KR20200007678A - Valve structure and construction machinery - Google Patents

Abstract

Provided are a valve structure and construction machinery having the same, wherein the valve structure is applicable to various forms. The valve structure (10) includes a valve unit (15), a drive unit (16), and a valve controller (17). The drive unit (16) drives the valve unit (15) in accordance with a drive current. The valve controller (17) controls the drive current supplied to the drive unit (16). The valve controller (17) is supported by the drive unit (16).

Description

VALVE STRUCTURE AND CONSTRUCTION MACHINERY

The present invention relates to a valve structure and a construction machine.

Construction machinery, such as a hydraulic excavator, is equipped with a hydraulic actuator and adjusts the flow of the pressurized oil (namely, working oil) supplied to a hydraulic actuator by an electromagnetic valve etc. (henceforth an "electric drive valve") electrically driven, and a hydraulic actuator. Can be operated. For example, in the hydraulic drive device disclosed in Patent Literature 1, the output pressure of the electromagnetic proportional control valve is applied to the direction control valve as a pilot pressure, and the direction control valve supplies oil of the flow rate corresponding to the pilot pressure to the corresponding actuator. do.

Japanese Patent Publication No. 2014-142032

In the machine provided with a hydraulic actuator, when adjusting the flow of pressure oil by an electric drive valve, it is necessary to provide the number of electric drive valves according to the number of hydraulic actuators. In particular, it is necessary to drive various hydraulic actuators in construction machinery, and the number of electric drive valves tends to increase. For example, when operating a boom, an arm, a bucket, a turning device, and a traveling device by a hydraulic actuator in a hydraulic excavator, it is necessary to provide five or more electric drive valves.

Particularly in the field of construction machinery, in recent years, as a control method of a hydraulic actuator, from a control method using only hydraulic pressure, to a control method using a combination of control using hydraulic pressure (hydraulic control) and control using electric drive valves (electric control), have. For example, when changing the drive speed of a hydraulic actuator according to the operation amount of an operation lever, although it was necessary to tune the opening degree of a spool conventionally, what is necessary is just to adjust a drive current, when using an electric drive valve. As such, the demand for utilization of the electric drive valve in the control of the hydraulic actuator is expected to increase gradually in the future.

The electric drive valve is controlled by the controller, and the controller can appropriately operate each hydraulic actuator by supplying a drive current to each electric drive valve. This controller is usually composed of a microcomputer provided under a clean environment of the main body of the machine, and in many cases, a plurality of electric drive valves are collectively driven and controlled by one controller (that is, one microcomputer). . In this case, it is necessary to assume the number or type of electric drive valves used at the stage of designing the controller. In particular, since a drive circuit (output port) for supplying a drive current to the electric drive valve needs to be provided for each electric drive valve, the controller is required to have a number of drive circuits corresponding to the number of the electric drive valves.

On the other hand, the conventional controller which collectively drives and controls a plurality of electric drive valves cannot later provide an additional drive circuit (output port), and can flexibly cope with an increase in the number of electric drive valves. none. In other words, if it is necessary to increase the number of electric drive valves after the design of the controller (especially when the number of drive circuits is insufficient), replace the existing controller with a new controller having an appropriate number of drive circuits or replace the new controller. It needs to be connected with controller of. The installation of a new controller requires a large amount of cost and a need to reconsider device designs such as wiring, which is a barrier to increasing the number of electric drive valves later.

There is also a desire to additionally mount electric drive valves for existing machines that do not have a controller. However, as described above, the installation of a new controller requires a great deal of labor and cost, preventing the introduction of a new electric drive valve for a machine without a controller.

In addition, a controller that collectively drives and controls a plurality of electric drive valves tends to be complicated in size and increase in size as the number of electric drive valves increases. Therefore, as the number of electric drive valves increases, the structure of the controller becomes complicated and enlarged, the controller itself becomes expensive, and the labor and cost associated with the installation of the controller also increase.

As such, a machine that collectively drives and controls a plurality of electric drive valves by one controller lacks adaptability to variations in the number of electric drive valves. In particular, in the field of construction machinery, it is expected that the demand for utilization of the electric drive valve will gradually increase in the future, and therefore, a valve structure that can be flexibly applied to various forms is desired.

This invention is made | formed in view of the above-mentioned situation, and an object of this invention is to provide the valve structure applicable to various forms, and the technique related to such a valve structure.

An aspect of the present invention includes a valve unit, a drive unit for driving the valve unit in accordance with a drive current, and a valve controller for controlling drive current supplied to the drive unit, wherein the valve controller relates to a valve structure supported by the drive unit. will be.

The drive unit may include a movable unit that moves on the reference axis in accordance with the drive current, and the valve controller may be provided at a position shifted from the drive unit with respect to the direction parallel to the reference axis.

The drive unit may include a movable unit that moves on the reference axis in accordance with the drive current, and the valve controller may be provided at a position shifted from the drive unit with respect to the radial direction perpendicular to the reference axis.

The valve controller may be disposed in a sealed space.

The drive unit may include an electromagnet through which a drive current flows, and a plunger that moves in accordance with a magnetic force caused by the electromagnet.

The valve portion may include a spool driven by the drive portion.

The valve controller may supply a drive current to the drive unit in accordance with a drive signal input from another controller.

The valve controller may supply a drive current to the drive unit in accordance with a detection signal input from the sensor.

The valve controller may be accommodated in the valve housing within the range of the width in the radial direction of the valve housing accommodating the drive portion.

Another aspect of the present invention relates to a construction machine comprising the valve structure described above.

According to the present invention, it is possible to provide a valve structure applicable in various forms and a technique related to such a valve structure.

1 is a side view illustrating the outline of a valve structure.
2 is a block diagram showing a functional configuration of a valve controller.
3 is a cross-sectional view illustrating a typical example of a drive unit.
4: A is sectional drawing which shows schematic structure of the positive proportional electromagnetic proportional valve.
4B is a sectional view showing a schematic configuration of a positive type electromagnetic proportional valve.
4C is a cross-sectional view illustrating a schematic configuration of a positive type electromagnetic proportional valve.
5: A is sectional drawing which shows schematic structure of the negative proportional electromagnetic proportional valve.
5B is a cross-sectional view illustrating a schematic configuration of a negative type electromagnetic proportional valve.
5C is a cross-sectional view illustrating a schematic configuration of a negative type electromagnetic proportional valve.
6 is an external view showing an outline of a typical structural example of a hydraulic excavator.
7 is a diagram illustrating an example of the control mode.
8 is a diagram illustrating another example of the control mode.
9 is a cross-sectional view showing a modification of the drive unit.

EMBODIMENT OF THE INVENTION Hereinafter, one Embodiment of this invention is described with reference to drawings.

1 is a side view illustrating the outline of the valve structure 10. The valve structure 10 is comprised as an electromagnetic proportional valve provided with the valve part 15, the drive part 16, and the valve controller 17. The drive part 16 drives the valve part 15 according to a drive current, and operates the valve part 15. FIG. The valve controller 17 controls the drive current supplied to the drive unit 16, and supplies the drive current according to the operation of the valve unit 15 to the drive unit 16.

