JP2016070238A - Solenoid pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To simplify a constitution by reducing the number of components, and to miniaturize a solenoid pump while reducing a volume of a pressure chamber.SOLUTION: A solenoid pump 40 is applied to a brake hydraulic pressure control device of a bar handle vehicle such as a motor cycle. In the solenoid pump 40, a pump housing 41 is composed of a fixed core 41B, and an inserting portion 41A. A discharge valve 80 is disposed at a movable core 43 side of a pressure chamber 60, and the inside of a pipe member 42 accommodating the movable core 43 is communicated to a discharge passage 62. The discharge valve 80 is a cup seal 80 having an U-shaped cross-sectional shape and capable of being slidably kept into contact with an outer peripheral face 53 of a piston 51, and its opening portion 81 is disposed at a movable core 43 side.EFFECT: The number of components can be reduced by dispensing with a seal member and a ring member for sealing between the pump housing and the piston.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a solenoid pump including a piston that slides in response to movement of a movable core within a pump housing.

  For example, some automobiles, motorcycles, and the like include a hydraulic brake, and a brake hydraulic pressure control device that optimizes the braking of the hydraulic brake is put into practical use. The brake fluid pressure control device has a pump that increases the hydraulic fluid of the brake. As such a pump, a solenoid pump is known in which a piston in a pump housing is slid by a solenoid to increase or decrease the volume of a pressure chamber (see, for example, Patent Document 1 (FIG. 1)).

  The solenoid pump (10) of this Patent Document 1 (the numbers in parentheses indicate the symbols described in Patent Document 1. The same applies hereinafter). The pump housing (fixed core) (11) and the pump housing (11) A movable core (13) provided movably with respect to the coil, a coil (16) for moving the movable core (13) toward the fixed core (11) by electromagnetic force, and a pressure formed on the pump housing (11) A suction valve (30) and a discharge valve (40) for controlling the inflow and outflow of the hydraulic fluid to and from the chamber (120), and a piston (14) for increasing and decreasing the volume of the pressure chamber (120) are provided.

  In the solenoid pump (10), a seal member (111a) is disposed, and an area closer to the armature chamber (movable core (13)) than the seal member (111a) communicates with the atmosphere. As described above, the technique disclosed in Patent Document 1 requires the seal member (111a) as described above and the ring member (111b) for holding the seal member (111a), which increases the number of components.

  In the technique of Patent Document 1, one of the suction valve (30) and the discharge valve (40) is disposed on the inner periphery of the cylinder member (21), and the other is disposed on the outer periphery of the cylinder member (21). Therefore, the size in the radial direction is increased. Furthermore, since the passage (14a) is formed in the piston (14) and communicates with the space (S1) through the passage (14a), the volume of the pressure chamber (120) is also increased.

A solenoid pump using an armature chamber as a liquid chamber is also known (see, for example, Patent Document 2 (FIG. 1)).
In the technique of Patent Document 2, the communication hole (56) of the rod (48) (the English letters and numbers with parentheses indicate the symbols described in Patent Document 2. The same applies hereinafter) and the communication hole of the movable core (31). (53) connects the suction passage (45) and the armature chamber. However, in the technique of Patent Document 2, since the plunger (9) has a cylindrical shape and the communication path (14) is formed therein, the size of the plunger (9) is increased, and the solenoid pump is reduced in size. It is difficult to plan.

Japanese Patent No. 5175809 JP 2000-45932 A

  It is an object of the present invention to reduce the number of parts to make the structure simple and to reduce the size of the solenoid pump while reducing the volume of the pressure chamber.

  In the invention according to claim 1, a fixed core, a movable core provided so as to be movable with respect to the fixed core, a coil for moving the movable core toward the fixed core, a cylindrical pump housing, A pressure chamber formed in the pump housing, a suction valve that opens when the hydraulic fluid is sucked into the pressure chamber, a discharge valve that opens when the hydraulic fluid is discharged from the pressure chamber, and the movable in the pump housing A solenoid pump that includes a piston that slides in accordance with the movement of the core and that increases or decreases the volume of the pressure chamber, and wherein the suction valve and the discharge valve are disposed at both ends of the piston axial direction across the pressure chamber. The discharge valve is disposed on the movable core side of the pressure chamber, the inside of the pipe member that accommodates the movable core communicates with the discharge path, and the discharge valve is an outer peripheral surface of the piston. A cup seal having a U-shaped cross section that is slidably contacted, and is disposed with the opening portion facing the movable core, and is discharged from the pressure chamber to the discharge path along the outer peripheral surface of the piston. It is a valve that allows or shuts off the flow of air.

  In the invention according to claim 2, a fixed core, a movable core provided to be movable with respect to the fixed core, a coil for moving the movable core to the fixed core side, a cylindrical pump housing, A pressure chamber formed in the pump housing, a suction valve that opens when the hydraulic fluid is sucked into the pressure chamber, a discharge valve that opens when the hydraulic fluid is discharged from the pressure chamber, and the movable in the pump housing A solenoid pump that includes a piston that slides in accordance with the movement of the core and that increases or decreases the volume of the pressure chamber, and wherein the suction valve and the discharge valve are disposed at both ends of the piston axial direction across the pressure chamber. The suction valve is disposed on the movable core side of the pressure chamber, and the inside of a pipe member that accommodates the movable core communicates with a suction path, and the suction valve is an outer peripheral surface of the piston. A cup seal having a U-shaped cross section that is slidably contacted, and is disposed with an opening opposite to the movable core, and is sucked into the pressure chamber from the suction path along the outer peripheral surface of the piston. It is a valve that allows or shuts off the flow of hydraulic fluid.

