KR101704042B1 - Flow variable controller apparatus - Google Patents

Flow variable controller apparatus Download PDF

Info

Publication number
KR101704042B1
KR101704042B1 KR1020100134300A KR20100134300A KR101704042B1 KR 101704042 B1 KR101704042 B1 KR 101704042B1 KR 1020100134300 A KR1020100134300 A KR 1020100134300A KR 20100134300 A KR20100134300 A KR 20100134300A KR 101704042 B1 KR101704042 B1 KR 101704042B1
Authority
KR
South Korea
Prior art keywords
poppet
piston
pilot
pressure
sectional area
Prior art date
Application number
KR1020100134300A
Other languages
Korean (ko)
Other versions
KR20120072519A (en
Inventor
여명구
이상우
Original Assignee
두산인프라코어 주식회사
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 두산인프라코어 주식회사 filed Critical 두산인프라코어 주식회사
Priority to KR1020100134300A priority Critical patent/KR101704042B1/en
Publication of KR20120072519A publication Critical patent/KR20120072519A/en
Application granted granted Critical
Publication of KR101704042B1 publication Critical patent/KR101704042B1/en

Links

Images

Classifications

    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D7/00—Control of flow
    • G05D7/03—Control of flow with auxiliary non-electric power

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • Fluid Mechanics (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Fluid-Driven Valves (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)

Abstract

The present invention relates to a variable flow control device, and more particularly to a variable flow control device capable of appropriately reducing a flow rate supplied to a working machine through auxiliary pilot signal pressure regardless of a pressure in a parallel passage, There is provided a flow control valve in which a pilot piston which is subjected to a signal pressure and which slides toward a poppet, a piston therebelow, and an annular pressure portion formed around the pilot piston and connected to the parallel passage through a flow passage, (Control amount) of the poppet can be controlled regardless of the pressure of the working fluid in the parallel passage by providing the variable flow control device with the same size as the lower end surface of the poppet. And the manufacturing cost is not high. Further, Which can provide a variable flow rate control device.

Description

[0001] Flow variable controller apparatus [0002]

[0001] The present invention relates to a variable flow control device, and more particularly, to a variable flow control device capable of appropriately reducing a flow rate supplied to a worker through an auxiliary pilot signal pressure provided to a variable flow control device corresponding to a predetermined work machine irrespective of a pressure in a parallel passage To a variable flow rate control device.

When the main pump and the plurality of working machines are connected through the corresponding plurality of directional switching valves so that the two or more working machines are combined and driven to increase the flow rate of the working oil to the specific working machine requiring a large load, And controls the flow rate of the hydraulic fluid supplied to the corresponding working machine to which it is connected to be reduced by receiving the pilot signal pressure.

The variable flow control device basically includes a direction switching valve disposed between a pump and a predetermined working machine for controlling start, stop and direction switching of the work machine by switching the spool when a pilot signal pressure is applied, And a control device for controlling the flow rate supplied to the working machine by at least partially closing the connection between the parallel passage and the pair of right and left cylinder flow paths by moving the poppet in response to the auxiliary pilot signal pressure The flow rate control valve means is provided.

In this configuration, the control of the actual flow rate may be indicated according to the result of the sum of the actuation forces acting on the device, specifically on the poppet, which acts on the auxiliary pilot signal pressure, the pressure of the hydraulic fluid in the parallel passage, The pressure can be determined in a complex manner by a plurality of pressure chambers provided with a real action force for each component and a plurality of spring forces contained therein.

