CN107448429B - Flow rate adjustment valve and valve structure - Google Patents
Flow rate adjustment valve and valve structure Download PDFInfo
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- CN107448429B CN107448429B CN201710368381.2A CN201710368381A CN107448429B CN 107448429 B CN107448429 B CN 107448429B CN 201710368381 A CN201710368381 A CN 201710368381A CN 107448429 B CN107448429 B CN 107448429B
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- hydraulic oil
- flow path
- pressure
- valve
- connection
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/029—Counterbalance valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/023—Excess flow valves, e.g. for locking cylinders in case of hose burst
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2221—Control of flow rate; Load sensing arrangements
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
- E02F9/2267—Valves or distributors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/01—Locking-valves or other detent i.e. load-holding devices
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/027—Check valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/405—Flow control characterised by the type of flow control means or valve
- F15B2211/40507—Flow control characterised by the type of flow control means or valve with constant throttles or orifices
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/42—Flow control characterised by the type of actuation
- F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Safety Valves (AREA)
- Fluid-Pressure Circuits (AREA)
- Check Valves (AREA)
Abstract
The invention provides a flow rate adjustment valve and a valve structure. The flow rate adjustment valve is an integrally configured flow rate adjustment valve that can appropriately function as both a flow rate control valve and a load holding check valve. The flow rate adjustment valve is provided with: a movable valve body, the arrangement position of which is changed according to the pressure of the working oil in the 1 st connection flow path and the 2 nd connection flow path; a 1 st cylindrical portion that changes an opening area of a 2 nd opening portion through which the working oil can pass, according to an arrangement position of the movable valve body; and a movable seal portion that varies an arrangement position according to a pressure of the hydraulic oil in the 1 st and 2 nd connection passages, and blocks a guide passage formed in the movable valve main body according to the arrangement position. When the pressure of the hydraulic oil in the 1 st connecting flow path is higher than the pressure of the hydraulic oil in the 2 nd connecting flow path and the difference between the pressure of the hydraulic oil in the 1 st connecting flow path and the pressure of the hydraulic oil in the 2 nd connecting flow path is equal to or greater than the 1 st pressure difference, the opening area of the 2 nd opening of the 1 st cylindrical portion is reduced.
Description
Technical Field
The present invention relates to a flow rate adjustment valve and a valve structure provided with the flow rate adjustment valve.
Background
The hydraulic device is configured by combining a hydraulic pressure generating device, a hydraulic drive device, and a hydraulic control device according to purposes, and is used in a wide range of fields from small-sized equipment to large-sized equipment, and is applied to, for example, an excavating machine such as a hydraulic excavator, and other construction machines.
As a hydraulic control device that controls supply of hydraulic oil to a hydraulic drive device, a pressure control valve, a flow control valve, and a directional control valve are generally used. Typically, relief valves, pressure reducing valves, relief valves, and the like are known as pressure control valves, throttle valves are known as flow control valves, and check valves and selector valves are known as directional control valves. By appropriately combining these independently provided control valves, a hydraulic control device capable of appropriately controlling the supply of the hydraulic oil to the hydraulic drive device can be configured.
For example, patent document 1 discloses a hydraulic control device for preventing vibration during operation of an actuator and for maintaining the actuator in a stopped state. The hydraulic control device is provided with: a variable discharge pump that controls a flow rate so as to be a pump discharge pressure obtained by adding a constant pressure to a load pressure of an actuator; a switching valve that controls a flow rate from the variable discharge pump; a pressure compensating valve disposed between the switching valve and the actuator; and a backflow preventing valve disposed between the pressure compensating valve and the actuator. The pressure compensation valve and the backflow prevention valve are provided independently, and pressure oil (working oil) discharged from the variable discharge pump is guided to the supply port, and the pressure compensation valve is opened by the pressure oil in the supply port. When the pressure compensating valve is opened, the pressure oil is supplied to the actuator via the connecting passage, the backflow preventing valve, the bridge passage, the 1 st annular groove, and the actuator port.
Documents of the prior art
Patent document
Patent document 1: japanese patent laid-open publication No. 2004-204923
Disclosure of Invention
Problems to be solved by the invention
As described above, in the conventional hydraulic control device, the flow control valve (see the "pressure compensating valve" in patent document 1) for controlling the flow rate of the hydraulic oil and the load retaining check valve (see the "backflow preventing valve" in patent document 1) for preventing the backflow of the hydraulic oil and retaining the pressure of the hydraulic oil supplied to the actuator are provided separately from each other.
Therefore, it is necessary to secure a space for installing the flow rate control valve and the load holding check valve separately in the main body of the valve structure constituting the hydraulic control device and form a flow path for appropriately associating the flow rate control valve and the load holding check valve.
Therefore, the body of the valve structure of the conventional hydraulic control device is large, and it is necessary to form a flow path for appropriately associating the flow rate control valve and the load holding check valve in the body of the valve structure.
The present invention has been made in view of the above circumstances, and an object thereof is to provide a flow rate regulating valve having an integrated structure capable of appropriately functioning as both a flow rate control valve and a load holding check valve, and a valve structure body including such a flow rate regulating valve.
Means for solving the problems
One aspect of the present invention relates to a flow rate adjustment valve including: a movable valve body having a guide flow path including a 1 st opening connected to the 1 st connection flow path and a 2 nd opening connected to the 2 nd connection flow path, wherein an arrangement position of the movable valve body varies according to a pressure of the hydraulic oil in the 1 st connection flow path and a pressure of the hydraulic oil in the 2 nd connection flow path; an opening area adjustment unit that changes the opening area of the 2 nd opening through which the hydraulic oil can pass, according to the position at which the movable valve body is disposed; a movable seal portion whose arrangement position varies according to the pressure of the working oil in the 1 st connection flow path and the pressure of the working oil in the 2 nd connection flow path, when the pressure of the hydraulic oil in the 1 st connecting passage is higher than the pressure of the hydraulic oil in the 2 nd connecting passage and the difference between the pressure of the hydraulic oil in the 1 st connecting passage and the pressure of the hydraulic oil in the 2 nd connecting passage is higher than the 1 st pressure difference, compared with the case that the difference between the pressure of the working oil in the 1 st connecting flow passage and the pressure of the working oil in the 2 nd connecting flow passage is less than or equal to the 1 st pressure difference, the opening area of the 2 nd opening part through which the working oil can pass is reduced by the opening area adjusting body, the movable seal portion can be disposed at a position where the guide flow path is blocked and at a position where the guide flow path is not blocked, according to the pressure of the hydraulic oil in the 1 st connection flow path and the pressure of the hydraulic oil in the 2 nd connection flow path.
The entire opening area adjustment body may be constituted by a 1 st cylindrical portion, the movable valve main body may have a 2 nd cylindrical portion disposed inside the 1 st cylindrical portion, a 2 nd opening portion may be formed in the 2 nd cylindrical portion, and the 1 st cylindrical portion may change an opening area of the 2 nd opening portion through which the working oil can pass by changing a range covering the 2 nd opening portion in accordance with a position at which the movable valve main body is disposed.
