JP2021025616A - Valve structure and operation machine - Google Patents

Abstract

To provide a valve structure and an operating machine capable of suppressing operation failure of a valve body.SOLUTION: A valve structure comprises: a body having a working fluid flow path through which working fluid can pass; a valve body 21 that opens and closes the working fluid flow path; and a permanent magnet 40 that holds the valve body in at least one of a valve-opened state of opening the working fluid flow path and a valve-closed state of closing the working fluid flow path. For example, the permanent magnet 40 holds the valve body in a state of being in contact with the permanent magnet 40 in at least one of the valve-open state and the valve-closed state. Further, for example, the valve structure further comprises a cushioning member that absorbs an impact generated when the valve body comes into contact with the permanent magnet 40.SELECTED DRAWING: Figure 2

Description

The present disclosure relates to valve structures and actuators.

As a conventional valve structure, for example, it is incorporated in a hydraulically operated machine. The hydraulically operated machine has a piston, a cylinder, a crankshaft, and a solenoid valve. In a hydraulically operated machine, pumping and motoring operations are performed by valve opening and closing operations of a valve, and the fluid energy of the working fluid and the rotational energy of the rotating shaft are configured to be mutually convertible. In a hydraulically operated machine, the valve opening operation or valve closing operation is an important operation that affects energy conversion efficiency and operation reliability.

For example, when the coil is energized, the electromagnetic force exceeds the urging force of the spring, and the valve body shifts to the closed state. Further, when the energization of the coil is stopped, the valve body returns to the valve open state by the urging force of the spring. When the coil is not energized, the valve body is held in the open state by the urging force of the spring.

Further, for example, when the coil is energized, the electromagnetic force exceeds the urging force of the spring, and the valve body shifts to the valve open state. Further, when the energization of the coil is stopped, the valve body returns to the closed state by the urging force of the spring. When the coil is not energized, the valve body is held in a closed state by a spring (for example, Patent Document 1).

JP-A-2017-8975

By the way, in a valve in which the valve body is held in the valve open state by a spring, a valve opening failure, for example, a bouncing motion may occur due to the force received by the valve body from the working fluid, so that the operation is not always stable. It cannot be said that the sex is high. In addition, an unintended valve closing operation may occur when the coil is not energized. This causes problems such as destabilization of pumping and motoring operations and a decrease in energy conversion efficiency.

Further, in a valve in which the valve body is held in the closed state by pulling, the valve body is maintained in the closed state by the force received from the spring and the pressure received from the working fluid, but the conditions of the working fluid, for example, Depending on the flow velocity and pressure of the working fluid, there is a problem that the valve is not closed properly, for example, the valve body may bounce.

An object of the present disclosure is to provide a valve structure and an operating machine capable of suppressing malfunction of a valve body.

In order to achieve the above object, the valve structure in the present disclosure is
A main body having a working fluid flow path through which the working fluid can pass,
A valve body that opens and closes the working fluid flow path,
A permanent magnet that holds the valve body in at least one of a valve open state for opening the working fluid flow path and a valve closed state for closing the working fluid flow path.
To be equipped.

The operating machine in the present disclosure is
It has the above valve structure.

According to the valve structure of the present disclosure, it is possible to suppress malfunction of the valve body.

FIG. 1 is a schematic view showing a hydraulic pump motor incorporating a valve structure according to the present embodiment. FIG. 2 is a schematic cross-sectional view showing the configuration of the valve structure. FIG. 3 is a schematic cross-sectional view showing the configuration of the valve structure. FIG. 4 is a schematic cross-sectional view showing the configuration of the valve structure according to the modified example. FIG. 5 is a schematic cross-sectional view showing the configuration of the valve structure according to the modified example.

Hereinafter, embodiments of the present disclosure will be described with reference to the drawings. It should be noted that this is an example of the embodiment described below, and the present disclosure is not limited to this embodiment.

The hydraulic pump motor 2 incorporating the valve structure 1 according to the present embodiment will be described with reference to FIG. In the following description, a hydraulic pump motor will be described as an example of the operating machine, but the operating machine is not limited to the hydraulic pump motor.

