JP5165446B2 - solenoid valve - Google Patents

Description

  The present invention relates to a solenoid valve.

  As this type of electromagnetic valve, the one shown in Patent Document 1 is known. As shown in FIG. 3 of Patent Document 1, the solenoid valve (121) is configured such that the base (fixed iron core 2) in which the guide hole (through hole 21) is formed and the guide hole (through hole 21) are axially arranged. A movable member (valve element 1) capable of reciprocating along the direction, an electromagnetic coil (64) that forms a magnetic field when energized and moves the movable member (valve element 1) according to the energized state, and a movable member Close the open end of the valve body (valve closing body 12 and contact surface 11) provided at one end of the (valve body 1) and the guide hole (through hole 21) on the side where the valve body is provided. A seat having a valve seat (4) that is fixed and that contacts and separates the valve body, and that has an inflow path that opens and closes when the valve body contacts and separates from the valve seat (4); An oil chamber into which oil liquid flows in from the path, and an outflow path that opens in the oil chamber and that is provided in the base body and flows out to the outside. It is an oil chamber and a, a compression coil spring (61) interposed so as to surround the valve body between the seat and the movable member (the valve body 1). The valve body includes a valve body shaft portion (valve closing body 12) protruding in an axial direction at one end of a movable member (valve body 1), and a valve seat ( 4) and an abutting portion (abutting surface 11) that abuts on 4).

In the solenoid valve configured as described above, when the solenoid valve is in an open state (when the valve body is at a position away from the valve seat), the oil liquid passes through the inflow path and flows into the compression coil spring. The oil flows out of the oil chamber from the outflow passage through the clearance of the compression coil spring.
JP 2002-347597 A

  In the electromagnetic valve described in Patent Document 1 described above, a gap is provided in the radial direction between the movable member and the guide hole (through hole 21) in order to ensure smooth reciprocation of the movable member (valve element 1). ing. Therefore, the movable member may be eccentric with the gap as a maximum. When the valve body is separated from the position where the valve body is in contact with the valve seat and the movable member is eccentric, the oil liquid flowing in from the inflow passage flows into the wide gap formed by the eccentricity of the valve body between the inflow passage and the valve body. However, most of the compression coil spring passes through a wide space (opposite to the eccentricity) formed by the eccentricity of the valve body between the valve body and the compression coil spring, and passes through the clearance of the compression coil spring on the wide space side. It flows out from inside. As a result, a portion of the valve body on the wide space side receives a relatively strong pressure due to the oil liquid flowing in the wide space. As a result, the valve body receives not only the pressure of only the axial component but also the pressure of the radial component relatively strongly, so that the smooth movement of the valve body in the axial direction is hindered and the hydraulic pressure may not be adjusted appropriately. .

  The present invention has been made to solve the above-described problems, and an object of the present invention is to appropriately adjust the hydraulic pressure by suppressing the pressure that the valve body receives in the radial direction due to the flow of oil in the electromagnetic valve. .

In order to solve the above problems, the structural feature of the invention according to claim 1 is that a base body in which a guide hole is formed, a movable member capable of reciprocating along the central axis direction in the guide hole, An electromagnetic coil that sometimes forms a magnetic field to move the movable member within the guide hole according to the energized state, a valve body provided at one end of the movable member, and an open end of the guide hole facing the valve body are closed. The seat has a valve seat that contacts and separates from the valve body, and has a first flow path that is opened and closed when the valve body contacts and separates from the valve seat, and a guide hole and a sheet that are formed from the first flow path to the inside. An oil chamber into which the oil liquid flows, a second flow path that opens in the oil chamber and is provided in the base body and from which the oil liquid in the oil chamber flows out, and a valve body between the seat and the movable member in the oil chamber A compression coil spring interposed so as to surround the valve body, the valve body being one of the movable members. A valve body shaft portion that extends in the axial direction and a contact portion that is provided at the tip of the valve body shaft portion and contacts the valve seat, and the valve body shaft portion has a diameter. A concave portion extending from one side of the direction to the other side, which is the opposite side, is formed, and the concave portion is composed of a spiral groove formed in a spiral shape on the outer wall surface of the valve body shaft portion, and the winding direction of the spiral groove The winding direction of the compression coil spring is the same .
The structural feature of the invention according to claim 2 is that a base body in which a guide hole is formed, a movable member capable of reciprocating along the central axis direction in the guide hole, and a magnetic field is formed during energization to form the energization. An electromagnetic coil that moves the movable member in the guide hole according to the state, a valve body provided at one end of the movable member, and a valve that closes the open end of the guide hole on the side facing the valve body so that the valve body contacts and separates A seat having a seat and having a first flow path that is opened and closed when the valve body contacts and separates from the valve seat; and an oil chamber that is formed of a guide hole and a sheet and into which an oil solution flows from the first flow path. A second flow path that opens in the oil chamber and is provided in the base body, and the oil in the oil chamber flows out to the outside, and is interposed between the seat and the movable member in the oil chamber so as to surround the valve body A solenoid valve having a compression coil spring, and the valve element extends in the axial direction at one end of the movable member. The valve body shaft portion and a contact portion provided at the tip of the valve body shaft portion and in contact with the valve seat, and the valve body shaft portion from the one side in the radial direction to the other side A concave portion extending to the side is formed, and the concave portion is configured by a spiral groove formed in a spiral shape on the outer wall surface of the valve body shaft portion, and the groove width of the spiral groove is determined when the electromagnetic valve is in an open state. It is that it is more than the clearance gap between lines of a compression coil spring.

