Closed-circuit hydraulic system for construction machine

Abstract

The present disclosure relates to a closed circuit hydraulic system for a construction machine including a plurality of actuators and a plurality of hydraulic pumps selectively supplying working oil to the plurality of actuators bidirectionally and the closed circuit hydraulic system includes: a charge line selectively connected with a low-pressure side hydraulic line which returns to the hydraulic pump from the actuator among hydraulic lines connecting the hydraulic pumps and the actuators; a charge pump supplying a supplement flow to the charge line; and a variable relief valve selectively changing a normal mode to limit a pressure of the charge line to a predetermined pressure or less and a boost mode to limit the pressure of the charge line to a pressure lower than the pressure of the charge line in the normal mode.

Claims

1. A closed circuit hydraulic system for a construction machine including a plurality of actuators and a plurality of hydraulic pumps selectively supplying working oil to the plurality of actuators bidirectionally, the system comprising: a charge line selectively connected with a low-pressure side hydraulic line which returns to the hydraulic pump from the actuator among hydraulic lines connecting the hydraulic pumps and the actuators; a charge pump supplying a supplement flow to the charge line; a variable relief valve selectively changing a normal mode to limit a pressure of the charge line to a predetermined pressure or less and a boost mode to limit the pressure of the charge line to a pressure lower than the pressure of the charge line in the normal mode; a pair of pilot check valves installed on the hydraulic lines in parallel so that the low-pressure side hydraulic line is in communication with the charge line by receiving a pilot signal from a high-pressure side hydraulic line among the hydraulic lines; and an accumulator provided on the charge line and storing an excessive flow among the supplement flow discharged from the charge pump or supplying an insufficient flow to the hydraulic lines connecting the hydraulic pumps and the actuators, wherein the accumulator includes a first accumulator storing the excessive flow among the supplement flow discharged from the charge pump or supplying the insufficient flow to the hydraulic line in the normal mode, and a second accumulator storing the excessive flow among the supplement flow discharged from the charge pump or supplying the insufficient flow to the hydraulic line in the boost mode, and having a lower discharge pressure than the first accumulator.

2. The closed circuit hydraulic system for a construction machine of claim 1, further comprising: a direction switch valve controlled by the control unit so as to supply the supplement flow discharged from the charge pump to the first accumulator or the second accumulator.

Description

DESCRIPTION OF DRAWINGS

(1) FIG. 1 is a diagram illustrating a hydraulic system for a construction machine having a boosting function in the related art.

(2) FIG. 2 is a diagram illustrating a closed circuit hydraulic system for a construction machine according to an exemplary embodiment of the present disclosure.

(3) FIG. 3 is a diagram illustrating a closed circuit hydraulic system for a construction machine according to another exemplary embodiment of the present disclosure.

(4) FIGS. 4 and 5 are diagrams illustrating an operating state of a closed circuit hydraulic system for a construction machine according to another exemplary embodiment of the present disclosure.

BEST MODE

(5) Hereinafter, exemplary embodiments of the present disclosure will be described in detail with reference to the accompanying drawings. In this process, sizes or shapes of constituent elements illustrated in the drawings, and the like may be exaggerated for clarity and ease of description. In addition, the terms, which are specially defined in consideration of configurations and operations of the present disclosure, may vary depending on the intention or usual practice of a user or an operator. These terms should be defined based on the content throughout the present specification. Further, the spirit of the present disclosure is not limited to the suggested exemplary embodiment, those skilled in the art who understand the spirit of the present disclosure may easily carry out other exemplary embodiments within the scope of the same spirit, and of course, the exemplary embodiments also belong to the scope of the present disclosure.

(6) FIG. 2 is a diagram illustrating a closed circuit hydraulic system for a construction machine according to an exemplary embodiment of the present disclosure. Referring to FIG. 2, a configuration of the closed circuit hydraulic system will be described in detail.