The valve structure 10 shown in FIG. 1 has a valve housing 20 and a base 21. The valve housing 20 is provided to extend along the reference axis Ax. The drive part 16 and the valve controller 17 are accommodated inside the valve housing 20 in a state arranged along the reference axis Ax. That is, the valve controller 17 is provided in the position which shifted from the drive part 16 with respect to the direction Dx (henceforth an "axial direction") parallel to the reference axis Ax. Thus, the valve controller 17 is within the range of the width | variety of the radial direction (that is, radial direction) Dr which is perpendicular to the reference axis Ax of the valve housing 20 which accommodates the drive part 16, The valve housing 20 ), It is possible to prevent the enlargement of the valve structure 10 in the radial direction Dr. Moreover, in the valve structure 10 of illustration, the movable part (refer the code | symbol "25" of FIG. 3 mentioned later) of the drive part 16 is provided on the reference axis | shaft Ax so that the movement is possible, and the valve controller 17 also reference | standards It is provided on the axis Ax.

The base 21 is fixedly connected to one end of the valve housing 20, is provided to extend in the radial direction Dr, and serves as a connecting portion for providing the valve structure 10 to the other member. For example, a mounting hole (not shown) (not shown) is formed in the base 21, and a fastener such as a screw, bolt, or screw is fitted into the mounting hole, and the fastener is fixed to the base 21. The valve structure 10 can be attached to another member.

The valve controller 17 of this embodiment is supported by the drive unit 16. In the valve structure 10 shown in FIG. 1, each of the drive part 16 and the valve controller 17 is provided in the valve housing 20, and the valve controller 17 drives the drive part 16 via the valve housing 20. Indirectly). In addition, the valve controller 17 may be directly supported by the drive unit 16, and for example, the valve controller 17 may be supported by an end position stopper 33 (see FIG. 3) described later. By employing the structure in which the valve controller 17 is supported by the drive unit 16, the valve structure 10 can unitize the drive unit 16 and the valve controller 17. As described above, according to the present embodiment, it is possible to provide the valve structure 10 which is compactly formed as a whole while physically integrally providing the elements related to both the driving and the control of the valve unit 15. Since the valve structure 10 has already provided the drive part 16 and the valve controller 17 which are necessary for operation | movement in the valve part 15, it is excellent in handleability and adaptability, and is mentioned in various forms as mentioned later. It is possible to apply flexibly.

Moreover, the valve controller 17 shown in FIG. 1 is arrange | positioned in the closed space Ss. Specifically, the liquid tightly sealed space Ss is formed in the valve housing 20, and the valve controller 17 is arrange | positioned in the sealed space Ss. As a result, the liquid such as the pressurized oil can be prevented from entering the sealed space Ss, and the occurrence of the failure of the valve controller 17 can be effectively avoided. In particular, since the construction machinery is often used under a strict environment, foreign matters (for example, dust or dirt) other than the pressurized oil may scatter during use, affecting the valve controller 17. In this regard, such a concern can be eliminated by arranging the valve controller 17 in the sealed space Ss as in the present embodiment.

In addition, the sealing degree of the sealed space Ss is not limited, and on the basis of the actual device configuration and the use environment, the degree to which the problem can be effectively prevented from occurring in the valve controller 17 by foreign matter such as hydraulic oil can be effectively prevented. It is preferable to have a sealing degree and the sealing space Ss. Therefore, from the viewpoint of preventing the water and the pressurized oil component floating in the air from entering the sealed space Ss, the sealed space Ss is provided airtight and the outside air may be prevented from entering the sealed space Ss. In practice, however, it is sometimes desirable that outside air be taken into the sealed space Ss from the viewpoint of temperature adjustment or the like. Therefore, it is preferable that the sealing degree of the sealed space Ss is determined in consideration of various requirements.

In addition, the space in the valve housing 20 in which the drive part 16 is arrange | positioned may be filled with oil, such as pressure oil. In that case, it is preferable that a seal structure is provided to prevent oil from leaking out from the space in the valve housing 20 in which the drive unit 16 is disposed.

Next, the typical example of the valve controller 17 is demonstrated.

2 is a block diagram showing the functional configuration of the valve controller 17. Each functional block of the valve controller 17 may be realized by any hardware and / or software, and for example, two or more functional blocks may be realized by a single hardware / software. In addition, the valve controller 17 may have a functional structure different from the functional structure shown in FIG. For example, the input unit 53 may input and output various types of information between the sensor 73 and the other controller 72 through communication means such as CAN communication.

The valve controller 17 shown in FIG. 2 includes a processing unit 51, a storage unit 52, an input unit 53, a drive current supply unit 54, and an output unit 55.

The processing unit 51 is a processing device that performs an operation based on various kinds of information and outputs an operation result, and can be configured by, for example, a computing circuit such as a central processing unit (CPU). The storage unit 52 is a memory device that stores various data and writes and reads data as necessary, and can be configured by, for example, an EEPROM or the like. The processing unit 51 inputs information via the input unit 53 or the like, reads information from the storage unit 52 and / or writes the information to the storage unit 52 as necessary, and the driving current supply unit 54. And outputs information to the output unit 55. In addition, "information" handled in the valve controller 17 is a concept that can be broadly interpreted and include various data such as numerical values, instructions (commands) to other devices, and other information.

The input unit 53 functions as an input interface unit of the valve controller 17, is connected to the processing unit 51, and various external devices are connected. The input unit 53 supplies the input information to the processing unit 51 in accordance with a signal input from a connected external device. Although the external device which can be connected to the input part 53 is not limited, In this embodiment, it is possible to connect the other controller 72 and / or the sensor 73 to the input part 53. FIG. For example, the other controller 72 may transmit the drive signal which instructs supply of the drive current to the drive part 16, and the magnitude | size of the drive current to the input part 53. FIG. The integrated controller (refer to reference numeral 18 in FIG. 7) to be described later may correspond to the “other controller 72” referred to herein. The sensor 73 detects predetermined information and inputs a detection signal indicating the detection result to the input unit 53. The sensor 73 can detect arbitrary information required for supplying the drive current to the drive unit 16 and determining the magnitude of the drive current, and for example, the flow is adjusted by the valve unit 15. The flow rate and / or pressure of the pressurized oil in the flow path may be detected.

The output part 55 functions as an output interface part of the valve controller 17, is connected to the process part 51, and various external devices are connected. The output part 55 outputs the signal containing various information to an external device according to the information from the process part 51. FIG. The output part 55 shown in FIG. 2 includes the information output part 56 connected to the display device 74, and the abnormal output part 57 connected to the warning device 75. The information output unit 56 transmits a signal including data input to the processing unit 51 and / or data derived by the processing unit 51 to the display device 74. The display device 74 displays various types of information in accordance with the signal from the information output unit 56. The abnormality output unit 57 outputs an output signal indicating the detected abnormality to the alarm device 75 when an abnormality is detected from data input to the processing unit 51 and / or data derived by the processing unit 51. Send. The processing for detecting such an abnormality may be performed by the processing unit 51 or may be performed by the abnormal output unit 57. The alarm device 75 issues an alarm such as a display or a voice indicating an abnormality as necessary based on the signal from the abnormal output unit 57.

