CN111561573A - Flow control valve - Google Patents

Flow control valve Download PDF

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Publication number
CN111561573A
CN111561573A CN202010090711.8A CN202010090711A CN111561573A CN 111561573 A CN111561573 A CN 111561573A CN 202010090711 A CN202010090711 A CN 202010090711A CN 111561573 A CN111561573 A CN 111561573A
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CN
China
Prior art keywords
spool
chamber
body portion
control valve
hole
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN202010090711.8A
Other languages
Chinese (zh)
Inventor
岩崎仁
西田裕平
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nabtesco Corp
Original Assignee
Nabtesco Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Nabtesco Corp filed Critical Nabtesco Corp
Publication of CN111561573A publication Critical patent/CN111561573A/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/14—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with ball-shaped valve member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0603—Multiple-way valves
    • F16K31/061—Sliding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
    • F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/20—Excess-flow valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K27/00—Construction of housing; Use of materials therefor
    • F16K27/04—Construction of housing; Use of materials therefor of sliding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0644—One-way valve
    • F16K31/0655—Lift valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0675—Electromagnet aspects, e.g. electric supply therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/36—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor

Abstract

The invention provides a flow control valve which can be operated with a relatively small force. A flow rate control valve (10) is provided with: a spool housing block (30) having a spool housing hole (31); and a spool (40) having: a spool main body portion (46); a spool large-diameter portion (50) having a diameter larger than that of the spool main body portion (46); and a flow path (51) which is open at one end side in the axial direction (da) and communicates with a chamber (C1), wherein the chamber (C1) is located between a portion of the spool main body portion (46) which is located on the other end side in the axial direction (da) than the spool large diameter portion (50) and the spool housing block (30), and wherein the spool (40) is movably housed in the spool housing hole (31).

Description

Flow control valve
Technical Field
The present invention relates to a flow control valve that controls the flow rate of a flowing fluid.
Background
Conventionally, in various fluid circuits, a flow rate control valve for controlling a flow rate of a fluid flowing through the fluid circuit is used. For example, in a working machine such as a construction vehicle driven by hydraulic pressure, a flow rate control valve for controlling the flow rate of oil flowing through a hydraulic circuit is used in the hydraulic circuit for supplying hydraulic oil to each hydraulic actuator of the working machine and in the hydraulic circuit for supplying pilot pressure for operating a hydraulic device such as a directional valve.
JP2010-144928A discloses an electro-hydraulic pilot valve including an electromagnetic actuator, a pilot body, and a pilot poppet. In this electrohydraulic pilot valve, the internal pressure of the 1 st control chamber communicates with the pilot control chamber via a control path provided in the pilot poppet. At this time, the tip of the pilot body closes a pilot passage provided in the pilot piston to block the flow of the liquid between the pilot control chamber and the outlet. The closed pressure presses the pilot poppet against the pilot poppet valve seat. Thus, the flow between the inlet and the outlet of the electro-hydraulic pilot valve is blocked. When the electromagnetic actuator is energized, the pilot body moves upward to open the pilot passage, and the pressure in the pilot control chamber is released to the release path. When the opening between the pilot control chamber and the pilot passage reaches a predetermined size, the pilot poppet moves following the pilot conductor. The movement of the conductor returns the tip of the leading conductor to the leading path, and reduces the flow passing through the leading path. When the flow of the pilot passage becomes balanced, the pilot poppet stops its movement and maintains the open position.
According to such electrohydraulic pilot valve, have following advantage: the current applied to the electromagnetic actuator can be selectively controlled to proportionally control the flow of fluid through the electro-hydraulic pilot valve.
However, in the control valve disclosed in JP2010-144928A, the pilot conductor receives the pressure in the pilot control chamber, that is, the internal pressure of the 1 st control chamber communicated via the control passage, at the tip end thereof. Since the internal pressure of the 1 st control chamber is high, a large force is required to move the pilot body against the internal pressure of the 1 st control chamber. Therefore, as an electromagnetic actuator for generating a driving force for driving the lead conductor, it is necessary to use an electromagnetic actuator capable of generating a large driving force. In this case, there are problems as follows: the electro-hydraulic pilot valve is large in size and high in cost.
Disclosure of Invention
The present invention has been made in view of such a point, and an object thereof is to provide a flow rate control valve which can be operated with a relatively small force.
The flow control valve of the present invention includes:
a spool receiving block having a spool receiving hole; and
a spool having: a spool body portion; a spool large-diameter portion having a diameter larger than that of the spool main body portion; and a flow path that is open at one end side in the axial direction and communicates with a chamber that is located between a portion of the spool main body portion that is located closer to the other end side in the axial direction than the spool large-diameter portion and the spool housing block, the spool being movably housed in the spool housing hole.
In the flow control valve of the present invention, it is also possible,
the spool body portion has an end face at the one end,
the spool large diameter portion has an acting surface facing the other end side,
the area of the one end surface is the same as that of the action surface.
In the flow control valve of the present invention, it is also possible,
the spool large diameter portion is located at an intermediate portion of the spool away from the one end and the other end.
In the flow control valve of the present invention, it is also possible,
the spool large diameter portion has another acting surface facing the one end side,
the spool has another flow path that opens to the other end side of the spool and communicates with another chamber located between the spool housing block and a portion of the spool body that is closer to the one end side than the spool large diameter portion.
In the flow control valve of the present invention, it is also possible,
the spool moves in the spool receiving hole by a driving force of a solenoid.
The flow control valve of the present invention includes:
a spool receiving block having a spool receiving hole;
and a spool having: a spool main body portion having an end surface located at one end in an axial direction; a spool large diameter portion having a diameter larger than that of the spool body portion, located in an intermediate portion of the spool body portion that is located away from the one end and the other end in the axial direction, and having an acting surface facing the other end side and another acting surface facing the one end side, the area of the one end surface being the same as the area of the acting surface; a flow path that opens to the one end side and communicates with a chamber between a portion of the spool main body portion on the other end side of the spool large diameter portion and the spool housing block; and another flow path that is open on the other end side and communicates with another chamber that is located between a portion of the spool main body portion on the one end side with respect to the spool large diameter portion and the spool housing block, the spool being movable in the spool housing hole by a driving force of a solenoid.
The flow control valve of the present invention includes:
a spool having: a spool main body portion that is disposed so as to be movable to one side and the other side along an axial direction; and a spool large diameter portion having a diameter larger than a diameter of the spool main body portion;
a pressure chamber, at least a part of which is defined by an end portion of the spool body portion on the one side, for generating a pressing force for pressing the spool body portion from the one side toward the other side;
a chamber, at least a part of which is defined by a portion of the spool main body portion located closer to the other end side than the spool large-diameter portion, and which generates another pressing force that presses the spool large-diameter portion from the other end toward the one end to cancel at least a part of the pressing force by the pressure chamber; and
and a pressure chamber connection passage capable of controlling a flow rate of the oil from the pressure chamber to a control passage whose flow rate is to be controlled when the spool main body portion is moved from the other side to the one side by a driving force of the solenoid.
