CN210123039U - Electric control large-capacity proportional valve - Google Patents

Abstract

An electrically-controlled large-capacity proportional valve has a decompression chamber, which is connected with sound guide hole channel, sensor channel and exhaust channel, the decompression chamber is provided with a main diaphragm with a check valve for driving a main shaft and a secondary shaft to move and detecting the sensor channel, when the pressure is too low, the main diaphragm pushes the main shaft downwards to prop against the secondary shaft, the secondary shaft member allows the valve port to perform two-stage displacement distance adjustment to control the fluid flow rate after the valve port is opened, and the primary side pressure enters the output end of the valve base to increase the secondary side pressure, so that the secondary side pressure has the output quantity of precisely adjusting the secondary side pressure, and the air vent arranged in the main shaft part and the airflow hole arranged in the exhaust chamber can be utilized to carry out two-stage exhaust, so that the whole structure can achieve the purposes of quick adjustment and precise pressure stabilization by virtue of two-stage air inlet and exhaust, and is suitable for a large-capacity proportional valve.

Description

Electric control large-capacity proportional valve

Technical Field

The utility model belongs to the technical field of the proportional valve technique and specifically relates to an automatically controlled large capacity proportional valve.

Background

Electrically controlled proportional valves are widely used in various industries, but the power provided by pneumatic fluid, the stability of the power and the pressure of the output vary with the magnitude of the pneumatic fluid, so that in order to make the pressure output stable and controlled by an electric control system, the technology of the existing electrically controlled proportional valves for controlling the pressure of the pneumatic fluid is commonly adopted, so as to control the pneumatic fluid used to obtain a stable and controlled pressure.

The existing electric control proportional valve is generally provided with a decompression chamber, a straight rod and a diaphragm, after fluid is input from an input end in the operation process, the fluid flows to the diaphragm through an internal flow path and drives the straight rod to move downwards, so that the fluid in the electric control proportional valve can flow to an output end through a valve port to be adjusted, the diaphragm and the straight rod are generally arranged in the decompression chamber, in order to be easily adjusted, the space height of the decompression chamber is generally slightly larger than the actuation stroke of the diaphragm, and the straight rod can push the displacement to be smooth.

Because the pressure difference between the diaphragm and the decompression chamber exerts a force on the straight rod, so that the input fluid pressure keeps a certain output flow, the input fluid pressure cannot be applied to precise pressure adjustment, and if the input fluid pressure needs to be applied to an electric control proportional valve with larger capacity, the mechanical design of the electric control proportional valve becomes more complicated, so that the input fluid can be optimally applied to the electric control proportional valve with the structure with larger capacity, and a structure capable of adjusting the pressure within a working pressure range and having precise adjustment is needed.

SUMMERY OF THE UTILITY MODEL

The invention discloses an electric control large-capacity proportional valve, which mainly aims at utilizing a main diaphragm with a check valve to be matched and arranged in a valve seat to form a decompression chamber, and when externally input primary side pressure flows into the decompression chamber through a sound guide hole channel and an air inlet electromagnetic valve is opened to push the main diaphragm, the main diaphragm and a secondary diaphragm can be pushed to perform displacement action, so that a valve port can be opened and closed to control the output quantity of the secondary side pressure.

The utility model discloses an automatically controlled large capacity proportional valve, it contains: a valve seat, which is composed of an upper valve, a middle valve and a valve base connected in sequence from top to bottom, wherein the valve seat is provided with an input end for inputting primary side pressure and an output end for outputting secondary side pressure, the input end is communicated with the output end through a flow path, a main diaphragm provided with a check valve is clamped between the upper valve and the middle valve to form a decompression chamber, the upper valve is connected with a sound guide hole channel which is controlled by the air inlet electromagnetic valve and communicated to the input end, an exhaust channel which is controlled by the exhaust electromagnetic valve and used for exhausting redundant pressure, and a sensor channel which is communicated with the output end is detected by a sensor, and the middle valve is internally provided with a steady flow hole which is communicated to the valve base and is communicated with a middle valve check valve of the sound guide hole channel and an air flow hole outside through the steady flow hole; wherein, a main shaft part with a vent hole is arranged in an exhaust chamber of the middle valve, a primary shaft part with an elastic component is arranged below the main shaft part, the main diaphragm props against the main shaft part, and then the secondary shaft part is driven by displacement to form a valve port by matching with the elasticity of the elastic component; when the pressure of the output end is too low, the main diaphragm pushes the main shaft part and the secondary shaft part downwards to perform two-stage air inlet adjustment, and the exhaust electromagnetic valve adjusts the secondary side pressure through the check valve and the vent hole of the main diaphragm to perform first-stage exhaust pressure reduction control so that the valve port adjusts the output quantity of the secondary side pressure; when a large amount of exhaust is required, the top end of the main shaft element completely enters the exhaust chamber, the annular area of the exhaust chamber minus the area of the main shaft element is equal to the area of the valve opening, and the airflow hole accelerates to output a large amount of pressure to be directly communicated with the outside of the valve seat to perform a second-stage large amount of exhaust pressure reduction so as to stabilize the secondary side pressure output.

