CN107725840B - Bidirectional control proportional flow stop valve - Google Patents
Bidirectional control proportional flow stop valve Download PDFInfo
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- CN107725840B CN107725840B CN201711088663.3A CN201711088663A CN107725840B CN 107725840 B CN107725840 B CN 107725840B CN 201711088663 A CN201711088663 A CN 201711088663A CN 107725840 B CN107725840 B CN 107725840B
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- Prior art keywords
- damping hole
- valve core
- pilot valve
- oil port
- sleeve
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K15/00—Check valves
- F16K15/02—Check valves with guided rigid valve members
- F16K15/06—Check valves with guided rigid valve members with guided stems
- F16K15/063—Check valves with guided rigid valve members with guided stems the valve being loaded by a spring
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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
- F15B13/027—Check valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K15/00—Check valves
- F16K15/18—Check valves with actuating mechanism; Combined check valves and actuated valves
- F16K15/182—Check valves with actuating mechanism; Combined check valves and actuated valves with actuating mechanism
- F16K15/1826—Check valves which can be actuated by a pilot valve
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
- F16K31/0644—One-way valve
- F16K31/0655—Lift valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
- F16K31/36—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor
- F16K31/40—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor with electrically-actuated member in the discharge of the motor
- F16K31/406—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor with electrically-actuated member in the discharge of the motor acting on a piston
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Magnetically Actuated Valves (AREA)
Abstract
The invention provides a bidirectional control proportional flow stop valve, which is characterized by comprising the following components: the proportional electromagnetic valve comprises a proportional electromagnet, a screw sleeve, an armature iron and a valve sleeve, wherein one end of the screw sleeve is connected with the proportional electromagnet, the armature iron is movably arranged in the screw sleeve, one end of the valve sleeve is fixedly connected with the other end of the screw sleeve, and an oil port A and an oil port B are formed in the other end of the valve sleeve; the main valve core is connected in the valve sleeve, a first damping hole communicated with the oil port B and a second damping hole communicated with the oil port A are formed in the main valve core, and the diameter of the first damping hole is larger than that of the second damping hole; the pilot valve sleeve is movably sleeved in the main valve core, and a pilot chamber and a third damping hole are arranged on the pilot valve sleeve; and one end of the pilot valve core is fixedly connected to the other end of the armature, the other end of the pilot valve core penetrates through the control cavity, the pilot chamber and the second damping hole, a conical head section matched with the second damping hole is arranged at the other end of the pilot valve core, and the conical head section can block the second damping hole. The proportional flow stop valve has the advantages of simple structure, low cost and capability of realizing bidirectional control.
Description
Technical Field
The invention relates to the technical field of valves, in particular to a bidirectional control proportional flow stop valve.
Background
In recent years, proportional flow cut-off valves have been increasingly used in lifting equipment such as truck-mounted cranes, overhead working vehicles, tractor rotary ploughs, electric forklifts, and the like. When the equipment stops, the proportional flow stop valve plays a role in maintaining pressure to prevent the hydraulic cylinder from sliding downwards; when the equipment needs to descend, the proportional flow stop valve controls the opening size according to the size of the input voltage signal, adjusts the flow output by the hydraulic cylinder, and further controls the descending speed of the lifting equipment. The proportional flow stop valve that exists in the existing market can only realize unilateral proportional flow control, that is to say that when hydraulic oil flows into hydraulic fluid port A from hydraulic fluid port B of proportional flow stop valve, proportional flow control can be realized, that hydraulic oil only plays the check valve effect when flowing into hydraulic fluid port B from hydraulic fluid port A, can not accomplish proportional flow control. For example, patent publication No. CN 105298967a entitled "a high horsepower tractor hoist valve assembly" provides a hydraulic valve assembly for controlling a tractor hoist in which 2 proportional flow shut-off valves are used to control the raising and lowering speed adjustments of the hoist, respectively. Because the price of the proportional valve is high, the adoption of 2 proportional flow stop valves inevitably causes cost increase, and the wide application of the proportional flow stop valves to some lower-price main machines is limited.
