JP2017062010A - Fluid pressure control device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enable a stable operation of a cylinder.SOLUTION: A fluid pressure control device is equipped with: a switch valve 22 which switches an operation of an operation check valve 21 by operating in cooperation with a control valve 6 by pilot pressure supplied through a pilot control valve 9; a relief valve 41 which opens when pressure in a load side pressure chamber 2a reaches predetermined pressure; and a relief discharge passage 77 which leads a relief fluid discharged from the relief valve 41 to a tank T. The switch valve 22 is equipped with a piston adding thrust on a spool by receiving the pilot pressure on a back surface, a drain chamber defined by the spool and the piston, and drain passages 76a and 76b communicating the drain chamber and the spring chamber to the relief discharge passage 77. The relief fluid discharged from the relief valve 41 is discharged to the tank T through the relief discharge passage 77 so as not to operate the switch valve 22.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a fluid pressure control device that controls the operation of a hydraulic working device.

  As a hydraulic control device that controls the operation of a hydraulic working device, Patent Document 1 discloses a cylinder device, a control valve that controls expansion and contraction of the cylinder device, and a load holding valve provided between the cylinder device and the control valve. The thing provided with is disclosed. The load holding valve includes a pilot check valve, a switching valve for releasing the check function of the pilot check valve, and a relief valve that opens when the load pressure in the bottom side pressure chamber of the cylinder device increases.

  The switching valve includes a pilot chamber to which a pilot pressure is guided and a spool that is moved by the pilot pressure in the pilot chamber. The end of the spool does not directly face the pilot chamber, but the end of the sub-spool provided adjacent to the spool.

  When the load pressure in the bottom side pressure chamber of the cylinder device rises and the relief valve opens, a relief back pressure is generated upstream of the orifice provided downstream of the relief valve, and the relief back pressure is generated in the pilot chamber of the switching valve. Between the spool and the sub spool. As a result, the spool moves to switch the switching valve, the check function of the pilot check valve is released, and the pressure in the bottom side pressure chamber decreases.

JP 2000-220603 A

  In the hydraulic control device disclosed in Patent Document 1, when the cylinder device is contracted, the operator of the hydraulic excavator manually operates the operation lever to introduce the pilot pressure into the pilot chamber of the switching valve. The pilot pressure acts on the sub spool, and the sub spool applies thrust to the spool, so that the spool is opened, the check function of the pilot check valve is released, and the cylinder device is contracted. On the other hand, when the load pressure in the bottom pressure chamber of the cylinder device rises and the relief valve opens, the relief back pressure generated upstream of the orifice provided downstream of the relief valve is guided between the spool and the sub-spool. Acting on the spool, and thrust is applied to the spool. Thus, when the pilot pressure is guided to the pilot chamber by the operator operation and the spool is moved, thrust is applied to the spool via the sub spool, while the relief back pressure is directly applied to the spool when the relief valve is opened. Act on.

  Here, when the relief valve is opened in a state where the pilot pressure is guided to the pilot chamber by an operator operation and the spool is open, the relief back pressure is guided between the spool and the sub-spool. The thrust due to the pilot pressure is not transmitted from the sub spool to the spool. When the pressure receiving area of the spool to which the relief back pressure acts is smaller than the pressure receiving area of the sub spool, the spool moves in the closing direction depending on the relief back pressure.

  Therefore, if the relief valve is opened while the operator is operating the operating lever so that the cylinder device is contracted, the spool moves in the closing direction, and the cylinder device intended by the operator A situation in which the contraction speed cannot be obtained may occur.

  The present invention has been made in view of the above problems, and an object of the present invention is to provide a fluid pressure control device that enables stable operation of a cylinder.

  A first aspect of the present invention is a fluid pressure control device that controls the expansion and contraction operation of a cylinder that drives a load, and the load-side pressure chamber and control valve of the cylinder on which the load pressure due to the load acts when the control valve is in a neutral position. And a load holding mechanism provided in the main passage, the load holding mechanism allows the flow of the working fluid from the control valve to the load side pressure chamber, while depending on the back pressure, An operation check valve that allows the flow of working fluid from the load side pressure chamber to the control valve, and a switching valve that operates in conjunction with the control valve by the pilot pressure guided through the pilot control valve and switches the operation of the operation check valve A relief valve that opens when the pressure in the load side pressure chamber reaches a predetermined pressure, and a relief discharge passage that guides the relief fluid discharged from the relief valve to the tank. The switching valve receives a pilot pressure on the back surface and applies a thrust force against the urging force of the urging member to the spool, a drain chamber defined by the spool and the piston, a drain chamber and a spring chamber, and relief discharge. And a drain passage communicating with the passage, wherein the relief fluid discharged from the relief valve is discharged to the tank through the relief discharge passage and does not operate the switching valve.

  In the first invention, since the relief fluid discharged from the relief valve is discharged to the tank through the relief discharge passage and does not operate the switching valve, the operator is operating the operating lever to extend and retract the cylinder. Even when the relief valve is opened, the spool does not move in the closing direction, and the expansion / contraction speed of the cylinder intended by the operator can be obtained.

  According to a second aspect of the present invention, there is provided a throttle for imparting resistance to the fluid passing through the drain passage.

  In the second invention, even when surge pressure is generated in the relief discharge passage when the relief valve is opened, it is possible to suppress the surge pressure from propagating to the spring chamber and the drain chamber. Therefore, malfunction of the spool can be prevented.

  According to a third aspect of the present invention, the relief valve has a larger discharge flow rate than a case where the operation check valve is opened by switching the switching valve with the discharged relief fluid.