In FIG. 1, one cylinder 3 in the hydraulic pump motor 2 is drawn. The cylinder 3 is connected to the oil passage 4 via the valve 20A and is connected to the oil passage 5 via the valve 20B. Both the valves 20A and 20B are check valves.

The cylinder 3 is provided with a piston 6, and the lower end of the piston 6 is in contact with the cam portion 8a of the crankshaft 8. The reciprocating motion of the piston 6 is converted into the rotational motion of the crankshaft 8. The volume of the cylinder 3 changes periodically due to the reciprocating motion of the piston 6.

FIG. 1 is a diagram showing an example of the valve structure 1. As shown in FIG. 1, the valve structure 1 is provided between the cylinder 3 of the hydraulic pump motor 2 and the oil passages 4 and 5. The valve structure 1 includes valves 20A and 20B.

The valve 20A has a valve seat 18 and a valve body 21. The spring (not shown) urges the valve body 21 in a direction (valve opening direction) away from the valve seat 18, for example. In this embodiment, the valve 20A is a poppet valve.

The valve 20B has a valve seat 18 and a valve body 21. The spring (not shown) urges the valve body 21 in a direction (valve closing direction) for seating the valve body 21, for example. In this embodiment, the valve 20B is a poppet valve.

The hydraulic pump motor 2 has a function as a pump that sucks the hydraulic fluid (hydraulic oil) from the oil passage 4 into the cylinder 3 by the rotational movement of the crankshaft 8 and discharges it to the oil passage 5, and the hydraulic pump motor 2 is a cylinder from the oil passage 5. It has a function as a motor that is introduced into 3 to rotate the crankshaft 8 and draws the working fluid used for the rotation of the crankshaft 8 from the cylinder 3 to the oil passage 4.

Next, the valve structure 1 including the valve 20A will be described with reference to FIGS. 2 and 3. FIG. 2 is a schematic cross-sectional view showing the configuration of the valve structure 1. In FIG. 2, a central axis CL extending in the vertical direction is drawn. In the following description, the direction along the central axis CL is referred to as the "axial direction" or the X direction, and for convenience, the upward direction in FIG. 2 is referred to as the upper side, the axial upper side or the "+ X direction", and the lower direction in FIG. 2 is referred to as the "+ X direction". , Lower side, axial lower side or "-X direction". Further, the direction orthogonal to the central axis CL is referred to as the "diameter direction" or the Y direction, the direction away from the central axis CL is referred to as the radial outside or the "+ Y direction", and the direction close to the central axis CL is the diameter. It is called the inside of the direction or the "-Y direction". Further, in FIG. 2, some configurations unrelated to the description are omitted.

The valve structure 1 has a body 10, a valve 20A, and a permanent magnet 40.

(Body 10)
The body 10 is made of a magnetic material such as iron. The body 10 has a substantially cylindrical shape, and the body 10 is provided with a hole 10a extending along the central axis CL. In other words, the body 10 has a cylindrical portion 10b having a hole 10a as a hollow portion, a disk portion 10c arranged on the axially upper side (+ X direction) of the cylindrical portion 10b, and an axially lower side of the cylindrical portion 10b ( It has a bottomed cylindrical shape with a disk portion 10d arranged in the −X direction).

The hole 10a is divided into a first space 11, a second space 12, a third space 13, and a fourth space 14. The first space 11 is defined by an upper surface 11a of the disk portion 10d and an end surface 11b on the lower side (-X direction) of the cylindrical portion 10b in the axial direction. The first space 11 is connected to the working chamber of the cylinder 3.

The second space 12 is located above the end surface 11b and is defined by an annular surface 12a facing downward and an inner peripheral surface 12b connecting the end surface 11b and the surface 12a.

The third space 13 is located above the surface 12a and is defined by an annular surface 13a facing downward and an inner peripheral surface 13b connecting the surface 12a and the surface 13a.

