffic requirement in the oil hydraulic cylinder decline process and turn-on flow rate requirement of relief valve 10 ' during in different opening.Therefore, the output flow of this traditional decline load hydraulic control circuit is bigger.And, the pilot pressure of equilibrium valve 9 ' is always the cracking pressure of relief valve 10 ', and because in order under limited conditions, (to push up top as oil hydraulic cylinder, this moment, the pressure of rodless cavity 711 ' was very high) guarantee that equilibrium valve 9 ' can open, the setting pressure of relief valve 10 ' often all than higher, makes system pressure too high.System pressure height and output flow are big, make that system's output power is big, cause energy loss.
In addition, in this traditional decline load hydraulic control circuit, in load decline process, the rate of descent of load is by the decision of the aperture of equilibrium valve 9 ', and the aperture of equilibrium valve 9 ' is decided by the back pressure that the return opening (the first actuator port 8A ') of the pressure of the rodless cavity 711 ' of the pilot pressure of equilibrium valve 9 ', oil hydraulic cylinder 71 ' and main valve 8 ' produces.Specifically, the positive opening of pilot pressure control equilibrium valve 9 ', the negative opening of the pressure of rodless cavity 711 ' and back pressure control equilibrium valve 9 '.The pressure of rodless cavity 711 ' is subjected to load effect, and when the pilot pressure that guarantees equilibrium valve 9 ' stablize, when needs increase or reduce rate of descent, thereby the oil filling capacity change back pressure of return opening that must be by change main valve 8 ' changed the aperture of equilibrium valve 9 '.When main valve 8 ' aperture is certain, when back pressure made the aperture of equilibrium valve 9 ' big for a short time, rate of descent was fast; The aperture of back pressure ambassador's equilibrium valve 9 ' hour, rate of descent is slow.So just make main valve 8 ' when design, its filler opening and return opening must mate good, otherwise it is unstable easily to cause load to descend.And the governor control characteristics of equilibrium valve 9 ' realizes that by back pressure when load variations was big, back pressure can produce shake, causes that the aperture of equilibrium valve 9 ' changes, and causes rate of descent to change, and it is unstable to make load descend.
Summary of the invention
The present invention aims to provide a kind of hydraulic control circuit and hydraulic control method, thereby overcomes the above-mentioned shortcoming of at least a portion that exists in the prior art, and a kind of useful alternative scheme perhaps is provided at least.
On the one hand, the present invention a kind of hydraulic control circuit is provided, wherein, this hydraulic control circuit comprises working connection, liquid resistance element and fuel tank, described liquid resistance element is connected with described fuel tank and other being connected on the described working connection.
On the other hand, the present invention also provides a kind of hydraulic control method, wherein, connects the liquid resistance element and makes this liquid resistance element take back fuel tank by other on working connection, thereby can control the pressure of described working connection by the flow of controlling described working connection.
According to such scheme, can control pressure in the working connection by controlling flow in the described working connection, thereby make the pressure in the working connection not be vulnerable to the influence of other parts in the hydraulic system, and need not to be provided with extra pressure valve and control pressure in the working connection, make that whole hydraulic system obtains simplifying.
Further, described hydraulic control circuit, described liquid resistance element is connected with described fuel tank and other being connected on the described working connection, this control loop also comprises the main valve that is arranged on the described working connection, equilibrium valve and executive component, first actuator port of described main valve is communicated with first working end of described executive component by described equilibrium valve, second actuator port of described main valve is communicated with second working end of described executive component, described liquid resistance element is arranged on the pipeline between second working end of second actuator port of described main valve and described executive component, the control port of described equilibrium valve is connected on second actuator port and the pipeline between the described liquid resistance element of described main valve, and second working end of described executive component is communicated with described fuel tank with pipeline between the described liquid resistance element.
Further, described hydraulic control method comprises: the main valve, equilibrium valve and the executive component that are arranged on the working connection are provided, and other liquid resistance element and the fuel tank that is connected on the described working connection, wherein said liquid resistance element and the series connection of described fuel tank; Make hydraulic oil in first working end of described executive component flow into first actuator port of described main valve by described equilibrium valve; Flow into described fuel tank after making the hydraulic oil that flows out from second actuator port of described main valve produce pressure drop, and the flow of the hydraulic oil that flows out of the voltage drop value that produces of this liquid resistance element and second actuator port from described main valve is proportional through the liquid resistance element; With the pressure of second actuator port of described main valve and the hydraulic oil in the pipeline between the described liquid resistance element pilot pressure as described equilibrium valve; Second working end of executive component is communicated with described fuel tank; The flow of the hydraulic oil that flows out from second actuator port of described main valve by control is controlled the speed of described executive component action, and/or control the speed of described executive component action by regulating described liquid resistance element.