  In the third invention, since the relief valve is a large capacity type with a large discharge flow rate, the degree of freedom in design is improved.

  According to the present invention, the cylinder can be stably operated.

It is a figure which shows a part of hydraulic excavator. 1 is a hydraulic circuit diagram of a fluid pressure control device according to an embodiment of the present invention. It is sectional drawing of the load holding mechanism of the fluid pressure control apparatus which concerns on embodiment of this invention. It is a top view of the load holding mechanism of the fluid pressure control device according to the embodiment of the present invention. It is a hydraulic-circuit figure of the fluid pressure control apparatus which concerns on the 1st modification of embodiment of this invention. It is a hydraulic-circuit figure of the fluid pressure control apparatus which concerns on the 2nd modification of embodiment of this invention. It is a hydraulic-circuit figure of the fluid pressure control apparatus which concerns on the 3rd modification of embodiment of this invention. It is a hydraulic-circuit figure of the fluid pressure control apparatus which concerns on the 4th modification of embodiment of this invention. It is a hydraulic circuit diagram which shows the comparative example of embodiment of this invention. It is sectional drawing which shows the comparative example of embodiment of this invention.

  A fluid pressure control apparatus according to an embodiment of the present invention will be described with reference to the drawings.

  The fluid pressure control device controls the operation of a hydraulic working device such as a hydraulic excavator. In this embodiment, the fluid pressure control device controls the expansion / contraction operation of the cylinder 2 that drives the arm (load) 1 of the hydraulic excavator shown in FIG. The hydraulic control device will be described.

  First, the hydraulic circuit of the hydraulic control device will be described with reference to FIG.

  The cylinder 2 has a cylindrical cylinder tube 2c, a piston 2d that is slidably inserted into the cylinder tube 2c and divides the cylinder tube 2c into a rod side chamber 2a and an anti-rod side chamber 2b, and one end connected to the piston 2d. A rod 2e having the other end extending outside the cylinder tube 2c and connected to the arm 1;

  An engine is mounted on the hydraulic excavator, and a pump 4 as a fluid pressure supply source and a pilot pump 5 as a pilot pressure supply source are driven by the power of the engine.

  The hydraulic control device includes a control valve 6 that controls the supply of hydraulic oil from the pump 4 to the cylinder 2, and a pilot control valve 9 that controls the pilot pressure guided from the pilot pump 5 to the control valve 6.

  The control valve 6 and the rod side chamber 2 a of the cylinder 2 are connected by a first main passage 7, and the control valve 6 and the non-rod side chamber 2 b of the cylinder 2 are connected by a second main passage 8.

  The control valve 6 is operated by the pilot pressure guided from the pilot pump 5 to the pilot chambers 6a and 6b through the pilot control valve 9 when the operator of the hydraulic excavator manually operates the operation lever 10.

  Specifically, when the pilot pressure is led to the pilot chamber 6a, the control valve 6 is switched to the position 6A, and hydraulic oil is supplied from the pump 4 to the rod side chamber 2a through the first main passage 7, The hydraulic oil in the non-rod side chamber 2 b is discharged to the tank T through the second main passage 8. As a result, the cylinder 2 contracts and the arm 1 moves up in the direction of the arrow 80 shown in FIG.

  On the other hand, when the pilot pressure is guided to the pilot chamber 6b, the control valve 6 is switched to the position 6B, the hydraulic oil is supplied from the pump 4 to the anti-rod side chamber 2b through the second main passage 8, and the rod side chamber The hydraulic oil 2 a is discharged to the tank T through the first main passage 7. As a result, the cylinder 2 is extended and the arm 1 is lowered in the direction of the arrow 81 shown in FIG.

  When the pilot pressure is not led to the pilot chambers 6a and 6b, the control valve 6 is in the position 6C, the supply and discharge of the hydraulic oil to and from the cylinder 2 is shut off, and the arm 1 is kept stopped.

  In this way, the control valve 6 has three positions: a contracted position 6A for contracting the cylinder 2, an extending position 6B for extending the cylinder 2, and a neutral position 6C for holding the load of the cylinder 2. The supply / discharge of the hydraulic oil is switched to control the expansion / contraction operation of the cylinder 2.

  Here, as shown in FIG. 1, when the control valve 6 is switched to the neutral position 6C and the movement of the arm 1 is stopped while the bucket 13 is lifted, the cylinder 2 A force in the direction of extension acts on. Thus, in the cylinder 2 that drives the arm 1, the rod side chamber 2a becomes a load side pressure chamber in which the load pressure acts when the control valve 6 is in the neutral position 6C.

  A load holding mechanism 20 is provided in the first main passage 7 connected to the rod side chamber 2a which is a load side pressure chamber. The load holding mechanism 20 holds the load pressure of the rod side chamber 2a when the control valve 6 is in the neutral position 6C, and is fixed to the surface of the cylinder 2 as shown in FIG.

  In the cylinder 15 that drives the boom 14, the anti-rod side chamber 15b serves as a load-side pressure chamber. Therefore, when the load holding mechanism 20 is provided in the boom 14, a load is applied to the main passage connected to the anti-rod side chamber 15b. A holding mechanism 20 is provided (see FIG. 1).

  The load holding mechanism 20 operates in conjunction with the operation check valve 21 provided in the first main passage 7 and the control valve 6 by the pilot pressure guided to the pilot chamber 23 through the pilot control valve 9. And a switching valve 22 for switching the operation.

  The operation check valve 21 includes a valve body 24 for opening and closing the first main passage 7, a seat portion 28 on which the valve body 24 is seated, a back pressure chamber 25 defined on the back surface of the valve body 24, and a valve body 24. A passage 26 that is formed and constantly guides the hydraulic oil in the rod side chamber 2a to the back pressure chamber 25 is provided. The passage 26 is provided with a throttle 26a.

