KR101791547B1 - A Multi-step Control Valve Apparatus for Improved Response and Accuracy - Google Patents

A Multi-step Control Valve Apparatus for Improved Response and Accuracy Download PDF

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Publication number
KR101791547B1
KR101791547B1 KR1020160006665A KR20160006665A KR101791547B1 KR 101791547 B1 KR101791547 B1 KR 101791547B1 KR 1020160006665 A KR1020160006665 A KR 1020160006665A KR 20160006665 A KR20160006665 A KR 20160006665A KR 101791547 B1 KR101791547 B1 KR 101791547B1
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South Korea
Prior art keywords
control block
pressure
main spool
piston
control valve
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KR1020160006665A
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Korean (ko)
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KR20170087123A (en
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주종호
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지성중공업 주식회사
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    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2232—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2239—Control of flow rate; Load sensing arrangements using two or more pumps with cross-assistance
    • 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
    • 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
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
    • F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
    • F16K11/07—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Multiple-Way Valves (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

The present invention relates to a multi-stage control valve apparatus with improved responsiveness and accuracy, and more particularly, to a multi-stage control valve apparatus having a cylinder main body in which a piston is reciprocatably movable and in which a plurality of pressure lines for pressure increase and decrease are formed, A control block for selectively opening each of the oil passages while moving the main spool in the left and right direction to set the stroke distance of the piston to a multi-stage; and a controller for charging the cylinder body with high pressure oil to raise the piston, A control valve housing for compressing gas and a bidirectional solenoid valve for controlling the control block in multiple stages by selectively supplying working oil to both sides of the control block.

Description

[0001] The present invention relates to a multi-step control valve device having improved response and accuracy,

The present invention relates to a multi-stage control valve apparatus with improved responsiveness and accuracy, and more particularly to a multi-stage control valve apparatus in which a pilot spool is installed on both sides of a main spool of a control block for setting a stroke distance of a piston, The present invention relates to a multi-stage control valve device capable of quick response and precise control by applying a valve.

Normally, a hydraulic breaker is mounted on an excavator, one of the construction equipment, to crush rock, concrete and cement structures and to excavate the ground.

The hydraulic breaker includes a cylinder body that reciprocates the piston by hydraulic pressure, a piston that reciprocates in the cylinder body, and a chisel that interlocks with the reciprocation of the piston and strikes the crushed material.

The reciprocating distance of the piston is generally referred to as the stroke distance. The larger the stroke distance, the greater the impact force applied to the chisel, which is advantageous for crushing the rock having a high strength, and the smaller the stroke distance, the more effective it is for rocks and ground excavation.

As the stroke distance increases, the impact force on the crushed material increases, but the number of times the crushed material is hit by the chisel decreases. Therefore, when the crushed material is crushed or the ground is excavated, the larger the stroke distance, the lower the working efficiency.

On the other hand, when the strength of the crushed material is large, the crushed material is not easily crushed if the crushing distance is reduced.

This problem of the working efficiency has caused a demand for the stroke distance control of the piston, and a two stroke control method has been proposed in which the stroke distance is set to two.

As a conventional technique for this, Korean Patent Laid-Open No. 10-2009-0041823 has proposed a hydraulic breaker that causes a two-stage stroke when the strength of the crushed material is low or high. Korean Unexamined Patent Application Publication No. 10-2009-0041823 measures the reciprocating distance of the piston to set the stroke distance for the two cases when the strength of the crushed material is high or low.

However, in the conventional hydraulic breaker, a sensor for measuring the reciprocating distance of the piston must be provided inside the cylinder, and the position of the piston is measured by these sensors to set the two-stage stroke. In addition, irrespective of the operator's intention, the crushed material is always struck with two steps of stroke distance. For example, even if the operator desires to strike the crushed material with a long stroke in the case where the crushed material is weak in strength, the crushed material is struck by the short stroke. However, the method of using the stroke distance for each country, Bar and operator convenience are neglected.