For example, FIG. 1 is a cross-sectional view showing an example of a conventional hydraulic control apparatus. The hydraulic control apparatus 10 shown in FIG. 1 receives a pilot signal pressure and starts, stops, A poppet 30 capable of opening and closing a connection portion between the parallel passage 22 and the cylinder fluid passage 24 in addition to the directional switching valve 20 capable of controlling the directional switching, (Or " flow rate control means ") 40 capable of controlling the amount of movement of the piston 30. More specifically, the poppet 30 is configured in the form of a double poppet in which a small poppet 34 is housed in a large poppet 32. The piston 40 is provided with a pressure chamber A compensating pressure chamber 46a for canceling the piston acting force of the pressure chamber 44a of the small piston and the pressure chamber 44a formed for the small piston 44 are formed on the upper portion of the extending piston 46 And the pressure chamber 44a of the small piston communicate with the right and left cylinder flow passages 24 through the connecting portion 50. [

The pilot signal pressure transmitted from another working machine is transmitted to the pressure chamber 42a of the large piston 42 to generate the action force F1 and the pressure chamber 44a of the small piston 44 The pressure P1 of the cylinder fluid passage 24 or the pressure P of the parallel passage 22 acts to generate an action force F3 acting on the small piston 44 and an action force F5 acting on the large poppet 32 , And the acting force F4 is generated in the compensating pressure chamber (46a) by being communicated with the pressure chamber (44a) of the small piston, thereby canceling the working force (F3). The force F2 generated when the large poppet 32 is opened can be substantially canceled with the force F5 generated in the pressure chamber 44a of the small piston 44. [ As a result, the amount of movement of the poppet 30 can be controlled by the action force F1 generated in the pressure chamber 42a of the large piston 42. This makes it possible to control the amount of movement of the poppet 30, It can be controlled only by the action force F1 generated by the pressure.

However, in order to obtain the above conclusion in the structure of the prior art, a small poppet 34 is formed in the large poppet 32, an opening 32b is formed in the tip end 32a of the large poppet, And a hollow (flow path) 36 (not shown) communicating with the pressure chamber 44a of the small piston and communicating with the left and right cylinder flow passages 24 is formed in the small poppet 32, And a connecting portion 50 for communicating the pressure chamber 44a of the small piston with the left and right cylinder flow paths 24 should be formed. The diameter of the small piston 44 and the diameter of the extension piston 46 must be the same and the hollow (flow path) 48 passing through the small piston 44, the large piston 42 and the extension piston 46 is also formed .

As described above, in the hydraulic control apparatus according to the related art, in order to accurately design the movement amount of the poppet (the control amount of the operating oil flow rate), a large and small double poppet and a connection portion communicating with the hollow, A complicated configuration is required such that the diameter of the small piston and the diameter of the extension piston are the same and the hollow is formed through the small piston and the large piston and the extension piston.

Therefore, the conventional hydraulic control apparatus having such a complicated configuration is complicated to manufacture, and has a disadvantage in that the dynamic characteristics of the hydraulic fluid flowing in the interior is deteriorated due to the complicated configuration. Moreover, the manufacturing cost is increased due to the complicated configuration.

SUMMARY OF THE INVENTION An object of the present invention is to provide a variable flow rate control device which can simplify the construction and can simply design a variable flow rate with auxiliary pilot voltage.

It is also an object of the present invention to provide a variable flow control device having improved dynamic characteristics by applying a simple structure using a single poppet.

The present invention is also intended to provide a variable flow control device with a low manufacturing cost by applying a simple structure.

The present invention relates to a hydraulic control apparatus for an internal combustion engine that includes a direction switching valve disposed between a pump and a predetermined working machine for controlling start, stop and direction switching of a work machine by switching a spool when a pilot signal pressure is applied, A flow control valve for controlling the degree of opening and closing of the poppet when the assistant pilot signal pressure is applied, wherein the flow control valve includes a valve body, which is hermetically sealed on the housing portion on which the poppet is formed, And a pilot port for guiding auxiliary pilot signal pressure is formed on the top of the pilot piston, and a pilot port is formed in the main body in a direction toward the poppet An annular pressure portion capable of being pressurized into the pilot piston along the periphery of the pilot piston The sectional area A 'of the annular pressure portion and the sectional area A of the lower portion of the poppet facing the parallel passage are made the same, and the annular pressure portion is connected to the parallel passage in the housing through the passage, And is controlled independently of the pressure in the passageway.

The present invention is further characterized in that a pilot spring for elastically supporting the poppet in a direction toward the parallel passage is further formed in the housing and a pilot spring for elastically supporting the pilot piston in the direction toward the pilot port is further formed in the main body.