  The first main passage 7 includes a cylinder-side first main passage 7 a that connects the rod-side chamber 2 a and the operation check valve 21, and a control valve-side first main passage 7 b that connects the operation check valve 21 and the control valve 6. .

  The valve body 24 includes a first pressure receiving surface 24a on which the pressure of the control valve side first main passage 7b acts, and a second pressure receiving surface 24b on which the pressure of the rod side chamber 2a acts through the cylinder side first main passage 7a. It is formed.

  A spring 27 as a biasing member that biases the valve body 24 in the valve closing direction is accommodated in the back pressure chamber 25. The pressure in the back pressure chamber 25 and the urging force of the spring 27 act in the direction in which the valve body 24 is seated on the seat portion 28.

  When the valve body 24 is seated on the seat portion 28, the operation check valve 21 functions as a check valve that blocks the flow of hydraulic oil from the rod side chamber 2 a to the control valve 6. That is, the operation check valve 21 prevents the hydraulic oil in the rod side chamber 2a from leaking, maintains the load pressure, and maintains the arm 1 in a stopped state.

  The load holding mechanism 20 further bypasses the operating check valve 21 for the hydraulic oil in the rod side chamber 2a to the control valve side first main passage 7b, and supplies the hydraulic oil in the back pressure chamber 25 to the control valve side. A back pressure passage 31 that leads to the first main passage 7b.

  The switching valve 22 is provided in the bypass passage 30 and the back pressure passage 31, switches the communication of the bypass passage 30 and the back pressure passage 31 with respect to the control valve side first main passage 7b, and operates the meter-out side when the cylinder 2 is extended. The flow of hydraulic oil in the first main passage 7 is controlled.

  The switching valve 22 has three ports: a first supply port 32 communicating with the bypass passage 30, a second supply port 33 communicating with the back pressure passage 31, and a discharge port 34 communicating with the control valve side first main passage 7b. Have. In addition, the switching valve 22 has three positions: a cutoff position 22A, a first communication position 22B, and a second communication position 22C.

  When pilot pressure is introduced into the pilot chamber 23 to the pilot chamber 6 b of the control valve 6, pilot pressure of the same pressure is introduced at the same time. That is, when the control valve 6 is switched to the extended position 6B, the switching valve 22 is also switched to the first communication position 22B or the second communication position 22C.

  More specifically, when the pilot pressure is not guided to the pilot chamber 23, the switching valve 22 maintains the cutoff position 22A by the urging force of the spring 36. At the blocking position 22A, both the first supply port 32 and the second supply port 33 are blocked.

  When a pilot pressure not lower than the first predetermined pressure and lower than the second predetermined pressure is introduced into the pilot chamber 23, the switching valve 22 is switched to the first communication position 22B. The first supply port 32 communicates with the discharge port 34 at the first communication position 22B. As a result, the hydraulic oil in the rod side chamber 2a is guided from the bypass passage 30 to the control valve side first main passage 7b through the switching valve 22. That is, the hydraulic oil in the rod side chamber 2a is guided to the control valve side first main passage 7b, bypassing the operation check valve 21. At this time, the throttle 37 gives resistance to the flow of hydraulic oil. The second supply port 33 is kept in a blocked state.

  When the pilot pressure equal to or higher than the second predetermined pressure is introduced into the pilot chamber 23, the switching valve 22 is switched to the second communication position 22C. At the second communication position 22 </ b> C, the first supply port 32 communicates with the discharge port 34, and the second supply port 33 also communicates with the discharge port 34. As a result, the hydraulic oil in the back pressure chamber 25 is guided from the back pressure passage 31 to the control valve side first main passage 7 b through the switching valve 22. At this time, the hydraulic oil in the back pressure chamber 25 bypasses the throttle 37, is led to the control valve side first main passage 7 b, and is discharged from the control valve 6 to the tank T. As a result, a differential pressure is generated before and after the restrictor 26a, and the pressure in the back pressure chamber 25 is reduced. Therefore, the force in the valve closing direction acting on the valve body 24 is reduced, and the valve body 24 is removed from the seat portion 28. The function as the check valve of the operation check valve 21 is released.

  A relief passage 40 is branched and connected upstream of the switching valve 22 in the bypass passage 30. The relief passage 40 is provided with a relief valve 41 that opens when the pressure in the rod side chamber 2a reaches a predetermined pressure, allows the hydraulic oil to pass, and releases the hydraulic oil in the rod side chamber 2a. The relief pressure oil discharged from the relief valve 41 is discharged to the tank T through a relief discharge passage 77 that connects the relief valve 41 and the tank T.

  A relief valve 43 that opens when the pressure in the control valve side first main passage 7b reaches a predetermined pressure is connected to the control valve side first main passage 7b.

  Next, the switching valve 22 will be described in detail mainly with reference to FIGS. FIG. 3 is a cross-sectional view of the load holding mechanism 20 and shows a state where the pilot pressure is not guided to the pilot chamber 23 and the switching valve 22 is in the cutoff position 22A. FIG. 4 is a plan view of the load holding mechanism 20. 3 and 4, the same reference numerals as those shown in FIG. 2 denote the same components as those shown in FIG.

  The switching valve 22 is incorporated in the body 60. A spool hole 60a is formed in the body 60, and a substantially cylindrical sleeve 61 is inserted into the spool hole 60a. A spool 56 is slidably incorporated in the sleeve 61.