  The invention according to claim 3 is characterized in that the suction valve or the discharge valve disposed on the opposite side of the movable core in the pressure chamber is a leaf spring valve.

  In the invention which concerns on Claim 4, a leaf | plate spring valve is connected to a part of this main-body part, and is arrange | positioned at the inner peripheral side of a main-body part, and the valve body which can move to a piston axial direction, A valve seat member on which the valve body is seated is provided, and the valve body is biased by the valve seat member by being inclined toward the valve seat member in a state before assembly.

  In the invention which concerns on Claim 5, it is further provided with the cylindrical cylinder member, The suction valve or discharge valve arrange | positioned on the opposite side of a movable core is provided in the inner peripheral part of a cylinder member, and a cylinder member is the one end part. Is press-fitted into the inner periphery of the pump housing.

  The invention according to claim 6 is characterized in that the cup seal is held between the axial end of the cylinder member and the pump housing.

In the invention which concerns on Claim 1, the piston which slides according to a movement of a movable core is provided in the pump housing. Since the inside of the pipe member communicates with the discharge passage, a seal member and a ring member for sealing between the pump housing and the piston as in Patent Document 1 are unnecessary, and the number of parts can be reduced.
Furthermore, the discharge valve is a cup seal having a U-shaped cross section that is slidably contacted with the outer peripheral surface of the piston, and is disposed with the opening portion facing the movable core, and discharges from the pressure chamber along the outer peripheral surface of the piston. Since the valve permits or blocks the flow of the hydraulic fluid discharged to the passage, the configuration can be simplified, and the intake valve and the discharge valve can be arranged in the axial direction while suppressing the size in the axial direction.

Furthermore, since it is not necessary to provide a communication hole as in Patent Document 2 inside the piston, the diameter of the piston can be reduced and the piston can be downsized. As a result, it is possible to reduce the size of the solenoid pump that is a plunger pump.
Furthermore, the volume of the pressure chamber can be reduced by arranging the suction valve and the discharge valve in the axial direction. For this reason, the compression ratio is increased and the pump efficiency can be increased.

In the invention which concerns on Claim 2, the piston which slides according to a movement of a movable core is provided in a pump housing, and a suction valve is arrange | positioned at the movable core side of a pressure chamber. Since the inside of the pipe member communicates with the suction passage, a seal member and a ring member for sealing between the pump housing and the piston as in Patent Document 1 are unnecessary, and the number of parts can be reduced.
Further, the suction valve is a cup seal having a U-shaped cross section that is in slidable contact with the outer peripheral surface of the piston, and is disposed with the opening portion on the side opposite to the movable core, and is disposed along the outer peripheral surface of the piston from the suction path. Since the valve allows or blocks the flow of the hydraulic fluid to the pressure chamber, a simple configuration can be achieved, and the intake valve and the discharge valve can be arranged in the axial direction while suppressing the size in the axial direction.

Furthermore, since it is not necessary to provide a communication hole as in Patent Document 2 inside the piston, the diameter of the piston can be reduced and the piston can be downsized. As a result, it is possible to reduce the size of the solenoid pump that is a plunger pump.
Furthermore, the volume of the pressure chamber can be reduced by arranging the suction valve and the discharge valve in the axial direction. For this reason, the compression ratio is increased and the pump efficiency can be increased.

  In the invention according to claim 3, since the suction valve or the discharge valve arranged on the non-movable core side of the pressure chamber is a leaf spring valve, the other valve can also have a simple configuration, and the axial direction The size can be further suppressed.

  In the invention which concerns on Claim 4, a leaf | plate spring valve is connected to a part of this main-body part, and is arrange | positioned at the inner peripheral side of a main-body part, and the valve body which can move to a piston axial direction. Prepare. Since the valve body is biased by the valve seat member by inclining to the valve seat member side before assembly, the sealing performance of the leaf spring valve can be improved with a simple configuration.

  In the invention according to claim 5, since the cylinder member provided with the suction valve or the discharge valve is press-fitted and fixed to the inner periphery of the pump housing, it can be easily assembled.

  In the invention according to claim 6, the cup seal is held between the axial end of the cylinder member and the pump housing. For example, by disposing a cup seal on the inner periphery of the pump housing and press-fitting a cylinder member into the inner periphery of the pump housing, the cup seal can be positioned and assembled, and assemblability is improved.

FIG. 3 is a hydraulic circuit diagram of a brake hydraulic pressure control device employing a solenoid pump according to the present invention. 1 is a cross-sectional view of a solenoid pump according to Embodiment 1. FIG. It is a disassembled perspective view of the solenoid pump shown in FIG. 6 is a cross-sectional view of a solenoid pump according to Embodiment 2. FIG. It is a disassembled perspective view of the solenoid pump shown in FIG. FIG. 6 is a sectional view taken along line 6-6 of FIG. FIG. 7 is a cross-sectional view taken along line 7-7 in FIG. 6. 6 is a sectional view of a solenoid pump according to Embodiment 3. FIG. It is a disassembled perspective view of the solenoid pump shown in FIG. 6 is a cross-sectional view of a solenoid pump according to Embodiment 4. FIG. It is a disassembled perspective view of the solenoid pump shown in FIG. 12 is a sectional view taken along line 12-12 of FIG. FIG. 13 is a sectional view taken along line 13-13 of FIG.

  Embodiments of the present invention will be described below with reference to the accompanying drawings. The drawings are viewed in the direction of the reference numerals.