The structural feature of the invention according to claim 3 is that in claim 1 or claim 2 , the angle of the spiral groove is the same as the angle of the winding of the compression coil spring when the solenoid valve is in the open state. It is.

The structural feature of the invention according to claim 4 is that, according to any one of claims 1 to 3 , the pitch of the spiral groove is the same as the pitch of the compression coil spring when the solenoid valve is in the open state. That is.

Structural feature of the invention according to claim 5, in at least one of claims 1 to 4, the spiral groove all the inter-line gap portion of the compression coil spring when the electromagnetic valve is open It is to face in the radial direction over the circumference.

The structural feature of the invention according to claim 6 is that the base body in which the guide hole is formed, the movable member capable of reciprocating along the central axis direction in the guide hole, and a magnetic field is formed during energization to form the energization. An electromagnetic coil that moves the movable member in the guide hole according to the state, a valve body provided at one end of the movable member, and a valve that closes the open end of the guide hole on the side facing the valve body so that the valve body contacts and separates A seat having a seat and having a first flow path that is opened and closed when the valve body contacts and separates from the valve seat; and an oil chamber that is formed of a guide hole and a sheet and into which an oil solution flows from the first flow path. A second flow path that opens in the oil chamber and is provided in the base body, and the oil in the oil chamber flows out to the outside, and is interposed between the seat and the movable member in the oil chamber so as to surround the valve body A solenoid valve having a compression coil spring, and the valve element extends in the axial direction at one end of the movable member. The valve body shaft portion and a contact portion provided at the tip of the valve body shaft portion and in contact with the valve seat, and the valve body shaft portion from the one side in the radial direction to the other side concave portion is formed extending to the side, the recess is composed of mutually parallel plural annular groove formed annularly on the outer wall surface of the valve shaft portion, the pitch of the annular groove on the solenoid valve is opened It is the same as the pitch of the compression coil spring at a certain time.