The flow rate adjustment valve may further include an elastic force applying portion that applies an elastic force to the movable valve body in a direction opposite to a direction in which the movable valve body is applied with the hydraulic oil from the 1 st connecting passage.
The movable valve body may determine the arrangement position based on: a force applied in the 1 st direction by the working oil in the 1 st connecting passage; a force is applied in a 2 nd direction opposite to the 1 st direction by the working oil flowing from the 1 st connection flow passage to the 2 nd connection flow passage; the force applied by the elastic force applying part.
When the pressure of the hydraulic oil in the 2 nd connecting passage is higher than the pressure of the hydraulic oil in the 1 st connecting passage, the movable seal portion may be disposed at a position in contact with the 1 st opening forming portion forming the 1 st opening to block the 1 st opening, and when the pressure of the hydraulic oil in the 2 nd connecting passage is lower than the pressure of the hydraulic oil in the 1 st connecting passage, the movable seal portion may be disposed at a position away from the 1 st opening forming portion.
The movable valve body may be provided with a valve body housing portion formed of a larger space than the movable seal portion and disposed so that the movable seal portion is movable, the guide flow path may include a 1 st opening portion, a valve body housing portion, and a 2 nd opening portion, the movable seal portion may have a spherical shape, and the 1 st opening portion may have a circular cross section having a diameter smaller than that of the movable seal portion.
Another aspect of the present invention relates to a valve structure including: a body part having a 1 st connection channel and a 2 nd connection channel; the flow rate regulating valve described above.
The body portion may have an insertion hole portion communicating with the 1 st and 2 nd connection flow paths, and the flow rate adjustment valve may be disposed in the insertion hole portion.
The flow rate adjustment valve may be detachable from the insertion hole.
The insertion hole may have: a 1 st insertion part arranged between the 1 st connection flow path and the 2 nd connection flow path; and a 2 nd insertion portion which communicates with the 2 nd connection flow path, in which a distal end portion of the movable valve body is disposed in the 1 st insertion portion so as to be able to advance and retreat, and in which a portion of the body portion where the 1 st insertion portion is formed is sealed from the distal end portion of the movable valve body.
The portion between the 1 st insertion portion and the 2 nd insertion portion inserted into the hole portion may be formed by a part of the 2 nd connection channel.
The 1 st connecting passage may communicate with a hydraulic pressure source, and the 2 nd connecting passage may communicate with an actuator.
ADVANTAGEOUS EFFECTS OF INVENTION
According to the present invention, the opening area of the 2 nd opening of the movable valve body is adjusted by the opening area adjusting body based on the pressure of the hydraulic oil in the 1 st connection flow path and the pressure of the hydraulic oil in the 2 nd connection flow path. The presence or absence of the blockage of the guide flow path is adjusted by the movable seal section according to the pressure of the hydraulic oil in the 1 st connection flow path and the pressure of the hydraulic oil in the 2 nd connection flow path. Thus, it is possible to provide a flow rate adjustment valve having an integrated structure capable of appropriately functioning as both a flow rate control valve and a load holding check valve, and a valve structure body provided with such a flow rate adjustment valve.
Drawings
Fig. 1 is a sectional view of a flow rate adjustment valve according to an embodiment of the present invention.
Fig. 2 is a circuit diagram schematically showing the function of the flow rate adjustment valve shown in fig. 1.
Fig. 3 is a diagram for explaining a function of the flow rate regulating valve as a flow rate control portion.
Fig. 4 is a diagram for explaining a function of the flow rate regulating valve as a flow rate control portion.
Fig. 5 is a diagram for explaining a function of the flow rate regulating valve as the flow rate control portion.
Fig. 6 is a diagram showing an example of the relationship between the pressure difference (X axis) of the hydraulic oil between the 1 st and 2 nd connection passages and the flow rate (Y axis) of the flow rate adjustment valve (guide passage).
Fig. 7 is a cross-sectional view showing an example of a valve structure provided with a flow rate adjustment valve.
Description of the reference numerals
10. A flow rate regulating valve; 12. a movable valve main body; 13. an O-shaped sealing ring; 14. a movable sealing part; 15. an elastic force imparting section; 16. a spring seat; 16a, a spring seat through hole; 17. a plug; 18. a guide flow path; 19. an elastic body housing part; 21. 1 st opening part; 22. a 2 nd opening part; 24. a valve core accommodating part; 25. a throttle section; 26. a tip portion; 27. a plug base; 28. a 1 st cylindrical part; 29. a 2 nd cylindrical part; 30. a flow rate control unit 31, a load holding check valve unit; 41. 1 st connecting channel; 42. a 2 nd connecting channel; 51. a main body portion; 53. an insertion hole portion; 54. the 1 st insertion part; 55. a 2 nd insertion part; 60. a valve structure; 61. an electromagnetic proportional valve; 62. a tank passage; 63. a valve core; 64. a valve core accommodating hole; 65. an overflow valve; 66. an actuator passage; 67. an actuator; 68. a pressure chamber; 69. a hydraulic source; d1, direction 1; d2, direction 2.
Detailed Description
Hereinafter, an embodiment of the present invention will be described with reference to the drawings. For convenience of illustration and understanding, the drawings attached to this specification include portions in which the reduction scale, the aspect ratio, and the like are appropriately changed and exaggerated relative to the actual reduction scale, the aspect ratio, and the like, but those skilled in the art can clearly understand the contents of the present invention based on the description contents of the specification, the claims, the abstract, and the drawings.
Fig. 1 is a sectional view of a flow rate adjustment valve 10 according to an embodiment of the present invention. Fig. 1 shows a state in which the movable seal portion 14 moves to abut against the throttle portion 25 and the 1 st opening 21 is closed by the movable seal portion 14, as will be described later.
The flow rate adjustment valve 10 includes a movable valve body 12, a movable seal portion 14, and a plug 17.
The movable valve body 12 has a cylindrical shape as a whole, and has a guide flow path 18 through which the working oil can flow. A throttle portion 25 that throttles the flow path to locally reduce the flow path area is provided in the middle portion of the movable valve body 12. The "flow path formed by the throttle portion 25" and the "flow path provided on the tip side of the throttle portion 25 (i.e., on the 1 st connection flow path 41 side described later)" constitute the 1 st opening portion 21, and the throttle portion 25 functions as a part of the 1 st opening forming portion forming the 1 st opening portion 21. The 2 nd opening 22 is formed in a portion (a 2 nd cylindrical portion 29 described later) of the main body portion of the movable valve main body 12 provided on the plug 17 side of the orifice portion 25, and the main body portion (the 2 nd cylindrical portion 29) of the movable valve main body 12 functions as a 2 nd opening forming portion forming the 2 nd opening 22. A space between the 1 st opening 21 and the 2 nd opening 22 in the movable valve body 12 (i.e., a valve body housing portion 24 described later) forms an intermediate flow path of the guide flow path 18.