First, a hydraulic fluid circuit of a brake hydraulic pressure control device 10 for a bar handle vehicle to which a solenoid pump according to an embodiment of the present invention is applied will be described.
As shown in FIG. 1, the brake hydraulic pressure control device 10 is suitably employed in a bar handle type vehicle such as a motorcycle equipped with a hydraulic brake and an all-terrain vehicle (ATV). The solenoid pump according to the embodiment of the present invention can also be applied to a brake fluid pressure control device for a four-wheeled vehicle. Hereinafter, the brake fluid pressure control device 10 for the front wheels of the motorcycle will be described. The brake hydraulic pressure control device 10 includes a brake system 20 for the front wheels, and can control the braking force applied to the wheel brakes 11 provided on the front wheels by the control device 12, thereby enabling antilock brake control of the wheel brakes 11. To do.

  The brake fluid pressure control device 10 includes a brake operator 14 provided on the bar handle 13, a master cylinder 15 that is activated by the operation of the brake operator 14, and a reservoir 16 that stores hydraulic fluid to be sent to the master cylinder 15. The brake system 20 transmits the hydraulic pressure from the master cylinder 15 to the wheel brake 11, and the control device 12 controls the braking force applied to the wheel brake 11.

  The brake system 20 brakes the wheel brake 11 by operating the brake operator 14. The brake system 20 has a main flow path from the inlet port 21 to the outlet port 22 that leads to the master cylinder 15, and a subport that leads directly from the main flow path to the reservoir 16. 23 sub-flow paths are provided. The master cylinder 15 and the inlet port 21 are connected by a first pipe 24, the outlet port 22 and the wheel brake 11 are connected by a second pipe 25, and the sub-port 23 and the reservoir 16 are connected by a third pipe. 26.

  The master cylinder 15 has a cylinder to which a reservoir 16 for storing hydraulic fluid (brake fluid) is connected, and the hydraulic fluid is slid in the cylinder axial direction by the operation of the brake operator 14 in the cylinder. An outflowing piston is provided.

  The brake system 20 includes an inlet valve 31, an outlet valve 32, and a solenoid pump 40. The inlet valve 31 and the outlet valve 32 are electromagnetic valves, the opening / closing of which is controlled by the control device 12, and the operation / stop of the solenoid pump 40 is also controlled by the control device 12.

  A flow path (oil path) from the inlet port 21 to the inlet valve 31 is an output hydraulic pressure path 33, and a flow path from the inlet valve 31 to the outlet port 22 is a wheel hydraulic pressure path 34. A flow path from the first branch portion 34a of the wheel hydraulic pressure path 34 to the outlet valve 32 is a branch path 35, and a flow path from the outlet valve 32 to the second branch section 36a in the middle of the subport 23 is an open path 36. A flow path from the second branch part 36 a to the subport 23 is referred to as a shared path 37. A flow path from the second branch part 36 a to the solenoid pump 40 is referred to as a suction hydraulic pressure path 38, and a flow path from the solenoid pump 40 to the first branch part 34 a is referred to as a discharge hydraulic pressure path 39.

  The brake fluid pressure control device 10 has a function of switching between a normal state, a pressure-reducing state during ABS control (anti-lock brake control), a holding state during ABS control, or a pressure-increasing state during ABS control. In the normal state, the output hydraulic pressure path 33 and the wheel hydraulic pressure path 34 are communicated (the inlet valve 31 is opened), and the branch path 35 and the open path 36 are blocked (the outlet valve 32 is closed). State. In the depressurized state during the ABS control, the output hydraulic pressure path 33 and the wheel hydraulic pressure path 34 are blocked (the inlet valve 31 is closed), and the branch path 35 and the open path 36 are communicated (the outlet valve 32 is opened). ). In the holding state during ABS control or the pressure increasing state during ABS control, the output hydraulic pressure path 33 and the wheel hydraulic pressure path 34 and the branch path 35 and the open path 36 are blocked (inlet valve 31 and outlet valve 36, respectively). The valve 32 is closed).

  The inlet valve 31 is a normally open type electromagnetic valve provided between the output hydraulic pressure passage 33 and the wheel hydraulic pressure passage 34. The inlet valve 31 is open in a normal state, thereby allowing the hydraulic fluid pressure from the master cylinder 15 to be transmitted from the output hydraulic pressure passage 33 to the wheel brake 11 via the wheel hydraulic pressure passage 34. . Further, the inlet valve 31 is closed by a signal from the control device 12 when the front wheel is about to be locked, and the hydraulic fluid pressure from the master cylinder 15 is transferred from the output hydraulic pressure passage 33 via the wheel hydraulic pressure passage 34 to the wheel brake 11. It is blocked from being transmitted to.

  The outlet valve 32 is a normally closed electromagnetic valve provided between the wheel hydraulic pressure path 34 and the open path 36 via the branch path 35. The outlet valve 32 is closed in a normal state. The outlet valve 32 is released by a signal from the control device 12 when the front wheel is about to be locked, and releases the hydraulic fluid pressure acting on the wheel brake 11 from the wheel hydraulic pressure passage 34 to the release passage 36 via the branch passage 35. Furthermore, the hydraulic fluid released to the open path 36 temporarily flows into the reservoir 16 through the dual-purpose path 37. In this way, the pressure is reduced during ABS control.

  The solenoid pump 40 is provided between the suction fluid pressure passage 38 and the discharge fluid pressure passage 39, and is operated by the movable core 43, the coil 44 (see FIG. 2), etc. The hydraulic fluid stored in the reservoir 16 is sucked through the passage 38 and discharged to the discharge hydraulic pressure passage 39. For this reason, the hydraulic fluid pressure can be increased with respect to the wheel brake 11. The solenoid pump 40 operates in a pressure-increasing state during ABS control by a signal from the control device 12. When the solenoid pump 40 is in operation (in a pressure-increasing state), the control device 12 closes the inlet valve 31 and the outlet valve 32, and between the output hydraulic pressure path 33 and the wheel hydraulic pressure path 34, the branch path 35, The connection with the open passage 36 is blocked, and the hydraulic fluid from the discharge hydraulic pressure passage 39 flows into the wheel hydraulic pressure passage 34.