The fourth space 14 is defined by an inner peripheral surface 14a that connects the surface 13a and the upper surface 11c of the disk portion 10c.

The diameter of the inner peripheral surface 12b is larger than the diameter of the inner peripheral surface 13b and the diameter of the inner peripheral surface 14a. The diameter of the inner peripheral surface 13b is larger than the diameter of the inner peripheral surface 14a.

A flow path 10f is provided in the cylindrical portion 10b. The flow path 10f extends in the radial direction. The radial outer (+ Y direction) end of the flow path 10f is connected to the oil passage 4. At the end of the flow path 10f in the radial direction (-Y direction), the flow path 10f changes the extending direction to the axial direction (X direction) and extends downward in the axial direction (-X direction). ing. The lower end (−X direction) of the flow path 10f in the axial direction is open to the end surface 11b. The end face 11b functions as a valve seat 18 on which the valve body 21 is seated.

A fifth space 15 is formed on the outer side (+ Y direction) of the third space 13 in the radial direction. A coil 30 is arranged in the fifth space 15. The coil 30 has a winding wound around the outer circumference of an annular bobbin made of a non-magnetic material.

(Valve 20A)
The valve 20A is a low-pressure valve that opens and closes a working fluid flow path 10 g (flow path 10f, first space 11) that communicates the oil passage 4 (see FIG. 1) and the working chamber of the cylinder 3 (see FIG. 1). is there.

The valve 20A includes a valve body 21, a valve seat 18 (end surface 11b), and a spring 25 that urges the valve body 21 in the valve opening direction.

The valve body 21 is made of a magnetic material such as iron. The valve body 21 may be made of a non-magnetic material. The valve body 21 has a substantially annular shape, and has an annular portion 22 and a shaft-shaped portion 23. The valve body 21 is movable in the axial direction (X direction).

The upper surface 22a of the annular portion 22 is in contact with the axially lower end of the spring 25. The axially upper end of the spring 25 shown in FIG. 2 is in contact with the annular surface 12a.

The spring 25 is a compression coil spring that fits outside the shaft-shaped portion 23. The inner diameter of the spring 25 is smaller than the inner diameter of the inner peripheral surface 12b and larger than the diameter of the shaft-shaped portion 23. The spring 25 is arranged in a compressed state between the surfaces 12a and 22a. As a result, the spring 25 urges the valve body 21 in the −X direction. In the following description, the -X direction is referred to as the valve opening direction. The + X direction is called the valve closing direction.

The shaft-shaped portion 23 has a shaft portion 23a and a shaft portion 23b. The shaft portion 23a extends from the central portion of the surface 22a to the upper side in the axial direction (+ X direction). The diameter of the shaft portion 23a is smaller than the inner diameter of the third space 13 and larger than the inner diameter of the fourth space 14.

The shaft portion 23b extends further upward in the axial direction (+ X direction) from the shaft portion 23a. The shaft portion 23b penetrates the fourth space 14.

When the coil 30 is not energized, the valve body 21 moves downward in the axial direction (−X direction) due to the urging force of the spring 25. The valve body 21 is held in a valve-opened state in which the working fluid flow path 10 g is opened by the urging force of the spring 25.

By the way, when the valve body 21 is held in the valve open state by the urging force of the spring 25, a bouncing motion occurs due to the force received by the valve body 21 from the working fluid, and it cannot be said that the stability is necessarily high. An unintended valve closing operation may occur when the coil is not energized. This causes problems such as destabilization of pumping and motoring operations and a decrease in energy conversion efficiency.

For example, it is conceivable to increase the urging force of the spring 25 so that the bouncing motion does not occur, but as the size of the spring 25 increases, the size of the entire device also increases. Further, when the valve is closed, it is necessary to move the valve body 21 by a large electromagnetic force against the urging force of the spring 25, so that the power consumption increases. In addition, it becomes difficult to operate the valve body 21 at high speed, which causes a problem that the responsiveness is lowered.