In the invention according to claim 1 configured as described above, the valve body shaft portion of the valve body is formed with a recess extending from one side in the radial direction to the other side that is the opposite side. When the movable member is decentered at this time, a recess extending from the wide space formed by the decentering of the valve body to the narrow space on the opposite side is provided between the compression coil spring and the valve body shaft portion. Become. As a result, the oil liquid flowing in from the first flow path flows in from a wide gap formed by the eccentricity of the valve body between the first flow path and the valve body, and a part of the oil liquid reaching the wide space is It flows out of the compression coil spring through the gap of the compression coil spring on the wide space side as it is conventionally. In addition to this, another part of the oil that has reached a wide space turns into the narrow space along the recess of the valve body shaft portion, passes through the clearance of the compression coil spring on the narrow space side, and from the inside of the compression coil spring. leak. Therefore, by flowing the oil along the recess, the pressure received by the wide space portion of the valve body is distributed to the opposite side and the pressure is prevented from concentrating on one side, and the valve body receives in the radial direction. By suppressing the pressure, the axial movement of the valve body becomes smoother and the hydraulic pressure can be adjusted appropriately.
Furthermore, since the concave portion is formed of a spiral groove formed in a spiral shape on the outer wall surface of the valve body shaft portion, a spiral groove and a compression coil spring can be obtained by matching the shape of the compression coil spring formed in a spiral shape. A wider gap can be secured. Therefore, a large amount of oil can be flowed from a wide space to a narrow space.
Furthermore, since the winding direction (right or left) of the spiral groove and the winding direction (right or left) of the compression coil spring are the same, a wider gap can be secured between the spiral groove and the compression coil spring (wide flow path). Cross-sectional area can be secured). Therefore, an even larger amount of oil can be allowed to flow from a wide space to a narrow space.
In the invention according to claim 2 configured as described above, the valve body shaft portion of the valve body is formed with a recess extending from one side in the radial direction to the other side which is the opposite side. When the movable member is decentered at this time, a recess extending from the wide space formed by the decentering of the valve body to the narrow space on the opposite side is provided between the compression coil spring and the valve body shaft portion. Become. As a result, the oil liquid flowing in from the first flow path flows in from a wide gap formed by the eccentricity of the valve body between the first flow path and the valve body, and a part of the oil liquid reaching the wide space is It flows out of the compression coil spring through the gap of the compression coil spring on the wide space side as it is conventionally. In addition to this, another part of the oil that has reached a wide space turns into the narrow space along the recess of the valve body shaft portion, passes through the clearance of the compression coil spring on the narrow space side, and from the inside of the compression coil spring. leak. Therefore, by flowing the oil along the recess, the pressure received by the wide space portion of the valve body is distributed to the opposite side and the pressure is prevented from concentrating on one side, and the valve body receives in the radial direction. By suppressing the pressure, the axial movement of the valve body becomes smoother and the hydraulic pressure can be adjusted appropriately.
Furthermore, since the concave portion is formed of a spiral groove formed in a spiral shape on the outer wall surface of the valve body shaft portion, a spiral groove and a compression coil spring can be obtained by matching the shape of the compression coil spring formed in a spiral shape. A wider gap can be secured. Therefore, a large amount of oil can be flowed from a wide space to a narrow space.
Furthermore, since the groove width of the spiral groove is equal to or larger than the clearance between the lines of the compression coil spring when the solenoid valve is in the open state, the clearance between the spiral groove and the compression coil spring can be secured even wider (wide flow). The road cross-sectional area can be secured). Therefore, an even larger amount of oil can be allowed to flow from a wide space to a narrow space.

In the invention according to claim 3 configured as described above, in the invention according to claim 1 or claim 2 , the angle of the spiral groove is the angle of the winding of the compression coil spring when the solenoid valve is in the open state. Therefore, the gap between the spiral groove and the compression coil spring can be further widened (a wide channel cross-sectional area can be secured). Therefore, an even larger amount of oil can be allowed to flow from a wide space to a narrow space.

In the invention according to Claim 4 as constructed above, in the invention according to any one of claims 1 to 3, the compression coil spring when the pitch of the spiral groove to which the electromagnetic valve is open Therefore, the gap between the spiral groove and the compression coil spring can be further widened (a wide channel cross-sectional area can be secured). Therefore, an even larger amount of oil can be allowed to flow from a wide space to a narrow space.

In the invention according to Claim 5 as constructed above, in the invention according to at least one of claims 1 to 4, the helical groove is the line of the compression coil spring when the electromagnetic valve is open Since the gap portion and the entire circumference are opposed to each other in the radial direction, the gap between the spiral groove and the compression coil spring can be further widened (a wide channel cross-sectional area can be secured). Therefore, an even larger amount of oil can be allowed to flow from a wide space to a narrow space.

In the invention according to claim 6 configured as described above, the recess is formed by a plurality of parallel annular grooves formed in an annular shape on the outer wall surface of the valve body shaft portion. A wider gap between the annular groove and the compression coil spring can be secured (a wide cross-sectional area of the flow path can be secured). Therefore, a large amount of oil can be flowed from a wide space to a narrow space.
The annular groove is parallel provided in plural, the pitch of that is the same as the pitch of the helical compression spring when the solenoid valve is open. Thereby , the clearance gap between an annular groove and a compression coil spring can be ensured still more widely (a wide channel cross-sectional area can be ensured). Therefore, an even larger amount of oil can be allowed to flow from a wide space to a narrow space.