In order to solve such a problem, the applicant of the present invention has proposed a hydraulic breaker (Korean Patent Laid-Open Publication No. 10-3258) which can maximize work productivity by automatically changing the stroke distance of the piston according to the strength of the crushed material by applying a PCP valve (proportional pressure control valve) 2015-36848).

The hydraulic breaker disclosed in Korean Patent Laid-open No. 10-2015-36848 is capable of changing the stroke distance of the piston in three stages through three directional switching stages and maintaining a constant pressure in order to be in the second stage, I had to write.

However, in the PCP valve system, since the responsiveness is poor and the spool is not precisely formed, a pressure loss is generated. Therefore, there is a limit in maintaining the pilot pressure constant in the two-stage control. This is because the control is not accurate at each stage and the efficiency of the work is lowered and it is difficult for the operator to adjust the stroke distance in the second stage. Therefore, measures are urgently required.

Korean Patent Laid-Open No. 10-2009-0041823. Korean Patent Publication No. 10-2015-0036848.

SUMMARY OF THE INVENTION The present invention has been made in order to solve the above problems, and it is an object of the present invention to provide a multi-stage The purpose of the present invention is to propose a control valve device.

In order to achieve the above object, according to the present invention, there is provided a cylinder structure including a cylinder body having a piston reciprocatingly formed therein and having a plurality of pressure lines for increasing and decreasing a pressure, A control block for selectively opening each of the oil passages while moving the main spool in the left and right directions to set the stroke distance of the piston in a multi-stage; and a control valve for charging the cylinder body with high pressure oil to raise the piston, And a bidirectional solenoid valve for controlling the control block in multiple stages by selectively supplying hydraulic fluid to both sides of the control block.

A main spool which is accommodated in the main body of the control block and whose position is controlled by operating oil supplied from a pump; Directional solenoid valve, an induction groove formed to communicate with the flow path in accordance with the position of the main spool, and an inlet port connected to each port of the bidirectional solenoid valve for moving the main spool in the left- And a pilot spool to be installed.

The present invention may further include a pressure adjusting spring that is wound on the outside of the pilot spool and elastically supports the main spool on both sides of the main spool in the lateral direction to adjust the position of the main spool.

In this case, the pressure regulating springs of the same size may be installed on both sides of the main spool.

Meanwhile, the control block may further include a low-pressure line for discharging the leaking water to the control valve housing when the leaking occurs in the control block main body, so that the leaking does not affect the leaking.

The low-pressure line may be installed at a position corresponding to any one of the pilot spools.

In addition, the flow path is formed in a plurality of corresponding to the pressure line, and the stroke distance of the piston is varied according to the pressure difference inside the cylinder body.

In this case, the flow path may be formed in three to five stages.

According to the present invention, the control valve housing may be installed on the upper portion of the cylinder body, and the control block may be installed on the control valve housing to be stacked.

Accordingly, the low-pressure line and the flow path provided in the control block are formed in a 'T' shape, and the pressure line passes through the control valve housing to communicate the flow path and the cylinder body.

According to the present invention as described above, a pilot spool is provided on both sides of the main spool of the control block for setting the stroke distance of the piston, and a bidirectional solenoid valve is used as a valve for moving the main spool. It is possible to improve the efficiency and the reliability of the work by making the responsiveness fast when adjusting and accurate control by each stage.

1 is an assembled perspective view showing the appearance of a multi-stage control valve apparatus according to the present invention.
2 is an assembled perspective view illustrating an internal configuration of a multi-stage control valve apparatus according to the present invention.
3 is an enlarged view of a portion A in Fig.
4 is a perspective view showing a control block of the present invention.
5 is an exploded perspective view showing a configuration of a control block of the present invention.
6 is a sectional view showing the operation states of the first to third stages of the control block of the present invention.
7 is a schematic block diagram of a hydraulic breaker to which the multi-stage control valve device of the present invention is applied.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. The present invention may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the invention to those skilled in the art. It is provided to let you know.