Further, the present invention is characterized in that when the sectional area of the pilot piston receiving the auxiliary pilot signal pressure Pi is S, the sectional area of the lower portion of the piston is a, the pressure formed in the space between the poppet and the piston is P A , the pressure in the parallel passage is P B , When the sum of the forces by the springs is F_spring, the equation of force formed around the poppet is expressed by Equation 2 described later.

Further, the present invention is characterized in that the cross-sectional area (a) of the lower portion of the piston is equal to the cross-sectional area (A) of the lower portion of the poppet facing the parallel passage.

Further, the present invention is characterized in that the cross-sectional area (a) of the lower portion of the piston is larger than the cross-sectional area (A) of the lower portion of the poppet facing the parallel passage.

According to the present invention, it is possible to provide a variable flow control device that can simply design a reduction in the flow rate (the amount of movement of the poppet) controlled by the auxiliary pilot voltage with a simple configuration.

Further, according to the present invention, a variable flow control device having improved dynamic characteristics can be provided by applying a simple structure using a single poppet.

Further, according to the present invention, it is possible to provide a variable flow control device having a low manufacturing cost by applying a simple structure.

1 is a sectional view showing an example of a hydraulic control apparatus of the prior art;
2 is a sectional view of a variable flow control device according to an embodiment of the present invention;
FIG. 3 is an enlarged cross-sectional view of the flow control valve portion of the variable flow control device of FIG. 2; FIG.
FIG. 4A is a cross-sectional view showing an example in which the poppet is operated without auxiliary pilot signal pressure in the variable flow control device of FIG. 2; FIG.
FIG. 4B is a sectional view showing an example in which the poppet is operated by receiving auxiliary pilot signal pressure from the variable flow control device of FIG. 2; FIG. And
5 is a hydraulic circuit diagram showing a hydraulic drive system according to another embodiment of the present invention.

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, preferred embodiments of the present invention will be described with reference to the accompanying drawings.

FIG. 2 is a cross-sectional view showing a variable flow control device according to an embodiment of the present invention, and FIG. 3 is an enlarged cross-sectional view showing a flow control valve of the variable flow control device of FIG. 2 and 3, a structure of a variable flow control device 100 according to the present invention will be described.

The variable flow rate control apparatus 100 according to the present invention includes a direction switching valve 110 disposed between a pump and a working machine for supplying hydraulic oil to a working machine for starting, stopping, and changing the direction of the working machine, A poppet 130 formed in the passage 120 and a flow control valve 140 for moving the poppet 130 based on the auxiliary pilot signal pressure Pi. The housing 112 of the directional switching valve 110 is provided with a parallel passage 120 and a pair of left and right cylinder oil passages 122 connected to the parallel passage 120 and a load A passage 124 and a load port 126 connected to the working machine are respectively formed.

The spool 114 is slidable in the left and right direction by the pilot signal pressure applied from the left side with reference to the drawing and the elasticity of the spring 118 disposed on the right side. For example, when the spool 114 slides to the left, The operating oil supplied from the pump through the cylinder 120 is supplied to the corresponding working machine through the left cylinder passage 122, the left load passage 124 and the left load port 126. At this time, Is returned to the tank through the drain port (not shown). On the contrary, when the spool 114 is slid to the right, for example, the hydraulic fluid supplied through the parallel passage 120 flows through the right cylinder block 122, the right cylinder block 124 and the right cylinder block 126 And the working oil in the left cylinder flow path is recovered to the tank through the drain port (not shown).

A poppet 130 is formed at a connection portion between the parallel passage 120 and the cylinder passage 122. The poppet 130 moves upward and downward with reference to the drawing and flows through the parallel passage 120, The flow rate can be selectively controlled (reduced). The flow control valve 140 described above controls the amount of movement of the poppet 130. A poppet spring 152 is disposed on the side of the poppet 130 facing the piston 144 and disposed on the stepped portion formed in the housing 112. The poppet spring 152 is connected to the poppet 130, 130 in the direction toward the parallel passage 120. The poppet spring 152 presses the poppet 130 toward the parallel passage 120 so that the poppet 130 completely closes the connection between the parallel passage 120 and the pair of right and left cylinder flow passages 122 Thereby closing the flow of the operating oil.