By technique scheme of the present invention, the pilot pressure of equilibrium valve (promptly, second actuator port of main valve and the pressure of the hydraulic oil in the pipeline between the liquid resistance element) produce by the liquid resistance element, and the voltage drop value that this liquid resistance element forms is proportional, promptly only relevant with the aperture of main valve with the flow of the hydraulic oil that second actuator port from described main valve flows out.Therefore the pilot pressure of equilibrium valve is not subjected to the influence of the load that executive component (for example oil hydraulic cylinder in the background technique) born fully, and is therefore more stable.In addition, the pilot pressure of equilibrium valve is controlled by the aperture of control main valve, and need not to control by regulating back pressure, therefore, hydraulic control circuit according to the present invention need not back pressure, so also just system pressure has been reduced a lot, owing to there is not back pressure, eliminated equilibrium valve and opened and closed retardation phenomenon simultaneously.Thereby can reduce system pressure, reduce the fluid flow, thereby reduced energy loss; And require not too high to the filler opening of main valve and the coupling of return opening.
Other features and advantages of the present invention will partly be described in detail in embodiment subsequently.
Description of drawings
Accompanying drawing is to be used to provide further understanding of the present invention, and constitutes the part of specification, is used from explanation the present invention with the specific embodiment of the present invention one, but is not construed as limiting the invention.
In the accompanying drawings:
Fig. 1 is the schematic representation of traditional decline load hydraulic control circuit;
Fig. 2 is the schematic representation according to the hydraulic control circuit of one embodiment of the present invention;
Fig. 3 is the schematic representation according to the hydraulic control circuit of another embodiment of the present invention;
Fig. 4 to Fig. 6 is the schematic representation of the hydraulic control circuit of another kind of mode of execution also according to the present invention;
Fig. 7 to Fig. 9 is the schematic representation of the hydraulic control circuit of another kind of mode of execution also according to the present invention;
Figure 10 is the schematic representation of the hydraulic control circuit of another kind of mode of execution also according to the present invention.
Description of reference numerals
1 working connection, 2 liquid resistance elements
3 fuel tanks, 4 Pilot operated check valves
5 solenoid directional control valves, 6 pilot operated directional control valves
7 executive components, 71 oil hydraulic cylinders
711 rodless cavities, 712 rod chambers
72 oil hydraulic motors, 721 filler openings
722 oil outlets, 8 main valves
9 equilibrium valves, 10 relief valves
11 first one-way valves, 12 second one-way valves
Embodiment
Below in conjunction with accompanying drawing the specific embodiment of the present invention is elaborated.Should be understood that embodiment described herein only is used for description and interpretation the present invention, is not limited to the present invention.
As shown in Figure 2, on the one hand, the invention provides a kind of hydraulic control circuit, wherein, this hydraulic control circuit comprises working connection 1, liquid resistance element 2 and fuel tank 3, and described liquid resistance element 2 is connected with described fuel tank 3 and other being connected on the described working connection 1.
In such scheme, the relation of the fluid flow Q in the oil liquid pressure p in the working connection 1, the flow area A of liquid resistance element 2 and the working connection 1 for example can draw by following formula (1):
Wherein, Q is the fluid flow; C
dBe flow coefficient; A is that the flow area Δ p of liquid resistance element 2 represents that fluid is fluid density through the voltage drop value ρ that liquid resistance element 2 produces.
Because the fluid in the working connection 1 flow to fuel tank 3 behind liquid resistance element 2, and the oil liquid pressure in the fuel tank 3 is a definite value, so the Δ p that the oil liquid pressure p in the working connection 1 equals in the above-mentioned formula (1) adds that this is as the oil liquid pressure in the fuel tank of definite value.Can draw from formula (1), this oil liquid pressure p and fluid flow Q square are directly proportional, with square being inversely proportional to of the circulation area A of liquid resistance element 2.When the circulation area A of liquid resistance element 2 was definite value, the oil liquid pressure p in the working connection 1 depended on flow Q.That is, oil liquid pressure p increases along with the increase of fluid flow Q proportionally.