Disclosure of Invention
In view of some or all of the above technical problems in the prior art, the present invention provides a bidirectional controlled proportional flow stop valve, which has a simple structure and low cost and can realize bidirectional control.
In order to achieve the above object, the present invention provides a bidirectional control proportional flow cut-off valve having the following structure, including:
a proportional electromagnet is arranged on the upper portion of the shell,
one end of the screw sleeve is connected with the proportional electromagnet;
the armature is movably arranged in the screw sleeve, and one end of the armature is abutted against the proportional electromagnet through an elastic piece;
one end of the valve sleeve is fixedly connected to the other end of the screw sleeve, and an oil port A and an oil port B are formed in the other end of the valve sleeve;
the main valve core is connected in the valve sleeve, a first damping hole communicated with the oil port B and a second damping hole communicated with the oil port A are formed in the main valve core, and the diameter of the first damping hole is larger than that of the second damping hole;
the pilot valve sleeve is movably sleeved in the main cavity of the main valve core, one end, close to the oil port A, of the pilot valve sleeve is provided with a pilot cavity opening towards the oil port A and a third damping hole communicated with the pilot cavity, and the third damping hole can be communicated with the first damping hole; and
one end of the pilot valve core is fixedly connected to the other end of the armature, the other end of the pilot valve core penetrates through the control cavity, the pilot chamber and the second damping hole, a conical head section matched with the second damping hole is arranged at the other end of the pilot valve core, and the conical head section can block the second damping hole;
when the pilot valve core moves to drive the pilot valve sleeve to move, the opening and closing of the first damping hole, the second damping hole and the main valve core and the opening size are controlled by controlling the voltage of the proportional electromagnet, so that the bidirectional throttling control is formed when the oil is fed to the oil port A or the oil port B.
In the invention, unlike the prior art in which a plurality of proportional one-way flow valves are respectively controlled, the opening, closing and opening sizes of the first damping hole, the second damping hole and the main valve element can be controlled by controlling the voltage of the proportional electromagnet through designing the internal structure of the proportional flow stop valve, so that the bidirectional throttling control during oil inlet of the oil port A or the oil port B can be realized through one proportional flow stop valve, and the proportional one-way flow stop valve has a simpler structure and lower cost.
In one embodiment, the control cavity is a cavity formed by the lower end face of the armature, the middle part of the threaded sleeve, the upper part of the valve sleeve, the upper end of the main valve core, the pilot valve sleeve and the pilot valve core and positioned at the upper end of the main valve core, and the control cavity is communicated with the pilot cavity. A control cavity with relatively large volume is formed, and multistage proportional control is convenient to carry out.
In one embodiment, when the pilot valve sleeve moves towards the proportional electromagnet along with the pilot valve core, the first damping hole moves from a throttling position communicated with the third damping hole to a closed position and then to a throttling position. When the first damping hole and the third damping hole are staggered, the pilot valve sleeve shields the first damping hole, oil in the first damping hole cannot enter the pilot cavity, and the first damping hole is located at a closed position.
In one embodiment, the second orifice moves from a closed position, blocked by the pilot valve element, to a throttled state when the pilot valve element follows the armature towards the proportional solenoid.
In one embodiment, an annular groove for connection is formed in the middle of the pilot valve core, and the pilot valve sleeve is fixedly connected with the pilot valve core through a connecting piece and the annular groove. The connecting piece connects the pilot valve sleeve and the pilot valve core, so that when the pilot valve core moves upwards along with the armature, the pilot valve sleeve also moves upwards along with the pilot valve core synchronously.
