KR100212219B1 - Flux distribution device of heavy equipment equipped with multi-working tool - Google Patents

Abstract

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a flow distribution device for heavy equipment with a multi-actuator, wherein the pressurized oil discharged from the main pump (1) is controlled by the main control valve (2), and each sprue (3a) of the main control valve (2), It is supplied to each of the actuators 4a, b, c, d through b, c, d, and parallel lines 6a, 6b to the main bypass line 5 formed in the main control valve 2. The branches are branched, and branch lines 7a, b, c, and d connected to the respective sprues 3a, b, c, and d are branched to the parallel lines 6a and 6b, respectively. A flow rate distribution valve 8 is installed on the parallel lines 6a, 6b between two spouls of b, c, and d so that one port thereof is one of the branch lines 7a, b, c, and d. The other side port is connected to the parallel line (6a, 6b) to selectively determine the priority flow path of the port, the control valve (8) is connected to the flow rate distribution valve (8) flow rate distribution valve ( 8) Preferred Euro Selector It's configured to do that. When operating a plurality of actuators to perform a complex operation, the pressurized oil discharged from the pump is distributed and supplied to each actuator by the flow rate distribution valve 8, so that the operator operates the control valve 8 as necessary to handle each actuator. The speed can be adjusted.

Description

Flow Separator for Heavy Equipments Having Multi-Actuator

The present invention relates to a flow distribution device of a heavy equipment having a plurality of actuators, in particular, heavy equipment equipped with a multi-actuator to be able to arbitrarily control the pressure oil supplied to the actuator in the case of complex operation by operating two actuators at the same time It relates to the operating flow distribution device of the.

In general, heavy equipment used as construction equipment is provided with a plurality of actuators for the desired work. Such a plurality of actuators are usually operated individually to perform a single operation, but if necessary, two or more may be operated to perform a complex operation.

When such a composite work is performed, each actuator is operated by receiving and supplying the pressurized oil discharged from the pump, but the pressurized oil supplied to the actuator is determined only by the load pressure applied to each actuator, thereby increasing the speed of any one actuator. There was a problem that it is not easy to make relatively fast or slow compared to the speed of other actuators.

For example, in the conventional heavy equipment, the pressurized oil discharged from the pump 101 is controlled by the main control valve 102, as shown in FIG. The sprues 103a, b, c, and d of the main control valve 102 are supplied to the actuators 104a, b, c, and d, respectively. c, d) is controlled by a pilot signal pressure to switch the direction of the hydraulic oil supplied via the main bypass line 105 formed in the main control valve 102, the corresponding actuators (104a, b, c, d) Control operation.

In addition, a parallel line 106 is branched to the main bypass line 105, and branch lines 107a and b for supplying pressure oil to the actuators 104a, b, c and d to the parallel line 106 are provided. When c and d are branched and one actuator is operated to block the main bypass line 105, the oil pressure discharged from the pump 101 passes through the parallel lines 106 to each branch line 107a. After being distributed to, b, c, d, it waits at the inlet of each of the spouls 103a, b, c, d, and selects the spoofs 103a, b, c, d in the stand-by state. As the pressure oil is supplied to the actuators 104a, b, c, and d, the composite work is performed, while the branch line 107b and the parallel line 106 are downstream of the swing spring 103b side. When the swing priority valve 108 is installed on the side and the swing and other work are combined, it is controlled through the priority valve control valve 109 to supply the swing motor 104b with the highest priority. It is to be done with the highest swing ever.

However, in the conventional flow distribution method, the pressure flow amount supplied to the actuators 104a, b, c, and d is determined only by the magnitude of the acting load pressure when the combined operation is performed. There was a problem that can not be controlled arbitrarily.

For example, the swing spring 103b for switching the swing motor 104b and the second spring 103c for switching the other actuator 104c are controlled while the swing priority valve 108 is opened. When the hydraulic pressure is switched and supplied to the actuators 104b and 104c and the combined operation is performed, when the load acting on the swing motor 104b is greater than the load acting on the second actuator 102c, swing mower The pressure of the first branch line 107b in communication with the rotor 104b is greater than the pressure of the second branch line 107c in communication with the second actuator 104c, so that the second branch is larger than the first branch line 107b. A relatively large amount of pressure oil is supplied to the line 107c so that the speed of the second actuator 104c becomes relatively faster than the swing motor 104b.

Therefore, according to the conventional flow distribution apparatus as described above, the pressure oil distribution amount to each actuator is determined only by the load pressure applied to each actuator, which makes it difficult to control the relative speed between the actuators.

Accordingly, the present invention has been made to solve the above problems, by adjusting the distribution pressure flow rate supplied to the actuator during the compound operation can be easily adjusted the relative speed between the actuators and multi-operator to perform the swing priority function The purpose is to provide a pressure distribution device for heavy equipment equipped with.

According to the present invention for achieving the above object, the pressurized oil discharged from the pump is controlled in the main control valve, it is supplied to each actuator through each sprue of the main control valve, the main of the main control valve Parallel lines are branched to the bypass line, and branch lines connected to each sprue are branched to the parallel line.