Therefore, according to such scheme, can control pressure in the working connection 1 by controlling flow in the described working connection 1, thereby make the pressure in the working connection 1 not be vulnerable to the influence of other parts in the hydraulic system, and need not to be provided with extra pressure valve and control pressure in the working connection 1, make that whole hydraulic system obtains simplifying.
Need to prove, above formula (1) only is general flow rate calculation formula, for example when being single damping hole, throttle valve or reduction valve, described liquid resistance element can be suitable for this formula (1), if selected liquid resistance element difference (for example when the liquid resistance element is the damping hole of a plurality of serial or parallel connections or when other more complicated liquid resistance element), its concrete flow rate calculation mode also may be different, but still can realize controlling the purpose of the pressure in the working connection 1 by controlling flow in the described working connection 1.
Described liquid resistance element 2 can be fixedly damping hole, adjustable damping hole, reduction valve or throttle valve etc.Preferably, described liquid resistance element 2 is adjustable damping hole or throttle valve, thereby except by the flow of control in the working connection 1, can also regulate pressure in the working connection 1 by the circulation area of regulating adjustable damping hole or throttle valve.
In above-mentioned hydraulic control circuit, described working connection 1 can be connected with the various hydraulic unit of pilot pressure or the oil hydraulic circuits of needing, thereby is used to control its pressure.For example, as shown in Figure 3, described working connection 1 can be communicated to the control port 41 of Pilot operated check valve 4, thereby controls the conducting of described Pilot operated check valve 4 or close.Perhaps, as shown in Figure 4, the control port 61,62 of the pilot operated directional control valve 6 that described working connection 1 can be communicated to by solenoid directional control valve 5.Thereby the hydraulic oil in the working connection 1 is controlled oil as the guide of pilot operated directional control valve 6, is used to control described pilot operated directional control valve 6 and commutates.More specifically, as shown in Figure 4, described solenoid directional control valve 5 can be the 3-position 4-way solenoid directional control valve, described pilot operated directional control valve 6 can be the 3-position 4-way pilot operated directional control valve, described working connection 1 is communicated to the oil inlet P 5 of described 3-position 4-way solenoid directional control valve, and two actuator port A5, B5 of described 3-position 4-way solenoid directional control valve are communicated to two control ports 61,62 of described 3-position 4-way pilot operated directional control valve respectively.When solenoid directional control valve 5 was positioned at position, a left side, the actuator port B5 of the hydraulic oil process solenoid directional control valve 5 in the working connection 1 flowed to the control mouth 62 of pilot operated directional control valve 6, makes pilot operated directional control valve 6 be moved to the left, and works in right position; When solenoid directional control valve 5 was positioned at right position, the actuator port A5 of the hydraulic oil process solenoid directional control valve 5 in the working connection 1 flowed to the control mouth 61 of pilot operated directional control valve 6, makes pilot operated directional control valve 6 move right, and works in position, a left side.
Further, as shown in Figure 4, two actuator port A6, B6 of described 3-position 4-way pilot operated directional control valve can be communicated to executive component 7 respectively.Thereby by the action of the further control actuating component 7 of the commutation of described pilot operated directional control valve 6, and the speed that just can regulate executive component 7 actions by the flow of controlling described working connection 1.As shown in Figure 5, described executive component 7 can be oil hydraulic cylinder 71, and two actuator port A6, B6 of described 3-position 4-way pilot operated directional control valve are communicated to the rodless cavity 711 and the rod chamber 712 of this oil hydraulic cylinder 71 respectively.As shown in Figure 6, described executive component 7 can be oil hydraulic motor 72, and two actuator port A6, B6 of described 3-position 4-way pilot operated directional control valve are communicated to the filler opening 721 and the oil outlet 722 of this oil hydraulic motor 72 respectively.
In Fig. 4 to Fig. 6, T5, T6 represent the return opening of solenoid directional control valve 5 and the return opening of pilot operated directional control valve 6 respectively.
Fig. 7 shows the hydraulic control circuit that also another kind of mode of execution of the present invention is provided, this hydraulic control circuit comprises working connection 1, liquid resistance element 2 and fuel tank 3, described liquid resistance element 2 is connected with described fuel tank 3 and other being connected on the described working connection 1, this control loop also comprises the main valve 8 that is arranged on the described working connection 1, equilibrium valve 9 and executive component 7, the first actuator port A8 of described main valve 8 is communicated with first working end of described executive component 7 by described equilibrium valve 9, the second actuator port B8 of described main valve 8 is communicated with second working end of described executive component 7, wherein, described liquid resistance element 2 is arranged on the pipeline between second working end of the second actuator port B8 of described main valve 8 and described executive component 7, the control port 91 of described equilibrium valve 9 is connected on the second actuator port B8 and the pipeline between the described liquid resistance element 2 of described main valve 8, and second working end of described executive component 7 is communicated with described fuel tank 3 with pipeline between the described liquid resistance element 2.