  The reservoir 16 sends to the tank for storing the working fluid for the master cylinder 15, the tank for releasing the working fluid from the wheel fluid pressure passage 34 in the pressure-reduced state during ABS control, and the solenoid pump in the pressure-increasing state during ABS control. It also serves as a tank for storing hydraulic fluid.

  The dual-purpose path 37 is a flow path for sending hydraulic fluid from the wheel hydraulic pressure path 34 in a reduced pressure state during ABS control to the reservoir 16, and a flow path for sending hydraulic fluid from the reservoir 16 in a pressure increase state during ABS control to the solenoid pump. Doubles as The control device 12 controls each device of the brake fluid pressure control device 12 based on measurement values from a front wheel speed sensor (not shown).

  In the embodiment, the hydraulic circuit described above is used. However, the present invention is not limited to this, and a reservoir for the master cylinder, a reservoir for releasing the hydraulic fluid from the wheel hydraulic pressure passage 34 and sending the hydraulic fluid to the solenoid pump 40, May be a separate hydraulic circuit, and other forms may be used as long as the hydraulic circuit incorporates the solenoid pump 40.

Next, normal brake control by the brake fluid pressure control device 10 will be described.
In normal brake control, the brake system 20 is in a state where the flow path from the master cylinder 15 to the wheel brake 11 is communicated via the output hydraulic pressure path 33, the inlet valve 31, and the wheel hydraulic pressure path 34. When the brake operation element 14 is operated, the working hydraulic pressure acts on the wheel brake 11 via the output hydraulic pressure path 33, the inlet valve 31, and the wheel hydraulic pressure path 34, and the front wheels can be braked. When the brake operator 14 is returned, the hydraulic fluid that has acted on the wheel brake 11 is returned to the master cylinder 15 via the wheel hydraulic pressure passage 34, the inlet valve 31, and the output hydraulic pressure passage 33.

Next, ABS control by the brake fluid pressure control device 10 will be described.
The ABS control is executed when the front wheels are likely to be locked, and controls the inlet valve 31, the outlet valve 32 and the solenoid pump 40 to reduce, increase and maintain the hydraulic fluid pressure acting on the wheel brake 11. Is executed. Based on the measured value from a wheel speed sensor (not shown) for the front wheels, the controller 12 controls the pressure reduction, pressure increase and holding.

  In the reduced pressure state, the inlet valve 31 is closed to shut off the output hydraulic pressure path 33 and the wheel hydraulic pressure path 34, and the outlet valve 32 is opened to open the gap between the wheel hydraulic pressure path 34 and the release path 36. Then, the solenoid pump 40 is stopped. The hydraulic fluid in the wheel hydraulic pressure passage 34 communicating with the wheel brake 11 flows into the reservoir 16 through the branch passage 35, the release passage 36, and the dual-use passage 37, and the hydraulic fluid pressure acting on the wheel brake 11 is reduced. .

  In the holding state, when the inlet valve 31 is closed, the output hydraulic pressure path 33 and the wheel hydraulic pressure path 34 are blocked, and when the outlet valve 32 is closed, the wheel hydraulic pressure path 34 (branch path 35) and the open path 36 are closed. And the solenoid pump 40 is stopped. The hydraulic fluid is confined in the flow path closed by the wheel brake 11, the inlet valve 31, the outlet valve 32, and the solenoid pump 40, and the hydraulic fluid acting on the wheel brake 11 is kept constant.

  In the pressure increasing state, the inlet valve 31 is closed to shut off the output hydraulic pressure path 33 and the wheel hydraulic pressure path 34, and the outlet valve 32 is closed to close the gap between the wheel hydraulic pressure path 34 and the open path 36. The solenoid pump 40 is activated by being shut off. By the operation of the solenoid pump 40, the working fluid is sucked from the reservoir 16 through the dual-purpose passage 37 and the suction fluid pressure passage 38, and enters the flow path closed by the wheel brake 11, the inlet valve 31, the outlet valve 32, and the solenoid pump 40. Then, the hydraulic fluid is sent from the discharge hydraulic pressure passage 39, the pressure in the flow passage is increased, and the wheel brake 11 is operated.

Next, the solenoid pump 40 will be described. For convenience, in the solenoid pump 40, the side where the pump housing 41 is inserted into the base body 90 is referred to as “one end side”, and the side where the movable core 43 is disposed is referred to as “the other end side”.
As shown in FIGS. 2 and 3, the solenoid pump 40 includes a cylindrical pump housing 41 having at least a part of a fixed core 41 </ b> B, and a bottomed cylindrical shape fixed to the other end of the pump housing 41. A pipe member 42 and a piston 51 inserted through a through hole 45 penetrating the pump housing 41 are provided.

  The pump housing 41 is made of a magnetic material that is an iron-based material, and a through hole 45 through which the piston 51 is inserted is formed along the axis of the pump housing 41. The pump housing 41 has an insertion portion 41A on one end side and a body portion 41B which is a fixed core on the other end side, and a cylindrical cylinder member 46 is provided at the end portion on one end side.