In one embodiment, one end of the pilot valve core, which is connected with the armature, is of a T-shaped structure, one end of the armature is provided with a first T-shaped hole which is matched with the T-shaped structure of the pilot valve core, the other end of the armature is provided with a second T-shaped hole, one end of the elastic piece is installed in a large hole of the second T-shaped hole, and the first T-shaped hole is communicated with the second T-shaped hole. The structure of the first T-shaped hole and the second T-shaped hole not only ensures the stable function of the elastic part, but also ensures the synchronism of the motion of the pilot valve core and the armature.
In one embodiment, when oil enters the oil port B, a voltage is applied to the proportional electromagnet, the armature overcomes the acting force of the elastic piece to drive the pilot valve core to move upwards, the pilot valve sleeve moves upwards to shield the first damping hole, the second damping hole is opened, the pressure of the control cavity is reduced, and the pressure difference between the oil port B and the control cavity acts on the main valve core;
increasing the voltage on the proportional electromagnet, increasing the pressure difference between the oil port B and the control cavity, opening the main valve core, and moving the oil liquid of the oil port B to the oil port A through the main valve core;
the voltage on the proportional electromagnet is further increased, the flow area between the pilot valve core and the second damping hole is maximized, the first damping hole is completely closed, and the main valve core is completely opened.
When the oil is fed from the oil port B, the throttling control of the oil from the oil port B to the oil port A is realized.
In one embodiment, when oil enters the oil port A, a voltage is firstly applied to the proportional electromagnet, so that the pilot valve sleeve is positioned at a position which completely shields the first damping hole, and the second damping hole is completely opened;
increasing the voltage of the proportional electromagnet, gradually opening the first damping hole, gradually increasing the flow area of the first damping hole to be larger than that of the second damping hole, and gradually opening the main valve core under the action of the pressure difference between the oil port A and the control cavity;
the voltage of the proportional electromagnet is further increased, and the main valve core reaches the maximum opening.
It can be understood that when the oil is fed from the oil port A, if the proportional electromagnet voltage is not applied, the oil is equivalent to a common one-way valve. In order to realize the proportional control from the oil port A to the oil port B, sufficient voltage is firstly given to the proportional electromagnet to enable the pilot valve sleeve to be located at a position which completely shields the first damping hole, and then oil is fed from the oil port A.
In a preferred embodiment, the valve sleeve is in threaded sealing connection with the other end of the screw sleeve, and a bevel is arranged at the connection position of the lower end of the main valve core and the valve sleeve. In order to realize better sealing connection, the inclined surface structure can realize pressure maintaining before the main valve core is opened.
Compared with the prior art, the invention has the following advantages:
1) the invention can realize the bidirectional control from the oil port A to the oil port B and from the oil port B to the oil port A through a proportional one-way valve; compared with the prior art that a plurality of proportional valves are adopted, the cost is greatly reduced, the difficulty in installing the plurality of valves is reduced, and the occupied area is small;
2) compared with the existing bidirectional control valve, the bidirectional control valve has fewer parts, simpler structure and more reliable use; the manufacturing process difficulty and the manufacturing cost are also reduced.
Drawings
Preferred embodiments of the present invention will be described in detail below with reference to the attached drawing figures, wherein:
FIG. 1 is a schematic diagram of the construction of one embodiment of a bi-directional controlled proportional flow shut-off valve of the present invention;
FIG. 2 is a schematic view of the embodiment of FIG. 1 in one of its positions at oil port B;
FIG. 3 is a schematic view of the latter position of FIG. 2;
FIG. 4 is a schematic view of the embodiment of FIG. 1 in one of its positions at oil port A;
FIG. 5 is a schematic view of the latter position of FIG. 4;
fig. 6 is a schematic diagram of a hydraulic system employing the bi-directionally controlled proportional flow shut-off valve of the present invention.
In the drawings, like parts are provided with like reference numerals. The figures are not drawn to scale.
Detailed Description
In order to make the technical solutions and advantages of the present invention more apparent, exemplary embodiments of the present invention are described in further detail below with reference to the accompanying drawings. It is clear that the described embodiments are only a part of the embodiments of the invention, and not an exhaustive list of all embodiments. And the embodiments and features of the embodiments may be combined with each other without conflict.