  A spring chamber 54 is defined by a cap 57 on the side of the one end surface 56 a of the spool 56. The spring chamber 54 is connected to the first drain passage 76 a through a notch 61 a formed in the end surface of the sleeve 61. The first drain passage 76 a is connected to the relief discharge passage 77. Accordingly, the hydraulic oil that has leaked into the spring chamber 54 is discharged to the tank T through the first drain passage 76 a and the relief discharge passage 77.

  The spring chamber 54 accommodates a spring 36 as a biasing member that biases the spool 56. The spring chamber 54 has an annular first spring receiving member 45 in which an end surface abuts on one end surface 56a of the spool 56 and a pin portion 56c formed to protrude from the one end surface 56a of the spool 56 is inserted into the hollow portion. And the second spring receiving member 46 disposed near the bottom of the cap 57 are accommodated. The spring 36 is interposed between the first spring receiving member 45 and the second spring receiving member 46 in a compressed state, and biases the spool 56 in the valve closing direction via the first spring receiving member 45.

  The axial position of the second spring receiving member 46 in the spring chamber 54 is set by the front end portion of the adjusting bolt 47 that penetrates and is screwed into the bottom portion of the cap 57 abutting against the back surface of the second spring receiving member 46. Is done. By screwing the adjusting bolt 47, the second spring receiving member 46 moves in a direction approaching the first spring receiving member 45. Therefore, the initial spring load of the spring 36 can be adjusted by adjusting the screwing amount of the adjusting bolt 47. The adjusting bolt 47 is fixed with a nut 48.

  On the side of the other end surface 56b of the spool 56, the pilot chamber 23 is defined by a piston hole 60b formed in communication with the spool hole 60a and a cap 58 that closes the piston hole 60b. Pilot pressure is guided to the pilot chamber 23 through a pilot passage 52 formed in the body 60. In the pilot chamber 23, a piston 50 that receives pilot pressure on the back surface and applies thrust to the spool 56 against the urging force of the spring 36 is slidably accommodated.

  A drain chamber 51 is defined by the spool 56 and the piston 50 in the piston hole 60b. The drain chamber 51 is connected to the second drain passage 76 b, and the second drain passage 76 b is connected to the relief discharge passage 77. Accordingly, the hydraulic oil that has leaked into the drain chamber 51 is discharged to the tank T through the second drain passage 76 b and the relief discharge passage 77.

  The piston 50 has a sliding portion 50a whose outer peripheral surface slides along the inner peripheral surface of the piston hole 60b, and a tip portion which is formed with a smaller diameter than the sliding portion 50a and faces the other end surface 56b of the spool 56. 50 b and a base end portion 50 c that is formed in a smaller diameter than the sliding portion 50 a and faces the tip end surface of the cap 58.

  When pilot pressure oil is supplied into the pilot chamber 23 through the pilot passage 52, pilot pressure acts on the back surface of the base end portion 50c and the annular back surface of the sliding portion 50a. As a result, the piston 50 moves forward, and the tip end portion 50 b comes into contact with the other end surface 56 b of the spool 56 to move the spool 56. As described above, the spool 56 receives the thrust of the piston 50 generated based on the pilot pressure acting on the back surface of the piston 50 and moves against the urging force of the spring 36. Even when the back surface of the base end portion 50c is in contact with the front end surface of the cap 58, the base end portion 50c is smaller in diameter than the sliding portion 50a, and the pilot pressure is applied to the annular back surface of the sliding portion 50a. Therefore, the piston 50 can move forward.

  Since one end of the piston 50 faces the pilot chamber 23 and the other end faces the drain chamber 51 connected to the tank T, the thrust of the piston 50 generated based on the pilot pressure in the pilot chamber 23 is efficiently spooled. 56.

  Each of the drain chamber 51 and the spring chamber 54 communicates with the relief discharge passage 77 through the first drain passage 76a and the second drain passage 76b. The relief discharge passage 77 is formed in communication with the drain port 53 that opens to the outer surface of the body 60. The drain port 53 is connected to the tank T through a pipe 55 (see FIG. 2). Since both the drain chamber 51 and the spring chamber 54 communicate with the tank T, when the switching valve 22 is in the shut-off position 22A, atmospheric pressure acts on both ends of the spool 56, and the spool 56 moves unintentionally. Such a situation is prevented.

  As described above, the relief pressure oil discharged from the relief valve 41 and the drain in the drain chamber 51 and the spring chamber 54 merge and are discharged to the tank T through the drain port 53 and the pipe 55.

  The spool 56 stops at a position where the biasing force of the spring 36 acting on the one end face 56 a and the thrust force of the piston 50 acting on the other end face 56 b are balanced, and the switching position of the switching valve 22 is at the stop position of the spool 56. Is set.

  The sleeve 61 includes a first supply port 32 communicating with the bypass passage 30 (see FIG. 2), a second supply port 33 communicating with the back pressure passage 31 (see FIG. 2), and the control valve side first main passage 7b. Three ports of the discharge port 34 that communicate with each other are formed.

  The outer peripheral surface of the spool 56 is partially cut out in an annular shape, and the first pressure chamber 64, the second pressure chamber 65, the third pressure chamber 66, and the cutout portion and the inner peripheral surface of the sleeve 61, A fourth pressure chamber 67 is formed.

  The first pressure chamber 64 is always in communication with the discharge port 34.

  The third pressure chamber 66 is always in communication with the first supply port 32. A plurality of throttles 37 communicating the third pressure chamber 66 and the second pressure chamber 65 are formed on the outer periphery of the land portion 72 of the spool 56 as the spool 56 moves against the urging force of the spring 36. .

  The fourth pressure chamber 67 is always in communication with the second pressure chamber 65 through a pressure guide passage 68 formed in the spool 56 in the axial direction.