  Hereinafter, an embodiment of a hydraulic brake device A to which an electromagnetic valve according to the present invention is applied will be described with reference to the drawings. FIG. 1 is a schematic diagram showing a hydraulic brake device A. The hydraulic brake device A generates a brake fluid (basic hydraulic pressure) having a hydraulic pressure corresponding to the depression state of the brake pedal 11 and supplies the brake fluid to the wheel cylinders WCfl, WCrr, WCrl, WCfr, thereby providing wheels Wfl, Wrr, Wrl. , Wfr, a master cylinder 10 for restricting rotation, a reservoir tank 12 for storing brake fluid and supplying it to the master cylinder 10, a negative pressure booster 13 for assisting the depression force of the brake pedal 11, and wheels Wfl, Wrr, Wrl , Wfr wheel speed sensors Sfl, Srr, Srl, Sfr, a brake actuator B, and a control device 40 for controlling the brake actuator B.

  Each wheel cylinder WCfl, WCrr, WCrl, WCfr is provided in each caliper CLfl, CLrr, CLrl, CLfr, and accommodates a piston (not shown) that slides fluidly. When the hydraulic pressure from the master cylinder 10 is supplied to each wheel cylinder WCfl, WCrr, WCrl, WCfr, each piston presses a pair of brake pads (not shown) to integrate with each wheel Wfl, Wrr, Wrl, Wfr. The rotating disk rotors DRfl, DRrr, DRrl, DRfr are sandwiched from both sides to restrict the rotation. In the present embodiment, a disc type brake is employed, but a drum type brake may be employed.

  The brake piping system of the hydraulic brake device A of the present embodiment is configured by the X piping system, and the first and second output ports 10a and 10b of the master cylinder 10 are the first and second piping systems La and Lb. Are connected to each. The first piping system La communicates the master cylinder 10 with the left front wheel Wfl and the wheel cylinders WCfl and WCrr of the right rear wheel Wrr. The second piping system Lb includes the master cylinder 10 and the left rear wheel Wrl, The wheel cylinders WCrl and WCfr of the right front wheel Wfr are communicated with each other.

  The first piping system La includes first to sixth oil passages La1 to La6. One end of the first oil passage La1 is connected to the first output port 10a of the master cylinder 10. The second oil passage La2 has one end connected to the first oil passage La1 and the other end connected to the wheel cylinder WCfl. A holding valve 21 is disposed on the second oil passage La2. The third oil passage La3 has one end connected to the first oil passage La1 and the other end connected to the wheel cylinder WCrr. A holding valve 22 is disposed on the third oil passage La3. The fourth oil passage La4 has one end connected to the first oil passage La1 and the other end connected to the built-in reservoir tank 24. A pump 23 is disposed on the fourth oil passage La4. One end of the fifth oil passage La5 is connected between the holding valve 21 of the second oil passage La2 and the wheel cylinder WCfl, and the other end is connected between the pump 23 of the fourth oil passage La4 and the built-in reservoir tank 24. ing. A pressure reducing valve 25 is disposed on the fifth oil passage La5. The sixth oil passage La6 has one end connected between the holding valve 22 of the third oil passage La3 and the wheel cylinder WCrr, and the other end connected between the pump 23 of the fourth oil passage La4 and the built-in reservoir tank 24. ing. A pressure reducing valve 26 is disposed in the sixth oil passage La6.

  The holding valve 21 is a normally open type (normally open type) electromagnetic on-off valve that communicates and blocks the master cylinder 10 and the wheel cylinder WCfl. The holding valve 22 is a normally open type electromagnetic on-off valve that communicates and blocks the master cylinder 10 and the wheel cylinder WCrr. The holding valves 21 and 22 are configured as two-position valves that can be controlled in a communication state (shown state) when de-energized in accordance with a command from the control device 40 and in a shut-off state when energized. The holding valves 21 and 22 are provided in parallel with check valves 21a and 22a that allow the flow from the wheel cylinders WCfl and WCrr to the master cylinder 10, respectively.

  The pressure reducing valve 25 is a normally closed type (normally closed type) electromagnetic on-off valve that communicates and blocks the wheel cylinder WCfl and the built-in reservoir tank 24. The pressure reducing valve 26 is a normally closed electromagnetic on-off valve that communicates and blocks the wheel cylinder WCrr and the built-in reservoir tank 24. The pressure reducing valves 25, 26 are configured as two-position valves that can be controlled to be in a cut-off state (shown state) when deenergized in accordance with a command from the control device 40, and in a communication state when energized.