As described above, the hydraulic oil introduction passage 18 includes: a 1 st opening 21 connected to a 1 st connection channel 41 formed in a main body 51 of the valve structure (in the present embodiment, a selector valve); a 2 nd opening 22 connected to the 2 nd connection channel 42 formed in the main body 51; and an intermediate flow path (valve element housing portion 24). The hydraulic oil delivered from the 1 st connection flow path 41 can flow into the 2 nd connection flow path 42 through the guide flow path 18. Further, the 1 st connection flow path 41 communicates with a hydraulic pressure source (refer to reference numeral "69" of fig. 7 described later), and the 2 nd connection flow path 42 communicates with an actuator (refer to reference numeral "67" of fig. 7 described later).
A valve body housing portion 24 formed of a space larger than the movable seal portion 14 is provided in the movable valve body 12 (in the present embodiment, in the 2 nd cylindrical portion 29), and the movable seal portion 14 is movably disposed in the valve body housing portion 24. The valve body housing portion 24 is defined by the throttle portion 25, the 2 nd cylindrical portion 29, and the spring seat 16, the 2 nd cylindrical portion 29 functions to guide the movement of the movable sealing portion 14, and the throttle portion 25 and the spring seat 16 constitute a seating portion that restricts the movement of the movable sealing portion 14. The inner diameter of the 2 nd cylindrical portion 29 is larger than the diameter of the movable seal portion 14, and the hydraulic oil can flow between the 2 nd cylindrical portion 29 and the movable seal portion 14. In the illustrated example, no member that restricts the movement of the movable seal portion 14 toward the spring seat 16 is disposed between the movable seal portion 14 and the spring seat 16, but an arbitrary restricting member (e.g., an elastic member) such as a spring may be provided between the spring seat 16 and the movable seal portion 14 in the valve body accommodating portion 24.
The movable valve body 12 slides and moves according to the pressure of the hydraulic oil in the 1 st connection passage 41 and the pressure of the hydraulic oil in the 2 nd connection passage 42, and the arrangement position in the body 51 changes. That is, the body 51 of the valve structure has an insertion hole 53 communicating with the 1 st and 2 nd connection channels 41 and 42, and the flow rate adjustment valve 10 is detachably disposed in the insertion hole 53. The movable valve body 12 of the flow rate adjustment valve 10 is disposed in the insertion hole 53 provided in the body 51 so as to be slidable and movable in a direction from the 1 st connection channel 41 to the 2 nd connection channel 42 (the 1 st direction D1) and in a direction from the 2 nd connection channel 42 to the 1 st connection channel 41 (the 2 nd direction D2).
The insertion hole 53 includes a 1 st insertion portion 54 disposed between the 1 st and 2 nd connection channels 41 and 42 and communicating with the 1 st and 2 nd connection channels 41 and 42, and a 2 nd insertion portion 55 communicating with the 2 nd connection channel 42. The distal end portion 26 of the movable valve body 12 is disposed in the 1 st insertion portion 54 so as to be movable forward and backward, and a portion of the body portion 51 where the 1 st insertion portion 54 is formed is sealed from the distal end portion 26 of the movable valve body 12. That is, a very small gap is provided between the body 51 and the portion of the outer peripheral portion of the movable valve body 12 provided on the distal end side of the throttle portion 25, and the movable valve body 12 is slidable, and the working oil does not flow between the body 51 and the portion of the outer peripheral portion of the movable valve body 12 provided on the distal end side of the throttle portion 25. On the other hand, a part of the 2 nd cylindrical portion 29 of the movable valve main body 12 is disposed in the 2 nd insertion portion 55 so as to be movable forward and backward. In the illustrated example, the 1 st insertion portion 54 and the 2 nd insertion portion 55 communicate with the 2 nd connection channel 42, respectively, a portion of the insertion hole 53 between the 1 st insertion portion 54 and the 2 nd insertion portion 55 is formed by a portion of the 2 nd connection channel 42, and the insertion hole 53 is formed by the 1 st insertion portion 54, the 2 nd insertion portion 55, and a portion of the 2 nd connection channel 42. The distal end portion 26 of the movable valve main body 12, into which the 1 st insertion portion 54 is insertable, is constituted by a portion of the throttle portion 25 and a portion of the movable valve main body 12 provided on the distal end side of the throttle portion 25.
The orifice 25 has an outer diameter larger than the diameter of the portion of the movable valve main body 12 provided on the tip side of the orifice 25, and includes a protruding portion that is tapered toward the 1 st connection flow path 41 and protrudes from the portion of the outer periphery of the movable valve main body 12 provided on the tip side of the orifice 25. The protruding portion of the throttle portion 25 functions as a stopper that regulates movement of the movable valve main body 12 toward the 1 st connection flow path 41 (in the 2 nd direction D2), and when the protruding portion of the throttle portion 25 is seated in contact with the main body portion 51, the movable valve main body 12 is disposed at a position closest to the 1 st connection flow path 41. Further, the protruding portion of the orifice portion 25 abuts against and seats on the body portion 51, and thus the flow of the hydraulic oil between the outer peripheral portion of the movable valve body 12 and the body portion 51 can be reliably blocked.
The plug 17 has a plug base portion 27 and a 1 st cylindrical portion 28 which are integrally configured, and the 1 st cylindrical portion 28 has a cylindrical shape as a whole. A male screw is formed on the outer periphery of the 1 st cylindrical portion 28, and the plug 17 is fixed to the body portion 51 by screwing the male screw to a female screw formed on the inner periphery of the 2 nd insertion portion 55 of the body portion 51. Further, an O-ring 13 is disposed between the plug base 27 and a threaded portion formed by the male thread and the female thread, and the plug 17 and the body portion 51 are sealed by the O-ring 13, so that the flow of the working oil is blocked. In the present embodiment, the 1 st cylindrical portion 28 functions as a "whole opening area adjustment body that changes the opening area of the 2 nd opening portion 22 through which the hydraulic oil can pass according to the arrangement position of the movable valve main body 12".
That is, the movable valve body 12 and the plug 17 are disposed in a nested state, and the 2 nd cylindrical portion 29 of the movable valve body 12 is disposed inside the 1 st cylindrical portion 28 constituting the tip end of the plug 17. The 2 nd opening 22 is formed in the 2 nd cylindrical portion 29, and when the movable valve main body 12 moves relative to the plug 17 (particularly, the 1 st cylindrical portion 28), the outer peripheral surface of the 2 nd cylindrical portion 29 slides on the inner peripheral surface of the 1 st cylindrical portion 28. Therefore, the 1 st cylindrical portion 28 of the plug 17 changes the range covering the 2 nd opening 22 according to the arrangement position of the movable valve body 12, and changes the opening area of the 2 nd opening 22 through which the working oil can pass. For example, when the movable valve main body 12 is disposed at the position closest to the 1 st connection flow path 41, the 1 st cylindrical portion 28 does not cover the 2 nd opening 22. On the other hand, when the movable valve main body 12 is disposed at the position farthest from the 1 st connection flow path 41, the 1 st cylindrical portion 28 completely covers and blocks the 2 nd opening 22.