By technique scheme of the present invention, the pilot pressure of equilibrium valve 9 (promptly, the pressure of the hydraulic oil in second actuator port B8 of main valve 8 and the pipeline between the liquid resistance element 2 (being equivalent to the working connection 1 in the above-mentioned hydraulic control circuit)) produce by liquid resistance element 2, and the voltage drop value that this liquid resistance element 2 forms is proportional, promptly only relevant with the aperture of main valve 8 with the flow of the hydraulic oil that the second actuator port B8 from described main valve 8 flows out.Therefore the pilot pressure of equilibrium valve 9 is not subjected to the influence of the load that executive component 7 (for example oil hydraulic cylinder in the background technique) born fully, and is therefore more stable.In addition, the pilot pressure of equilibrium valve 9 is controlled by the aperture of control main valve 8, and need not to control by regulating back pressure, therefore, hydraulic control circuit according to the present invention need not back pressure, so also just system pressure has been reduced a lot, owing to there is not back pressure, eliminated equilibrium valve and opened and closed retardation phenomenon simultaneously.Thereby can reduce system pressure, reduce the fluid flow, thereby reduced energy loss; And require not too high to the filler opening of main valve 8 and the coupling of return opening.
In technique scheme of the present invention, as Fig. 8 and shown in Figure 9, described executive component 7 can be oil hydraulic cylinder 71, and first working end of described executive component 7 and second working end are respectively the rodless cavity 711 and the rod chamber 712 of described oil hydraulic cylinder 71; Perhaps, described executive component 7 is an oil hydraulic motor 72, and first working end of described executive component 7 and second working end are respectively the filler opening 721 and the oil outlet 722 of described oil hydraulic motor 72.When described executive component 7 can be for oil hydraulic cylinder 71, be corresponding with the decline load hydraulic control circuit described in the background technique, be that example is described in detail with this scheme below.
Described liquid resistance element 2 can be fixedly damping hole, adjustable damping hole, reduction valve or throttle valve.Preferably, described liquid resistance element 2 is adjustable damping hole or throttle valve, thereby except aperture, can also come the pilot pressure of adjustment valve 9, thereby the speed of regulating the decline load by the circulation area of regulating adjustable damping hole or throttle valve by the described main valve 8 of control.
Described liquid resistance element 2 can be used as parts independently and is installed on the oil pipe road between the rod chamber 712 of the second actuator port B of described main valve 1 and described oil hydraulic cylinder 71, and described liquid resistance element 2 also can be integrated in described main valve 8 or the described equilibrium valve 9.
When described liquid resistance element 2 was damping hole, described damping hole can be an independent damping hole, also can form by several damping hole series connection and/or parallel connection.
In load decline process, the repairing of the rod chamber 712 of oil hydraulic cylinder 71 directly comes from fuel tank 3, because the fluid in the rodless cavity 711 of oil hydraulic cylinder 71 flows back to fuel tank 3 through the return tube actuator port A8 and the oil return inlet T 8 of equilibrium valve 9, main valve 8 (promptly through), therefore system has enough fluid to add in the rod chamber 712 of oil hydraulic cylinder 71, and can not produce negative pressure.Preferably, as shown in figure 10, this hydraulic control circuit can also comprise first one-way valve 11 and second one-way valve 12, described first one-way valve 11 allows fluid to flow to the second actuator port B8 of described main valve 8 from the rod chamber 712 of described oil hydraulic cylinder 71, and described second one-way valve 12 allows fluid to flow to the rod chamber 712 of described oil hydraulic cylinder 71 from described fuel tank 3.For example, described first one-way valve 11 is on the pipeline between the second actuator port B8 of the rod chamber 712 of described oil hydraulic cylinder 71 and described main valve 8, and is and in parallel with described liquid resistance element 2; Described second one-way valve 12 and is connected with liquid resistance element 2 on the pipeline between the rod chamber 712 of described fuel tank 3 and described oil hydraulic cylinder 71.In this hydraulic control circuit uphill process, first one-way valve 11 can guarantee further that the fluid in the rod chamber 712 of oil hydraulic cylinder 71 flows to the second actuator port B8 of main valve 8, and can directly not flow back to fuel tank 3, thereby can guarantee other additional function of the system that do not influence.And in load decline process, second one-way valve 12 can further be guaranteed from rod chamber 712 repairings of fuel tank 3 to oil hydraulic cylinder 71.Because the fluid in the load decline process in the rod chamber 711 flows back to fuel tank through return tube, so there are enough repairing effects in system and can produce negative pressure.