(7) The closed circuit hydraulic system for a construction machine as a system in which a plurality of actuators 110 including a boom, an arm, a bucket, an upper swing body, left and right carriages, and an option device is connected to a plurality of hydraulic pumps 120, respectively to configure a closed circuit and a flow and a flow direction of working oil provided to each actuator 110 are controlled by controlling a swash plate angle of each hydraulic pump 120 is configured to include a charge line 100, a charge pump 200, a variable relief valve 400, a pilot check valve 160, a control unit 500, and the like.

(8) The charge line 100 which is selectively connected with a low-pressure side hydraulic line 130 which returns to the hydraulic pump 120 from the actuator 110 among hydraulic lines 130 connecting the hydraulic pumps 120 and the actuators 110 serves to supply an insufficient flow by a difference in cylinder dimension among the actuators 110 to the hydraulic line 130 or discharge an excessive flow of the hydraulic line 130 due to a characteristic of the closed circuit hydraulic system.

(9) The charge pump 200 discharges a supplement flow and supplies the discharged supplement flow to the charge line 100 and the variable relief valve 400 selectively changes a mode so that the construction machine operates in a normal mode or a boost mode.

(10) That is, the variable relief valve 400 limits the pressure of the charge line 100 to a predetermined pressure or less when the construction machine operates in the normal mode and according to the exemplary embodiment of the present disclosure, the variable relief valve 400 operates at a pressure of approximately 20 to 30 bar in the normal mode.

(11) Meanwhile, there is a case in which the construction machine such as the excavator, or the like needs to excavate a large rock or pun a lot of soil in the bucket unexpectedly while excavating stones having a relatively small size in a quarry and in this case, a boosting button is pressed, which is provided in the joystick, and the like that is configured to implement the boosting function in order to temporarily exert the large force.

(12) In this case, the variable relief valve 400 changes a set pressure of the charge line 100 to a lower pressure than the set pressure in the normal mode to implement the boost mode.

(13) That is, the charge line 100 is connected to the low-pressure side hydraulic line 130 among the hydraulic lines and the variable relief valve 400 increases thrust of a cylinder or torque of a hydraulic motor by reducing a pressure applied in an opposite direction to an actuation direction of the cylinder or hydraulic motor that actuates each actuator 110 to implement a boosting function and according to the exemplary embodiment of the present disclosure, the variable relief valve 400 operates at a pressure less than approximately 10 bar in the boost mode.

(14) One pair of pilot check valves 160 which are connected to the hydraulic line 130 in parallel receive a pilot signal of a high-pressure side hydraulic line 130 among the hydraulic lines 130 to connect the low-pressure side hydraulic line 130 to the charge line 100.

(15) Accordingly, according to the set pressure of the variable relief valve 400, the low-pressure side hydraulic line 130 between the charge line 100 and the hydraulic line 130 maintains the same pressure.

(16) The control unit 500 changes the set pressure of the variable relief valve 400 according to a control signal generated when a worker operates an operating unit such as the joystick or a pedal. That is, when the worker intends to change the normal mode to the boost mode, the control unit 500 controls the variable relief valve 400 according to a boosting operation of the worker.

(17) FIG. 3 is a diagram illustrating a closed circuit hydraulic system for a construction machine according to another exemplary embodiment of the present disclosure. A configuration of the closed circuit hydraulic system is described in detail with reference to FIG. 3, and description of the same configuration as the closed circuit hydraulic system according to the exemplary embodiment of the present disclosure will be omitted.

(18) The closed circuit hydraulic system according to another exemplary embodiment of the present disclosure is configured to further include an accumulator 300 and a direction switch valve 600 as illustrated in FIG. 3 and the accumulator 300 is provided on the charge line 100 to store an excessive flow among the supplement flow discharged from the charge pump 200 or supply an insufficient flow to the hydraulic line 130.

