CN101191506A - Double check valve having floating function - Google Patents
Double check valve having floating function Download PDFInfo
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- CN101191506A CN101191506A CNA2007101371672A CN200710137167A CN101191506A CN 101191506 A CN101191506 A CN 101191506A CN A2007101371672 A CNA2007101371672 A CN A2007101371672A CN 200710137167 A CN200710137167 A CN 200710137167A CN 101191506 A CN101191506 A CN 101191506A
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- valve
- control 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
- 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
- F15B13/01—Locking-valves or other detent i.e. load-holding devices
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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
- F15B2211/20576—Systems with pumps with multiple pumps
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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
- F15B2211/30505—Non-return valves, i.e. check valves
- F15B2211/3051—Cross-check 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
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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
- F15B2211/3122—Special positions other than the pump port being connected to working ports or the working ports being connected to the return line
- F15B2211/3127—Floating position connecting the working ports and the 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
- F15B2211/30—Directional control
- F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
- F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
- F15B2211/31576—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single output member
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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
- F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
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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
- F15B2211/30—Directional control
- F15B2211/35—Directional control combined with flow control
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Check Valves (AREA)
- Fluid-Pressure Circuits (AREA)
- Operation Control Of Excavators (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
A double check valve having a floating function is disclosed, whereby a working device that is operated by a hydraulic cylinder having a double check valve (e.g., a dozer blade) can perform a floating function when the working device performs land readjustment of a work surface. The double check valve having a floating function includes a hydraulic pump, a hydraulic cylinder operating a working device, a control valve controlling a start, a stop, and a direction change of the hydraulic cylinder, and a double check valve installed to open/close flow paths between the control valve and the hydraulic cylinder, and having a pair of plungers dividedly formed to be shifted in opposite directions to each other when a signal pressure is applied thereto, and a pair of check valves being pressed to remove their check functions through a shifting of the plungers. When the control valve is shifted to a neutral state and a floating function mode is selected, a large chamber and a small chamber of the hydraulic cylinder are connected to each other by the double check valve.
Description
The cross reference of related application
The application is based on the korean patent application No.10-2006-119035 that submitted to Korea S Department of Intellectual Property on November 29th, 2006 and require its preference, introduces the full content of this application here by reference.
Technical field
The present invention relates to a kind of double check valve with float function, thus, the equipment (for example, blade) that is used for carrying out land levelling work on working surface can carry out float function.
What term " floated " functional representation is, under the state that the supply of hydraulic fluid from the oil hydraulic pump to the oil hydraulic cylinder interrupted temporarily, the equipment that is in unloaded state (at this moment, the big chamber and the cell that are used for the oil hydraulic cylinder of operation element device (for example, blade) interconnect) be operated according to the degree of being uneven of working surface or road surface.
Background technique
As shown in Figure 1, in Architectural Equipment, big chamber d1 and the cell d2 of oil hydraulic cylinder d interconnect by pipeline h.Therefore, when the equipment with equipment f mounted thereto was along driving on uneven ground and on the descending road surface, equipment f was owing to the weight of himself descends, and therefore oil hydraulic cylinder d is driven to such an extent that stretch.On the contrary, when this Architectural Equipment was on the upward slope road surface, oil hydraulic cylinder d was driven to such an extent that shrink.
In other words, even be not supplied at the hydraulic fluid of supplying with from oil hydraulic pump under the situation of oil hydraulic cylinder d of operation element device f, equipment f also repeats to be operated according to the uneven degree on ground.
Shown in Fig. 2 to 5, the Architectural Equipment with traditional double check valve comprises: oil hydraulic pump P; Oil hydraulic cylinder d, it is connected to oil hydraulic pump P, with operation blade f; Control valve a, it is installed in the stream between oil hydraulic pump P and the oil hydraulic cylinder d and is moved, with the startup of control oil hydraulic cylinder d, stop and direction changes; With double check valve k, it is installed in order to the stream between opening/closing control valve a and the oil hydraulic cylinder d, and have a pair of safety check b and the c that supports by extrusion f1 and f2, this extrusion f1 and f2 are respectively by first and second elastic components (for example, compression disc spring) e1 and e2 flexibly support, and comprise plunger h, it slidably is installed between safety check b and the c, in case thrust soil machine scraper f sinks.
As shown in Figure 3, when control valve a is held when mediating state, by the safety check b and the c that are flexibly supported by the first elastic component e1 and the second elastic component e2 and extrusion f1 and f2, double check valve k has played the safety check effect.
