CN212899206U - Control valve device and hydraulic drive device provided with same - Google Patents
Control valve device and hydraulic drive device provided with same Download PDFInfo
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- CN212899206U CN212899206U CN202021806876.2U CN202021806876U CN212899206U CN 212899206 U CN212899206 U CN 212899206U CN 202021806876 U CN202021806876 U CN 202021806876U CN 212899206 U CN212899206 U CN 212899206U
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Abstract
The utility model relates to a control valve device and possess its oil pressure drive arrangement who equips of this control valve device. A control valve device for controlling the flow of hydraulic oil supplied to and discharged from a hydraulic cylinder in order to operate the hydraulic cylinder, the control valve device comprising: a control valve having a spool movable from a neutral position to a first position, a second position, and a third position, respectively, the control valve changing the position of the spool to control the flow of hydraulic oil supplied to and discharged from the hydraulic cylinder; and an electromagnetic proportional control valve for changing a position of a spool by a pilot pressure, which outputs a pressure corresponding to an input operation signal, wherein the control valve is connected to a head side port and a rod side port of the hydraulic pump, the accumulator, and the hydraulic cylinder, the spool is formed so as to be cut off from each other at a neutral position of the hydraulic pump, the accumulator, the head side port, and the rod side port, the head side port is connected to the hydraulic pump and the rod side port is connected to the accumulator at a first position, the rod side port is connected to the hydraulic pump and the head side port is connected to the accumulator at a second position, and all the hydraulic pump, the head side port, and the rod side port are connected to the accumulator at a third position.
Description
Technical Field
The present invention relates to a control valve device for controlling the flow of hydraulic oil supplied to and discharged from a hydraulic cylinder, and an oil pressure drive device provided with the control valve device.
Background
When the hydraulic excavator performs a site leveling operation, both the head side port and the rod side port of the boom cylinder are connected to the storage tank, and the working oil in the head chamber and the rod chamber of the boom cylinder is returned to the storage tank. Therefore, the boom can move up and down (floating function) according to the rise and fall of the ground, and the work of leveling the ground can be easily performed. As a hydraulic drive device having a floating function in this manner, for example, a hydraulic device of patent document 1 is known.
The hydraulic device of patent document 1 includes a float valve in addition to a main control valve for controlling the flow of hydraulic oil supplied to and discharged from a boom cylinder. The float valve is interposed between the main control valve and the boom cylinder, and the float function switch is operated as follows after being switched to the open state. That is, the float valve connects the flow paths connected to the large chamber side (i.e., head side chamber) and the small chamber side (i.e., rod side chamber) of the boom cylinder to the reservoir, and returns the hydraulic oil in each chamber to the reservoir. Therefore, the boom cylinder is configured to be freely extendable and retractable, and the boom can move up and down in accordance with the rise and fall of the ground during the work of leveling the ground.
Prior art documents:
patent documents:
patent document 1: japanese patent No. 5498865.
SUMMERY OF THE UTILITY MODEL
Problem that utility model will solve:
in the hydraulic device of patent document 1, a float valve must be provided in addition to the main valve body. Therefore, the hydraulic drive device is increased in size. On the other hand, a hydraulic drive device, more specifically, a control valve device having a float function is required to be downsized, and a compact control valve device having a float function is required to be developed.
In addition to the floating function, hydraulic excavators having a hammer mode function have been developed. The hammer mode function herein is a function of preventing the vehicle body from being lifted when the crusher (i.e., the hammer) is attached to the excavator to crush rocks or the like. In the hammer mode function, the supply and discharge of the working oil to and from the head side chamber are stopped, and the pressure in the head side chamber is maintained. After that, the boom presses the breaking hammer against the rock by its own weight, and since the rise of the boom can be suppressed, the rising of the vehicle body due to the reaction force of the breaking hammer at the time of breaking is suppressed. The hydraulic drive device having the hammer mode function is also constructed compactly, as is the hydraulic drive device with the float function and the control valve device.
Therefore, the present invention is directed to a compact control valve device with a floating function or a breaker mode function, and an oil pressure driving device provided with the control valve device.
Means for solving the problems:
the utility model discloses a control valve device for make the hydraulic cylinder work control to the controlling means of the flow of hydraulic cylinder plumbing operating oil possesses: a control valve having a valve body movable from a neutral position to a first position, a second position, and a third position, respectively, and controlling a flow of hydraulic oil to be supplied to and discharged from the hydraulic cylinder by changing a position of the valve body; the electromagnetic proportional control valve is used for respectively outputting pilot pressures corresponding to the pressures of the input operation signals and changing the position of the valve core, and the control valve is connected with an oil pressure pump, a storage tank and a head side port and a rod side port of the oil pressure cylinder; the spool is formed such that the hydraulic pump, the reservoir, the head-side port and the rod-side port are shut off from each other in a neutral position; connecting the head side port and the oil hydraulic pump and connecting the rod side port and a reservoir in a first position; connecting the rod side port and oil hydraulic pump and connecting the head side port and reservoir in a second position; in a third position the oil pressure pump, the reservoir, the head side port and the rod side port are interconnected.