  A pressure chamber 60 is formed in the pump housing 41 and the cylinder member 46. The solenoid pump 40 is disposed so as to be able to advance and retreat in the pipe member 42, and the movable core 43 that presses the piston 51 toward the pressure chamber 60, the coil 44 that is externally mounted on the pump housing 41 and the pipe member 42, and pressure of the hydraulic fluid. A suction valve 70 that opens when sucking into the chamber 60 and a discharge valve 80 that opens when hydraulic fluid is discharged from the pressure chamber 60 are provided. The suction valve 70 and the discharge valve 80 are disposed at both ends of the piston axial direction with the pressure chamber 60 interposed therebetween. The coil 44 is an electromagnetic coil.

  The fixed core 41B on the other end side of the pump housing 41 has a cylindrical shape. The insertion portion 41A on one end side of the pump housing 41 is inserted in a liquid-tight manner through a sealing material 92 into a mounting hole 91 formed in a base body 90 serving as a base. A bottomed tubular pipe member 42 is welded to the outer periphery of the fixed core 41B, for example, and the space between the fixed core 41B and the pipe member 42 is sealed. For this reason, the space 42a inside the pipe member 42 is liquid-tight. The fixing method is not limited to welding, and may be press-fitting or caulking.

  The insertion portion 41A includes a large-diameter hole 45a formed at the end on one end side, a small-diameter hole 45b formed continuously from the large-diameter hole 45a and having a smaller diameter than the large-diameter hole 45a, and an insertion portion from the small-diameter hole 45b. And a discharge passage 62 communicating with the outside of 41A. The through hole 45 has a smaller diameter than the small diameter hole 45 b, and the discharge passage 62 extends in the vertical direction with respect to the through hole 45. The at least one discharge path 62 is positioned so as to be continuous with the discharge hydraulic pressure path 39 of the base body 90, and communicates the discharge hydraulic pressure path 39 formed on the side wall of the mounting hole 91 of the base body 90 with the pressure chamber 60. For this reason, hydraulic fluid can be poured smoothly.

  A space 42 a inside the pipe member 42 that accommodates the movable core 43 communicates with the discharge path 62. Since the inside of the pipe member 42 communicates with the discharge passage 62, a seal member and a ring member for sealing between the pump housing 41 and the piston 51 as in Patent Document 1 are unnecessary, and the number of parts can be reduced.

  The cylinder member 46 is a valve arrangement in which a convex portion 46a formed so as to protrude to an end portion on the other end side, a pressure chamber 60 formed on the other end side, and a suction valve 70 formed on one end side are arranged. Part 46b.

  The convex portion 46 a is press-fitted into a large-diameter hole 45 a that is the inner periphery of the pump housing 41. The cylinder member 46 can be easily assembled because the convex portion 46a, which is one end thereof, is press-fitted and fixed to the inner periphery of the pump housing 41. Since the cylinder member 46 is formed of a non-magnetic material, an inexpensive material can be used, and the cost of parts can be reduced. In the embodiment, the cylinder member 46 is a non-magnetic material. However, the present invention is not limited to this, and the cylinder member 46 may be formed of a magnetic material that is an iron-based material.

  A discharge valve 80 is disposed on the movable core 43 side of the pressure chamber 60. The discharge valve 80 is a cup seal 80 having a U-shaped cross-section provided so as to be slidable on the outer peripheral surface 53 of the main body 52 of the piston 51, and an opening 81 that is an end portion on the inner peripheral side of the cup seal 80. It is arranged on the movable core 43 side. Therefore, the discharge valve 80 allows or blocks the flow of the hydraulic fluid discharged from the pressure chamber 60 to the discharge path 62 along the outer peripheral surface 53 of the piston 51. Since the discharge valve 80 is the cup seal 80, it can have a simple configuration, and the suction valve 70 and the discharge valve 80 can be arranged in the axial direction while suppressing the size in the axial direction. By disposing the suction valve 70 and the discharge valve 80 in the axial direction, the volume of the pressure chamber 60 can be reduced. For this reason, the compression ratio is increased and the pump efficiency can be increased.

  Furthermore, since it is not necessary to provide a communication hole in the piston 51, the diameter of the piston 51 can be reduced and the piston 51 can be downsized. As a result, the solenoid pump 40 that is a plunger pump can be downsized.

  The cup seal 80 is held between the axial end 46 c of the cylinder member 46 and the pump housing 41 in the large-diameter hole 45 a of the pump housing 41. Further, the outer peripheral surface of the cup seal 80 is in contact with the inner peripheral surface of the large diameter hole 45 a, and the inner peripheral end of the cup seal 80 is in contact with the outer peripheral surface 53 of the piston 51. By disposing the cup seal 80 on the inner peripheral portion of the pump housing 41 and press-fitting the cylinder member 46 into the inner periphery of the pump housing 41, the cup seal 80 can be positioned and assembled, thereby improving the assemblability. it can.

  The insertion portion 41 </ b> A of the pump housing 41 is fixed to the opening of the attachment hole 91 by a ring-shaped retaining member 93. As a result, both the pump housing 41 and the cylinder member 46 are fixed to the mounting hole 91. In the embodiment, the pump housing 41 is fixed to the mounting hole 91 by the retaining member 93. However, the present invention is not limited to this, and the pump housing 41 may be fixed by press fitting or caulking.

  The pressure chamber 60 is disposed between the pump housing 41 and the cylinder member 46, and is formed by partitioning the space inside the cylinder member 46 by the suction valve 70, the discharge valve 80 and the piston 51.

  A return spring 64 is disposed in the pressure chamber 60. The return spring 64 is a coil spring that biases the piston 51 toward the movable core 43. One end of the return spring 64 is received by a receiving portion 65 formed at the bottom of the pressure chamber 60 of the cylinder member 46, and the other end is the piston 51. Received at the tip.