ADVANTAGEOUS EFFECTS OF INVENTION
According to the present invention, it is possible to provide a flow rate control valve that can be operated with a relatively small force.
Drawings
Fig. 1 is a diagram for explaining an embodiment of the present invention, and is a cross-sectional view showing a flow rate control valve in a state of being attached to a member to be attached.
Fig. 2 is an enlarged view of a portion denoted by II in fig. 1, and shows the flow rate control valve in a closed state.
Fig. 3 is a view corresponding to fig. 2, showing the flow rate control valve in a flow-through state.
Fig. 4 is a longitudinal sectional view showing a spool of the flow control valve.
Fig. 5 is a longitudinal sectional view showing a section of the spool orthogonal to the section shown in fig. 4.
Fig. 6 is a sectional view corresponding to line VI-VI of fig. 4.
Fig. 7 is a sectional view corresponding to line VII-VII of fig. 4.
Description of the reference numerals
10. A flow control valve; 12. a spool pressing spring; 14. a poppet valve pressing spring; 16. a gap; 20. a housing; 21. an accommodating hole; 22. a pressure source port; 23. a control port; 25. a seat portion; 30. a spool accommodating block; 30a, block 1; 30b, block 2; 31. a spool receiving bore; 40. a spool; 41. an end face; 44. the other end face; 46. a spool body portion; 47. an outer peripheral groove (pressure chamber connection flow path); 48. a notch (pressure chamber connection flow path); 50. a spool large diameter portion; 50a, the 1 st acting surface (acting surface); 50b, the 2 nd action surface (the other action surface); 51. 1 st connection channel (flow path); 55. the 2 nd connecting channel (the other channel); 60. a poppet valve; 61. a main body; 63. placing the noodles; 68. a throttle section; 69. a notch portion; 70. a ball; 71. a support member; 80. a drive device; 82. a drive rod; 84. a drive section; 90. an installed member; 91. a main body portion; 92. a flow control valve mounting hole; 95. a pressure source flow path; 96. a control flow path; 97. a discharge flow path; A. a central axis; c1, chamber 1 (chamber); c2, chamber 2 (the other chamber); c3, chamber 3; cp, a pressure chamber; cr, rod chamber.
Detailed Description
Hereinafter, an embodiment of the present invention will be described with reference to the drawings. In the drawings attached to the present specification, the scale, the vertical and horizontal size ratios, and the like are appropriately changed and exaggerated relative to the actual ones for the convenience of illustration and easy understanding.
In addition, terms such as "parallel", "orthogonal" and "the same", lengths, angles, and the like used in the present specification, conditions of shape and geometry, and terms for determining the degrees thereof are not limited to strict meanings, and are interpreted to include ranges of degrees to which the same functions can be expected.
Fig. 1 to 7 are diagrams for explaining an embodiment of the present invention. Fig. 1 is a sectional view showing the flow rate control valve 10 in a state attached to an attached member 90, and fig. 2 and 3 are enlarged views showing a portion denoted by II in fig. 1. In fig. 2, the flow control valve 10 is shown in a closed state, and in fig. 3, the flow control valve 10 is shown in a flow-through state.
The mounted member 90 is a member to which the flow rate control valve 10 is mounted. The body 91 of the attached member 90 is provided with a flow rate control valve attachment hole 92 to which the flow rate control valve 10 is attached. The flow control valve mounting hole 92 extends along the axial direction da, and has a substantially circular shape in a cross section orthogonal to the axial direction da. The flow rate control valve mounting hole 92 has a 1 st inner peripheral groove 93 and a 2 nd inner peripheral groove 94 in this order from the tip side (one side) of the flow rate control valve mounting hole 92. The 1 st inner circumferential groove 93 and the 2 nd inner circumferential groove 94 are formed annularly along the circumferential direction of the flow control valve mounting hole 92, respectively. In the example shown in fig. 1, the main body 91 is provided with a pressure source flow path 95 communicating with the tip end portion of the flow rate control valve mounting hole 92, a control flow path 96 communicating with the 1 st inner circumferential groove 93, and a drain flow path 97 communicating with the 2 nd inner circumferential groove 94. The pressure source flow path 95 communicates with a pressure source, not shown, and the control flow path 96 communicates with a hydraulic device, not shown. In a state where the flow rate control valve 10 is attached to the flow rate control valve attachment hole 92, the flow rate of the fluid, particularly the oil, flowing from the pressure source flow path 95 to the control flow path 96 is controlled by the flow rate control valve 10. The drain passage 97 communicates with a tank, not shown, and the oil that has flowed into the drain passage 97 is discharged to the tank.
The flow rate control valve 10 includes: a spool receiving block 30 having a spool receiving hole 31; and a spool 40 movably housed in the spool housing block 30. The flow rate control valve 10 of the present embodiment further includes: a housing 20 having a housing hole 21; a poppet 60 housed in the housing 20; and a spool pressing spring 12 and a poppet pressing spring 14.
In the present specification, the "axial direction (da)" refers to a direction in which the central axis a of the spool 40 extends (the longitudinal direction of the spool 40). Further, the distal end side (the side communicating with the pressure source flow path 95, the lower side in fig. 1 to 5) of the flow rate control valve 10 along the axial direction da is referred to as "one side", and the proximal end side (the side communicating with the driving device 80, the upper side in fig. 1 to 5) of the flow rate control valve 10 along the axial direction da is referred to as "the other side".
The housing 20 has a housing hole 21 that houses at least a part of the spool housing block 30, the spool 40, the poppet 60, the spool pressing spring 12, and the poppet pressing spring 14. The housing 20 has a pressure source port 22 communicating with the pressure source flow path 95 and a control port 23 communicating with the control flow path 96 in a state where the flow control valve 10 is attached to the flow control valve attachment hole 92. The pressure source port 22 extends from a tip end portion (one side end portion) of the housing hole 21 in the axial direction da. The control flow path 96 extends from the side surface of the housing hole 21 in the radial direction orthogonal to the axial direction da. In the illustrated example, the housing 20 has a plurality of control ports 23 arranged in a circumferential direction about the central axis a of the spool 40. The housing hole 21 has an inner circumferential groove 24 communicating with the control port 23. The inner circumferential groove 24 is formed annularly along the circumferential direction of the housing hole 21. A seat portion 25 on which the seating surface 63 of the poppet 60 is seated is provided in an opening portion of the pressure source port 22 on the side (the other side) of the housing hole 21. In the illustrated example, the seat 25 is located at the connection between the pressure source port 22 and the inner circumferential groove 24. The seat portion 25 is formed of a surface extending in a direction inclined to both the axial direction and the radial direction, and is formed in a ring shape along the circumferential direction of the housing hole 21. The housing 20 has a 1 st through hole 26 and a 2 nd through hole 27 which communicate the housing hole 21 with the outer surface of the housing 20. The 1 st through hole 26 communicates the housing hole 21 and the inner circumferential groove 24 via the gap 16 formed between the inner surface of the flow rate control valve mounting hole 92 and the outer surface of the housing 20. The 2 nd through hole 27 is located on the other side of the 1 st through hole 26, and communicates the accommodating hole 21 with the 2 nd inner circumferential groove 94.