Specifically, safety check b blocks first stream s1 and the s3 that control valve a is connected to the cell d2 of oil hydraulic cylinder d, and safety check c blocks second stream s2 and the s4 that control valve a is connected to the big chamber d1 of oil hydraulic cylinder d.
Therefore, the hydraulic fluid of supplying with from oil hydraulic pump P is not supplied to oil hydraulic cylinder d.Equally, the hydraulic fluid of being supplied with by oil hydraulic cylinder d can not be back to hydraulic fluid tank.
Therefore, prevented that blade f from sinking.
As shown in Figure 4, when control valve a by the signal pressure that applies from the outside along when right moves, the hydraulic fluid of being supplied with by oil hydraulic pump P is supplied to the first stream s1 of double check valve k through control valve a.
Hydraulic fluid among the first stream s1 acts on the barrier film n1, and plunger h is moved along left direction, and as shown in FIG. along to the right direction extruding safety check b, eliminates check function (at this moment, the first elastic component e1 accepts compressive force).That is to say that the first stream s1 and the s3 of safety check k interconnect.
In this case, as shown in the figure, plunger h is moved, and the direction extruding safety check c along left eliminates check function (at this moment, the second elastic component e2 accepts compressive force).That is to say that the second stream s2 and the s4 of safety check k interconnect.
Therefore, the hydraulic fluid of supplying with from oil hydraulic pump P is after order is through the first stream s1 of control valve a and safety check k and s3 and be supplied to the cell d2 of oil hydraulic cylinder d.In this case, the hydraulic fluid of supplying with from the big chamber d1 of oil hydraulic cylinder d is after safety check c, the second stream s2 that order has been eliminated through its check function and s4 and control valve a and the hydraulic return case.
Therefore, oil hydraulic cylinder d is driven under the hydraulic fluid effect from oil hydraulic pump P and shrinks.
As shown in Figure 5, when control valve a by the signal pressure that applies from the outside when left direction moves, the hydraulic fluid of being supplied with by oil hydraulic pump P is supplied to the second stream s2 of double check valve k by control valve a.
Hydraulic fluid among the second stream s2 acts on the barrier film n2, and plunger h is moved along to the right direction, and as shown in the figure along left direction extruding safety check c, to eliminate check function (at this moment, the second elastic component e2 accepts compressive force).That is to say that the second stream s2 and the s4 of safety check k interconnect.
In this case, as shown in the figure, plunger h is moved, and along direction extruding safety check b to the right, thereby eliminates check function (at this moment, the first elastic component e1 accepts compressive force).That is to say that the first stream s1 and the s3 of safety check k interconnect.
Therefore, the hydraulic fluid of supplying with from oil hydraulic pump P is after order is through the second stream s2 of control valve a and safety check k and s4 and be supplied to the big chamber d1 of oil hydraulic cylinder d.In this case, the hydraulic fluid of supplying with from the cell d2 of oil hydraulic cylinder d is after safety check b, the first stream s1 that order has been eliminated through its check function and s3 and control valve a and the hydraulic return case.
Therefore, oil hydraulic cylinder d is driven under the hydraulic fluid effect of supplying with from oil hydraulic pump P and stretches.
As mentioned above, Architectural Equipment with traditional double check valve has following problem: be held at control valve a under the situation of the state of mediating, the big chamber d1 of oil hydraulic cylinder d and cell d2 can not interconnect by being installed in safety check b among the double check valve k and the check function of c.Therefore, under the situation of needs float function, can not realize float function according to operating conditions at blade f.
Summary of the invention
Therefore, in order to solve the problems referred to above that occur in the prior art, the advantage that realized of complete reservation prior art simultaneously, and make the present invention.
An object of the present invention is to provide double check valve with float function, thus, when by the land levelling on the equipment execution work surface of the oil hydraulic cylinder operation with double check valve, this equipment can be realized float function, thereby and has improved practicability.
In order to realize these purposes, according to an aspect of the present invention, provide a kind of double check valve with float function, it comprises: oil hydraulic pump; Oil hydraulic cylinder, it is connected on the described oil hydraulic pump, with the operation element device; Control valve, it is mounted to the stream between described oil hydraulic pump of opening/closing and the oil hydraulic cylinder and is moved, with the startup of controlling described oil hydraulic cylinder, stop and direction changes; And double check valve, it is installed in the stream between described control valve and the oil hydraulic cylinder, and have a pair of plunger and a pair of check valves, wherein this forms dividually to plunger, when when the outside applies signal pressure, they move along opposite directions, and this is extruded by described plunger movement safety check, to eliminate their check function; Wherein be moved to intermediateness and selected under the situation of float function pattern of equipment at described control valve, the big chamber and the cell of described oil hydraulic cylinder interconnect by described double check valve.