  The piston 51 has a main body 52 that is movably inserted into the through hole 45, and a spring seat 54 that is formed at the front end of the main body 52 and supports the return spring 64. Is configured to appear and disappear with respect to the pressure chamber 60. That is, the volume of the pressure chamber 60 is reduced when the piston 51 slides to one end side and one end portion of the piston 51 projects into the pressure chamber 60, and the piston 51 slides to the other end side. The volume increases as one end of the sunk from the pressure chamber 60. Note that the piston 51 does not have an opening serving as a passage for the hydraulic fluid in a portion facing the pressure chamber 60, and the hydraulic fluid does not flow through the piston 51.

  The valve arrangement portion 46 b opens toward the suction fluid pressure path 38 formed on the bottom of the mounting hole 91 of the base body 90 on one end side of the cylinder member 46. A suction valve 70 is provided in the valve arrangement portion 46 b, and a filter 61 is provided on one end side of the suction valve 70.

  The suction valve 70 is a one-way valve that opens and closes the flow path between the suction fluid pressure path 38 and the pressure chamber 60, and is arranged coaxially with the axis of the piston 51. The intake valve 70 is provided so as to be movable between a retainer 71 provided on the other end side of the valve arrangement portion 46b, a valve seat member 72 provided on one end side of the retainer 71, and the retainer 71 and the valve seat member 72. And a spherical valve body 73. The retainer 71 has a cup shape and a fluid passage hole 74 through which hydraulic fluid passes. The end of the retainer 71 is in contact with the stepped portion 46d of the valve placement portion 46b.

  As the piston 51 moves in the direction of reducing the volume of the pressure chamber 60 (the direction toward one end side), the pressure chamber 60 is pressurized. For this reason, the valve body 73 is seated on the valve seat member 72 and is closed to prevent the valve body 73 from flowing out from the pressure chamber 60 to the suction fluid pressure path 38. On the other hand, as the piston 51 moves in the direction of increasing the volume of the pressure chamber 60 (the direction toward the other end side), the pressure chamber 60 is depressurized. For this reason, the valve body 73 opens away from the valve seat member 72, and the working fluid flows into the pressure chamber 60 from the suction fluid pressure path 38.

  The return pin 64 has a biasing force that biases the piston 51 to the non-actuated position when it is not actuated. For this reason, when the coil 44, which will be described later, is demagnetized, the return force of the return spring 64 causes the piston 51 to slide in the direction (movable core 43 side) in which the piston 51 sinks.

  In the discharge valve 80, the cup seal 80 is an elastic member, and the end portion of the opening 81 is urged against the outer peripheral surface 53 of the piston 51 by the elastic force. As the piston 51 moves in the direction of reducing the volume of the pressure chamber 60 (the direction toward one end side), the pressure chamber 60 is pressurized. For this reason, in the discharge valve 80, the end of the opening 81 is opened away from the outer peripheral surface 53 of the piston 51, and the working fluid flows out from the pressure chamber 60 to the discharge hydraulic pressure passage 39. Further, as the piston 51 moves in the direction in which the volume of the pressure chamber 60 increases (the direction toward the other end side), the pressure chamber 60 is depressurized. Therefore, the discharge valve 80 closes with the end of the opening 81 abutting against the outer peripheral surface 53 of the piston 51, thereby preventing hydraulic fluid from flowing into the pressure chamber 60 from the discharge hydraulic pressure passage 39. .

  The movable core 43 is made of a magnetic material, and moves in the axial direction inside the pipe member 42 in a state where one end face thereof is in contact with the other end of the piston 51. The movable core 43 is attracted to the pump housing 41 by exciting the coil 14 and moves to one end side against the urging force of the return spring 64. When the movable core 43 moves to one end side, the piston 51 is also pushed to one end side, and one end portion of the piston 51 protrudes into the pressure chamber 60. As a result, the volume of the pressure chamber 60 is reduced and the pressure chamber 60 is increased in pressure.

  The coil 44 is mounted with a resin bobbin 44a, and a yoke 44b that forms a magnetic path is provided outside the bobbin 44a.

Next, the operation of the solenoid pump 40 described above will be described.
As shown in FIG. 2, when the coil 44 is excited, the movable core 43 is drawn toward one end side. Pressed by the movable core 43, the piston 51 moves to the pressure chamber 60 side. As the volume of the pressure chamber 60 is reduced, the pressure chamber 60 is increased in pressure and the discharge valve 80 is opened. The hydraulic fluid in the pressure chamber 60 flows to the discharge valve 80 and further flows out from the discharge path 62 to the discharge hydraulic pressure path 39.

  Subsequently, when the coil 44 is demagnetized, the piston 51 and the movable core 43 are moved to the other end side by the biasing force of the return spring 64. As the volume of the pressure chamber 60 increases, the pressure chamber 60 is depressurized and the discharge valve 80 is closed. When the pressure chamber 60 is further depressurized, the valve body 73 moves to the pressure chamber 60 side, and the suction valve 70 is opened. The working fluid flows from the suction fluid pressure path 38 to the suction valve 70 and is further sucked into the pressure chamber 60. Subsequently, the coil 44 is excited again, the piston 51 moves to the pressure chamber 60 side, the pressure chamber 60 is increased, the valve body 73 moves to one end side, and the suction valve 70 is closed. By repeating such an operation, the working fluid is continuously sucked and discharged.

Next, a second embodiment of the present invention will be described with reference to the drawings. The same components as those shown in FIGS. 2 and 3 are denoted by the same reference numerals, and detailed description thereof is omitted.
As shown in FIGS. 4 and 5, the solenoid pump 40 includes a suction valve 100 in the valve arrangement portion 46 b of the cylinder member 46. The suction valve 100 is a leaf spring valve 100. Since the suction valve 100 is the leaf spring valve 100, the size in the axial direction can be further suppressed, and the solenoid pump 40 can be reduced in size.