Optionally, the secondary shaft further comprises: and the caulking groove is arranged in the center of the upper part of the secondary shaft part and can be used for accommodating the main shaft part so as to control the opening and closing of the vent hole.

Optionally, the flow stabilizer further comprises: and the middle valve check valve is arranged on one side in the flow stabilizing hole and is used for communicating the flow stabilizing hole to the sound guide hole channel, so that the secondary side pressure is matched with the reduction of the primary side pressure, and the secondary side pressure is reduced and balanced.

Optionally, the flow stabilizing holes are symmetrically arranged in an even number in a ring shape with the central axis of the middle valve as a reference. This creation is an automatically controlled large capacity proportional valve, and it is by: an air inlet electromagnetic valve, an air exhaust electromagnetic valve and a sensor are arranged above a valve seat with a flow path, the flow path is provided with an input end for the inflow of primary side pressure and an output end for the outflow of secondary side pressure, a main diaphragm with a check valve is clamped in the valve seat to form a decompression chamber, the decompression chamber is connected with a sound guide hole channel which is controlled to be communicated with the input end by the air inlet electromagnetic valve, an air exhaust channel which is controlled to be communicated with the output end by the air exhaust electromagnetic valve and a sensor channel which is detected to be communicated with the output end by the sensor, a main shaft part with an air vent is arranged in an air exhaust chamber of the middle valve, a primary shaft part of an elastic component is arranged below the main shaft part, the main diaphragm props against the main shaft part to further displace and drive a secondary shaft part, the secondary shaft part forms a valve port by matching with the elastic force of the elastic component, when the pressure at the output end is too low, the main diaphragm pushes, the secondary shaft member enables the valve port to carry out two-stage displacement distance adjustment, controls the fluid flow after the valve port is opened, and then the primary side pressure enters the output end of the valve seat to improve the secondary side pressure; if the pressure is too high, the exhaust electromagnetic valve can adjust the secondary side pressure by the check valve to perform pressure reduction control, so that the valve port achieves the output quantity of precisely adjusting the secondary side pressure, and when a large amount of exhaust is required, the top end of the main shaft element completely enters the exhaust chamber, and because the annular area of the exhaust chamber minus the area of the main shaft element is equal to the area of the valve port, the large-size structural characteristic of the exhaust hole can accelerate the output of a large amount of pressure to be directly communicated with the outside of the valve seat, so that the purpose of accelerating and stabilizing the output of the secondary side pressure is achieved. The electric control large-capacity proportional valve is driven by the main shaft part and the secondary shaft part in a combined staged mode, the two-stage air inlet adjusting design of the secondary shaft part can be obtained, and the air vent arranged in the main shaft part is matched for first-stage air exhaust and the airflow hole arranged in the exhaust chamber is matched for second-stage air exhaust, so that the electric control large-capacity proportional valve can quickly perform secondary side pressure stabilization and achieve the purpose of precise pressure regulation in a short time in the field of large-capacity electric control proportional valves.

Drawings

The accompanying drawings, which are incorporated in and constitute a part of the specification, illustrate embodiments of the invention and together with the description, serve to explain the principles of the invention.

FIG. 1 is a schematic diagram of the present creation.

FIG. 2 is a schematic diagram of the circuit of the present creation architecture.

FIG. 3 is a diagram illustrating the operation of the present authoring in the ready state.

FIG. 4 is a schematic diagram illustrating the operation of the present invention in the startup state.

FIG. 5 is a schematic diagram of the operation of the present invention in the start-up state for microliter pressure.

FIG. 6 is a schematic diagram illustrating the operation of the present invention performing a micro-pressure reduction in the startup state.

FIG. 7 is a diagram illustrating the operation of the present invention in a standby state.

FIG. 8 is a schematic diagram illustrating the operation of the present invention in an operating state.

