KR20210028096A - Control valve, hydraulic circuit, hydraulic equipment and construction machine - Google Patents

Abstract

A control valve (30) comprises: a valve main body (40) having a spool hole (41) and at least a first port, a second port, and a common port connected to the spool hole (41); a first spool (60) movable in the spool hole (41) of the valve main body (40) and connecting the first port and the common port through the spool hole (41); and a second spool (70) movable in the spool hole (41) of the valve main body and connecting the second port and the common port.

Description

Control valves, hydraulic circuits, hydraulic equipment and construction machinery {CONTROL VALVE, HYDRAULIC CIRCUIT, HYDRAULIC EQUIPMENT AND CONSTRUCTION MACHINE}

The present invention relates to a control valve, a hydraulic circuit, a hydraulic device, and a construction machine.

For example, as disclosed in JP1996-170353A, a control valve having a valve body and a spool disposed in a spool hole of the valve body is known. The spool is provided with a notch, and the spool has a small diameter in the notch forming portion provided with the notch. The two ports are connected through the spool hole by facing the notched portion of the spool on both sides of the two ports connected to the spool hole. On the other hand, when the land portion in which the notch of the spool is not formed is located between the two ports of the spool hole, the connection between the two ports is blocked.

When connecting two ports with a conventional control valve, a notch forming portion of the spool is located in the spool hole connecting the two ports. Thus, when fluid flows between the two ports, a pressure loss occurs due to the presence of this notch formation. The present invention has been made in consideration of the above points, and an object of the present invention is to reduce the pressure loss of the control valve.

The first control valve according to the present invention,

A valve body provided with a spool hole,

And a first spool and a second spool movable within the spool hole of the valve body.

The second control valve according to the present invention,

A valve body provided with a spool hole and at least two ports passing through the spool hole,

And a first spool and a second spool movable within the spool hole of the valve body and spaced apart from each other when connecting the two ports through at least the spool hole.

The third control valve according to the present invention,

A valve body provided with a spool hole and at least two ports passing through the spool hole,

A first spool and a second spool are movable within the spool hole of the valve body and are spaced apart from each other and connect the two ports through the spool hole.

The fourth control valve according to the present invention,

A valve body provided with a spool hole, and at least a first port, a second port, and a common port through the spool hole,

A first spool capable of moving the spool hole of the valve body and connecting the first port and the common port through the spool hole;

A second spool capable of moving the spool hole of the valve body and connecting the second port and the common port

Equipped.

The fifth control valve according to the present invention,

A valve provided with a first spool hole and a first port through the first spool hole, a second spool hole and a second port through the second spool hole, and a common port through the first spool hole and the second spool hole With the body,

A first spool capable of moving the first spool hole of the valve body and connecting the first port and the common port through the first spool hole;

A second spool capable of moving the second spool hole of the valve body and connecting the second port and the common port

Equipped.

In the first to fifth control valves according to the present invention, the first spool and the second spool may move synchronously.

In the first to fifth control valves according to the present invention, the first spool and the second spool may move asynchronously.

In the first to fifth control valves according to the present invention, the separation distance between the first spool and the second spool may be longer than the state in which the connection of the two ports is cut off when the two ports are connected. .

The first to fifth control valves according to the present invention include a first back pressure chamber passing through a through hole provided in the first spool to the spool hole, and a second back pressure chamber passing through a through hole provided in the second spool to the spool hole. You may make it provide a back pressure chamber.

The first to third control valves according to the present invention may include a first movement control unit that controls the movement of the first spool, and a second movement control unit that controls the movement of the second spool.

The first to third control valves according to the present invention include a first movement control unit for controlling supply of pilot hydraulic oil for driving the first spool, and a first movement control unit for controlling supply of pilot hydraulic oil for driving the second spool. 2 You may make it equipped with the movement control part.

In the first to third control valves according to the present invention, when the first spool moves to one side, the second spool also moves to one side, and when the first spool moves to the other side, the second spool is You can keep it stationary.

The first to third control valves according to the present invention may be provided with movement control for controlling supply of pilot hydraulic oil for driving the first spool and the second spool.

The hydraulic circuit according to the present invention includes any of the first to third control valves according to the present invention described above.

The hydraulic device according to the present invention,

Any of the hydraulic circuits according to the present invention described above, and

And an actuator controlled by the hydraulic circuit.

The construction machine according to the present invention includes any of the hydraulic circuits according to the present invention described above.

According to the present invention, it is possible to effectively reduce the pressure loss of the control valve.

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a diagram for explaining an embodiment, and is a diagram showing a specific example of a control valve incorporated in a construction machine, a hydraulic device, and a hydraulic circuit.
FIG. 2 is a cross-sectional view schematically showing the configuration of the control valve of FIG. 1, and is a view for explaining the operation of the control valve.
FIG. 3 is a cross-sectional view corresponding to FIG. 2 and is a view for explaining the operation of the control valve.
FIG. 4 is a cross-sectional view corresponding to FIG. 2 and is a view for explaining the operation of the control valve.
FIG. 5 is a cross-sectional view corresponding to FIG. 1 and is a view for explaining a modified example of the control valve.
6 is a cross-sectional view schematically showing the configuration of the control valve of FIG. 5, and is a view for explaining the operation of the control valve of FIG. 5.
FIG. 7 is a cross-sectional view corresponding to FIG. 2 and is a view for explaining another modified example of the control valve.
FIG. 8 is a cross-sectional view corresponding to FIG. 2 and is a view for explaining another modified example of the control valve.

Hereinafter, an embodiment of the present invention will be described with reference to specific examples shown in the drawings. In addition, elements shown in each of the drawings may include elements in which sizes and scales are shown differently from actual ones in order to facilitate understanding.