The spool receiving block 30 has a spool receiving hole 31 extending in the axial direction to receive the spool 40. The spool receiving hole 31 penetrates the spool receiving block 30 in the axial direction da. A spring receiving surface 32 is formed at one end of the spool receiving block 30. The spring support surface 32 supports the poppet pressing spring 14 and receives the pressing force from the poppet pressing spring 14. In the illustrated example, the spool housing block 30 is composed of a 1 st block 30a and a 2 nd block 30b positioned on the other side of the 1 st block 30 a. The spool receiving hole 31 is provided across the 1 st block 30a and the 2 nd block 30 b. In the illustrated example, the spool accommodating hole 31 is formed by a 1 st small-diameter hole 31a and a large-diameter hole 31b provided to the 1 st block 30a, and a 2 nd small-diameter hole 31c provided to the 2 nd block 30 b. The 1 st, large, and 2 nd small-diameter holes 31a, 31b, and 31c extend in the axial direction, and the center axes of the 1 st, large, and 2 nd small-diameter holes 31a, 31b, and 31c coincide with each other. The center axes of the 1 st, large, and 2 nd small-diameter holes 31a, 31b, and 31c coincide with the center axis a of the spool 40. The 1 st, large, and 2 nd small-diameter holes 31a, 31b, and 31c each have a circular shape in a cross section orthogonal to the central axis. The 1 st small-diameter hole 31a is located on the side of the large-diameter hole 31b and has a diameter smaller than that of the large-diameter hole 31 b. The 2 nd small-diameter hole 31c is located on the other side of the large-diameter hole 31b and has a diameter smaller than that of the large-diameter hole 31 b. The magnitude relation between the diameter of the 1 st small-diameter hole 31a and the diameter of the 2 nd small-diameter hole 31c is not particularly limited, and in the illustrated example, the diameter of the 1 st small-diameter hole 31a is equal to the diameter of the 2 nd small-diameter hole 31 c. The 1 st and 2 nd small-diameter holes 31a and 31c have a diameter corresponding to the diameter of the spool main body portion 46 of the spool 40, and the large-diameter hole 31b has a diameter corresponding to the diameter of the spool large-diameter portion 50 of the spool 40.
The 1 st small-diameter hole 31a is provided with a 1 st inner circumferential groove 33. Further, a 2 nd inner circumferential groove 35 is provided between the 1 st small-diameter hole 31a and the large-diameter hole 31 b. The 1 st inner circumferential groove 33 and the 2 nd inner circumferential groove 35 are each formed in an annular shape along the circumferential direction of the spool accommodating hole 31. On the outer surface of the spool accommodating hole 31, a 1 st outer circumferential groove 36 communicating with the 1 st through hole 26 of the housing 20 and a 2 nd outer circumferential groove 37 communicating with the 2 nd through hole 27 of the housing 20 are provided. The spool housing block 30 (the 1 st block 30a) includes: a 1 st through hole 38 extending in the radial direction and communicating the 1 st inner circumferential groove 33 with the 1 st outer circumferential groove 36; and a 2 nd through hole 39 extending in the radial direction and communicating the 2 nd inner circumferential groove 35 with the 2 nd outer circumferential groove 37. In the illustrated example, the spool housing block 30 (the 1 st block 30a) has a plurality of 1 st through holes 38 and a plurality of 2 nd through holes 39 arranged in the circumferential direction.
In a state where the flow rate control valve 10 is mounted in the flow rate control valve mounting hole 92 of the mounting member 90, the housing 20 is fixed to the flow rate control valve mounting hole 92 by screwing or the like, and the spool housing block 30 is fixed to the housing 20 by screwing or the like. Therefore, in a state where the flow rate control valve 10 is attached to the flow rate control valve attachment hole 92 of the attached member 90, the housing 20 and the spool receiving block 30 do not move relative to the attached member 90.
Fig. 4 is a vertical sectional view showing the spool 40, and fig. 5 is a vertical sectional view showing a section of the spool 40 perpendicular to the section shown in fig. 4. The spool 40 has a central axis a extending in the longitudinal direction, and is accommodated in the spool accommodation hole 31 of the spool accommodation block 30 so as to be movable in the axial direction da. The central axis a of the spool 40 extends in the axial direction da. The spool 40 has one end surface 41 at one end (one-side end portion) along the axial direction da and the other end surface 44 at the other end (the other-side end portion). That is, the one end surface 41 is a surface of the spool 40 facing one side, and the other end surface 44 is a surface of the spool 40 facing the other side. One end surface 41 includes a projecting surface 42 projecting toward one side and a spring bearing surface 43 located around the projecting surface 42. The spring support surface 43 supports the spool pressing spring 12 and receives a pressing force from the spool pressing spring 12. The other end surface 44 has a notched portion 45 that communicates with a 2 nd connection flow path 55 discussed later. The notch portion 45 is provided so that the drive lever 82 does not close the opening of the 2 nd connection flow path 55 when the drive lever 82 of the drive device 80, which will be described later, abuts against the other end surface 44.
The spool 40 has: a spool main body portion 46; and a spool large diameter portion 50 having a diameter larger than the diameter of the spool main body portion 46. In the illustrated example, the spool large diameter portion 50 is located at an intermediate portion between one end and the other end away from the spool 40. The spool main body portion 46 has an outer peripheral groove 47 located on one side of the spool large diameter portion 50. The outer peripheral groove 47 is formed annularly along the circumferential direction of the spool main body portion 46. A cutout 48 is formed at one end of the outer circumferential groove 47 along the axial direction da, with the spool main body portion 46 partially removed. In the present specification, one end of the spool 40 is referred to as "one end", and the other end is referred to as "the other end". Meanwhile, one side of the spool 40 is sometimes referred to as "one end side" and the other side is sometimes referred to as "the other end side".
The spool large diameter portion 50 has a 1 st acting surface (acting surface) 50a facing the other end side and a 2 nd acting surface (the other acting surface) 50b facing the one end side. The 1 st acting surface 50a connects the other end side edge portion of the outer surface of the spool large diameter portion 50 extending in the axial direction da and the outer surface of the spool main body portion 46 at the portion closer to the other end side than the spool large diameter portion 50. The 2 nd acting surface 50b connects one end side edge portion of the outer surface of the spool large diameter portion 50 extending in the axial direction da and the outer surface of the spool main body portion 46 at a portion on the one end side of the spool large diameter portion 50. In the illustrated example, the area of one end surface 41 of the spool 40 and the area of the 1 st acting surface 50a are the same as each other. In addition, the area of the other end surface 44 of the spool 40 and the area of the 2 nd acting surface 50b are the same as each other. Here, the areas of the one end surface 41, the other end surface 44, the 1 st acting surface 50a, and the 2 nd acting surface 50b are the areas on a plane orthogonal to the central axis a (the axial direction da) when the surfaces 41, 44, 50a, and 50b are projected along the axial direction da.