The elastic body housing portion 19 formed inside the plug base portion 27 and the 1 st cylindrical portion 28 is provided with: a spring seat 16; and a spring force applying portion 15 disposed on the opposite side of the 2 nd cylindrical portion 29 of the movable valve main body 12 with the spring seat 16 interposed therebetween. The elastic force applying portion 15 is elastically and telescopically disposed in an elastic body housing portion 19 defined by the spring seat 16, the 1 st cylindrical portion 28, and the plug base portion 27. The elastic force applying portion 15 of the present embodiment is configured as a spring, and one end portion side is disposed inside the 1 st cylindrical portion 28, and the other end portion side is covered with the plug base portion 27. The O-ring 13 provided around a part of the 1 st cylindrical portion 28 of the plug 17 is press-fitted into an insertion hole portion 53 (2 nd insertion portion 55) formed in the main body portion 51 of the valve structure, and is in close contact with the main body portion 51, so that the working oil does not leak between the plug 17 and the main body portion 51. Since the plug 17 is fixedly provided in the body portion 51 as described above, the position of the spring bearing 16 and the position of the movable valve main body 12 are changed in accordance with the expansion and contraction operation of the spring force applying portion 15.
The spring force applying portion 15 is compressed between the plug 17 (particularly, the plug base portion 27) and the spring seat 16, and the spring seat 16 is urged by the spring force applying portion 15 and abuts against the distal end of the 2 nd cylindrical portion 29. Therefore, the spring force applying portion 15 applies a spring force to the movable valve main body 12 via the spring seat 16 in a direction (the 2 nd direction D2) opposite to the direction (the 1 st direction D1) in which the hydraulic oil from the 1 st connection flow path 41 is applied to the movable valve main body 12, and functions as follows: the position of the movable valve body 12 (particularly, the 2 nd opening 22) is determined based on the force received by the movable valve body 12 from the hydraulic oil in the 1 st connection flow path 41. That is, the movable valve body 12 determines the configuration position based on the following forces: a force applied by the hydraulic oil of the 1 st connection flow path 41 to the "1 st direction D1 which is one of the slidable movement directions of the movable valve main body 12"; a force applied in the "2 nd direction D2 opposite to the 1 st direction D1" by the hydraulic oil flowing into the 2 nd connection flow path 42 from the 1 st connection flow path 41 through the throttle portion 25; the force applied by the elastic force imparting portion 15.
The movable seal portion 14 is provided so as to be movable mainly in the same direction as the direction of the 1 st opening 21, and in the example shown in fig. 1, is disposed in the valve body housing portion 24 so as to be movable in the 1 st direction D1 and the 2 nd direction D2 that coincide with the slidable direction of the movable valve body 12.
The movable seal portion 14 has a spherical shape, and the 1 st opening portion 21 formed in the throttle portion 25 has a circular cross section having a diameter smaller than that of the movable seal portion 14. Therefore, when the movable seal portion 14 abuts against the throttle portion 25, the movable seal portion 14 comes into close contact with the edge of the throttle portion 25 to block the 1 st opening 21, the guide flow path 18 is blocked by the movable seal portion 14, and the working oil cannot flow between the movable seal portion 14 and the throttle portion 25.
The arrangement position of the movable seal portion 14 varies depending on the pressure of the hydraulic oil in the 1 st connection passage 41 and the pressure of the hydraulic oil in the 2 nd connection passage 42. That is, the spherical movable seal portion 14 disposed in the valve body housing portion 24 is forced by the hydraulic oil flowing into the valve body housing portion 24 from the 1 st connection flow path 41 and/or the 2 nd connection flow path 42, and exhibits characteristics and arrangement according to the flow of the hydraulic oil.
For example, when the pressure of the hydraulic oil flowing through the 1 st connection flow path 41 is higher than the pressure of the hydraulic oil flowing through the 2 nd connection flow path 42 (that is, when the pressure of the hydraulic oil in the 2 nd connection flow path 42 is lower than the pressure of the hydraulic oil in the 1 st connection flow path 41), the hydraulic oil flows into the spool housing portion 24 from the 1 st connection flow path 41 through the 1 st opening 21, and flows out from the spool housing portion 24 to the 2 nd connection flow path 42 through the 2 nd opening 22. In this case, the force applied to the movable seal portion 14 by the hydraulic oil from the 1 st connecting passage 41 is larger than the force applied to the movable seal portion 14 by the hydraulic oil from the 2 nd connecting passage 42. Therefore, the movable seal portion 14 receives a force from the hydraulic oil flowing into the valve body housing portion 24 through the 1 st opening portion 21, moves in a direction away from the throttle portion 25 (the 1 st direction D1), and is disposed at a position apart from the throttle portion 25. Thus, the guide flow path 18 that connects the 1 st connection flow path 41 and the 2 nd connection flow path 42 is formed in the movable valve main body 12, and a flow path for the hydraulic oil from the 1 st connection flow path 41 to the 2 nd connection flow path 42 is ensured.
On the other hand, when the pressure of the hydraulic oil flowing through the 2 nd connection passage 42 is higher than the pressure of the hydraulic oil flowing through the 1 st connection passage 41 (that is, when the pressure of the hydraulic oil in the 1 st connection passage 41 is lower than the pressure of the hydraulic oil in the 2 nd connection passage 42), the hydraulic oil flows from the 2 nd connection passage 42 into the valve body housing portion 24 through the 2 nd opening portion 22, passes between the movable seal portion 14 and the 2 nd cylindrical portion 29, and also spreads into the space on the spring seat 16 side of the movable seal portion 14. In this case, the force applied to the movable seal 14 by the hydraulic oil from the 2 nd connecting passage 42 is larger than the force applied to the movable seal 14 by the hydraulic oil from the 1 st connecting passage 41. Therefore, the movable seal portion 14 receives a force from the hydraulic oil to move in a direction (the 2 nd direction D2) toward the throttle portion 25 under the influence of the hydraulic oil flowing from the 2 nd opening portion 22 toward the 1 st opening portion 21, and is disposed in a position abutting against the throttle portion 25. Thereby, the movable seal portion 14 blocks the 1 st opening 21 formed in the throttle portion 25, and blocks the guide flow path 18 to put the 1 st connection flow path 41 and the 2 nd connection flow path 42 in a non-communicating state.
Fig. 2 is a circuit diagram schematically showing the function of the flow rate adjustment valve 10 shown in fig. 1. The circuit diagram shown in fig. 2 does not necessarily completely show the function of the flow rate adjustment valve 10 shown in fig. 1, but is a diagram useful for understanding the function of the flow rate adjustment valve 10.