Description of reference numerals:

(10) .. valve seat

(101) .. Main diaphragm

(1011) .. check valve

(102) .. decompression chamber

(11) .. Top valve

(111) .. Sound pilot hole channel

(112) .. exhaust passage

(113) .. sensor channel

(12) .. middle valve

(121) .. Steady flow hole

(122) .. check valve with middle valve

(123) .. air flow hole

(124) .. air exhaust chamber

(13) .. valve base

(131) .. input terminal

(132) .. output terminal

(133) .. flow path

(134) .. elastic component

(14) .. Main shaft element

(141) .. air vent

(15) .. Secondary shaft

(151) .. caulking groove

(152) .. valve port

(PA)

(PA 1.) choke

(PB.) exhaust solenoid valve

(PB 1.) atmosphere vent

(PC)

(P.) control circuit

(PR.) power supply

(PI.) force signal

Pressure representation

(PO.) output signal

(P1.) the primary side pressure

(P2.) secondary side pressure

(PT)

Detailed Description

Generally, the best possible embodiment is described in detail with reference to FIGS. 1-8 to enhance the understanding of the present invention.

This creation is an automatically controlled large capacity proportional valve, and its structure includes: a valve seat 10, which is formed by connecting a top valve 11, a middle valve 12 and a valve base 13 from top to bottom in sequence, wherein the valve seat 10 has an input end 131 for inputting a primary pressure P1 and an output end 132 for outputting a secondary pressure P2, the input end 131 to the output end 132 are communicated by a flow path 133, a main diaphragm 101 with a check valve 1011 is sandwiched between the top valve 11 and the middle valve 12 to form a decompression chamber 102, and the required volume of the central space of the decompression chamber 102, such as the circular hole area and the circular hole height, can be reduced to the minimum, so that the main diaphragm 101 can rapidly balance the pressure in the decompression chamber 102, more specifically, the adjustment of the balance pressure PT is quicker, and if the intake flow of the throttle port PA1 of the primary pressure P1 is limited, but the effect of increasing the pressure stably is still kept, the opening time of the intake solenoid valve PA can be shortened, the displacement stroke of the main diaphragm 101 can be controlled more easily.

The decompression chamber 102 is connected to a sound pilot hole channel 111 controlled by an air inlet solenoid valve PA and communicated to the input end 131, an exhaust channel 112 controlled by an exhaust solenoid valve PB to exhaust excessive pressure, and a sensor channel 113 detected by a sensor PC and communicated with the output end 132, and a steady flow hole 121 communicated to the valve base 13, a middle valve check valve 122 communicated to the sound pilot hole channel 111 by the steady flow hole 121, and an air flow hole 123 communicated to the outside are provided in the middle valve 12.

A main shaft 14 with a vent hole 141 is installed in the exhaust chamber 124 of the middle valve 12, and a secondary shaft 15 with an elastic component 134 is installed under the main shaft 14, the main diaphragm 101 pushes the main shaft 14 up and down, and further the secondary shaft 15 is driven to displace to form a valve opening 152 in cooperation with the elastic force of the elastic component 134, when the pressure at the output end 132 is too low, the main diaphragm 101 pushes the main shaft 50 and the secondary shaft 15 downwards, and the secondary shaft 15 performs two-stage air intake adjustment, the exhaust solenoid valve PB can adjust the output of the secondary pressure P2 through the check valve 1011, and when a large amount of exhaust is required, the top end of the main shaft 14 completely enters the exhaust chamber 124, because the annular area of the exhaust chamber 124 minus the area of the main shaft 14 is equal to the area of the valve opening 152, a large amount of pressure can be accelerated and output to the outside of the valve seat 10 through the airflow hole 123, thereby accelerating the stabilization of the output of the secondary pressure P2.

Referring to fig. 1, it can be seen that the top valve 11 is connected to an intake solenoid valve PA, an exhaust solenoid valve PB and a sensor PC, which is mainly driven by a control circuit P via a power supply PR, after setting an input signal PI and an output signal PO, the control circuit P displays a related pressure representation PP to drive the intake solenoid valve PA and the exhaust solenoid valve PB, and a path connecting the top valve 11 to the control circuit P via an output end 132 is a sensor channel 113, the sensor PC is mainly used to detect the pressure of the secondary pressure P2, when the pressure exceeds or is lower than the set value of the secondary pressure P2, the information is fed back to the control circuit P to perform the determination between the intake solenoid valve PA and the exhaust solenoid valve PB, if the secondary pressure P2 is too high, the exhaust solenoid valve PB and a check valve 1011 are further driven to perform the first stage exhaust of the secondary pressure P2 and open an atmospheric vent PB1 located in the exhaust solenoid valve PB to increase the volume, when a large amount of exhaust is required, the top end of the main shaft element 14 completely enters the exhaust chamber 124, and because the annular area of the exhaust chamber 124 minus the area of the main shaft element 14 is equal to the area of the valve opening 152, a large amount of pressure can be accelerated and output by the airflow hole 123 to be directly communicated to the outside of the valve seat 10, which is the second stage of exhaust; on the contrary, if the secondary pressure P2 is too low, the intake solenoid valve PA is driven to push the primary diaphragm 101, so that the primary shaft 14 continues to displace downward to push the secondary shaft 143, so that the secondary pressure P2 can continue to increase to reach the predetermined value, and the related operation flow can be understood more clearly by referring to the circuit diagram of the overall structure shown in fig. 2.

