CN104863913A - Control Valve Device With A Float Position - Google Patents
Control Valve Device With A Float Position Download PDFInfo
- Publication number
- CN104863913A CN104863913A CN201510087072.9A CN201510087072A CN104863913A CN 104863913 A CN104863913 A CN 104863913A CN 201510087072 A CN201510087072 A CN 201510087072A CN 104863913 A CN104863913 A CN 104863913A
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- Prior art keywords
- pipeline
- pressure
- control valve
- valve
- hydraulic cylinder
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Classifications
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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
- F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
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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
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/0401—Valve members; Fluid interconnections therefor
- F15B2013/0412—Valve members; Fluid interconnections therefor with three positions
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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
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20546—Type of pump variable capacity
- F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
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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
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/3052—Shuttle valves
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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
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
- F15B2211/3053—In combination with a pressure compensating valve
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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
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/3056—Assemblies of multiple valves
- F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
- F15B2211/3058—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having additional valves for interconnecting the fluid chambers of a double-acting actuator, e.g. for regeneration mode or for floating mode
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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
- F15B2211/30—Directional control
- F15B2211/31—Directional control characterised by the positions of the valve element
- F15B2211/3105—Neutral or centre positions
- F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
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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
- F15B2211/30—Directional control
- F15B2211/31—Directional control characterised by the positions of the valve element
- F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
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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
- F15B2211/30—Directional control
- F15B2211/32—Directional control characterised by the type of actuation
- F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
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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
- F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
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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
- F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
- F15B2211/5159—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a return line
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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
- F15B2211/52—Pressure control characterised by the type of actuation
- F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid pressure
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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
- F15B2211/575—Pilot pressure 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/605—Load sensing circuits
- F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
- F15B2211/6057—Load sensing circuits having valve means between output member and the load sensing circuit using directional control valves
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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
- F15B2211/60—Circuit components or control therefor
- F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
- F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
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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
- F15B2211/60—Circuit components or control therefor
- F15B2211/67—Methods for controlling pilot pressure
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention relates to a control valve device used for controlling a double-acting hydraulic pressure cylinder of a mobile operation machine. The control valve device includes a control valve connected to a conveying pipeline, a container pipeline, an ascending pipeline and a descending pipeline of a pump. The control valve has a middle position, an ascending position and a descending position. The control valve device has a floating position. When the control valve is moved to the descending position, the ascending pipeline is connected with the container pipeline and the pump is connected with a descending side and switching meets failure. A release valve is arranged, so that the descending side can bypass the control valve to connect with the container and the descending side can be connected with the container in the floating position. When the control valve moves to the ascending position during ascending operation, the conveying pipeline is connected with the ascending pipeline and the descending side is enabled to connect with the container by the aid of the release valve during ascending operation, so that the descending pipeline is connected with the container through the release valve and pressure medium flow from the descending side flows to the container via the release valve.
Description
Technical field
The present invention relates to a kind of control valve device of the double action oil hydraulic cylinder for controlling mobile operation machinery, wherein, described control valve device is included in the control valve of throttling in neutral position, this control valve is connected to the transfer line of pump, container pipeline, the rising pipeline be connected with the uplifted side of described oil hydraulic cylinder, on the decline pipeline be connected with the decline side of described oil hydraulic cylinder, wherein, described control valve has neutral position, lifting position and lowering position, described in described neutral position, the connection of transfer line and described container pipeline and described rising pipeline and described decline pipeline is cut off, described in described lifting position, transfer line is connected with described rising pipeline and described decline pipeline is connected with described container pipeline, described in described lowering position, transfer line is connected with described decline pipeline and described rising pipeline is connected with described container pipeline, wherein, described control valve device has the floating position for described oil hydraulic cylinder, wherein, being maneuvered in described lowering position at control valve described in described floating position, the pipeline that rises described in this lowering position is connected with described container pipeline, and the connection of the decline side of described pump and described oil hydraulic cylinder is switched to inoperative, wherein, be provided with escape valve, by means of this escape valve, the decline side of described oil hydraulic cylinder can be connected with container when getting around described control valve, wherein, in described floating position, by means of described escape valve, the decline side of described oil hydraulic cylinder is connected with described container.
Background technique
Control valve device according to generic uses in mobile operation machinery (such as excavator or wheeled loader), for hydraulic control cylinder, described oil hydraulic cylinder controls the working equipment of this Work machine, such as excavator or the cantilever of wheeled loader.
According in the control valve device of generic, achieve the decline of the saving energy of oil hydraulic cylinder when there is no pump volume stream when utilizing the floating position of control valve device to there is respective load on oil hydraulic cylinder, in this control valve device, the decline side of oil hydraulic cylinder is connected with container with uplifted side.Utilize the floating position of control valve device can realize equally, the working equipment dropped in lower surface of Work machine can follow bottom Roughness.
Known by DE 101 49 787B4 according to the control valve device of generic.In order to only there is a neutral position, the control valve of a lifting position and a lowering position realizes floating position in combination, by this document it is known that control valve being maneuvered in lowering position and configuration being maneuvered in rest position to the pressure balance of the decline side of oil hydraulic cylinder.Thus in lowering position, the uplifted side of oil hydraulic cylinder is connected with container via control valve.Make the connection of the decline side of pump and oil hydraulic cylinder be cut off and then make the connection of the decline side of pump and oil hydraulic cylinder to be switched to inoperative via the pressure balance be loaded in rest position.Be connected with container equally to make the decline side of oil hydraulic cylinder in floating position, be provided with and regulating relief valve variable in pressure, this relief valve configures to decline pipeline and in floating position, is adjusted to minimal adjustment pressure, to be connected with container the decline side of oil hydraulic cylinder equally in floating position.In addition, in floating position, the load pressure signal of oil hydraulic cylinder is interrupted to the transmission in the delivered volume controlling device of pump, thus pump only supplies minimum conveying stream in the floating position of control valve device.