FIG. 1 is a perspective view showing the appearance of a multi-stage control valve apparatus according to the present invention, FIG. 2 is a perspective view showing an internal structure of a multi-stage control valve apparatus according to the present invention, to be.

7 is a schematic block diagram of a hydraulic breaker to which the multi-stage control valve device of the present invention is applied.

As shown in the drawings, the multi-stage control valve apparatus 100 according to the present invention includes a cylinder 111 having a plurality of pressure lines 114, 116, and 118 for increasing and decreasing the pressure of the piston 111, 124b and 124c connected to the main body 110 and the pressure lines 114, 116 and 118 are formed and the main spool 126 moves in the left and right direction, 124a, 124b and 124c to set the stroke of the piston to a multi-stage, and a control block 120 for charging the cylinder body 110 with high pressure oil to raise the piston, A control valve housing 130 for compressing the working gas filled in the control block 120 and a bidirectional solenoid valve for controlling the control block 120 in multiple stages by selectively supplying operating fluid to both sides of the control block 120 .

The multi-stage control valve apparatus 100 of the present invention can be applied, for example, to a hydraulic breaker to be used for crushing rocks, concrete, and cement structures or excavating grounds.

7, the hydraulic breaker includes a cylinder body 110, a piston 111 reciprocating by hydraulic pressure in the cylinder body 110, and a piston 111 interlocked with the reciprocation of the piston 111 A plurality of pressure lines 114, 116 and 118 for increasing and decreasing the pressure are formed in the cylinder body 110 so as to be connected to the control block 120 So that the stroke distance of the piston 111 can be changed.

The control valve housing 130 charges the high pressure oil in the lower portion of the cylinder body 110 to raise the piston and compress the working gas filled in the gas chamber. When high pressure oil is supplied to the control valve housing from the control block 120 when the piston rises above a predetermined height, the direction of the control valve is switched to supply the high pressure oil to the upper portion of the cylinder body. Accordingly, the pressure of the compressed working gas in the gas chamber and the pressure of the oil supplied to the upper portion of the cylinder body 110 drop the piston at a high speed and strike the chisel.

1, the control valve housing 130 is installed on an upper portion of the cylinder body 110, and the control valve housing 130 is disposed on the upper portion of the control valve housing 130 And the control block 120 is installed. As described above, since the three components are stacked, the installation space can be reduced, and the structural characteristics will be described later.

FIG. 4 is a perspective view showing a control block of the present invention, and FIG. 5 is an exploded perspective view showing a configuration of a control block of the present invention.

The control block 120 includes a control block main body 122 having flow paths 124a, 124b and 124c connected to the pressure lines 114, 116 and 118, A main spool 126 which is accommodated in the main spool 126 and whose position is controlled by the operating oil supplied from the pump and is formed at a central rim of the main spool 126, Directional solenoid valve 124b and 124c and an inlet port connected to each port of the bidirectional solenoid valve so as to move the main spool 126 in the lateral direction, And a pilot spool 128 installed on both sides of the pilot spool 128.

The control block body 122 is formed with a hollow portion 122a having a length and width enough to reciprocate by the hydraulic oil received in the main spool 126, .

As described above, the present invention is configured to supply the operating fluid to both sides of the control block body 122 through the bidirectional solenoid valve, so that the position of the main spool 126 can be efficiently controlled by the pressure control.

A block nut 127 is inserted into the inlet port on both sides of the hollow portion 122a and the pilot spool 128 is inserted into the block nut 127 by a predetermined length, The main spool 126 is pushed to move the main spool 126 in the left-right direction.

The position of the main spool 126 can be precisely controlled by the pilot spool 128. That is, when the pilot spool 128 having the cylindrical shape is supplied with the operating oil, the main spool 126 is pushed, and the main spool 126 is moved in the left-right direction. And the pressure of the pilot spool 128, so that the main spool 126 can be moved to a very precise position.