The inventor notices in the invention process that the existing proportional flow stop valve can only realize unidirectional proportional flow control, and the application range of the proportional flow stop valve is limited.
In view of the above disadvantages, the embodiment of the present invention provides a bidirectional controlled proportional flow shutoff valve, which will be described below.
FIG. 1 shows one embodiment of the bi-directionally controlled proportional flow shut-off valve of the present invention. In this embodiment, the bidirectional control proportional flow shutoff valve of the present invention mainly includes: the proportional electromagnet comprises a proportional electromagnet 1, a threaded sleeve 2, an armature 7, a main valve core 4, a pilot valve sleeve 5 and a pilot valve core 6. Wherein, the one end and the proportion electro-magnet 1 fixed connection of swivel nut 2, the other end of swivel nut 2 passes through threaded connection valve barrel 3, and valve barrel 3 keeps away from one of swivel nut 2 and is equipped with hydraulic fluid port A and hydraulic fluid port B. The main valve core 4 is connected in the valve sleeve 3, a first damping hole 8 communicated with the oil port B and a second damping hole 9 communicated with the oil port A are formed in the main valve core, and the diameter of the first damping hole 8 is larger than that of the second damping hole 9. The pilot valve sleeve 5 is movably sleeved in the main cavity of the main valve core 6, and a pilot cavity and a third damping hole 12 communicated with the pilot cavity are arranged in the pilot valve sleeve 5. One end of the pilot valve core 6 is fixedly connected to the armature 7, and the other end of the pilot valve core 6 penetrates through the control cavity 10, the pilot cavity and the second damping hole 9.
In one embodiment, the pilot valve core 6 is provided with a conical head section 62 corresponding to the second damping hole 9, so it can be understood that when the pilot valve core 6 is not lifted, the conical head section 62 of the pilot valve core leans against the second damping hole 9, and the second damping hole 9 is in a closed state, as shown in fig. 1.
In one embodiment of the present invention, when the pilot valve element 6 moves toward the proportional electromagnet 1 following the armature 7, the second orifice 9 moves from the closed position, which is blocked by the conical head section 62 at the lower end of the pilot valve element 6, to the throttle state.
In one embodiment, as shown in fig. 1 to 5, the control chamber 10 is a chamber formed by the lower end surface of the armature 7, the middle portion of the screw sleeve 2, the upper portion of the valve sleeve 3, the upper end of the main spool 4, the pilot valve sleeve 5, and the upper end of the pilot spool 6, which is located at the upper end of the main spool 4. The control chamber 10 communicates with the pilot chamber. Here, a control chamber 10 having a relatively large volume is formed to facilitate multi-stage proportional control. It will be appreciated that the control chamber 10 shown in the embodiment is one of these, and that the size and shape of the control chamber may in fact be varied in a number of ways, for example by varying the shape of the upper end of the valve sleeve 3 to vary the shape and size of the control chamber, etc.
In one embodiment, when the pilot valve sleeve 5 moves in the direction of the proportional electromagnet 1 (upward in fig. 3) following the pilot valve spool 6, the first orifice 8 moves from the orifice position in communication with the third orifice 12 to the closed position in which they are not in communication, and the first orifice 8 is blocked by the pilot valve sleeve 5. Here, when the first damping hole 8 and the third damping hole 12 are staggered, the pilot valve sleeve 5 shields the first damping hole 8, oil in the first damping hole 8 cannot enter the pilot chamber, the first damping hole 8 is in the closed position, the pilot valve sleeve 5 continues to move upwards, and then the first damping hole 8 is slowly opened again.