  When pilot pressure is not guided to the pilot chamber 23, the poppet valve 70 formed on the spool 56 is pressed against the valve seat 71 formed on the inner periphery of the sleeve 61 by the biasing force of the spring 36, and the second pressure Communication between the chamber 65 and the first pressure chamber 64 is blocked. Therefore, the communication between the first supply port 32 and the discharge port 34 is blocked. Thereby, the hydraulic oil in the rod side chamber 2a does not leak to the discharge port 34. This state corresponds to the cutoff position 22A of the switching valve 22. In a state where the poppet valve 70 is seated on the valve seat 71 by the urging force of the spring 36, there is a slight gap between the end surface of the first spring receiving member 45 and the end surface of the sleeve 61. The seat 71 is reliably seated by the biasing force of the spring 36.

  When the pilot pressure is guided to the pilot chamber 23 and the thrust of the piston 50 acting on the spool 56 becomes larger than the biasing force of the spring 36, the spool 56 moves against the biasing force of the spring 36. As a result, the poppet valve 70 moves away from the valve seat 71 and the third pressure chamber 66 and the second pressure chamber 65 communicate with each other through the plurality of throttles 37. Therefore, the first supply port 32 is connected to the third pressure chamber 66 and the second pressure chamber. The exhaust port 34 communicates with the chamber 65 and the first pressure chamber 64. Due to the communication between the first supply port 32 and the discharge port 34, the hydraulic oil in the rod side chamber 2 a is guided to the control valve side first main passage 7 b through the throttle 37. This state corresponds to the first communication position 22B of the switching valve 22.

  When the pilot pressure guided to the pilot chamber 23 increases, the spool 56 further moves against the urging force of the spring 36, and the fourth pressure chamber 67 communicates with the second supply port 33. Accordingly, the second supply port 33 communicates with the discharge port 34 through the fourth pressure chamber 67, the pressure guiding passage 68, the second pressure chamber 65, and the first pressure chamber 64. By the communication between the second supply port 33 and the discharge port 34, the hydraulic oil in the back pressure chamber 25 is guided to the control valve side first main passage 7b. This state corresponds to the second communication position 22C of the switching valve 22.

  Next, the operation of the hydraulic control apparatus will be described mainly with reference to FIGS.

  When the control valve 6 is in the neutral position 6C, the hydraulic oil discharged from the pump 4 is not supplied to the cylinder 2. At this time, since the pilot pressure is not guided to the pilot chamber 23 of the switching valve 22, the switching valve 22 is also in the cutoff position 22A.

  For this reason, the back pressure chamber 25 of the operation check valve 21 is maintained at the pressure of the rod side chamber 2a. Here, the pressure receiving area in the valve closing direction of the valve body 24 (the area of the back surface of the valve body 24) is larger than the area of the second pressure receiving surface 24b that is the pressure receiving area in the valve opening direction. Due to the load acting on the back surface of the valve body 24 and the urging force of the spring 27, the valve body 24 is seated on the seat portion 28. In this way, the operation check valve 21 prevents the hydraulic oil in the rod side chamber 2a from leaking, and the arm 1 is kept stopped.

  When the operation lever 10 is operated and pilot pressure is guided from the pilot control valve 9 to the pilot chamber 6a of the control valve 6, the control valve 6 is switched to the contracted position 6A by an amount corresponding to the pilot pressure. When the control valve 6 is switched to the contracted position 6A, the discharge pressure of the pump 4 acts on the first pressure receiving surface 24a of the operation check valve 21. At this time, since the switching valve 22 is in the cutoff position 22A without pilot pressure being guided to the pilot chamber 23, the back pressure chamber 25 of the operation check valve 21 is maintained at the pressure in the rod side chamber 2a. When the load acting on the first pressure receiving surface 24 a becomes larger than the total load of the load acting on the back surface of the valve body 24 due to the pressure of the back pressure chamber 25 and the urging force of the spring 27, the valve body 24 is It leaves | separates from the sheet | seat part 28. FIG. When the operation check valve 21 is opened in this manner, the hydraulic oil discharged from the pump 4 is supplied to the rod side chamber 2a, and the cylinder 2 contracts. As a result, the arm 1 rises in the direction of the arrow 80 shown in FIG.

  When the operation lever 10 is operated and pilot pressure is guided from the pilot control valve 9 to the pilot chamber 6b of the control valve 6, the control valve 6 switches to the extended position 6B by an amount corresponding to the pilot pressure. At the same time, since the pilot pressure is guided to the pilot chamber 23, the switching valve 22 is switched to the first communication position 22B or the second communication position 22C according to the supplied pilot pressure.

  When the pilot pressure guided to the pilot chamber 23 is not less than the first predetermined pressure and less than the second predetermined pressure, the switching valve 22 is switched to the first communication position 22B. In this case, since the communication between the second supply port 33 and the discharge port 34 is cut off, the back pressure chamber 25 of the operation check valve 21 is maintained at the pressure of the rod side chamber 2a, and the operation check valve 21 is closed. It becomes a state.

  On the other hand, since the first supply port 32 communicates with the discharge port 34, the hydraulic oil in the rod side chamber 2a passes through the throttle 37 from the bypass passage 30 and is guided to the control valve side first main passage 7b, and the control valve 6 To the tank T. Further, since the hydraulic oil discharged from the pump 4 is supplied to the anti-rod side chamber 2b, the cylinder 2 extends. As a result, the arm 1 is lowered in the direction of the arrow 81 shown in FIG.