Known by WO 2013/103954A2 equally according to the control valve device of generic.In order to only there is a neutral position, the control valve of a lifting position and a lowering position realizes floating position in combination, known by this document, control valve being maneuvered in lowering position, and in this lowering position, the uplifted side of oil hydraulic cylinder is connected with container via control valve.In order to the decline side of oil hydraulic cylinder being connected with container and making the connection of the decline side of pump and oil hydraulic cylinder be switched to inoperative, be provided with expulsion valve, this expulsion valve is controlled in switching position in floating position, and in this switching position, decline pipeline is connected with container.Pump can regulate electricly and so control in floating position in delivered volume, makes the quantity delivered that pump only provides little.
In the rising of oil hydraulic cylinder runs, in this control valve device, squeeze the hydraulic medium that from the decline side of oil hydraulic cylinder and flow to container via the corresponding control seamed edge of control valve.Depending on the structure of control valve, the pressure medium flow in container via the control valve be in lifting position for oil hydraulic cylinder can form high dynamic pressure and then be formed high to pressure, this dynamic pressure and cause corresponding energy loss and then cause corresponding loss power in running the rising being pressed in oil hydraulic cylinder.
Summary of the invention
Task of the present invention is, provides the control valve device that generic is mentioned in a kind of beginning, and this control valve device can realize floating position with little structure consumes and little cost consumption and can realize the reduction of loss power in the rising of oil hydraulic cylinder runs.
According to the present invention, this task solves in the following way, namely in the rising of oil hydraulic cylinder runs, control valve being maneuvered in lifting position, in this lifting position, transfer line is connected with rising pipeline, and in the rising of oil hydraulic cylinder runs, the decline side of oil hydraulic cylinder can be made to be connected with container by means of escape valve, thus the decline pipeline of oil hydraulic cylinder to be connected with container via escape valve and the pressure medium volume flow flowed out from the decline side of oil hydraulic cylinder flows out to container via escape valve.
Thus, design according to the present invention is, also use the escape valve that floating position has been existed, by means of this escape valve, the decline side of oil hydraulic cylinder can be connected with container when getting around control valve, to make the decline side of oil hydraulic cylinder be connected with container when getting around control valve in the rising of oil hydraulic cylinder runs.Utilize the escape valve existed can in the rising of oil hydraulic cylinder run, reduce the dynamic pressure in the decline side of oil hydraulic cylinder and then reduce thus rise operating energy dissipation and then reduce loss power.By repeatedly utilizing escape valve to be connected with container to make the decline side of oil hydraulic cylinder, the reduction of the floating position of oil hydraulic cylinder and the operating dynamic pressure of rising of oil hydraulic cylinder can be achieved thus with little structure consumes and little cost consumption.
According to favourable mode of execution of the present invention, escape valve is configured to the switching valve with rest position and flow passing position, and wherein, escape valve is in the floating position of oil hydraulic cylinder and being maneuvered in flow passing position when the rising of this oil hydraulic cylinder.This escape valve has little structure consumes, thus the reduction of operating dynamic pressure of rising is achieved to the unloading of the decline side of oil hydraulic cylinder with little structure consumes for floating position.
Special advantage is, according to favourable mode of execution of the present invention, escape valve is configured to regulating relief valve adjustable and variable in pressure, this relief valve makes the decline side of oil hydraulic cylinder be connected with container, wherein, relief valve is adjustable as minimal adjustment pressure in running in the floating position of oil hydraulic cylinder and in the rising of this oil hydraulic cylinder.Utilize changeable relief valve in adjustment pressure can realize with little structure consumes equally, the decline side of oil hydraulic cylinder is connected with container via the relief valve opened, thus achieves the unloading of the decline side of oil hydraulic cylinder equally with little structure consumes for floating position and for the reduction of operating dynamic pressure of rising.
According to favourable mode of execution of the present invention, relief valve is configured to pressure-limit valve or Combined pressure restricting valve and liquid-filling valve, and wherein, the adjustment pressure of pressure-limit valve is adjustable and variable.Utilize in adjustment pressure and then opening adjustable pressure-limit valve in pressure, can realize with simple especially structure consumes: the decline side achieving oil hydraulic cylinder for floating position and for the reduction of operating dynamic pressure of rising is connected with container.
Special advantage is, according to favourable mode of execution of the present invention, escape valve is arranged in the bypass line that decline pipeline is connected with container pipeline, wherein, in the downstream of bypass line to the joint on container pipeline, in container pipeline, be furnished with throttling arrangement.Normally, the control valve device of generic is provided with two escape valves, one in these escape valves is connected with rising pipeline and is arranged in and gets around in the bypass line of control valve, this bypass line is connected with the container pipeline be connected on control valve, and another in these escape valves is connected with decline pipeline and is arranged in and get around in the bypass line of control valve, this bypass line is connected with the container pipeline be connected on control valve equally.Escape valve is here for guaranteeing the maximum operating pressure in rising pipeline and decline pipeline.Configure to the escape valve of decline pipeline as regulating variable in pressure and the embodiment of changeable relief valve, can realize in the mode that abnormal cost is cheap thus, the relief valve existed makes the decline side of oil hydraulic cylinder be connected with container in order to the pressure maximum insurance of the decline side of oil hydraulic cylinder equally in running with the rising at oil hydraulic cylinder in the floating position of oil hydraulic cylinder.Utilize the throttling arrangement be arranged in container pipeline to achieve, enable to realize in the decline side of pressure medium from uplifted side to oil hydraulic cylinder reclaiming.