The spool large-diameter portion 50 is disposed in the large-diameter hole 31b of the spool housing hole 31. The 1 st and 2 nd small diameter holes 31a and 31c of the spool receiving hole 31 have a smaller diameter than the spool large diameter portion 50. Thus, the spool large-diameter portion 50 is movable in the axial direction da over the entire range within the large-diameter hole 31b and within the 2 nd inner circumferential groove 35. More specifically, the spool 40 is movable in the axial direction da from a position where the 1 st acting surface 50a of the spool large diameter portion 50 contacts the other end portion of the large diameter hole 31b to a position where the 2 nd acting surface 50b of the spool large diameter portion 50 contacts one end portion of the 2 nd inner circumferential groove 35.
In the example shown in fig. 1 to 3, 3 spaces (the 1 st chamber C1, the 2 nd chamber C2, and the 3 rd chamber C3) are formed between the spool 40 and the spool housing block 30. The 1 st chamber (chamber) C1 is located between the spool housing block 30 and a portion of the spool main body portion 46 on the other end side of the spool large diameter portion 50. In the illustrated example, the 1 st acting surface 50a of the spool large diameter portion 50 faces the 1 st chamber C1. In this case, the 1 st chamber C1 is defined by the portion of the spool main body portion 46 on the other end side of the spool large diameter portion 50, the 1 st acting surface 50a, and the spool receiving hole 31 of the spool receiving block 30. The 2 nd chamber (the other chamber) C2 is located between the spool housing block 30 and a portion of the spool main body portion 46 on the one end side of the spool large diameter portion 50. In the illustrated example, the 2 nd acting surface 50b of the spool large diameter portion 50 faces the 2 nd chamber C2. In this case, the 2 nd chamber C2 is defined by the portion of the spool main body portion 46 on the other end side of the spool large diameter portion 50, the 2 nd acting surface 50b, and the spool receiving hole 31 of the spool receiving block 30. In particular, in the illustrated example, the portion of the spool accommodating hole 31 that defines the 2 nd chamber C2 includes the 2 nd inner circumferential groove 35. The 3 rd chamber C3 is located between the spool accommodating block 30 and a portion of the spool main body portion 46 on the one end side of the spool large diameter portion 50 on the 2 nd chamber C2 side (one end side). In particular, in the illustrated example, the portion of the spool body portion 46 that defines the 3 rd chamber C3 includes the outer circumferential groove 47, and the portion of the spool receiving hole 31 that defines the 3 rd chamber C3 includes the 1 st inner circumferential groove 33.
The spool 40 has a 1 st connection flow path (flow path) 51, and the 1 st connection flow path (flow path) 51 opens at one end side in the axial direction da and communicates with the 1 st chamber C1. In the illustrated example, the 1 st connection channel 51 is open at one end surface 41 on one end side of the spool 40. In particular, the 1 st connection channel 51 opens at the projection surface 42 of the one end surface 41. The 1 st connection flow path 51 includes a 1 st connection hole 52 located inside the spool 40 and a 1 st connection groove 53 formed in an outer surface of the spool large diameter portion 50. The 1 st connecting hole 52 includes: an axial direction portion 52a, which is open at one end side of the spool 40, extending along the center axis a; and a radial portion 52b that communicates with the other-end side end portion of the axial direction portion 52a and extends in the radial direction of the spool 40. The 1 st connecting groove 53 communicates with a radially outer portion of the radial portion 52b of the 1 st connecting hole 52, and extends in the axial direction da. In the illustrated example, the radial portion 52b of the 1 st connecting hole 52 penetrates the spool large-diameter portion 50 through the other end side end portion of the axial direction portion 52 a. In other words, the radial portion 52b extends from the other-end side end portion of the axial direction portion 52a toward the opposite direction at an angle of 180 degrees from each other. And, the 1 st coupling groove 53 is connected to both end portions of the radial portion 52b, respectively. That is, the spool 40 has two 1 st connecting grooves 53 located on opposite sides from each other with respect to the center axis a. Further, without being limited thereto, the spool 40 may have 1 st connection groove 53, or may have 3 or more 1 st connection grooves 53.
The spool 40 has a 2 nd connection flow path (another flow path) 55, and the 2 nd connection flow path (another flow path) 55 opens on the other end side in the axial direction da and communicates with the 2 nd chamber C2. In the illustrated example, the 2 nd connection channel 55 opens at the other end side of the spool 40 at the other end surface 44. The 2 nd connection flow path 55 includes a 2 nd connection hole 56 located inside the spool 40 and a 2 nd connection groove 57 formed at an outer surface of the spool large diameter portion 50. The 2 nd connecting hole 56 includes: an axial direction portion 56a that is open at the other end side of the spool 40 and extends along the center axis a; and a radial portion 56b that communicates with one end side end portion of the axial direction portion 56a and extends in the radial direction of the spool 40. The 2 nd connecting groove 57 communicates with a radially outer portion of the radial portion 56b of the 2 nd connecting hole 56, and extends in the axial direction da. In the illustrated example, the radial portion 56b of the 2 nd connecting hole 56 penetrates the spool large-diameter portion 50 through one end side end portion of the axial portion 56 a. In other words, the radial portion 56b extends from one end side end portion of the axial direction portion 56a toward opposite directions at an angle of 180 degrees from each other. And, the 2 nd coupling grooves 57 are respectively coupled to both end portions of the radial portion 56 b. That is, the spool 40 has two 2 nd connecting grooves 57 located on opposite sides from each other with respect to the center axis a. Further, without being limited thereto, the spool 40 may have 12 nd connecting groove 57, or may have 3 or more 2 nd connecting grooves 57.
Fig. 6 is a sectional view corresponding to the line VI-VI of fig. 4, and fig. 7 is a sectional view corresponding to the line VII-VII of fig. 4. In the illustrated example, the radial portion 52b of the 1 st connecting hole 52 and the radial portion 56b of the 2 nd connecting hole 56 extend orthogonally to each other when viewed in the axial direction da. Thus, the 1 st coupling groove 53 and the 2 nd coupling groove 57 have an angle of 90 degrees in the circumferential direction of the spool 40 and are separated from each other. Therefore, the 1 st connection channel 51 and the 2 nd connection channel 55 form mutually independent channels.
The poppet valve 60 is disposed movably in the axial direction da in the housing hole 21 of the housing 20. The poppet valve 60 includes: a body 61 that closes and opens the pressure source port 22 of the housing 20; and a ball 70 and a support member 71 housed in the main body 61. The main body 61 has a small diameter portion 61a located inside the pressure source port 22 in the closed state of the pressure source port 22, and a large diameter portion 61b located on the other side of the small diameter portion 61 a. The main body 61 has a distal end surface 62 located at one end of the small diameter portion 61 a. A seating surface 63 that seats on the seat portion 25 of the housing 20 in a closed state is formed on a portion of the outer surface of the main body 61 between the small diameter portion 61a and the large diameter portion 61 b. The seating surface 63 is a surface extending in a direction inclined with respect to both the axial direction and the radial direction, and is formed in an annular shape along the circumferential direction of the poppet valve 60.
