JP7346037B2 - flow control valve - Google Patents

Description

The present invention relates to a flow control valve that controls the flow rate of flowing fluid.

Conventionally, in various fluid circuits, a flow control valve has been used to control the flow rate of fluid flowing through the fluid circuit. For example, in working machines such as construction vehicles that are driven using hydraulic pressure, hydraulic circuits that supply hydraulic fluid to each hydraulic actuator of the working machine and pilot pressure that operates hydraulic devices such as directional valves are supplied. A flow control valve is used in a hydraulic circuit for controlling the flow rate of oil flowing in the hydraulic circuit.

Patent Document 1 discloses an electrohydraulic pilot valve including a solenoid actuator, a pilot body, and a pilot poppet. In this electrohydraulic pilot valve, the internal pressure of the first control chamber communicates with the pilot control chamber through a control path provided in the pilot poppet. At this time, the tip of the pilot body closes the pilot passage provided in the pilot piston, blocking the flow of liquid between the pilot control chamber and the outlet. The trapped pressure forces the pilot poppet against the pilot poppet seat. This blocks the flow between the inlet and outlet of the electrohydraulic pilot valve. When the solenoid actuator is energized, the pilot body moves upwardly, opening the pilot passage and releasing pressure within the pilot control chamber into the discharge passage. When the opening between the pilot control chamber and the pilot passage reaches a predetermined size, the pilot poppet follows the pilot body. This movement moves the tip of the pilot body back toward the pilot passageway, reducing flow through the pilot passageway. When the flow in the pilot passage reaches equilibrium, the pilot poppet stops its movement and remains in the open position.

Such an electrohydraulic pilot valve has the advantage that by selectively controlling the current applied to the solenoid actuator, the flow of liquid passing through the electrohydraulic pilot valve can be proportionally controlled.

Japanese Patent Application Publication No. 2010-144928

However, in the control valve disclosed in Patent Document 1, the pilot body receives, at its tip, the pressure within the pilot control chamber, that is, the internal pressure of the first control chamber communicated via the control path. Since the internal pressure of the first control chamber is relatively high, a large force is required to move the pilot body against the internal pressure of the first control chamber. Therefore, it is necessary to use a solenoid actuator capable of generating a large driving force as the solenoid actuator for generating the driving force for driving the pilot body. In this case, there is a problem that the entire electrohydraulic pilot valve becomes larger and the cost also increases.

The present invention has been made in consideration of these points, and an object of the present invention is to provide a flow control valve that can be operated with a relatively small force.

The flow control valve according to the present invention comprises:
a spool accommodation block having a spool accommodation hole;
a spool main body portion, a spool large diameter portion having a diameter larger than the diameter of the spool main body portion, and a spool large diameter portion having an opening on one end side in the axial direction, and a spool large diameter portion having a diameter larger than the diameter of the spool main body portion; a spool movably housed in the spool housing hole, the spool having an end portion and a flow path communicating with a chamber located between the spool housing block;
Equipped with.

In the flow control valve according to the present invention,
The spool main body has one end surface located at the one end,
The spool large diameter portion has a working surface facing the other end,
The area of the one end surface and the area of the working surface may be the same.

In the flow control valve according to the present invention,
The spool large diameter portion may be located at an intermediate portion spaced apart from the one end and the other end of the spool.

In the flow control valve according to the present invention,
The spool large diameter portion has another working surface facing the one end side,
The spool is open at the other end of the spool, and has another chamber that communicates with another chamber located between a portion of the spool main body that is closer to the one end than the spool large diameter portion and the spool housing block. It may have a flow path.

In the flow control valve according to the present invention,
The spool may be moved within the spool accommodation hole by the driving force of a solenoid.

The flow control valve according to the present invention comprises:
a spool accommodation block having a spool accommodation hole;
a spool main body having one end face located at one end in the axial direction; a spool body having a diameter larger than the diameter of the spool main body and located in an intermediate portion spaced apart from the one end and the other end in the axial direction; and the other end a spool large-diameter portion having a working surface facing toward the side and another working surface facing the one end side, the area of the one end surface being the same as the area of the working surface; and an opening on the one end side; A flow path communicating with a chamber located between a portion of the spool main body that is closer to the other end than the spool large diameter portion and the spool housing block, and a flow path that opens to the other end, and The spool accommodating hole has a portion that is closer to the one end than the spool large diameter portion and another flow path that communicates with another chamber located between the spool accommodating block, and is movable within the spool accommodating hole by the driving force of a solenoid. A spool and
Equipped with.

The flow control valve according to the present invention comprises:
a spool having a spool body disposed movably on one side and the other side along the axial direction, and a spool large diameter portion having a diameter larger than the diameter of the spool body;
a pressure chamber that is at least partially defined by the end of the one side of the spool body and generates a pressing force that pushes the spool body from the one side toward the other side;
At least a portion of the spool main body is defined by a portion closer to the other end than the spool large diameter portion, and the spool large diameter portion is pushed from the other side toward the one side, and is pushed by the pressure chamber. a chamber producing another pushing force that counteracts at least a portion of the pressure;
Pressure chamber communication capable of controlling the flow rate of oil from the pressure chamber toward the control flow path whose flow rate is to be controlled when the spool main body moves from the other side to the one side in response to the driving force of a solenoid. A flow path.

According to the present invention, it is possible to provide a flow control valve that can be operated with a relatively small force.

FIG. 1 is a diagram for explaining one embodiment of the present invention, and is a sectional view showing a flow control valve in a state attached to a member to be attached. FIG. 2 is an enlarged view of the portion marked II in FIG. 1, showing the flow control valve in a closed state. FIG. 3 is a diagram corresponding to FIG. 2, showing the flow control valve in a flow state. FIG. 4 is a longitudinal sectional view showing the spool of the flow control valve. FIG. 5 is a longitudinal sectional view showing a cross section of the spool orthogonal to the cross section shown in FIG. 4. FIG. FIG. 6 is a cross-sectional view corresponding to the line VI-VI in FIG. FIG. 7 is a cross-sectional view corresponding to line VII-VII in FIG. 4.

Hereinafter, one embodiment of the present invention will be described with reference to the drawings. In addition, in the drawings attached to this specification, for convenience of illustration and ease of understanding, the scale, vertical and horizontal dimension ratios, etc. are appropriately changed and exaggerated from those of the actual drawings.

In addition, terms such as "parallel," "perpendicular," and "identical," and values of length and angle used in this specification that specify shapes, geometric conditions, and their degree, etc., are strictly The term shall be interpreted to include the extent to which similar functions can be expected, without being bound by meaning.