The branch line is connected to the parallel line via a flow rate distribution valve, and a control valve for controlling the flow rate distribution valve is provided between the flow rate distribution valve and the oil tank.

According to the present invention made as described above, since the pressure oil amount to be supplied to each of the actuators is determined in accordance with the switching position of the flow distribution valve when operating a plurality of actuators to perform a complex operation, the driver By operating the control valve, it is possible to adjust the relative speed of each actuator to do the desired work.

1 is a hydraulic circuit diagram and enlarged main part of the flow distribution device of the heavy equipment with a multi-actuator according to the present invention,

Figure 2 is a schematic hydraulic circuit diagram of a heavy equipment for explaining the flow distribution process of heavy equipment with a multi-actuator according to the prior art.

* Explanation of symbols for main parts of the drawings

1: Pump 2: Main Control Valve

3a, b, c, d: Spoul 4a, b, c, d: actuator

5: Main bypass line 6a, 6b: Parallel line

7a, b, c, d: Branch line 8: Flow distribution valve

9: oil tank 10: control valve

11 housing 12 sprue

13: spring 14: first orifice

15: the second orifice 16: the first communication flow

17: second communication path S1, S2: chamber

Hereinafter, with reference to the accompanying drawings, the present invention will be described in detail.

1 is a hydraulic circuit diagram and main portion enlarged view for explaining the flow distribution device of the heavy equipment with a multi-actuator according to the present invention.

As shown in the present invention, the pressurized oil discharged from the pump 1 is controlled by the main control valve 2, and through each of the spouls 3a, b, c, d of the main control valve 2, respectively. The actuators 4a, b, c, and d are supplied to the.

Here, each of the sprues 3a, b, c, d is controlled by an operation lever (not shown) for operating the respective actuators 4a, b, c, d.

In addition, parallel lines 6a and 6b are branched to the main bypass line 5 formed in the main control valve 2, and the sprues 3a, b, c, respectively, to the parallel lines 6a and 6b. The branch lines 7a, b, c, d connected to d) are branched, respectively, so that one actuator 4a, b, c, d is operated so that the main bypass line 5 is blocked. The hydraulic oil distributed in the lines 6a and 6b is supplied to the respective actuators 4a, b, c and d via the branch lines 7a, b, c and d.

Here, the branch line (7b) is connected in communication with the parallel lines (6a, 6b) via a flow distribution valve (8; only one is shown here), the flow distribution valve (8) and the oil tank (9) A control valve 10 for controlling and controlling the flow rate distribution valve 8 is installed, and the flow rate distribution valve 8 is controlled to operate the pump side parallel line 6a as the control valve 10 is operated. The pressure oil flowed into the tank side parallel line 6b and the branch line 7b can be adjusted.

The control valve 10 uses a solenoid valve connected to a power source via a switch (not shown), and when the switch is installed near the driver's seat, the driver simply operates the control valve 10 according to the switch operation. You can do it.

On the other hand, the flow rate distribution valve (8) is a housing (11) in communication with the parallel lines (6a, 6b) and the branch line (7b) and the control valve 10, the housing 11 is slidably embedded It comprises a sprue 12 and a spring 13 elastically installed between the housing 11 and the sprue 12.

In addition, the sprue 12 has a first orifice 14 for communicating the pump side parallel line 6a and the branch lines 7b and c, and the pump side parallel line 6a and the tank side parallel line ( The second orifice 15 and the first communication passage 16 for communicating 6b) and the second communication passage 17 for communicating the second orifice 15 and the control valve 10 are formed. .

Accordingly, the sprue 12 is slid according to the back pressure applied to the first chamber S1 of the housing 11 in which the spring 13 is embedded, and thus the first chamber from the pump side parallel line 6a. The pressure oil flowing into the second chamber S2 formed at the opposite side (S1) to the branch line 7b and the tank side parallel line 6b can be adjusted.

Referring to the process of distributing the flow rate according to the flow distribution device of the present invention made as described above are as follows.

For convenience of explanation, a case in which the first and second actuators 4b and 4c of the actuators 4a, b, c, and d are operated to perform a complex operation will be described.

First, when the combined operation is performed by switching the first and second springs 3b and 3c to control the corresponding first and second actuators 4b and 4c, the switched first actuator 4b is controlled. The main bypass line 5 is blocked by the first spun 3b so that the pressure oil discharged from the pump 1 flows along the pump side parallel line 6a branched from the main bypass line 5. .

The pressure oil flowing through the parallel line 6a is distributed in the flow rate distribution valve 8, and part of the pressure oil is distributed to the first branch line 7b connected to the first spring 3b, and the remaining pressure oil is The pressure oil flowing through the tank side parallel line 6b, which flows through the tank side parallel line 6b, is distributed to the second branch line 7c connected to the second spring 3c.

