JP2017215004A - Flow rate regulating valve and valve structure - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a flow rate regulating valve which can properly fulfill both functions of a flow rate control valve and a load hold check valve, and a valve structure having the flow rate regulating valve.SOLUTION: A flow rate regulating valve 10 comprises: a movable valve body 12 whose arrangement position is varied according to the pressure of working fluids of a first connecting flow passage 41 and a second connecting flow passage 42; a first cylindrical part 28 for changing an opening area of a second opening part 22 through which the working fluids can pass according to the arrangement position of the movable valve body 12; and a movable seal part 14 whose arrangement position is varied according to the pressure of the working fluids of the first connecting flow passage 41 and the second connecting flow passage 42, and which blocks a guide flow passage 18 formed at the movable valve body 12 according to the arrangement position. When the pressure of the working fluid of the first connecting flow passage 41 is higher than the pressure of the working fluid of the second connecting flow passage 42, and a difference between the pressure of the working fluid of the first connecting flow passage 41 and the pressure of the working fluid of the second flow passage 42 is not smaller than a first pressure difference, the first cylindrical part 28 reduces the opening area of the second opening part 22.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a flow rate adjusting valve and a valve structure including the flow rate adjusting valve.

  The hydraulic device is configured by combining a hydraulic pressure generating device, a hydraulic drive device, and a hydraulic control device according to the purpose, and is used in a wide range of fields from small equipment to large equipment. For example, excavating machines such as hydraulic excavators, It is applied to other construction machines.

  Generally, a pressure control valve, a flow rate control valve, and a direction control valve are used as a hydraulic control device that controls the supply of hydraulic oil to the hydraulic drive device. Typically, relief valves, pressure reducing valves and unload valves are known as pressure control valves, throttle valves are known as flow control valves, and check valves and direction switching valves are known as direction control valves. It has been. By appropriately combining these control valves provided separately, it is possible to configure a hydraulic control device that can appropriately control the supply of hydraulic oil to the hydraulic drive device.

  For example, Patent Literature 1 discloses a hydraulic control device that aims to hold an actuator in a stopped state while preventing a shock when the actuator is operated. The hydraulic control device includes a variable discharge pump that controls a flow rate so that a pump discharge pressure is 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, and the switching valve And a pressure compensation valve provided between the actuator and the actuator, and a backflow prevention valve provided between the pressure compensation valve and the actuator. The pressure compensation valve and the backflow prevention valve are provided separately, and the pressure oil (working oil) discharged from the variable discharge pump is guided to the supply port, and the pressure compensation valve is operated by the action of the pressure oil in the supply port. open. When the pressure compensation valve is opened, the pressure oil is supplied to the actuator through the communication passage, the backflow prevention valve, the bridge passage, the first annular groove, and the actuator port.

JP 2004-204923 A

  As described above, in the conventional hydraulic control device, the flow rate control valve for controlling the flow rate of the hydraulic oil (see “pressure compensation valve” in Patent Document 1) and the hydraulic oil supplied to the actuator while preventing the backflow of the hydraulic oil. A load hold check valve (see “Backflow prevention valve” in Patent Document 1) for maintaining pressure is provided separately.

  Therefore, in order to secure the space for installing each of the flow control valve and the load hold check valve in the main body of the valve structure constituting the hydraulic control device, and appropriately link the flow control valve and the load hold check valve. It was necessary to form a flow path.

  Therefore, in the conventional hydraulic control device, the main body of the valve structure is enlarged, and it is necessary to form a flow path in the main body of the valve structure for properly connecting the flow control valve and the load hold check valve. This is not always desirable from the viewpoint of further miniaturization and simplification.

  The present invention has been made in view of the above-described circumstances, and has an integrally configured flow rate adjustment valve capable of appropriately fulfilling both functions of a flow rate control valve and a load hold check valve, and a valve including such a flow rate adjustment valve. An object is to provide a structure.

  One aspect of the present invention is a movable valve body having a guide flow path including a first opening connected to the first connection flow path and a second opening connected to the second connection flow path. A movable valve body whose arrangement position varies according to the pressure of the hydraulic fluid in the first connection flow path and the pressure of the hydraulic oil in the second connection flow path, and a second hydraulic oil that can pass through the hydraulic oil according to the arrangement position of the movable valve body. An opening area adjusting body that changes the opening area of the two opening portions, and a movable seal portion whose arrangement position varies depending on the pressure of the hydraulic oil in the first connection flow path and the pressure of the hydraulic oil in the second connection flow path. The opening area adjuster is configured such that the pressure of the hydraulic oil in the first connection flow path is greater than the pressure of the hydraulic oil in the second connection flow path and the pressure of the hydraulic oil in the first connection flow path and the operation of the second connection flow path. When the difference from the oil pressure is larger than the first pressure difference, the hydraulic oil pressure in the first connection flow path and the hydraulic oil pressure in the second connection flow path The opening area of the second opening through which the hydraulic oil can pass is made smaller than when the difference is equal to or less than the first pressure difference, and the movable seal portion is configured so that the pressure of the hydraulic oil in the first connection flow path and the second connection The present invention relates to a flow rate adjusting valve that can be disposed at a position where the guide flow path is blocked, and can be disposed at a position where the guide flow path is not blocked, according to the pressure of the hydraulic oil in the flow path.

  The opening area adjusting body is configured by a first cylindrical portion, and the movable valve body has a second cylindrical portion disposed inside the first cylindrical portion, and the second cylindrical portion is provided with the second cylindrical portion. The second opening is formed, and the first cylindrical portion changes the range covering the second opening according to the arrangement position of the movable valve body, and the second opening through which the hydraulic oil can pass The opening area may be changed.

  The flow rate adjusting valve may further include an elastic force applying unit that applies an elastic force to the movable valve body in a direction opposite to the direction of the force applied to the movable valve body by the hydraulic oil from the first connection flow path.