1 to 7 are diagrams for explaining one embodiment of the present invention. FIG. 1 is a sectional view showing the flow control valve 10 in a state where it is attached to a member to be attached 90, and FIGS. 2 and 3 are enlarged views showing the portion indicated by II in FIG. 1. In FIG. 2 the flow control valve 10 is shown in a closed condition, and in FIG. 3 the flow control valve 10 is shown in a flowing condition.

The attached member 90 is a member to which the flow rate control valve 10 is attached. The main body portion 91 of the attached member 90 is provided with a flow rate control valve attachment hole 92 into 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 perpendicular to the axial direction da. The flow control valve mounting hole 92 has a first inner circumferential groove 93 and a second inner circumferential groove 94 in order from the distal end side (one side) of the flow control valve attaching hole 92 . The first inner circumferential groove 93 and the second inner circumferential groove 94 are each formed in an annular shape along the circumferential direction of the flow control valve mounting hole 92 . In the example shown in FIG. 1, the main body 91 includes a pressure source flow path 95 communicating with the tip of the flow control valve mounting hole 92, a control flow path 96 communicating with the first inner circumferential groove 93, and a second inner circumferential groove 93. A drain channel 97 communicating with the groove 94 is provided. 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). With the flow control valve 10 attached to the flow control valve mounting hole 92, the flow rate of fluid, especially oil, flowing from the pressure source flow path 95 to the control flow path 96 is controlled by the flow 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 into the tank.

The flow control valve 10 includes a spool housing block 30 having a spool housing hole 31, and a spool 40 movably housed within the spool housing block 30. The flow control valve 10 of the present embodiment further includes a casing 20 having a housing hole 21, a poppet 60, a spool pressing spring 12, and a poppet pressing spring 14 housed in the casing 20.

Note that in this specification, the "axial direction (da)" refers to the direction in which the central axis A of the spool 40 extends (the longitudinal direction of the spool 40). In addition, the tip side of the flow control valve 10 along the axial direction da (the side leading to the pressure source flow path 95, the lower side in FIGS. 1 to 5) is defined as "one side", and the flow control valve 10 along the axial direction da The base end side (the side connected to the drive device 80, the upper side in FIGS. 1 to 5) is the "other side".

The casing 20 has an accommodation hole 21 that accommodates at least a portion of the spool accommodation block 30, the spool 40, the poppet 60, the spool pressing spring 12, and the poppet pressing spring 14. The casing 20 has a pressure source port 22 that communicates with the pressure source channel 95 and a control port 23 that communicates with the control channel 96 when the flow rate control valve 10 is attached to the flow rate control valve mounting hole 92. . The pressure source port 22 extends from the tip (one end) of the accommodation hole 21 along the axial direction da. The control flow path 96 extends from the side surface of the accommodation hole 21 in a radial direction perpendicular to the axial direction da. In the illustrated example, the casing 20 has a plurality of control ports 23 arranged along the circumferential direction around the central axis A of the spool 40. The accommodation hole 21 has an inner circumferential groove 24 that communicates with the control port 23 . The inner circumferential groove 24 is formed in an annular shape along the circumferential direction of the accommodation hole 21 . A seat portion 25 on which the seat surface 63 of the poppet 60 seats is provided at the opening of the pressure source port 22 on the accommodation hole 21 side (the other side). In the illustrated example, the seat portion 25 is located at the connection between the pressure source port 22 and the inner circumferential groove 24 . The seat portion 25 is configured with a surface extending in a direction oblique to both the axial direction and the radial direction, and is formed in an annular shape along the circumferential direction of the accommodation hole 21 . The casing 20 has a first through hole 26 and a second through hole 27 that allow the accommodation hole 21 and the outer surface of the casing 20 to communicate with each other. The first through hole 26 allows the accommodation hole 21 and the inner circumferential groove 24 to communicate through the gap 16 formed between the inner surface of the flow control valve mounting hole 92 and the outer surface of the casing 20 . The second through hole 27 is located on the other side of the first through hole 26 and allows the accommodation hole 21 and the second inner circumferential groove 94 to communicate with each other.

The spool accommodation block 30 has a spool accommodation hole 31 that extends in the axial direction and accommodates the spool 40 . The spool accommodation hole 31 penetrates the spool accommodation block 30 along the axial direction da. A spring support surface 32 is formed at the tip of one side of the spool accommodation block 30. The spring support surface 32 supports the poppet pressing spring 14 and receives a pressing force from the poppet pressing spring 14 . In the illustrated example, the spool accommodation block 30 is composed of a first block 30a and a second block 30b located on the other side of the first block 30a. The spool accommodation hole 31 is provided across the first block 30a and the second block 30b. In the illustrated example, the spool accommodation hole 31 is composed of a first small diameter hole 31a and a large diameter hole 31b provided in the first block 30a, and a second small diameter hole 31c provided in the second block 30b. There is. The first small diameter hole 31a, the large diameter hole 31b, and the second small diameter hole 31c each extend in the axial direction, and the center axes of the first small diameter hole 31a, the large diameter hole 31b, and the second small diameter hole 31c coincide with each other. There is. Further, the center axes of the first small diameter hole 31a, the large diameter hole 31b, and the second small diameter hole 31c coincide with the center axis A of the spool 40. The first small diameter hole 31a, the large diameter hole 31b, and the second small diameter hole 31c each have a circular shape in a cross section perpendicular to the central axis. The first small diameter hole 31a is located on one side of the large diameter hole 31b and has a diameter smaller than that of the large diameter hole 31b. The second 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 31b. Although the size relationship between the diameter of the first small diameter hole 31a and the diameter of the second small diameter hole 31c is not particularly limited, in the illustrated example, the diameter of the first small diameter hole 31a is equal to the diameter of the second small diameter hole 31c. The diameters of the first small diameter hole 31a and the second small diameter hole 31c correspond to the diameter of the spool body 46 of the spool 40, and the diameter of the large diameter hole 31b corresponds to the diameter of the spool large diameter part 50 of the spool 40. are doing.