The flow control valve 140 of the present invention has a body 142 that is sealed above a portion of the housing 112 where the poppet 130 is formed and is vertically slidable A piston 144, a pilot piston 146, and a pilot port 148, which are sequentially disposed in the direction facing the poppet, are formed. The pilot port 148 serves to guide the auxiliary pilot signal pressure Pi to the upper portion 146a of the pilot piston. The pilot piston 146 is also provided with a pilot spring 154 disposed on the side of the pilot piston 146 that faces the pilot piston 146 and a step formed in the main body 142, Thereby elastically supporting the piston 146 in the direction toward the pilot port 148. The pilot spring 154 serves to press the pilot piston 146 toward the pilot port 148 side when the auxiliary pilot signal pressure is not applied.

An annular pressure portion 146b is further provided in the body 142 along the periphery of the pilot piston 146 which is capable of urging the pilot piston 146 in the direction toward the piston 144, Sectional area A of the lower portion of the poppet 130 facing the parallel passage 120 and the cross sectional area A of the lower portion of the poppet 130 facing the parallel passage 120 are equal to each other and the flow path connecting the annular pressure portion 146b to the parallel passage 120 150 is formed through the housing 112 and the main body 142 so that the opening and closing degree of the poppet 130 can be controlled corresponding to the auxiliary pilot signal pressure Pi irrespective of the pressure in the parallel passage 120 have.

That is, the pressure is applied to the annular pressure portion 146b connected to the parallel passage 120 through the oil passage 150 to eliminate the action of the pressure in the parallel passage 120 with respect to the movement amount (control amount) of the poppet 130, And the sectional area A of the lower portion of the poppet facing the parallel passage 120 and the sectional area A 'of the annular pressure portion 146b around the pilot piston 146 are equal to each other, Can counteract each other with a pair of forces acting in opposite directions to each other.

An example in which a variable flow control device having such a structure operates in an actual hydraulic circuit will be described. 4A and 4B show an example of a flow control valve and a poppet which are changed depending on the presence or absence of auxiliary pilot signal pressure Pi when the directional switching valve is operated by receiving the pilot signal pressure, respectively.

4A shows a flow control valve 140 'in which the hydraulic fluid is pushed upward from the parallel passage 120 when the spool is driven by the pilot signal pressure (not shown). As the poppet 130 'rises upward, the poppet spring 152', which was resiliently supporting the poppet 130 'downward (in the direction toward the parallel passage), is compressed and thus the poppet 130' The parallel passage 120 and the pair of right and left cylinder flow passages 122 are completely opened. At this time, the lifting range of the poppet 130 'can be limited by the upper end of the poppet contacting the stepped portion in the housing 112 where one end of the poppet spring 152' is supported.

4A, the force for pushing up the poppet 130 'is due to the pressure in the parallel passage 120. However, as described above, the parallel passage 120 is formed between the annular pressure portion 146b around the pilot piston 146 And is connected through the oil line 150, so that it also acts downward from the poppet. Thus, the force that actually raises the poppet can be implemented by the difference between the force of the poppet spring 152 ', which resiliently supports the poppet 130, and the force of the pilot spring 154, which supports the pilot piston 146.

4B shows that when the spool is driven (not shown) by the pilot signal pressure, the hydraulic oil from the parallel passage 120 pushes up the poppet 130 '' and at the same time receives the auxiliary pilot signal pressure Pi The pilot piston 146 '' pushes down the piston 144 '' and the poppet 130 '' and consequently the poppet 130 '' moves the parallel passage 120 and the pair of right and left cylinder passages 122 The flow control valve 140 ' ' ' Thus, it can be seen that the amount of movement of the poppet (elevation height) is controlled (reduced) by receiving the auxiliary pilot signal pressure Pi while the spool is operated, thereby reducing the flow rate of the hydraulic fluid supplied to the working machine.