According to the utility model discloses, when making the case remove to the third position, 2 ports of oil hydraulic cylinder are connected in the storage tank. This makes it possible to make the pressure difference between the 2 ports substantially zero, and to freely extend and retract the hydraulic cylinder in accordance with the load applied to the hydraulic cylinder (more specifically, the piston rod thereof). Therefore, when the control valve device having such a function is applied to, for example, a control valve device for hydraulic oil flowing through a boom cylinder of a hydraulic excavator, a floating function during a leveling work can be realized. The control valve device having such a function is constituted by 1 valve element, and can be constituted more compactly than the conventional art.
The hydraulic drive device of the present invention is a hydraulic drive device for driving a boom cylinder for supplying and discharging hydraulic oil to and from the boom cylinder for operating a boom of a hydraulic excavator, and comprises a hydraulic pump for discharging the hydraulic oil, an operation device for operating the boom cylinder for operating the boom, and a boom control valve device for controlling the flow of the hydraulic oil supplied and discharged from the hydraulic pump to and from the boom cylinder; the boom cylinder is the oil pressure cylinder, the control valve device for the boom is the control valve device, and the control valve controls the flow of the working oil supplied to and discharged from the boom cylinder by changing the position of the valve element.
According to the above structure, the hydraulic drive device having the above-described type of function can be manufactured.
The utility model has the advantages that:
according to the utility model discloses, can provide the compact control valve device that has unsteady function or quartering hammer mode function to and possess this control valve device's oil pressure drive arrangement.
Drawings
Fig. 1 is an oil pressure circuit diagram showing an oil pressure drive device of the present invention;
fig. 2 is an enlarged hydraulic circuit diagram showing a part of a control valve device provided in the hydraulic drive device of fig. 1;
fig. 3 is a sectional view showing the structure of the control valve device of fig. 2;
fig. 4 is an enlarged sectional view showing a region X of the control valve device of fig. 3 enlarged;
description of the symbols:
1 oil pressure driving device
2 control valve device
3 Movable arm cylinder (oil hydraulic cylinder)
3a head side port
3b rod side port
11L first oil pressure pump (oil pressure pump)
13 first arm control valve (control valve)
13a electromagnetic proportional control valve for movable arm
13b electromagnetic proportional control valve for movable arm
13c valve core
22 storage tank
30 cutting mechanism
32 inlet throttle stop valve
33 stop control valve
34 oil passage (passage)
35 back pressure side passage
40 valve block
40a spool bore.
Detailed Description
Hereinafter, the hydraulic drive device 1 according to the embodiment of the present invention will be described with reference to the drawings. In the following description, the concept of the direction is applied for convenience of description, and the direction of the structure of the invention is not limited to this direction. The hydraulic drive device 1 described below is only one embodiment of the present invention. Therefore, the present invention is not limited to the embodiments, and additions, deletions, and modifications may be made without departing from the scope of the present invention.
(oil pressure drive device)
An attachment (attachment) is provided at the tip end of the hydraulic excavator, and various operations can be performed using the attachment. Examples of the accessories include a bucket and a breaking hammer, and the bucket can be used to excavate and level a field, and the breaking hammer can break rock. In the hydraulic excavator, the attachment having such a function is provided on the vehicle body via the boom and the arm, and can be moved up and down and back and forth via the boom and the arm. The attachment, the boom, and the arm are provided with hydraulic cylinders 3, 4, and 5 as hydraulic actuators for their operation as shown in fig. 1, respectively, and the attachment, the boom, and the arm can be operated by supplying and discharging hydraulic oil to and from the hydraulic cylinders 3, 4, and 5.
(oil pressure drive device)
The hydraulic drive device 1 mainly includes 2 hydraulic pumps 11L and 11R as shown in fig. 1; 5 control valves 13-16; a plurality of operating devices 17L, 17R, 18-20 and a control device 21. The 2 hydraulic pumps 11L and 11R are connected to a drive source such as an engine or a motor, not shown in detail, and receive power from the drive source to rotate and discharge hydraulic oil. The 2 hydraulic pumps 11L, 11R having such a function are, for example, variable displacement swash plate pumps having swash plates 11La, 11 Ra. The swash plates 11La and 11Ra change the tilt angle by an unillustrated regulator, and change the discharge flow rates of the hydraulic pumps 11L and 11R by changing the tilt angle. The hydraulic pumps 11L and 11R configured as described above are connected to first and second pump passages 31L and 31R, respectively, and discharge hydraulic oil from the hydraulic pumps 11L and 11R to the pump passages 31L and 31R, respectively. That is, the first hydraulic pump 11L is connected to the first pump passage 31L, and the left-side travel motor control valve 12L, the first boom control valve 13, and the bucket control valve 14 are connected in parallel. The second hydraulic pump 11R is connected to the second pump passage 31R, and the right-side travel motor control valve 12R, the second boom control valve 15, and the arm control valve 16 are connected in parallel.