The flow rate adjustment valve 10 of the present embodiment has both a function as the flow rate control portion 30 and a function as the load holding check valve portion 31. That is, the flow rate adjustment valve 10 functions as the flow rate control portion 30 that controls the flow rate of the hydraulic oil from the 1 st connection flow path 41 to the 2 nd connection flow path 42, and functions as the load holding check valve portion 31 that prevents the hydraulic oil from flowing from the 2 nd connection flow path 42 to the 1 st connection flow path 41.
As described above, the force applied to the flow rate adjustment valve 10 in the 1 st direction D1 is mainly a force caused by the hydraulic oil from the 1 st connection passage 41 (in particular, the hydraulic oil before passing through the orifice 25). On the other hand, the force applied to the flow rate adjustment valve 10 in the 2 nd direction D2 opposite to the 1 st direction D1 is mainly a resultant force of the force applied by the elastic force applying portion 15 and the force applied by the hydraulic oil (i.e., the hydraulic oil flowing into the 2 nd connection passage 42) that has flowed out of the 1 st connection passage 41 and passed through the orifice portion 25. Therefore, the flow rate adjustment valve 10 determines the state of the guide passage 18 based on the relationship between "the force in the 1 st direction D1 of the hydraulic oil from the 1 st connection passage 41 before passing through the orifice 25" and "the resultant force of the hydraulic oil from the 1 st connection passage 41 after passing through the orifice 25 and the force in the 2 nd direction D2 of the elastic force imparting unit 15".
For example, in the case where "the force in the 1 st direction D1 exerted on the movable seal portion 14 by the hydraulic oil from the 1 st connection channel 41 is larger than the force in the 2 nd direction D2 exerted on the movable seal portion 14 by the hydraulic oil from the 2 nd connection channel 42" and "the force in the 1 st direction D1 of the hydraulic oil from the 1 st connection channel 41 before passing through the orifice 25" is smaller than "the resultant force of the force in the 2 nd direction D2 of the hydraulic oil from the 1 st connection channel 41 after passing through the orifice 25 and the force in the 2 nd direction D2 of the elastic force applying portion 15", the flow rate adjusting valve 10 allows the flow of the hydraulic oil from the 1 st connection channel 41 to the 2 nd connection channel 42 (see the lower block of reference numeral "30" in fig. 2). On the other hand, when "the force of the hydraulic oil from the 1 st connection passage 41 applied to the movable seal unit 14 in the 1 st direction D1 is larger than the force of the hydraulic oil from the 2 nd connection passage 42 applied to the movable seal unit 14 in the 2 nd direction D2" and "the force of the hydraulic oil from the 1 st connection passage 41 in the 1 st direction D1 before passing through the orifice 25" is larger than "the resultant force of the hydraulic oil from the 1 st connection passage 41 after passing through the orifice 25 and the force of the elastic force imparting unit 15 in the 2 nd direction D2", the flow rate adjusting valve 10 restricts (eventually blocks) the guide passage 18 and restricts the flow of the hydraulic oil between the 1 st connection passage 41 and the 2 nd connection passage 42 (see the upper block of reference numeral "30" in fig. 2).
When the force in the 1 st direction D1 exerted on the movable seal 14 by the hydraulic oil from the 1 st connection flow path 41 is smaller than the force in the 2 nd direction D2 exerted on the movable seal 14 by the hydraulic oil from the 2 nd connection flow path 42, the guide flow path 18 is blocked by the movable seal 14 as described above (see reference numeral "31" in fig. 2), and the hydraulic oil does not flow between the 1 st connection flow path 41 and the 2 nd connection flow path 42.
According to the flow rate adjustment valve 10 shown in fig. 1, not only the function as the load holding check valve portion 31 but also the function as the flow rate control portion 30 can be realized by a single valve body.
In the above description of fig. 2, "the hydraulic oil from the 1 st connection flow path 41 after passing through the orifice portion 25" corresponds to the hydraulic oil that flows in sequence into the valve body housing portion 24, the 2 nd opening portion 22, and the 2 nd connection flow path 42 shown in fig. 1, and the pressure thereof depends on the pressure difference between the hydraulic oil flowing through the 1 st connection flow path 41 and the hydraulic oil flowing through the 2 nd connection flow path 42. Therefore, the position of the movable valve body 12 varies depending on the pressure of the hydraulic oil in the 1 st connection passage 41 and the pressure of the hydraulic oil in the 2 nd connection passage 42.
Fig. 3 to 5 are diagrams for explaining the function of the flow rate control portion 30 of the flow rate adjustment valve 10, and show a state in which the pressure of the hydraulic oil in the 1 st connection passage 41 is higher than the pressure of the hydraulic oil in the 2 nd connection passage 42. Fig. 3 shows a case where the pressure difference Δ P1 between the hydraulic oil in the 1 st connection channel 41 and the hydraulic oil in the 2 nd connection channel 42 is relatively small, and fig. 4 shows a case where the pressure difference Δ P2 between the hydraulic oil in the 1 st connection channel 41 and the hydraulic oil in the 2 nd connection channel 42 is larger than the pressure difference Δ P1 in the case of fig. 3. Fig. 5 is a diagram showing a state in which the 1 st connection channel 41 and the 2 nd connection channel 42 are blocked.
Fig. 6 is a diagram showing an example of the relationship between the pressure difference (X axis) of the hydraulic oil between the 1 st and 2 nd connection passages 41, 42 and the flow rate (Y axis) of the flow rate adjustment valve 10 (guide passage 18).
In a state where the pressure of the hydraulic oil in the 1 st connecting passage 41 is higher than the pressure of the hydraulic oil in the 2 nd connecting passage 42, and where "the force in the 1 st direction D1 of the hydraulic oil from the 1 st connecting passage 41 before passing through the orifice 25" is equal to or less than "the resultant force of the hydraulic oil from the 1 st connecting passage 41 after passing through the orifice 25 (i.e., the hydraulic oil flowing into the 2 nd connecting passage 42) and the force in the 2 nd direction D2 of the elastic force imparting portion 15", as shown in fig. 3, the movable sealing portion 14 is disposed at a position separated from the orifice 25 and in contact with the spring bearing 16, the protruding portion of the orifice 25 is in contact with the body portion 51, and the movable valve main body 12 is disposed at a position closest to the 1 st connecting passage 41. In this case, the 1 st cylindrical portion 28 functioning as the opening area adjustment body is disposed at a position not covering the 2 nd opening 22, and the flow path area of the guide flow path 18 (particularly, the flow path area of the 2 nd opening 22) is maximized.