A spring receiving hole 64 is provided in the large diameter portion 61b, and the spring receiving hole 64 opens on the other side of the poppet 60 and receives at least a part of the spool pressing spring 12 and at least a part of the poppet pressing spring 14. A spring receiving surface 64a is formed at one end of the spring receiving hole 64. The spring support surface 64a supports the poppet pressing spring 14 and receives the pressing force from the poppet pressing spring 14.
The main body 61 further has a support member accommodating hole 65, a ball accommodating hole 66, a connection hole 67, and a throttle portion 68. The support member accommodating hole 65 opens to the spring accommodating hole 64 on the other side, and accommodates the support member 71. The ball receiving hole 66 opens to the support member receiving hole 65 on the other side, and receives the ball 70. The connection hole 67 opens to the support member accommodating hole 65 on the other side, and communicates with the throttle portion 68 on one side. The throttle portion 68 opens at the other side to the connection hole 67 and at the one side to the top end surface 62. A notch 69 is formed radially outward of the distal end surface 62.
The support member 71 includes: a protruding surface 72 protruding toward the other side from the other side; and a spring bearing surface 73 located around the projection surface 72. The spring support surface 73 supports the spool-pressing spring 12 and receives the pressing force from the spool-pressing spring 12. The support member 71 further has a through hole 74 extending along the central axis a and a notch portion 75 communicating with the through hole 74. The through hole 74 extends along the center axis a and opens to the protruding surface 72 on the other side of the support member 71. The notch 75 is formed of a groove-like notch provided on one side of the support member 71 and extending in the radial direction of the support member 71. The notch 75 communicates with the through hole 74 on the radially inner side and communicates with the outer surface of the support member 71 on the radially outer side. Further, the notch portion 75 may not communicate with the outer surface of the support member 71 radially outward. The notch 75 is not particularly limited as long as the through hole 74 is not completely closed by the ball 70 even when the ball 70 comes into contact with the through hole 74 of the support member 71, and the ball receiving hole 66 and the through hole 74 communicate with each other through the notch 75.
The orifice 68 functions as an orifice that restricts the flow rate per unit time of the oil flowing from the pressure source port 22 of the casing 20 toward the connection hole 67. Therefore, the sectional area of the throttle portion 68 is much smaller than that of the connection hole 67.
The ball 70 is accommodated in the ball accommodation hole 66 so as to be movable in the ball accommodation hole 66. The diameter of the ball 70 is smaller than the diameter of the ball receiving hole 66 and larger than the diameter of the connection hole 67. Thus, the entirety of the ball 70 does not enter the connection hole 67. Thereby, the ball 70 functions as a check valve in cooperation with the connection hole 67. Specifically, the ball 70 allows the oil to flow from the connection hole 67 toward the ball receiving hole 66. On the other hand, when the oil is about to flow from the ball housing hole 66 toward the connection hole 67, the ball 70 closes the opening portion on the other side of the connection hole 67. Thus, the oil is not allowed to flow from the ball receiving hole 66 toward the connection hole 67.
A spool pressing spring 12 is disposed between the spool 40 and the poppet 60. In the illustrated example, the spool pressing spring 12 is disposed in a compressed state between the spring support surface 43 of the spool 40 and the spring support surface 73 of the support member 71 of the poppet valve 60. Therefore, the pressing forces from the spool pressing spring 12 act on the spring support surfaces 43 and 73, respectively.
A poppet pressing spring 14 is disposed between the spool housing block 30 and the poppet 60. In the illustrated example, the poppet pressing spring 14 is disposed in a compressed state between the spring support surface 32 of the spool housing block 30 and the spring support surface 64a of the poppet 60. Therefore, the pressing forces from the poppet-valve pressing spring 14 act on the spring support surfaces 32 and 64a, respectively.
A pressure chamber Cp is formed between the spool housing block 30 and the poppet 60. The oil flows from the pressure source flow path 95 of the attached member 90 into the pressure chamber Cp via the pressure source port 22 of the housing 20, the throttle portion 68 of the poppet 60, the connection hole 67, the ball housing hole 66, the support member housing hole, and the spring housing hole 64.
Sealing members 18 such as O-rings for preventing leakage of oil are disposed between the flow rate control valve mounting hole 92 of the mounted member 90 and the outer surface of the housing 20, and between the housing hole 21 of the housing 20 and the outer surface of the spool housing block 30, respectively.
The movement of the spool 40 in the axial direction da is controlled by the drive device 80. The driving device 80 has a driving rod 82 and a driving portion 84. In the illustrated example, the driving portion 84 drives the driving lever 82 toward one side in the axial direction da by a driving force generated by a solenoid. The drive rod 82 abuts the other end surface 44 of the spool 40 to move the spool 40 in the axial direction da. That is, in the illustrated example, the spool 40 moves in the spool accommodating hole 31 in the axial direction da by the driving force of the solenoid. The drive unit 84 may be configured to drive the drive lever 82 by another drive force such as a pilot pressure. A rod chamber Cr surrounded by the driving device 80 and the flow rate control valve 10 is formed in a joint portion where the driving device 80 and the flow rate control valve 10 are joined. In the illustrated example, the rod chamber Cr is defined by the drive device 80 and the spool housing block 30 (2 nd block 30 b). The drive rod 82 of the drive device 80 and the other end portion (the other end surface 44) of the spool 40 are disposed in the rod chamber Cr.
Next, the operation of the flow rate control valve 10 according to the present embodiment will be described with reference to fig. 2 and 3.
As shown in fig. 2, when the drive lever 82 of the drive device 80 is retracted to the maximum extent, that is, when the drive lever 82 is located at the position closest to the other side, the spool 40 is located at the position closest to the other side (retracted position) by the urging force of the spool urging spring 12. Specifically, the spool 40 is positioned at the retracted position by the pressing force of the spool pressing spring 12 acting on the spring support surface 43 of the spool 40. At this time, the other end surface 44 of the spool 40 contacts the drive rod 82 of the drive device 80.
At this time, the 2 nd chamber C2 formed between the spool 40 and the spool housing block 30 communicates with the drain flow path 97 via the 2 nd through hole 39 of the spool housing block 30, the 2 nd outer circumferential groove 37, the 2 nd through hole 27 of the housing 20, and the 2 nd inner circumferential groove 94 of the attached member 90. The 3 rd chamber C3 communicates with the control flow path 96 via the 1 st through hole 38 of the spool housing block 30, the 1 st outer circumferential groove 36, the 1 st through hole 26 of the housing 20, the gap 16 formed between the inner surface of the flow control valve mounting hole 92 and the outer surface of the housing 20, and the 1 st inner circumferential groove 93 of the attached member 90. The spool 40 closes between the pressure chamber Cp and the 3 rd chamber C3.