Referring to the preparation state shown in fig. 3, it can be seen that when the intake solenoid valve PA is closed and the exhaust solenoid valve PB is opened, the primary pressure P1 is blocked by the closing of the valve port 152 after entering from the input end 131, and part of the primary pressure P1 is blocked from flowing to the decompression chamber 102 after flowing to the intake solenoid valve PA through the pilot hole channel 111, and the secondary pressure P2 is 0 at this time.

Referring to the starting state shown in fig. 4, when the intake solenoid valve PA is open and the exhaust solenoid valve PB is closed, the primary pressure P1 flows through the orifice PA1 of the intake solenoid valve PA through the pilot orifice channel 111 to the decompression chamber 102 above the main diaphragm 101, and forms a balanced pressure PT to push the main diaphragm 101 downward to the lowest position, and drives the main shaft 14 to displace downward, and further drives the secondary shaft 15 to displace downward together, thereby opening the valve port 152; the primary pressure P1 passing through the valve port 152 is converted into the secondary pressure P2, and then flows to the output end 132, the middle valve 12 and the sensor channel 113, when the sensor PC sends back a signal to the control circuit P to judge the related secondary pressure P2, and after the air intake solenoid valve PA and the air exhaust solenoid valve PB are judged, if the secondary pressure P2 is too high, a command is output to the air exhaust solenoid valve PB to perform the action of exhaust and pressure reduction; the secondary pressure P2 can flow into the center valve 12 through the flow stabilizing hole 121, and the flow stabilizing hole 121 is formed by an even number of flow stabilizing holes arranged in a ring shape and symmetrically arranged by taking the central axis of the center valve 12 as a reference, so that the displacement stability of the main diaphragm 101 is increased.

The design can effectively help the stability of the main diaphragm 101 during displacement to be increased; the valve opening 152 is opened completely at the stage when the first stage air intake and the second stage air intake are performed simultaneously.

Referring to the starting state shown in fig. 5, in order to adjust the rise of the secondary pressure P2, the intake solenoid valve PA is closed, the exhaust solenoid valve PB is opened, the exhaust solenoid valve PB controls to reduce the fluid flowing into the decompression chamber 102 above the main diaphragm 101, further, the equilibrium pressure PT is lowered, and after the equilibrium pressure PT is equalized with the secondary pressure P2 in the decompression chamber 102 below the primary diaphragm 101, the force generated by the main diaphragm 101 is applied to the main diaphragm 101, so that the main diaphragm 101 is upwardly displaced from the lowest position in fig. 4, the main shaft 14 and the secondary shaft 15 are both upwardly restored by the elastic component 134, and the valve port 152 is in the first stage of air intake state, the primary pressure P1 flows to the output end 132 through the gap between the secondary shaft 15 and the valve port 152, the secondary pressure P2 does not rise rapidly, and the intake solenoid valve PA can control the time and speed of rise of the secondary pressure P2 by a hundred percent.

Referring to the starting state shown in fig. 6, in order to adjust the pressure drop, the intake solenoid valve PA is closed, the exhaust solenoid valve PB is opened, and the valve port 152 is closed at this time, so that the primary pressure P1 cannot flow through the valve port 152, and the vent hole 141 in the main shaft 14 also allows the secondary pressure P2 to flow into the decompression chamber 102, wherein the flow is referred to as the first stage exhaust in this creation, and the time and speed of the fluid being exhausted through the exhaust solenoid valve PB completely controls the time and speed of the reduction of the secondary pressure P2 one hundred percent to achieve the predetermined target value.

Referring to the standby state shown in fig. 7, the intake solenoid valve PA is closed, the exhaust solenoid valve PB is closed, the valve port 152 is closed, the output port 132 is also closed, and the secondary pressure P2 can be kept in a stable state.

Referring to the operation state shown in fig. 8, the intake solenoid valve PA is opened, the exhaust solenoid valve PB is closed, the valve port 152 is fully opened during the first stage and the second stage of intake, and the secondary pressure P2 is output from the output end 132 in a large amount.