Alternatively, escape valve can be arranged in and guide to the take-off line of container from decline pipeline.Utilize the additional escape valve being arranged in and guiding to from decline pipeline the take-off line of container, the little additional structure for escape valve expends to achieve and in floating position with in running in rising, the decline side of oil hydraulic cylinder is connected with container.
According to suitable make of the present invention, escape valve according to load described control valve towards the control signal in lifting position direction and/or can be manipulated to according to floating position signal the decline side of oil hydraulic cylinder is connected with container position in.Thus, in a straightforward manner it is possible that escape valve rising run in and so handle in floating position, the decline side of oil hydraulic cylinder is connected with container via escape valve.
For this reason, in the embodiment of escape valve as relief valve, relief valve is enable to regulate towards the direction reducing described adjustment pressure towards the control signal in lifting position direction and/or according to described floating position signal according to controlling described control valve in an advantageous manner.
According to the embodiment of the present invention, escape valve can be handled electricly.There is such as can identifying by means of corresponding sensor or by means of the manipulation of operation equipment (such as operating handle), correspondingly to handle this escape valve with the running state run that rises of the floating position of the dynamic pressure of reduction.For this reason, be provided with electric control device in an adequate manner, this electric control device controls this escape valve and is connected with sensor or operation equipment.
According to alternative mode of execution of the present invention, escape valve can hydraulically be handled.
For this reason, in the embodiment of escape valve as relief valve, relief valve is enable hydraulically to change in adjustment pressure in an advantageous manner.
Here, make control signal be configured to hydraulic control pressure in an adequate manner, this hydraulic control pressure is present in the pilot pressure pipeline of control valve.
, make floating position signal configuration be hydraulic operation pressure in an adequate manner here, this hydraulic operation pressure is present in control pipeline.
The hydraulic operation of escape valve can realize with simple structure consumes in following situation: the Effector of escape valve is connected with manipulation pipeline, this manipulation pipeline is connected on the output terminal of change valve device, wherein, the first input end of change valve device be connected to guide described hydraulic control signal pilot pressure pipeline on, and the second input end of change valve device be connected to guide described hydraulic operation pressure control pipeline on.By means of change valve device in a straightforward manner likely, in rising runs, the pilot pressure of control valve is transferred on the Effector of escape valve, or will pressure transmission be handled on the Effector of escape valve in floating position, not only to make the decline side of oil hydraulic cylinder be connected with container by means of escape valve in floating position but also in the rising of oil hydraulic cylinder runs.
According to favourable improvement project of the present invention, be provided with two-position switching valve, this two-position switching valve controls described Effector to handle the loading of pressure.In an adequate manner, two-position switching valve makes the drainage of control pipeline to container and in the second switching position, makes control pipeline be connected with manipulation pressure source in the first switching position.Utilize this two-position switching valve in a straightforward manner it is possible that floating position is activated by being manipulated to by two-position switching valve in the second switching position or being removed by being manipulated in the first switching position by two-position switching valve.
Regulating in relief valve variable in pressure, Effector is preferably configured as adjustment pressure altering device.
Two-position switching valve electricly or hydraulically can handle enforcement.
According to make of the present invention, control valve has the pressure balance in the connection of the decline side of transfer line and the oil hydraulic cylinder being arranged in pump, and wherein, in the floating position of oil hydraulic cylinder, pressure balance is manipulated in rest position by pressure signal.Utilize the pressure balance (this pressure balance exists to independently handle this oil hydraulic cylinder with load in the drive system that adjusts at load-sensitive) existed the connection of pump and decline side can be made to be cut off and then to be switched to inoperative with little additional the expending for floating position by being loaded into by pressure balance in rest position.
Pressure signal is made to be formed by the discharge pressure of pump in an adequate manner.If be replaced in induced pressure and the discharge pressure of pump is directed to pressure balance towards on the chain of command of cut-off direction effect, then the pressure balance handled towards circulating direction towards rest position direction and by the discharge pressure of pump in the normal operation of induced pressure and spring can being maneuvered in rest position in a straightforward manner for floating position.
If pressure balance has the chain of command towards the effect of rest position direction, this chain of command is connected with load pressure signal pipeline, then the chain of command towards the effect of rest position direction of pressure balance can be controlled with little structure consumes by the loading of induced pressure or discharge pressure, wherein, two-position switching valve makes load pressure signal pipeline and induced pressure report that pipeline is connected in the first switching position, the conveying stream regulator of the adjustment pump that this induced pressure report pipeline adjusts with guiding to load-sensitive, and in the second switching position, make load pressure signal pipeline be connected with guiding the signal pipe line of described pressure signal.Thus, in the first switching position of two-position switching valve, pressure balance controlled towards rest position direction by load pressure signal and in a normal way operation independently to handle this oil hydraulic cylinder with load.For floating position, two-position switching valve being maneuvered in the second switching position, thus by means of the pressure balance being maneuvered in rest position, the transfer line of pump is cut off to the connection of the decline side of oil hydraulic cylinder.
Signal pipe line is made to be connected on the transfer line of pump in an adequate manner.
Accompanying drawing explanation
Other advantage of the present invention and details is explained in detail according to the embodiment shown in schematic diagram.Shown here:
Fig. 1 illustrates the circuti diagram of the first mode of execution of the present invention,
Fig. 2 goes out the Local map of Fig. 1 with enlarged icon, and
Fig. 3 illustrates the circuti diagram of the second mode of execution of the present invention.
Embodiment
Fig. 1 illustrates the circuti diagram of the drive system AS of the load-sensitive adjustment of the mobile operation machinery being such as configured to excavator or wheeled loader, and this drive system has according to control valve device SV of the present invention.