  As shown in FIGS. 5 and 6, the leaf spring valve 100 is connected to an annular main body 101 and a part of the main body 101 via a connection portion 102 and arranged on the inner peripheral side of the main body 101. And a substantially circular valve body 103 movable in the piston axial direction, and a valve seat member 104 on which the valve body 103 is seated.

Next, the operation of the solenoid pump 40 of the second embodiment will be described.
As shown in FIG. 7A, the valve body 103 is inclined toward the valve seat member 104 in a state before assembly. By assembling the valve body 103 to the cylinder member 46, as shown in FIG. 7B, the valve body 103 is urged and seated on the valve seat member 104 by an elastic force. When the pressure chamber 60 is depressurized, the valve body 103 moves toward the valve opening space 105 as shown by an arrow, and the suction valve 100 is opened. As a result, the hydraulic fluid flows into the pressure chamber 60.

  Since the valve body 103 is biased by the valve seat member 104 by inclining toward the valve seat member 104 before assembly, the sealing performance of the leaf spring valve 100, which is the suction valve 100, is simplified. Can be improved.

Next, Embodiment 3 of the present invention will be described with reference to the drawings. The same components as those shown in FIGS. 2 and 3 are denoted by the same reference numerals, and detailed description thereof is omitted.
As shown in FIGS. 8 and 9, in the solenoid pump 40, the suction valve 110 is disposed on the movable core 43 side of the pressure chamber 60. A space 42 a inside the pipe member 42 that accommodates the movable core 43 communicates with the suction path 63. Since the inside of the pipe member 42 communicates with the suction passage 63, a seal member and a ring member for sealing between the pump housing 41 and the piston 51 as in Patent Document 1 are unnecessary, and the number of parts can be reduced.

  The suction valve 110 includes a cup seal 110 having a U-shaped cross section that is slidably contacted with the outer peripheral surface 53 of the piston 51, and is a cup seal 110 having a U-shaped cross section. The opening 111 is arranged on the opposite side of the movable core 43. For this reason, the suction valve 110 allows or blocks the flow of hydraulic fluid sucked from the suction passage 63 into the pressure chamber 60 along the outer peripheral surface 53 of the piston 51. Since the suction valve 110 is the cup seal 110, it can have a simple configuration, and the suction valve 110 and the discharge valve 120 can be arranged in the axial direction while suppressing the size in the axial direction. By disposing the suction valve 110 and the discharge valve 120 in the axial direction, the volume of the pressure chamber 60 can be reduced. For this reason, the compression ratio is increased and the pump efficiency can be increased.

  In the solenoid pump 40, the discharge valve 120 is disposed on the side of the pressure chamber 60 opposite to the movable core 43. The discharge valve 120 has a retainer 121 provided on the other end side of the valve arrangement portion 46b, a valve seat 122 formed on the cylinder member 46, and a spherical shape provided movably between the retainer 121 and the valve seat 122. The valve body 123 includes a valve spring 124 that is provided inside the retainer 121 and biases the valve body 123 toward the valve seat 122. The retainer 121 has a cup shape and is formed with a liquid passage hole 125 through which hydraulic fluid passes. The retainer 121 is press-fitted into the inner periphery of the cylinder member 46.

Next, the operation of the solenoid pump 40 of the third embodiment will be described.
As shown in FIG. 8, when the piston 51 slides to the other end side and one end of the piston 51 is submerged from the pressure chamber 60, the pressure chamber 60 is depressurized and the intake valve 110 is opened. The hydraulic fluid flows from the suction fluid pressure passage 38 to the suction valve 110 through the suction passage 63 and flows into the pressure chamber 60 from between the outer peripheral surface 53 of the piston 51 and the opening 111.

  Subsequently, when the piston 51 moves to the pressure chamber 60 side and the pressure chamber 60 is increased in pressure, the suction valve 110 is closed. Furthermore, the valve body 123 of the discharge valve 120 moves to one end side, and the discharge valve 120 opens. The hydraulic fluid flows from the pressure chamber 60 through the discharge valve 120 to the discharge hydraulic pressure passage 39. By repeating such an operation, the working fluid is continuously sucked and discharged.

  In the solenoid pump 40 of the third embodiment, the working fluid can be flowed in from the vertical direction with respect to the axis of the piston 51, and the working fluid can be flowed out in the axial direction of the piston 51. In other words, even if the arrangement of the suction hydraulic pressure path 38 and the discharge hydraulic pressure path 39 of the base body 90 is different, it can be dealt with, and the degree of freedom of the arrangement of the suction hydraulic pressure path 38 and the discharge hydraulic pressure path 39 can be given. it can.

Next, a fourth embodiment of the present invention will be described with reference to the drawings. In addition, the same code | symbol is attached about the same structure as the structure shown in FIG. 8, FIG. 9, and detailed description is abbreviate | omitted.
As shown in FIGS. 10 and 11, the solenoid pump 40 includes a discharge valve 130 in the valve arrangement portion 46 b of the cylinder member 46. The discharge valve 130 is a leaf spring valve 130. Since the discharge valve 130 is the leaf spring valve 130, the size in the axial direction can be further suppressed, and the solenoid pump 40 can be reduced in size.

  As shown in FIGS. 12 and 13, the leaf spring valve 130 is connected to an annular main body 131 and a part of the main body 131 via a connection portion 132 and arranged on the inner peripheral side of the main body 131. And a substantially circular valve body 133 that is movable in the piston axial direction, and a support member 134 that supports the valve body 133.