  The movable valve main body flows into the second connection flow path from the first connection flow path in the first direction and the force applied by the hydraulic fluid of the first connection flow path in the first direction and in the second direction opposite to the first direction. The arrangement position may be determined based on the force applied by the working oil and the force applied by the elastic force applying unit.

  When the pressure of the hydraulic fluid in the second connection channel is greater than the pressure of the hydraulic fluid in the first connection channel, the movable seal portion is in a position that contacts the first opening forming portion that forms the first opening. When the pressure of the hydraulic fluid in the second connection flow path is smaller than the pressure of the hydraulic fluid in the first connection flow path, the first opening is closed and disposed at a position separated from the first opening formation portion. May be.

  In the movable valve body, there is provided a valve body housing portion that is formed by a space larger than the movable seal portion, and the movable seal portion is movably disposed. The guide flow path includes the first opening portion, the valve body housing portion. And the second opening, the movable seal portion may have a spherical shape, and the first opening may have a circular cross section smaller than the diameter of the movable seal portion.

  Another aspect of the present invention relates to a valve structure including a main body having a first connection flow path and a second connection flow path, and the flow rate adjustment valve.

  The main body may include an insertion hole that communicates with the first connection channel and the second connection channel, and the flow rate adjustment valve may be disposed in the insertion hole.

  The flow rate adjusting valve may be detachably disposed in the insertion hole.

  The insertion hole portion includes a first insertion portion disposed between the first connection flow channel and the second connection flow channel, and a second insertion portion communicating with the second connection flow channel. The tip of the movable valve main body is disposed in the part so as to be able to advance and retreat, and the portion of the main body that forms the first insertion portion and the tip of the movable valve main body may be sealed.

  A portion of the insertion hole portion between the first insertion portion and the second insertion portion may be formed by a part of the second connection channel.

  The first connection channel may be in communication with a hydraulic pressure source, and the second connection channel may be in communication with an actuator.

  According to the present invention, the opening area of the second opening portion of the movable valve main body is adjusted by the opening area adjusting body according to the pressure of the hydraulic oil in the first connection flow path and the pressure of the hydraulic oil in the second connection flow path. Adjusted. Further, whether or not the guide channel is blocked is adjusted by the movable seal portion according to the pressure of the hydraulic fluid in the first connection channel and the pressure of the hydraulic fluid in the second connection channel. As described above, it is possible to provide an integrally configured flow rate adjustment valve that can appropriately perform both functions of the flow rate control valve and the load hold check valve, and a valve structure including such a flow rate adjustment valve.

FIG. 1 is a cross-sectional view of a flow regulating valve according to an embodiment of the present invention. FIG. 2 is a circuit diagram schematically showing the function of the flow regulating valve shown in FIG. FIG. 3 is a diagram for explaining the function of the flow rate adjustment valve as a flow rate control unit. FIG. 4 is a diagram for explaining a function of the flow rate adjustment valve as a flow rate control unit. FIG. 5 is a diagram for explaining the function of the flow rate adjustment valve as a flow rate control unit. FIG. 6 shows an example of the relationship between the pressure difference (X axis) of the hydraulic oil between the first connection flow path and the second connection flow path and the flow rate (Y axis) of the flow rate adjustment valve (guide flow path). FIG. FIG. 7 is a cross-sectional view illustrating an example of a valve structure including a flow rate adjustment valve.

  Hereinafter, an embodiment of the present invention will be described with reference to the drawings. Note that the drawings attached to the present specification include exaggerated portions in which the scale and vertical / horizontal dimensional ratios are appropriately changed from those of the actual ones for convenience of illustration and easy understanding. Those skilled in the art can clearly understand the contents of the present invention based on the description, claims, abstract, and drawings.

  FIG. 1 is a cross-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 and contacts the throttle portion 25 and the first 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 main body 12, a movable seal portion 14, and a plug 17.

  The movable valve main body 12 has a cylindrical shape as a whole and has a guide channel 18 through which hydraulic oil can flow. An intermediate portion of the movable valve body 12 is provided with a throttle portion 25 that throttles the flow path to locally reduce the flow path area. The first opening 21 is configured by “the flow path formed by the throttle portion 25” and “the flow path provided on the tip side (that is, the first connection flow channel 41 side described later)” from the throttle portion 25, The diaphragm 25 functions as a part of the first opening forming part that forms the first opening 21. A second opening 22 is formed in a body portion (second tubular portion 29 described later) of the movable valve body 12 provided on the plug 17 side of the throttle portion 25, and a body portion (second portion) of the movable valve body 12. The cylindrical portion 29) functions as a second opening forming portion that forms the second opening 22. A space between the first opening 21 and the second opening 22 in the movable valve body 12 (that is, a valve body accommodating portion 24 described later) forms an intermediate flow path of the guide flow path 18.

  Thus, the hydraulic oil guide channel 18 includes the first opening 21 connected to the first connection channel 41 formed in the main body 51 of the valve structure (in this embodiment, the direction switching valve), and the main body. 2nd opening part 22 connected to the 2nd connection flow path 42 formed in the part 51, and the intermediate | middle flow path (valve body accommodating part 24) are included. The hydraulic oil sent from the first connection channel 41 can flow into the second connection channel 42 through the guide channel 18. The first connection flow path 41 is connected to a hydraulic pressure source (see reference numeral “69” in FIG. 7 described later), and the second connection flow path 42 is connected to an actuator (refer to reference numeral “67” in FIG. 7 described later). Yes.