The drive current supply unit 54 supplies a drive current to the drive unit 16 in accordance with the information from the processing unit 51. The processor 51 directly or indirectly measures the magnitude of the drive current required to drive the valve unit 15 based on data input from the other controller 72 and / or the sensor 73 through the input unit 53. To derive. The drive current supply unit 54 supplies a drive current to the drive unit 16 in accordance with this derivation result of the processing unit 51, and a drive current having a desired magnitude is applied to the drive unit 16. The drive current is energy for driving the drive unit 16 (particularly, the movable unit 25), and the drive current supply unit 54 uses electricity from the power source 71 connected to the valve controller 17. The drive current is supplied to the driver 16.

Thus, the valve controller 17 can supply a drive current to the drive part 16 according to the drive signal input from the other controller 72. In addition, the valve controller 17 may supply a drive current to the drive unit 16 in accordance with a detection signal input from the sensor 73.

Next, a typical example of the drive unit 16 will be described.

3 is a cross-sectional view illustrating a typical example of the drive unit 16. 3, although the drive part 16 comprised from what is called a push solenoid actuator is shown, the drive system and structure of the drive part 16 are not limited. Therefore, the drive part 16 which employ | adopts a pull type drive system, for example may be used in the valve structure 10 mentioned above.

The drive part 16 includes the movable part 25 which moves on the reference axis Ax according to a drive current. Specifically, the drive unit 16 includes an electromagnet 27 through which the drive current supplied from the valve controller 17 flows, and a plunger 28 that moves in accordance with the magnetic force caused by the electromagnet 27. .

The movable part 25 shown in FIG. 3 has the plunger 28, the push rod 30 fixedly provided with respect to one end part (right end part of FIG. 3) of the plunger 28, and the other of the plunger 28. As shown in FIG. And a spring stopper 32 fixedly mounted relative to one end (left end in FIG. 3). The spring stopper 32, the plunger 28, and the push rod 30 are arranged along the reference axis Ax, and are provided to be movable integrally in the axial direction Dx according to the magnetic force of the electromagnet 27. have.

The electromagnet 27 is composed of a solenoid coil, and in the drive unit 16 shown in FIG. 3, the movable part 25 (particularly the plunger 28 and the push rod 30) is provided inside the box-shaped drive housing 26. ), An electromagnet 27 is disposed. In addition, the drive housing 26 may be comprised by a part of the valve housing 20, and may be comprised separately from the valve housing 20. FIG. Although the spring stopper 32, the plunger 28, and the push rod 30, which are integrally provided, are provided to penetrate the drive housing 26 as a whole, the spring stopper 32 is disposed outside the drive housing 26. do. On the other hand, the plunger 28 and the push rod 30 are partially disposed inside the drive housing 26. In addition to the spring stopper 32, although the end position stopper 33 and the spring 29 which are mentioned later are arrange | positioned outside the drive housing 26 in FIG. 3, the valve housing 20 (refer FIG. 1) ) Is located inside.

The plunger stopper 31 is provided in the drive housing 26. The plunger stopper 31 is provided so that it may extend in the axial direction Dx (especially the reverse axial direction Dx2) toward the inside of the drive housing 26, and the through hole extended along the reference axis Ax is formed. The push rod 30 is disposed in the through hole and penetrates the plunger stopper 31, and is provided to be reciprocated in the axial direction Dx without being impeded by the plunger stopper 31. The end part (left end part of FIG. 3) of the plunger stopper 31 of the plunger stopper 31 has the shape corresponding to the shape of the plunger 28. As shown in FIG. In the drive part 16 shown in FIG. 3, the edge part (right end part of FIG. 3) of the plunger stopper 31 side of the plunger 28 has a taper shape, and the edge part (of the plunger 28 side of the plunger stopper 31) ( In the left end part of FIG. 3, a recess having a tapered surface is formed. And the plunger 28 engages in the said recessed part of the plunger stopper 31, and the movement to the axial direction Dx (especially forward axial direction Dx1) of the plunger 28 is restrict | limited. Thus, the plunger stopper 31 acts as a member for guiding the push rod 30 and acts as a member for limiting the movement of the plunger 28 (ie, the movable portion 25).

A spring 29 in a compressed state is disposed between the spring stopper 32 and the drive housing 26. The spring 29 imparts elastic force to the spring stopper 32 and the drive housing 26 so as to widen the distance between the spring stopper 32 and the drive housing 26 (particularly, the distance in the axial direction Dx).

When the drive current flows through the electromagnet 27 by the valve controller 17, the plunger 28 is drawn into the drive housing 26. That is, the plunger 28 is attracted to the electromagnet 27 by magnetic force, and moves to an axial direction Dx (especially forward axial direction Dx1). At this time, the spring 29 is compressed between the spring stopper 32 and the drive housing 26, and the elastic force applied to the spring stopper 32 and the drive housing 26 from the spring 29 is increased. Therefore, the movable part 25 (namely, the spring stopper 32, the plunger 28, and the push rod 30) is applied by the spring 29 in a state where the plunger 28 and the plunger stopper 31 are not in contact. The losing elastic force and the magnetic force applied by the electromagnet 27 are disposed at a balanced position. Therefore, when no driving current is supplied to the electromagnet 27, no magnetic force is applied to the plunger 28, and the movable portion 25 is disposed on the left side relatively in FIG. 3 under the elastic force of the spring 29. , The amount of protrusion of the push rod 30 from the drive housing 26 is relatively small. On the other hand, when a driving current is applied to the electromagnet 27, a magnetic force is applied to the plunger 28, and the movable portion 25 is disposed on the right side relatively in FIG. 3, and the push rod from the drive housing 26 The amount of protrusion of 30) becomes relatively large.

Moreover, the end position stopper 33 is fixedly provided on the opposite side to the spring 29 via the spring stopper 32. For example, the end position stopper 33 may be fixedly supported by the valve housing 20. The contact of the spring stopper 32 with the end position stopper 33 limits the movement of the spring stopper 32 (i.e., the movement in the reverse axial direction Dx2), while the plunger 28 contacts the plunger stopper 31 so as to contact the plunger. Movement of 28 (ie, movement in the forward axial direction Dx1) is limited. Therefore, according to the position of the end position stopper 33, the minimum protrusion amount of the push rod 30 from the drive housing 26 is determined, and also according to the position of the plunger stopper 31, from the drive housing 26 The maximum protrusion amount of the push rod 30 is determined.

Moreover, it is preferable that a heat insulator (not shown) is provided between the drive part 16 (especially the electromagnet 27 shown in FIG. 3) and the valve controller 17, for example by the valve housing 20. The heat insulator may be fixedly supported. In this case, heat emitted from the valve controller 17 can be prevented from being transmitted to the drive unit 16, and heat transmitted from the drive unit 16 can be prevented from being transmitted to the valve controller 17.