In this variable flow rate control device 100, the movement amount of the poppet can be designed based on a plurality of pressures and the pressure receiving portions subjected to these pressures. For example, the auxiliary pilot signal pressure Pi supplied to the pilot port 148, the pressure in the space between the poppet 130 and the piston 144, the hydraulic oil pressure supplied through the parallel passage 120, It may be based on the cross section of the receiving pressure receiving portions, for example, the upper portion 146a of the pilot piston, the end face of the annular pressure portion 146b, the lower portion of the piston 144 and the lower portion of the poppet portion facing the parallel passage 120 have.

We define an equation of force acting on the poppet to numerically represent the movement of the poppet. First, define the following for each element to obtain the force acting on the poppet.

Auxiliary pilot signal pressure: Pi

The pressure P A formed in the space between the poppet 130 and the piston 144

The pressure in the parallel passage 120: P B

The cross sectional area of the upper portion 146a of the pilot piston 146: S

Sectional area of the lower portion of the poppet 130 facing the parallel passage 120: A

Sectional area of the annular pressure portion 146b: A '

Sectional area of the lower portion of the piston 144: a

Total force applied to each spring: F_spring

Here, the force applied to the spring can be distinguished for the poppet spring 152 and the pilot spring 154, but is simply referred to herein as the sum.

Using the above-described factors and definitions, the equation of force acting on the poppet 130 can be obtained as shown in Equation 1 below. Note that since the annular pressure portion 146b is connected to the parallel passage 120 through the passage 150, the annular pressure portion 146b has the same pressure P B as the pressure in the parallel passage 120.

Figure 112010085540917-pat00001

Applying the fact that the sectional area A 'of the annular pressure portion 146b is equal to the sectional area A of the lower portion of the poppet facing the parallel passage 120 according to the characteristic of the present invention, 2 can be obtained.

Figure 112010085540917-pat00002

As a result, the force acting on the poppet 130 is canceled by canceling the term relating to the pressure P B in the parallel passage 120. Thus, regardless of the pressure in the parallel passage 120, that is, the pressure P B of the operating oil supplied from the pump, Can be easily controlled based on the pressure Pi.

A simpler expression can be obtained by setting the relationship between the cross-sectional area a of the lower portion of the piston 144 and the cross-sectional area A of the lower portion of the poppet 130 facing the parallel passage 120 in the following equation (2) .

For example, if the cross-sectional area a of the lower portion of the piston 144 is formed to be equal to the cross-sectional area A of the lower portion of the poppet 130 facing the parallel passage, the following Equation 3 can be obtained.

Figure 112010085540917-pat00003

At this time, since the value of P_spring is a value determined by the spring constant, the equation of force can be interpreted as a linear equation having the auxiliary pilot signal pressure Pi as a variable.

Further, the cross-sectional area (a) of the lower portion of the piston may be larger than the cross-sectional area (A) of the lower portion of the poppet facing the parallel passage.

As described above, the variable flow rate control device of the present invention is configured to use the auxiliary pilot signal pressure Pi to reduce the movement amount of the poppet, that is, the flow rate of the operating fluid supplied to the working machine, Therefore, the use of a simple structure enables easy manufacture, lowers the related costs, and can exhibit excellent dynamic characteristics through a simple structure.

Next, Fig. 5 shows a hydraulic drive system 200 according to another embodiment of the present invention. 5, the hydraulic drive system 200 of the present invention includes a plurality of working machines, such as a boom 212, a bucket 214, and a traveling motor 216, A plurality of directional control valves 222 and 224 disposed between the pump 210 and the working machines 212, 214 and 216, And 226 are formed in the work machine control means. In addition, the pilot signal pressure is provided through a control unit such as a joystick (not shown) to control whether or not each of the working machines is driven by these directional switching valves so that the start, stop and direction switching Can be implemented.

Reference numeral 202 denotes a center bypass line, reference numeral 204 denotes a parallel line, reference numeral 240 denotes a relief valve, and reference numeral 250 denotes a tank in which hydraulic oil is recovered.