Drive system AS is included in the adjustable pump 1 in delivered volume aspect, and this pump runs in open loop in the illustrated embodiment and input side is connected with container 2 and outlet side is delivered in transfer line 3, and multiple customer is connected on this transfer line.The customer being configured to double action oil hydraulic cylinder 4 is shown in the illustrated embodiment, and the control in order to this customer is provided with according to control valve device SV of the present invention.
Control valve device SV is included in the control valve 5 of throttling in neutral position.The oil hydraulic cylinder 4 being configured to the linear actuator making the cantilever of Work machine rise and decline has uplifted side A and decline side B.Uplifted side A is connected on control valve 5 by means of rising pipeline 6a.Decline side B is connected on control valve 5 by means of decline pipeline 6b.In addition, control valve 5 be connected to pump 1 transfer line 3 on and be connected with container 2 by means of reservoir limb pipeline 8a, 8b of being connected on container pipeline 8.
In the illustrated embodiment, uplifted side A is made up of the pressure chamber of the piston side of oil hydraulic cylinder 4, and the side B that declines is made up of the pressure chamber of the piston rod side of oil hydraulic cylinder 4.
The control valve 5 being configured to multi-way valve has neutral position N, and in this neutral position, connection and the container pipeline 8 of the transfer line 3 of pump 1 are cut off with the connection of rising pipeline 6a and decline pipeline 6b.In the lifting position H of control valve 5, transfer line 3 is connected with rising pipeline 6a, and the pipeline 6b that declines is connected with reservoir limb pipeline 8b.Correspondingly, in the lowering position S of control valve 5, decline pipeline 6b is connected with transfer line 3, and the pipeline 6a that rises is connected with reservoir limb pipeline 8.Control valve 5 has the measuring diaphragm that is not shown specifically and is provided with the pressure balance 11a being arranged in this measuring diaphragm downstream in lifting position H.In addition, control valve 5 has the measuring diaphragm that is not shown specifically and is provided with the pressure balance 11b being arranged in this measuring diaphragm downstream in lowering position S.
Control valve 5 towards during the directional control of lifting position H pressure balance 11a downstream, oil hydraulic cylinder 4 induced pressure be present on uplifted side A reported and is transferred in load pressure signal pipeline 20a, this load pressure signal pipeline is connected on the induced pressure report pipeline 21 of load sensitive system.Correspondingly, control valve 5 towards during lowering position S directional control pressure balance 11b downstream, the induced pressure be present on the B of decline side of oil hydraulic cylinder 4 reported and is transferred in load pressure signal pipeline 20b, with induced pressure, this load pressure signal pipeline can report that pipeline 21 is connected.
Not shown further, be configured to multi-way valve, to be correspondingly connected to transfer line 3, container pipeline 8 and induced pressure report pipeline 21 for the control valve controlling other customer of described drive system.
The structure of pressure balance 11a or pressure balance 11b describes in detail according to Fig. 2, goes out the control valve device SV of Fig. 1 in the figure with enlarged icon.
The pressure balance 11a be arranged in the circulation path from transfer line 3 to asending pipe line 6a in lifting position H has flow passing position 12a and rest position 12b.Towards the direction of flow passing position 12a, pressure balance 11a loads by being present in the discharge pressure measuring flow controller downstream.Towards the direction of rest position 12b, pressure balance 11a is loaded by the highest load pressure of controlled customer.The load pressure signal path be made up of load pressure signal pipeline 20a of uplifted side A starts in a bifurcation in pressure balance 11a downstream, and in this bifurcation, load pressure signal pipeline 20a diverges from the circulation path of uplifted side A.Control pilot pressure face that pipeline 13a is bifurcated into pressure balance 11a from load pressure signal pipeline 20a, that act on towards rest position 12b direction.
The pressure balance 11b be arranged in the circulation path from transfer line 3 to decline pipeline 6b in lowering position S has flow passing position 12a and rest position 12b.Towards the direction of flow passing position 12a, pressure balance 11a loads by being present in the discharge pressure measuring flow controller downstream.Towards the direction of rest position 12b, pressure balance 11a is loaded by the highest load pressure of the customer controlled.The load pressure signal path formed by load pressure signal pipeline 20b of decline side B is in pressure balance 11a downstream a bifurcation, and in this bifurcation, load pressure signal pipeline 20b diverges from the circulation path of decline side B.Control pilot pressure face that pipeline 13b is bifurcated into pressure balance 11b from load pressure signal pipeline 20b, that act on towards rest position 12b direction.
When handling multiple customer, the highest load pressure of the customer of control is present in induced pressure report pipeline 21, to control the quantity delivered being configured to the pump 1 regulating pump in the illustrated embodiment.Pump 1 has controlling device 25 to control quantity delivered, adjustable pitch in gradient of such as axial piston pump, and this axial piston pump is in act on regulating piston device 26 to handle and is connected.Regulating piston device 26 has the pilot pressure room 26a of the direction effect towards the quantity delivered increasing pump 1, and this pilot pressure room loads with the discharge pressure of pump 1.For this reason, the control pipeline 3b be directed on transfer line 3 is provided with.In addition, towards the direction increasing quantity delivered, spring assembly 27 can work.Regulating piston pipeline 26, can control by means of the conveying stream regulator 30 being configured to flow of requirement regulating valve towards the loading of pilot pressure room 26b of direction effect of the quantity delivered reducing pump 1.Conveying stream regulator 30 makes pilot pressure room 26b be connected with container 2 in the first control position 30a illustrated.In the second control position 30b, pilot pressure room 26b is connected with the transfer line of pump 1 and then is loaded by the discharge pressure of pump 1.Conveying stream regulator 30 is loaded towards the second adjusted position 30b direction by the discharge pressure of pump 1.Towards the direction of the first control position 30a, by the induced pressure that is present in of the customer controlled and spring assembly 31, conveying stream regulator 30 reports that the highest load pressure in pipeline 21 loads, the pretension of described spring assembly is corresponding to the adjustment pressure difference of load sensitive system.