Described double check valve also can comprise: shell, in this shell, be formed with described control valve be connected to described oil hydraulic cylinder cell first stream and described control valve is connected to second stream of the big chamber of described oil hydraulic cylinder; The signal pressure stream, the signal pressure that is used to described plunger is moved is fed into this signal pressure stream; Extrusion, it pushes described safety check, with described first stream of opening/closing; First elastic component, it flexibly supports described extrusion, thereby will be elastically biased toward original state to them by described first stream of described check-valve obstruction; Extrusion, it pushes described safety check, with described second stream of opening/closing; With second elastic component, it flexibly supports described extrusion, thereby will be elastically biased toward original state to them by described second stream of described check-valve obstruction.
The control signal pressure of supplying with to the signal pressure stream from described oil hydraulic pump is used as and is used to signal pressure that described plunger is moved.
Description of drawings
Above-mentioned and other purposes of the present invention, characteristics and advantage will become clearer by the detailed description below in conjunction with accompanying drawing, wherein:
Fig. 1 is the view of the float function of explanation equipment;
Fig. 2 is the schematic representation with Architectural Equipment of traditional double check valve mounted thereto;
Fig. 3 is the view of expression user mode of double check valve when control valve mediates state as shown in Figure 2;
Fig. 4 is the view of expression user mode of double check valve when control valve is moved as shown in Figure 2;
Fig. 5 is the view of expression user mode of double check valve when control valve is moved as shown in Figure 2;
Fig. 6 is the sectional view that has the double check valve of float function according to an embodiment of the invention;
Fig. 7 is the view of expression user mode of double check valve when control valve is moved as shown in Figure 6;
Fig. 8 is the view of expression user mode of double check valve when control valve is moved as shown in Figure 6; With
Fig. 9 is the view of expression user mode of double check valve when control valve mediates state as shown in Figure 6.
Embodiment
Below, preferred implementation of the present invention is described with reference to the accompanying drawings.The item that defines in the specification does not have other meanings such as detailed structure and element, and they are the detail for helping the present invention of those of ordinary skills' complete understanding to provide just, and therefore the present invention is not limited to this.
To shown in Figure 9, the double check valve that has float function according to an embodiment of the invention comprises: oil hydraulic pump P as Fig. 6; Oil hydraulic cylinder d, it is connected on the oil hydraulic pump P, with the operation element device; Control valve a, it is installed in the stream between oil hydraulic pump P and the oil hydraulic cylinder d and is moved, with the startup of control oil hydraulic cylinder d, stop and direction changes; With double check valve k, it is installed among the first stream s1 and s3 and the second stream s2 and s4 between control valve a and the oil hydraulic cylinder d, and (for example have a pair of plunger h1 and h2 and pair of check valves b and c, spherical valve or poppet valve), wherein this forms dividually to plunger, when from the outside when barrier film n3 and n4 apply signal pressure, they move along opposite direction relative to each other, and this is extruded by moving of plunger h1 and h2 safety check, to eliminate their check function.
Move to intermediateness and selected under the situation of float function pattern of equipment (for example, blade) at control valve a, big chamber d1 and the cell d2 of oil hydraulic cylinder d interconnect by double check valve k.
Double check valve k also can comprise: shell m is formed with in this shell control valve a is connected to the first stream s1 and the s3 of cell d2 of oil hydraulic cylinder d and second stream s2 and the s4 that control valve a is connected to the big chamber d1 of oil hydraulic cylinder d; Signal pressure stream j, the signal pressure that is used to plunger is moved is fed into this signal pressure stream from control pump Pp; Extrusion f1, its extruding safety check b is with opening/closing first stream s1 and the s3; The first elastic component e1, it flexibly supports extrusion f1, thus first stream s1 that will be blocked by safety check b and s3 are elastically biased toward the original state to them; Extrusion f2, its extruding safety check c is with opening/closing second stream s2 and the s4; With the second elastic component f2, it flexibly supports extrusion f2, thereby second stream s2 that will be blocked by safety check c and s4 are elastically biased toward the original state to them.
Be supplied to the control signal pressure of signal pressure stream j to be used as to be used to the signal pressure that plunger h1 and h2 are moved by oil hydraulic pump Pp.