In the hydraulic drive system 200, a flow control valve 230 is connected to the directional control valve 224 disposed corresponding to the bucket 214, and the directional control valve 224 and the flow control valve 230 are connected to each other. Are combined to constitute the variable flow control device 100 of the present invention. The flow control valve 230 is formed with a port (for example, the pilot port 148 in FIG. 2) for receiving auxiliary pilot signal pressure. In addition, reference numeral 232 corresponds to the flow path 150 in Fig.

An example in which the variable flow control device 100 of the present invention is operated on the basis of the hydraulic drive system 200 will be described below.

For example, when the boom and the bucket are required to be loaded more than the bucket in the combined driving of the bucket, the boom 212 and the bucket 214 are provided with the directional switching valves 222 and 224, A signal is provided to simultaneously drive each of the machines (boom, bucket), wherein a portion of the pilot signal provided to the boom is additionally provided as an auxiliary pilot signal Pi to the bucket, thereby reducing the supply flow rate of hydraulic fluid to the bucket , This reduced flow rate is further provided by the boom, which allows the boom to be driven more preferentially than the bucket.

In FIG. 5, the variable flow control valve 100 of the present invention is shown as being disposed in correspondence with the bucket, but the present invention is not limited thereto. That is, the variable flow rate control device of the present invention can be applied not only to a bucket but also to any working machine such as a boom or a traveling motor, It is possible to arbitrarily appropriately control (distribute) the flow rate of the hydraulic fluid supplied from the pump, thereby improving the overall working efficiency.

In addition, since a variable flow control valve having a simple structure can be used, the configuration of the system can be made easier and the circuit having improved dynamic characteristics can be implemented as compared with the case of using the element having the complicated structure.

100: Variable flow control device 110: Directional switching valve
112: housing 114: spool
116: pilot port 118: spring
120: Parallel passage 122:
124: load passage 126: load port
130: Poppet 140: Flow control valve
142: main body 142a: drain port
142b: tank 144: piston
146: Pilot piston 146a: Upper part of the pilot piston
146b: annular pressure portion 148: pilot port
150: Euro
200: Hydraulic drive system 210: Pump
212, 214, 216: a working machine 222, 224, 226: a direction switching valve
230: flow control valve 232:
240: relief valve 250: tank

Claims (5)

A direction switching valve (110) disposed between the pump (210) and a predetermined working machine (214) for controlling start, stop and direction switching of the working machine by switching the spool (114) A parallel port 120 for supplying operating fluid to the housing 112 of the directional control valve 112, a poppet 130 for opening and closing the parallel passage 120, And a flow control valve (140) for controlling the opening and closing degree,
The flow control valve 140 includes a main body 142 that is hermetically sealed over a portion of the housing 112 where the poppet 130 is formed. A pilot piston 146 and a pilot port 148 for guiding the auxiliary pilot signal pressure to the upper portion of the pilot piston,
An annular pressure portion 146b capable of pressing the pilot piston 146 toward the piston 144 is further formed within the body 142 along the periphery of the pilot piston,
Sectional area A 'of the annular pressure portion 146b is equal to a sectional area A of the lower portion of the poppet 130 facing the parallel passage 120 and the annular pressure portion 146b is connected to the housing Wherein the degree of opening and closing of the poppet (130) is controlled irrespective of the pressure of the parallel passage by connecting the parallel passage (120) with the passage (120) through the passage (150). The pilot piston (146) according to claim 1, further comprising a poppet spring (152) for elastically supporting the poppet (130) in a direction toward the parallel passage (120) And a pilot spring (154) for resiliently supporting the valve body in a direction toward the port (148) is further formed in the body (142). The pilot piston (146) according to claim 2, wherein a sectional area of an upper portion (146a) of the pilot piston (146) receiving the auxiliary pilot signal pressure (Pi) is S, a sectional area of the lower portion of the piston When the sectional area of the lower portion of the poppet 130 is A, the pressure formed in the space between the poppet 130 and the piston 144 is P A , and the sum of the forces of the springs 152 and 154 is F_spring , The equation of force formed around the poppet 130 is:
(aA) xP A + F_spring = S x Pi
And a variable flow rate control device. 4. The variable flow rate control device according to claim 3, wherein a sectional area (a) of the lower portion of the piston (144) is equal to a sectional area (A) of the lower portion of the poppet (130) facing the parallel passage (120). 4. The variable flow rate control device according to claim 3, wherein the sectional area (a) of the lower portion of the piston (144) is larger than the sectional area (A) of the lower portion of the poppet (130) facing the parallel passage (120).
KR1020100134300A 2010-12-24 2010-12-24 Flow variable controller apparatus KR101704042B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
KR1020100134300A KR101704042B1 (en) 2010-12-24 2010-12-24 Flow variable controller apparatus