The control valve 30 described below is a device that switches between supply and stop of supply of a liquid capable of applying pressure, in particular, a pressure oil. The control valve 30 is built-in and used in a hydraulic circuit 20 including a supply passage for hydraulic oil, such as a hydraulic circuit including a supply passage for a liquid, for example, as described below. The hydraulic circuit and the hydraulic circuit 20 are applied to, as an example, a machine for performing construction work, that is, a construction machine 10. As the construction machine 10, a forklift, a crane car, a forklift, etc. are illustrated. The hydraulic circuit 20 applied to the construction machine 10 constitutes an actuator 18 connected to mechanical equipment 13 such as a shovel, a crane, a forklift, a hammer, and a traveling means, and a hydraulic device 15. . The hydraulic circuit 20 controls the operation of the actuator 18 by supplying hydraulic oil to the actuator 18 and discharging the hydraulic oil from the actuator 18. As the actuator 18 operates, it drives the mechanical equipment 13.

Hereinafter, the control valve 30 will be described in more detail. As shown in FIG. 1, the control valve 30 includes a valve body 40 and a first spool 60 and a second spool 70 movable within the spool hole 41 of the valve body 40. Has. The valve body 40 is provided with a spool hole 41. The spool hole 41 is an elongated hole, and forms a columnar space, for example. The first spool 60 and the second spool 70 are movable within the spool hole 41 along the central axis CA of the spool hole 41.

In addition, in the control valve 30 in the present embodiment, in the valve body 40, a first port 47B, a second port 48B, and a common port 46B passing through the spool hole 41 are provided. It is prepared. By moving the first spool 60 within the spool hole 41, it is possible to switch the connection and disconnection of the first port 47B and the common port 46B through the spool hole 41. Further, by moving the second spool 70 in the spool hole 41, the connection and disconnection of the second port 48B and the common port 46B through the spool hole 41 can be switched.

In the following, the direction parallel to the central axis CA of the spool hole 41, that is, the moving direction of the first spool 60 and the second spool 70 is referred to as axial direction AD. In addition, one side in the axial direction AD (right side in the paper in Fig. 1) is referred to as one SA, and the other side (left side in the paper in Fig. 1) is referred to as the other side SB. In order to clarify the directional relationship between the drawings, in FIGS. 1 to 7, the axial direction AD, one side SA, and the other side SB are shown as being common between the drawings. In addition, the "outside" in the axial direction AD is a side separated from the center of the control valve 30 in the axial direction AD. Conversely, "inside" in the axial direction AD is a side close to the center of the control valve 30 in the axial direction AD.

In the valve body 40, a supply passage P and a tank passage T are formed. The supply passage P communicates with a pressure oil pressure feeding means such as a pump of the hydraulic circuit 20. In the supply passage P, pressure oil maintained at high pressure is usually filled or flowing. On the other hand, the tank passage T is a passage for recovering the pressure oil not supplied to the actuator 18 or the pressure oil discharged from the actuator 18. The tank passage T normally passes through a tank (not shown). The pressure oil recovered to the tank through the tank passage T is fed back into the supply passage P by the pressure oil pressure feeding means.

The valve body 40 is provided with a first supply port 47A and a second supply port (the first port described above) 47B through the supply passage P through the check valve CV. The 1st supply port 47A and the 2nd supply port 47B are opened in the spool hole 41 and are connected to the spool hole 41. Further, the valve body 40 is provided with a first discharge port 48A and a second discharge port (the second port described above) 48B through the tank passage T. The 1st discharge port 48A and the 2nd discharge port 48B are opened in the spool hole 41 and are connected to the spool hole 41.

Further, the valve body 40 is provided with a first actuator port 46A and a second actuator port (common port) 46B via the actuator 18. The first actuator port 46A and the second actuator port 46B communicate with different seals of the hydraulic cylinder constituting the actuator 18. In the illustrated example, the second actuator port 46B communicates with the rod chamber 18a on the side through which the rod passes. The first actuator port 46A communicates with the piston chamber 18b on the side where the rod does not penetrate. The first actuator port 46A and the second actuator port 46B are opened in the spool hole 41 and communicated with the spool hole 41.

In the illustrated example, in the region where the first discharge port 48A, the first actuator port 46A, and the first supply port 47A become one SA in the axial direction AD, the spool hole 41 It is connected to. The connection positions (opening positions) of the first discharge port 48A, the first actuator port 46A, and the first supply port 47A to the spool hole 41 are in this order from one side SA in the axial direction AD. It is made into. Similarly, in the illustrated example, in a region where the second discharge port 48B, the second actuator port 46B, and the second supply port 47B become the other SB in the axial direction AD, the spool hole ( 41). The connection position (opening position) of the second discharge port 48B, the second actuator port 46B, and the second supply port 47B to the spool hole 41 is in this order from the other side SB in the axial direction AD. It is made into.

In addition, in the example shown in Fig. 1, the valve body 40 includes a valve block 50, a first side block 51X fixed to the valve block 50 from one side SA in the axial direction AD, and , A second side block 51Y fixed to the valve block 50 from the other side SB in the axial direction AD. In the illustrated example, the passages P and T described above and the ports 46A, 46B, 47A, 47B, 48A, and 48B are formed in the valve block 50. On the other hand, the spool hole 41 passes through the valve block 50 and extends from the valve block 50 to the first side block 51X and the second side block 51Y.

Next, the first spool 60 and the second spool 70 will be described. The first spool 60 and the second spool 70 are members provided separately. The first spool 60 and the second spool 70 are rod-shaped members. The first spool 60 and the second spool 70 have cross sections corresponding to the cross-sectional shape of the spool hole 41. Then, the first spool 60 or the second spool 70 is located in the spool hole 41, thereby restricting the flow of hydraulic oil through the portion of the spool hole 41 in the axial direction AD.