Accordingly, when the stroke distance of the piston is controlled by the first, second, and third stages, the main spool 126 is accurately moved to accurately open the respective flow paths 124a, 124b, 124c, Can be improved.

On the other hand, a pressure regulating spring (129) for regulating the position of the main spool (126) by elastically supporting the main spool (126) on both sides when the main spool (126) ) May be further included.

In this case, both ends of the pressure regulating spring 129 are supported by the main spool 126 and the block nut 127 to support the main spool 126 on both sides when the main spool 126 moves. The two pressure regulating springs 129 are provided so as to correspond to both sides of the main spool 126 so that the bidirectional solenoid valves can be moved to the left or right side, So that the control of each stage of the control block 120 is accurately performed.

The control block 120 may further include a low pressure line 123 for discharging the leakage to the control valve housing 130 when the leakage occurs in the control block body 122, . That is, leakage may occur in the process of moving left and right while the main spool 126 is inserted into the hollow portion 122a. The leakage generated at this time may be transmitted to the control valve 122 through the low- And is discharged to the housing 130 so that there is no influence due to leakage.

The low pressure line 123 is installed at a position corresponding to one of the two pilot spools 128 and may be installed in the pilot spool 128.

The flow paths 124a, 124b and 124c are formed corresponding to the pressure lines 114, 116 and 118 to form the first flow path 124a, the second flow path 124b, And the stroke distance of the piston 111 is varied in accordance with the pressure difference inside the cylinder body 110. [

In this case, the flow paths 124a, 124b, and 124c may be formed in four stages or five stages as well as three stages.

The low pressure line 123 and the flow paths 124a, 124b, and 124c provided in the control block 120 are connected to the control block 120 by the structure in which the control block 120 is installed above the control valve housing 130. [ Quot; T ".

That is, the control block 120, the control valve housing 130, and the cylinder body 110 are stacked so that the control block 120 and the control valve housing 130 are installed closest to each other, The pressure lines 114, 116 and 118 pass through the control valve housing 130 to connect the flow paths 124a, 124b and 124c to the cylinder body 110. [

That is, one end of the pressure line 114, 116, 118 is communicated with the flow path 124a, 124b, 124c, and the other end is connected to the cylinder body 110. The control valve housing 130, The pressure lines 114,116 and 118 are inserted into the control valve housing 130 and the flow paths 124a and 124b and 124c And the cylinder body 110 are connected to each other.

Due to such an installation structure, the low-pressure line 123 and the flow paths 124a, 124b and 124c in the control block 120 are formed in a T shape.

An induction groove 126a communicating with the flow paths 124a, 124b and 124c is formed in a center frame of the main spool 126 according to the position of the main spool 126. The bidirectional solenoid valve The pilot spool 128 pushes the main spool 126 by the supplied operating fluid so that the main spool 126 is moved to the left or right side of the control block main body 122, The corresponding oil passages 124a 124b 124c and the guide groove 126a are communicated with each other and the hydraulic oil is supplied to the control valve housing 130 through the oil passages 124a 124b 124c.

When the operating fluid is supplied to both sides of the control block main body 122, pressure regulating springs 129 may be further formed on both sides of the main spool 126 to allow the main spool 126 to perform more precise control and quick response Speed.

The flow paths 124a, 124b and 124c formed in the control block body 122 are formed correspondingly to the pressure lines 114, 116 and 118, The stroke distance of the piston 111 is changed according to the pressure difference inside the piston 111. [

The flow paths 124a, 124b and 124c are formed to correspond to the number of the pressure lines 114, 116 and 118, and are formed in three to five stages, Diversify the distance.

(1) an automatic mode, (2) an automatic mode, and (3) an automatic mode in which the stroke distance of the piston 111 can be varied through a stroke distance control unit according to a pressure difference inside the cylinder body 110, Manual mode or (3) set mode.