A first inner circumferential groove 33 is provided in the first small diameter hole 31a. Further, a second inner circumferential groove 35 is provided between the first small diameter hole 31a and the large diameter hole 31b. The first inner circumferential groove 33 and the second inner circumferential groove 35 are each formed in an annular shape along the circumferential direction of the spool accommodation hole 31 . A first outer circumferential groove 36 communicating with the first through hole 26 of the casing 20 and a second outer circumferential groove 37 communicating with the second through hole 27 of the casing 20 are provided on the outer surface of the spool accommodation hole 31 . The spool accommodation block 30 (first block 30a) has a first through hole 38 that extends in the radial direction and allows the first inner circumferential groove 33 and the first outer circumferential groove 36 to communicate with each other, and a first through hole 38 that extends in the radial direction and allows the first inner circumferential groove 33 and the first outer circumferential groove 36 to communicate with each other. It has a second through hole 39 that communicates with the second outer circumferential groove 37 . In the illustrated example, the spool accommodation block 30 (first block 30a) has a plurality of first through holes 38 and a plurality of second through holes 39 arranged along the circumferential direction.

In a state where the flow control valve 10 is attached to the flow control valve attachment hole 92 of the attached member 90, the casing 20 is fixed to the flow control valve attachment hole 92 by screw connection or the like, and the spool accommodation block 30 is attached to the casing 20. It is fixed by screw connection or the like. Therefore, in a state where the flow control valve 10 is attached to the flow control valve attachment hole 92 of the attached member 90, the casing 20 and the spool accommodation block 30 do not move with respect to the attached member 90.

FIG. 4 is a longitudinal sectional view showing the spool 40, and FIG. 5 is a longitudinal sectional view showing a cross section of the spool 40 orthogonal to the cross section shown in FIG. The spool 40 has a central axis A that extends in the longitudinal direction, and is accommodated in the spool accommodation hole 31 of the spool accommodation block 30 so as to be movable along the axial direction da. A central axis A of the spool 40 extends along the axial direction da. The spool 40 has one end surface 41 located at one end (one side end) along the axial direction da, and the other end surface 44 located at the other end (other side end). That is, one end surface 41 is a surface facing one side of the spool 40, and the other end surface 44 is a surface facing the other side of the spool 40. One end surface 41 includes a protruding surface 42 that protrudes toward one side, and a spring support surface 43 located around the protruding surface 42 . The spring support surface 43 supports the spool pressing spring 12 and receives pressing force from the spool pressing spring 12. The other end surface 44 has a notch 45 that communicates with a second communication channel 55, which will be described later. The notch portion 45 is provided so that when a drive rod 82 of a drive device 80 (described later) comes into contact with the other end surface 44, the drive rod 82 does not close the opening of the second communication channel 55.

The spool 40 includes a spool body 46 and a spool large diameter portion 50 having a diameter larger than the diameter of the spool body 46 . In the illustrated example, the spool large diameter portion 50 is located at an intermediate portion spaced apart from one end and the other end of the spool 40. The spool main body portion 46 has an outer circumferential groove 47 located on one side of the spool large diameter portion 50. The outer circumferential groove 47 is formed in an annular shape along the circumferential direction of the spool main body portion 46. A notch 48 is formed at one end of the outer circumferential groove 47 by cutting out the spool main body 46 along the axial direction da. In this specification, one end of the spool 40 is referred to as "one end," and the other end is referred to as "the other end." Accordingly, one side of the spool 40 is sometimes referred to as the "one end side" and the other side is sometimes referred to as the "other end side."

The spool large diameter portion 50 has a first working surface (working surface) 50a facing the other end, and a second working surface (other working surface) 50b facing the one end. The first working surface 50a includes the other end side edge of the outer surface of the spool large diameter portion 50 extending along the axial direction da, and the outer surface of the spool body portion 46 at the other end side than the spool large diameter portion 50. are connected. The second action surface 50b connects one end side edge of the outer surface of the spool large diameter portion 50 extending along the axial direction da and the outer surface of the spool main body 46 at a portion closer to one end than the spool large diameter portion 50. are doing. In the illustrated example, the area of one end surface 41 of the spool 40 and the area of the first working surface 50a are the same. Furthermore, the area of the other end surface 44 of the spool 40 and the area of the second working surface 50b are the same. Note that the areas of the one end surface 41, the other end surface 44, the first working surface 50a, and the second working surface 50b are defined by the respective surfaces 41, 44, 50a, and 50b being connected to the central axis A (axial direction da). It is defined as the area on a perpendicular plane when projected along the axial direction da.

The spool large diameter portion 50 is arranged within the large diameter hole 31b of the spool accommodation hole 31. The diameters of the first small diameter hole 31a and the second small diameter hole 31c of the spool accommodation hole 31 are smaller than the diameter of the spool large diameter portion 50. Therefore, the spool large diameter portion 50 is movable along the axial direction da within the large diameter hole 31b and within the second inner circumferential groove 35. More specifically, the spool 40 is arranged such that the first working surface 50a of the spool large diameter section 50 contacts the other end of the large diameter hole 31b, and the second working surface 50b of the spool large diameter section 50 contacts the second inner circumference. It is movable along the axial direction da up to a position in contact with one end of the groove 35.

In the example shown in FIGS. 1 to 3, three spaces (a first chamber C1, a second chamber C2, and a third chamber C3) are formed between the spool 40 and the spool accommodation block 30. The first chamber (chamber) C1 is located between the spool housing block 30 and a portion of the spool main body 46 that is closer to the other end than the spool large diameter portion 50. In the illustrated example, the first working surface 50a of the spool large diameter portion 50 faces the first chamber C1. In this case, the first chamber C1 is defined by the portion of the spool main body 46 that is on the other end side of the spool large diameter portion 50, the first working surface 50a, and the spool accommodation hole 31 of the spool accommodation block 30. Ru. The second chamber (another chamber) C2 is located between the spool housing block 30 and a portion of the spool main body 46 that is closer to one end than the spool large diameter portion 50. In the illustrated example, the second working surface 50b of the spool large diameter portion 50 faces the second chamber C2. In this case, the second chamber C2 is defined by the portion of the spool main body 46 that is on the other end side of the spool large diameter portion 50, the second working surface 50b, and the spool accommodation hole 31 of the spool accommodation block 30. Ru. Particularly in the illustrated example, the portion of the spool accommodation hole 31 that defines the second chamber C2 includes the second inner circumferential groove 35. The third chamber C3 is located between the spool housing block 30 and a portion of the spool main body 46 that is closer to one end than the spool large diameter portion 50 on one side (one end side) of the second chamber C2. Particularly in the illustrated example, the portion of the spool body 46 that defines the third chamber C3 includes the outer circumferential groove 47, and the portion of the spool accommodation hole 31 that defines the third chamber C3 includes the first inner circumferential groove 33. include.