  The pump 23 has a suction port that communicates with a built-in reservoir tank 24 that stores brake fluid, and a discharge port that communicates with the master cylinder 10 and the wheel cylinders WCfl and WCrr via a check valve 27. The pump 23 is driven by the operation of the electric motor 23a in accordance with a command from the control device 40. The electric motor 23a is a DC motor, for example. The pump 23 sucks the brake fluid stored in the built-in reservoir tank 24 and returns it to the master cylinder 10 in the ABS control decompression mode. In order to alleviate the pulsation of the brake fluid discharged from the pump 23, a damper 28 is disposed on the discharge side of the pump 23 in the fourth oil passage La4. The check valve 27 is a check valve that allows flow to the master cylinder 10.

  The second piping system Lb has the same configuration as the first piping system La described above. That is, the second piping system Lb includes first to sixth oil passages Lb1 to Lb6, holding valves 31, 32, pump 33, built-in reservoir tank 34, pressure reducing valves 35, 36, check valves 31a, 32a, 37, dampers. 38.

  The brake actuator B includes the above-described electromagnetic valves 21, 22, 25, 26, 31, 32, 35, 36, pumps 23, 33, an electric motor 23a, built-in reservoirs 24, 34, and the like. The brake actuator B is provided separately from the master cylinder 10 and can independently generate the hydraulic pressure corresponding to the brake operation state of the brake pedal 11.

  Wheel speed sensors Sfl, Srr, Srl, Sfr are provided in the vicinity of each wheel Wfl, Wrr, Wrl, Wfr, and control a pulse signal having a frequency corresponding to the rotation of each wheel Wfl, Wrr, Wrl, Wfr. It is output to the device 40.

  The hydraulic brake device A includes a stop switch 14 that is turned on when the brake pedal 11 is depressed and turned off when the depression is released. The on / off signal of the stop switch 14 is input to the control device 40.

  Further, the hydraulic brake device A includes the stop switch 14, the electric motor 23a, the solenoid valves 21, 22, 25, 26, 31, 32, 35, 36, and the wheel speed sensors Sfl, Srr, Srl, Sfr. And a control device 40 connected to the.

  Next, the operation of the hydraulic brake device configured as described above will be described. First, brake fluid pressure control will be described. The control device 40 calculates a wheel speed Vw based on detection signals from the wheel speed sensors Sfl to Sfr every predetermined time, calculates a wheel acceleration DVw from the wheel speed Vw, and based on the wheel speed Vw of the four wheels. When the vehicle body speed Vs is calculated and it is detected that the stop switch 14 is turned on and brake braking is being performed, an optimal control is applied to each wheel so that the difference between the wheel speed Vw and the vehicle body speed Vs does not exceed a predetermined value. Implement ABS control to give power.

  Specifically, the control device 40 controls each of the holding valve 21 and the pressure reducing valve 25 to control the pair of holding valves 21 and the pressure reducing valves 25 assigned to the wheels Wfl to the pressure increasing / holding / depressurizing mode. Energized / de-energized according to the mode. The holding valve 21 and the pressure reducing valve 25 are de-energized in the pressure increasing mode, respectively, and the holding valve 21 and the pressure reducing valve 25 are opened and closed, and in the holding mode, they are excited and de-energized, respectively. 25 is closed, and in the decompression mode, each is excited and the holding valve 21 and the decompression valve 25 are closed and opened, respectively. Other wheels are similarly controlled. During the ABS control, the electric motor 23a is energized and the pumps 23 and 33 are controlled to operate.

  Next, a normally open type solenoid valve (the holding valves 21, 22, 31, 32 described above) will be described with reference to FIGS. The electromagnetic valve 50 includes a guide (base body) 52 that forms a magnetic path member made of a magnetic material. The guide 52 is formed in a stepped cylindrical shape, and the large diameter portion 52 a side of the guide 52 is fitted in the recess 71 of the housing 70. Further, a part of the large diameter portion 52 a and the small diameter portion 52 b of the guide 52 protrude outside the recess 71.