  Here, the switching valve 22 is switched to the first communication position 22 </ b> B mainly when a crane operation is performed to lower a conveyed product attached to the bucket 13 to a target position. In the crane operation, the cylinder 2 needs to be extended at a low speed and the arm 1 needs to be slowly lowered in the direction of the arrow 81, so the control valve 6 is only slightly switched to the extended position 6B. For this reason, the pilot pressure led to the pilot chamber 6b of the control valve 6 is small, the pilot pressure led to the pilot chamber 23 of the switching valve 22 is not less than the first predetermined pressure and less than the second predetermined pressure, and the switching valve 22 is in the first communication Only switch to position 22B. Therefore, the hydraulic oil in the rod side chamber 2a is discharged through the throttle 37, and the arm 1 descends at a low speed suitable for crane work.

  Further, when the switching valve 22 is in the first communication position 22B, even if a situation occurs such that the control valve side first main passage 7b ruptures and the hydraulic fluid leaks to the outside, it is discharged from the rod side chamber 2a. Since the flow rate of the working oil is limited by the throttle 37, the falling speed of the bucket 13 is suppressed. This function is called metering control. For this reason, before the bucket 13 falls to the ground, the switching valve 22 can be switched to the cutoff position 22A, and the sudden fall of the bucket 13 can be prevented.

  As described above, the throttle 37 is for suppressing the descending speed of the cylinder 2 when the operation check valve 21 is closed, and suppressing the falling speed of the bucket 13 when the control valve side first main passage 7b is ruptured. .

  When the pilot pressure guided to the pilot chamber 23 is equal to or higher than the second predetermined pressure, the switching valve 22 is switched to the second communication position 22C. In this case, since the second supply port 33 communicates with the discharge port 34, the hydraulic oil in the back pressure chamber 25 of the operation check valve 21 is guided to the control valve side first main passage 7 b through the back pressure passage 31 and is controlled. It is discharged from the valve 6 to the tank T. As a result, a differential pressure is generated before and after the restrictor 26a, and the pressure in the back pressure chamber 25 is reduced, so that the force in the valve closing direction acting on the valve body 24 is reduced, and the valve body 24 is separated from the seat portion 28. The function of the operation check valve 21 as a check valve is released.

  In this way, the operation check valve 21 allows the flow of hydraulic oil from the control valve 6 to the rod side chamber 2a, while the flow of hydraulic oil from the rod side chamber 2a to the control valve 6 according to the pressure of the back pressure chamber 25. Works to allow.

  When the operation check valve 21 is opened, the hydraulic oil in the rod side chamber 2a passes through the first main passage 7 and is discharged to the tank T, so that the cylinder 2 extends quickly. That is, when the switching valve 22 is switched to the second communication position 22C, the flow rate of the hydraulic oil discharged from the rod side chamber 2a increases, so the flow rate of the hydraulic oil supplied to the non-rod side chamber 2b increases. The elongation speed is increased. As a result, the arm 1 quickly descends in the direction of the arrow 81.

  The switching valve 22 is switched to the second communication position 22C when excavation work or the like is performed, and the control valve 6 is largely switched to the extended position 6B. For this reason, the pilot pressure led to the pilot chamber 6b of the control valve 6 is large, the pilot pressure led to the pilot chamber 23 of the switching valve 22 becomes equal to or higher than the second predetermined pressure, and the switching valve 22 switches to the second communication position 22C. .

  Next, the operation of this embodiment will be described.

  First, a comparative example of this embodiment will be described with reference to FIGS. 9 and 10, the same reference numerals as those in FIGS. In the comparative example shown in FIGS. 9 and 10, the relief passage 40 is provided with a relief valve 90 that opens when the pressure in the rod side chamber 2a reaches a predetermined pressure and releases the hydraulic oil in the rod side chamber 2a. An orifice 91 is provided in the relief discharge passage 77 that connects the relief valve 90 and the tank T. When the pressure in the rod side chamber 2a reaches a predetermined pressure and the relief valve 90 opens, the relief pressure oil upstream from the orifice 91 discharged from the relief valve 90 is guided to the drain chamber 51 through the second drain passage 76b. Thereby, when the switching valve 22 is switched to the second communication position 22C, the operation check valve 21 is opened, and the pressure of the hydraulic oil in the rod side chamber 2a is reduced.

  In such a comparative example, the pilot pressure is guided to the pilot chamber 23 by the operator's operation, the spool 56 is moved, and the cylinder 2 is operated to extend, so that the pressure in the rod side chamber 2a rises and the relief valve 90 opens. When the valve is operated, the relief pressure oil upstream of the orifice 91 discharged from the relief valve 90 is guided to the drain chamber 51. Since the relief back pressure upstream of the orifice 91 guided to the drain chamber 51 is larger than the pilot pressure guided to the pilot chamber 23, the piston 50 moves away from the spool 56. Therefore, the thrust of the piston 50 generated by the pilot pressure is not transmitted to the spool 56. Further, since the pressure receiving area of the spool 56 on which the pressure of the drain chamber 51 acts is smaller than the pressure receiving area of the piston 50, depending on the magnitude of the relief back pressure upstream of the orifice 91 guided to the drain chamber 51, the spool 56 May move in the closing direction due to the urging force of the spring 36.

  As described above, in the comparative example, when the relief valve 90 is opened while the operator is operating the operation lever to extend the cylinder 2, the spool 56 moves in the closing direction. Therefore, a situation may occur in which the extension speed of the cylinder 2 intended by the operator cannot be obtained.