Double check valve k can drive by the hydraulic fluid of supplying with from oil hydraulic pump P or from the air pressure that the source of compressed air (not shown) applies.
Below, the operation according to the double check valve with float function of the embodiment of the invention is described with reference to the accompanying drawings.
As shown in Figure 6, when control valve a is held when mediating state, by the safety check b and the c that are flexibly supported by the first elastic component e1 and the second elastic component e2 and extrusion f1 and f2, double check valve k has played the effect of safety check.In this case, a pair of plunger h1 that forms dividually keeps closely contacting mutually with h2.
Specifically, safety check b blocks first stream s1 and the s3 that control valve a is connected to the cell d2 of oil hydraulic cylinder d, and safety check c blocks second stream s2 and the s4 that control valve a is connected to the big chamber d1 of oil hydraulic cylinder d.
Therefore, the hydraulic fluid of being supplied with by oil hydraulic pump P can not be supplied to oil hydraulic cylinder d.And, can the hydraulic return case by the hydraulic fluid that oil hydraulic cylinder d supplies with.
Therefore, prevented that blade f from sinking.
As shown in Figure 7, when control valve a by the signal pressure that applies from the outside when to the right direction moves, the hydraulic fluid of being supplied with by oil hydraulic pump P is supplied to the first stream s1 of double check valve k through control valve a.In this case, being retained a pair of plunger h1 of mutually closely contact and h2 moves slidably and moves along direction left.
Hydraulic fluid in the second stream s1 acts on the barrier film n1, makes plunger h1 and h2 as shown in the figure when left direction moves, and safety check b is extruded, and eliminating check function, and the first stream s1 and s3 interconnect.Therefore, the hydraulic fluid of being supplied with by oil hydraulic pump P is after order is through control valve a and the first stream s1 and s3 and be supplied to the cell d2 of oil hydraulic cylinder d.
Simultaneously, because the moving of plunger h1 and h2, safety check c is extruded, and eliminating check function, and the second stream s2 and s4 interconnect.Therefore, the hydraulic fluid of being supplied with by the big chamber d1 of oil hydraulic cylinder d is after order is through the second stream s2 and s4 and control valve a and the hydraulic return case.
As shown in Figure 8, when control valve a by the signal pressure that applies from the outside when left direction moves, the hydraulic fluid of being supplied with by oil hydraulic pump P is supplied to the second stream s2 of double check valve k through control valve a.In this case, mutually closely the plunger h1 of contact and h2 move slidably and move along direction to the right.
Hydraulic fluid in the second stream s2 acts on the barrier film n2, makes plunger h1 and h2 as shown in FIG. when to the right direction moves, and safety check c is extruded, and eliminating check function, and the second stream s2 and s4 interconnect.Therefore, the hydraulic fluid of being supplied with by oil hydraulic pump P is after order is through control valve a and the second stream s2 and s4 and be supplied to the big chamber d1 of oil hydraulic cylinder d.
Simultaneously, because the moving of plunger h1 and h2, safety check b is extruded, and eliminating check function, and the second stream s2 and s4 interconnect.Therefore, the hydraulic fluid of supplying with from the cell d2 of oil hydraulic cylinder d is after order is through the first stream s1 and s3 and control valve a and the hydraulic return case.
Fig. 9 is the view of expression user mode of double check valve when control valve a moves to intermediateness and selected the float function of blade f.
When the control signal pressure from oil hydraulic pump Pp was applied to the signal pressure stream j that is formed among the safety check k, plunger h1 of Xing Chenging and h2 moved along opposite directions simultaneously dividually.
Specifically, when plunger h1 as shown in FIG. by the control signal pressure on the barrier film n3 that acts on plunger h1 when to the right direction moves, safety check b is extruded along direction to the right, to eliminate its check function (at this moment, the first elastic component e1 accepts compressive force).That is to say that the first stream s1 and the s3 of safety check k interconnect.
Simultaneously, when plunger h2 as shown in FIG. by the control signal pressure on the barrier film n4 that acts on plunger h2 when left direction moves, safety check c is extruded along direction left, to eliminate its check function (at this moment, the second elastic component e2 accepts compressive force).That is to say that the second stream s2 and the s4 of safety check k interconnect.
Therefore, the cell d2 of control valve a and oil hydraulic cylinder d interconnects by the first stream s1 and s3, and the big chamber d1 of control valve a and oil hydraulic cylinder d interconnects by the second stream s2 and s4.