Each control valve 13 to 16 is connected to each hydraulic actuator 3 to 5, 6L, 6R, respectively, and controls the flow of the hydraulic oil to be supplied to and discharged from the corresponding hydraulic actuator 3 to 5, 6L, 6R. That is, the left-side travel motor control valve 12L is connected to the left-side travel motor 6L as the hydraulic motor 6L, and the right-side travel motor control valve 12R is connected to the right-side travel motor 6R as the hydraulic motor 6R. The first and second boom control valves 13 and 15 are connected to the boom cylinder 3, the arm control valve 16 is connected to the arm cylinder 4, and the bucket control valve 14 is connected to the bucket cylinder 5.
Between the control valves 12L, 12R, 13 to 16 connected in this way, the travel motor control valves 12L, 12R are pilot type spool valves, and a left travel operation device 17L and a right travel operation device 17R are provided in correspondence with each other. The left-side travel operation device 17L and the right-side travel operation device 17R, which are two travel operation devices 17L and 17R, are configured by, for example, remote control valves and the like, and have operation levers 17La and 17Ra, respectively. The travel operation devices 17L and 17R tilt the operation levers 17La and 17Ra in a predetermined direction, and output pilot pressures corresponding to the tilt amounts thereof, respectively. The travel motor control valves 12L and 12R can control the flow of the hydraulic oil supplied to and discharged from the hydraulic motors 6L and 6R based on the pilot pressure output from the corresponding travel operation devices 17L and 17R, respectively, and can operate the corresponding hydraulic motors 6L and 6R. For example, the spools 12Lc and 12Rc are operated by the pilot pressure output from the travel operation devices 17L and 17R, and the hydraulic oil is supplied to and discharged from the 2 travel motors 6L and 6R to operate them, whereby the hydraulic excavator can be driven straight.
On the other hand, the first and second boom control valves 13 and 15, the bucket control valve 14, and the arm control valve 16 are all formed of electromagnetic spool valves. Therefore, the first and second boom control valves 13 and 15 and the arm control valve 16 are provided with electromagnetic proportional control valves 13a to 16a and 13b to 16b, respectively. The electromagnetic proportional control valves 13a to 16a and 13b to 16b output pilot pressures corresponding to the input signals, and the control valves 13 to 16 move the spools 13c to 16c to positions corresponding to the pilot pressures. Therefore, the flow of the hydraulic oil supplied to and discharged from the corresponding hydraulic actuators 3 to 5 can be controlled, and the corresponding hydraulic actuators 3 to 5 can be operated. For example, the pilot pressure is output from the electromagnetic proportional control valves 13b to 16b, and then the valve bodies 13c to 16c move to supply and discharge the hydraulic fluid to and from the hydraulic cylinders 3 to 5, thereby operating the boom, arm, and bucket. In the hydraulic drive device 1 having such a configuration, the operation amounts of the hydraulic actuators 3 to 5 can be adjusted by the plurality of operation devices 18 to 20, respectively.
The operation devices 18 to 20 are provided corresponding to the hydraulic actuators 3 to 5, and the operation devices 18 to 20 include a boom operation device 18, an arm operation device 19, and an bucket operation device 20, which are configured by, for example, an electric control lever or a remote control valve. That is, the plurality of operation devices 18 to 20 include operation levers 18a to 20a, and output operation signals corresponding to the tilting amounts of the operation levers 18a to 20a by tilting the operation levers in a predetermined direction. The plurality of operation devices 18 to 20 are electrically connected to the control device 21, respectively, and output operation signals are input to the control device 21.
The control device 21 controls each mechanism provided in the hydraulic drive device 1. More specifically, the control device 21 is electrically connected to the respective electromagnetic proportional control valves 13a to 16a, 13b to 16b, and outputs signals to the respective electromagnetic proportional control valves 13a to 16a, 13b to 16b in response to signals output from the operation devices 18 to 20 to operate the hydraulic actuators 3 to 5. For example, when the control lever 18a of the boom operation device 18 is operated, the control device 21 outputs a signal to the electromagnetic proportional control valves 13a and 15a (or the electromagnetic proportional control valves 13b and 15 b). Accordingly, the valve bodies 13c and 15c of the first and second boom control valves 13 and 15 move to supply and discharge the hydraulic oil to and from the boom cylinder 3. Therefore, the boom cylinder 3 extends (or contracts), and the boom ascends (or descends).