(19) That is, the supplement flow discharged from the charge pump 200 is supplied to the accumulator 300 and the excessive flow among the supplement flow supplied to the accumulator 300 is discharged to a tank T through the variable relief valve 400, and as a result, the charge line 100 is maintained at the set pressure of the variable relief valve 400.

(20) In detail, the accumulator 300 is configured to include a first accumulator 310 and a second accumulator 320 and in the normal mode, the supplement flow discharge from the charge pump 200 is supplied to the first accumulator 310 and in the boost mode, the supplement flow discharged from the charge pump 200 is supplied to the second accumulator 320.

(21) That is, the first accumulator 310 stores the excessive flow among the supplement flow discharged from the charge pump 200 or supplies the insufficient flow to the hydraulic line 130 in the normal mode and the second accumulator 320 stores the excessive flow among the supplement flow discharged from the charge pump 200 or supplies the insufficient flow to the hydraulic line 130 and has a lower discharge pressure than the first accumulator 310 in the boost mode.

(22) According to another exemplary embodiment of the present disclosure, since the set pressure of the variable relief valve 400 in the normal mode is higher than the set pressure of the variable relief valve 400 in the boost mode, the accumulator 300 is divided into the high-pressure first accumulator 310 and the low-pressure second accumulator 320 and the control unit 500 reduces the set pressure of the variable relief valve 400 and supplies the supplement flow discharged from the charge pump 200 to the second accumulator 320 in the boost mode.

(23) The direction switch valve 600 controls a flow direction of the supplement flow so that the supplement flow discharged from the charge pump 200 is supplied to the first accumulator 310 or the second accumulator 320 and the control unit 500 controls the direction switch valve 600.

(24) In detail, in the normal mode, the control unit 500 sets the set pressure of the variable valve 400 to approximately 20 to 30 bar which is a predetermined pressure and controls the direction switch valve 600 so as to supply the supplement flow discharged from the charge pump 200 to the first accumulator 310.

(25) On the contrary, in the boost mode, the control unit 500 sets the set pressure of the variable relief valve 400 to a pressure less than approximately 10 bar which is lower than the predetermined pressure and controls the direction switch valve 600 so as to supply the supplement flow discharged from the charge pump 200 to the second accumulator 320.

(26) FIGS. 4 and 5 are diagrams illustrating an operating state of a closed circuit hydraulic system for a construction machine according to an exemplary embodiment of the present disclosure. An operating process of implementing the boosting function in the closed circuit hydraulic system will be described in detail with reference to FIGS. 4 and 5.

(27) FIG. 4 is a diagram illustrating a state in which the cylinder of the actuator 110 extends when the closed circuit hydraulic system operates in the normal mode.

(28) Referring to FIG. 4, in the normal mode, the control unit 500 controls the direction switch valve 600 so as to connect the charge pump 200 and the first accumulator 310 and controls the variable relief valve 400 so that the set pressure of the variable relief valve 400 is approximately 20 to 30 bar which is the predetermined pressure.

(29) In this case, the supplement flow discharged from the charge pump 200 is supplied to the first accumulator 310, the excessive flow is discharged to the tank T through the variable relief valve 400, and the charge line 100 is maintained at the set pressure of the variable relief valve 400.

(30) In addition, in the normal mode, when the cylinder of the actuator 110 extends, the discharge flow of the hydraulic pump 120 is supplied to a head of the cylinder and a high pressure is formed on the discharge line 140 side among the hydraulic lines 130 by a cylinder load.

(31) A high-pressure pilot signal formed on the discharge line 140 side actuates the check valve 160 connected with a low-pressure supply line 150 among the hydraulic lines 130 between the pair of check valves 160 to connect the supply line 150 and the charge line 100, and as a result, the charge line 100 and the supply line 150 maintain the same pressure.

(32) In this case, maximum thrust of the cylinder of the actuator 110 becomes a value acquired by subtracting force at the cylinder load side from force at the cylinder head side.