Next, the typical example of the valve part 15 is demonstrated.

Hereinafter, although the valve part 15 is comprised by the electromagnetic proportional valve for supplying the hydraulic pressure of a desired pressure with respect to a hydraulic actuator, the structure and function of the valve which comprise the valve part 15 are not limited. Do not.

An electromagnetic proportional valve capable of controlling the supply pressure of the hydraulic oil in accordance with the drive current (that is, the excitation current) is connected to a hydraulic device such as a hydraulic actuator to supply the hydraulic pressure of a desired pressure to the hydraulic device. In addition, the pressurized oil here is not necessarily limited to oil, such as mineral oil, and is a concept which can contain the whole fluid (especially liquid) which can be used as an energy transmission medium. In general, a type of electromagnetic proportional valve includes a positive electromagnetic proportional valve and a negative type electromagnetic proportional valve. As the driving current increases, the electromagnetic proportional valve in which the pressure (ie hydraulic pressure) of the output hydraulic oil is increased is classified as a positive electromagnetic proportional valve, and the electromagnetic proportional valve in which the pressure of the output hydraulic oil is lowered is proportional to the negative type. Are classified as valves.

As the valve part 15 mentioned above, both the positive type electromagnetic proportional valve and the negative type electromagnetic proportional valve can be employ | adopted. The valve part 15 illustrated below is comprised by the spool type electromagnetic proportional valve, and the spool driven by the drive part 16 is provided. First, the positive valve portion 15 will be described, and then the negative valve portion 15 will be described.

Positive valve section

4A to 4C are cross-sectional views showing the schematic configuration of the valve unit 15 of the positive type. 4A shows a non-excited state in which no drive current flows through the drive unit 16. 4B shows a state in which a relatively small drive current flows through the drive unit 16 and the spool main body 112 is disposed at a neutral position. 4C shows a state in which a relatively large drive current flows through the drive unit 16.

The valve part 15 shown to FIGS. 4A-4C is equipped with the valve main body 111, the spool main body 112, and the press part 114. As shown in FIG. The valve body 111 includes a valve hole 121 extending in the axial direction Dx, an inlet port 131, an outlet port 132, a drain port 133, and an output port (opened through the valve hole 121). 134). The inlet port 131 communicates with the hydraulic pressure source P for supplying the pressurized oil, and the outlet port 132 communicates with the drainage portion T through which the pressurized oil is discharged. The drain port 133 communicates with the drain portion through which the pressurized oil is discharged. In the valve part 15 shown to FIGS. 4A-4C, the drain part T acts as a drain part, and the outlet port 132 and the drain port 133 have a common drain part T (namely, a drain part). Communicate on The output port 134 communicates with the hydraulic actuator A which is a supply object of hydraulic oil. The specific structure of the hydraulic actuator A is not limited, Typically, the hydraulic actuator A is comprised by a hydraulic cylinder or a hydraulic motor.

The valve hole 121 has a large diameter hole portion 122 having a first diameter H1 with respect to the radial direction Dr perpendicular to the axial direction Dx, and a second smaller than the first diameter H1 with respect to the radial direction Dr. A small diameter hole 123 having a diameter H2. The large diameter hole part 122 is provided adjacent to the small diameter hole part 123, and is arrange | positioned rather than the small diameter hole part 123 in the forward axial direction Dx1 side. One end side of the spool body 112 is disposed in the large diameter hole portion 122, and the other end side of the spool body 112 is disposed in the small diameter hole portion 123. Although not shown clearly in FIG. 4A-4C, each of the large diameter hole part 122 and the small diameter hole part 123 forms a closed space, and is filled with the hydraulic oil supplied from the hydraulic pressure source P. In FIG. . In addition, the large diameter hole 122 communicates with the hydraulic actuator A via the output port 134.

The drain space 124, which is a space surrounded by the small diameter spool portion 146, the large diameter spool portion 147, and the valve body 111 among the large diameter hole portions 122, has an axial direction of the spool body 112. The volume changes depending on the position of Dx, but communicates with the drain port 133 regardless of the position of the spool body 112 in the axial direction Dx. Therefore, irrespective of the position of the spool main body 112 in the axial direction Dx, the oil pressure in the drain space 124 flows out to the drain part T through the drain port 133, and the valve main body 111 and the spool The main body 112 does not receive pressure from the pressurized oil in the drain space 124.

The spool body 112 is arranged to be movable in the axial direction Dx in the valve hole 121. One end side of the spool main body 112 is disposed in the large diameter hole 122, and the other end side of the spool main body 112 is disposed in the small diameter hole 123. On one end side of the spool body 112 disposed in the large diameter hole portion 122, a large diameter spool portion 147 having an outer diameter corresponding to the diameter of the large diameter hole portion 122 is provided. On the other end side of the spool body 112 disposed in the small diameter hole 123, a small diameter spool portion 146 having an outer diameter corresponding to the diameter of the small diameter hole 123 is provided.

The large diameter spool portion 147 is in close contact with the inner wall surface of the valve body 111 (especially the inner wall surface forming the large diameter hole 122) to the extent that the movement of the spool body 112 in the axial direction Dx is allowed. It is. In addition, the small diameter spool portion 146 is formed on the inner wall surface of the valve body 111 (in particular, the inner wall surface forming the small diameter hole 123) to the extent that the movement of the spool body 112 in the axial direction Dx is allowed. It is in close contact. However, the oil pressure in the valve hole 121 does not basically pass between the large diameter spool part 147 and the valve main body 111, and the small diameter spool part 146 and the valve main body 111. As shown in FIG.

The spool body 112 includes a spool hole 141 extending in the axial direction Dx, a contact hole 142, an outlet hole 143, an inlet hole 144, and a control hole 145 that are opened through the spool hole 141. Has In this embodiment, the contact hole 142 and the control hole 145 are formed in the both ends of the spool main body 112, respectively, and the exit hole 143 and the inlet hole 144 are the contact of the spool main body 112, respectively. It is formed in the part between the hole 142 and the control hole 145.

The contact hole 142, the outlet hole 143, and the inlet hole 144 are opened in the radial direction Dr. In particular, the contact hole 142 is opened by the small diameter hole 123, and the small diameter hole 123 and the spool hole 141 are not bound to the position of the axial direction Dx of the spool main body 112. Communicate with each other. Also, depending on the position of the spool body 112 in the axial direction Dx, the outlet hole 143 is an inner wall surface of the outlet port 132 or the valve body 111 (in particular, an inner wall surface forming the large diameter hole 122). The inlet hole 144 is opened toward the inner wall surface of the inlet port 131 or the valve body 111 (in particular, the inner wall surface forming the large diameter hole 122).