In the hydraulic drive device 1 having such a configuration, the corresponding hydraulic actuators 3 to 5, 6L, and 6R can be operated by tilting the operating levers 17La, 17Ra, and 18a to 20a of the operating devices 17L, 17R, and 18 to 20. For example, the ground can be leveled by tilting the operating lever 19a of the arm operating device 19 in a state where the bucket contacts the ground and pulling the arm toward the vehicle body side. In such a field leveling work, it is preferable that the hydraulic drive device 1 has a floating function for moving the boom up and down in accordance with the fluctuation of the ground surface, and the hydraulic drive device has the following configuration in order to have the floating function.
(controller device with float function)
In the hydraulic drive device 1 shown in fig. 1 and 2, the first boom control valve 13 has the following configuration in order to achieve the floating function. That is, the first boom control valve 13 is connected to the first pump passage 31L (more specifically, the oil passage 34 connecting the first pump passage 31L and the first boom control valve 13), the tank 22, and the head side port 3a and the rod side port 3b of the boom cylinder 3, and the connection state thereof can be switched by changing the position of the spool 13 c. The pilot pressures p1 and p2 of the respective boom electromagnetic proportional control valves 13a and 13b act on the spool 13c so as to oppose each other, and the positions thereof are changed by strokes according to the output pilot pressures p1 and p2 (or the differential pressure | p1-p2 |). By this, the connection state of the oil passage 34, the tank 22, and the head-side port 3a and the rod-side port 3b of the boom cylinder 3 is switched.
More specifically, as shown in fig. 3, a spring member 13d such as a compression coil spring is provided to the valve body 13c, and the valve body 13c is urged by the spring member 13d so as to hold the valve body 13c at the neutral position M. That is, when the valve body 13c moves from the neutral position M to the first offset position a1 (first position) and the second offset position a2 (second position), respectively, the spring member 13d biases the valve body 13c to return to the neutral position M. Thus, the valve body 13c can be operated by a stroke amount corresponding to the pressure of the pilot pressures p1 and p2 of the boom electromagnetic proportional control valves 13a and 13 b. That is, when both pilot pressures of the boom electromagnetic proportional control valves 13a and 13b are zero, the spool 13c is located at the neutral position M and moves to the first offset position a1 under the pilot pressure p1 from the boom electromagnetic proportional control valve 13 a. The spool 13c moves to the second offset position a2 under the pilot pressure p2 (≦ pset) from the boom solenoid proportional control valve 13 b.
The valve body 13c having such a structure can be moved to the third offset position a3 (third position) when the float mode is selected by a float mode selection means to be described later in order to achieve the float function. Specifically, when the pilot pressure p2 from the boom solenoid proportional control valve 13b exceeds the set value pset, the spool 13c moves to the third offset position A3. The set value pset is a pressure value determined based on the urging force of the spring member 13 d. When the pilot pressures of the boom electromagnetic proportional control valves 13a and 13b are set to zero in a state where the spool 13c is located at the first to third offset positions a1 to A3, the neutral position M is returned by the urging force of the spring member 13 d.
In the first boom control valve 13 configured as described above, in a state where the spool 13c is located at the neutral position M, the oil passage 34, the tank 22, the head-side port 3a, and the rod-side port 3b are blocked from each other, and the rod 3c of the boom cylinder 3 is held. In a state where the spool 13c is located at the first offset position a1, the head-side port 3a is connected to the oil passage 34, the rod-side port 3b is connected to the tank 22, and the boom cylinder 3 extends. In a state where the spool 13c is located at the second offset position a2, the head-side port 3a is connected to the tank 22, the rod-side port 3b is connected to the oil passage 34, and the boom cylinder 3 contracts. On the other hand, in a state where the spool 13c is located at the third offset position a3, all of the oil passage 34, the head-side port 3a, and the rod-side port 3b are connected to the tank 22. Therefore, the pressure difference between the head-side port 3a and the rod-side port 3b can be made substantially zero, and the boom cylinder 3 can be freely expanded and contracted in accordance with the load acting on the rod 3 c.
The hydraulic drive device 1 further includes a cutoff mechanism 30 capable of further increasing the floating function. The cutoff mechanism 30 is located in an oil passage 34 connecting the first boom control valve 13 and the first pump passage 31L, and is capable of stopping the hydraulic oil flowing from the first pump passage 31L (specifically, the hydraulic pump 11L) to the first boom control valve 13. The shutoff mechanism 30 having such a function further includes an meter-in shutoff valve 32 and a shutoff control valve 33.