The spool 40 has a first communication flow path (flow path) 51 that opens at one end in the axial direction da and communicates with the first chamber C1. In the illustrated example, the first communication channel 51 opens to the one end surface 41 at one end side of the spool 40. In particular, the first communication channel 51 is open to the protruding surface 42 of the one end surface 41 . The first communication channel 51 includes a first communication hole 52 located inside the spool 40 and a first communication groove 53 formed on the outer surface of the spool large diameter portion 50. The first communication hole 52 has an axial portion 52a that opens at one end of the spool 40 and extends along the central axis A, and a radial direction that communicates with the other end of the axial portion 52a and extends in the radial direction of the spool 40. A portion 52b is included. The first communication groove 53 communicates with a radially outer portion of the radial portion 52b of the first communication hole 52 and extends along the axial direction da. In the illustrated example, the radial portion 52b of the first communication hole 52 passes through the spool large diameter portion 50 through the other end of the axial portion 52a. In other words, the radial portions 52b extend from the other end of the axial portion 52a in opposite directions at an angle of 180 degrees. A first communication groove 53 is connected to each of the two ends of the radial portion 52b. That is, the spool 40 has two first communication grooves 53 located on opposite sides of the central axis A. Note that the present invention is not limited to this, and the spool 40 may have one first communication groove 53 or three or more first communication grooves 53.

The spool 40 has a second communication flow path (another flow path) 55 that opens on the other end side in the axial direction da and communicates with the second chamber C2. In the illustrated example, the second communication channel 55 opens to the other end surface 44 at the other end of the spool 40 . The second communication channel 55 includes a second communication hole 56 located inside the spool 40 and a second communication groove 57 formed on the outer surface of the spool large diameter portion 50. The second communicating hole 56 includes an axial portion 56a that opens at the other end of the spool 40 and extends along the central axis A, and a radial direction that extends in the radial direction of the spool 40 and communicates with one end side of the axial portion 56a. A portion 56b is included. The second communicating groove 57 communicates with a radially outer portion of the radial portion 56b of the second communicating hole 56 and extends along the axial direction da. In the illustrated example, the radial portion 56b of the second communicating hole 56 passes through the spool large diameter portion 50 through one end of the axial portion 56a. In other words, the radial portions 56b extend from one end of the axial portion 56a in opposite directions at an angle of 180 degrees. A second communication groove 57 is connected to each of the two ends of the radial portion 56b. That is, the spool 40 has two second communication grooves 57 located on opposite sides of the central axis A. Note that the present invention is not limited to this, and the spool 40 may have one second communication groove 57 or three or more second communication grooves 57.

6 is a sectional view taken along line VI-VI in FIG. 4, and FIG. 7 is a sectional view taken along line VII-VII in FIG. In the illustrated example, when viewed along the axial direction da, the radial portion 52b of the first communicating hole 52 and the radial portion 56b of the second communicating hole 56 extend orthogonally to each other. Thereby, the first communication groove 53 and the second communication groove 57 are spaced apart from each other at an angle of 90 degrees in the circumferential direction of the spool 40. Therefore, the first communicating channel 51 and the second communicating channel 55 form mutually independent channels.

The poppet 60 is arranged so as to be movable within the accommodation hole 21 of the casing 20 in the axial direction da. The poppet 60 includes a main body 61 that closes and opens the pressure source port 22 of the casing 20, and a ball 70 and a support member 71 housed within the main body 61. The main body 61 has a small diameter portion 61a located inside the pressure source port 22 when the pressure source port 22 is closed, and a large diameter portion 61b located on the other side of the small diameter portion 61a. The main body 61 has a distal end surface 62 located at one end of the small diameter portion 61a. A seat surface 63 that seats on the seat section 25 of the casing 20 in the closed state is formed between the small diameter section 61a and the large diameter section 61b on the outer surface of the main body 61. The seat surface 63 is constituted by 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 60.

A spring housing hole 64 is provided in the large diameter portion 61b and is open to the other side of the poppet 60 and accommodates at least a portion of the spool pressing spring 12 and the poppet pressing spring 14. A spring support surface 64a is formed at one end of the spring accommodation hole 64. The spring support surface 64 a supports the poppet pressing spring 14 and receives pressing force from the poppet pressing spring 14 .

The main body 61 further includes a support member housing hole 65, a ball housing hole 66, a communication hole 67, and a constricted portion 68. The support member accommodating hole 65 opens into the spring accommodating hole 64 on the other side and accommodates the support member 71 therein. The ball accommodating hole 66 opens to the support member accommodating hole 65 on the other side and accommodates the ball 70 therein. The communication hole 67 opens into the support member receiving hole 65 on the other side and communicates with the constriction part 68 on one side. The diaphragm portion 68 opens into the communication hole 67 on the other side and opens into the distal end surface 62 on one side. A notch 69 is formed on the radially outer side of the tip surface 62.

The support member 71 includes a protrusion surface 72 that protrudes to the other side on a surface facing the other side, and a spring support surface 73 located around the protrusion surface 72 . The spring support surface 73 supports the spool pressing spring 12 and receives pressing force from the spool pressing spring 12. The support member 71 further includes a through hole 74 extending along the central axis A, and a notch 75 communicating with the through hole 74. The through hole 74 extends along the central axis A and opens into the protruding surface 72 on the other side of the support member 71 . The cutout portion 75 is a groove-shaped cutout provided on one side of the support member 71 and extending in the radial direction of the support member 71. The cutout portion 75 communicates with the through hole 74 on the inside in the radial direction, and communicates with the outer surface of the support member 71 on the outside in the radial direction. Note that the cutout portion 75 does not necessarily need to communicate with the outer surface of the support member 71 on the outside in the radial direction. The notch portion 75 is such that even when the ball 70 comes into contact with the through hole 74 of the support member 71, the through hole 74 is not completely closed by the ball 70, and the ball receiving hole 66 and the through hole 74 are connected to the notch portion 75. The specific shape is not particularly limited as long as it is communicated through.

The throttle portion 68 functions as a throttle that limits the flow rate of oil flowing from the pressure source port 22 of the casing 20 toward the communication hole 67 per unit time. Therefore, the cross-sectional area of the constricted portion 68 is sufficiently smaller than the cross-sectional area of the communication hole 67.