  The guide 52 has a guide hole 52c which is a stepped through hole. The guide hole 52c is positioned on the small diameter portion 52b side to hold the shaft 53 slidably, and the guide hole 52c is positioned on the large diameter portion 52a side to insert the sheet 55 into the large diameter guide hole (sheet insertion). Hole) 52c2. The guide 52 is formed with a second flow path 52e that connects the first oil chamber 52d formed by being surrounded by the seat 55 and the large diameter guide hole 52c2 to the pipe line A2. The second flow path 52e opens to the first oil chamber 52d, and the oil liquid in the first oil chamber 52d flows out to the outside. In the present embodiment, a pair of the second flow paths 52e are provided at portions of the first oil chamber 52d that face each other. Only one second flow path 52e may be provided. The pipe A2 communicates with a corresponding one of the wheel cylinders described above (for example, when the solenoid valve is 21, the wheel cylinder WCfl).

  The shaft 53 is a movable member capable of reciprocating along the central axis direction in the small diameter guide hole 52c1. The shaft 53 is formed of a nonmagnetic metal (for example, stainless steel) in a columnar shape (bar shape). The end portion (lower end portion) of the shaft 53 on the seat 55 side protrudes from the small diameter guide hole 52c1 of the guide 52 and extends to the first oil chamber 52d, and the valve body 54 is fixed to the tip thereof. A pair of grooves 53a are formed on the outer wall surface of the shaft 53 in the axial direction coinciding with the central axis of the guide hole 52c, and the grooves 53a communicate the first oil chamber 52d and the second oil chamber R2. It is. The second oil chamber R <b> 2 is formed by being surrounded by the guide 52, the sleeve 58, and the plunger 59.

  As shown in FIG. 3, the valve body 54 includes a valve body shaft portion 54a projecting from the lower end (one end) of the shaft 53 so as to extend in the axial direction of the shaft 53, and a distal end of the valve body shaft portion 54a. And an abutting portion 54b that abuts on the valve seat 55b. On the outer peripheral wall surface of the valve body shaft portion 54a, a concave portion extending from one radial side (the right side in FIGS. 2 and 3) to the other side (the left side in FIGS. A spiral groove (concave portion) 54c is formed.

  The concave portion 54c may be provided at any position as long as it is a range surrounded by the compression coil spring 60 of the valve body shaft portion 54a, that is, a range from the lower end surface of the shaft 53 to the upper end surface of the seat 55.

  The angle α of the spiral groove 54 c is preferably the same as the angle β of the winding of the compression coil spring 60. The angle α is an angle formed with the plane P orthogonal to the axial direction of the valve body 54, and the angle β is an angle formed with the plane Q orthogonal to the radial central axis of the compression coil spring 60. In addition, the pitch of the spiral grooves 54 c is preferably the same as the pitch of the compression coil springs 60. In either case, the compression coil spring 60 is mounted on the electromagnetic valve 50, and when the electromagnetic valve 50 is in the open state, that is, in a contracted state from a state where the compression coil spring 60 starts to fully open ( It is preferably an angle and a pitch (for a state where it is not mounted and not compressed).

  It is desirable that the winding direction of the spiral groove 54c and the winding direction of the compression coil spring 60 be the same. The angle α of the spiral groove 54c is preferably the same as the angle β of the winding of the compression coil spring 60 when the electromagnetic valve 50 is in the open state. The groove width of the spiral groove 54c is desirably equal to or larger than the gap between the lines of the compression coil spring 60 when the electromagnetic valve 50 is in the open state. It is desirable that the spiral groove 54c is opposed to the gap portion between the compression coil springs 60 when the electromagnetic valve 50 is in the open state in the radial direction over the entire circumference.

  The present invention may be applied to a case where pressure adjustment is performed while maintaining a sufficiently small open state with respect to the fully open state (completely opened state) of the electromagnetic valve 50. , The pitch of the compression coil spring 60, the gap between the lines and the angle β, and the pitch of the spiral groove 54c, the gap between the adjacent grooves and the angle α are preferably the same in the same order.

  The seat 55 is fixed by closing the open end of the large-diameter guide hole 52c2 (that is, the open end of the guide hole 52c on the side where the valve body 54 is provided). The sheet 55 is formed in a columnar shape, and the sheet 55 is formed with a first flow path 55a that connects the first oil chamber 52d in the guide 52 and the pipe line A1 at the center in the radial direction. A tapered valve seat 55b is formed at the end of the first flow passage 55a on the first oil chamber 52d side so that the contact portion 54b of the valve body 54 contacts and separates. Thus, the first flow passage 55a is opened and closed by the contact portion 54b of the valve body 54 coming into contact with and separating from the valve seat 55b. The pipe line A1 communicates with the master cylinder 10.