(1) The automatic mode is a mode for automatically controlling the stroke distance of the piston 111 in accordance with the hardness of the crushed material. The hardened level of the crushed material is measured by a pressure sensor (the applicant's application number 10-2013-0115790) A compression load cell, a pressure sensor, or an acceleration sensor), and the stroke distance of the piston 111 is input with a preset value. When the automatic mode is executed, the operating fluid of the corresponding pressure by the pressure sensing unit To the control block 120 so that the stroke of the piston 111 can be automatically set by selectively increasing or decreasing the pressure of the pressure lines 114, 116 and 118 formed in the cylinder body 110 .

(2) In the manual mode, the operation mode of the piston (111) is changed to the first, second, and third stages (the stroke increases as the number of stages increases) by manual operation regardless of the hardness of the crushed product To operate.

(3) It is also possible to implement a setting mode in which the stroke distance of the piston 111 is automatically controlled, but the hardness range of each operating mode is set.

In the setting mode, the automatic mode is set to, for example, one stage when the hardness of the crushed material is 1 to 30, two stages when the crushed material has a hardness of 31 to 60, and three stages when the hardness of the crushed material is 61 to 100 And corresponds to a mode in which the hardness range for each operation mode is automatically set.

In this setting mode, the hydraulic breaker operates automatically in the first, second and third stages, but corresponds to the mode in which the minimum value and the maximum value of each operation mode are customized. For example, the minimum and maximum values of the single-stage operating mode can be user-set to 1-20, or 1-40.

Here, the manual mode corresponds to a mode in which the worker determines the stroke distance of the piston 111 that applies a force to the crushed material regardless of the hardness of the crushed material.

By implementing the above three operation modes of the present invention, the hydraulic breaker can be operated according to the working environment, the circumstances, and the operator's taste for each region or each country.

In the above description, the control block 120 for controlling the hydraulic breaker has three stroke distances. However, the flow paths 124a, 124b and 124c provided in the control block 120 shown in FIG. And if it is expanded to four, it can have four stroke distances.

That is, the stroke distance of the piston 111 can be varied according to the number of the oil passages 124a, 124b, and 124c formed in the stroke control valve. At this time, the number of pressure holes formed in the cylinder body 110 should be the same as the number of the oil passages 124a, 124b, and 124c formed in the stroke control valve.

Hereinafter, the operation and effect of the present invention will be described in detail.

6 is a sectional view showing the operation states of the first to third stages of the control block of the present invention.

First, when the hydraulic fluid discharged from the pump is supplied to the control block 120 through the bidirectional solenoid valve, the position of the main spool 126 is determined, and the guide groove 126a formed in the rim of the main spool 126 The pressure of the pressure lines 114, 116, and 118 formed in the cylinder body 110 is determined.

The flow paths 124a, 124b and 124c provided in the control block 120 according to the present invention are respectively connected to the pressure lines 114, 116 and 118 formed in the cylinder body 110, The stroke distance of the piston 111 reciprocating in the cylinder body 110 varies depending on the inner pressure difference.

When the pressure lines 114, 116 and 118 are maintained at a high pressure, the piston 111 moves up to the first position having the maximum stroke distance and moves to the head cap to the maximum, and the pressure holes 122a and 122b, When the pressure hole 122a is maintained at a high pressure, it can rise to a third position which is one step lower than the second position, when the pressure hole 122a is maintained at a high pressure.

That is, if it is desired to set a specific stroke distance in consideration of the hardness of the crushed material and various working environments, the corresponding high pressure oil is supplied to cause the piston 111 to rise to the maximum, And the pressure lines 114, 116 and 118 are communicated with each other by supplying the operating fluid to the induction grooves 120 and the induction grooves 126a, the flow paths 124a, 124b and 124c, So that it is lowered while having a hitting force.

6A shows a case where the hydraulic oil is supplied to the right inlet of the control block 120 through the bidirectional solenoid valve and reaches the predetermined pressure, The guide groove 126a formed at the rim of the main spool 126 communicates with the first flow path 124a while the gate of the first flow path 124a is opened.