The oil flows into the pressure chamber Cp from the pressure source flow path 95 of the attached member 90 through the pressure source port 22 of the housing 20, the throttle portion 68 of the poppet 60, the connection hole 67, the ball housing hole 66, the support member housing hole, and the spring housing hole 64. The throttle portion 68 restricts the flow rate per unit time of the oil flowing from the pressure source port 22 toward the connection hole 67. Therefore, when a high hydraulic pressure acts on the pressure source passage 95, the same hydraulic pressure as that of the pressure source passage 95 acts on the pressure chamber Cp even after a certain time has elapsed.
A pressing force that presses the poppet valve 60 toward one side by the pressure in the pressure chamber Cp acts on the surface (the other side surface) of the large diameter portion 61b of the poppet valve 60 that faces the other side. Further, a pressing force that presses the poppet valve 60 toward the other side by the pressure in the pressure source flow path 95 acts on a surface (one side surface) of the small diameter portion 61a that faces one side. The area of the other side surface of the large diameter portion 61b is equal to the area on a plane orthogonal to the central axis a (axial direction da) when the large diameter portion 61b is projected along the axial direction da. The area of one side surface of the small diameter portion 61a is equal to the area on a plane orthogonal to the central axis a (axial direction da) when the small diameter portion 61a is projected along the axial direction da. In the illustrated example, the other side surface of the large diameter portion 61b has a larger area than one side surface of the small diameter portion 61 a. Therefore, the pressing force acting on the other side surface of the large diameter portion 61b to press the poppet valve 60 to one side is larger than the pressing force acting on the one side surface of the small diameter portion 61a to press the poppet valve 60 to the other side. Further, the poppet valve 60 receives a pressing force for pressing the poppet valve 60 to one side from the poppet valve pressing spring 14 via the spring support surface 73 of the support member 71. Thus, the poppet valve 60 is pressed against the seat portion 25 of the housing 20 by the difference between the pressing force pressing the poppet valve 60 to one side by the pressure in the pressure chamber Cp and the pressing force pressing the poppet valve 60 to the other side by the pressure in the pressure source flow passage 95 and the pressing force received from the poppet valve pressing spring 14. More specifically, the seating surface 63 of the poppet 60 is pressed against the seat 25 of the housing 20. At this time, as shown in fig. 2, the poppet valve 60 is positioned at the most side (closed position), and the flow rate control valve 10 is in a closed state in which the flow path communicating from the pressure source flow path 95 to the control flow path 96 is closed.
Next, an operation for making the flow rate control valve 10 transit from the closed state to the flow state will be described. When the drive portion 84 of the drive device 80 is driven to move the drive lever 82 toward one side in the axial direction da, the spool 40 is pressed by the drive lever 82 and also moves toward one side (advanced position) in the axial direction da. In the present embodiment, the driving portion 84 includes an electromagnetic actuator, and the driving lever 82 is moved toward one side by a driving force generated by the electromagnetic actuator.
A pressing force toward the other side is generated on the spool 40 via the one end surface 41 by the pressure acting in the pressure chamber Cp. The spool 40 has a 1 st connection flow path (flow path) 51, and the 1 st connection flow path (flow path) 51 is open at one end surface 41 and communicates with a 1 st chamber (chamber) C1. Further, the 1 st acting surface (acting surface) 50a of the spool large diameter portion 50 of the spool 40 faces the 1 st chamber C1. Thereby, the same pressure as the pressure acting on the one end surface 41 of the spool 40 acts on the 1 st acting surface 50 a. That is, a pressing force toward one side is generated on the spool 40 via the 1 st acting surface 50a by the pressure acting on the 1 st chamber C1. Therefore, the pressing force toward one side generated on the spool 40 by the 1 st acting surface 50a cancels (cancels) at least a part of the pressing force toward the other side by the one end surface 41. This can effectively reduce the pressing force of the spool 40 to the other side due to the pressure in the pressure chamber Cp, and can reduce the driving force required by the driving device 80. Therefore, the size of the driving device 80 can be reduced, and the cost of the driving device 80 can be reduced.
In particular, in the flow rate control valve 10 of the present embodiment, the area of the one end surface 41 and the area of the 1 st acting surface 50a are the same as each other. In this case, the pressing force toward the other side by the one end surface 41 and the pressing force toward the one side by the 1 st acting surface 50a cancel each other out. Therefore, only the pressing force of the spool pressing spring 12 becomes a pressing force that presses the spool 40 toward the other side. That is, the drive device 80 can move the spool 40 toward the advanced position only by pressing the spool 40 against the pressing force of the spool pressing spring 12. In this case, the driving force required for the driving device 80 can be further reduced. Therefore, the size of the driving device 80 can be further reduced, and the cost of the driving device 80 can be further reduced.
Further, the volume in the rod chamber Cr varies with the movement of the drive rod 82 of the drive device 80 and the spool 40, and a positive or negative pressure can be generated in the oil held in the rod chamber Cr. A pressing force toward one side or the other side is generated on the spool 40 via the other end surface 44 by the pressure acting in the rod chamber Cr. The spool 40 has a 2 nd connection flow path (another flow path) 55, and the 2 nd connection flow path (another flow path) 55 is open at the other end surface 44 and communicates with a 2 nd chamber (another chamber) C2. Further, the 2 nd acting surface (the other acting surface) 50b of the spool large diameter portion 50 of the spool 40 faces the 2 nd chamber C2. Thereby, the same pressure as the pressure acting on the other end surface 44 of the spool 40 acts on the 2 nd acting surface 50 b. That is, a pressing force toward the other side or the one side is generated on the spool 40 via the 2 nd acting surface 50b by the pressure acting on the 2 nd chamber C2. Therefore, the pressing force toward the other side or the one side generated by the 2 nd acting surface 50b on the spool 40 cancels (cancels) at least a part of the pressing force toward the one side or the other side by the other end surface 44. This effectively reduces the pressing force acting on the spool 40 due to the pressure in the rod chamber Cr, and the spool 40 can be operated stably.
In particular, in the flow rate control valve 10 of the present embodiment, the area of the other end surface 44 and the area of the 2 nd acting surface 50b are the same as each other. In this case, the pressing force toward one side by the other end surface 44 and the pressing force toward the other side by the 2 nd acting surface 50b cancel each other out. Therefore, the spool 40 can be operated more stably.
In the flow rate control valve 10 of the present embodiment, the 2 nd chamber C2 is always in communication with the drain flow path 97 via the 2 nd through hole 39 of the spool housing block 30, the 2 nd outer circumferential groove 37, the 2 nd through hole 27 of the housing 20, and the 2 nd inner circumferential groove 94 of the attached member 90. Thus, the oil held in the rod chamber Cr and the 2 nd chamber C2 is discharged to the drain passage 97, and the hydraulic pressure does not act on the rod chamber Cr and the 2 nd chamber C2. Therefore, the spool 40 can be operated more stably.