  The seat 55 is formed with a communication passage 55c that communicates the first oil chamber 52d in the guide 52 and the pipe line A1 in parallel with the first flow path 55a, and the end of the communication path 55c on the pipe line A1 side. A tapered valve seat 55d to which the spherical check valve 51 comes in contact with and separates from is formed in the portion. The check valve 51 is held at a position facing the valve seat 55d by a filter 56 that is press-fitted into the end of the large-diameter guide hole 52c2 of the guide 52. The check valve 51 is the check valve 21a. Further, a filter 57 is disposed on the outer periphery of the large diameter portion 52a of the guide 52 so as to surround the second flow path 52e. These filters 56 and 57 prevent foreign matters mixed in the brake fluid from entering the electromagnetic valve 50.

  The tip surface of the small diameter portion 52b of the guide 52 is a flat suction surface 52b1 having no recess, and a sleeve 58 is fitted on the outer peripheral side of the small diameter portion 52b so that the suction surface 52b1 is fitted. The sleeve 58 is formed of a non-magnetic metal (for example, stainless steel), has a cup shape with one end opened, and the cup bottom has a substantially spherical shape.

  A substantially cylindrical plunger 59 made of a magnetic material is disposed on the bottom side (closed side) of the sleeve 58, and the plunger 59 can slide in the sleeve 58. Note that the plunger 59 is in contact with the bottom surface of the sleeve 58, and when the plunger 59 is in contact with the bottom surface of the sleeve 58, sliding of the plunger 59 in the upward direction on the paper surface is restricted.

  The shaft 53 is urged toward the plunger 59 by a compression coil spring 60 interposed between the shaft 53 and the seat 55, and the shaft 53 and the plunger 59 are always in contact with each other so as to operate integrally. ing. The shaft 53 and the plunger 59 are moved according to the energized state of the electromagnetic coil 61.

  The compression coil spring 60 is formed by spirally winding an elongated metal wire, and is provided with a gap between the wires. The compression coil spring 60 is interposed in the oil chamber 52d so as to surround the valve body 54 between the shaft 53 and the seat 55.

  Around the sleeve 58, a cylindrical spool 62 that houses an electromagnetic coil 61 that forms a magnetic field when energized is disposed. A terminal 63 is drawn out from the electromagnetic coil 61, and the electromagnetic coil 61 can be energized from the outside through this terminal 63.

  Furthermore, a magnetic yoke 64 is disposed on the outer periphery of the spool 62. The spool 62 is fitted to the yoke 64, and the spool 62 and the yoke 64 are fitted to the guide 52 and the sleeve 58.

  Next, the operation of the electromagnetic valve configured as described above will be described with reference to FIG. When the shaft 53 (valve element 54) is eccentric when the electromagnetic valve 50 is minutely opened, the valve element shaft portion 54a of the valve element 54 extends from one side in the radial direction to the other side which is the opposite side. Since the spiral groove (concave portion) 54c is formed, the space between the compression coil spring 60 and the valve body shaft portion 54a extends from the wide space S1 formed by the eccentricity of the valve body 54 to the narrow space S2 on the opposite side. The flow path is provided by the recessed portion 54c. This flow passage is formed in a plurality of stages in parallel along the axial direction of the valve body shaft portion 54a.

  As a result, the oil liquid flowing in from the first flow path 55a flows in from a wide gap formed by the eccentricity of the valve body between the first flow path 55a and the valve body 54 (contact portion 54b), so that a wide space is obtained. A part of the oil that has reached S1 flows out of the compression coil spring as it is through the clearance of the compression coil spring on the wide space S1 side as in the past (the flow indicated by the arrow a1 in FIG. 4A). . In addition to this, another part of the oil that has reached the wide space S1 wraps around the narrow space S2 along the concave portion (flow passage) 54c of the valve body shaft portion 54a, and the compression coil spring 60 on the narrow space S2 side. Flows out of the compression coil spring 60 through the gap (the flow shown by the arrow a2 in FIG. 4A).