The ball 70 is accommodated within the ball accommodation hole 66 and is movable within the ball accommodation hole 66. The diameter of the ball 70 is smaller than the diameter of the ball accommodation hole 66 and larger than the diameter of the communication hole 67. Therefore, the entire ball 70 does not enter the communication hole 67. Thereby, the ball 70 functions as a check valve in cooperation with the communication hole 67. Specifically, the ball 70 allows oil to flow from the communication hole 67 toward the ball accommodation hole 66. On the other hand, when the oil attempts to flow from the ball accommodation hole 66 toward the communication hole 67, the ball 70 closes the opening on the other side of the communication hole 67. Therefore, the flow of oil from the ball accommodation hole 66 toward the communication hole 67 is not allowed.

A spool pressing spring 12 is arranged between the spool 40 and the poppet 60. In the illustrated example, the spool biasing spring 12 is disposed in a compressed state between the spring bearing surface 43 of the spool 40 and the spring bearing surface 73 of the support member 71 of the poppet 60. Therefore, the pressing force from the spool pressing spring 12 acts on the spring support surfaces 43 and 73, respectively.

A poppet pressing spring 14 is arranged between the spool accommodation block 30 and the poppet 60. In the illustrated example, the poppet biasing spring 14 is disposed in a compressed state between the spring support surface 32 of the spool receiving block 30 and the spring support surface 64a of the poppet 60. Therefore, a pressing force from the poppet pressing spring 14 acts on each of the spring support surfaces 32 and 64a.

A pressure chamber Cp is formed between the spool accommodation block 30 and the poppet 60. The pressure source flow of the attached member 90 is connected to the pressure chamber Cp through the pressure source port 22 of the casing 20, the constriction part 68 of the poppet 60, the communication hole 67, the ball accommodation hole 66, the support member accommodation hole, and the spring accommodation hole 64. Oil flows in from path 95.

Between the flow rate control valve mounting hole 92 of the attached member 90 and the outer surface of the casing 20, and between the accommodation hole 21 of the casing 20 and the outer surface of the spool accommodation block 30, there are provided O holes to prevent oil leakage. A sealing member 18, such as a ring, is arranged.

Movement of the spool 40 along the axial direction da is controlled by a drive device 80. The drive device 80 includes a drive rod 82 and a drive section 84. In the illustrated example, the drive unit 84 drives the drive rod 82 toward one side along the axial direction da using a drive force generated by a solenoid. The drive rod 82 contacts the other end surface 44 of the spool 40 and moves the spool 40 along the axial direction da. That is, in the illustrated example, the spool 40 moves within the spool accommodation hole 31 along the axial direction da by the driving force of the solenoid. Note that the present invention is not limited to this, and the drive unit 84 may be configured to drive the drive rod 82 using other drive force such as pilot pressure. Note that a rod chamber Cr surrounded by the drive device 80 and the flow control valve 10 is formed at a joint portion between the drive device 80 and the flow control valve 10. In the illustrated example, the rod chamber Cr is defined by the drive device 80 and the spool accommodation block 30 (second block 30b). A drive rod 82 of the drive device 80 and the other end (other end surface 44) of the spool 40 are arranged within the rod chamber Cr.

Next, the operation of the flow control valve 10 of this embodiment will be described with reference to FIGS. 2 and 3.

As shown in FIG. 2, when the drive rod 82 of the drive device 80 is most retracted, that is, when the drive rod 82 is located on the other side, the spool 40 is Therefore, it is located at the farthest side (retracted position). Specifically, the pressing force of the spool pressing spring 12 acts on the spring support surface 43 of the spool 40, thereby placing the spool 40 in the retracted position. At this time, the other end surface 44 of the spool 40 is in contact with the drive rod 82 of the drive device 80.

At this time, the second chamber C2 formed between the spool 40 and the spool accommodation block 30 includes the second through hole 39 of the spool accommodation block 30, the second outer peripheral groove 37, the second through hole 27 of the casing 20, and the It communicates with a drain flow path 97 via a second inner circumferential groove 94 of the mounting member 90 . Further, the third chamber C3 is located between the inner surface of the first through hole 38 of the spool accommodation block 30, the first outer circumferential groove 36, the first through hole 26 of the casing 20, and the flow control valve mounting hole 92, and the outer surface of the casing 20. It communicates with the control flow path 96 via the gap 16 formed in the first inner circumferential groove 93 of the attached member 90 . The spool 40 closes off the pressure chamber Cp and the third chamber C3.

The pressure source flow of the attached member 90 is connected to the pressure chamber Cp through the pressure source port 22 of the casing 20, the constriction part 68 of the poppet 60, the communication hole 67, the ball accommodation hole 66, the support member accommodation hole, and the spring accommodation hole 64. Oil flows in from path 95. The throttle portion 68 limits the flow rate of oil flowing from the pressure source port 22 toward the communication hole 67 per unit time. Therefore, when a high oil pressure acts on the pressure source flow path 95, the same oil pressure as the pressure source flow path 95 acts on the inside of the pressure chamber Cp after a certain period of time.

A pressing force that pushes the poppet 60 toward one side acts on the surface (other side surface) of the large diameter portion 61b of the poppet 60 that faces the other side due to the pressure within the pressure chamber Cp. Furthermore, a pressing force that pushes the poppet 60 toward the other side acts on the surface (one side) of the small diameter portion 61a that faces one side due to the pressure within the pressure source channel 95. The area of the other side surface of the large diameter portion 61b is the area on the plane when the large diameter portion 61b is projected along the axial direction da onto a plane orthogonal to the central axis A (axial direction da). equal. Further, the area of one side of the small diameter portion 61a is the area on the plane when the small diameter portion 61a is projected along the axial direction da onto a plane perpendicular to the central axis A (axial direction da). equal. In the illustrated example, the area of the other side of the large diameter portion 61b is larger than the area of one side of the small diameter portion 61a. Therefore, the pressing force acting on the other side of the large diameter portion 61b to push the poppet 60 toward one side is greater than the pressing force acting on one side of the small diameter portion 61a pushing the poppet 60 toward the other side. . Furthermore, the poppet 60 receives a pressing force from the poppet pressing spring 14 that pushes the poppet 60 toward one side via the spring support surface 73 of the support member 71 . As a result, the poppet 60 receives the difference between the pushing force that pushes the poppet 60 toward one side due to the pressure in the pressure chamber Cp and the pushing force that pushes the poppet 60 toward the other side due to the pressure inside the pressure source channel 95, and , is pressed against the seat portion 25 of the casing 20 by the pressing force received from the poppet pressing spring 14. More specifically, the seat surface 63 of the poppet 60 is pressed against the seat portion 25 of the casing 20. At this time, as shown in FIG. 2, the poppet 60 is located at the most one side (closed position), and the flow rate control valve 10 is in a closed state in which the flow path leading from the pressure source flow path 95 to the control flow path 96 is closed.