Control valve 5 can be handled towards the direction of lowering position S by means of control signal Y towards the direction of lifting position H by means of control signal X.Control signal X is made up of the hydraulic control pressure be present in pilot pressure pipeline 35a, and this hydraulic control pressure connects to the corresponding chain of command of control valve 5.Control signal Y is correspondingly made up of the hydraulic control pressure be present in pilot pressure pipeline 35b, and this hydraulic control pressure connects to the corresponding chain of command of control valve 5.
In order to the pressure maximum of oil hydraulic cylinder insures, control valve device SV is provided with relief valve 40a, 40b.Relief valve 40a is arranged in the bypass line 41a that rising pipeline 6a is connected with reservoir limb pipeline 8a, and this bypass line gets around control valve 5.Relief valve 40b is arranged in the bypass line 41b that decline pipeline 6b is connected with reservoir limb pipeline 8b, and this bypass line gets around control valve 5.At bypass line 41b to the downstream, joint on container pipeline 8 and bypass line 41a to the downstream, joint on container pipeline 8, in container pipeline 8, be furnished with throttling arrangement 42.
Relief valve 40a, 40b are configured to Combined pressure restricting valve and liquid-filling valve in the illustrated embodiment.
In addition, control valve device SV has the floating position for oil hydraulic cylinder 4, and in this floating position, the uplifted side A of oil hydraulic cylinder 4 is connected with container 2 with decline side B.In the floating position of oil hydraulic cylinder 4, control valve 5 being maneuvered in lowering position S, and in this lowering position, rising pipeline 6a is connected with reservoir limb pipeline 8a and then with container pipeline 8.
In addition, in floating position, pump 1 is made to be switched to inoperative with the connection of the decline side B of oil hydraulic cylinder 4.For this reason, when control valve 5 is in lowering position S, the pressure balance 11b be arranged in the transfer line 3 of pump 1 and the connection of the decline side B of oil hydraulic cylinder 4 is manipulated in rest position 12b by pressure signal.
For this reason, load pressure signal pipeline 20b is connected on two-position switching valve 50, and this load pressure signal pipeline is connected with the chain of command acted on towards rest position 12b direction of pressure balance 11b in the lowering position S of control valve 5.Switching valve 50 has the first switching position 50a, and in this first switching position, load pressure signal pipeline 20b and induced pressure report that pipeline 21 is connected, and this induced pressure report pipeline guides to the conveying stream regulator 30 of the adjustment pump 1 of load-sensitive adjustment.Switching valve 50 has the second switching position 50b, and in this second switching position, load pressure signal pipeline 20b is connected with the signal pipe line 51 of guide pressure signal.
In the illustrated embodiment, pressure signal is formed by the discharge pressure of pump 1, and for this reason, signal pipe line 51 is connected on the transfer line 3 of pump 1.
Two-position switching valve 50 to being maneuvered in the first switching position 50a by means of spring 52 and can be switched in the second switching position 50b by means of Effector 53.In the floating position of control valve device SV, two-position switching valve 50 being maneuvered in the second switching position 50b.
In the illustrated embodiment, two-position switching valve 50 can be handled by electricity, and for this reason, Effector 53 is made up of magnet (such as magnetic switch), this magnet and being connected for the electric control device controlled of not being shown specifically.
In order to make decline pipeline 6b be connected with container 2 in floating position, control valve device 5 is provided with escape valve 60, makes the decline side B of oil hydraulic cylinder 4 be connected with container 2 when getting around control valve 5 by means of this escape valve in floating position.
In addition according to the present invention, escape valve 60 is utilized can to reduce the dynamic pressure be present in the B of decline side, to reduce dissipation power in the rising of oil hydraulic cylinder 4 runs.In rising runs, control valve 5 being maneuvered in lifting position H, and in this lifting position, transfer line 3 is connected with rising pipeline 6a.In the rising of oil hydraulic cylinder 4 runs, the decline side B of oil hydraulic cylinder 4 is connected by means of escape valve 60 with container 2, thus the decline pipeline 6b of oil hydraulic cylinder 4 to be connected with container 2 via escape valve 60 and to flow out to container 2 from the pressure medium volume flow that the decline side B of oil hydraulic cylinder 4 flows out via escape valve 50 and then when getting around control valve 5.
In the embodiment of Fig. 1 and Fig. 2, escape valve 60 is arranged in and guides to the take-off line 6c of container 2 from decline pipeline 6b.Escape valve 60 is configured to regulating relief valve 61 adjustable and variable in pressure, and this relief valve makes the decline pipeline 6b of oil hydraulic cylinder 4 be connected with container 2.Relief valve 61 is not only adjustable as minimal adjustment pressure in floating position but also in the rising of oil hydraulic cylinder 4 runs.
Relief valve 61 is configured to Combined pressure restricting valve and liquid-filling valve 62 in the illustrated embodiment, and wherein, the adjustment pressure of pressure-limit valve is adjustable and variable.
Relief valve 61 is adjusted to maximal regulated pressure by means of spring assembly 63.The pretension of spring assembly 63 and then the adjustment pressure of adjustable relief valve 61 can be changed by means of Effector 65.
In order to make relief valve 61 not only be adjusted to minimal adjustment pressure in floating position but also in rising runs, relief valve 61 can regulate towards reducing the direction regulating pressure towards the control signal X in lifting position direction and/or according to floating position signal Z according to controlling described control valve 5.