On the other hand, the control hole 145 is opened in the axial direction Dx (the forward axial direction Dx1 in FIGS. 4A to 4C), and the output port 134 through the valve hole 121 (particularly the large diameter hole 122). Communicate on The large-diameter hole 122 connected to the hydraulic actuator A via the output port 134 is one of the contact hole 142 and the control hole 145 (FIG. 4A to FIG. 4C, the "control hole 145"). Through the spool hole 141). In addition, the small diameter hole part 123 communicates with the spool hole 141 through the other (the "contact hole 142" in FIGS. 4A-4C) among the contact hole 142 and the control hole 145. FIG. Therefore, the large diameter hole 122 and the small diameter hole 123 in the valve hole 121 communicate with each other through the spool hole 141, the contact hole 142, and the control hole 145. The pressure of the pressure oil in the diameter hole 122, the pressure of the pressure oil in the small diameter hole 123, and the pressure of the pressure oil in the valve hole 121 are equal to each other.

The movable part 25 (especially the push rod 30) of the drive part 16 presses the spool main body 112 in the forward axial direction Dx1, and according to the drive current applied by the valve controller 17, the spool main body 112 The pressing force on) is variable.

The pressing part 114 presses the spool main body 112 (large diameter spool part 147 in this embodiment) in reverse axial direction Dx2. The force applied to the spool body 112 from the pressing unit 114 varies depending on the position of the spool body 112 in the axial direction Dx, and as the spool body 112 is disposed on the forward axial direction Dx1 side, the pressing unit ( The force applied to the spool body 112 from 114 becomes large.

In the positive valve portion 15 having the above-described configuration, a hydraulic pressure area difference is provided between the both ends of the spool body 112, and the hydraulic force resulting from the hydraulic pressure area difference, the driving force of the driving unit 16, and the pressing part 114 are obtained. By balancing the pressing forces of), the pressurized oil of the desired pressure can be sent from the control hole 145 toward the hydraulic actuator A. FIG. That is, the surface area of the spool main body 112 which receives a force in the forward axial direction Dx1 from the pressure oil filled in the valve hole 121 and the spool hole 141 is the spool main body which receives a force in the reverse axial direction Dx2 from the said pressure oil. It is different from the surface area of (112). Specifically, the surface area of the spool main body 112 that receives the force in the reverse axial direction Dx2 from the pressure oil is larger than the surface area of the spool main body 112 that receives the force in the forward axial direction Dx1 from the pressure oil.

Therefore, the force F1 which the pressurized oil has on the forward axial direction Dx1 with respect to the spool main body 112 differs from the force F2 which the pressurized oil has on the reverse axial direction Dx2 with respect to the spool main body 112, and is shown to FIGS. 4A-4C. In the valve part 15, the relationship of "F1 <F2" is established. Therefore, the spool main body 112 receives the force in the reverse axial direction Dx2 from the pressure oil filled in the valve hole 121 and the spool hole 141. Specifically, the force F0 derived by "F0 = F2-F1" acts on the reverse axial direction Dx2 with respect to the spool main body 112 from pressure oil.

The spool body 112 also receives a force from the push rod 30 and the pressing portion 114 of the drive unit 16. The pressure of the hydraulic oil in the valve hole 121 and the spool hole 141 is represented by "Ph", and the spool main body receives a force in the forward axial direction Dx1 from the hydraulic oil in the valve hole 121 and the spool hole 141 ( The difference between the surface area S1 of 112 and the surface area S2 of the spool main body 112 which is forced from the pressure oil in the reverse axial direction Dx2 is represented by "Up (= S2-S1)", and the driving unit 16 is in the forward axial direction Dx1. When the force applied to the spool body 112 is represented by "Fd", and the force applied to the spool body 112 by the pressing unit 114 in the reverse axial direction Dx2 is represented by "Fsp", the following relational expression 1 This holds true.

Relation 1 Fd = Ph × Up + Fsp

In the actual valve part 15, said "Up" is basically set to a fixed value. In addition, said "Fsp" is the valve part 15 of this embodiment in which supply and discharge of the pressure oil to the spool hole 141 and the valve hole 121 are performed according to the position of the axial direction Dx of the spool main body 112. FIG. Takes a value within a range. Therefore, as apparent from the relational expression 1, with the increase in the force "Fd" applied to the spool body 112 from the drive unit 16, the pressure of the oil in the valve hole 121 and the spool hole 141 is increased. Pressure "Ph" also increases. Therefore, the valve controller 17 controls the drive current value applied to the drive unit 16, and adjusts the force Fd applied by the drive unit 16 to the spool main body 112, so that the pressure oil having the desired pressure can be obtained. From the control hole 145, it can send to the hydraulic actuator A via the large diameter hole part 122 and the output port 134. FIG.

Next, the behavior in the positive valve portion 15 described above will be described.

When no current is applied to the drive unit 16 or when a first drive current is applied to the drive unit 16, the spool body 112 is disposed at the first position shown in FIG. 4A. In this case, the spool hole 141 communicates with the outlet port 132 through the outlet hole 143, so that the pressure of the pressure oil in the spool hole 141 and the pressure oil in the valve hole 121 are lowered.

When a second current larger than the first drive current is applied to the drive unit 16, the spool main body 112 is pushed in the forward axial direction Dx1 by the push rod 30 of the drive unit 16 and shown in FIG. 4C. Disposed in the second position. In this case, the spool hole 141 communicates with the inlet port 131 through the inlet hole 144, so that the pressure oil from the hydraulic pressure source P is supplied to the spool hole 141, so that the spool hole 141 is in the spool hole 141. The pressure of the hydraulic oil and the hydraulic oil in the valve hole 121 is increased. Thus, in the valve part 15 of this embodiment, the spool main body 112 (refer FIG. 4A) arrange | positioned at a 1st position is reverse to the spool main body 112 (refer FIG. 4C) arrange | positioned at a 2nd position. It is located in the direction Dx2 side.

When a third current larger than the first drive current and smaller than the second current is applied to the drive unit 16, the spool body 112 is disposed at the third position (that is, the neutral position) shown in FIG. 4B. In this case, the outlet hole 143 does not communicate with the outlet port 132, and the inlet hole 144 does not communicate with the inlet port 131. Thereby, the spool hole 141 is cut off from both the inlet port 131 and the outlet port 132, and the pressure of the pressure oil in the spool hole 141 and the pressure oil in the valve hole 121 increase basically the fall degree. It stays without doing either.

Thus, in the positive valve part 15, when the drive current applied to the drive part 16 is small, and the thrust of the push rod 30 is zero (0) or weak, the valve hole 121 and the spool hole 141 are used. ), The amount of pressure oil discharged into the drainage portion T increases, and the pressure of the pressure oil in the valve hole 121 and the spool hole 141 decreases. On the other hand, when the driving current applied to the drive unit 16 is large and the thrust of the push rod 30 is strong, the amount of pressure oil supplied from the hydraulic source P into the valve hole 121 and the spool hole 141 is increased. The pressure of the hydraulic oil in the valve hole 121 and in the spool hole 141 increases. And when the drive current applied to the drive part 16 is in the intermediate range, and the spool main body 112 is arrange | positioned in the neutral position shown in FIG. 4B, the valve hole 121, the spool hole 141, and the hydraulic pressure source ( The flow path between P) and the drainage portion T is blocked, and the supply and discharge of the pressurized oil to the valve hole 121 and the spool hole 141 are stopped.