As shown in fig. 3 to 8, the secondary pressure P2 in the preparation state and the working state is the normal fluid output, and the secondary pressure P2 in other states is not output from the output end 132; in addition, the air flow hole 123 provided in the middle valve 12 can open the second stage exhaust only in the preparation state or when the pressure of the counter flow fluid at the output end 132 is too high, so as to accelerate the completion of the large-capacity exhaust, and the other states are not open; the intermediate valve check valve 122, which is also located in the intermediate valve 12, is further detailed: the flow stabilizing hole 121 is communicated with the sound guide hole passage 111, when the primary pressure P1 is lower than the secondary pressure P2, the secondary pressure P2 is matched with the primary pressure P1 in a flowing mode, and the pressure of the secondary pressure P2 is quickly reduced and balanced.

In summary, the electrically controlled large-capacity proportional valve of the present invention is designed to be driven in stages by the combination of the main shaft 14 and the sub shaft 15, so as to adjust the two-stage intake air of the sub shaft 15, and to perform the first stage exhaust through the vent hole 141 provided in the main shaft 14 and the second stage exhaust through the air flow hole 123 provided in the exhaust chamber 124, so that the secondary side pressure P2 can be stabilized and precisely adjusted in a short time in the field of electrically controlled large-capacity proportional valves.

Claims (4)

1. An electrically controlled large capacity proportional valve comprising: a valve seat (10) which is formed by connecting an upper valve (11), a middle valve (12) and a valve base (13) from top to bottom in sequence, wherein the valve seat (10) is provided with an input end (131) for inputting a primary pressure (P1) and an output end (132) for outputting a secondary pressure (P2), the input end (131) is communicated with the output end (132) through a flow path (133), a main diaphragm (101) provided with a check valve (1011) is clamped between the upper valve (11) and the middle valve (12) to form a decompression chamber (102), the upper valve (11) is connected with a sensor channel (113) which is communicated with the output end (132) and is controlled by an air inlet solenoid valve (PA) to be communicated with a sound guide hole channel (111) of the input end (131), is controlled by an air outlet solenoid valve (PB) to be discharged to control redundant pressure, and is detected by a sensor (PC), a flow stabilizing hole (121) communicated with the valve base (13) is arranged in the middle valve (12), a middle valve check valve (122) communicated with the sound guide hole channel (111) through the flow stabilizing hole (121) and an air flow hole (123) communicated with the outside directly; the method is characterized in that: a main shaft member (14) with a vent hole (141) is arranged in a gas exhaust chamber (124) of the middle valve (12), a primary shaft member (15) with an elastic component (134) is arranged below the main shaft member (14), the main diaphragm (101) is propped against the main shaft member (14), and then the secondary shaft member (15) is driven to displace to form a valve opening (152) by matching with the elastic force of the elastic component (134); when the pressure of the output end (132) is too low, the main diaphragm (101) pushes the main shaft element (14) and the secondary shaft element (15) downwards to perform two-stage air inlet adjustment, and the exhaust electromagnetic valve (PB) adjusts the secondary pressure (P2) through the check valve (1011) and the vent hole (141) of the main diaphragm (101) to perform first-stage exhaust pressure reduction control, so that the valve port (152) adjusts the output quantity of the secondary pressure (P2); when a large amount of exhaust is needed, the top end of the main shaft element (14) completely enters the exhaust chamber (124), the annular area of the exhaust chamber (124) minus the area of the main shaft element (14) is equal to the area of the valve opening (152), and the airflow hole (123) accelerates to output a large amount of pressure to be directly communicated with the outside of the valve seat (10) for a second-stage large amount of exhaust decompression so as to stabilize the output of the secondary pressure (P2).

2. An electrically controlled large capacity proportioning valve according to claim 1 wherein the secondary shaft (15) further comprises: and the embedded groove (151) is arranged in the center of the upper part of the secondary shaft element (15), and the embedded groove (151) can be used for accommodating the main shaft element (14) so as to control the opening and closing of the vent hole (141).

3. An electrically controlled large capacity proportional valve according to claim 1, wherein the flow stabilizing orifice (121) further comprises: and the middle valve check valve (122) is arranged on one side in the flow stabilizing hole (121) and is used for communicating the flow stabilizing hole (121) to the pilot hole channel (111) so that the secondary side pressure (P2) is matched with the reduction of the primary side pressure (P1) to reduce and balance the secondary side pressure (P2).

4. An electrically controlled large capacity proportional valve according to claim 1, wherein the orifice stabilizing holes (121) are symmetrically arranged in an even number in a circular arrangement with respect to the central axis of the center valve (12).

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