The meter-in Valve 32 is a so-called Poppet Valve (Poppet Valve), and is interposed in an oil passage 34 connecting the first boom control Valve 13 and the first pump passage 31L, and is capable of stopping the hydraulic oil flowing from the first pump passage 31L to the first boom control Valve 13. That is, the meter-in shutoff valve 32 has a poppet 32a, and the tip end of the poppet 32a is seated on the valve seat 32b to block the oil passage 34 and stop the flow of the hydraulic oil. In the meter-in shutoff valve 32, the poppet 32a is separated from the valve seat 32b, and the hydraulic oil flows through the oil passage 34 while being opened.
More specifically, the meter-in shutoff valve 32 has a back pressure chamber 32c formed on the base end side of the poppet 32a, and the spring 32d is accommodated in the back pressure chamber 32 c. The spring 32d is a so-called compression coil spring, and pushes the poppet 32a toward the valve seat 32b together with the hydraulic oil in the back pressure chamber 32 c. The poppet 32a receives pressure against the biasing force of the spring 32d from the hydraulic oil flowing through the oil passage 34 (more specifically, the hydraulic oil flowing through the oil passage 34 on the upstream side of the meter-in stop valve 32). Therefore, in the meter-in shutoff valve 32, the oil passage 34 is opened and closed in accordance with the balance between the pressure of the back pressure chamber 32c, the biasing force of the spring 32d, and the oil pressure of the oil passage 34 (i.e., the oil pressure of the first pump passage 31L).
Further, the back pressure chamber 32c is connected to the back pressure side passage 35, and the back pressure chamber 32c is connected to the meter-in shutoff valve 32 downstream of the oil passage 34 through the back pressure side passage 35. A communication passage 32e is formed to communicate between the upstream side of the oil passage 34 and the back pressure chamber 32 c. Therefore, the upstream side of the meter-in shutoff valve 32 is guided to the back pressure chamber 32c via the communication passage 32e, and the hydraulic oil in the back pressure chamber 32c is discharged to the downstream side of the meter-in shutoff valve 32 via the back pressure side passage 35. Further, the communication passage 32e is provided with a throttle valve 32f, and the hydraulic oil on the upstream side of the meter-in stop valve 32 is guided to the back pressure chamber 32c by the throttle valve 32f of the communication passage 32e, and is discharged to the downstream side of the meter-in stop valve 32 through the back pressure side passage 35. Therefore, the pressure of the hydraulic oil in the back pressure chamber 32c becomes lower than the pressure on the upstream side of the meter-in stop valve 32, and the poppet 32a is pushed up to be separated from the valve seat 32b by the hydraulic oil on the upstream side of the meter-in stop valve 32, that is, the oil passage 34 is opened. Further, a shutoff control valve 33 is interposed in the back pressure side passage 35 to close the oil passage 34.
The shutoff control valve 33 is a so-called pilot valve and is configured to open and close the back pressure side passage 35. More specifically, the shutoff control valve 33 is connected to the shutoff device solenoid valve 36. The solenoid valve 36 for the shutoff device outputs a pilot pressure in response to an opening/closing signal from the control device 21, and the shutoff control valve 33 opens and closes the back pressure side passage 35 in response to the output pilot pressure. Further, by closing the back pressure side passage 35 by the shutoff control valve 33, the hydraulic oil guided to the back pressure chamber 32c via the communication passage 32e cannot be discharged from the back pressure chamber 32c, and the back pressure of the back pressure chamber 32c is maintained at the same pressure as the oil pressure in the first pump passage 31L (more specifically, the oil passage 34). Thus, the poppet 32a is pushed toward the valve seat 32b and seated by the hydraulic oil in the back pressure chamber 32c, and the oil passage 34 is closed. This can shut off the flow from the hydraulic pump 11L to the boom cylinder 3 (more specifically, from the hydraulic pump 11L to the first boom control valve 13), and prevent the hydraulic oil from the hydraulic pump 11L from flowing into the boom cylinder 3 regardless of the position of the spool 13c in the first boom control valve 13. In this way, the meter-in cut valve 32 can close the oil passage 34, preventing the working oil from the oil hydraulic pump 11L from flowing into the boom cylinder 3.
The hydraulic drive device 1 further includes a floating mode selector 23, and the floating mode selector 23 is electrically connected to the controller 21. The floating mode selecting device 23 is, for example, a switch, and outputs a mode selection command to the control device 21 by operation. Upon receiving the mode selection command from the floating mode selection device 23, the control device 21 switches the control mode from the normal mode to the floating mode. In the float control mode, which is the first control mode, first, the control device 21 releases the restriction on the pilot pressure p2 output from the arm solenoid proportional control valve 13 b. That is, a set value pset that is a limit value for the pilot pressure p2 is set, and the control device 21 causes the arm electromagnetic proportional control valve 13b to output the pilot pressure p2 within a range equal to or less than the set value pset in the normal mode.