The first spool 60 has a first tip end surface 62 facing the inside in the axial direction AD and a first base end surface 63 facing the outside (one side SA) in the axial direction AD. The first spool 60 is provided with a first through hole 61 penetrating between the first tip end surface 62 and the first base end surface 63. The first spool 60 has a first bulging portion 64 made wide (large-hardened) in a region of one side SA in the axial direction AD. The first spool 60 is expanded in a direction perpendicular to the axial direction AD in the first expanded portion 64. The first bulging portion 64 forms a first one shoulder portion 64X that faces one side SA in the axial direction AD, and a first other side shoulder portion 64Y that faces the other side SB in the axial direction AD. In addition, the first spool 60 has a narrow (small-hardened) notch forming portion 65 in a region between the first tip surface 62 and the first bulging portion 64 in the axial direction AD. I have. That is, the 1st spool 60 forms the notch 65C in the notch formation part 65, and consequently is concave in the direction perpendicular to the axial direction AD.

Similarly, the second spool 70 has a second end surface 72 facing the inside in the axial direction AD and a second base end surface 73 facing the outside (the other side SB) in the axial direction AD. have. The second spool 70 is provided with a second through hole 71 penetrating between the second tip end surface 72 and the second base end surface 73. In the illustrated example, the first spool 60 is located on one side SA of the second spool 70 in the axial direction AD. Then, the second tip end surface 72 of the second spool 70 faces the first tip end surface 62 of the first spool 60 and the axial direction AD. Further, the second spool 70 has a second bulging portion 74 that is wide (large-hardened) in a region serving as the other SB in the axial direction AD. That is, the 2nd spool 70 is expanded in the direction perpendicular to the axial direction AD in the 2nd bulging part 74. The 2nd bulging part 74 forms a 2nd one side shoulder part 74X facing the one side SA in the axial direction AD, and the 2nd other side shoulder part 74Y facing the other side SB in the axial direction AD.

The first spool 60 and the second spool 70 move in the axial direction AD within the spool hole 41 to connect the two ports through the spool hole 41, or through the spool hole 41. Block access to both ports. In the illustrated example, the two ports to be connected and to be disconnected are two ports which are connected to the spool hole 41 at adjacent positions in the axial direction AD.

In the illustrated example, the first spool 60 switches the connection and disconnection of the first actuator port 46A and the first supply port 47A, and the first actuator port 46A and the first discharge port Block 48A and switch the connection. As described above, the first spool 60 has a cross-section corresponding to the cross-sectional shape of the spool hole 41. Therefore, by placing the first spool 60 in the spool hole 41, the hydraulic oil is restricted from flowing in the spool hole 41 in the axial direction AD. On the other hand, in the 1st spool 60, the notch 65C is formed in the notch formation part 65. And, in other words, both sides of the connection position (opening position) of the two ports to the spool hole 41 so as to overlap in the axial direction AD with the connection position (opening position) of the two ports By arranging the notch forming portion 65 so as to face the direction perpendicular to the direction AD, the two ports adjacent to the axial direction AD are connected to each other through the notch 65C. That is, by moving the first spool 60 provided with the notch 65C in the axial direction AD, the connection and disconnection of the first actuator port 46A and the first supply port 47A can be switched, and the first Shut-off and connection of the actuator port 46A and the first discharge port 48A are switched.

In this embodiment, the first tip end surface 62 and the second spool 70 of the first spool 60 can be separated from each other in the axial direction AD. At this time, a space S is formed between the first tip surface 62 of the first spool 60 and the second tip surface 72 of the second spool 70. This space S functions similarly to the notch 65C of the first spool 60 to switch the connection and disconnection of the two ports. Specifically, the connection position (opening position) of the two ports to the spool hole 41 and the connection position (opening position) of the two ports to the spool hole 41 so that they overlap in the axial direction AD By forming the space S so as to face the direction perpendicular to the axial direction AD, the two ports adjacent to the axial direction AD are connected to each other through the space S. In the illustrated example, the first spool 60 and the second spool 70 are, by adjusting the position of the space S, the second actuator port (common port) 46B and the second supply port (first port) The connection and disconnection of 47B can be switched, and the disconnection and connection of the second actuator port (common port) 46B and the second discharge port (second port) 48B can be switched.

Next, a configuration for moving the first spool 60 and the second spool 70 in the axial direction AD will be described. First, between the first spool 60 and the valve body 40, a first one side chamber 43AX and a first other side chamber 43AY are provided. The first one side chamber 43AX is formed on one side SA of the first bulging portion 64 of the first spool 60 in the axial direction AD. The first one side shoulder portion 64X of the first bulging portion 64 constitutes a part of the wall portion that divides the first one side chamber 43AX. The first one shoulder 64X facing one side SA in the axial direction AD is pressed against the other side SB in the axial direction AD by the pressure in the first one side chamber 43AX. The valve body 40 is provided with a first one-side passage 44AX through which the first one-side chamber 43AX is passed. Similarly, the first other side chamber 43AY is formed in the other side SB in the axial direction AD of the first bulging portion 64 of the first spool 60. The first other side shoulder portion 64Y of the first bulging portion 64 constitutes a part of a wall portion that divides the first other side chamber 43AY. The first other side shoulder portion 64Y facing the other side SB in the axial direction AD is pressed against the one side SA in the axial direction AD by the pressure in the first other side chamber 43AY. The valve main body 40 is provided with a first other side passage 44AY that leads to the first other side chamber 43AY.

In the illustrated example, the first one side chamber 43AX and the first other side chamber 43AY are formed between the first spool 60 and the first side block 51X. Further, the first one side passage 44AX and the first other side passage 44AY are formed in the first side block 51X.

Further, the control valve 30 further includes a movement control unit 80 that controls the movement of the first spool 60 in the axial direction AD. In the illustrated example, the movement control unit 80 switches between supplying and stopping the supply of pilot pressure oil to the first one side passage 44AX and the first other side passage 44AY. Typically, such movement control unit 80 can be referred to as a switching valve.