In a preferred embodiment, the middle part of the pilot valve core 6 is provided with an annular groove 61 for connection, and the pilot valve sleeve 5 is fixedly connected with the pilot valve core 6 through a connecting piece and the annular groove 61. That is, the pilot valve sleeve 5 and the pilot valve core 6 are connected by a connecting member, and when the pilot valve core 6 moves upward along with the armature 7, the pilot valve sleeve 5 also moves upward along with the pilot valve core 6 in synchronization.
In a preferred embodiment, one end of the pilot valve core 6 connected with the armature 7 is in a T-shaped structure, one end (upper end in fig. 1) of the armature 7 is provided with a first T-shaped hole matched with the T-shaped structure of the pilot valve core 6, the other end (lower end in fig. 1) of the armature 7 is provided with a second T-shaped hole, one end of the elastic element 11 is installed in a large hole of the second T-shaped hole, and the first T-shaped hole is communicated with the second T-shaped hole.
In one embodiment, when oil enters the oil port B, a voltage is applied to the proportional electromagnet 1, the armature 7 overcomes the acting force of the elastic member 11, the pilot valve core 6 is driven to move upwards, the pilot valve sleeve 5 moves upwards to shield the first damping hole 8, the second damping hole 9 is opened, the pressure of the control cavity 10 is reduced, and the pressure difference between the oil port B and the control cavity 10 acts on the main valve core 4. The voltage on the proportional electromagnet 1 is increased, the pressure difference between the oil port B and the control cavity 10 is increased, the main valve core 4 is opened, and the oil liquid of the oil port B moves to the oil port A through the main valve core 4. Further increasing the voltage on the proportional electromagnet 1, the flow area between the pilot valve element 6 and the second damping hole 9 reaches the maximum, and the main valve element 4 is completely opened.
In one embodiment, when oil enters the oil port a, a voltage is first applied to the proportional electromagnet 1, so that the pilot valve sleeve 5 is in a position (shown in fig. 4) that completely blocks the first damping hole 8. The voltage of the proportional electromagnet 1 is increased, the first damping hole 8 is gradually opened, and when the overflowing area of the first damping hole is larger than that of the second damping hole, the main valve element 4 is gradually opened under the action of the pressure difference between the oil port A and the control cavity 10. The voltage of the proportional electromagnet 1 is further increased, and the main valve element 4 reaches the maximum opening.
In the embodiment of the invention, when the pilot valve core 6 drives the pilot valve sleeve 5 to move upwards, the opening, closing and opening sizes of the first damping hole 8, the second damping hole 9 and the main valve core 4 can be controlled by controlling the voltage of the proportional electromagnet 1, so that the bidirectional throttling control is formed when the oil enters the oil port a or the oil port B. The specific operation is described in detail below.
If oil enters the oil port B, when a certain voltage is given to the proportional electromagnet 1, the proportional electromagnet 1 generates a certain suction force, the armature 7 overcomes the action of the spring 11 to generate a certain displacement under the action of the suction force, the pilot valve core 6 is driven to separate from the second damping hole 9, and the pilot valve sleeve 5 moves upwards to slowly cover the first damping hole 8 (as shown in fig. 2). At this time, the pressure in the control chamber 10 will drop, and the pressure in the oil port B and the pressure in the control chamber 10 form a pressure difference, which acts on the main valve element 4 (since the main valve element 4 is also in a step shape, an area difference is generated), but the resultant force is not enough to push the main valve element 4 to rise.
Continuing to increase the voltage on the proportional electromagnet 10, the first orifice 8 is further covered, the second orifice 9 is further opened, the pressure of port B and the pressure difference in the control chamber 10 increase, the main valve element 4 starts moving upward, and the oil of port B flows to port a (as shown in fig. 3).
Further, the voltage of the electromagnet 1 with the given proportion is increased, the pilot valve sleeve 5 completely covers the first damping hole 8, the flow area between the second damping hole 9 and the pilot valve core 6 is maximized, and at this time, the main valve core 4 is completely opened.