On the other hand, in the float control mode, the control device 21 releases the limit value for the pilot pressure p2, and the slave arm electromagnetic proportional control valve 13b can output the pilot pressure p2 exceeding the set value pset. Therefore, when the operation lever 18a of the boom operation device 18 is operated in the float control mode (more specifically, a lowering operation is performed), the control device 21 may output a float command signal (first command signal) to the boom solenoid proportional control valve 13b so as to output a pilot pressure p2 that exceeds the set value pset, and may move the spool 13c of the first boom control valve 13 to the third offset position A3. Accordingly, the pressure difference between the head-side port 3a and the rod-side port 3b can be made substantially zero, and the boom can be moved up and down in accordance with the undulation of the ground during the field leveling work. That is, in the hydraulic drive device 1, the floating function can be achieved.
When the operation lever 18a of the boom operation device 18 is operated (more specifically, a lowering operation is performed) in the float control mode, the control device 21 performs the following control. That is, the controller 21 outputs an opening/closing signal to the shutoff device solenoid valve 36 to operate the shutoff control valve 33, thereby closing the back pressure side passage 35. In this way, the pressure in the back pressure chamber 32c of the meter-in shutoff valve 32 rises, the poppet 32a is seated on the valve seat 32b, and the oil passage 34 is closed. Thereby, the gap between the boom cylinder 3 and the hydraulic pump 11L is blocked, and the pressures of the head-side port 3a and the rod-side port 3b become the tank pressure. Therefore, by operating the arm cylinder 4, a constant low load can be applied to the boom cylinder 3, and the responsiveness of the boom to the undulation of the ground can be improved at the time of field leveling work. That is, the floating function in the hydraulic drive device 1 can be improved.
The hydraulic drive device 1 having such a function includes a valve block 40 as shown in fig. 3, wherein the valve elements 13c to 16c are movably accommodated in a plurality of valve element holes (only one valve element hole 40a is shown in fig. 3) formed in the valve block 40, and the electromagnetic proportional control valves 13a to 16a and 13b to 16b are mounted on the opening end portions on both sides of each valve element hole so as to block them. For example, taking the first boom control valve 13 as an example, as shown in fig. 3, in the valve block 40, a spool hole 40a for the first boom control valve 13 is formed so as to penetrate the valve block 40, and a spool 13c of the first boom control valve 13 is inserted therein. Further, the open end portions on both sides of the valve core hole 40a are covered with casings 41a and 41b so as to close them, and the boom electromagnetic proportional control valves 13a and 13b are mounted, respectively.
Further, a receiving hole 40d extending in a direction orthogonal to the spool hole 40a is formed in the valve block 40, and the poppet 32a of the meter-in shutoff valve 32 is received therein. To explain in more detail, the accommodation hole 40d is connected to the oil passage 34 as shown in fig. 4, and the valve seat 32b is formed in the oil passage 34. The poppet 32a is inserted into the receiving hole 40d so as to be seated on the valve seat 32b, and the oil passage 34 is closed by seating of the poppet 32 a. The tip end of the poppet 32a having such a function faces the first pump passage 31L, and is subjected to a load in a direction away from the valve seat 32b, that is, in an opening direction of the hydraulic oil flowing through the first pump passage 31L.
As described later, the open end of the receiving hole 40d is closed by the case 44 on the base end side of the poppet 32a, thereby forming the back pressure chamber 32 c. The working oil is introduced into the back pressure chamber 32c through the shutoff control valve 33, and the poppet 32a receives a back pressure at its base end. A spring 32d is accommodated in the back pressure chamber 32c, and the poppet 32a is biased by the spring 32d against the oil pressure in the oil passage 34. As a result, the oil passage 34 is opened and closed in accordance with the balance between the biasing force of the pressure spring 32d in the back pressure chamber 32c and the hydraulic pressure in the first pump passage 31L, as described above.
The poppet 32a has a communication passage 32e formed through the center thereof, and the check valve body 43 is accommodated therein. The check valve body 43 is configured to open and close the through passage, and the downstream side of the check valve body 43 communicates with the back pressure chamber 32c through the throttle valve 32 f. The check valve body 43 is also formed to guide the working oil on the upstream side of the oil passage 34, and opens and closes the communication passage 32e corresponding to the balance of the oil pressure of the oil passage 34, the pressure of the back pressure chamber 32c, and the force of the spring 43a that further biases the check valve body 43. That is, in a state where the poppet 32a is seated, the hydraulic oil is guided to the back pressure chamber 32c through the communication passage 32e, and the poppet 32a maintains the seated position. In this way, the meter-in shutoff valve 32 is accommodated in the accommodation hole 40d, and the housing 44 is attached to the opening of the accommodation hole 40 d.