In general, when a flow Coefficient (Coefficient of discharge) is represented by "C", a cross-sectional area of an orifice (flow channel) is represented by "a", and a differential pressure of hydraulic oil before and after the orifice is represented by "Δ P", a flow rate (flow velocity) "Q" flowing through the orifice is represented by
And (4) showing. While in the state shown in fig. 3, the cross-sectional area of the introduction flow path 18 (particularly, the cross-sectional area of the 2 nd opening 22) is not changed, and therefore, as the pressure difference between the hydraulic oil in the 1 st connection flow path 41 and the hydraulic oil in the 2 nd connection flow path 42 becomes larger, the flow rate of the hydraulic oil flowing from the 1 st connection flow path 41 into the 2 nd connection flow path 42 increases in proportion (see the range indicated by "Δ P1" in fig. 6).
On the other hand, in a state where the pressure of the hydraulic oil in the 1 st connecting passage 41 is higher than the pressure of the hydraulic oil in the 2 nd connecting passage 42, and "the force in the 1 st direction D1 of the hydraulic oil from the 1 st connecting passage 41 before passing through the orifice 25" is higher than "the resultant force in the 2 nd direction D2 of the hydraulic oil from the 1 st connecting passage 41 (i.e., the hydraulic oil flowing into the 2 nd connecting passage 42) and the spring force imparting portion 15 after passing through the orifice 25", as shown in fig. 4, the movable seal portion 14 is disposed at a position abutting against the spring bearing 16, the protruding portion of the orifice 25 separates from the body portion 51, and the movable valve main body 12 moves in a direction (the 1 st direction D1) separating from the 1 st connecting passage 41. With the movement of the movable valve main body 12 in the 1 st direction D1, the 2 nd opening 22 formed in the 2 nd cylindrical portion 29 is gradually covered by the 1 st cylindrical portion 28 (opening area adjustment body), and the flow passage area of the guide flow passage 18 (particularly the flow passage area of the 2 nd opening 22) gradually decreases. Therefore, the rate of increase in the flow rate of the hydraulic oil flowing from the 1 st connection passage 41 to the 2 nd connection passage 42 gradually slows (see the range indicated by "Δ P2" in fig. 6).
In this case, the movable valve main body 12 is disposed at a position where "a force (a force of the hydraulic oil from the 1 st connection flow path 41) applied to the movable valve main body 12 in the 1 st direction D1" and "a force (a force from the hydraulic oil flowing from the 1 st connection flow path 41 into the 2 nd connection flow path 42 via the valve body housing portion 24 and a force from the elastic force applying portion 15)" applied to the movable valve main body 12 in the 2 nd direction D2 are balanced. When the movable valve main body 12 moves in the direction away from the 1 st connection flow path 41 (the 1 st direction D1) and the 2 nd opening 22 formed in the 2 nd cylindrical portion 29 is completely covered with the 1 st cylindrical portion 28 (the opening area adjusting body) (see fig. 5), the guide flow path 18 is blocked by the 1 st cylindrical portion 28 (the opening area adjusting body), and the flow rate of the hydraulic oil flowing from the 1 st connection flow path 41 to the 2 nd connection flow path 42 becomes zero (0).
As described above, when the pressure of the hydraulic oil in the 1 st connecting passage 41 is higher than the pressure of the hydraulic oil in the 2 nd connecting passage 42 and the difference between the pressure of the hydraulic oil in the 1 st connecting passage 41 and the pressure of the hydraulic oil in the 2 nd connecting passage 42 is higher than the 1 st pressure difference, the 1 st cylindrical portion 28 (the entire opening area adjustment body) reduces the opening area of the 2 nd opening portion 22 through which the hydraulic oil can pass, compared to a case where the difference between the pressure of the hydraulic oil in the 1 st connecting passage 41 and the pressure of the hydraulic oil in the 2 nd connecting passage 42 is equal to or lower than the 1 st pressure difference. Therefore, as the differential pressure between the hydraulic oil in the 1 st connection passage 41 and the hydraulic oil in the 2 nd connection passage 42 increases, the "force in the 1 st direction D1 of the hydraulic oil in the 1 st connection passage 41 before passing through the orifice 25" becomes larger than the "resultant force in the 2 nd direction D2 of the hydraulic oil from the 1 st connection passage 41 and the spring force applying portion 15 after passing through the orifice 25", the flow rate in the flow rate adjustment valve 10 (the guide passage 18) also increases, and the rate of increase in the flow rate gradually decreases (see the range indicated by "Δ P1" to "Δ P2" in fig. 6). The flow rate in the flow rate control valve 10 (guide flow channel 18) according to the present embodiment has a maximum value Rmax.
Therefore, the flow rate adjustment valve 10 of the present embodiment can be suitably applied to a valve structure that requires the flow rate of the hydraulic oil to set the maximum value Rmax.
In addition, as described above, when "the force in the 1 st direction D1 of the hydraulic oil from the 1 st connection flow path 41 before passing through the orifice 25" is equal to or less than "the resultant force in the 2 nd direction D2 of the hydraulic oil from the 1 st connection flow path 41 and the spring force applying portion 15 after passing through the orifice 25", the movable valve main body 12 does not move. When the above-described "1 st pressure difference" indicates the upper limit value of the difference between the pressure of the hydraulic oil in the 1 st connection flow path 41 and the pressure of the hydraulic oil in the 2 nd connection flow path 42 in the state where the movable valve body 12 is not moving, the "1 st pressure difference" is determined based on the force in the 2 nd direction D2 of the elastic force applying portion 15. That is, the force that is relatively applied to the movable valve main body 12 in the 1 st direction D1 by the above-described "1 st pressure difference" is larger than the force that is applied to the movable valve main body 12 in the 2 nd direction D2 by the spring force applying portion 15. Further, since the force applied to the movable valve main body 12 by the elastic force applying portion 15 is determined based on the elastic modulus of the elastic force applying portion 15, the above-described "1 st pressure difference" is determined based on the elastic modulus of the elastic force applying portion 15. After the 2 nd opening 22 is completely covered with the 1 st cylindrical portion 28, the opening area of the 2 nd opening 22 does not change. Therefore, the "1 st pressure difference" is set to a value smaller than the "difference between the pressure of the hydraulic oil in the 1 st connection flow path 41 and the pressure of the hydraulic oil in the 2 nd connection flow path 42" when the 2 nd opening 22 is completely covered with the 1 st cylindrical portion 28.
On the other hand, the movable seal portion 14 can be disposed at a position where the guide flow path 18 is blocked and at a position where the guide flow path 18 is not blocked, depending on the pressure of the hydraulic oil in the 1 st connection flow path 41 and the pressure of the hydraulic oil in the 2 nd connection flow path 42. The movable seal portion 14 shown in the drawing of this example is disposed at a position to block the guide flow path 18 when the pressure of the hydraulic oil in the 2 nd connection flow path 42 is higher than the pressure of the hydraulic oil in the 1 st connection flow path 41, and is disposed at a position to not block the guide flow path 18 when the pressure of the hydraulic oil in the 2 nd connection flow path 42 is lower than the pressure of the hydraulic oil in the 1 st connection flow path 41. When the pressure of the hydraulic oil in the 2 nd connection channel 42 is equal to the pressure of the hydraulic oil in the 1 st connection channel 41, the movable seal portion 14 does not move and stops.