If oil enters the oil port a, a sufficient initial voltage needs to be given to the proportional electromagnet 1, so that the pilot valve sleeve 5 is in the initial control position (shown in fig. 4) where it is completely covered, and at this time, the maximum flow area of the second damping hole is reached. On the basis of initial voltage, a voltage signal is gradually increased, the first damping hole 8 is gradually opened through the conical surface structure at the lower part of the pilot valve sleeve 5, and the flow area of the second damping hole cannot be changed in the gradual rising process of the pilot valve core 6. That is, the area of the first orifice 8 gradually increases and is gradually larger than the flow area of the second orifice, so that the pressure of the control chamber 10 and the pressure of the port B are gradually close to each other, the pressure difference between the pressure of the control chamber 10 and the pressure of the port a is gradually larger, as shown in fig. 5, so that the main valve element 4 is gradually opened under the effect of the resultant force, and the flow from the port a to the port B gradually increases.
According to the above, when the oil is fed from the oil port A, the proportional electromagnet 1 is given the maximum voltage, the main valve core 4 can reach the maximum opening, and the flow from the oil port A to the oil port B can reach the maximum flow. If the proportional electromagnet 1 is not energized, the pilot valve core 6 is in a position (as shown in fig. 1) for sealing the second damping hole 9, and the flow from the oil port a to the oil port B is equivalent to a check valve, and the maximum flow can be achieved. Therefore, the maximum flow control can be realized by two modes of giving the oil from the oil port A to the maximum voltage of the proportional electromagnet 1 and not giving the voltage to the one-way valve.
To better illustrate the function of the two-way controlled proportional flow shut-off valve of the present invention, fig. 6 shows a schematic diagram of a hydraulic system employing the two-way controlled proportional flow shut-off valve 15 of the present invention. In the figure, the oil from the hydraulic pump 13 passes through the two-position three-way electromagnetic directional valve 14, and if the left side of the two-position three-way electromagnetic directional valve 14 is electrified, the oil enters the bidirectional control proportional flow stop valve 15 of the present invention after being reversed, and under the condition that sufficient initial voltage is provided for the proportional electromagnet 1, the oil controllably flows to the oil port B through the oil port a and then enters the hydraulic cylinder 16 through a pipeline.
If the two-position three-way electromagnetic directional valve 14 shown in fig. 6 does not work at the right position electrically, the oil in the hydraulic cylinder 16 flows through the oil port B, and under the condition that the proportional electromagnet 1 is supplied with the corresponding voltage, the oil flows from the oil port B to the oil port a in a proportional control manner, and then returns to the oil tank through the electromagnetic directional valve 14. In this case, if the lowering is stopped halfway, the proportional electromagnet 1 is deenergized, and the bidirectional control proportional flow cut-off valve 15 of the present invention can perform the function of pressure maintaining.
In the invention, unlike the prior art in which a plurality of proportional check valves are arranged to control respectively, the opening, closing and opening sizes of the first damping hole 8, the second damping hole 9 and the main valve element 4 can be controlled by controlling the voltage of the proportional electromagnet 1 by designing the internal structure of the proportional check valves, so that the bidirectional throttling control during oil feeding of the oil port a or the oil port B can be realized by one proportional check valve, and the structure is simpler and the cost is lower.
The core technology of the present invention is as follows: the pilot valve sleeve 5 and the first damping hole 8 form a first variable throttling, the pilot valve core 6 and the second damping hole 9 form a second variable throttling, when hydraulic oil flows into the oil port A from the oil port B, the area of the first variable throttling is controlled to be smaller than that of the second variable throttling, the main valve core 4 is slowly opened, the smaller the area of the first variable throttling is, the larger the area of the second variable throttling is, and the larger the main valve core 4 is opened. When hydraulic oil flows into the oil port B from the oil port A, the second variable throttling reaches the maximum overflowing area, the first overflowing area is the minimum, then the area of the first variable throttling is gradually increased, when the overflowing area of the first variable throttling is larger than the overflowing area of the second damping hole, the main valve element 4 is slowly opened, the area of the first variable throttling continues to be increased, and the opening of the main valve element 4 is larger.