In the illustrated embodiment, relief valve 61 can hydraulically change in adjustment pressure.
As hereinbefore explain, control signal X is configured to hydraulic control pressure, and this hydraulic control pressure is present in pilot pressure pipeline 35a.Floating position signal Z is configured to hydraulic operation pressure, and this hydraulic operation pressure is present in control pipeline 70.Control pipeline 70 to be here connected with manipulation pressure source 71 (the pilot pressure pump of such as drive system AS or supply pump).
In order to not only relief valve 61 is adjusted to minimal adjustment pressure by floating position signal Z but also in rising runs by control signal X in floating position, the Effector 65 of relief valve 61 is connected with manipulation pipeline 75, and this manipulation pipeline is connected on the output terminal of change valve device 76.The first input end of change valve device 76 is connected to by means of take-off line 77 and guides hydraulic control pressure and then guide on the pilot pressure pipeline 35a of control signal X.Second input end of change valve device 76 is connected on the control pipeline 70 of guiding hydraulic operation pressure Z.In order to only be transferred on Effector 65 as floating position signal Z in floating position using being present in the manipulation pressure controlled in pipeline 70, Effector 65 utilizes the loading of the floating position signal Z formed by the manipulation pressure controlled in pipeline 70 can control by means of two-position switching valve 50.
In the first switching position 50a of two-position switching valve 50, control pipeline 70 with handle the section that is connected of pressure source 71 and to be cut off and the section be connected with the second input end of change valve device 76 controlling pipeline 70 is vented to container 2.In the second switching position 50b of two-position switching valve 50, control pipeline 70 and open, thus floating position signal Z is present on the second input end of change valve device 76.
In fig 1 and 2, control valve 5 and relief valve 40a, 40b are arranged in control valve housing 80 jointly.
Be arranged in a housing or mounting plate 81 to activate and remove necessary two-position, floating position switching valve 50, this housing with Flange joint on control valve housing 80.
Escape valve 60 is arranged in a housing or mounting plate 82, this housing equally with Flange joint on control valve housing 80.
Second mode of execution of the present invention shown in Figure 3.Identical component is provided with identical reference character.
In figure 3, in order to oil hydraulic cylinder 4 rising run in in floating position, make the decline side B of oil hydraulic cylinder 4 be connected with container 2, the function of escape valve 60 is accepted by the relief valve 40b existed, this relief valve is arranged in bypass line 41b, and this bypass line makes decline pipeline 6b be connected with container 2.With Fig. 1 and Fig. 2 correspondingly, the relief valve 40b with the function of escape valve 60 of Fig. 3 is configured to regulating relief valve 61 adjustable and variable in pressure, this relief valve is preferably configured as Combined pressure restricting valve and liquid-filling valve 62, wherein, the adjustment pressure of pressure-limit valve is adjustable and variable by means of Effector 65.
The control valve device SV according to the present invention of Fig. 1 to 3 works as follows.
In the rising of oil hydraulic cylinder 4 runs, two-position switching valve 50 is not controlled and is in the first switching position 50a, and in this first switching position, floating position is removed.Control signal X makes control valve 5 load towards lifting position H direction and is present in via selector valve 76 in manipulation pipeline 75, thus, adjustable relief valve 40b (Fig. 3) or 61 (Fig. 1 and Fig. 2) in pressure are being regulated to be regulated towards reducing the direction regulating pressure by control signal X.Bypass can be realized switch when relief valve 40b or 61 opens, utilize this bypass to switch and the decline side B of oil hydraulic cylinder 4 is connected with container 2 when getting around control valve 5.Thus, in the rising of oil hydraulic cylinder 4 running, making the dynamic pressure at the B place, decline side of oil hydraulic cylinder 4 and then pressure being reduced by activating relief valve 40b or 61 by control signal X, the loss power of this drive system AS can be reduced thus.
In order to the floating position of oil hydraulic cylinder 4, control valve 5 to be manipulated in lowering position S by control signal Y and two-position switching valve 50 is manipulated in the second switching position 50b.The discharge pressure be present in the transfer line 3 of pump 1 to be present in thus in load pressure signal pipeline 20b and to be loaded in rest position 12b by pressure balance 11b.The induced pressure of oil hydraulic cylinder 4 blocks to induced pressure report pipeline 21 and then to the transmission on the conveying stream regulator 30 of pump 1 in the second switching position 50b of two-position switching valve 50, thus pump 1 remains in the position with minimum delivery stream.In addition, in the second switching position 50b of two-position switching valve 50, floating position signal Z is present in manipulation pipeline 75 via selector valve 76, thus, relief valve 40b or 61 is regulated, to make the decline side B of oil hydraulic cylinder 4 be connected with container towards reducing the direction regulating pressure by floating position signal Z.The uplifted side A of oil hydraulic cylinder 4 is connected with container 2 via the control valve 5 be in lowering position S.In floating position, the stress-free decline of oil hydraulic cylinder 4 can be achieved thus when there is no the conveying stream of pump 1.Here, to achieve the recovery the calm pipeline 8 of pressure medium or the decline side B from container 2 to oil hydraulic cylinder 4 with short flow distance via relief valve 40b or 61.
In floating position, equally by the uplifted side A of oil hydraulic cylinder 4 and achieving without pressure switching of decline side B: the working equipment be reduced in lower surface of Work machine can produce bottom Roughness and can adaptive bottom profile trend.
The present invention has series of advantages:
Utilize and by repeatedly utilizing escape valve 60 according to escape valve according to the present invention 60 can not only achieve the floating position of oil hydraulic cylinder 4 with less structure consumes and cost consumption but also achieve the reduction of the operating dynamic pressure of rising of oil hydraulic cylinder 4.