  In the movable valve main body 12 (in the second cylindrical portion 29 in the present embodiment), a valve body accommodating portion 24 formed by a space larger than the movable seal portion 14 is provided. Is arranged such that the movable seal portion 14 is movable. The valve body accommodating portion 24 is partitioned by the throttle portion 25, the second cylindrical portion 29, and the spring seat 16, and the second cylindrical portion 29 serves to guide the movement of the movable seal portion 14. The spring seat 16 constitutes a seat portion that restricts the movement of the movable seal portion 14. The inner diameter of the second cylindrical portion 29 is larger than the diameter of the movable seal portion 14, and the hydraulic oil can flow between the second cylindrical portion 29 and the movable seal portion 14. In the illustrated example, a member that restricts the movement of the movable seal portion 14 toward the spring seat 16 is not disposed between the movable seal portion 14 and the spring seat 16, but an arbitrary restriction member such as a spring (for example, an elastic member) Member) may be provided between the spring seat 16 and the movable seal portion 14 in the valve body accommodating portion 24.

  The movable valve main body 12 slides according to the pressure of the hydraulic oil in the first connection flow path 41 and the pressure of the hydraulic oil in the second connection flow path 42, and the arrangement position in the main body 51 changes. That is, the main body 51 of the valve structure has an insertion hole 53 that communicates with the first connection channel 41 and the second connection channel 42, and the flow rate adjusting valve 10 is detachably disposed in the insertion hole 53. . The movable valve main body 12 of the flow rate adjusting valve 10 is slidably disposed in an insertion hole 53 provided in the main body 51, and is directed from the first connection flow path 41 toward the second connection flow path 42 (first It is possible to move in the direction D1) and the direction from the second connection channel 42 toward the first connection channel 41 (second direction D2).

  The insertion hole 53 is disposed between the first connection flow path 41 and the second connection flow path 42, and communicates with the first connection flow path 41 and the second connection flow path 42. And a second insertion portion 55 communicating with the connection flow path 42. A distal end portion 26 of the movable valve main body 12 is disposed in the first insertion portion 54 so as to be movable back and forth. Between the portion of the main body portion 51 forming the first insertion portion 54 and the distal end portion 26 of the movable valve main body 12. Is sealed. That is, a very small gap that allows the movable valve body 12 to slide is provided between the outer peripheral portion of the movable valve body 12 provided on the tip side of the throttle portion 25 and the main body portion 51, It does not flow between the outer peripheral portion of the movable valve main body 12 provided on the tip side of the portion 25 and the main body portion 51. On the other hand, a part of the second cylindrical portion 29 of the movable valve main body 12 is disposed in the second insertion portion 55 so as to freely advance and retract. In the illustrated example, each of the first insertion portion 54 and the second insertion portion 55 communicates with the second connection flow path 42, and between the insertion hole portion 53 between the first insertion portion 54 and the second insertion portion 55. The portion is formed by a part of the second connection channel 42, and an insertion hole 53 is configured by the first insertion part 54, the second insertion part 55, and a part of the second connection channel 42. The distal end portion 26 of the movable valve main body 12 that can be inserted into the first insertion portion 54 is constituted by a part of the throttle portion 25 and the movable valve main body 12 provided on the distal end side of the throttle portion 25.

  The throttle portion 25 includes a protrusion having an outer diameter larger than the diameter of the movable valve body 12 provided on the tip side of the throttle portion 25 and tapering toward the first connection flow path 41. It protrudes from the outer periphery of the movable valve body 12 provided on the tip side of the throttle portion 25. The protruding portion of the throttle portion 25 functions as a stopper that restricts the movement of the movable valve main body 12 toward the first connection flow path 41 (second direction D2). When seated in contact, the movable valve body 12 is disposed at a position closest to the first connection flow path 41. In addition, the flow of the hydraulic oil between the outer peripheral part of the movable valve main body 12 and the main-body part 51 can be interrupted | blocked reliably because the protrusion part of the aperture | diaphragm | squeeze part 25 contact | abuts and seats on the main-body part 51. FIG.

  The plug 17 includes a plug base portion 27 and a first tubular portion 28 that are integrally formed, and the first tubular portion 28 has a tubular shape as a whole. A male screw is formed on the outer periphery of the first cylindrical portion 28, and the male screw is screwed with a female screw formed on the inner periphery of the second insertion portion 55 of the main body portion 51, so that the plug 17 is connected to the main body. It is fixed to the part 51. Note that an O-ring 13 is disposed between the threaded portion formed by the male screw and the female screw and the plug base 27, and the plug 17 and the main body 51 are sealed by the O-ring 13 to operate. Oil distribution is blocked. In the present embodiment, the first cylindrical portion 28 functions as “an opening area adjusting body that changes the opening area of the second opening 22 through which hydraulic oil can pass according to the arrangement position of the movable valve body 12”.

  That is, the movable valve main body 12 and the plug 17 are arranged in a nested manner, and the second cylindrical portion 29 of the movable valve main body 12 is arranged inside the first cylindrical portion 28 constituting the tip of the plug 17. . A second opening portion 22 is formed in the second tubular portion 29, and when the movable valve body 12 moves relative to the plug 17 (particularly, the first tubular portion 28), the first opening portion 22 is formed. The outer peripheral surface of the second cylindrical portion 29 slides on the inner peripheral surface of the cylindrical portion 28. Therefore, the first cylindrical portion 28 of the plug 17 changes the range covering the second opening 22 according to the arrangement position of the movable valve body 12, and the opening area of the second opening 22 through which the hydraulic oil can pass is changed. Change. For example, when the movable valve main body 12 is disposed at a position closest to the first connection flow path 41, the first tubular portion 28 does not cover the second opening 22. On the other hand, when the movable valve main body 12 is disposed at a position farthest from the first connection flow path 41, the first tubular portion 28 completely covers and closes the second opening portion 22.