(Permanent magnet 40)
Therefore, in the present embodiment, the valve body 21 is held in the valve open state by the attractive force of the permanent magnet 40. The permanent magnet 40 is arranged between the annular portion 22 of the valve body 21 and the disc portion 10d. The permanent magnets 40 are arranged on the upper surface 11a of the disk portion 10d so as to face the lower surface 22b of the annular portion 22 and at predetermined intervals along the circumferential direction of the annular portion 22. ing.

When the coil 30 is not energized, the valve body 21 moves downward in the axial direction (−X direction) due to the urging force F1 of the spring 25. Then, as shown in FIG. 2, the valve body 21 is permanently in a state where the lower surface 22b of the valve body 21 is in contact with the permanent magnet 40, that is, in a valve open state in which the working fluid flow path 10 g is opened. It is held by the attractive force F2 of the magnet 40. The attractive force F2 of the permanent magnet 40 is set to, for example, the minimum necessary size for suppressing the bouncing motion. The attractive force F2 of the permanent magnet 40 can be obtained by experiments or simulations.

When the coil 30 is energized, the electromagnetic force F3 exceeds the urging force F1 of the spring 25 and the attractive force F2 of the permanent magnet 40 (F3> F1 + F2), and the valve body 21 moves upward in the axial direction (+ X direction). To do. Then, the valve body 21 is held by the electromagnetic force F3 in a state in which the annular portion 22 is seated on the valve seat 18, that is, in a valve closed state in which the working fluid flow path 10 g is closed, as shown in FIG. To.

According to the valve structure 1 according to the above embodiment, the body 10 having the working fluid flow path 10g through which the hydraulic oil can pass, the valve body 21 for opening and closing the working fluid flow path 10g, and the working fluid flow path 10g are opened. A permanent magnet 40 that holds the valve body 21 in the valve open state is provided.

As a result, when the valve 21 is held in the closed state by the attractive force F2 of the permanent magnet 40, the bouncing operation of the valve body 21 is suppressed even when the valve body 21 receives a force from the working fluid. It becomes possible. Further, since the valve body 21 can be held in the valve open state without increasing the urging force of the spring 25, it is possible to prevent the entire device from becoming large. Further, since it is not necessary to move the valve body 21 by a large electromagnetic force against the urging force of the spring 25, an increase in power consumption can be suppressed. Further, since it is not difficult to operate the valve body 21 at high speed, it is possible to prevent the responsiveness from being lowered.

<Modification example>
Next, a modified example of the present embodiment will be described. In the description of the modified example, a configuration different from the above-described embodiment will be mainly described, and the same configuration will be designated by the same reference numerals and the description thereof will be omitted.

In the above embodiment, the permanent magnet 40 holds the valve body 21 in the valve open state. On the other hand, in the modified example, the permanent magnet 40 holds the valve body 21 in the closed state.

In the modified example, the valve structure 1 including the valve 20B will be described with reference to FIGS. 4 and 5. In the description of the modified example, the central axis CL, the axial direction (X direction), the radial direction (Y direction), and the like are used as in the above embodiment.

The valve structure 1 has a body 100, a valve 20B, and a permanent magnet 40.

(Body 100)
The body 100 has a bottomed cylindrical shape including a cylindrical portion 110b having a hole 110a as a hollow portion and a disk portion 110c arranged on the axially upper side (+ X direction) of the cylindrical portion 110b.

The hole 110a is divided into a first space 111, a second space 112, a third space 113, and a fourth space 114. The first space 111 is defined by a lower surface 111a of the disk portion 110c and an end surface 111b on the upper side (+ X direction) of the cylindrical portion 110b in the axial direction. The first space 111 is connected to the oil passage 5.

The second space 112 is located below the end surface 111b and is defined by an annular surface 112a facing downward and an inner peripheral surface 112b connecting the end surface 111b and the surface 112a.

The third space 113 is located below the surface 112a and is defined by an annular surface 113a facing downward and an inner peripheral surface 113b connecting the surface 112a and the surface 113a.

The fourth space 114 is defined by an inner peripheral surface 114a that connects the surface 113a and the lower surface 111c of the cylindrical portion 110b.