If the function of escape valve 60 is accepted by the relief valve 40b existed, for the connection of decline side B in floating position of oil hydraulic cylinder 4 and the reduction for operating dynamic pressure of rising, without the need to additional escape valve 60, but only to regulate in pressure convertibly and variably implementing the relief valve 40b existed of the decline side B of this oil hydraulic cylinder 4.
In the present invention, by repeatedly utilizing escape valve 60 to draw less structure consumes for these two functions and less cost consumption for the floating position of oil hydraulic cylinder 4 with for the reduction of operating dynamic pressure of rising.
The present invention is not limited to shown embodiment.Be replaced in and handle two-position switching valve 50 electricly, this two-position switching valve 50 can alternatively hydraulically, such as be handled by hydraulic pressure pwc pilot pressure.
Be substituted in and regulate escape valve 60 described in pressure aspect hydraulic regulation, alternatively in adjustment pressure, regulate this escape valve 60 to be possible electricly, wherein, control signal X and floating position signal Z can detect by means of sensor or for floating position or in the rising of this oil hydraulic cylinder 4 runs the manipulation of escape valve 60 can directly be identified by the manipulation of operation equipment (such as operating handle) and control signal, utilize this operation equipment can control rise operation and floating position.
Claims (22)
1. one kind for controlling the control valve device (SV) of the double action oil hydraulic cylinder (4) of mobile operation machinery, wherein, described control valve device (SV) is included in the control valve (5) of throttling in neutral position, this control valve is connected to the transfer line (3) of a pump (1), one container pipeline (8), the one rising pipeline (6a) be connected with the uplifted side (A) of described oil hydraulic cylinder (4), on the one decline pipeline (6b) be connected with the decline side (B) of described oil hydraulic cylinder (4), wherein, described control valve (5) has neutral position (N), lifting position (H) and lowering position (S), in described neutral position, described transfer line (3) and described container pipeline (8) are cut off with the connection of described rising pipeline (6a) and described decline pipeline (6b), in described lifting position, described transfer line (3) is connected with described rising pipeline (6a) and described decline pipeline (6b) is connected with described container pipeline (8), in described lowering position, described transfer line (3) is connected with described decline pipeline (6b) and described rising pipeline (6a) is connected with described container pipeline (8), wherein, described control valve device (SV) has the floating position for described oil hydraulic cylinder (4), wherein, in the floating position of described oil hydraulic cylinder (4), described control valve (5) being maneuvered in described lowering position (S), in this lowering position, described rising pipeline (6a) is connected with described container pipeline (8), and described pump (1) is switched to inoperative with the connection of the decline side (B) of described oil hydraulic cylinder (4), wherein, one escape valve (60) is set, the decline side (B) of described oil hydraulic cylinder (4) can be made to be connected with described container (2) when walking around described control valve (5) by means of this escape valve, wherein, in described floating position, by means of described escape valve (60), the decline side (B) of described oil hydraulic cylinder (4) is connected with described container (2), it is characterized in that, in the rising of described oil hydraulic cylinder (4) runs, described control valve (5) being maneuvered in described lifting position (H), in this lifting position, described transfer line (3) is connected with described rising pipeline (6a), in the rising of described oil hydraulic cylinder (4) runs, the decline side (B) of described oil hydraulic cylinder (4) can be made to be connected with described container (2) by means of described escape valve (60), thus the decline pipeline (6b) of described oil hydraulic cylinder (4) to be connected with described container (2) via described escape valve (60) and the pressure medium volume flow flowed out from the decline side (B) of described oil hydraulic cylinder (4) flow to described container (2) via described escape valve (60).
2. control valve device according to claim 1, it is characterized in that, described escape valve (60) is configured to the switching valve with rest position and flow passing position, wherein, described escape valve to being maneuvered in described flow passing position when described oil hydraulic cylinder (4) rises in described floating position.
3. control valve device according to claim 1, is characterized in that, described escape valve (60) be configured to regulate can regulate in pressure and the relief valve (40b that can change; 61), described relief valve makes the decline side (B) of described oil hydraulic cylinder (4) be connected with described container (2), wherein, and described relief valve (40b; 61) minimal adjustment pressure can be adjusted in running in described floating position and in the rising of described oil hydraulic cylinder (4).
4. control valve device according to claim 3, is characterized in that, described relief valve (40b; 61) be configured to pressure-limit valve or Combined pressure-limiting-and liquid-filling valve (62), wherein, the adjustment pressure of described pressure-limit valve can regulate and can change.
5. control valve device according to any one of claim 1 to 4, it is characterized in that, described escape valve (60) is arranged in the bypass line (41b) that described decline pipeline (6b) is connected with described container pipeline (8), wherein, in the downstream of described bypass line (41b) with the joint of described container pipeline (8), in described container pipeline (8), arrange a throttling arrangement (42).
6. control valve device according to any one of claim 1 to 4, it is characterized in that, described escape valve (60) is arranged in the take-off line (6c) from described decline pipeline (6b) towards described container (2).
7. control valve device according to any one of claim 1 to 6, it is characterized in that, described escape valve (60) can according to the control signal (X) that described control valve (5) is loaded towards the direction of described lifting position (H) and/or being maneuvered to according to floating position signal (Z) the decline side (B) of described oil hydraulic cylinder (4) is connected with described container (2) position in.
8. the control valve device according to any one of claim 3 to 7, is characterized in that, described relief valve (40b; 61) can regulate towards the direction reducing described adjustment pressure towards the control signal (X) of the direction controlling of described lifting position (H) and/or according to described floating position signal (Z) according to by described control valve (5).