Further, the first through hole 61 is formed in the first spool 60 as described above. Further, in the valve body 40, a first back pressure chamber 42A that passes through the first through hole 61 of the first spool 60 to the spool hole 41 in which the first tip end surface 62 is located. There is this. The first base end surface 63 of the first spool 60 constitutes a part of a wall portion that divides the first back pressure chamber 42A. The first base end surface 63 facing one side SA in the axial direction AD is pressed against the other side SB in the axial direction AD by the pressure in the first back pressure chamber 42A. On the other hand, the first tip surface 62 facing the other side SB in the axial direction AD is pressed against one side SA in the axial direction AD by the pressure in the spool hole 41 (space S). The pressure in the first back pressure chamber 42A is maintained equally as the pressure in the spool hole 41 (space S) and the pressure oil flows through the first through hole 61. And, by making the area of the first distal end surface 62 and the area of the first proximal end surface 63 the same, the force applied to the first distal end surface 62 and the first proximal end surface 63 are The power can be equalized. Therefore, for example, even when high-pressure hydraulic oil flows into the space S, it becomes possible to smoothly move the first spool 60 with a small force.

Further, the valve body 40 has a first positioning means 56A for positioning the first spool 60 in a state in which a driving force for movement is not loaded, that is, in a neutral state. In the illustrated example, the first positioning means 56A includes a first one pressing member 57AX disposed in the first one side chamber 43AX, and a first other pressing member disposed in the first other side chamber 43AY. It has a member 57AY. The first one pressing member 57AX is disposed between the valve body 40 and the first one shoulder 64X of the first spool 60. The first one pressing member 57AX presses the first spool 60 against the other SB in the axial direction AD via the first one shoulder 64X. The first other pressing member 57AY is disposed between the valve body 40 and the first other shoulder 64Y of the first spool 60. The first other pressing member 57AY presses the first spool 60 against the one SA in the axial direction AD via the first other shoulder 64Y. At a position in the axial direction AD where the force of the first one pressing member 57AX pressing the first spool 60 and the force pressing the first other pressing member 57AY of the first spool 60 are balanced, the driving force is The unloaded first spool 60 can be positioned. The first one pressing member 57AX and the first other pressing member 57AY may be an elastic body accommodated in the first one side chamber 43AX or the first other side chamber 43AY in a compressed state, typically a compression spring. have.

On the other hand, between the second spool 70 and the valve body 40, a second one side chamber 43BX and a second second side chamber 43BY are provided. The second one side chamber 43BX is formed on one side SA of the second bulging portion 74 of the second spool 70 in the axial direction AD. The second one-side shoulder portion 74X of the second bulging portion 74 constitutes a part of the wall portion that partitions the second one-side chamber 43BX. The second one side shoulder portion 74X facing one side SA in the axial direction AD is pressed against the other side SB in the axial direction AD by the pressure in the second one side chamber 43BX. The valve body 40 is provided with a second one-side passage 44BX that passes through the second one-side chamber 43BX. Similarly, the second other side chamber 43BY is formed in the other side SB in the axial direction AD of the second bulging portion 74 of the second spool 70. The second other side shoulder portion 74Y of the second bulging portion 74 constitutes a part of a wall portion that divides the second other side chamber 43BY. The second other side shoulder portion 74Y facing the other side SB in the axial direction AD is pressed against the one side SA in the axial direction AD by the pressure in the second other side chamber 43BY. The valve body 40 is provided with a second other side passage 44BY through which the second other side chamber 43BY is passed.

In the illustrated example, the second one side chamber 43BX and the second second side chamber 43BY are formed between the second spool 70 and the second side block 51Y. Further, the second one side passage 44BX and the second second side passage 44BY are formed in the second side block 51Y.

The above-described movement control unit 80 also controls movement of the second spool 70 in the axial direction AD. The movement control unit 80 switches the supply of the pilot pressure oil to the second one side chamber 43BX and the supply stop. The second one-side passage 44BX leading to the second one-side chamber 43BX is in communication with the first one-side passage 44AX leading to the first one-side chamber 43AX. Then, under the control of the movement control unit 80, when the pilot pressure oil is supplied to the first one side chamber 43AX, the pilot pressure oil is also supplied to the second one side chamber 43BX. Further, when the supply of the pilot pressure oil to the first one side chamber 43AX is stopped under the control of the movement control unit 80, the supply of the pilot pressure oil to the second one side chamber 43BX is also stopped.

Like the first spool 60, the second through hole 71 is formed in the second spool 70. Further, in the valve body 40, a second back pressure chamber 42B that passes through the second through hole 71 of the second spool 70 to the spool hole 41 in which the second tip end surface 72 is located. There is this. The second base end surface 73 of the second spool 70 constitutes a part of a wall portion that divides the second back pressure chamber 42B. The second base end surface 73 facing the other side SB in the axial direction AD is pressed against one side SA in the axial direction AD by the pressure in the second back pressure chamber 42B. As with the first spool 60, by making the area of the second end surface 72 and the area of the second base end surface 73 the same, the force applied to the second end surface 72 and the second base end are The force applied to the surface 73 can be made the same. Therefore, for example, even when high-pressure hydraulic oil flows into the space S, it becomes possible to smoothly move the second spool 70 with a small force.

Further, the valve body 40 has a second positioning means 56B for positioning the second spool 70 in a state in which a driving force for movement is not loaded, that is, in a neutral state. In the illustrated example, the 2nd positioning means 56B has the 2nd other side urging member 57BY arrange|positioned in the 2nd other side chamber 43BY. The second second pressing member 57BY is disposed between the valve body 40 and the second other shoulder portion 74Y of the second spool 70. The second other pressing member 57BY presses the second spool 70 against the one SA in the axial direction AD via the second other shoulder 74Y. In the illustrated example, the second one side pressing member is not provided in the second one side chamber 43BX. When the second second pressing member 57BY presses the second spool 70, the first spool 60 to which no driving force is loaded can be positioned at one side SA in the axial direction AD. That is, in the illustrated example, even if there is no supply of pilot pressure oil to the second other side passage 44BY, the second spool 70 is moved to one side SA in the axial direction AD by the second positioning means 56B. I can make it. The second other pressing member 57BY can be an elastic body accommodated in the second other side chamber 43BY in a compressed state, typically a compression spring.