When the spool 40 moves toward the advanced position, the notch portion 48 continuously provided to the outer circumferential groove 47 of the spool 40 communicates with the pressure chamber Cp. Thereby, the pressure chamber Cp and the 3 rd chamber C3 communicate via the notch portion 48. As described above, the 3 rd chamber C3 is always in communication with the control flow passage 96. That is, when the spool 40 moves toward the advanced position, the pressure chamber Cp and the control flow passage 96 communicate with each other via the 3 rd chamber C3. When the pressure chamber Cp communicates with the control flow passage 96, the oil in the pressure chamber Cp flows into the control flow passage 96, and the pressure in the pressure chamber Cp rapidly decreases. Therefore, in the present embodiment, the outer peripheral groove 47 and the cutout portion 48 constitute a pressure chamber connection flow path that can control the flow rate of the oil from the pressure chamber Cp to the control flow path 96 whose flow rate should be controlled when the spool main body portion 46 moves from the other side to the one side by the driving force of the driving portion 84 (solenoid) of the driving device 80. On the other hand, the throttle portion 68 of the poppet valve 60 restricts the flow rate per unit time of the oil flowing from the pressure source flow passage 95 toward the pressure chamber Cp.
When the force pressing the poppet 60 to one side by the pressure in the pressure chamber Cp and the pressing force of the poppet pressing spring 14 is smaller than the force pressing the poppet 60 to the other side by the pressure in the pressure source flow passage 95, the poppet 60 moves to the other side in the axial direction da and the seating surface 63 of the poppet 60 is separated from the seat portion 25 of the housing 20. Thereby, the pressure source port 22 of the housing 20 and the inner circumferential groove 24 communicate via the notch portion 69 of the poppet 60. That is, the pressure source flow path 95 and the control flow path 96 communicate via the pressure source port 22, the notched portion 69, the inner circumferential groove 24, the control port 23, and the 1 st inner circumferential groove 93 of the attached member 90. Thereby, the flow rate control valve 10 is in the flow state shown in fig. 3, and the oil flows from the pressure source flow path 95 to the control flow path 96.
At this time, since the pressure chamber Cp communicates with the control flow path 96, the oil that has flowed into the control flow path 96 from the pressure source flow path 95 also flows into the pressure chamber Cp, and the pressure in the pressure chamber Cp rises. When the force pressing the poppet valve 60 to one side by the pressure in the pressure chamber Cp and the pressing force of the poppet valve pressing spring 14 exceeds the force pressing the poppet valve 60 to the other side by the pressure in the pressure source flow path 95, the poppet valve 60 moves to one side, and the opening area between the pressure source flow path 95 and the control flow path 96 via the notch portion 69 of the poppet valve 60 decreases. Accordingly, the notch portion 69 of the poppet valve 60 functions as an orifice, the flow rate of the oil flowing from the pressure source flow path 95 to the control flow path 96 decreases, and the pressure in the control flow path 96 and the pressure chamber Cp decreases. At the same time, the poppet valve 60 moves to the other side, and the opening area between the pressure source flow path 95 and the control flow path 96 due to the notch portion 69 of the poppet valve 60 increases. Then, the poppet valve 60 is stopped at a position where the force pressing the poppet valve 60 to one side by the pressure in the pressure chamber Cp and the pressing force of the poppet valve pressing spring 14 is balanced with the force pressing the poppet valve 60 to the other side by the pressure in the pressure source flow path 95, and the oil flows from the pressure source flow path 95 to the control flow path 96 at a flow rate corresponding to the opening area between the pressure source flow path 95 and the control flow path 96 by the notch portion 69 at this time. The stop position of the poppet valve 60 can be controlled by controlling the amount of projection of the drive lever 82 to one side in the axial direction da by the drive portion 84 of the drive device 80. That is, by controlling the amount of projection of the drive rod 82 to one side along the axial direction da, the flow rate of the oil flowing from the pressure source flow passage 95 to the control flow passage 96 can be controlled.
Next, an operation for making the flow rate control valve 10 transit from the flow state to the closed state again will be described. When the drive rod 82 of the drive device 80 is retracted to the other side, the spool 40 is retracted toward the retracted position by the pressing force of the spool pressing spring 12, and the space between the pressure chamber Cp and the 3 rd chamber C3 is closed by the spool 40. Thereafter, the oil flows from the pressure source flow path 95 into the pressure chamber Cp via the throttle portion 68 of the poppet 60, and the pressure in the pressure chamber Cp rises. When the force pressing the poppet 60 to one side by the pressure in the pressure chamber Cp and the poppet pressing spring 14 exceeds the force pressing the poppet 60 to the other side by the pressure in the pressure source flow passage 95, the poppet 60 moves to one side and is pressed against the seat portion 25 of the housing 20. Thereby, the flow control valve 10 is restored to the closed state shown in fig. 2.
The flow rate control valve 10 of the present invention includes: a spool receiving block 30 having a spool receiving hole 31; and a spool 40 having: a spool main body portion 46; a spool large diameter portion 50 having a diameter larger than that of the spool main body portion 46; and a flow passage 51 which opens at one end side in the axial direction da and communicates with a chamber C1, the chamber C1 being located between a portion of the spool main body portion 46 which is located on the other end side in the axial direction da than the spool large diameter portion 50 and the spool housing block 30, and the spool 40 being movably housed in the spool housing hole 31.
The flow rate control valve 10 of the present invention includes: a spool receiving block 30 having a spool receiving hole 31; and a spool 40 having: a spool main body portion 46 having one end surface 41 located at one end in the axial direction da; a spool large diameter portion 50 having a diameter larger than that of the spool body portion 46, located in an intermediate portion of the other end apart from the one end and the axial direction da, having an acting surface 50a facing the other end side and another acting surface 50b facing the one end side, and having an area of the one end surface 41 equal to that of the acting surface 50 a; a flow path 51 which opens on one end side and communicates with a chamber C1, the chamber C1 being located between the spool housing block 30 and a portion of the spool main body portion 46 on the other end side of the spool large diameter portion 50; and another flow path 55 which is open at the other end side and communicates with another chamber C2, the other chamber C2 being located between the spool housing block 30 and a portion of the spool main body portion 46 which is located on the one end side of the spool large diameter portion 50, and the spool 40 being movable in the spool housing hole 31 by the driving force of the solenoid.
The flow rate control valve 10 of the present invention includes: a spool 40 having: a spool main body portion 46 configured to be movable to one side and the other side along an axial direction da; and a spool large diameter portion 50 having a diameter larger than that of the spool main body portion 46; a pressure chamber Cp, at least a part of which is defined by one end of the spool main body portion 46, and which generates a pressing force that presses the spool main body portion 46 from one side toward the other side; a chamber C1, at least a part of which is defined by a portion of the spool main body portion 46 located on the other end side of the spool large diameter portion 50, and which generates another pressing force that presses the spool large diameter portion 50 from the other side toward the one side, thereby canceling at least part of the pressing force from the pressure chamber Cp; and pressure chamber connection passages (47, 48) which are capable of controlling the flow rate of oil from the pressure chamber Cp to the control passage 96 whose flow rate is to be controlled when the spool main body portion 46 is moved from the other side to the one side by the driving force of the solenoid (driving portion 84).