9. control valve device according to any one of claim 1 to 8, is characterized in that, described escape valve (60) can be handled by electricity.
10. control valve device according to any one of claim 1 to 8, is characterized in that, described escape valve (60) can by hydraulic operation.
11. control valve devices according to any one of claim 3 to 10, is characterized in that, described relief valve (40b; 61) can hydraulically change in adjustment pressure.
12. control valve devices according to any one of claim 7 to 11, it is characterized in that, described control signal (X) is configured to hydraulic control pressure, and this hydraulic control pressure is present in the pilot pressure pipeline (35a) of described control valve (5).
13. control valve devices according to any one of claim 7 to 12, it is characterized in that, described floating position signal (Z) is configured to hydraulic operation pressure, and this hydraulic operation pressure is present in and controls in pipeline (70).
14. control valve devices according to claim 12 or 13, it is characterized in that, the Effector (65) of described escape valve (60) is connected with manipulation pipeline (75), this manipulation pipeline is connected to the output terminal of change valve device (76), wherein, the first input end of described change valve device (76) be connected to guide described hydraulic control pressure (X) pilot pressure pipeline (35a) and the second input end of described change valve device (76) is connected to the control pipeline (70) guiding described hydraulic operation pressure (Z).
15. control valve devices according to claim 14, it is characterized in that, arrange a two-position switching valve (50), this two-position switching valve makes the drainage of described control pipeline (70) to described container (2) and in the second switching position (50b), makes described control pipeline (70) be connected with manipulation pressure source (71) in the first switching position (50a).
16. control valve devices according to claim 15, is characterized in that, described two-position switching valve (70) being maneuvered in described second switching position (50b) in described floating position.
17., according to claim 14 to the control valve device according to any one of 16, is characterized in that, described relief valve (40b; 61) Effector (65) is configured to regulate pressure altering device.
18., according to claim 15 to the control valve device according to any one of 17, is characterized in that, described two-position switching valve (50) can be handled by electricity or can by hydraulic operation.
19. control valve devices according to any one of claim 1 to 18, it is characterized in that, described control valve (5) has the pressure balance (11b) in the joint of the decline side (B) of transfer line (3) and the described oil hydraulic cylinder (4) being arranged in described pump (1), wherein, in the floating position of described oil hydraulic cylinder (4), described pressure balance (11b) is manipulated in rest position (12b) by pressure signal.
20. control valve devices according to claim 19, it is characterized in that, described pressure signal is formed by the discharge pressure of described pump (1).
21. control valve devices according to claim 20, it is characterized in that, described pressure balance (11b) has the chain of command that the direction towards rest position (12b) acts on, this chain of command is connected with load pressure signal pipeline (20b), wherein, described two-position switching valve (50) makes described load pressure signal pipeline (20b) and induced pressure report that pipeline (21) is connected in the first switching position (50), the conveying stream regulator (30) of the adjustment pump (1) that this induced pressure report pipeline adjusts with guiding to load-sensitive, described two-position switching valve makes described load pressure signal pipeline (20b) be connected with guiding the signal pipe line (51) of described pressure signal in the second switching position (50b).
22. control valve devices according to claim 21, is characterized in that, described signal pipe line (51) is connected to the transfer line (3) of described pump (2).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102014102336.6A DE102014102336A1 (en) | 2014-02-24 | 2014-02-24 | Control valve device with a floating position |
| DE102014102336.6 | 2014-02-24 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104863913A true CN104863913A (en) | 2015-08-26 |
| CN104863913B CN104863913B (en) | 2018-06-12 |
Family
ID=52472184
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510087072.9A Active CN104863913B (en) | 2014-02-24 | 2015-02-25 | Control valve gear with floating position |
Country Status (3)
| Country | Link |
|---|---|
| EP (1) | EP2910796B9 (en) |
| CN (1) | CN104863913B (en) |
| DE (1) | DE102014102336A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN106927402A (en) * | 2015-11-11 | 2017-07-07 | 林德材料处理有限责任公司 | The jacking equipment of ground conveying machine and the load on the load-receipt device of ground conveying machine is unloaded the method being placed on discharge face |
| CN111655953A (en) * | 2017-08-10 | 2020-09-11 | 普茨迈斯特工程有限公司 | Large manipulator and hydraulic circuit assembly for a large manipulator |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6914206B2 (en) | 2018-01-11 | 2021-08-04 | 株式会社小松製作所 | Hydraulic circuit |
| DE102020210441A1 (en) | 2020-08-17 | 2022-02-17 | Hawe Hydraulik Se | Proportional spool valve with a pressure relief valve, pressure relief valve and hydraulic system |
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- 2014-02-24 DE DE102014102336.6A patent/DE102014102336A1/en not_active Withdrawn
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| CN1441171A (en) * | 2002-02-04 | 2003-09-10 | 神钢建设机械株式会社 | Controller for hydraulic operation mechanism and its controlling method |
| US20050092169A1 (en) * | 2003-10-23 | 2005-05-05 | Sauer-Danfoss Aps | Control device for a hydraulic lifting arrangement |
| JP2010525274A (en) * | 2007-05-02 | 2010-07-22 | ローベルト ボツシユ ゲゼルシヤフト ミツト ベシユレンクテル ハフツング | Valve device with individual pressure balance and descent brake valve |
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Also Published As
| Publication number | Publication date |
|---|---|
| EP2910796B1 (en) | 2018-04-04 |
| EP2910796B9 (en) | 2018-10-10 |
| CN104863913B (en) | 2018-06-12 |
| EP2910796A1 (en) | 2015-08-26 |
| DE102014102336A1 (en) | 2015-08-27 |
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