Next, the operation of the solenoid pump 40 according to the fourth embodiment will be described.
As shown in FIG. 13A, the valve body 133 is inclined toward the valve seat 136 as a valve seat member in a state before assembly. By assembling the valve body 133 to the cylinder member 46, as shown in FIG. 13B, the valve body 133 is urged and seated on the valve seat 136 by an elastic force. When the pressure chamber 60 is increased in pressure, the valve body 133 moves toward the valve opening space 135 as shown by the arrow, and the suction valve 130 is opened. As a result, the hydraulic fluid flows out from the pressure chamber 60.

  Since the valve body 133 is biased toward the valve seat 136 by inclining toward the valve seat 136 before assembly, the sealing performance of the leaf spring valve 130 as the discharge valve 130 is improved with a simple configuration. Can be made.

In the embodiment, the hydraulic circuit is a circuit sharing the reservoir 16 for the master cylinder 15, the outlet valve 32, and the solenoid pump 40. A circuit in which the reservoir 16 for the outlet valve 32 and the solenoid pump 40 is separated may be used, and if the solenoid pump 40 is incorporated, another hydraulic circuit may be used.
Further, the present invention is not limited to the above-described embodiment, and the volume of the pressure chamber 60, the diameter of the piston 51, and the discharge amount of the piston 51 may be changed as appropriate, and the discharge amount of the hydraulic fluid may be different. There is no problem.
In addition, the valve bodies 103 and 133 of the leaf spring valves 100 and 130 may not be inclined.

  The solenoid pump of the present invention is suitable for a bar handle vehicle.

  DESCRIPTION OF SYMBOLS 10 ... Brake hydraulic pressure control apparatus, 40 ... Solenoid pump, 41 ... Pump housing, 41B ... Fixed core (body | body part), 42 ... Pipe member, 43 ... Movable core, 44 ... Coil, 46 ... Cylinder member, 46c ... Cylinder member 51 ... piston, 53 ... outer peripheral surface, 60 ... pressure chamber, 62 ... discharge passage, 63 ... suction passage, 70 ... suction valve, 80 ... discharge valve (cup seal), 81 ... opening, 100 DESCRIPTION OF SYMBOLS ... Suction valve (plate spring valve), 101 ... Main body part, 103 ... Valve body, 104, Valve seat member, 110 ... Suction valve (cup seal), 111 ... Opening part, 120 ... Discharge valve, 130 ... Discharge valve (plate) Spring valve), 131... Main body, 133... Valve body, 136... Valve seat member (valve seat).

Claims (6)

A fixed core;
A movable core provided movably with respect to the fixed core;
A coil for moving the movable core toward the fixed core;
A cylindrical pump housing;
A pressure chamber formed in the pump housing;
A suction valve that opens when hydraulic fluid is sucked into the pressure chamber;
A discharge valve that opens when hydraulic fluid is discharged from the pressure chamber;
A piston that slides in accordance with the movement of the movable core in the pump housing and increases or decreases the volume of the pressure chamber;
In the solenoid pump in which the suction valve and the discharge valve are disposed at both ends of the piston axial direction across the pressure chamber,
The discharge valve is disposed on the movable core side of the pressure chamber, and the inside of a pipe member that accommodates the movable core communicates with the discharge path.
The discharge valve is a cup seal having a U-shaped cross section that is slidably contacted with the outer peripheral surface of the piston, and is disposed with an opening portion on the movable core side, and the pressure along the outer peripheral surface of the piston A solenoid pump characterized by being a valve for allowing or blocking a flow of hydraulic fluid discharged from a chamber to the discharge passage. A fixed core;
A movable core provided movably with respect to the fixed core;
A coil for moving the movable core toward the fixed core;
A cylindrical pump housing;
A pressure chamber formed in the pump housing;
A suction valve that opens when hydraulic fluid is sucked into the pressure chamber;
A discharge valve that opens when hydraulic fluid is discharged from the pressure chamber;
A piston that slides in accordance with the movement of the movable core in the pump housing and increases or decreases the volume of the pressure chamber;
In the solenoid pump in which the suction valve and the discharge valve are disposed at both ends of the piston axial direction across the pressure chamber,
The suction valve is disposed on the movable core side of the pressure chamber, and the inside of a pipe member accommodating the movable core communicates with a suction path;
The suction valve is a cup seal having a U-shaped cross section that is slidably contacted with the outer peripheral surface of the piston, and is disposed with an opening opposite to the movable core, along the outer peripheral surface of the piston. A solenoid pump characterized by being a valve that allows or blocks a flow of hydraulic fluid sucked into the pressure chamber from the suction passage. The solenoid pump according to claim 1 or 2,
The solenoid pump, wherein the suction valve or the discharge valve disposed on the opposite side of the movable core in the pressure chamber is a leaf spring valve. The solenoid pump according to claim 3, wherein
The leaf spring valve is connected to a part of the annular main body, and is disposed on the inner peripheral side of the main body, and is movable in the piston axial direction. Comprising a valve seat member,
The solenoid pump, wherein the valve body is biased by the valve seat member by inclining toward the valve seat member before assembly. The solenoid pump according to any one of claims 1 to 4,
Further comprising a cylindrical cylinder member;
The suction valve or the discharge valve disposed on the opposite side of the movable core is provided on an inner peripheral portion of the cylinder member,
One end of the cylinder member is press-fitted into the inner periphery of the pump housing. The solenoid pump according to claim 5, wherein
The solenoid pump according to claim 1, wherein the cup seal is held between an axial end of the cylinder member and the pump housing.

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