Next, an example of a valve structure to which the flow rate adjustment valve 10 described above can be applied will be described. Such a valve structure is not particularly limited, and the flow rate adjustment valve 10 can be suitably used in a selector valve including a spool valve, for example.
Fig. 7 is a cross-sectional view showing an example of a valve structure 60 provided with the flow rate adjustment valve 10.
The valve structure 60 shown in fig. 7 is configured as a directional valve that controls the supply of the hydraulic oil from the hydraulic source 69 to the actuator 67. The valve structure 60 includes a body 51 having a valve body accommodating hole 64 in which the valve body 63 is disposed. The valve body 63 has a plurality of cutout portions, and a land surface having a diameter substantially equal to the diameter of the valve body accommodating hole 64 is provided between the cutout portions. The 1 st connection flow path 41 is connected to the valve body accommodating hole 64 via the 2 nd connection flow path 42, and the actuator 67 is connected to the valve body accommodating hole 64 via the actuator passage 66.
The valve structure 60 of this example supplies the working oil from the hydraulic pressure source 69 to the two 1 st connecting passages 41, and the 1 st connecting passage 41 and the 2 nd connecting passage 42 are connected to each other in the main body portion 51 of the valve structure 60.
The body portion 51 of the valve structure 60 is also provided with a solenoid proportional valve 61, a relief valve 65, and a pressure chamber 68, and a tank passage 62 is formed. Two pressure chambers 68 are provided, and both end portions of the valve body 63 are disposed. Two electromagnetic proportional valves 61 are provided corresponding to the pressure chambers 68, and supply and discharge of control oil (pressure oil) to and from the pressure chambers 68 are performed to control the movement and arrangement of the spool 63 in the spool housing hole 64. Two relief valves 65 are provided, and are connected to the actuator passage 66 and the tank passage 62, respectively. When the hydraulic oil in the actuator passage 66 is equal to or higher than a predetermined pressure, each relief valve 65 communicates the actuator passage 66 and the tank passage 62, releases the hydraulic oil from the actuator passage 66 to the tank passage 62, and reduces the pressure of the hydraulic oil in the actuator passage 66.
The supply of the hydraulic oil from the 1 st connection flow path 41 to the 2 nd connection flow path 42 to the actuator 67 is controlled by the position of the valve body 63 in the valve body accommodating hole 64. When the hydraulic oil is supplied to the actuator 67, the cutout portion formed in the valve body 63 is disposed between the 2 nd connection flow path 42 and the actuator passage 66, and the 2 nd connection flow path 42 and the actuator passage 66 communicate with each other through the cutout portion, so that the hydraulic oil is supplied to and discharged from the actuator 67. On the other hand, when the hydraulic oil is not supplied to the actuator 67, the land surface between the cutout portions of the valve body 63 is disposed between the 2 nd connecting flow path 42 and the actuator passage 66, and the communication between the 2 nd connecting flow path 42 and the actuator passage 66 is blocked by the land surface, so that the supply and discharge of the hydraulic oil to and from the actuator 67 are not performed.
In the valve structure body 60 having the above-described structure, the flow rate adjustment valve 10 is attached to and detached from the insertion hole 53 formed in the body portion 51 of the valve structure body 60 such that the guide flow path 18 (see fig. 1 and the like) of the flow rate adjustment valve 10 is disposed between the 1 st connection flow path 41 and the 2 nd connection flow path 42. Thus, the flow of the hydraulic oil between the 1 st connection channel 41 and the 2 nd connection channel 42 is adjusted by the flow rate adjustment valves 10, and the flow rate (particularly, the maximum flow rate) of the hydraulic oil supplied from the 1 st connection channel 41 to the 2 nd connection channel 42 can be accurately controlled by the flow rate adjustment valves 10, and the inflow (reverse flow) of the hydraulic oil from the 2 nd connection channel 42 to the 1 st connection channel 41 can be reliably prevented.
As described above, according to the present embodiment, the load holding check valve for holding the load pressure supplied to the actuator 67 and the flow control valve having an orifice and flowing a constant flow rate in accordance with the differential pressure between the inlet pressure and the outlet pressure of the orifice can be realized by the single valve body (flow rate adjustment valve 10) having an integrated structure. This makes it possible to prevent the valve structure 60 from becoming large and complicated, to improve the performance thereof, and to control the flow rate of the hydraulic oil flowing into the actuator 67 while preventing an unexpected reverse flow of the hydraulic oil. By providing the flow rate adjustment valve 10 integrally configured to function as both the flow rate control valve and the load holding check valve as described above, and the valve structure 60 including such a flow rate adjustment valve 10, it is possible to limit the maximum flow rate of the hydraulic oil flowing into the actuator 67 while achieving downsizing and simplification of the valve structure 60.
Further, by detachably mounting the flow rate adjustment valve 10 as in the valve structure (the selector valve) 60, not only maintenance and repair of the flow rate adjustment valve 10 can be easily performed, but also a valve that performs another function can be attached and fixed in place of the flow rate adjustment valve 10.
Conventionally, there have been known reversing valves (valve structures) in which only one of the load holding check valve and the flow rate control valve is fixed to, for example, one fixing portion (i.e., one insertion hole portion 53), and there are many reversing valves of low-cost specifications in which only one of the load holding check valve and the flow rate control valve is provided. In such a low-cost reversing valve, a high-performance reversing valve having improved functions can be realized only by changing the conventional attachment/fixation valve to the flow rate adjustment valve 10 having the functions of both the load holding check valve and the flow rate control valve. Further, the load holding check valve, the flow rate control valve, and the flow rate adjustment valve 10 described above, which are detachably attached and fixed to the attachment fixing portion (the insertion hole portion 53) of the valve structure, are prepared in advance, and an appropriate valve that meets the need is attached and fixed to the attachment fixing portion from among these valves, so that various functions can be performed by one valve structure 60.
The present invention is not limited to the above-described embodiments and modifications, and may include various forms that are conceivable to those skilled in the art to which various modifications are applied, and the effects of the present invention are not limited to the above-described matters. Therefore, various additions, modifications, and partial deletions may be made to the respective elements described in the claims and the description without departing from the spirit and scope of the present invention.
For example, in the above-described embodiment, the opening area adjustment body is constituted by the 1 st cylindrical portion 28 integrally constituted with the plug base portion 27 of the plug 17, but the opening area adjustment body may be constituted by the 1 st cylindrical portion 28 separate from the plug base portion 27, or the opening area adjustment body may be constituted by a member separate from the plug 17.