The diameter of the inner peripheral surface 112b is smaller than the diameter of the inner peripheral surface 113b and the diameter of the inner peripheral surface 114a. The diameter of the inner peripheral surface 113b is smaller than the diameter of the inner peripheral surface 114a.

The lower end (−X direction) of the flow path 110f extending in the cylindrical portion 110b along the axial direction (X direction) is connected to the working chamber of the cylinder 3. The upper end (+ X direction) of the flow path 110f in the axial direction is open to the end surface 111b. The end face 111b functions as a valve seat 18 on which the valve body 21 is seated.

A fifth space 115 is formed on the outer side (+ Y direction) of the third space 113 in the radial direction. A coil 30 is arranged in the fifth space 115. The coil 30 has a winding wound around the outer circumference of an annular bobbin made of a non-magnetic material.

(Valve 20B)
The valve 20B is a high-pressure valve that opens and closes a working fluid flow path 110g (flow path 110f, first space 111) that communicates the oil passage 5 and the working chamber of the cylinder 3.

The valve 20B includes a valve body 21, a valve seat 18 (end surface 111b), and a spring 25 that urges the valve body 21 in the valve closing direction.

The valve body 21 has a substantially annular shape, and has an annular portion 22 and a shaft-shaped portion 23. The valve body 21 is movable in the axial direction (X direction).

The upper surface 22a of the annular portion 22 is in contact with the axially lower end of the spring 25. The axially upper end of the spring 25 shown in FIG. 4 is in contact with the lower surface 111a of the disc portion 110c.

The spring 25 is arranged in a compressed state between the surface 22a and the surface 111a. As a result, the spring 25 urges the valve body 21 in the −X direction. In the following description, the -X direction is referred to as the valve closing direction. The + X direction is called the valve opening direction.

The axial portion 23 extends from the central portion of the lower surface 22b of the annular portion 22 to the lower side in the axial direction (−X direction). The diameter of the shaft-shaped portion 23 is smaller than the inner diameter of the inner peripheral surface 112b. The shaft-shaped portion 23 penetrates the second space 112.

When the coil 30 is not energized, the valve body 21 moves downward in the axial direction (−X direction) due to the urging force of the spring 25. The valve body 21 is held in a valve closed state in which the working fluid flow path 110 g is closed by the urging force of the spring 25.

By the way, when the valve body 21 is held in the closed state by the urging force of the spring 25, the pressure received by the valve body 21 from the working fluid causes a bouncing motion, and it cannot be said that the stability is necessarily high. There's a problem. For example, when the urging force of the spring 25 is increased so as not to cause a bouncing motion, the size of the device is increased, the power consumption is increased, and the responsiveness is increased, as in the above embodiment. Problems such as deterioration occur.

Therefore, in the modified example, the valve body 21 is held in the closed state by the attractive force of the permanent magnet 40. The permanent magnet 40 is arranged on the lower side (−X direction) in the axial direction from the annular portion 22 of the valve body 21. The permanent magnets 40 are arranged on the end faces 111b so as to face the lower surface 22b of the ring portion 22 and at predetermined intervals along the circumferential direction of the ring portion 22. The upper surface 40a and the end surface 111b of the permanent magnet 40 are located on the same plane.

When the coil 30 is not energized, the valve body 21 moves downward in the axial direction (−X direction) due to the urging force F1 of the spring 25. Then, as shown in FIG. 5, the valve body 21 is in a state where the lower surface 22b of the valve body 21 is in contact with the upper surface 40a of the permanent magnet 40 (a state of being seated on the valve seat 18), that is, The valve closed state in which the working fluid flow path 110 g is closed is held by the attractive force F2 of the permanent magnet 40.

When the coil 30 is energized, the electromagnetic force F3 exceeds the urging force F1 of the spring 25 and the attractive force F2 of the permanent magnet 40 (F3> F1 + F2), and the valve body 21 moves upward in the axial direction (+ X direction). To do. Then, as shown in FIG. 4, the valve body 21 is held in a state in which the annular portion 22 is separated from the valve seat 18, that is, in a valve-opened state in which the working fluid flow path 110 g is opened.