  On the other hand, in this embodiment, as shown in FIGS. 2 and 3, no orifice is provided in the relief discharge passage 77 that connects the relief valve 41 and the tank T. Therefore, the relief pressure oil discharged from the relief valve 41 is discharged to the tank T through the relief discharge passage 77 and no high pressure acts on the drain chamber 51. Thus, in this embodiment, even if the relief valve 41 is opened, the operation of the switching valve 22 is not affected, and the relief pressure oil discharged from the relief valve 41 does not operate the switching valve 22. More specifically, when the relief valve 41 is opened, a little relief pressure oil is guided to the drain chamber 51 through the second drain passage 76b. However, the relief pressure oil overcomes the thrust of the piston 50 generated by the pilot pressure. Thus, there is no pressure to move the piston 50 away from the spool 56. Therefore, according to the present embodiment, the spool 56 moves in the closing direction even when the relief valve 41 is opened while the operator is operating the operation lever to extend the cylinder 2. The extension speed of the cylinder 2 intended by the operator is obtained.

  As shown in FIG. 2, the relief discharge passage 77 communicates with the second drain port 86 opened on the outer surface of the body 60 through the passage 87. A pipe may be connected to the second drain port 86, and the second drain port 86 and the tank T may be connected via the pipe. With this configuration, the relief pressure oil discharged from the relief valve 41 is also discharged to the tank through the passage 87, so that the flow rate of the relief pressure oil guided to the drain chamber 51 can be reduced. However, in order to reduce the number of pipes connecting the body 60 of the load holding mechanism 20 and the tank T, no pipes are connected to the second drain port 86, and the second drain port 86 is sealed with a plug 88 (see FIG. 4). It is preferable to do this. Further, the drain port 53 is sealed with a plug, a pipe is connected to the second drain port 86, and the relief pressure oil discharged from the relief valve 41 and the drain in the drain chamber 51 and the spring chamber 54 are connected to the second drain port. It may be discharged to the tank T through 86.

  According to the above embodiment, the following effects are obtained.

  Since the relief pressure oil discharged from the relief valve 41 is discharged to the tank T through the relief discharge passage 77 and does not operate the switching valve 22, the operator is operating the operation lever to extend and retract the cylinder 2. Even when the relief valve 41 is opened, the spool 56 does not move in the closing direction, and the expansion / contraction speed of the cylinder 2 intended by the operator can be obtained. Therefore, stable operation of the cylinder 2 is possible.

  In this embodiment, the relief pressure oil discharged from the relief valve 41 joins the drains in the drain chamber 51 and the spring chamber 54 and is discharged to the tank T through the drain port 53 and the pipe 55. Therefore, there is no need to provide a dedicated pipe for leading the relief pressure oil discharged from the relief valve 41 to the tank T, and the number of pipes can be reduced.

  In addition, since the relief pressure oil discharged from the relief valve 41 is discharged to the tank T through the relief discharge passage 77 and hardly guided to the drain chamber 51, the relief back pressure pulsates when the relief valve 41 is opened. However, the pulsation is prevented from propagating to the spool 56. Therefore, the occurrence of vibration is suppressed.

  Further, the relief valve 90 of the comparative example that switches the switching valve 22 by the discharged relief pressure oil and opens the operation check valve 21 has a pressure sufficient to switch the spool 56 of the switching valve 22 to the second communication position 22C. Since it is sufficient to lead to the chamber 51, a small-capacity relief valve with a small discharge flow rate is used. On the other hand, the relief valve 41 of the present embodiment opens when the pressure in the rod side chamber 2a reaches a predetermined pressure, releases the hydraulic oil in the rod side chamber 2a to the tank T, and reduces the pressure in the rod side chamber 2a. Since it is necessary to have a function of lowering, a large-capacity relief valve having a larger discharge flow rate than the relief valve 90 of the comparative example is used. Thus, since the relief valve 41 of this embodiment is a large capacity type | mold, the freedom degree of design improves. Further, since the relief valve 41 is a large capacity type, the pressure in the rod side chamber 2a can be kept at a predetermined pressure even when a surge pressure is generated such that the pressure in the rod side chamber 2a suddenly increases. Therefore, it is possible to prevent the cylinder 2 from being damaged by the surge pressure.

  Next, a modified example of the present embodiment will be described with reference to FIGS.

  In the first modification shown in FIG. 5, as a throttle that provides resistance to the hydraulic oil passing through each of the first drain passage 76 a connected to the spring chamber 54 and the second drain passage 76 b connected to the drain chamber 51. Orifices 82 and 83 are provided. Even if a surge pressure is generated in the relief discharge passage 77 when the relief valve 41 is opened by providing the orifices 82 and 83 in the first drain passage 76 a and the second drain passage 76 b, the spring chamber 54. And it can suppress that surge pressure propagates to the drain chamber 51. Therefore, malfunction of the spool 56 can be prevented.

  In the second and third modifications shown in FIGS. 6 and 7, the method of connecting the first drain passage 76a and the second drain passage 76b to the relief discharge passage 77 is different from the embodiment shown in FIGS. Thus, the connection method of the 1st drain path 76a and the 2nd drain path 76b with respect to the relief discharge path 77 is not limited to a specific structure.

  In the fourth modified example shown in FIG. 8, an orifice 84 is provided as a throttle that provides resistance to the passing hydraulic oil in a confluence drain passage 76c where the first drain passage 76a and the second drain passage 76b merge. With this configuration, only one orifice that suppresses the propagation of surge pressure can be provided.

  Hereinafter, the configuration, operation, and effect of the embodiment of the present invention will be described together.