The pressurized oil distributed to the first and second branch lines 7b and 7c is supplied to the swing motor 4b and the second actuator 4c via the first and second springs 3b and 3c. Accordingly, the two actuators 4b and 4c are operated separately to perform a compound operation.

Here, the amount of oil pressure distributed to the first and second actuators 4b and 4c is determined according to the load pressure applied to the actuators 4b and 4c and the switching position of the flow rate distribution valve 8.

That is, the inverse relationship between the load pressure and the distribution pressure flow rates applied to the first and second actuators 4b and 4c is established, so that a larger amount of pressure oil is supplied to the actuator having a lower load pressure than the actuator having a large load pressure. do.

When the control valve 10 is blocked, the pressure oil flowing into the first chamber S1 through the second communication passage 17 does not flow into the oil tank 9 and increases the pressure in the first chamber S1. The pressure in the first chamber S1 pushes the sprue 12 in the direction in which the spring 13 extends, so that the second chamber S2 is provided with the first orifice 14 and the first. It communicates with the 1st branch line 7b and the tank side parallel line 6b through the communication flow path 16, respectively.

Therefore, a part of the pressurized oil supplied to the second chamber S2 is distributed and supplied to the first branch line 7b via the first orifice 14, and the remaining pressurized oil is passed through the first communication passage 16 to the tank ( 9) It is distributed to the side parallel lines 6a and 6b and is supplied to the second branch lines 7a, b, c and d.

Here, since the cross-sectional area of the first communication passage 16 is relatively larger than the first orifice 14, a relatively large amount of pressure oil is distributed and supplied to the first communication passage 16 than the first orifice 14, The operating speed of the second actuator 4c may be relatively faster than the swing motor 4b.

In addition, when the control valve 10 communicates, the pressure oil introduced into the first chamber S1 through the second communication passage 17 is drained to the oil tank 9 via the control valve 10 so as to be discharged into the first chamber. Since no pressure is formed in S1, the sprue 12 returns to the direction in which the spring 13 is compressed, and the second chamber S2 is in direct communication with the first branch line 7b. The second orifice 15 is connected to the tank side parallel line 6a.

Therefore, a part of the pressurized oil supplied to the second chamber S2 is directly supplied to the first branch line 7b, and the remaining pressurized oil is distributed to the tank side parallel line 6b via the second orifice 15. And then is supplied to the second branch line 7c, whereby a relatively small amount of pressure oil is dispensed and supplied to the second orifice 15, so that the swing motor 4b operates relatively faster than the second actuator 4c. Done.

In this case, when the first actuator 4b is a swing motor for swinging the upper swing body, it is possible to adjust the amount of pressure oil supplied to the swing motor by the flow distribution valve 8, thereby providing a swing priority function. As a result, it is not necessary to additionally install a swing priority valve for swing priority and a swing priority valve switching valve for controlling the valve.

As described above, according to the flow rate distribution device of the heavy equipment equipped with the multi-actuator according to the present invention, the pressure pressure supplied to each actuator and the load pressure acting on each actuator when the multiple operation is performed Since it is determined by the switching position of the flow distribution valve controlled by the control valve, the driver can operate the control valve as needed to control the relative speed of each actuator and perform the desired work as well as the swing priority function. You can do it.

Claims (3)

The pressurized oil discharged from the pump 1 is controlled by the main control valve 2, and the respective actuators 4a, b, c through the sprues 3a, b, c, d of the main control valve 2 are controlled. and d), and parallel lines 6a and 6b are branched to the main bypass line 5 formed in the main control valve 2, and each sprue is connected to the parallel lines 6a and 6b. In the heavy-duty flow distribution device having a multi-actuator having branching lines 7a, b, c, and d connected to 3a, b, c, and d, respectively, A flow rate distribution valve 8 is installed on the parallel lines 6a, 6b between two spouls of the spouls 3a, b, c, and d, and one port thereof has the branch lines 7a, b, c, d) is connected to any one of the other port is connected to the parallel line (6a, 6b) to selectively determine the priority flow path of the port, the control valve 8 is connected to the flow rate distribution valve (8) And the flow distribution device of the heavy equipment with the multi-actuator, characterized in that it is configured to selectively control the preferential flow path of the flow distribution valve (8). 2. The housing (11) according to claim 1, wherein the flow rate distribution valve (8) is in communication with the parallel lines (6a, 6b), the branch line (7b), and the control valve (10); The sprue 12, which is built in to be able to adjust the distribution pressure flow rate to the parallel line 6b and the branch line 7b, and a spring 13 elastically installed between the housing 11 and the sprue 12. Flow distribution device of heavy equipment with a multi-actuator, characterized in that made. 3. The first orifice (14) for communicating the pump side parallel line (6a) and the branch line (7b) to the sprue (12), and the pump side parallel line (6a) and the tank side parallelism. The second orifice 15 and the first communication passage 16 for communicating the line 6b and the second orifice 17 for communicating the second orifice 15 and the control valve 10 are formed. Distributor of heavy equipment with multi-actuators.

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