Next, the operation of the control valve 30 having the above configuration will be mainly described with reference to FIGS. 2 to 4. Here, FIGS. 2 to 4 are cross-sectional views schematically showing components of the control valve 30 shown in FIG. 1.

In the state shown in Fig. 2, the movement control unit 80 is not supplying the pilot pressure oil to any of the passages 44AX, 44AY, 44BX, and 44BY. That is, the movement control unit 80 stops supplying the pilot pressure oil to the respective chambers 43AX, 43AY, 43BX, and 43BY. The control valve 30 shown in Fig. 2 is in a so-called neutral position. At this time, the first spool 60 is disposed at a predetermined position positioned by the first positioning means 56A. Similarly, the second spool 70 is disposed at a predetermined position positioned by the second positioning means 56B.

In the state of Fig. 2, the notch formation portion 65 in which the notch 65C of the first spool 60 is formed overlaps only with the first actuator port 46A in the axial direction AD, and the axial direction AD from the other ports. It's out of place. In other words, the notch formation portion 65 faces only the first actuator port 46A in the direction perpendicular to the axial direction AD, and does not face the other ports. Therefore, the 1st actuator port 46A does not communicate with either of the 1st supply port 47A and the 1st discharge port 48A.

Similarly, in the state of Fig. 2, the space S between the first spool 60 and the second spool 70 overlaps only with the second actuator port (common port) 46B in the axial direction AD, and Is shifted in the axial direction AD. In other words, the space S faces only the second actuator port 46B in a direction perpendicular to the axial direction AD, and does not face other ports. Accordingly, the second actuator port (common port) 46B is not in communication with either the second supply port (first port) 47B and the second discharge port (second port) 48B. According to another expression, the first spool 60 is in the portion between the second actuator port (common port) 46B and the second supply port (first port) 47B in the spool hole 41 It is positioned and blocks the second actuator port (common port) 46B and the second supply port (first port) 47B. The second spool 70 is located in a portion between the second actuator port (common port) 46B and the second discharge port (second port) 48B in the spool hole 41, and the second The actuator port (common port) 46B and the second discharge port (second port) 48B are blocked.

Next, in the state shown in FIG. 3, the movement control unit 80 supplies pilot pressure oil to the first one-side passage 44AX and the second one-side passage 44BX. That is, the pilot pressure oil is supplied to the first one side chamber 43AX and the second one side chamber 43BX. Accordingly, the pilot pressure oil is discharged from the first other side chamber 43AY and the second other side chamber 43BY, and the first spool 60 and the second spool 70 are from the neutral position shown in FIG. As shown in, it moves to the other side SB in the axial direction AD.

In the state of Fig. 3, the notch formation portion 65 in which the notch 65C of the first spool 60 is formed is both of the first actuator port 46A and the first supply port 47A in the axial direction AD. It overlaps with and deviates from the other ports in the axial direction AD. In other words, the notch formation portion 65 faces both the first actuator port 46A and the first supply port 47A in a direction perpendicular to the axial direction AD, and does not face the other ports. As a result, the 1st actuator port 46A communicates with the 1st supply port 47A through the part where the notch 65C of the spool hole 41 is located. Then, the hydraulic oil supplied from the supply passage P passes through the first supply port 47A and the first actuator port 46A, and flows into the piston chamber 18b of the actuator 18.

In the state of Fig. 3, the space S between the first spool 60 and the second spool 70 is both of the second actuator port 46B and the second discharge port 48B in the axial direction AD. It overlaps with and deviates from the other ports in the axial direction AD. In other words, the space S faces both the second actuator port 46B and the second discharge port 48B in a direction perpendicular to the axial direction AD, and does not face other ports. As a result, the 2nd actuator port 46B communicates with the 2nd discharge port 48B through the part where the space S of the spool hole 41 is located. Then, the hydraulic oil discharged from the rod chamber 18a of the actuator 18 passes through the second actuator port 46B and the second discharge port 48B, and is recovered to a tank (not shown).

According to another expression, in the state of FIG. 3, the first spool 60 is the second actuator port (common port) 46B and the second supply port (first port) in the spool hole 41 ( It is located in the part between 47B), and blocks the 2nd actuator port (common port) 46B and the 2nd supply port (1st port) 47B. On the other hand, the second spool 70 is discharged second than the portion between the second actuator port (common port) 46B and the second discharge port (second port) 48B in the spool hole 41 Located on the port (second port) 48B side, the second discharge port (second port) 48B is at least partially opened in the spool hole 41. Thus, the second spool 70 connects the second actuator port (common port) 46B and the second discharge port (second port) 48B.

In this embodiment, the 1st spool 60 and the 2nd spool 70 are separate members. Accordingly, the narrow-width (thin diameter) connecting portion 90 as indicated by the double-dashed line in FIG. 3 does not exist between the first spool 60 and the second spool 70. Accordingly, the flow path in the spool hole 41 of the hydraulic oil from the second actuator port 46B toward the second discharge port 48B can be made thick. That is, the cross-sectional area of the hydraulic oil passage from the second actuator port 46B to the second discharge port 48B can be increased. Further, it is possible to reduce the frictional resistance of the hydraulic oil from the second actuator port 46B toward the second discharge port 48B. Thereby, compared with the case where the connection part 90 is provided, the pressure loss in the control valve 30 can be reduced significantly.

Next, in the state shown in FIG. 4, the movement control part 80 is supplying the pilot pressure oil to the 1st other side chamber 43AY. That is, the pilot pressure oil is supplied to the first other side chamber 43AY. Thereby, the pilot pressure oil is discharged from the first one side chamber 43AX, and the first spool 60 is, from the neutral position shown in FIG. 2, as shown in FIG. 4, on one side SA in the axial direction AD. Go to.