  In the present embodiment, the fluid pressure control device controls the expansion and contraction operation of the cylinder 2 that drives the arm 1, and is controlled from the control valve 6 that controls the supply of hydraulic oil from the pump 4 to the cylinder 2 and from the pilot pump 5. The pilot control valve 9 for controlling the pilot pressure guided to the valve 6 is connected to the control valve 6 and the rod side pressure chamber 2a of the cylinder 2 on which the load pressure by the arm 1 acts when the control valve 6 is in the neutral position 6C. A main passage 7 and a load holding mechanism 20 provided in the main passage 7. The load holding mechanism 20 allows the flow of hydraulic oil from the control valve 6 to the rod-side pressure chamber 2a, while depending on the back pressure. The operation check valve 21 allowing the flow of hydraulic oil from the rod side pressure chamber 2a to the control valve 6 and the pilot pressure guided through the pilot control valve 9 operate in conjunction with the control valve 6. The switching valve 22 for switching the operation of the operation check valve 21, the relief valve 41 that opens when the pressure in the rod-side pressure chamber 2a reaches a predetermined pressure, and the relief fluid discharged from the relief valve 41 A relief discharge passage 77 that leads to T. The switching valve 22 includes a pilot chamber 23 through which pilot pressure is guided through the pilot control valve 9, a spool 56 that moves according to the pilot pressure in the pilot chamber 23, and a spool 56 A spring chamber 54 in which a spring 36 urging in the valve closing direction is accommodated; a piston 50 which receives pilot pressure on the back surface and applies a thrust force against the urging force of the spring 36 to the spool 56; The partitioned drain chamber 51, the drain chamber 51, and the spring chamber 54 are connected to the relief discharge passage 77. That drain passage 76a, includes a 76 b, the relief pressure oil discharged from the relief valve 41 is discharged to the tank T not operate the switching valve 22 through the relief discharge passage 77.

  In this configuration, the relief pressure oil discharged from the relief valve 41 is discharged to the tank T through the relief discharge passage 77 and does not operate the switching valve 22. Therefore, the operator operates the operation lever so that the cylinder 2 is expanded and contracted. Even when the relief valve 41 is opened during the operation, the spool 56 does not move in the closing direction, and the expansion / contraction speed of the cylinder 2 intended by the operator can be obtained. Therefore, stable operation of the cylinder 2 is possible.

  In this embodiment, the drain passages 76a and 76b are provided with throttles 82 and 83 for imparting resistance to the passing hydraulic fluid.

  In this configuration, even if surge pressure is generated in the relief discharge passage 77 when the relief valve 41 is opened, it is possible to suppress the surge pressure from propagating to the spring chamber 54 and the drain chamber 51. Therefore, malfunction of the spool 56 can be prevented.

  In the present embodiment, the relief valve 41 has a larger discharge flow rate than the case where the switching valve 22 is switched by the discharged relief pressure oil to open the operation check valve 21.

  In this configuration, the relief valve 41 is a large-capacity type with a large discharge flow rate, so the degree of freedom in design is improved.

  The embodiment of the present invention has been described above. However, the above embodiment only shows a part of application examples of the present invention, and the technical scope of the present invention is limited to the specific configuration of the above embodiment. Absent.

DESCRIPTION OF SYMBOLS 1 ... Arm (load), 2 ... Cylinder, 2a ... Rod side pressure chamber (load side pressure chamber), 4 ... Pump (fluid pressure supply source), 5 ... Pilot pump (pilot) Pressure supply source), 6 ... control valve, 7 ... first main passage, 9 ... pilot control valve, 20 ... load holding mechanism, 21 ... operate check valve, 22 ... switching Valve, 23 ... Pilot chamber, 41 ... Relief valve, 50 ... Piston, 51 ... Drain chamber, 53 ... Drain port, 54 ... Spring chamber, 56 ... Spool, 76a ... 1st drain passage, 76b ... 2nd drain passage, 77 ... Relief discharge passage, 82, 83, 84 ... Orifice (throttle)

Claims (3)

A fluid pressure control device that controls expansion and contraction of a cylinder that drives a load,
A control valve for controlling the supply of the working fluid from the fluid pressure supply source to the cylinder;
A pilot control valve for controlling a pilot pressure led to the control valve from a pilot pressure supply source;
A main passage that connects the control valve and the load side pressure chamber of the cylinder, to which a load pressure due to a load acts when the control valve is in a neutral position;
A load holding mechanism provided in the main passage,
The load holding mechanism is
An operation check valve that allows the flow of the working fluid from the control valve to the load-side pressure chamber while allowing the flow of the working fluid from the load-side pressure chamber to the control valve according to back pressure;
A switching valve that operates in conjunction with the control valve by a pilot pressure guided through the pilot control valve, and switches the operation of the operation check valve;
A relief valve that opens when the pressure in the load side pressure chamber reaches a predetermined pressure;
A relief discharge passage for guiding the relief fluid discharged from the relief valve to the tank, and
The switching valve is
A pilot chamber into which pilot pressure is guided through the pilot control valve;
A spool that moves according to the pilot pressure in the pilot chamber;
A spring chamber containing a biasing member that biases the spool in the valve closing direction;
A piston that receives pilot pressure on the back surface and applies a thrust force against the biasing force of the biasing member to the spool;
A drain chamber defined by the spool and the piston;
A drain passage that connects the drain chamber and the spring chamber to the relief discharge passage,
The fluid pressure control device according to claim 1, wherein the relief fluid discharged from the relief valve is discharged to the tank through the relief discharge passage and does not operate the switching valve.   The fluid pressure control device according to claim 1, wherein the drain passage is provided with a throttle for imparting resistance to the fluid passing therethrough.   3. The fluid pressure control according to claim 1, wherein the relief valve has a larger discharge flow rate than a case where the operation check valve is opened by switching the switching valve with the discharged relief fluid. 4. apparatus.

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