  The elastic body accommodating portion 19 formed inside the plug base portion 27 and the first tubular portion 28 includes a spring seat 16 and a second tubular portion 29 of the movable valve body 12 via the spring seat 16. An elastic force applying unit 15 disposed on the opposite side is provided. The elastic force imparting portion 15 is arranged to be elastically stretchable in the elastic body accommodating portion 19 defined by the spring seat 16, the first cylindrical portion 28, and the plug base portion 27. The elastic force applying portion 15 of the present embodiment is configured as a spring, one end side is disposed inside the first cylindrical portion 28, and the other end side is covered with a plug base portion 27. The O-ring 13 provided around a part of the first tubular portion 28 of the plug 17 is press-fitted into an insertion hole portion 53 (second insertion portion 55) formed in the main body portion 51 of the valve structure. The hydraulic fluid is in close contact with the main body 51 and does not leak from between the plug 17 and the main body 51. Thus, since the plug 17 is fixedly provided with respect to the main body portion 51, the position of the spring seat 16 and the position of the movable valve main body 12 vary according to the expansion and contraction of the elastic force applying portion 15.

  The elastic 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 receiving a force from the elastic force applying portion 15 and is a second cylindrical portion. It abuts on the tip of 29. Therefore, the elastic force imparting portion 15 springs in a direction (second direction D2) opposite to the direction of force (first direction D1) applied to the movable valve body 12 by the hydraulic oil from the first connection flow path 41. The position of the movable valve body 12 (particularly, the second opening 22) is applied to the movable valve body 12 via the seat 16 according to the force received by the movable valve body 12 from the hydraulic oil in the first connection flow path 41. Play a role in determining. In other words, the movable valve main body 12 has a force applied by the hydraulic fluid of the first connection flow path 41 to the “first direction D1 which is one of the movable directions of the movable valve main body 12”, and “first To the second direction D2 opposite to the direction D1 "by the working force and the elastic force applying unit 15 applied by the hydraulic oil flowing from the first connection channel 41 through the throttle unit 25 to the second connection channel 42. The placement position is determined based on the force.

  The movable seal portion 14 is mainly provided so as to be movable in the same direction as the direction of the first opening 21. In the example shown in FIG. 1, the first direction D1 that coincides with the slide movable direction of the movable valve body 12 and It arrange | positions in the valve body accommodating part 24 so that a movement to the 2nd direction D2 is possible.

  While the movable seal portion 14 has a spherical shape, the first opening 21 formed in the throttle portion 25 has a circular cross section that is smaller than the diameter of the movable seal portion 14. Therefore, when the movable seal portion 14 comes into contact with the throttle portion 25, the movable seal portion 14 is in close contact with the edge portion of the throttle portion 25 and closes the first opening 21, and the guide channel 18 is blocked by the movable seal portion 14. Therefore, the hydraulic oil cannot flow between the movable seal portion 14 and the throttle portion 25.

  Such an arrangement position of the movable seal portion 14 varies depending on the pressure of the hydraulic oil in the first connection flow path 41 and the pressure of the hydraulic oil in the second connection flow path 42. That is, the spherical movable seal portion 14 disposed in the valve body housing portion 24 is applied with force by the hydraulic oil flowing into the valve body housing portion 24 from the first connection flow path 41 and / or the second connection flow path 42, The behavior and arrangement according to the flow of hydraulic oil are shown.

  For example, when the pressure of the hydraulic oil flowing through the first connection flow path 41 is higher than the pressure of the hydraulic oil flowing through the second connection flow path 42 (that is, the pressure of the hydraulic oil in the second connection flow path 42 is the first connection flow path When the hydraulic oil pressure is lower than 41, the hydraulic oil flows from the first connection channel 41 through the first opening 21 into the valve body housing portion 24, and from the valve body housing portion 24 to the second opening portion 22. It flows out to the 2nd connection channel 42 via. In this case, the force applied to the movable seal part 14 by the hydraulic oil from the first connection flow path 41 is greater than the force applied to the movable seal part 14 by the hydraulic oil from the second connection flow path 42. Therefore, the movable seal part 14 receives a force from the hydraulic oil in the direction away from the throttle part 25 (first direction D1) due to the influence of the hydraulic oil flowing into the valve body housing part 24 through the first opening 21. It moves and is arranged at a position away from the diaphragm unit 25. As a result, the movable valve body 12 is formed with the guide channel 18 that communicates the first connection channel 41 and the second connection channel 42, and the operation from the first connection channel 41 to the second connection channel 42 is performed. An oil flow path is secured.

  On the other hand, when the pressure of the hydraulic oil flowing through the second connection flow path 42 is larger than the pressure of the hydraulic oil flowing through the first connection flow path 41 (that is, the pressure of the hydraulic oil in the first connection flow path 41 is the second connection When the pressure is lower than the pressure of the hydraulic oil in the flow path 42), the hydraulic oil flows from the second connection flow path 42 through the second opening 22 into the valve body accommodating portion 24, and the movable seal portion 14 and the second cylinder It passes through the space between the shape portions 29 and also enters the space closer to the spring seat 16 than the movable seal portion 14. In this case, the force applied to the movable seal part 14 by the hydraulic oil from the second connection flow path 42 is greater than the force applied to the movable seal part 14 by the hydraulic oil from the first connection flow path 41. Therefore, the movable seal portion 14 receives the force from the hydraulic oil in the direction approaching the throttle portion 25 (second direction D2) due to the influence of the hydraulic oil from the second opening portion 22 toward the first opening portion 21, and moves. It arrange | positions in the position contact | abutted to the aperture | diaphragm | squeeze part 25. FIG. Accordingly, the movable seal portion 14 closes the first opening 21 formed in the throttle portion 25, blocks the guide flow path 18, and the first connection flow path 41 and the second connection flow path 42 are in a non-communication state. Placed in.

  FIG. 2 is a circuit diagram schematically showing the function of the flow regulating valve 10 shown in FIG. In addition, although the function of the flow regulating valve 10 shown in FIG. 1 is not necessarily expressed completely in the circuit diagram shown in FIG. 2, it is a diagram useful for understanding the function of the flow regulating valve 10.

  The flow rate adjusting valve 10 of this embodiment has both a function as the flow rate control unit 30 and a function as the load hold check valve unit 31. That is, the flow rate adjusting valve 10 functions as the flow rate control unit 30 that controls the flow rate of the hydraulic oil from the first connection flow path 41 to the second connection flow path 42, and from the second connection flow path 42 to the first connection flow path. It functions as a load hold check valve portion 31 that prevents the hydraulic oil from flowing into the oil supply 41.