Next, an operation for shifting the flow rate control valve 10 from the closed state to the flowing state will be described. When the drive unit 84 of the drive device 80 is driven to move the drive rod 82 toward one side along the axial direction da, the spool 40 is pushed by the drive rod 82 and also moves toward the one side (forward) along the axial direction da. position). In this embodiment, the drive section 84 includes a solenoid actuator, and the drive rod 82 is moved toward one side by the driving force generated by the solenoid actuator.

Due to the pressure acting within the pressure chamber Cp, a pressing force is generated on the spool 40 through one end surface 41 toward the other side. The spool 40 has a first communication flow path (flow path) 51 that is open at one end surface 41 and communicates with the first chamber (chamber) C1. Further, the first working surface (working surface) 50a of the spool large diameter portion 50 of the spool 40 faces the first chamber C1. As a result, the same pressure as the pressure acting on the one end surface 41 of the spool 40 acts on the first working surface 50a. That is, the pressure acting on the first chamber C1 generates a pressing force on the spool 40 toward one side via the first action surface 50a. Therefore, the pressing force generated toward one side of the spool 40 via the first operating surface 50a cancels out (cancels out) at least a portion of the pressing force directed toward the other side via the one end surface 41. Thereby, it is possible to effectively reduce the pressing force that pushes the spool 40 toward the other side due to the pressure within the pressure chamber Cp, and it is possible to reduce the driving force required for the drive device 80. . Therefore, the drive device 80 can be downsized and the cost of the drive device 80 can be reduced.

In particular, in the flow control valve 10 of this embodiment, the area of the one end surface 41 and the area of the first working surface 50a are the same. In this case, the pressing force directed toward the other side via the one end surface 41 and the pressing force directed toward the one side via the first working surface 50a cancel each other out. Therefore, only the pressing force of the spool pressing spring 12 becomes the pressing force that presses the spool 40 toward the other side. That is, the drive device 80 can move the spool 40 toward the forward position simply by pushing the spool 40 against the pushing force of the spool pushing spring 12. In this case, it becomes possible to further reduce the driving force required for the drive device 80. Therefore, the drive device 80 can be further downsized and the cost of the drive device 80 can be further reduced.

Further, as the drive rod 82 of the drive device 80 and the spool 40 move, the volume within the rod chamber Cr changes, and positive or negative pressure may be generated in the oil held within the rod chamber Cr. Due to the pressure acting within the rod chamber Cr, a pressing force is generated on the spool 40 through the other end surface 44 toward one side or the other side. The spool 40 has a second communication flow path (another flow path) 55 that is open to the other end surface 44 and communicates with the second chamber (another chamber) C2. Further, a second working surface (another working surface) 50b of the spool large diameter portion 50 of the spool 40 faces the second chamber C2. As a result, the same pressure as the pressure acting on the other end surface 44 of the spool 40 acts on the second working surface 50b. That is, the pressure acting on the second chamber C2 generates a pressing force on the spool 40 toward the other side or one side via the second action surface 50b. Therefore, the pressing force generated on the spool 40 through the second action surface 50b toward the other side or one side cancels out at least a portion of the pressing force toward the one side or the other side through the other end surface 44. do). Thereby, the pressing force acting on the spool 40 caused by the pressure inside the rod chamber Cr can be effectively reduced, and the spool 40 can be operated stably.

In particular, in the flow control valve 10 of this embodiment, the area of the other end surface 44 and the area of the second operating surface 50b are the same. In this case, the pressing force directed toward one side via the other end surface 44 and the pressing force directed toward the other side via the second action surface 50b cancel each other out. Therefore, it becomes possible to operate the spool 40 more stably.

Furthermore, in the flow control valve 10 of the present embodiment, the second chamber C2 includes the second through hole 39 of the spool accommodation block 30, the second outer circumferential groove 37, the second through hole 27 of the casing 20, and the second through hole 39 of the spool accommodation block 30, the second through hole 27 of the casing 20, and It always communicates with the drain passage 97 via the second inner circumferential groove 94 . As a result, the oil held in the rod chamber Cr and the second chamber C2 is discharged to the drain passage 97, and no hydraulic pressure acts on the rod chamber Cr and the second chamber C2. Therefore, it becomes possible to operate the spool 40 more stably.

When the spool 40 moves toward the forward position, a notch 48 continuously provided in the outer circumferential groove 47 of the spool 40 communicates with the pressure chamber Cp. Thereby, the pressure chamber Cp and the third chamber C3 communicate through the notch portion 48. As mentioned above, the third chamber C3 always communicates with the control flow path 96. That is, when the spool 40 moves toward the forward position, the pressure chamber Cp and the control flow path 96 communicate with each other via the third chamber C3. When the pressure chamber Cp and the control channel 96 communicate with each other, the oil in the pressure chamber Cp flows to the control channel 96, and the pressure in the pressure chamber Cp decreases rapidly. Therefore, in the present embodiment, when the spool main body 46 moves from the other side to the one side under the driving force of the drive unit 84 (solenoid) of the drive device 80, the outer circumferential groove 47 and the notch 48 A pressure chamber communication flow path is configured that can control the flow rate of oil heading from the pressure chamber Cp to the control flow path 96 whose flow rate is to be controlled. On the other hand, the throttle portion 68 of the poppet 60 limits the flow rate of oil flowing from the pressure source channel 95 toward the pressure chamber Cp per unit time.

When the force pushing the poppet 60 to one side due to the pressure in the pressure chamber Cp and the pushing force of the poppet pushing spring 14 becomes smaller than the force pushing the poppet 60 to the other side due to the pressure in the pressure source channel 95, the poppet 60 moves in the axial direction. moving to the other side along da, the seat surface 63 of the poppet 60 separates from the seat portion 25 of the casing 20. Thereby, the pressure source port 22 of the casing 20 and the inner circumferential groove 24 communicate through the notch 69 of the poppet 60. That is, the pressure source flow path 95 and the control flow path 96 communicate through the pressure source port 22, the notch 69, the inner circumferential groove 24, the control port 23, and the first inner circumferential groove 93 of the attached member 90. As a result, the flow control valve 10 enters the flow state shown in FIG. 3, and oil flows from the pressure source flow path 95 toward the control flow path 96.