(33) FIG. 5 is a diagram illustrating a state in which the cylinder of the actuator 110 extends when the closed circuit hydraulic system operates in the boost mode. Referring to FIG. 5, when the normal mode is changed to the boost mode in order to temporarily exert large force, the control unit 500 controls the direction change valve 600 so as to connect the charge pump 200 and the second accumulator 320 and controls the variable relief valve 400 to operate so that the set pressure of the variable relief valve 400 is at a pressure less than approximately 10 bar which is the pressure lower than the predetermined pressure.

(34) In this case, the supplement flow discharged from the charge pump 200 is supplied to the second accumulator 320, the excessive flow is discharged to the tank T through the variable relief valve 400, and the charge line 100 is maintained at the set pressure lower than the predetermined pressure of the variable relief valve 400.

(35) In addition, in the boost mode, when the cylinder of the actuator 110 extends, the discharge flow of the hydraulic pump 120 is supplied to the head of the cylinder and the high pressure is formed on the discharge line 140 side among the hydraulic lines 130 by the cylinder load.

(36) The high-pressure pilot signal formed on the discharge line 140 side actuates the check valve 160 connected with the low-pressure supply line 150 among the hydraulic lines 130 between the pair of check valves 160 to connect the supply line 150 and the charge line 100, and as a result, the charge line 100 and the supply line 150 maintain the same pressure as the set pressure lower the predetermined pressure of the variable relief 400.

(37) In this case, the maximum thrust of the cylinder of the actuator 110 becomes a value acquired by subtracting the force at the cylinder load side from the force at the cylinder head side and the force applied to the cylinder head side in the normal mode is the same as that in the boost mode, but the force applied to the cylinder load side in the boost mode is reduced to implement the boosting function.

(38) That is, the variable relief valve 400 reduces pressure applied in an opposite direction to an extension direction of the cylinder which actuates each actuator 110, that is, the force applied to the cylinder load side to implement the boosting function to increase the thrust of the cylinder.

(39) Meanwhile, when the cylinder extends in the closed circuit hydraulic system according to the exemplary embodiment of the present disclosure illustrated in FIGS. 4 and 5, the normal mode or the boost mode is described, but when the cylinder is contracted, contrary to this, a pressure applied in an opposite direction to a contraction direction of the cylinder, that is, the force applied to the cylinder head is reduced to implement the boosting function to increase the thrust of the cylinder.

(40) In addition, while the implement of the boosting function is described in the closed circuit hydraulic system according to the exemplary embodiment of the present disclosure illustrated in FIGS. 4 and 5, the actuator 110 is provided as the cylinder as an example, but even when the actuator 110 is provided as the hydraulic motor, it is apparent that the closed circuit hydraulic system of the present disclosure is similarly actuated.

(41) Further, according to the exemplary embodiment of the present disclosure, the accumulator 300 is divided into the first accumulator 310 and the second accumulator 320 and the direction switch valve 600 that controls the flow direction of the flow discharged from the charge pump 200 is provided, but since a core feature of the present disclosure is that the pressure applied in the opposite direction to the actuation direction of the cylinder or the hydraulic motor of each actuator 110 is reduced by varying the set pressure of the variable relief valve 400 to implement the boosting function, a single accumulator may be used and in this case, it is apparent that the direction switch valve need not be provided.

(42) The exemplary embodiments of the present disclosure have been described hereinabove, but they are just illustrative, and it would be appreciated by those skilled in the art that various modifications and equivalent exemplary embodiments may be made therefrom. Accordingly, the true technical scope of the present disclosure should be defined by the appended claims.

DESCRIPTION OF MAIN REFERENCE NUMERALS OF DRAWINGS

(43) 100: Charge line

(44) 110: Actuator

(45) 120: Hydraulic pump

(46) 130: Hydraulic line

(47) 160: Check valve

(48) 200: Charge pump

(49) 300: Accumulator

(50) 310: First accumulator

(51) 320: Second accumulator

(52) 400: Variable relief valve

(53) 500: Control unit

(54) 600: Direction switch valve