  As described above, the force applied to the flow rate adjustment valve 10 in the first direction D1 is a force mainly caused by the hydraulic fluid from the first connection flow path 41 (particularly hydraulic fluid before passing through the throttle portion 25). . On the other hand, the force applied to the flow rate adjustment valve 10 in the second direction D2 opposite to the first direction D1 mainly flows out from the first connection flow path 41 and passes through the throttle portion 25 (that is, first oil) 2 is a resultant force of the hydraulic oil flowing into the connection flow path 42 and the force of the elastic force applying unit 15. Therefore, “the force in the first direction D1 of the hydraulic oil from the first connection channel 41 before passing through the throttle unit 25” and “the hydraulic oil from the first connection channel 41 after passing through the throttle unit 25”. The flow rate adjusting valve 10 determines the state of the guide flow path 18 in accordance with the relationship with “the resultant force of the elastic force applying unit 15 in the second direction D2”.

  For example, “the force that the hydraulic oil from the first connection flow path 41 applies to the movable seal portion 14 in the first direction D1 is the second level of the hydraulic oil from the second connection flow path 42 to the movable seal portion 14. Is greater than the force applied in the direction D2 ”and“ the force in the first direction D1 of the hydraulic oil from the first connection flow path 41 before passing through the throttle 25 ”is“ after passing through the throttle 25 ”. When the hydraulic oil from the first connection flow path 41 and the resultant force of the elastic force applying unit 15 in the second direction D2 are smaller than “the combined force in the second direction D2,” the flow rate adjusting valve 10 moves from the first connection flow path 41 to the second connection flow path. The flow of hydraulic oil toward 42 is allowed (see the lower block of reference numeral “30” in FIG. 2). On the other hand, “the force that the hydraulic oil from the first connection flow path 41 applies to the movable seal portion 14 in the first direction D1 is that the hydraulic oil from the second connection flow path 42 2 ”and“ the force in the first direction D1 of the hydraulic oil from the first connection flow path 41 before passing through the throttle part 25 ”is“ after passing through the throttle part 25 ”. The hydraulic fluid from the first connection flow path 41 and the resultant force of the elastic force applying portion 15 in the second direction D2 is larger than the flow regulating valve 10 restricts the guide flow path 18 (finally, The flow of the hydraulic fluid between the first connection flow path 41 and the second connection flow path 42 is restricted (see the upper block of reference numeral “30” in FIG. 2).

  Note that the force applied by the hydraulic oil from the first connection flow path 41 to the movable seal portion 14 in the first direction D1 is the second level of the hydraulic oil from the second connection flow path 42 to the movable seal portion 14. When the force is smaller than the force applied in the direction D2, the guide channel 18 is blocked by the movable seal portion 14 as described above (see reference numeral “31” in FIG. 2), and the first connection channel 41 and the second connection are connected. No hydraulic oil flows between the flow path 42.

  As described above, according to the flow rate adjusting valve 10 shown in FIG. 1, not only the function as the load hold check valve unit 31 but also the function as the flow rate control unit 30 can be realized by a single valve body.

  Note that “the hydraulic fluid from the first connection flow path 41 after passing through the throttle portion 25” in the description of FIG. 2 is the valve body accommodating portion 24, the second opening portion 22 and the second connection shown in FIG. This corresponds to the hydraulic oil that sequentially flows into the flow path 42, and its pressure depends on the differential pressure between the hydraulic oil that flows through the first connection flow path 41 and the hydraulic oil that flows through the second connection flow path 42. Accordingly, the arrangement position of the movable valve main body 12 varies depending on the pressure of the hydraulic oil in the first connection flow path 41 and the pressure of the hydraulic oil in the second connection flow path 42.

  3-5 is a figure for demonstrating the function as the flow control part 30 of the flow regulating valve 10, and the pressure of the hydraulic fluid of the 1st connection flow path 41 is the hydraulic fluid of the 2nd connection flow path 42. It shows a state larger than the pressure. 3 shows a case where the pressure difference ΔP1 between the hydraulic oil in the first connection flow path 41 and the hydraulic oil in the second connection flow path 42 is relatively small, and FIG. The case where the pressure difference ΔP2 between the hydraulic fluid in the second connection flow path 42 is larger than the pressure difference ΔP1 in the case of FIG. 3 is shown. FIG. 5 is a diagram illustrating a state where the first connection channel 41 and the second connection channel 42 are blocked.

  FIG. 6 shows the difference between the hydraulic oil pressure difference (X axis) between the first connection channel 41 and the second connection channel 42 and the flow rate (Y axis) of the flow rate adjusting valve 10 (guide channel 18). It is a figure which shows the example of a relationship.

  In a state where the pressure of the hydraulic oil in the first connection flow path 41 is larger than the pressure of the hydraulic oil in the second connection flow path 42, “the hydraulic oil from the first connection flow path 41 before passing through the throttle portion 25 The “force in the first direction D1” is “the hydraulic oil from the first connection flow path 41 after passing through the throttle portion 25 (that is, the hydraulic oil flowing into the second connection flow path 42) and the elastic force applying section 15. In the case of “the resultant force in the second direction D2” or less, as shown in FIG. 3, the movable seal portion 14 is disposed at a position in contact with the spring seat 16 apart from the throttle portion 25, while the throttle portion The 25 protruding portions abut on the main body 51 and the movable valve main body 12 is disposed at a position closest to the first connection flow path 41. In this case, the first cylindrical portion 28 that functions as the opening area adjusting body is disposed at a position that does not cover the second opening portion 22, and the flow passage area of the guide flow passage 18 (particularly, the flow passage area of the second opening portion 22). ) Is the maximum.