The housing 44 is attached to the valve block 40 so as to close the opening of the accommodation hole 40d, and forms the back pressure chamber 32c on the opening side of the accommodation hole 40 d. The housing 44 and the valve block 40 have a back pressure side passage 35 formed therein, and the shutoff control valve 33 is attached to the housing 44 so as to be interposed therebetween. Therefore, the pressure of the back pressure chamber 32c can be maintained by the shutoff control valve 33, and opening and closing of the oil passage 34 can be performed.
The valve block 40 thus constitutes the first boom control valve 13 and the meter-in stop valve 32 together with the valve body 13c and the poppet 32a, and the first boom control valve 13, the meter-in stop valve 32 and the stop control valve 33 together constitute the boom control valve device (hereinafter simply referred to as "control valve device") 2 having a float function. That is, the first boom control valve 13, the meter-in shutoff valve 32, and the shutoff control valve 33 that constitute the control valve device 2 are formed in association with one valve body hole 40 a. In the conventional hydraulic device, a float valve is provided in addition to a main control valve in order to have a float function, and each valve is configured by a spool valve, and at least two spool holes (or two spools) are required. On the other hand, the control valve device 2 is formed in association with one spool hole 40a (i.e., one spool 13 c) as described above, and thus can be configured more compactly than the conventional technique, and the hydraulic drive device 1 can be configured more compactly.
The receiving hole 40d of the valve block 40 is originally a hole for mounting a check valve for preventing a reverse flow from the oil passage to the first pump passage 31L, and the meter-in shutoff valve 32 having a reverse flow preventing function is mounted in the hydraulic drive device 1. That is, in the hydraulic drive device 1, the valve which is newly added mainly to have the float function is the cut-off control valve 33, and the cut-off control valve 33 is smaller in size than a float valve type spool or the like in the related art. Therefore, even if the cut-off control valve 33 is installed, the hydraulic drive device 1 is not greatly increased in size, and the hydraulic drive device 1 having improved float function while maintaining compactness can be manufactured.
< control valve device with breaking hammer mode function >
The hydraulic drive device 1 also has a breaking hammer mode function for pressing the breaking hammer against the rock by the weight of the boom or the like when the breaking hammer is attached to the tip end of the arm to break the rock or the like. More specifically, the hydraulic drive device 1 further includes a hammer mode selector 24, and the hammer mode selector 24 is electrically connected to the controller 21. The hammer mode selector 24 is, for example, a switch, and is operated to output a mode selection command to the controller 21. Upon receiving the mode selection command from the hammer mode selection device 24, the control device 21 switches the control mode from the normal mode to the hammer control mode. In the hammer control mode as the second control mode, when the operation lever 18a of the boom operation device 18 is operated (more specifically, a lowering operation is performed), the control device 21 outputs a signal to the boom electromagnetic proportional control valve 13b so that the valve body 13 moves to the second offset position a2, and performs the following control. That is, the controller 21 outputs an opening/closing signal to the shutoff device solenoid valve 36 to operate the shutoff control valve 33 and close the back pressure side passage 35. After that, the oil passage 34 is closed, the gap between the boom cylinder 3 and the hydraulic pump 11 is blocked, and the pressure of the rod side port 3b is maintained. On the other hand, since the head-side port 3a becomes the tank pressure, the boom descends by its own weight, and the breaker hammer is lowered to the ground. In this state, since the raising operation of the boom is restricted, the crushing operation can be performed while the crushing hammer is reliably pressed against the ground by its own weight, and the vehicle body can be prevented from being lifted up by the boom due to the reaction force from the crushing hammer.
The oil pressure driving device 1 having such a function can realize the breaking hammer control mode by the compact control valve device 2 as described above. That is, the compact control valve device 2 and the hydraulic drive device 1 having the function of the breaker mode can be realized.
(other embodiment)
In the above description, the hydraulic excavator is exemplified as an example of the hydraulic machine to which the present invention is applied, but the present invention is not necessarily limited to the hydraulic excavator. That is, the hydraulic machine of the present invention may be a hydraulic machine and an apparatus having a floating function or a breaking hammer mode function. The hydraulic drive device 1 has both the floating function and the hammer mode function, but does not necessarily have both of them, and may have at least one function. In addition, when the hydraulic drive device 1 has only the hammer mode function, the valve body 13c of the boom control valve 13 does not necessarily have to be configured to be movable to the third offset position a 3. In the float control mode, the mechanism for stopping the hydraulic oil flowing from the first pump 11L to the first boom control valve 13 is not necessarily the cutting mechanism 30 described above, and may be constituted by another control valve. For example, the shutoff mechanism is not necessarily provided in the oil passage 34, and may be provided in the first pump passage 31L. The application target is not limited to the boom cylinder, and may be a boom cylinder, a bucket cylinder, or the like, or may be another hydraulic cylinder.