According to the valve structure 1 according to the modified example, the body 100 having the working fluid flow path 110g through which the hydraulic oil can pass, the valve body 21 for opening and closing the working fluid flow path 110g, and the working fluid flow path 110g are closed. It includes a permanent magnet 40 that holds the valve body 21 in a closed state.

As a result, when the valve body 21 is held in the valve closed state by the attractive force F2 of the permanent magnet 40, the bouncing operation of the valve body 21 is suppressed even when the valve body 21 receives pressure from the working fluid. It becomes possible to do. Further, since the valve body 21 can be held in the closed state without increasing the urging force of the spring 25, it is possible to prevent the entire device from becoming large. Further, since it is not necessary to move the valve body 21 by a large electromagnetic force against the urging force of the spring 25, an increase in power consumption can be suppressed. Further, since it is not difficult to operate the valve body 21 at high speed, it is possible to prevent the responsiveness from being lowered.

In addition, all of the above embodiments are merely examples of embodiment of the present disclosure, and the technical scope of the present disclosure should not be construed in a limited manner by these. That is, the present disclosure can be implemented in various forms without departing from its gist or its main features.

In the above embodiment, the permanent magnet 40 holds the valve body 21 in the valve open state. Further, in the modified example, the permanent magnet 40 holds the valve body 21 in the valve closed state. However, this disclosure is not limited to this. In order to suppress the bouncing operation of the valve body 21, the permanent magnet 40 may hold the valve body 21 in at least one of the valve open state and the valve closed state. For example, the valve body 21 may be held in both the valve open state and the valve closed state.

Further, in the present disclosure, a cushioning member for absorbing the impact generated when the valve body 21 comes into contact with the permanent magnet 40 when the valve 20A is opened or the valve 20B is closed is provided. May be good. As a result, the impact force that the valve body 21 and the permanent magnet 40 receive from each other can be reduced, so that the durability of the valve body 21 and the permanent magnet 40 can be improved.

The present disclosure is suitably used for an operating machine having a valve structure that is required to suppress malfunction of the valve body.

1 Valve structure 2 Hydraulic pump motor 3 Cylinder 4 Oil passage 5 Oil passage 6 Piston 8 Crank shaft 10,100 Body 10a, 110a Hole 10b, 110b Cylindrical part 10c, 110c Disc part 10d Disc part 10f, 110f Flow path 10g, 110g working fluid flow path 11,111 1st space 11a, 111a surface 11b, 111b End surface 11c, 111c surface 12,112 2nd space 12a, 112a surface 12b, 112b Inner peripheral surface 13,113 3rd space 13a, 113a surface 13b , 113b Inner peripheral surface 14,114 4th space 14a, 114a Inner peripheral surface 15,115 5th space 18 Valve seat 20A, 20B Valve 21 Valve body 22 Ring part 22a, 22b surface 23 Axial part 25 Spring 30 Coil 40 Permanent magnet 40a surface

Claims (5)

A main body having a working fluid flow path through which the working fluid can pass,
A valve body that opens and closes the working fluid flow path,
A permanent magnet that holds the valve body in at least one of a valve open state for opening the working fluid flow path and a valve closed state for closing the working fluid flow path.
A valve structure. The permanent magnet holds the valve body in contact with the permanent magnet in at least one of the valve open state and the valve closed state.
The valve structure according to claim 1. A cushioning member for absorbing an impact generated when the valve body abuts on the permanent magnet is further provided.
The valve structure according to claim 2. An urging member that urges the valve body in either the valve closing direction in which the valve body closes the working fluid flow path or the valve opening direction in which the valve body opens the working fluid flow path. With more
The valve body is configured to move in a direction opposite to the one direction by an electromagnetic force.
The valve structure according to any one of claims 1 to 3. An operating machine comprising the valve structure according to any one of claims 1 to 4.

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