  In general, the flow rate (flow velocity) “Q” flowing through the orifice is represented by “C” as a flow coefficient (Coefficient of discharge), “A” as a cross-sectional area of the orifice (flow path), When the differential pressure is expressed by “ΔP”, it is expressed by “Q = CA√ (ΔP)”. Since the cross-sectional area of the guide channel 18 (particularly, the cross-sectional area of the second opening 22) remains unchanged while being placed in the state shown in FIG. 3, the hydraulic oil and the second connection of the first connection channel 41 are not changed. As the differential pressure with the hydraulic oil in the flow path 42 increases, the flow rate of the hydraulic oil flowing from the first connection flow path 41 into the second connection flow path 42 increases proportionally (indicated by “ΔP1” in FIG. 6). Range).

  On the other hand, the pressure of the hydraulic oil in the first connection channel 41 is larger than the pressure of the hydraulic oil in the second connection channel 42, and “operation from the first connection channel 41 before passing through the throttle portion 25”. The “force in the first direction D1 of the oil” is “the working oil from the first connection flow path 41 after passing through the throttle portion 25 (that is, the hydraulic oil flowing into the second connection flow path 42) and the elastic force applying section. 15 is greater than “the resultant force in the second direction D2”, as shown in FIG. The protruding part moves away from the main body part 51 and the movable valve main body 12 moves in a direction away from the first connection flow path 41 (first direction D1). As the movable valve body 12 moves in the first direction D1, the second opening 22 formed in the second tubular portion 29 is gradually moved by the first tubular portion 28 (opening area adjusting body). The channel area of the guide channel 18 (in particular, the channel area of the second opening 22) is gradually reduced. Therefore, the rate of increase in the flow rate of the hydraulic oil flowing from the first connection flow path 41 to the second connection flow path 42 gradually decreases (see the range indicated by “ΔP2” in FIG. 6).

  In this case, “the force applied to the movable valve body 12 in the first direction D1 (force from the hydraulic fluid in the first connection flow path 41)” and “the force applied to the movable valve body 12 in the second direction D2 ( The movable valve body 12 is in a position where the force from the hydraulic oil flowing into the second connection flow path 42 from the first connection flow path 41 through the valve body accommodating portion 24 and the force from the elastic force applying section 15 are balanced. Be placed. The movable valve main body 12 moves in the direction away from the first connection flow path 41 (first direction D1), and the second opening 22 formed in the second cylindrical portion 29 is the first cylindrical portion 28. When completely covered by the (opening area adjusting body) (see FIG. 5), the guide channel 18 is blocked by the first cylindrical portion 28 (opening area adjusting body), and the second connection is made from the first connection channel 41. The flow rate of the hydraulic oil flowing into the flow path 42 is zero (0).

  As described above, the first cylindrical portion 28 (opening area adjusting body) is configured so that the pressure of the hydraulic oil in the first connection flow path 41 is larger than the pressure of the hydraulic oil in the second connection flow path 42 and the first connection flow path. When the difference between the pressure of the hydraulic oil 41 and the pressure of the hydraulic oil in the second connection flow path 42 is larger than the first pressure difference, the pressure of the hydraulic oil in the first connection flow path 41 and the second connection flow The opening area of the second opening 22 through which hydraulic oil can pass is made smaller than when the difference from the hydraulic oil pressure in the passage 42 is equal to or less than the first pressure difference. Therefore, the differential pressure between the hydraulic oil in the first connection flow path 41 and the hydraulic oil in the second connection flow path 42 is increased, and “the first hydraulic fluid in the first connection flow path 41 before passing through the throttle portion 25 is increased. As the “force in one direction D1” becomes larger than “the resultant force in the second direction D2 of the hydraulic oil and the elastic force applying portion 15 after passing through the throttle portion 25”, Although the flow rate in the flow rate adjusting valve 10 (guide channel 18) also increases, the rate of increase in the flow rate gradually decreases (see the range indicated by “ΔP1” to “ΔP2” in FIG. 6). In addition, the maximum value Rmax is set for the flow rate in the flow rate adjustment valve 10 (guide flow path 18) of the present embodiment.

  Therefore, the flow rate adjusting valve 10 of the present embodiment can be suitably applied to a valve structure in which the maximum value Rmax is required to be set for the hydraulic oil flow rate.

  As described above, the “force in the first direction D1 of the hydraulic oil from the first connection channel 41 before passing through the throttle unit 25” is “the first connection channel after passing through the throttle unit 25”. When the hydraulic oil from 41 and the resultant force of the elastic force applying unit 15 in the second direction D2 are equal to or less than the movable valve body 12, the movable valve body 12 does not move. The above “first pressure difference” indicates the upper limit value of the difference between the hydraulic oil pressure in the first connection flow path 41 and the hydraulic oil pressure in the second connection flow path 42 in a state where the movable valve body 12 does not move. In this case, the “first pressure difference” is determined based on the force of the elastic force applying unit 15 in the second direction D2. That is, the force that is relatively applied to the movable valve main body 12 in the first direction D1 based on the “first pressure difference” is applied to the movable valve main body 12 in the second direction D2 by the elastic force applying unit 15. It becomes larger than the magnitude of the applied force. Since the force applied to the movable valve body 12 by the elastic force applying unit 15 is determined based on the elastic coefficient of the elastic force applying unit 15, the above “first pressure difference” is the elastic coefficient of the elastic force applying unit 15. It will be determined based on. Moreover, after the 2nd opening part 22 is completely covered with the 1st cylindrical part 28, the opening area of the 2nd opening part 22 does not change. Therefore, the above “first pressure difference” means that “the pressure of the hydraulic oil in the first connection flow path 41 and the second connection when the second opening 22 is completely covered by the first cylindrical portion 28. It is set to a value smaller than the “difference from the hydraulic oil pressure in the flow path 42”.