Preferably, to shown in Figure 10, described hydraulic control circuit can also comprise the relief valve 10 on the pipeline between the control port 91 of other second actuator port B8 that is connected on described main valve 8 and described equilibrium valve 9 as Fig. 7.Thereby can further control the CLV ceiling limit value of the pilot pressure of equilibrium valve 9 by this relief valve 10.Certainly, this relief valve 10 also can omit.
Described main valve 8 can be selected as the case may be, and for example extremely shown in Figure 10 as Fig. 7, described main valve 8 can be three position four-way directional control valve.
Certainly, described Pilot operated check valve and pilot operated directional control valve also can be other liquid controling element.
On the other hand, as shown in Figure 2, the invention provides a kind of hydraulic control method, wherein, connect liquid resistance element 2 and make this liquid resistance element 2 take back fuel tank 3 by other on working connection 1, thereby with reference to the described principle of formula (1), can control the pressure of described working connection 1 by the flow of controlling described working connection 1 according to above.Thereby make the pressure in the working connection 1 not be vulnerable to the influence of other parts in the hydraulic system, and need not to be provided with extra pressure valve and control pressure in the working connection 1, make that whole hydraulic system obtains simplifying.
As indicated above, described working connection 1 can be used to control Pilot operated check valve 4 or pilot operated directional control valve 6, specifically can be referring to the explanation of above carrying out with reference to figure 3 to Fig. 6.
In addition, to shown in Figure 10, described hydraulic control method can also comprise: the main valve 8, equilibrium valve 9 and the executive component 7 that are arranged on the working connection 1 are provided as Fig. 7; Make hydraulic oil in first working end of described executive component 7 flow into the first actuator port A8 of described main valve 8 by described equilibrium valve 9; Flow into described fuel tank 3 after making the hydraulic oil that flows out from the second actuator port B8 of described main valve 8 produce pressure drops, and the flow of the hydraulic oil that flows out of the voltage drop value that produces of this liquid resistance element 2 and the second actuator port B8 from described main valve 8 is proportional through liquid resistance element 2; With the pressure of the second actuator port B8 of described main valve 8 and the hydraulic oil in the pipeline between the described liquid resistance element 2 pilot pressure as described equilibrium valve 9; Second working end of executive component 7 is communicated with described fuel tank 3; The flow of the hydraulic oil that flows out from the second actuator port B8 of described main valve 8 by control is controlled the speed of described executive component 7 actions, and/or control the speed of described executive component 7 actions by regulating described liquid resistance element 2.
By technique scheme of the present invention, the pilot pressure of equilibrium valve 9 (promptly, the pressure of the hydraulic oil in second actuator port B8 of main valve 8 and the pipeline between the liquid resistance element 2 (being equivalent to the working connection 1 in the above-mentioned hydraulic control circuit)) produce by liquid resistance element 2, and the voltage drop value that this liquid resistance element 2 forms is proportional, promptly only relevant with the aperture of main valve 8 with the flow of the hydraulic oil that the second actuator port B8 from described main valve 8 flows out.Therefore the pilot pressure of equilibrium valve 9 is not subjected to the influence of the load that executive component 7 (for example oil hydraulic cylinder in the background technique) born fully, and is therefore more stable.In addition, the pilot pressure of equilibrium valve 9 is controlled by the aperture of control main valve 8, and need not to control by regulating back pressure, therefore, hydraulic control circuit according to the present invention need not back pressure, so also just system pressure has been reduced a lot, owing to there is not back pressure, eliminated equilibrium valve and opened and closed retardation phenomenon simultaneously.Thereby can reduce system pressure, reduce the fluid flow, thereby reduced energy loss; And require not too high to the filler opening of main valve 8 and the coupling of return opening.