Claims (10)
1. A control valve device for controlling the flow of hydraulic oil supplied to and discharged from a hydraulic cylinder in order to operate the hydraulic cylinder,
the hydraulic control device is provided with a control valve which is provided with a valve core capable of moving from a neutral position to a first position, a second position and a third position, and controls the flow of the working oil supplied to and discharged from the hydraulic cylinder by changing the position of the valve core,
the control valve is connected with the oil pressure pump, the storage tank and the head side port and the rod side port of the oil pressure cylinder,
the valve body is formed such that, in a neutral position, the hydraulic pump, the reservoir, the head-side port, and the rod-side port are disconnected from each other, in a first position, the head-side port is connected to the hydraulic pump and the rod-side port is connected to the reservoir, in a second position, the rod-side port is connected to the hydraulic pump and the head-side port is connected to the reservoir, and in a third position, all of the hydraulic pump, the head-side port, and the rod-side port are connected to the reservoir.
2. The control valve device according to claim 1, further comprising an electromagnetic proportional control valve that outputs pilot pressures of pressures corresponding to the input operation signals, respectively, and changes the position of the spool.
3. The control valve device according to claim 1 or 2, further comprising a shut-off mechanism that is interposed in a passage connecting the hydraulic pump and the control valve, and shuts off the passage to stop supply and discharge of the hydraulic oil from the hydraulic pump to the hydraulic cylinder through the control valve.
4. The control valve device according to claim 3, wherein the shutoff mechanism includes: an intake throttle cut valve having a back pressure chamber, cutting off the passage in accordance with a pressure of the back pressure chamber, and having a backflow prevention function capable of preventing a flow of the hydraulic oil flowing backward in the passage from the control valve to the hydraulic pump; and a shutoff control valve for stopping the discharge of the pressure oil from the back pressure chamber and shutting off the passage by the meter-in shutoff valve.
5. The control valve arrangement as recited in claim 4, characterized in that the control valve has a valve block movably accommodating the spool,
the valve block is formed with a spool hole that movably receives the spool and the passage,
the inlet throttle cut-off valve is accommodated in the valve block in such a manner as to be inserted into the passage,
and the stop control valve is arranged on the inlet throttling stop valve.
6. The control valve apparatus as claimed in claim 3, wherein the shut-off mechanism is capable of shutting off the passage when the spool is in the second position.
7. The control valve apparatus as claimed in claim 4 or 5, wherein the shut-off mechanism is capable of shutting off the passage when the spool is in the second position.
8. The control valve apparatus as claimed in claim 3, wherein the shut-off mechanism is capable of shutting off the passage when the spool is in the third position.
9. The control valve apparatus according to claim 4 or 5, wherein the shutoff mechanism is capable of shutting off the passage when the spool is located at the third position.
10. A hydraulic drive device for driving a boom cylinder that operates a boom of a hydraulic excavator by supplying and discharging hydraulic oil to and from the boom cylinder,
the disclosed device is provided with:
a hydraulic pump for discharging the working oil, and
a boom control valve device for controlling a flow of the hydraulic oil supplied from the hydraulic pump to the boom cylinder,
the movable arm cylinder is an oil pressure cylinder,
the boom control valve apparatus is the control valve apparatus according to any one of claims 1 to 9,
the control valve controls the flow of the working oil supplied to and discharged from the boom cylinder by changing the position of the spool.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2019160255A JP7304776B2 (en) | 2019-09-03 | 2019-09-03 | CONTROL VALVE GEAR AND HYDRAULIC DRIVING SYSTEM INCLUDING THE SAME |
| JP2019-160255 | 2019-09-03 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN212899206U true CN212899206U (en) | 2021-04-06 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202021806876.2U Active CN212899206U (en) | 2019-09-03 | 2020-08-26 | Control valve device and hydraulic drive device provided with same |
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| Country | Link |
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| JP (1) | JP7304776B2 (en) |
| CN (1) | CN212899206U (en) |
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| JP2024008538A (en) * | 2022-07-08 | 2024-01-19 | 株式会社小松製作所 | hydraulic valve device |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0514765U (en) * | 1991-08-06 | 1993-02-26 | 株式会社 神崎高級工機製作所 | Hydraulic lifting device |
| JP5485007B2 (en) * | 2010-05-07 | 2014-05-07 | 日立建機株式会社 | Hydraulic control device for work vehicle |
| JP5762328B2 (en) * | 2012-02-03 | 2015-08-12 | カヤバ工業株式会社 | Construction machine control equipment |
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2019
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| Publication number | Publication date |
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| JP7304776B2 (en) | 2023-07-07 |
| JP2021038792A (en) | 2021-03-11 |
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