While preferred embodiments of the present invention have been described, additional variations and modifications in those embodiments may occur to those skilled in the art once they learn of the basic inventive concepts. Therefore, the appended claims are intended to be construed to include preferred embodiments and all such changes and/or modifications as fall within the scope of the invention, and all such changes and/or modifications as are made to the embodiments of the present invention are intended to be covered by the scope of the invention.
Claims (4)
1. A bidirectionally controlled proportional flow stop valve, comprising:
a proportional electromagnet is arranged on the upper portion of the shell,
one end of the screw sleeve is connected with the proportional electromagnet;
the armature is movably arranged in the screw sleeve, and one end of the armature is abutted against the proportional electromagnet through an elastic piece;
one end of the valve sleeve is fixedly connected to the other end of the screw sleeve, and an oil port A and an oil port B are formed in the other end of the valve sleeve;
the main valve core is connected in the valve sleeve, a first damping hole communicated with the oil port B and a second damping hole communicated with the oil port A are formed in the main valve core, and the diameter of the first damping hole is larger than that of the second damping hole;
the pilot valve sleeve is movably sleeved in the main valve core, one end, close to the oil port A, of the pilot valve sleeve is provided with a pilot chamber opening towards the oil port A and a third damping hole communicated with the pilot chamber, and the third damping hole can be communicated with the first damping hole; and
one end of the pilot valve core is fixedly connected to the other end of the armature, the other end of the pilot valve core penetrates through the control cavity and the pilot chamber, a conical head section matched with the second damping hole is arranged at the other end of the pilot valve core, and the conical head section can block the second damping hole;
when the pilot valve core moves to drive the pilot valve sleeve to move, the opening, the closing and the opening sizes of the first damping hole, the second damping hole and the main valve core are controlled by controlling the voltage of the proportional electromagnet, so that bidirectional throttling control is formed when the oil is fed to the oil port A or the oil port B;
the control cavity is a cavity which is formed by the lower end face of the armature, the middle part of the threaded sleeve, the upper part of the valve sleeve, the upper end of the main valve core, the pilot valve sleeve and the pilot valve core and is positioned at the upper end of the main valve core, and the control cavity is communicated with the pilot cavity; when the pilot valve sleeve moves towards the proportional electromagnet along with the pilot valve core, the first damping hole moves from a throttling position communicated with the third damping hole to a closed position and then to a throttling position; when the pilot valve core moves towards the proportional electromagnet along with the armature, the second damping hole moves to a throttling state from a closing position blocked by the pilot valve core;
when oil enters the oil port B, a voltage is applied to the proportional electromagnet, the armature overcomes the acting force of the elastic piece to drive the pilot valve core to move upwards, the pilot valve sleeve moves upwards to shield the first damping hole, the second damping hole is opened, the pressure of the control cavity is reduced, and the pressure difference between the oil port B and the control cavity acts on the main valve core;
increasing the voltage on the proportional electromagnet, increasing the pressure difference between the oil port B and the control cavity, opening the main valve core, and moving the oil liquid of the oil port B to the oil port A through the main valve core; further increasing the voltage on the proportional electromagnet, wherein the flow area between the pilot valve core and the second damping hole reaches the maximum, the first damping hole is completely closed, and the main valve core is completely opened;
when oil enters the oil port A, a voltage is applied to the proportional electromagnet, so that the pilot valve sleeve is positioned at a position which completely shields the first damping hole; increasing the voltage of the proportional electromagnet, gradually opening the first damping hole, gradually increasing the flow area of the first damping hole to be larger than that of the second damping hole, and gradually opening the main valve core under the action of the pressure difference between the oil port A and the control cavity; the voltage of the proportional electromagnet is further increased, and the main valve core reaches the maximum opening.