Claims (12)
1. A flow rate adjustment valve is provided with:
a movable valve body having a guide flow path including a 1 st opening connected to a 1 st connection flow path and a 2 nd opening connected to a 2 nd connection flow path, the movable valve body being disposed at a position that varies according to a pressure of the hydraulic oil in the 1 st connection flow path and a pressure of the hydraulic oil in the 2 nd connection flow path;
an opening area adjuster that changes an opening area of the 2 nd opening through which the hydraulic oil can pass, according to a position at which the movable valve body is disposed;
a movable seal portion whose arrangement position varies according to the pressure of the working oil in the 1 st connection flow path and the pressure of the working oil in the 2 nd connection flow path,
when the pressure of the hydraulic oil in the 1 st connecting passage is higher than the pressure of the hydraulic oil in the 2 nd connecting passage and the difference between the pressure of the hydraulic oil in the 1 st connecting passage and the pressure of the hydraulic oil in the 2 nd connecting passage is higher than the 1 st pressure difference, the opening area of the 2 nd opening through which the hydraulic oil can pass is reduced as a whole as compared with a case where the difference between the pressure of the hydraulic oil in the 1 st connecting passage and the pressure of the hydraulic oil in the 2 nd connecting passage is equal to or less than the 1 st pressure difference,
the movable seal portion may be disposed at a position where the guide flow path is blocked and at a position where the guide flow path is not blocked, according to the pressure of the hydraulic oil in the 1 st connection flow path and the pressure of the hydraulic oil in the 2 nd connection flow path.
2. The flow regulating valve according to claim 1,
the opening area adjusting body is composed of a 1 st cylindrical part,
the movable valve main body has a 2 nd cylindrical portion disposed inside the 1 st cylindrical portion,
the 2 nd opening is formed in the 2 nd cylindrical portion,
the 1 st cylindrical portion changes a range covering the 2 nd opening portion according to an arrangement position of the movable valve body, and changes an opening area of the 2 nd opening portion through which the hydraulic oil can pass.
3. The flow regulating valve according to claim 1 or 2,
the flow rate adjustment valve further includes an elastic force applying portion that applies an elastic force to the movable valve body in a direction opposite to a direction in which the movable valve body is acted upon by the hydraulic oil from the 1 st connection flow path.
4. The flow regulating valve according to claim 3,
the movable valve body determines a configuration position based on: a force applied in the 1 st direction by the hydraulic oil in the 1 st connecting passage; a force in a 2 nd direction opposite to the 1 st direction is applied by the hydraulic oil flowing from the 1 st connection flow path to the 2 nd connection flow path; a force applied by the elastic force imparting portion.
5. The flow regulating valve according to claim 1 or 2,
wherein when the pressure of the hydraulic oil in the 2 nd connecting passage is higher than the pressure of the hydraulic oil in the 1 st connecting passage, the movable seal portion is disposed at a position in contact with a 1 st opening forming portion forming the 1 st opening, and closes the 1 st opening,
when the pressure of the hydraulic oil in the 2 nd connection passage is lower than the pressure of the hydraulic oil in the 1 st connection passage, the movable seal portion is disposed at a position separated from the 1 st opening forming portion.
6. The flow regulating valve according to claim 1 or 2,
a valve body housing portion formed of a space larger than the movable seal portion and disposed movably with respect to the movable seal portion is provided in the movable valve body,
the guide flow path includes the 1 st opening, the valve body housing portion, and the 2 nd opening,
the movable seal portion has a spherical shape,
the 1 st opening has a circular cross section having a diameter smaller than a diameter of the movable sealing portion.
7. A valve structure comprising:
a body part having a 1 st connection channel and a 2 nd connection channel;
a flow rate adjustment valve according to any one of claims 1 to 6.
8. The valve construct of claim 7 wherein,
the main body portion has an insertion hole portion communicating with the 1 st connection channel and the 2 nd connection channel,
the flow rate adjustment valve is disposed in the insertion hole.
9. The valve construct of claim 8 wherein,
the flow rate adjustment valve is disposed to be attachable to and detachable from the insertion hole.
10. The valve construct of claim 8 wherein,
the insertion hole portion has: a 1 st insertion portion disposed between the 1 st connection channel and the 2 nd connection channel; a 2 nd insertion portion communicating with the 2 nd connection flow path,
a distal end portion of the movable valve body is disposed in the 1 st insertion portion so as to be movable forward and backward, and a space between a portion of the body portion where the 1 st insertion portion is formed and the distal end portion of the movable valve body is sealed.
11. The valve construction of claim 10,
a portion between the 1 st insertion portion and the 2 nd insertion portion in the insertion hole portion is formed by a portion of the 2 nd connection flow path.
12. The valve structure according to any one of claims 7 to 11,
the 1 st connecting flow path is communicated with a hydraulic pressure source,
the 2 nd connection flow path communicates with an actuator.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2016110325A JP6773455B2 (en) | 2016-06-01 | 2016-06-01 | Flow control valve and valve structure |
| JP2016-110325 | 2016-06-01 |
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| Publication Number | Publication Date |
|---|---|
| CN107448429A CN107448429A (en) | 2017-12-08 |
| CN107448429B true CN107448429B (en) | 2020-05-01 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201710368381.2A Active CN107448429B (en) | 2016-06-01 | 2017-05-22 | Flow rate adjustment valve and valve structure |
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| Country | Link |
|---|---|
| JP (1) | JP6773455B2 (en) |
| KR (1) | KR102342222B1 (en) |
| CN (1) | CN107448429B (en) |
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| JP7360858B2 (en) * | 2019-09-10 | 2023-10-13 | ナブテスコ株式会社 | Fluid control equipment and construction machinery |
| CN112879634B (en) * | 2021-02-09 | 2022-12-27 | 国家石油天然气管网集团有限公司华南分公司 | Blade motor direct-drive and manual double-control electromagnetic pilot type Y-shaped water hammer relief valve |
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| CN201547364U (en) * | 2009-11-06 | 2010-08-11 | 周重威 | Liquid-control flow valve for ultra-high-pressure double-pole pump |
| CN202811595U (en) * | 2012-09-24 | 2013-03-20 | 温州美瑞克液压有限公司 | Novel thread plug-in mounting type split shuttle valve |
| CN202991686U (en) * | 2012-12-14 | 2013-06-12 | 阜新阜太泵业制造有限公司 | Constant flow overflow valve with spring base |
| DE102013103685A1 (en) * | 2013-04-12 | 2014-10-16 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | Changeover valve and internal combustion engine with such a changeover valve |
| CN104314899A (en) * | 2013-09-11 | 2015-01-28 | 昆山新金福精密电子有限公司 | Reversing oil path system |
| CN203516093U (en) * | 2013-09-16 | 2014-04-02 | 合肥力威汽车油泵有限公司 | Pressure and flow control valve of steering oil pump |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2017215004A (en) | 2017-12-07 |
| KR102342222B1 (en) | 2021-12-21 |
| JP6773455B2 (en) | 2020-10-21 |
| KR20170136427A (en) | 2017-12-11 |
| CN107448429A (en) | 2017-12-08 |
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