Therefore, the cell d2 of oil hydraulic cylinder d and big chamber d1 are connected with each other.That is to say, after order is through the second stream s2 and s4, control valve a and the first stream s1 and s3 and be passed under the situation of cell d2 (as shown by arrows) of oil hydraulic cylinder d, oil hydraulic cylinder d is driven and is shunk at hydraulic fluid that the big chamber d1 from the oil hydraulic cylinder d that is in unloaded state supplies with.
On the contrary, after order is through the first stream s1 and s3, control valve a and the second stream s2 and s4 and be transmitted under the situation of big chamber d1 (as shown by arrows) of oil hydraulic cylinder d, oil hydraulic cylinder d is driven and is stretched at hydraulic fluid that the cell d2 from the oil hydraulic cylinder d that is in unloaded state supplies with.
As a result, under the situation that the equipment with blade f mounted thereto travels along ground g, the moving of oil hydraulic cylinder d that is in unloaded state will be regulated automatically according to the uneven degree of ground g, and therefore can carry out float function.
As mentioned above, the double check valve that has according to the float function of the embodiment of the invention has the following advantages.
Adjust work carrying out ground by the equipment of oil hydraulic cylinder operation with double check valve, so that under the smooth situation in ground, it carries out float function, thus the practicability and the reliability of raising equipment.
Though described the preferred embodiments of the present invention for illustrative purposes, those skilled in the art should understand: under the situation that does not deviate from the disclosed scope and spirit of the present invention of claims, can carry out various modifications, interpolation and replacement.
Claims (4)
1. double check valve with float function, it comprises:
Oil hydraulic pump;
Oil hydraulic cylinder, it is connected on the described oil hydraulic pump, in order to the operation element device;
Control valve, it is installed in the stream between described oil hydraulic pump and the oil hydraulic cylinder, and is moved, in order to the startup of controlling described oil hydraulic cylinder, stop and direction changes; With
Double check valve, it is installed in the stream between described control valve and the oil hydraulic cylinder, and have a pair of plunger and a pair of check valves, wherein this forms dividually to plunger, when when the outside applies signal pressure, they move along opposite directions, and this is extruded by right the moving of described plunger safety check, to eliminate their check function;
Wherein be moved to intermediateness and selected under the situation of float function pattern of equipment at described control valve, the big chamber and the cell of described oil hydraulic cylinder interconnect by described double check valve.
2. double check valve according to claim 1, wherein said double check valve also comprises:
Shell, in this shell, be formed with described control valve be connected to described oil hydraulic cylinder cell first stream and described control valve is connected to second stream of the big chamber of described oil hydraulic cylinder;
The signal pressure stream, the signal pressure that is used to described plunger is moved is fed into this signal pressure stream;
Extrusion, it pushes described safety check, with described first stream of opening/closing;
First elastic component, it flexibly supports described extrusion, is elastically biased toward original state to them so that will be by described first stream of described check-valve obstruction;
Extrusion, it pushes described safety check, with described second stream of opening/closing; With
Second elastic component, it flexibly supports described extrusion, is elastically biased toward original state to them so that will be by described second stream of described check-valve obstruction.
3. double check valve according to claim 1, wherein, the control signal pressure that supplies to described signal pressure stream from described oil hydraulic pump is used as and is used to signal pressure that described plunger is moved.