  On the other hand, the movable seal portion 14 can be arranged at a position where the guide flow path 18 is blocked and guided according to the pressure of the hydraulic oil in the first connection flow path 41 and the pressure of the hydraulic oil in the second connection flow path 42. It can be arranged at a position where the flow path 18 is not blocked. The illustrated movable seal portion 14 of this example is disposed at a position where the guide channel 18 is blocked when the pressure of the hydraulic fluid in the second connection channel 42 is greater than the pressure of the hydraulic fluid in the first connection channel 41. When the pressure of the hydraulic fluid in the second connection channel 42 is smaller than the pressure of the hydraulic fluid in the first connection channel 41, the guide channel 18 is not cut off. In addition, when the pressure of the hydraulic fluid of the 2nd connection flow path 42 is equal to the pressure of the hydraulic fluid of the 1st connection flow path 41, the movable seal | sticker part 14 stops without moving.

  Next, an example of a valve structure to which the above-described flow rate adjustment valve 10 can be applied will be described. Such a valve structure is not particularly limited, and for example, the flow rate adjusting valve 10 described above can be suitably used in a directional switching valve including a spool valve.

  FIG. 7 is a cross-sectional view illustrating an example of the valve structure 60 including the flow rate adjusting valve 10.

  The valve structure 60 shown in FIG. 7 is configured as a direction switching valve that controls the supply of hydraulic oil from the hydraulic source 69 to the actuator 67. The valve structure 60 includes a main body 51 in which a spool accommodation hole 64 in which a spool 63 is disposed is formed. The spool 63 is formed with a plurality of notches, and a land portion having a diameter substantially the same as the diameter of the spool accommodation hole 64 is provided between the notches. The spool housing hole 64 is connected to the first connection channel 41 via the second connection channel 42 and to the actuator 67 via the actuator channel 66.

  In the valve structure 60 of this example, hydraulic oil is supplied from the hydraulic source 69 to the two first connection channels 41, and each first connection channel 41 is a second connection channel in the main body 51 of the valve structure 60. 42.

  The main body 51 of the valve structure 60 is further provided with an electromagnetic 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 ends of the spool 63 are disposed. Two electromagnetic proportional valves 61 are provided so as to correspond to the pressure chamber 68, and supply and discharge of control oil (pressure oil) to the pressure chamber 68, and movement of the spool 63 in the spool accommodation hole 64 and Control placement. Two relief valves 65 are provided, and each is connected to an actuator passage 66 and a tank passage 62. When the hydraulic oil in the actuator passage 66 indicates a predetermined pressure or more, each relief valve 65 communicates the actuator passage 66 and the tank passage 62 to release the hydraulic oil from the actuator passage 66 to the tank passage 62. Reduce hydraulic oil pressure.

  The supply of hydraulic oil supplied from the first connection channel 41 to the second connection channel 42 to the actuator 67 is controlled by the position of the spool 63 in the spool accommodation hole 64. When hydraulic fluid is supplied to the actuator 67, a notch formed in the spool 63 is disposed between the second connection channel 42 and the actuator passage 66, and the second connection channel 42 is interposed via the notch. And the actuator passage 66 communicate with each other, and hydraulic oil is supplied to and discharged from the actuator 67. On the other hand, when hydraulic oil is not supplied to the actuator 67, the land portion between the notches of the spool 63 is disposed between the second connection flow path 42 and the actuator passage 66, and the second connection flow path is formed by the land portion. Communication between the actuator 42 and the actuator passage 66 is cut off, and hydraulic oil is not supplied to or discharged from the actuator 67.

  In the valve structure 60 having the above-described structure, the guide flow path 18 (see FIG. 1 and the like) of the flow rate adjustment valve 10 is disposed between each first connection flow path 41 and the second connection flow path 42. The flow rate adjusting valve 10 is detachably attached to the insertion hole 53 formed in the main body 51 of the valve structure 60. Thereby, the flow of the hydraulic fluid between the first connection flow path 41 and the second connection flow path 42 is adjusted by the flow rate adjustment valve 10, and the second connection is made from the first connection flow path 41 by each flow rate adjustment valve 10. While accurately controlling the flow rate (especially the maximum flow rate) of the hydraulic oil supplied to the flow path 42, the flow of hydraulic oil from the second connection flow path 42 to the first connection flow path 41 (reverse flow) is reliably prevented. Is possible.

  As described above, according to the present embodiment, the load hold check valve that holds the load pressure supplied to the actuator 67 and the throttle are provided, and the flow rate is constant according to the differential pressure between the inlet pressure and the outlet pressure of the throttle. Can be realized by a single valve body (flow rate adjusting valve 10) having an integral structure. Accordingly, the valve structure 60 can be improved in function while preventing an increase in size and complexity, and the flow rate of the working oil flowing into the actuator 67 can be controlled while preventing the unintended backflow of the working oil. Thus, by providing the integral flow control valve 10 that can appropriately perform both the functions of the flow control valve and the load hold check valve, and the valve structure 60 including such a flow control valve 10, the valve The maximum flow rate of the hydraulic oil flowing into the actuator 67 can be regulated while reducing the size and simplification of the structure 60.

  Further, by providing the flow regulating valve 10 so as to be detachable like the above-described valve structure (direction switching valve) 60, not only can the maintenance and repair of the flow regulating valve 10 be performed easily, but also other functions can be achieved. It is also possible to attach a valve to be used instead of the flow rate adjustment valve 10.

  For example, a direction switching valve (valve structure) in which only one of a load hold check valve and a flow rate control valve is mounted on one mounting portion (that is, one insertion hole portion 53) has been conventionally known. There are also many low-priced directional control valves in which only one of a load hold check valve and a flow rate control valve is provided. In such a low-priced directional control valve, the existing mounted valve is changed to the above-described flow rate adjusting valve 10 having both functions of a load hold check valve and a flow rate control valve, and the functionally improved direction is improved. It is possible to realize a switching valve. In addition, a load hold check valve, a flow rate control valve, and the above-described flow rate adjustment valve 10 that can be detachably attached to the mounting portion (insertion hole portion 53) of the valve structure are prepared in advance. It is possible to perform various functions by the single valve structure 60 by mounting an appropriate valve as necessary from the inside on the mounting portion.