According to the flow rate control valve 10, the same pressure as the pressure acting on the one end side of the spool 40 acts on the portion of the spool 40 facing the chamber C1, and a pressing force is generated in the spool 40 toward the one side in the axial direction da. Therefore, the pressing force toward one side generated at the portion of the spool 40 facing the chamber C1 cancels (cancels) at least a part of the pressing force toward the other side generated at one end side of the spool 40. This can effectively reduce the pressing force of the spool 40 toward the other side due to the pressure acting on the one end side of the spool 40, and can reduce the driving force required by the driving device 80. Therefore, the size of the driving device 80 can be reduced, and the cost of the driving device 80 can be reduced.
In the flow rate control valve 10 of the present invention, the spool main body portion 46 has one end surface 41 located at one end, the spool large diameter portion 50 has an acting surface 50a facing the other end side, and the area of the one end surface 41 is the same as the area of the acting surface 50 a.
According to the flow rate control valve 10, the pressing force toward the other side by the one end surface 41 and the pressing force toward the one side by the acting surface 50a cancel each other out. Therefore, only the pressing force of the spool pressing spring 12 becomes a pressing force that presses the spool 40 toward the other side. That is, the drive device 80 can move the spool 40 toward the advanced position only by pressing the spool 40 against the pressing force of the spool pressing spring 12. In this case, the driving force required for the driving device 80 can be further reduced. Therefore, the size of the driving device 80 can be further reduced, and the cost of the driving device 80 can be further reduced.
In the flow rate control valve 10 of the present invention, the spool large diameter portion 50 is located at an intermediate portion between one end and the other end away from the spool 40.
According to the flow rate control valve 10, since the area of the one end surface 41 and the area of the acting surface 50a can be adjusted independently of each other, the degree of freedom in designing the spool 40 can be improved. This also makes it easy to make the area of the one end surface 41 and the area of the working surface 50a the same.
In the flow rate control valve 10 of the present invention, the spool large diameter portion 50 has the other acting surface 50b facing one end side, the spool 40 has the other flow passage 55, the other flow passage 55 opens to the other end side of the spool 40 and communicates with the other chamber C2, and the other chamber C2 is located between the spool housing block 30 and a portion of the spool main body portion 46 on the one end side of the spool large diameter portion 50.
According to the flow rate control valve 10, the same positive or negative pressure as that applied to the other end side of the spool 40 acts on the portion of the spool 40 facing the other chamber C2, and a pressing force is generated on the spool 40 toward the other side or one side in the axial direction da. Therefore, the pressing force toward the other side or the one side generated by the other acting surface 50b on the spool 40 cancels (cancels) at least a part of the pressing force toward the one side or the other side by the other end side of the spool 40. This effectively reduces the pressing force acting on the spool 40 due to the pressure in the rod chamber Cr, and the spool 40 can be operated stably.
In the flow rate control valve 10 of the present invention, the spool 40 moves in the spool housing hole 31 by the driving force of the solenoid.
In general, an electromagnetic actuator capable of outputting a large driving force is large and expensive. In contrast, according to the flow rate control valve 10 of the present invention, since the driving force required to move the spool 40 can be reduced, even when the spool 40 moves in the spool housing hole 31 by the driving force of the solenoid, a small and inexpensive electromagnetic actuator having a relatively small driving force can be used as the driving source of the spool 40.

Claims (7)

1. A flow rate control valve is provided with:
a spool receiving block having a spool receiving hole; and
a spool having: a spool body portion; a spool large-diameter portion having a diameter larger than that of the spool main body portion; and a flow path that is open at one end side in the axial direction and communicates with a chamber, at least a part of the chamber being defined by a portion of the spool main body portion that is located on the other end side in the axial direction with respect to the spool large-diameter portion and the spool housing block, the spool being movably housed in the spool housing hole.
2. The flow control valve of claim 1,
the spool body portion has an end face at the one end,
the spool large diameter portion has an acting surface facing the other end side,
the area of the one end surface is the same as that of the action surface.
3. The flow control valve of claim 1,
the spool large diameter portion is located at an intermediate portion of the spool away from the one end and the other end.
4. The flow control valve of claim 1,
the spool large diameter portion has another acting surface facing the one end side,
the spool has another flow path that opens to the other end side of the spool and communicates with another chamber located between the spool housing block and a portion of the spool body that is closer to the one end side than the spool large diameter portion.
5. The flow control valve of claim 1,
the spool moves in the spool receiving hole by a driving force of a solenoid.
6. A flow rate control valve is provided with:
a spool receiving block having a spool receiving hole; and
a spool having: a spool main body portion having an end surface located at one end in an axial direction; a spool large diameter portion having a diameter larger than that of the spool body portion, located in an intermediate portion of the spool body portion that is located away from the one end and the other end in the axial direction, and having an acting surface facing the other end side and another acting surface facing the one end side, the area of the one end surface being the same as the area of the acting surface; a flow path that opens to the one end side and communicates with a chamber, at least a part of which is defined by a portion of the spool body portion on the other end side of the spool large-diameter portion and the spool housing block; and another flow path that is open on the other end side and communicates with another chamber that is defined at least in part by a portion of the spool main body portion that is located closer to the one end side than the spool large diameter portion and the spool housing block, the spool being movable in the spool housing hole by a driving force of a solenoid.
7. A flow rate control valve is provided with:
a spool having: a spool main body portion that is disposed so as to be movable to one side and the other side along an axial direction; and a spool large diameter portion having a diameter larger than a diameter of the spool main body portion;
a pressure chamber, at least a part of which is defined by an end portion of the spool body portion on the one side, for generating a pressing force for pressing the spool body portion from the one side toward the other side;
a chamber, at least a part of which is defined by a portion of the spool main body portion on the other side than the spool large-diameter portion, and which generates another pressing force that presses the spool large-diameter portion from the other side toward the one side and eliminates at least a part of the pressing force by the pressure chamber; and
and a pressure chamber connection passage capable of controlling a flow rate of the oil from the pressure chamber to a control passage whose flow rate is to be controlled when the spool main body portion is moved from the other side to the one side by a driving force of the solenoid.
CN202010090711.8A 2019-02-13 2020-02-13 Flow control valve Pending CN111561573A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2019023927A JP7346037B2 (en) 2019-02-13 2019-02-13 flow control valve
JP2019-023927 2019-02-13

Publications (1)

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CN111561573A true CN111561573A (en) 2020-08-21

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Application Number Title Priority Date Filing Date
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Country Link
JP (1) JP7346037B2 (en)
KR (1) KR20200099092A (en)
CN (1) CN111561573A (en)

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5793679U (en) * 1980-11-28 1982-06-09
JPS6154567U (en) * 1984-09-17 1986-04-12
US8256739B2 (en) 2008-12-22 2012-09-04 Husco International, Inc. Poppet valve operated by an electrohydraulic poppet pilot valve
JP6710609B2 (en) 2016-08-31 2020-06-17 ナブテスコ株式会社 Spool valves and valve systems

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