4. double check valve according to claim 1 and 2, wherein spherical valve or poppet valve are as described safety check.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR1020060119035A KR100849500B1 (en) | 2006-11-29 | 2006-11-29 | double check valve with floating function |
| KR1020060119035 | 2006-11-29 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101191506A true CN101191506A (en) | 2008-06-04 |
Family
ID=39167691
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2007101371672A Pending CN101191506A (en) | 2006-11-29 | 2007-07-30 | Double check valve having floating function |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20080121101A1 (en) |
| EP (1) | EP1927759A1 (en) |
| JP (1) | JP2008138870A (en) |
| KR (1) | KR100849500B1 (en) |
| CN (1) | CN101191506A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103620232A (en) * | 2011-06-23 | 2014-03-05 | 株式会社尼利可 | Electro-hydraulic hybrid drive device |
| CN108884844A (en) * | 2016-03-31 | 2018-11-23 | 罗尔工业公司 | The bivalve safe unit of hydraulic cylinder |
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| JP5283862B2 (en) * | 2007-06-05 | 2013-09-04 | 三陽機器株式会社 | Hydraulic control device |
| KR100915206B1 (en) * | 2007-09-20 | 2009-09-02 | 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 | double check valve with floating function |
| FR2933471B1 (en) * | 2008-07-03 | 2013-02-15 | Vianney Rabhi | BALANCED ELECTRO-HYDRAULIC VALVE FOR A VARIABLE COMPRESSION RATE MOTOR HYDRAULIC CONTROL UNIT |
| KR100985814B1 (en) | 2010-02-18 | 2010-10-08 | 파카코리아 주식회사 | That cavitation prevention equipment is equipped double pilot check valve |
| CN102859080B (en) * | 2010-05-18 | 2015-05-06 | 沃尔沃建造设备有限公司 | Double check valve for construction equipment |
| KR101294673B1 (en) * | 2010-08-16 | 2013-08-09 | 국방과학연구소 | Automatic shut valve for rapid transfer of flow in hydraulic cirrcuit |
| EP2696080B1 (en) * | 2012-08-09 | 2016-12-14 | HAWE Hydraulik SE | Commande électro-hydraulique |
| KR101741702B1 (en) * | 2012-12-20 | 2017-05-30 | 볼보 컨스트럭션 이큅먼트 에이비 | Construction machine with floating function |
| CA2905312C (en) | 2014-11-04 | 2021-03-30 | Cnh Industrial Canada, Ltd. | Hydraulic system for an air cart |
| KR101570390B1 (en) | 2015-05-12 | 2015-11-19 | 주식회사 에프피씨 | valve unit for automatic volumetric flow compensation |
| CN109996924B (en) * | 2017-09-29 | 2021-04-06 | 株式会社日立建机Tierra | Construction machine |
| KR101835691B1 (en) * | 2017-11-06 | 2018-04-19 | 주식회사 에프피씨 | Auxiliary valve for hydraulic operation |
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| US3274902A (en) * | 1965-10-22 | 1966-09-27 | Deere & Co | Hydraulic control system |
| US3908515A (en) * | 1973-09-10 | 1975-09-30 | Caterpillar Tractor Co | Hydraulic circuit with selectively actuatable float control |
| US4166506A (en) | 1975-06-30 | 1979-09-04 | Kabushiki Kaisha Komatsu Seisakusho | Controlling apparatus for bulldozer blade |
| WO1981000600A1 (en) * | 1979-08-30 | 1981-03-05 | Caterpillar Tractor Co | Lock valve with variable length piston and hydraulic system for a work implement using the same |
| US4506700A (en) | 1983-10-07 | 1985-03-26 | Deere & Company | Poppet valve with float function |
| JPH06128984A (en) * | 1992-10-15 | 1994-05-10 | Kubota Corp | Dozer device for service car |
| JPH10183674A (en) | 1996-12-25 | 1998-07-14 | Toyo Umpanki Co Ltd | Lifting device of earth-moving tool |
| DE19919014C2 (en) | 1999-04-27 | 2001-03-01 | Danfoss Fluid Power As Nordbor | Hydraulic valve with a locking and a floating function |
| US6477937B1 (en) * | 1999-12-13 | 2002-11-12 | Aladdin Engineering & Manufacturing | Valve arrangement including release valve |
-
2006
- 2006-11-29 KR KR1020060119035A patent/KR100849500B1/en active IP Right Grant
-
2007
- 2007-07-06 US US11/825,637 patent/US20080121101A1/en not_active Abandoned
- 2007-07-27 EP EP07014738A patent/EP1927759A1/en not_active Withdrawn
- 2007-07-30 CN CNA2007101371672A patent/CN101191506A/en active Pending
- 2007-11-01 JP JP2007284674A patent/JP2008138870A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103620232A (en) * | 2011-06-23 | 2014-03-05 | 株式会社尼利可 | Electro-hydraulic hybrid drive device |
| CN103620232B (en) * | 2011-06-23 | 2015-11-25 | 株式会社尼利可 | Liquid electricity hybrid drive |
| CN108884844A (en) * | 2016-03-31 | 2018-11-23 | 罗尔工业公司 | The bivalve safe unit of hydraulic cylinder |
| CN108884844B (en) * | 2016-03-31 | 2020-06-16 | 罗尔工业公司 | Double-valve safety unit of hydraulic cylinder |
Also Published As
| Publication number | Publication date |
|---|---|
| US20080121101A1 (en) | 2008-05-29 |
| EP1927759A1 (en) | 2008-06-04 |
| KR100849500B1 (en) | 2008-07-31 |
| JP2008138870A (en) | 2008-06-19 |
| KR20080048711A (en) | 2008-06-03 |
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Application publication date: 20080604 |