At this time, since the pressure chamber Cp and the control channel 96 communicate with each other, the oil that has flowed from the pressure source channel 95 into the control channel 96 also flows into the pressure chamber Cp, and the pressure in the pressure chamber Cp increases. When the force pushing the poppet 60 to one side due to the pressure in the pressure chamber Cp and the pushing force of the poppet pushing spring 14 exceeds the force pushing the poppet 60 to the other side due to the pressure in the pressure source channel 95, the poppet 60 moves to one side. As a result, the opening area between the pressure source flow path 95 and the control flow path 96 via the notch 69 of the poppet 60 is reduced. As a result, the notch 69 of the poppet 60 functions as a throttle, the flow rate of oil flowing from the pressure source channel 95 toward the control channel 96 is reduced, and the pressure in the control channel 96 and the pressure chamber Cp is reduced. . Along with this, the poppet 60 moves to the other side, and the opening area between the pressure source channel 95 and the control channel 96 by the notch 69 of the poppet 60 increases. Then, the poppet 60 is moved at a place where the force pushing the poppet 60 to one side due to the pressure in the pressure chamber Cp and the pushing force of the poppet pushing spring 14 is balanced with the force pushing the poppet 60 to the other side due to the pressure in the pressure source channel 95. The oil flows from the pressure source flow path 95 toward 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 due to the notch portion 69 at this time. The stop position of the poppet 60 can be controlled by controlling the amount of protrusion of the drive rod 82 to one side along the axial direction da by the drive unit 84 of the drive device 80 . That is, by controlling the amount of protrusion of the drive rod 82 to one side along the axial direction da, it is possible to control the flow rate of oil flowing from the pressure source flow path 95 toward the control flow path 96.

Next, a description will be given of an operation for shifting the flow rate control valve 10 from the flow state to the closed state again. 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 spool 40 closes the space between the pressure chamber Cp and the third chamber C3. be done. Thereafter, oil flows into the pressure chamber Cp from the pressure source channel 95 through the constriction portion 68 of the poppet 60, thereby increasing the pressure within the pressure chamber Cp. When the pressure in the pressure chamber Cp and the force pushing the poppet 60 to one side by the poppet pressing spring 14 exceed the force pushing the poppet 60 to the other side due to the pressure in the pressure source channel 95, the poppet 60 moves to one side. It is pressed against the seat portion 25 of the casing 20. Thereby, the flow control valve 10 returns to the closed state shown in FIG. 2.

The flow control valve 10 of the present invention includes a spool accommodation block 30 having a spool accommodation hole 31, a spool main body 46, a spool large diameter part 50 having a diameter larger than the diameter of the spool main body 46, and an axial direction da. It has a flow path 51 that is open on one end side and communicates with the chamber C1 located between the portion of the spool main body 46 that is closer to the other end in the axial direction da than the spool large diameter portion 50 and the spool accommodation block 30. , and a spool 40 movably accommodated in the spool accommodation hole 31.

Further, the flow control valve 10 of the present invention includes a spool housing block 30 having a spool housing hole 31, a spool body portion 46 having one end surface 41 located at one end in the axial direction da, and a diameter larger than the diameter of the spool body portion 46. It has a working surface 50a that has a diameter and is located at an intermediate portion spaced apart from one end and the other end in the axial direction da, and has an operating surface 50a facing the other end side and another working surface 50b facing the one end side, and has an area equal to the area of the one end surface 41. Between the spool large-diameter portion 50 having the same area as the working surface 50a, the portion of the spool body portion 46 that is open at one end and which is on the other end side of the spool large-diameter portion 50, and the spool accommodation block 30. A flow path 51 communicating with the chamber C1 located at the spool body C1 and another chamber C2 located between the spool housing block 30 and a portion of the spool main body 46 which is open to the other end and which is closer to one end than the spool large diameter portion 50. The spool 40 has another flow path 55 communicating with the spool 40 and is movable within the spool accommodation hole 31 by the driving force of a solenoid.

The flow control valve 10 according to the present invention also includes a spool main body 46 disposed movably on one side and the other side along the axial direction da, and a spool large diameter portion having a diameter larger than the diameter of the spool main body 46. 50, a pressure chamber Cp that is at least partially partitioned by one end of the spool body 46 and generates a pressing force that pushes the spool body 46 from one side to the other, and a spool body At least a portion of the portion 46 is partitioned at the other end side of the spool large diameter portion 50, and pushes the spool large diameter portion 50 from the other side toward one side, and at least part of the pressing force by the pressure chamber Cp The flow rate should be controlled from the pressure chamber Cp when the spool main body 46 moves from the other side to the one side under the driving force of the chamber C1 that generates another pressing force that cancels out the solenoid (driving unit 84). A pressure chamber communication flow path (47, 48) capable of controlling the flow rate of oil toward the control flow path 96 is provided.

According to such a flow control valve 10, the same pressure as the pressure acting on one end side of the spool 40 acts on the portion of the spool 40 facing the chamber C1, pushing the spool 40 toward one side in the axial direction da. Pressure is created. Therefore, the pushing force toward one side generated in the portion of the spool 40 facing the chamber C1 cancels out (cancels out) at least a portion of the pushing force generated at one end of the spool 40 toward the other side. As a result, the pressing force that pushes the spool 40 toward the other side due to the pressure acting on one end of the spool 40 can be effectively reduced, and the driving force required for the drive device 80 can be reduced. It becomes possible. Therefore, the drive device 80 can be downsized and the cost of the drive device 80 can be reduced.

In the flow control valve 10 of the present invention, the spool main body 46 has one end surface 41 located at one end, the spool large diameter section 50 has an operating surface 50a facing the other end, and the area of the one end surface 41 is and the area of the working surface 50a are the same.

According to such a flow control valve 10, the pressing force directed toward the other side via the one end surface 41 and the pressing force directed toward the one side via the working surface 50a cancel each other out. Therefore, only the pressing force of the spool pressing spring 12 becomes the pressing force that presses the spool 40 toward the other side. That is, the drive device 80 can move the spool 40 toward the forward position simply by pushing the spool 40 against the pushing force of the spool pushing spring 12. In this case, it becomes possible to further reduce the driving force required for the drive device 80. Therefore, the drive device 80 can be further downsized and the cost of the drive device 80 can be further reduced.

In the flow control valve 10 of the present invention, the spool large diameter portion 50 is located at an intermediate portion spaced apart from one end and the other end of the spool 40.