The high pressure oil is moved through the pressure line 114 communicated with the first passage 124a and supplied to the control valve housing 130 so that the high pressure oil is supplied to the upper portion of the cylinder body, .

Since the pressure regulating spring 129 is interposed in the pilot spool 128, when the pressure is not supplied to both sides of the main spool 126, the main spool 126 becomes parallel, Is positioned at the center of the hollow portion 122a and the guide groove 126a is communicated with the second flow path 124b so that the gate of the second flow path 124b is opened.

Meanwhile, when the hydraulic oil is supplied to the left inlet of the control block 120 through the bidirectional solenoid valve and reaches a predetermined pressure or more, the main spool 126 moves to the right and the guide groove 126a Is communicated with the third flow path 124c and the gate of the third flow path 124c is opened.

Accordingly, the stroke distance of the piston 111 is determined through the pressure line 118 communicated with the third flow path 124c.

It is to be understood that the invention is not limited to the disclosed embodiment, but is capable of many modifications and variations within the scope of the appended claims. It is self-evident.

100: multi-stage control valve device 110: cylinder body
114, 116, 118: pressure line 120: control block
124a, 124b, 124c:
126: main spool 126a: guide groove
128: Pilot spool 129: Pressure regulating spring
130: Control valve housing

Claims (10)

A cylinder body in which a piston is reciprocatably formed and in which a plurality of pressure lines for pressure increase and decrease are formed;
A control block having a passage connected to the pressure line and selectively opening each of the passages while moving the main spool in the left and right direction to set the stroke of the piston to a multi-stage;
A control valve housing for filling the cylinder body with high pressure oil to raise the piston and compress the working gas filled in the gas chamber; And
A bidirectional solenoid valve for selectively supplying hydraulic fluid to both sides of the control block to control the control block in multiple stages; Lt; / RTI >
Wherein the control block includes a control block body having a flow path connected to the pressure line; A main spool accommodated in the control block main body and controlled in position by operating fluid supplied from a pump; An induction groove formed in a central rim of the main spool and communicating with the passage according to a position of the main spool; A pilot spool inserted into an inlet connected to each port of the bidirectional solenoid valve and installed on both sides of the main spool to move the main spool in the left and right direction; And a low pressure line for discharging the leakage of the control block body to the control valve housing when there is leakage from the control block body so that there is no influence due to leakage. delete The method according to claim 1,
Further comprising a pressure adjusting spring that is wound on the outside of the pilot spool and elastically supports the main spool on both sides when the main spool is moved in the lateral direction to adjust the position of the main spool. The method of claim 3,
Wherein the pressure regulating springs of the same size are installed corresponding to both sides of the main spool. delete The method according to claim 1,
And the low-pressure line is installed at a position corresponding to any one of the pilot spools. The method according to claim 1,
Wherein the flow path is formed in a plurality corresponding to the pressure line,
And the stroke distance of the piston is varied according to a pressure difference inside the cylinder body. The method of claim 7,
Wherein the flow path is formed in three to five stages. The method according to claim 1,
Wherein the control valve housing is provided on an upper portion of the cylinder body,
And the control block housing is stacked on the upper portion of the control valve housing. The method of claim 9,
The low-pressure line and the flow path installed in the control block are formed in a T shape,
Wherein the pressure line passes through the control valve housing to communicate the flow path with the cylinder body.


KR1020160006665A 2016-01-19 2016-01-19 A Multi-step Control Valve Apparatus for Improved Response and Accuracy KR101791547B1 (en)

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Citations (2)

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Publication number Priority date Publication date Assignee Title
KR200306630Y1 (en) * 1997-10-30 2003-11-17 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 Count balance valve
JP6037089B1 (en) * 2015-08-17 2016-11-30 三菱電機株式会社 Heat utilization device

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR200306630Y1 (en) * 1997-10-30 2003-11-17 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 Count balance valve
JP6037089B1 (en) * 2015-08-17 2016-11-30 三菱電機株式会社 Heat utilization device

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