Can be with reference to the above relevant explanation of relevant hydraulic control circuit, the described liquid resistance element 2 in the hydraulic control method provided by the invention can be included in damping hole, reduction valve or the throttle valve that is provided with on the pipeline between second working end of the second actuator port B8 of described main valve 8 and executive component 7.Described liquid resistance element 2 also can be included in adjustable damping hole or the throttle valve that is provided with on the pipeline between second working end of the second actuator port B8 of described main valve 8 and executive component 7, to realize controlling the speed of described executive component 7 actions by regulating the described adjustable damping circulation area hole or throttle valve.
As Fig. 8 and shown in Figure 9, described executive component 7 can be oil hydraulic cylinder 71, and first working end of described executive component 7 and second working end are respectively the rodless cavity 711 and the rod chamber 712 of described oil hydraulic cylinder 71; Perhaps, described executive component 7 is an oil hydraulic motor 72, and first working end of described executive component 7 and second working end are respectively the filler opening 721 and the oil outlet 722 of described oil hydraulic motor 72.
Preferably, can also be according to described hydraulic control method provided by the invention by between the control port 91 of the second actuator port B8 of described main valve 8 and described equilibrium valve 9, the pilot pressure upper limit that relief valve 10 is controlled described equilibrium valve 9 being set.
Need to prove that each the concrete technical characteristics described in above-mentioned embodiment can carry out combination in any by any suitable manner, it falls within the scope disclosed in this invention equally.In addition, also can carry out combination in any between the various mode of execution of the present invention, as long as it is without prejudice to thought of the present invention, it should be considered as content disclosed in this invention equally.
Below describe preferred implementation of the present invention in conjunction with the accompanying drawings in detail; but; the present invention is not limited to the detail in the above-mentioned mode of execution; in technical conceive scope of the present invention; can carry out multiple simple variant to technological scheme of the present invention, these simple variant all belong to protection scope of the present invention.
Claims (22)
1. a hydraulic control circuit is characterized in that, this hydraulic control circuit comprises working connection (1), liquid resistance element (2) and fuel tank (3), and described liquid resistance element (2) is connected with described fuel tank (3) and other being connected on the described working connection (1).
2. hydraulic control circuit according to claim 1 is characterized in that, described liquid resistance element (2) is fixedly damping hole, adjustable damping hole, reduction valve or throttle valve.
3. hydraulic control circuit according to claim 1 is characterized in that, described working connection (1) is communicated to the control port (41) of Pilot operated check valve (4).
4. hydraulic control circuit according to claim 1 is characterized in that, described working connection (1) is communicated to the control port (61,62) of pilot operated directional control valve (6) by solenoid directional control valve (5).
5. hydraulic control circuit according to claim 4, it is characterized in that, described solenoid directional control valve (5) is the 3-position 4-way solenoid directional control valve, described pilot operated directional control valve (6) is the 3-position 4-way pilot operated directional control valve, described working connection (1) is communicated to the filler opening (P5) of described 3-position 4-way solenoid directional control valve, (A5 B5) is communicated to two control ports (61,62) of described 3-position 4-way pilot operated directional control valve respectively to two actuator ports of described 3-position 4-way solenoid directional control valve.
6. hydraulic control circuit according to claim 5 is characterized in that, (A6 B6) is communicated to executive component (7) respectively to two actuator ports of described 3-position 4-way pilot operated directional control valve.
7. hydraulic control circuit according to claim 6, it is characterized in that, described executive component (7) is oil hydraulic cylinder (71), and (A6 B6) is communicated to the rodless cavity (711) and the rod chamber (712) of this oil hydraulic cylinder (71) respectively to two actuator ports of described 3-position 4-way pilot operated directional control valve.
8. hydraulic control circuit according to claim 6, it is characterized in that, described executive component (7) is oil hydraulic motor (72), and (A6 B6) is communicated to the filler opening (721) and the oil outlet (722) of this oil hydraulic motor (72) respectively to two actuator ports of described 3-position 4-way pilot operated directional control valve.
9. hydraulic control circuit according to claim 1, it is characterized in that, this hydraulic control circuit also comprises the main valve (8) that is arranged on the described working connection (1), equilibrium valve (9) and executive component (7), first actuator port (A8) of described main valve (8) is communicated with first working end of described executive component (7) by described equilibrium valve (9), second actuator port (B8) of described main valve (8) is communicated with second working end of described executive component (7), described liquid resistance element (2) is arranged on the pipeline between second working end of second actuator port (8B) of described main valve (8) and described executive component (7), the control port (91) of described equilibrium valve (9) is connected on second actuator port (B8) and the pipeline between the described liquid resistance element (2) of described main valve (8), and second working end of described executive component (7) is communicated with described fuel tank (3) with pipeline between the described liquid resistance element (2).