  The present invention is not limited to the above-described embodiments and modifications, and can include various aspects to which various modifications that can be conceived by those skilled in the art can be included. It is not limited to the matter of. Therefore, various additions, modifications, and partial deletions can be made to each element described in the claims and the specification without departing from the technical idea and spirit of the present invention.

  For example, in the above-described embodiment, the opening area adjusting body is configured by the first cylindrical portion 28 integrally formed with the plug base portion 27 of the plug 17, but the first cylindrical shape separated from the plug base portion 27. The opening area adjusting body may be configured by the portion 28, or the opening area adjusting body may be configured by a member separate from the plug 17.

DESCRIPTION OF SYMBOLS 10 Flow control valve 12 Movable valve main body 13 O ring 14 Movable seal part 15 Elastic force provision part 16 Spring seat 16a Spring seat through-hole 17 Plug 18 Guide flow path 19 Elastic body accommodating part 21 1st opening part 22 2nd opening part 24 Valve body housing part 25 Restriction part 26 Tip part 27 Plug base part 28 First cylindrical part 29 Second cylindrical part 30 Flow rate control part 31 Load hold check valve part 41 First connection flow path 42 Second connection flow path 51 Main body 53 Insert hole 54 First insert 55 Second insert 60 Valve structure 61 Proportional solenoid valve 62 Tank passage 63 Spool 64 Spool receiving hole 65 Relief valve 66 Actuator passage 67 Actuator 68 Pressure chamber 69 Hydraulic source D1 First Direction D2 second direction

Claims (12)

A movable valve body having a guide flow path including a first opening connected to the first connection flow path and a second opening connected to the second connection flow path, the operation of the first connection flow path A movable valve body whose arrangement position varies depending on the pressure of the oil and the pressure of the hydraulic oil in the second connection flow path;
An opening area adjusting body that changes an opening area of the second opening through which hydraulic oil can pass according to an arrangement position of the movable valve body;
A movable seal portion whose arrangement position varies according to the pressure of the hydraulic oil in the first connection flow path and the pressure of the hydraulic oil in the second connection flow path,
In the opening area adjusting body, the pressure of the hydraulic oil in the first connection channel is greater than the pressure of the hydraulic oil in the second connection channel, and the pressure of the hydraulic oil in the first connection channel and the second connection When the difference between the hydraulic oil pressure in the flow path is larger than the first pressure difference, the difference between the hydraulic oil pressure in the first connection flow path and the hydraulic oil pressure in the second connection flow path is The opening area of the second opening through which hydraulic oil can pass is smaller than in the case of the first pressure difference or less,
The movable seal portion can be disposed at a position that blocks the guide flow path according to the pressure of the hydraulic oil in the first connection flow path and the pressure of the hydraulic oil in the second connection flow path, and the guide flow A flow control valve that can be placed in a position that does not block the road. The opening area adjusting body is constituted by a first cylindrical portion,
The movable valve body has a second cylindrical portion disposed inside the first cylindrical portion,
The second cylindrical portion is formed with the second opening,
The first cylindrical portion changes an opening area of the second opening through which hydraulic oil can pass by changing a range covering the second opening according to an arrangement position of the movable valve body. 1. The flow regulating valve according to 1.   The apparatus according to claim 1, further comprising an elastic force applying unit that applies an elastic force to the movable valve body in a direction opposite to a direction of a force applied to the movable valve body by the hydraulic oil from the first connection flow path. The flow regulating valve described.   The movable valve body is configured such that the force applied by the hydraulic oil in the first connection flow path in the first direction and the second connection from the first connection flow path in the second direction opposite to the first direction. The flow regulating valve according to claim 3, wherein the arrangement position is determined based on a force applied by the hydraulic oil flowing into the flow path and a force applied by the elastic force applying unit. The movable seal portion is
When the pressure of the hydraulic fluid in the second connection channel is greater than the pressure of the hydraulic fluid in the first connection channel, the hydraulic fluid is disposed at a position that contacts the first opening forming portion that forms the first opening. Close the first opening,
When the pressure of the hydraulic fluid in the second connection channel is smaller than the pressure of the hydraulic fluid in the first connection channel, the hydraulic fluid is disposed at a position separated from the first opening forming portion. The flow regulating valve according to any one of the above. In the movable valve body, there is provided a valve body accommodating portion that is formed by a space larger than the movable seal portion, and the movable seal portion is movably disposed.
The guide flow path includes the first opening, the valve body accommodating portion, and the second opening,
The movable seal portion has a spherical shape,
The flow control valve according to claim 1, wherein the first opening has a circular cross section that is smaller than a diameter of the movable seal portion. A main body having a first connection channel and a second connection channel;
A valve structure comprising the flow regulating valve according to any one of claims 1 to 6. The main body has an insertion hole that communicates with the first connection channel and the second connection channel,
The valve structure according to claim 7, wherein the flow rate adjusting valve is disposed in the insertion hole.   The valve structure according to claim 8, wherein the flow regulating valve is detachably disposed in the insertion hole. The insertion hole portion includes a first insertion portion disposed between the first connection flow channel and the second connection flow channel, and a second insertion portion communicating with the second connection flow channel. ,
In the first insertion portion, a distal end portion of the movable valve main body is disposed so as to be movable back and forth, and a portion of the main body portion forming the first insertion portion and the distal end portion of the movable valve main body are between The valve structure according to any one of claims 8 and 9, which is sealed.   The valve structure according to claim 10, wherein a portion between the first insertion portion and the second insertion portion in the insertion hole portion is formed by a part of the second connection flow path. The first connection flow path communicates with a hydraulic pressure source;
The valve structure according to any one of claims 7 to 11, wherein the second connection flow path communicates with an actuator.

Images