The positive type valve part 15 which exhibits the above-mentioned behavior sends the pressure oil of desired pressure from the control hole 145 according to the following mechanism.

That is, by the valve controller 17 (especially the drive current supply part 54), the drive current of a predetermined value is applied to the drive part 16 according to the desired pressure of hydraulic oil. As a result, the push rod 30 of the driving unit 16 moves the spool body 112 in the forward axial direction Dx1 and arranges it in the second position (see FIG. 4C), whereby the outlet hole 143 and the outlet port 132 are located. The inlet hole 144 communicates with the inlet port 131 while being blocked. Therefore, the hydraulic oil from the hydraulic pressure source P is supplied to the spool hole 141 and the valve hole 121, and the pressure oil in the spool hole 141 and the valve hole 121 raises a pressure.

And when the pressure of the hydraulic oil in the spool hole 141 and the valve hole 121 becomes larger than a desired pressure in the state in which the magnitude | size of the drive current applied to the drive part 16 is maintained, the spool main body 112 will return to the reverse axial direction Dx2. Is moved to a first position (see FIG. 4A). Thereby, between the inlet hole 144 and the inlet port 131 is interrupted, the outlet hole 143 communicates with the outlet port 132, and the oil pressure in the spool hole 141 and the valve hole 121 is Pressure drops.

Then, when the pressure of the hydraulic oil in the spool hole 141 and the valve hole 121 becomes smaller than the desired pressure in the state where the magnitude of the drive current applied to the drive unit 16 is maintained, the spool body 112 moves in the forward axial direction. It is moved to Dx1, and placed again in the second position (see FIG. 4C). As a result, the outlet hole 143 and the outlet port 132 are blocked, and the inlet hole 144 communicates with the inlet port 131, whereby the pressure of the hydraulic oil in the spool hole 141 rises again.

In this way, in the state where the drive current of a predetermined value is continuously applied to the drive unit 16 in accordance with the desired pressure of the hydraulic oil, the spool body 112 is positioned in the second position (see FIG. 4C) and the first position (FIG. 4A). By repeating the movement between the two sides, the supply and discharge of the pressurized oil to the spool hole 141 is repeatedly performed. As a result, the pressure of the pressure oil in the spool hole 141 and the valve hole 121 is maintained at the desired pressure, and the pressure oil of the desired pressure flows out of the control hole 145 and is supplied to the hydraulic actuator A. FIG.

[Negative Type Electronic Proportional Valve]

In the negative valve portion 15 described below, the same or similar configuration as that of the positive valve portion 15 (refer to FIGS. 4A to 4C) described above is given the same reference numeral, and the detailed description thereof is omitted. do.

5A to 5C are cross-sectional views showing the schematic configuration of the valve portion 15 of the negative type. FIG. 5A shows a non-excited state in which no drive current is applied to the drive unit 16, FIG. 5B shows a state in which the spool body 112 is disposed in a neutral position, and FIG. 5C shows the drive unit 16. The state in which the relatively large drive current is flowing is shown.

The small diameter hole part 123 of the valve hole 121 of this embodiment is provided adjacent to the large diameter hole part 122, and is arrange | positioned rather than the large diameter hole part 122 in the forward axial direction Dx1 side. Although not shown clearly in FIGS. 5A to 5C, each of the large diameter hole portion 122 and the small diameter hole portion 123 forms a closed space and is filled with the hydraulic oil supplied from the hydraulic pressure source P. FIG. . In addition, the small diameter hole 123 communicates with the hydraulic actuator A via the output port 134.

One end side of the spool main body 112 is disposed in the large diameter hole 122, and the other end side of the spool main body 112 is disposed in the small diameter hole 123. On one end side of the spool body 112 disposed in the large diameter hole portion 122, a large diameter spool portion 147 having an outer diameter corresponding to the diameter of the large diameter hole portion 122 is provided. On the other end side of the spool body 112 disposed in the small diameter hole 123, a small diameter spool portion 146 having an outer diameter corresponding to the diameter of the small diameter hole 123 is provided.

The control hole 145 is formed in one of the one end side and the other end side of the spool main body 112, and the contact hole 142 is formed in the other side. In addition, the outlet hole 143 and the inlet hole 144 are formed in the small diameter spool part 146 of the spool main body 112.

The contact hole 142 is opened to the large diameter hole part 122 and is not bound to the position of the axial direction Dx of the spool main body 112, The large diameter hole part 122 and the spool hole 141 communicate with each other. Let's do it. In addition, depending on the position of the spool body 112 in the axial direction Dx, the outlet hole 143 is an inner wall surface of the outlet port 132 or the valve body 111 (in particular, an inner wall surface forming the small diameter hole portion 123). The inlet hole 144 is opened toward the inner wall surface of the inlet port 131 or the valve body 111 (in particular, the inner wall surface forming the small diameter hole portion 123).

The control hole 145 is opened in the forward axial direction Dx1 and communicates with the output port 134 through the valve hole 121 (especially the small diameter hole part 123). Thus, the small diameter hole part 123 connected to the hydraulic actuator A via the output port 134 is one of the contact hole 142 and the control hole 145 (FIG. 5A to FIG. 5C, the "control hole". 145 '') to communicate with the spool hole 141. In addition, the large-diameter hole 122 communicates with the spool hole 141 via the other of the communication hole 142 and the control hole 145 ("contact hole 142" in FIGS. 5A to 5C). Therefore, the large diameter hole part 122 and the small diameter hole part 123 communicate with each other through the spool hole 141, the contact hole 142, and the control hole 145, and the pressure in the large diameter hole part 122 The oil pressure, the pressure of the pressure oil in the small diameter hole 123 and the pressure of the pressure oil in the spool hole 141 become equal to each other.

The movable part 25 (especially the push rod 30) of the drive part 16 presses the spool main body 112 in the forward axial direction Dx1, and the pressing force with respect to the spool main body 112 is variable according to a drive current. The pressing part 114 presses the spool main body 112 (small diameter spool part 146 in this embodiment) to the reverse axial direction Dx2.

Also in the negative valve portion 15 described above, a hydraulic pressure area difference is provided between the both ends of the spool body 112, and the hydraulic force, the driving force of the driving unit 16, and the pressing unit 114 due to the hydraulic pressure area difference are provided. By balancing the pressing forces with each other, the pressure oil of the desired pressure can be sent from the control hole 145 toward the hydraulic actuator A. FIG.

That is, the surface area of the spool main body 112 which receives a force in the forward axial direction Dx1 from the pressure oil filled in the valve hole 121 and the spool hole 141 is the spool main body which receives a force in the reverse axial direction Dx2 from the said pressure oil. It is different from the surface area of (112). Specifically, the surface area of the spool body 112 that is forced from the hydraulic oil in the forward axial direction Dx1 is larger than the surface area of the spool body 112 that is forced from the oil pressure in the reverse axial direction Dx2.