2. The proportional flow stop valve of claim 1, wherein an annular groove is formed in the middle of the pilot valve spool for connection, and the pilot valve sleeve is fixedly connected with the pilot valve spool through a connecting piece and the annular groove.
3. The proportional flow stop valve according to any one of claims 1 to 2, wherein the end of the pilot valve spool connected to the armature is of a T-shaped structure, one end of the armature is provided with a first T-shaped hole matched with the T-shaped structure of the pilot valve spool, the other end of the armature is provided with a second T-shaped hole, one end of the elastic member is installed in a large hole of the second T-shaped hole, and the first T-shaped hole is communicated with the second T-shaped hole.
4. The proportional flow stop valve of claim 1, wherein said valve housing is in threaded sealing connection with the other end of said threaded sleeve, and a bevel is provided at the connection of the lower end of said main valve element and said valve housing.
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| CN108916459A (en) * | 2018-07-14 | 2018-11-30 | 东莞海特帕沃液压科技有限公司 | A kind of two-way shut-off valve |
| CN109253304B (en) * | 2018-10-19 | 2020-09-15 | 中国航发贵州红林航空动力控制科技有限公司 | Two-position two-way normally closed type miniature large-flow fuel electromagnetic valve |
| CN109373021B (en) * | 2018-12-19 | 2023-12-19 | 重庆红江机械有限责任公司 | Automatic fuel circulation valve |
| CN109973456A (en) * | 2019-04-16 | 2019-07-05 | 武汉科技大学 | A kind of automatically controlled high pressure check valve of combined type |
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| US6149124A (en) * | 1999-05-03 | 2000-11-21 | Husco International, Inc. | Pilot solenoid control valve with pressure responsive diaphragm |
| JP4035467B2 (en) * | 2003-03-24 | 2008-01-23 | 株式会社ファインシンター | Pilot operated solenoid valve |
| DE10343608B4 (en) * | 2003-09-20 | 2015-01-08 | Buchholz Hydraulik Gmbh | Solenoid operated valve |
| CN202040405U (en) * | 2011-05-09 | 2011-11-16 | 宁波克泰液压有限公司 | Thread plug-in two-position two-way normally closed electromagnetic valve |
| CN201992139U (en) * | 2011-05-09 | 2011-09-28 | 宁波克泰液压有限公司 | Threaded insertion pilot normally closed dual-check electromagnetic valve |
| CN202176805U (en) * | 2011-09-07 | 2012-03-28 | 浙江中宝自控元件有限公司 | Energy-saving valve needle type solenoid valve |
| CN202851493U (en) * | 2012-09-24 | 2013-04-03 | 温州美瑞克液压有限公司 | Threaded inserted type counterbalance valve |
| CN203571176U (en) * | 2013-10-25 | 2014-04-30 | 宁波隆腾轴承液压件有限公司 | Two-position two-way solenoid valve |
| CN203571177U (en) * | 2013-10-25 | 2014-04-30 | 宁波隆腾轴承液压件有限公司 | Two-position two-way normally open solenoid valve |
| CN205047559U (en) * | 2015-09-29 | 2016-02-24 | 浙江华益精密机械股份有限公司 | Hydraulic control valve |
| CN206036237U (en) * | 2016-04-13 | 2017-03-22 | 湖南凯恩利液压机械制造有限公司 | Solenoid valve and mechanical equipment for water |
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Effective date of registration: 20200514 Address after: 325000 No.422 Binhai 22nd Road, Wenzhou Economic and Technological Development Zone, Zhejiang Province Applicant after: Ennis Valve Group Co., Ltd Address before: 315000 Zhejiang province Ningbo city Ningbo high tech Zone Juxian Road No. 555 building 035 room 18-1 No. 013 station Applicant before: NINGBO WENZE ELECTROMECHANICAL TECHNOLOGY DEVELOPMENT Co.,Ltd. |
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