In the state of Fig. 4, the notch formation portion 65 in which the notch 65C of the first spool 60 is formed is both of the first actuator port 46A and the first discharge port 48A in the axial direction AD. It overlaps with and deviates from the other ports in the axial direction AD. In other words, the notch formation portion 65 faces both the first actuator port 46A and the first discharge port 48A in a direction perpendicular to the axial direction AD, and does not face the other ports. As a result, the 1st actuator port 46A communicates with the 1st discharge port 48A through the part where the notch 65C of the spool hole 41 is located. Then, the hydraulic oil discharged from the piston chamber 18b of the actuator 18 passes through the first actuator port 46A and the first discharge port 48A, and is recovered to a tank (not shown).

In the state of Fig. 4, the space S between the first spool 60 and the second spool 70 overlaps both of the second actuator port 46B and the second supply port 47B in the axial direction AD. , It is deviated from other ports in the axial direction AD. In other words, the space S faces both the second actuator port 46B and the second supply port 47B in a direction perpendicular to the axial direction AD, and does not face other ports. As a result, the 2nd actuator port 46B communicates with the 2nd supply port 47B through the part where the space S of the spool hole 41 is located. Then, the hydraulic oil supplied from the supply passage P passes through the second supply port 47B and the second actuator port 46B, and flows into the load chamber 18a of the actuator 18.

According to another expression, in the state of FIG. 4, the first spool 60 is the second actuator port (common port) 46B and the second supply port (first port) in the spool hole 41 ( The second supply port (first port) 47B is at least partially opened in the spool hole 41, and is positioned on the side of the second supply port (first port) 47 than the portion between 47B). Thus, the first spool 60 connects the second actuator port (common port) 46B and the second supply port (first port) 47B.

In addition, in the illustrated example, the movement control unit 80 does not supply pilot pressure oil to the first one side chamber 43AX and the second second side chamber 43BY in the state of FIG. 4. At this time, the second spool 70 is positioned by the second other pressing member 57BY of the second positioning means 56B. That is, in the state shown in Fig. 4, the first spool 60 is moving from the state shown in Fig. 2 to one side SA along the axial direction AD, but the second spool 70 is shown in Fig. 2 It is located in the same position in the axial direction AD and in the axial direction. That is, the first spool 60 and the second spool 70 are moving asynchronously.

And, the axial direction of the 1st spool 60 and the 2nd spool 70 in the state of FIG. 4 connecting two ports (specifically, the 2nd actuator port 46B and the 2nd supply port 47B) The separation distance LD along AD is longer than the separation distance LD along the axial direction AD of the first spool 60 and the second spool 70 in the state of Fig. 2 in which the connection of the two ports is cut off. As a result, at least one of the two ports to be connected can be exposed to the spool hole 41 to be larger. In the illustrated example, the connection point of the second actuator port 46B to the spool hole 41 is largely opened in the spool hole 41 without being blocked by the second spool 70. That is, in addition to removing the above-described connection portion 90, by increasing the separation distance LD between the first spool 60 and the second spool 70 to increase the space S, the inside of the control valve 30 Pressure loss can be further reduced.

In the above-described embodiment, the control valve 30 includes the valve body 40 provided with the spool hole 41 and the first spool 60 provided to be movable to the spool hole 41 of the valve body 40. ) And a second spool (70). According to this control valve 30, when connecting the two ports through the spool hole 41 through the spool hole 41, the first spool 60 and the second spool 70 are formed in the spool hole 41. They can be separated from each other. Accordingly, the first spool 60 and the second spool 70 can be moved out of the region of the spool hole that is between the opening positions (connection positions) of the two ports to be connected to the spool hole 41. Thereby, a reduction in the cross-sectional area due to the remaining portion 90 (refer to FIG. 3) of a narrow width (thin diameter) of the spool in the area connecting the two ports of the spool hole 41, or on the surface of the portion 90 Friction can be avoided. As a result, the pressure loss in the control valve 30 can be effectively reduced.

Further, in the above-described embodiment, the control valve 30 includes at least a first port (second supply port) 47B and a second port (second supply port) passing through the spool hole 41 and the spool hole 41. The valve body provided with the discharge port) 48B and the common port (second actuator port) 46B, and the spool hole 41 of the valve body 40 are movable, and the first port through the spool hole 41 (2nd supply port) 47B and the 1st spool 60 which makes the common port (2nd actuator port) 46B connectable, and the spool hole 41 of the valve body 40 are movable, It has a 2nd spool 70 which makes the 2nd port (2nd discharge port) 48B and the common port (2nd actuator port) 46B connectable. According to this control valve 30, when connecting the two ports through the spool hole 41 through the spool hole 41, the first spool 60 and the second spool 70 are formed in the spool hole 41. They can be separated from each other. Therefore, the first spool 60 and the second spool 70 can be moved outside the area of the spool hole 41 that is between the opening positions (connection positions) of the two ports to be connected to the spool hole 41. I can. Thereby, a reduction in the cross-sectional area due to the remaining portion 90 (refer to FIG. 3) of a narrow width (thin diameter) of the spool in the area connecting the two ports of the spool hole 41, or on the surface of the portion 90 Friction can be avoided. As a result, the pressure loss in the control valve 30 can be effectively reduced.

In one specific example of the above-described embodiment, the first spool 60 and the second spool 70 move asynchronously. That is, the first spool 60 and the second spool 70 can be moved independently. According to this example, it is possible to more effectively reduce the pressure loss.

In one specific example of the above-described embodiment, the first spool 60 and the second spool 60 and the second in a state in which two ports (for example, the second actuator port 46B and the second supply port 47B) are connected. The separation distance LD of the spool 70 becomes longer than the separation distance LD between the first spool 60 and the second spool 70 in a state in which the connection between the two ports is cut off. According to this example, when connecting the two ports, it is possible to more effectively reduce the pressure loss. In addition, when disconnecting the connection between the two ports, it is possible to effectively prevent unintended leakage of hydraulic oil.