Therefore, the force F1 which the pressurized oil has on the forward axial direction Dx1 with respect to the spool main body 112 differs from the force F2 which the pressurized oil has on the reverse axial direction Dx2 with respect to the spool main body 112, and is shown to FIGS. 5A-5C. In the valve part 15, the relationship of "F1> F2" is established. Therefore, the spool main body 112 receives a force in the forward axial direction Dx1 from the pressure oil filled in the valve hole 121 and the spool hole 141. Specifically, the force F0 derived by "F0 = F1-F2" acts on the forward axial direction Dx1 with respect to the spool main body 112 from pressure oil.

The pressure of the hydraulic oil in the valve hole 121 and the spool hole 141 is represented by "Ph", and the spool main body receives a force in the forward axial direction Dx1 from the hydraulic oil in the valve hole 121 and the spool hole 141 ( The difference between the surface area S1 of 112 and the surface area S2 of the spool main body 112 that is forced in the reverse axial direction Dx2 from the pressure oil is represented by "Un (= S1-S2)", and the driving unit 16 shows the forward axial direction Dx1 The force applied to the spool body 112 is represented by "Fd", and the force applied to the spool body 112 by the pressing unit 114 in the reverse axial direction Dx2 is represented by "Fsp". Is established.

Relation 2 Fd = Fsp-Ph × Un

In the actual valve part 15, said "Un" is basically set to a fixed value. In addition, said "Fsp" is the valve part 15 of this embodiment in which supply and discharge of the pressure oil to the spool hole 141 and the valve hole 121 are performed according to the position of the axial direction Dx of the spool main body 112. FIG. Takes a value within a range. Therefore, as is apparent from the relational expression 2, with the increase in the force "Fd" applied to the spool main body 112 from the drive unit 16, the pressure of the hydraulic oil in the valve hole 121 and the spool hole 141 is increased. Pressure "Ph" is reduced. Therefore, by controlling the drive current value applied to the drive unit 16 by the valve controller 17, and adjusting the force Fd applied by the drive unit 16 to the spool body 112, the pressure oil having the desired pressure is adjusted. From the control hole 145, the small diameter hole 123 and the output port 134 can be fed to the hydraulic actuator A.

Next, the behavior in the above-mentioned negative valve part 15 is demonstrated.

When no current is applied to the drive unit 16 or when a first drive current is applied to the drive unit 16, the spool body 112 is disposed at the first position shown in FIG. 5A. In this case, the spool hole 141 communicates with the inlet port 131 through the inlet hole 144, and the pressure of the pressure oil in the spool hole 141 and the pressure oil in the valve hole 121 are increased.

In addition, when a second current larger than the first drive current is applied to the drive unit 16, the spool main body 112 is pushed in the forward axial direction Dx1 by the push rod 30 of the drive unit 16 and shown in FIG. 5C. Disposed in the second position. In this case, the spool hole 141 communicates with the outlet port 132 via the outlet hole 143, and the pressure of the pressure oil in the spool hole 141 and the pressure oil in the valve hole 121 are lowered. Moreover, in the valve part 15 of this embodiment, the spool main body 112 (refer FIG. 5A) arrange | positioned in a 1st position is reverse to the spool main body 112 (refer FIG. 5C) arrange | positioned in a 2nd position. It is located in the direction Dx2 side.

In addition, when a third current larger than the first drive current and smaller than the second current is applied to the drive unit 16, the spool body 112 is disposed at the third position shown in FIG. 5B. In this case, the outlet hole 143 does not communicate with the outlet port 132, and the inlet hole 144 does not communicate with the inlet port 131, but the pressure oil in the spool hole 141 and the pressure in the valve hole 121. Oil pressure is basically maintained without deterioration or increase.

Thus, in the negative type valve part 15, when the drive current applied to the drive part 16 is small and the thrust of the push rod 30 is zero (0) or weak, the valve hole 121 from the hydraulic source P is carried out. The amount of pressure oil supplied in the inner and spool holes 141 increases, and the pressure of the pressure oil in the valve holes 121 and in the spool holes 141 increases. On the other hand, when the drive current applied to the drive unit 16 is large and the thrust of the push rod 30 is strong, the amount of pressure oil discharged in the valve hole 121 and the spool hole 141 to the drainage part T is increased. The pressure of the hydraulic oil in the valve hole 121 and in the spool hole 141 decreases. And when the drive current applied to the drive part 16 is in the intermediate range, and the spool main body 112 is arrange | positioned in the neutral position shown in FIG. 5B, the valve hole 121, the spool hole 141, and the hydraulic pressure source ( The flow path between P) and the drainage portion T is blocked. As a result, the supply and discharge of the pressurized oil in the valve hole 121 and in the spool hole 141 are stopped, and the pressure of the pressurized oil in the valve hole 121 and the spool hole 141 is maintained.

As for the valve part 15 of the negative type which shows the above-mentioned behavior, the hydraulic oil of desired pressure is sent out from the control hole 145 according to the following mechanism.

That is, in the state in which the valve hole 121 and the spool hole 141 are filled with pressure oil, the drive current of a predetermined value is applied to the drive part 16 according to the desired pressure of pressure oil. Thereby, the push rod 30 of the drive part 16 moves the spool main body 112 to the forward axial direction Dx1, and arrange | positions it in a 2nd position (refer FIG. 5C), and the inlet hole 144 and the inlet port 131 are located. While being blocked, the outlet hole 143 communicates with the outlet port 132. As a result, the pressure of the oil pressure in the spool hole 141 and the valve hole 121 decreases.

Then, when the pressure of the hydraulic oil in the spool hole 141 and the valve hole 121 becomes smaller than the desired pressure in the state where the magnitude of the drive current applied to the drive unit 16 is maintained, the spool body 112 moves in the reverse axial direction. Move to Dx2 and place it in the first position (see FIG. 5A). Thereby, between the outlet hole 143 and the outlet port 132 is interrupted | blocked, the inlet hole 144 communicates with the inlet port 131, and the oil pressure from the hydraulic pressure source P spool hole 141 and It is supplied to the valve hole 121, and the pressure oil in the spool hole 141 and the valve hole 121 raises a pressure.

Then, when the pressure of the hydraulic oil in the spool hole 141 and the valve hole 121 becomes larger than the desired pressure in the state where the magnitude of the drive current applied to the drive unit 16 is maintained, the spool main body 112 has the forward axial direction Dx1. And the outlet hole 143 communicates with the outlet port 132 while the inlet hole 144 is blocked between the inlet port 131. As a result, the pressure of the hydraulic oil in the spool hole 141 and the valve hole 121 is lowered again.