10. hydraulic control circuit according to claim 9, it is characterized in that, this hydraulic control circuit also comprises first one-way valve (11) and second one-way valve (12), described first one-way valve (11) allows fluid to flow to second actuator port (B8) of described main valve (8) from second working end of described executive component (7), and described second one-way valve (12) allows fluid to flow to second working end of described executive component (7) from described fuel tank (3).
11. hydraulic control circuit according to claim 10, it is characterized in that, described first one-way valve (11) is positioned on the pipeline between second actuator port (B8) of second working end of described executive component (7) and described main valve (8), and in parallel with described liquid resistance element (2); Described second one-way valve (12) is positioned on the pipeline between second working end of described fuel tank (3) and described executive component (7), and connects with liquid resistance element (2).
12. hydraulic control circuit according to claim 9, it is characterized in that this hydraulic control circuit also comprises the relief valve (10) on the pipeline between the control port (91) of other second actuator port (B8) that is connected on described main valve (8) and described equilibrium valve (9).
13. hydraulic control circuit according to claim 9, it is characterized in that, described executive component (7) is oil hydraulic cylinder (71), and first working end of described executive component (7) and second working end are respectively the rodless cavity (711) and the rod chamber (712) of described oil hydraulic cylinder (71); Perhaps, described executive component (7) is oil hydraulic motor (72), and first working end of described executive component (7) and second working end are respectively the filler opening (721) and the oil outlet (722) of described oil hydraulic motor (72).
14. hydraulic control circuit according to claim 9 is characterized in that, described main valve (8) is a selector valve.
15. hydraulic control circuit according to claim 9 is characterized in that, described liquid resistance element (2) is integrated in described main valve (8) or the described equilibrium valve (9).
16. hydraulic control method, it is characterized in that, otherly connect liquid resistance element (2) and make this liquid resistance element (2) take back fuel tank (3) by going up, thereby can control the pressure of described working connection (1) by the flow of controlling described working connection (1) at working connection (1).
17. hydraulic control method according to claim 16 is characterized in that, described working connection (1) is used to control Pilot operated check valve (4) or pilot operated directional control valve (6).
18. hydraulic control method according to claim 16 is characterized in that, this hydraulic control method also comprises:
The main valve (8), equilibrium valve (9) and the executive component (7) that are arranged on the described working connection (1) are provided;
Make hydraulic oil in first working end of described executive component (7) flow into first actuator port (A8) of described main valve (8) by described equilibrium valve (9);
Flow into described fuel tank (3) after making the hydraulic oil that flows out from second actuator port (B8) of described main valve (8) produce pressure drop, and the flow of the hydraulic oil that flows out of the voltage drop value that produces of this liquid resistance element (2) and second actuator port (B8) from described main valve (8) is proportional through liquid resistance element (2);
With the pressure of second actuator port (B8) of described main valve (8) and the hydraulic oil in the pipeline between the described liquid resistance element (2) pilot pressure as described equilibrium valve (9);
Second working end of executive component (7) is communicated with described fuel tank (3);
The flow of the hydraulic oil that flows out from second actuator port (B8) of described main valve (8) by control is controlled the speed of described executive component (7) action, and/or control the speed that described executive component (7) moves by regulating described liquid resistance element (2).
19. hydraulic control method according to claim 18, it is characterized in that described liquid resistance element (2) is included in fixedly damping hole, adjustable damping hole, reduction valve or the throttle valve that is provided with on the pipeline between second working end of second actuator port (B8) of described main valve (8) and executive component (7).
20. hydraulic control method according to claim 18, it is characterized in that, described liquid resistance element (2) is included in adjustable damping hole or the throttle valve that is provided with on the pipeline between second working end of second actuator port (B8) of described main valve (8) and executive component (7), to realize controlling the speed of described executive component (7) action by regulating the described adjustable damping circulation area hole or throttle valve.
21. decline load hydraulic control method according to claim 18, it is characterized in that, described executive component (7) is oil hydraulic cylinder (71), and first working end of described executive component (7) and second working end are respectively the rodless cavity (711) and the rod chamber (712) of described oil hydraulic cylinder (71); Perhaps, described executive component (7) is oil hydraulic motor (72), and first working end of described executive component (7) and second working end are respectively the filler opening (721) and the oil outlet (722) of described oil hydraulic motor (72).