According to such a flow control valve 10, since the area of the one end surface 41 and the area of the working surface 50a can be adjusted independently of each other, the degree of freedom in designing the spool 40 can be improved. Thereby, it becomes possible to easily make the area of the one end surface 41 and the area of the working surface 50a the same.

In the flow control valve 10 of the present invention, the spool large diameter portion 50 has another working surface 50b facing one end, and the spool 40 opens toward the other end of the spool body 46. It has another flow path 55 that communicates with another chamber C2 located between a portion closer to one end than the large diameter portion 50 and the spool accommodation block 30.

According to such a flow control valve 10, the same pressure as the positive or negative pressure acting on the other end side of the spool 40 acts on the portion of the spool 40 facing the other chamber C2, causing the spool 40 to move in the axial direction. A pressing force is generated toward the other side or one side of da. Therefore, the pressing force generated on the spool 40 through the other working surface 50b toward the other side or one side absorbs at least part of the pressing force toward the one side or the other side through the other end side of the spool 40. to cancel out (to cancel out). Thereby, the pressing force acting on the spool 40 caused by the pressure inside the rod chamber Cr can be effectively reduced, and the spool 40 can be operated stably.

In the flow control valve 10 of the present invention, the spool 40 moves within the spool accommodation hole 31 by the driving force of a solenoid.

Solenoid actuators capable of outputting large driving force are generally large and expensive. On the other hand, according to the flow control valve 10 of the present invention, the driving force required to move the spool 40 can be reduced, so that the spool 40 can be moved into the spool accommodation hole 31 by the driving force of the solenoid. When moving the spool 40, a solenoid actuator, which has a relatively small driving force, is small, and is inexpensive, can be used as the drive source for the spool 40.

10 Flow control valve 12 Spool pressing spring 14 Poppet pressing spring 16 Gap 20 Casing 21 Accommodating hole 22 Pressure source port 23 Control port 25 Seat part 30 Spool housing block 30a First block 30b Second block 31 Spool housing hole 40 Spool 41 One end surface 44 Other end surface 46 Spool main body 47 Outer circumferential groove (pressure chamber communication channel)
48 Notch (pressure chamber communication channel)
50 Spool large diameter part 50a first working surface (working surface)
50b Second action surface (other action surface)
51 First communication flow path (flow path)
55 Second communication channel (other channel)
60 Poppet 61 Main body 63 Seat surface 68 Restricted part 69 Notch part 70 Ball 71 Support member 80 Drive device 82 Drive rod 84 Drive part 90 Mounted member 91 Main body part 92 Flow rate control valve mounting hole 95 Pressure source flow path 96 Control flow path 97 Drain passage A Center axis C1 First chamber (chamber)
C2 2nd room (other rooms)
C3 Third chamber Cp Pressure chamber Cr Rod chamber

Claims (11)

a spool accommodation block having a spool accommodation hole;
a spool main body portion, a spool large diameter portion having a diameter larger than the diameter of the spool main body portion, and a spool large diameter portion having an opening on one end side in the axial direction, and a spool large diameter portion having a diameter larger than the diameter of the spool main body portion; a spool movably housed in the spool housing hole, the spool having an end portion and a flow path leading to a chamber at least partially partitioned by the spool housing block;
a casing having a pressure source port communicating with a pressure source flow path and accommodating the spool;
a poppet housed in the casing and closing and opening the pressure source port;
Flow control valve with. The spool main body has one end surface located at the one end,
The spool large diameter portion has a working surface facing the other end,
The flow control valve according to claim 1, wherein the area of the one end surface and the area of the working surface are the same. The flow control valve according to claim 1 or 2, wherein the spool large diameter portion is located at an intermediate portion spaced apart from the one end and the other end of the spool. The spool large diameter portion has another working surface facing the one end side,
The spool is open at the other end of the spool, and has another chamber that communicates with another chamber located between a portion of the spool main body that is closer to the one end than the spool large diameter portion and the spool housing block. The flow control valve according to any one of claims 1 to 3, having a flow path. The flow control valve according to any one of claims 1 to 4, wherein the spool moves within the spool accommodation hole by a driving force of a solenoid. The flow control valve according to any one of claims 1 to 5, wherein the poppet has a constriction portion opening at a distal end surface of the poppet. a pressure chamber formed between the spool housing block and the poppet;
The flow control valve according to claim 6, wherein oil flows from the pressure source flow path into the pressure chamber via the pressure source port and the throttle section. 8. The flow control valve according to claim 1, further comprising a spool pressing spring disposed between the spool and the poppet. 9. The flow control valve according to claim 1, further comprising a poppet pressing spring disposed between the spool housing block and the poppet. a spool accommodation block having a spool accommodation hole;
a spool main body having one end face located at one end in the axial direction; a spool body having a diameter larger than the diameter of the spool main body and located in an intermediate portion spaced apart from the one end and the other end in the axial direction; and the other end a spool large-diameter portion having a working surface facing toward the side and another working surface facing the one end side, the area of the one end surface being the same as the area of the working surface; and an opening on the one end side; A portion of the spool main body portion that is closer to the other end than the spool large diameter portion and a flow path that communicates with a chamber at least partially partitioned by the spool storage block and that opens to the other end side, and the spool main body. a part of the spool that is closer to the one end than the spool large diameter part, and another flow path that communicates with another chamber at least partially partitioned by the spool storage block, and the spool storage is carried out by the driving force of a solenoid. a spool movable within the hole;
a casing having a pressure source port communicating with a pressure source flow path and accommodating the spool;
a poppet housed in the casing and closing and opening the pressure source port;
Flow control valve with. a spool having a spool body disposed movably on one side and the other side along the axial direction, and a spool large diameter portion having a diameter larger than the diameter of the spool body;
a pressure chamber that is at least partially defined by the end of the one side of the spool body and generates a pressing force that pushes the spool body from the one side toward the other side;
At least a portion of the spool main body is defined by a portion on the other side than the spool large diameter portion, and the spool large diameter portion is pushed from the other side toward the one side, and the pressing force by the pressure chamber is a chamber producing another pressing force that counteracts at least a portion of the
Pressure chamber communication capable of controlling the flow rate of oil from the pressure chamber toward the control flow path whose flow rate is to be controlled when the spool main body moves from the other side to the one side in response to the driving force of a solenoid. A flow path and
a casing having a pressure source port communicating with a pressure source flow path and accommodating the spool;
a poppet housed in the casing and closing and opening the pressure source port;
Flow control valve with.