In one specific example of the above-described embodiment, the control valve 30 is a first back pressure chamber 42A that passes through the first through hole 61 provided in the first spool 60 to the spool hole 41. And, a second back pressure chamber 42B that passes through the second through hole 71 provided in the second spool 70 to the spool hole 41. According to this example, the driving force required for driving the first spool 60 can be significantly reduced. In addition, the driving force required for driving the second spool 70 can be significantly reduced. Thereby, the configuration of the control valve 30 can be simplified, and the size and weight of the control valve 30 can be reduced.

In one specific example of the above-described embodiment, when the first spool 60 moves to one side (for example, from the state shown in Fig. 2 to the other side SB along the axial direction AD as shown in Fig. 3) When moving to), the second spool 70 also moves to one side, while the first spool 60 moves to the other side (for example, from the state shown in FIG. 2 to the state shown in FIG. 4 ). Similarly, when moving to one side SA along the axial direction AD), the second spool 70 is stopped. According to this example, the configuration and control for driving the second spool 70 can be simplified. In addition, by moving only the first spool 60 while the second spool 70 is stopped, it becomes possible to secure a large flow path for the pressure oil formed by the space S, and it is also possible to more effectively reduce the pressure loss. It becomes.

In one specific example of the above-described embodiment, the control valve 30 is a movement control unit (pressure oil supply control unit, which controls the supply of pilot hydraulic oil for driving the first spool 60 and the second spool 70). An example with the pressure oil supply control valve) 80 was shown. A single movement control unit 80 controls both the movement of the first spool 60 and the movement of the second spool 70. According to this example, since the positions of the first spool and the second spool can be controlled by one driving unit (pressure oil supply control unit and pressure oil supply control valve), the size and weight of the directional valve can be reduced.

Although one embodiment has been described with reference to a specific example, the above-described specific example is not intended to limit one embodiment. The above-described embodiment can be implemented in various other specific examples, and various omissions, substitutions, changes, and additions can be made without departing from the gist of the embodiment.

Hereinafter, an example of the modification will be described with reference to the drawings. In the following description and the drawings used in the following description, the same reference numerals as those used for the corresponding portions in the above-described specific examples are used for portions that can be configured similarly to the above-described specific examples, and overlapping Omit the explanation.

First, even when the first spool 60 and the second spool 70 move to either side in the axial direction AD, they may move synchronously. According to this example, it becomes possible to effectively reduce the pressure loss by simple control and configuration.

Specifically, the control valve 30 may be configured as follows. First, in addition to the second other side pressing member 57BY, the second positioning means 56B further includes a second one side pressing member in the second one side chamber 43BX. This second one-side pressing member is disposed between the valve body 40 and the second one-side shoulder portion 74X of the second spool 70, and the second spool 70 is axially formed through the second one-side shoulder portion 74X. Press the other SB in the direction AD. The second spool 70 in the neutral position is disposed at a position where the force from the second other pressing member 57BY and the force from the second one pressing member are balanced, and from the neutral position in the axial direction AD You can move on both sides.

In addition, the movement control unit 80 switches the supply of the pilot pressure oil and the supply stop to the second other side chamber 43BY in addition to the second one side chamber 43BX. Specifically, the second other side passage 44BY leading to the second other side chamber 43BY may be connected to the first other side passage 44AY leading to the first other side chamber 43AY. According to this example, when the pilot pressure oil is supplied to the first other side chamber 43AY under the control of the movement control unit 80, the pilot pressure oil is also supplied to the second other side chamber 43BY. Further, when the supply of the pilot pressure oil to the first other side chamber 43AY is stopped under the control of the movement control unit 80, the supply of the pilot pressure oil to the second other side chamber 43BY is also stopped.

According to this example, the first spool 60 and the second spool 70 can be moved synchronously. According to this example, pressure loss can be effectively reduced by simple control and configuration.

In addition, in the above-described example, one movement control unit 80 controls both movement of the first spool 60 and movement of the second spool 70. However, it is not limited to this example, and the control valve 30 includes a first movement control unit 80A that controls the movement of the first spool 60, and a second movement that controls the movement of the second spool 70. You may have the control part 80B separately. According to this example, the movement of the first spool 60 and the second spool 70 can be independently controlled. Therefore, it is possible to more effectively reduce the pressure loss.

As an example of such a modification, the control valve 30 shown in FIG. 5 includes a first movement control unit (first hydraulic oil supply control unit) 80A that controls the supply of pilot hydraulic oil for driving the first spool 60. , A second movement control unit (second hydraulic oil supply control unit) 80B that controls the supply of pilot hydraulic oil for driving the second spool 70 may be separately provided. According to this example, movement of the first spool 60 and the second spool 70 can be independently controlled by a simple configuration and simple control.

In the example shown in FIG. 5, the first movement control unit 80A and the second movement control unit 80B may be configured by, for example, a switching valve for switching a flow path, similar to the movement control unit 80 described above. have. For example, in the state shown in Fig. 6, from the neutral state shown in Fig. 2, both the first spool 60 and the second spool 70 are moved to the other side SB along the axial direction AD. However, the amount of movement of the second spool 70 to one side SA along the axial direction AD is longer than the amount of movement of the first spool 60 to one side SA along the axial direction AD. As a result, separation of the first spool 60 and the second spool 70 in the axial direction AD in the state of Fig. 6 in which the two ports (the second actuator port 46B and the second discharge port 48B) are connected. The distance LD is longer than the separation distance LD between the first spool 60 and the second spool 70 in the state of Fig. 2 in which the connection of the two ports is cut off. According to this example, it is possible to more effectively reduce the pressure loss. In addition, the position of the first spool 60 in Fig. 6 is the same as the position of the first spool 60 in Fig. 3, and the position of the second spool 70 shown by the double-dashed line in Fig. The position is the same as that of the second spool 70 in FIG. 3. And, the distance between the first spool 60 and the second spool 70 in the axial direction AD in the state of FIG. 3 in which the two ports (the second actuator port 46B and the second discharge port 48B) are connected. LD is equal to the separation distance LD between the first spool 60 and the second spool 70 in the state of Fig. 2 in which the connection of the two ports is cut off.