In this way, in a state in which a driving current of a predetermined value is continuously applied to the driving unit 16 in accordance with the desired pressure of the hydraulic oil, the spool body 112 is positioned in the second position (see FIG. 5C) and the first position (FIG. 5A). By repeating the movement between the two ends, the supply and discharge of the pressurized oil to the spool hole 141 is repeatedly performed. As a result, the pressure of the pressure oil in the spool hole 141 and the valve hole 121 is maintained at the desired pressure, and the pressure oil of the desired pressure flows out of the control hole 145 and is supplied to the hydraulic actuator A. FIG.

[Application Example]

The valve structure 10 mentioned above can be mounted in various machines, and it can mount suitably especially with respect to construction machines, such as a hydraulic excavator.

FIG. 6: is an external view which shows the outline of the typical structural example of the hydraulic excavator 210. As shown in FIG. The hydraulic excavator 210 generally includes a lower frame 244 including a crawler, an upper frame 245 provided to be pivotable with respect to the lower frame 244, and a boom installed on the upper frame 245. 247, an arm 248 provided on the boom 247, and a bucket 249 provided on the arm 248. The hydraulic cylinders 267, 268, and 269 as the actuators are hydraulic cylinders for booms, arms, and buckets, and drive the booms 247, the arms 248, and the buckets 249, respectively. The rotational drive force from the turning motor 246 is transmitted to the upper frame 245 so that the upper frame 245 is turned by the turning motor 246. In addition, the rotational driving force from the traveling motor 251 is transmitted to the crawler of the lower frame 244 so that the crawler is driven by the traveling motor 251 to drive the hydraulic excavator 210.

In this hydraulic excavator 210, each of the hydraulic cylinders 267, 268, 269, the turning motor 246, and the traveling motor 251 corresponds to the hydraulic actuator A shown to FIG. 4A-5C. Therefore, the some valve structure 10 corresponding to each of the hydraulic cylinders 267, 268, 269, the turning motor 246, and the traveling motor 251 can be provided in the appropriate place among the flow paths. In this case, the hydraulic oil of desired pressure can be supplied to each of the hydraulic cylinders 267, 268, and 269, the turning motor 246, and the traveling motor 251.

Next, the typical example of the control structure using the valve structure 10 mentioned above is demonstrated. As described above, the valve structure 10 including the drive unit 16 and the valve controller 17 can be applied in various forms.

For example, as shown in FIG. 7, the plurality of valve controllers 17 may be connected to the integrated controller 18, and these valve controllers 17 may be integratedly controlled by the integrated controller 18. In this case, since each valve controller 17 is provided with the drive current supply part 54, the integrated controller 18 may not be provided with the drive current supply part 54. FIG. Therefore, even when the new valve structure 10 (valve controller 17) is connected to the existing integrated controller 18, it is necessary to increase the drive current supply unit 54 with respect to the existing integrated controller 18. none. Therefore, it is possible to introduce the valve structure 10 mentioned above with respect to an existing machine newly, simply and at low cost.

As shown in FIG. 8, the plurality of valve controllers 17 may be connected to each other via the wiring N. As shown in FIG. In this case, even if the integrated controller 18 is not provided, it is possible to transmit and receive information between the valve controllers 17 through the wiring N, and based on such information, each valve controller 17 is provided with a corresponding drive unit ( 16) can be controlled. Therefore, the valve structure 10 mentioned above can be newly introduced in the simple and low cost also about the machine in which the integrated controller 18 (refer FIG. 7) is not provided. 8, even when the plurality of valve controllers 17 are connected to each other, the integrated controller 18 as shown in FIG. 7 may be provided.

[Modification]

For example, as shown in FIG. 9, the valve controller 17 may be provided in the position shifted from the reference axis Ax and the drive part 16 (especially the movable part 25) with respect to the radial direction Dr. FIG. Also in this case, the movable part 25 of the drive part 16 moves on the reference axis Ax according to the drive current, and the valve controller 17 is supported by the drive part 16. That is, in the valve structure 10 shown in FIG. 9, the valve controller 17 is supported by the drive part 16 via the valve housing 20, and the drive part 16 and the valve controller 17 are physically integrated. It consists of. Thereby, enlargement of the valve structure 10 regarding the axial direction Dx can be prevented.

In addition, although the valve part 15 comprised by the electromagnetic proportional valve for supplying the hydraulic oil of desired pressure to the hydraulic actuator A is shown by FIGS. 4A-5C, the valve part 15 is comprised by the valve which has another function. You may be. For example, the valve part 15 may be comprised by the direction change valve which can switch the flow direction of the hydraulic oil in a flow path according to the drive current supplied to the drive part 16. FIG. For example, by controlling the protrusion amount of the push rod 30 (moving part 25) in accordance with the drive current, the spool type direction switching valve which can change the flow direction of the pressure oil by adjusting the position of the spool body, The valve part 15 may be comprised. In addition, since the typical structure of such a directional valve is known, illustration is abbreviate | omitted.

This invention is not limited to embodiment mentioned above and a modification. For example, various deformation | transformation may be added to each element of embodiment mentioned above and a modification, and embodiment and a modification may be combined partially. Moreover, the effect exhibited by this invention is not limited to the above-mentioned effect, either, The effect peculiar to a specific structure is exhibited.

10: valve structure
15: valve part
16: drive section
17: valve controller
18: integrated controller
20: valve housing
21: Donation
25: movable part
26: drive housing
27: electromagnet
28: plunger
29: spring
30: push rod
31: Plunger Stopper
32: spring stopper
33: end position stopper
51: processing unit
52: memory
53: input unit
54: drive current supply
55: output unit
56: information output unit
57: abnormal output unit
71: power
72: other controller
73: sensor
74: display device
75: alarm device
A: hydraulic actuator
Ax: reference axis
Dr: radial direction
Dx: axial direction
Dx1: Net axis direction
Dx2: reverse axis direction
N: wiring
P: hydraulic source
Ss: Enclosed Space
T: drainage

Claims (10)

With valve section,
A driving unit for driving the valve unit according to a driving current;
And a valve controller which is supported by the drive unit and controls the drive current supplied to the drive unit. The method of claim 1,
The driving unit includes a movable unit moving on a reference axis in accordance with the driving current,
The valve controller is provided at a position shifted from the drive section with respect to a direction parallel to the reference axis. The method of claim 1,
The driving unit includes a movable unit moving on a reference axis in accordance with the driving current,
The valve controller is provided at a position shifted from the drive section with respect to a radial direction perpendicular to the reference axis. The method of claim 1,
The valve controller is disposed in a sealed space. The method of claim 1,
The said drive part is a valve structure including the electromagnet through which the said drive current flows, and the plunger which moves according to the magnetic force caused by the said electromagnet. The method of claim 1,
And the valve portion includes a spool driven by the drive portion. The method of claim 1,
The valve controller is configured to supply the drive current to the drive unit in accordance with a drive signal input from another controller. The method of claim 1,
The valve controller supplies the drive current to the drive unit in accordance with a detection signal input from a sensor. The method of claim 1,
The valve controller is housed in the valve housing within a range of a width in the radial direction of the valve housing accommodating the drive portion. The construction machine provided with the valve structure in any one of Claims 1-9.

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