22. decline load hydraulic control method according to claim 18, it is characterized in that this method is also by being provided with the pilot pressure upper limit that relief valve (10) is controlled described equilibrium valve (9) between the control port (91) of second actuator port (B8) of described main valve (8) and described equilibrium valve (9).
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201010255962 CN102042273B (en) | 2010-08-13 | 2010-08-13 | Hydraulic control loop and method |
| PCT/CN2011/076878 WO2012019498A1 (en) | 2010-08-13 | 2011-07-05 | Hydraulic control circuit and method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201010255962 CN102042273B (en) | 2010-08-13 | 2010-08-13 | Hydraulic control loop and method |
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| Publication Number | Publication Date |
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| CN102042273A true CN102042273A (en) | 2011-05-04 |
| CN102042273B CN102042273B (en) | 2013-03-27 |
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| CN 201010255962 Active CN102042273B (en) | 2010-08-13 | 2010-08-13 | Hydraulic control loop and method |
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| CN (1) | CN102042273B (en) |
| WO (1) | WO2012019498A1 (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN102269190A (en) * | 2011-07-04 | 2011-12-07 | 长沙中联重工科技发展股份有限公司 | Hydraulic control loop |
| WO2012019498A1 (en) * | 2010-08-13 | 2012-02-16 | 长沙中联重工科技发展股份有限公司 | Hydraulic control circuit and method |
| CN102583173A (en) * | 2011-12-19 | 2012-07-18 | 徐州重型机械有限公司 | Suspension arm telescopic hydraulic control system and crane with same |
| CN102758389A (en) * | 2012-06-28 | 2012-10-31 | 湖南海捷精密工业有限公司 | Hydraulic balance loop of mobile device |
| CN103089727A (en) * | 2011-10-31 | 2013-05-08 | 约克广州空调冷冻设备有限公司 | Reversing valve |
| WO2013063997A1 (en) * | 2011-10-31 | 2013-05-10 | 中联重科股份有限公司 | Hydraulic control loop |
| CN103603839A (en) * | 2013-11-20 | 2014-02-26 | 长沙中联消防机械有限公司 | Anti-shake hydraulic circuit, cantilever crane anti-shake hydraulic circuit, engineering machinery and engineering vehicle |
| CN104948524A (en) * | 2015-06-30 | 2015-09-30 | 中国船舶重工集团公司第七一九研究所 | Full-flow combined backpressure device with little pressure fluctuation |
| CN106246550A (en) * | 2016-09-08 | 2016-12-21 | 珠海格力电器股份有限公司 | Control device, control method and the compressor of a kind of guiding valve |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| WO2012019498A1 (en) * | 2010-08-13 | 2012-02-16 | 长沙中联重工科技发展股份有限公司 | Hydraulic control circuit and method |
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| CN103089727A (en) * | 2011-10-31 | 2013-05-08 | 约克广州空调冷冻设备有限公司 | Reversing valve |
| WO2013063997A1 (en) * | 2011-10-31 | 2013-05-10 | 中联重科股份有限公司 | Hydraulic control loop |
| CN102583173A (en) * | 2011-12-19 | 2012-07-18 | 徐州重型机械有限公司 | Suspension arm telescopic hydraulic control system and crane with same |
| CN102758389A (en) * | 2012-06-28 | 2012-10-31 | 湖南海捷精密工业有限公司 | Hydraulic balance loop of mobile device |
| CN103603839A (en) * | 2013-11-20 | 2014-02-26 | 长沙中联消防机械有限公司 | Anti-shake hydraulic circuit, cantilever crane anti-shake hydraulic circuit, engineering machinery and engineering vehicle |
| CN103603839B (en) * | 2013-11-20 | 2016-08-10 | 长沙中联消防机械有限公司 | Stabilization hydraulic circuit, jib stabilization hydraulic circuit, engineering machinery and engineering truck |
| CN104948524A (en) * | 2015-06-30 | 2015-09-30 | 中国船舶重工集团公司第七一九研究所 | Full-flow combined backpressure device with little pressure fluctuation |
| CN104948524B (en) * | 2015-06-30 | 2017-05-10 | 中国船舶重工集团公司第七一九研究所 | Full-flow combined backpressure device with little pressure fluctuation |
| CN106246550A (en) * | 2016-09-08 | 2016-12-21 | 珠海格力电器股份有限公司 | Control device, control method and the compressor of a kind of guiding valve |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2012019498A1 (en) | 2012-02-16 |
| CN102042273B (en) | 2013-03-27 |
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