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
KR1020100134300A KR101704042B1 (en) 2010-12-24 2010-12-24 Flow variable controller apparatus

Publications (2)

Publication Number Publication Date
KR20120072519A KR20120072519A (en) 2012-07-04
KR101704042B1 true KR101704042B1 (en) 2017-02-07

Family

ID=46707191

Family Applications (1)

Application Number Title Priority Date Filing Date
KR1020100134300A KR101704042B1 (en) 2010-12-24 2010-12-24 Flow variable controller apparatus

Country Status (1)

Country Link
KR (1) KR101704042B1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105179351B (en) * 2015-09-28 2018-02-02 深圳市嘉润精密模具有限公司 A kind of motor-driven 3 position-5 way valve of plug-in
US10858806B2 (en) 2019-03-12 2020-12-08 Caterpillar Inc. Modular manifold having at least two control modules for controlling operation of at least two hydraulic actuators of an earthmoving machine

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100255013B1 (en) 1996-02-23 2000-05-01 오까노 사다오 Hydraulic pressure control valve mechanism
JP2004360751A (en) 2003-06-03 2004-12-24 Toshiba Mach Co Ltd Hydraulic control device

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0627522B2 (en) * 1984-10-08 1994-04-13 カヤバ工業株式会社 Hydraulic control device
KR100631064B1 (en) * 2001-12-21 2006-10-02 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 hydraulic apparatus for construction heavy equipment

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100255013B1 (en) 1996-02-23 2000-05-01 오까노 사다오 Hydraulic pressure control valve mechanism
JP2004360751A (en) 2003-06-03 2004-12-24 Toshiba Mach Co Ltd Hydraulic control device

Also Published As

Publication number Publication date
KR20120072519A (en) 2012-07-04

Similar Documents

Publication Publication Date Title
US9103355B2 (en) Flow control valve for construction machine
KR101808680B1 (en) Control valve
KR101737901B1 (en) Hydraulic pressure-regulating valve for construction equipment
KR20150036001A (en) Flow control valve for construction machinery
CN107250563B (en) Flow control valve for construction machine
KR101718835B1 (en) Hydraulic control valve for construction machinery
JP6067953B1 (en) Flow control valve
JP2014502711A (en) Holding valve for construction machinery
JP4354419B2 (en) Flow control valve with pressure compensation valve
EP2670987A1 (en) Directional valve equipped with pressure control
US9903396B2 (en) Valve assembly
KR101704042B1 (en) Flow variable controller apparatus
JP2009243669A (en) Holding control valve
JP3549126B2 (en) Directional control valve
US8156960B2 (en) Servo pressure control valve
JP6822930B2 (en) Flow control valve
JP4969541B2 (en) Hydraulic control device for work machine
KR20100075290A (en) Holding valve of hydraulic device
KR102078496B1 (en) Pump gear
US11286962B2 (en) Flow control valve and hydraulic machine including the same
KR100998611B1 (en) Holding Valve for Heavy Construction Equipment
CN108138810B (en) Slide valve
CN114060344B (en) Pilot handle valve, hydraulic system of excavator and control method of hydraulic system
JP5105845B2 (en) Hydraulic control device
KR200182919Y1 (en) Hydraulic system

Legal Events

Date Code Title Description
A201 Request for examination
E902 Notification of reason for refusal
E701 Decision to grant or registration of patent right
GRNT Written decision to grant