On the other hand, in the control valve 30 shown in FIG. 5, when moving the first spool 60 to one side SA along the axial direction AD, the second movement control unit 80B is similar to the example shown in FIG. Likewise, the second spool 70 may be in a stopped state, and the second spool 70 may be moved to one side SA along the axial direction AD only with a small amount of movement of the first spool 60.

However, depending on the type of actuator to be driven, the supply and discharge of the pressure oil to the actuator is controlled by a control method called a single acting type or a hammer type. In a conventional control method, both supply of the hydraulic oil to the actuator and the discharge of the hydraulic oil from the actuator are performed simultaneously in two passages in one control valve. The supply amount of the hydraulic oil to the actuator and the discharge amount of the hydraulic oil from the actuator are balanced by the control of the proportional valve that drives the spool. However, in a control method called a single acting type or a hammer type, the supply of hydraulic oil to the actuator is realized by driving the spool as usual, but the discharge path of the hydraulic oil from the actuator is kept completely open or a certain amount open. . For example, in mechanical equipment such as a hammer, the hydraulic oil is discharged when the supplied hydraulic oil pressure exceeds a predetermined value. Accordingly, the amount of supply of the hydraulic oil to the actuator through the control valve and the discharge amount of the hydraulic oil are greatly different. If such pressure oil is discharged from the control valve, there is a possibility that the control valve will be damaged. Therefore, in a control method called a single acting type or a hammer type, it is necessary to separately provide a dedicated discharge path that does not pass through the control valve, so that the hydraulic circuit is complicated and the hydraulic equipment has been enlarged.

On the other hand, this embodiment is also very suitable for a control method called such a single acting type or a hammer type. For example, as shown in FIG. 6, by controlling the position of the first spool 60, the amount of hydraulic oil supplied to the actuator 18 can be controlled. On the other hand, by holding the second spool 70 in a predetermined position, for example, the second spool 70 is held in a position where the second discharge port 48B is completely opened, and thus the position of the first spool 60 The pressure oil discharge path capable of always discharging a predetermined amount of pressurized oil can be secured in the control valve 30 without being particular about this. Accordingly, it is possible to simplify the hydraulic circuit 20 and reduce the size and weight of the hydraulic device 15 by eliminating the need to provide a separate discharge path.

In addition, in the specific example described above, an example in which the movement control unit 80, 80A, 80B is configured using a pressure oil supply control unit (e.g., a pressure oil supply control valve) that switches the supply and stop of supply of the pilot hydraulic oil Although shown, it is not limited to this example, Other means, such as a motor, etc. may be used.

In addition, in the above-described example, an example in which both the first spool 60 and the second spool 70 are disposed in the straight spool hole 41 was shown. In this example, a portion of the first spool 60 and a portion of the second spool 70 may be disposed at the same position within the spool hole 41. However, it is not limited to the above-described example. For example, as shown in Figs. 7 and 8, the first spool 60 is movable in the first spool hole 41A, and the second spool 70 in the second spool hole 41B. ) May be movable. In the example shown in Figs. 7 and 8, the center axis CA1 of the first spool hole 41A and the center axis line CA2 of the second spool hole 41B are shifted and are not positioned on a straight line.

In the example shown in Figs. 7 and 8, the control valve 30 is a first port (second supply port 47B) through the first spool hole 41A and the first spool hole 41A, 2 A second port (2nd discharge port (48B)) through the spool hole (41B) and the second spool hole (41B), and a common port through the first spool hole (41A) and the second spool hole (41B) ( The valve body 40 provided with the second actuator port 46B) and the first spool hole 41A of the valve body 40 are movable, and the first port (the second The first spool 60 to which the supply port 47B) and the common port (the second actuator port 46B) can be connected, and the second spool hole 41B of the valve body 40 can be moved, and the second port It has a 2nd spool 70 which can connect (2nd discharge port 48B) and a common port (2nd actuator port 46B). Also by this control valve 30, the same effect as in the above-described embodiment can be exhibited.

In addition, although several modifications to the above-described embodiment have been described above, it is naturally possible to appropriately combine and apply a plurality of modifications.

Claims (12)

A valve body provided with a spool hole, and at least a first port, a second port, and a common port through the spool hole,
A first spool capable of moving the spool hole of the valve body and connecting the first port and the common port through the spool hole;
A second spool capable of moving the spool hole of the valve body and connecting the second port and the common port
Equipped with a control valve. A first spool hole and a first port through the first spool hole, a second spool hole and a second port through the second spool hole, and a common port through the first spool hole and the second spool hole are provided. The valve body,
A first spool capable of moving the first spool hole of the valve body and connecting the first port and the common port through the first spool hole;
A second spool capable of moving the second spool hole of the valve body and connecting the second port and the common port
Equipped with a control valve. The control valve according to claim 1 or 2, wherein the first spool and the second spool move synchronously. The control valve according to claim 1 or 2, wherein the first spool and the second spool move asynchronously. The method according to claim 1 or 2, wherein in a state in which the first port and the common port are connected, the first spool and the second spool are more Control valves with longer separation distances. The control according to claim 1, further comprising: a first back pressure chamber communicating with the spool hole through a through hole provided in the first spool, and a second back pressure chamber communicating with the spool hole through a through hole provided in the second spool. valve. The control valve according to claim 1 or 2, comprising: a first movement control unit that controls movement of the first spool, and a second movement control unit that controls movement of the second spool. The first movement control unit of claim 1 or 2, further comprising: a first movement control unit that controls supply of pilot hydraulic oil for driving the first spool, and a second movement control unit that controls supply of pilot hydraulic oil to drive the second spool. With a control valve. The method according to claim 1 or 2, wherein when the first spool moves to one side, the second spool also moves to one side,
When the first spool moves to the other side, the second spool is stopped. A hydraulic circuit comprising the control valve according to claim 1 or 2. The hydraulic circuit according to claim 10, and
A hydraulic machine comprising an actuator controlled by the hydraulic circuit. A construction machine comprising the hydraulic circuit according to claim 10.

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