  As a comparative example, the operation of a solenoid valve in which the recess 54c is not provided in the valve body shaft portion 54a will be described with reference to FIG. When the shaft 53 (valve element 54) is eccentric when the electromagnetic valve 50 is minutely opened, the eccentricity of the valve element 54 is between the compression coil spring 60 and the valve element shaft portion 54a as described above. As a result, a wide space S1 is formed and a narrow space S2 is formed on the opposite side. However, since there is no recess 54c extending from one side to the other side, the oil liquid flowing in from the first flow path 55a has a valve body between the first flow path 55a and the valve body 54 (contact portion 54b). 54 flows in from a wide gap formed by the eccentricity of 54, most of which passes through the wide space S1 formed by the eccentricity of the valve body between the valve body 54 and the compression coil spring, and the compression coil spring on the wide space S1 side It flows out of the compression coil spring 60 through the gap 60 (the flow shown by the arrow a3 in FIG. 4B).

  As is apparent from the above description, according to the present embodiment in which the concave portion 54c is provided and the oil liquid flows along the concave portion (flow passage) 54c, the first embodiment is compared with the comparative example in which the concave portion 54c is not provided. The flow of the oil liquid flowing in from the one flow path 55a can be formed not only on one side but also on the other side. Therefore, the pressure received by the portion on the wide space S1 side of the valve body 54 is dispersed to the opposite side and the pressure is prevented from concentrating on one side, and the pressure received by the valve body 54 in the radial direction is suppressed. The movement of the body 54 in the axial direction becomes smoother, and the hydraulic pressure can be adjusted appropriately.

  Further, according to the above-described embodiment, the concave portion 54c is formed of a spiral groove formed in a spiral shape on the outer wall surface of the valve body shaft portion 54a, so that the shape of the compression coil spring 60 formed in a spiral shape is formed. By adjusting to, a wider gap between the spiral groove and the compression coil spring can be secured. Therefore, a large amount of oil can be flowed from the wide space S1 to the narrow space S2.

  Further, since the winding direction (right or left) of the spiral groove 54c and the winding direction (right or left) of the compression coil spring 60 are the same, a wider clearance can be secured between the spiral groove 54c and the compression coil spring 60. (A wide channel cross-sectional area can be secured). Therefore, an even larger amount of oil can be allowed to flow from the wide space S1 to the narrow space S2.

  Further, since the angle α of the spiral groove 54c is the same as the angle β of the winding of the compression coil spring 60 when the solenoid valve 50 is in the open state, the gap between the spiral groove 54c and the compression coil spring 60 is further increased. It can be secured (a wide channel cross-sectional area can be secured). Therefore, an even larger amount of oil can be allowed to flow from the wide space S1 to the narrow space S2.

  Further, since the pitch of the spiral groove 54c is the same as the pitch of the compression coil spring 60 when the solenoid valve 50 is in the open state, a wider clearance can be secured between the spiral groove 54c and the compression coil spring 60 (wide flow). The road cross-sectional area can be secured). Therefore, an even larger amount of oil can be allowed to flow from a wide space to a narrow space.

  Further, since the groove width of the spiral groove 54c is equal to or larger than the gap between the lines of the compression coil spring 60 when the solenoid valve 50 is in the open state, a wider clearance is ensured between the spiral groove 54c and the compression coil spring 60. Yes (wide channel cross-sectional area can be secured). Therefore, an even larger amount of oil can be allowed to flow from the wide space S1 to the narrow space S2.

  Further, since the spiral groove 54c is radially opposed to the gap portion between the lines of the compression coil spring 60 when the electromagnetic valve 50 is in the open state, the clearance between the spiral groove 54c and the compression coil spring 60 is present. Can be secured even more widely (a wide channel cross-sectional area can be secured). Therefore, an even larger amount of oil can be allowed to flow from the wide space S1 to the narrow space S2.

  Furthermore, a modified example of the recess will be described with reference to FIG. In the above-described embodiment, the concave portion is constituted by the spiral groove 54c. Instead, the concave portion may be constituted by an annular groove 154c formed in an annular shape on the outer wall surface of the valve body shaft portion 54a. Good. The annular groove 154c may be one or plural. In the case of a plurality, they may or may not be parallel to each other. In the case of being parallel, the pitch of the annular grooves 154c is preferably the same as the pitch of the compression coil springs 60. The gap between the annular groove 154c and the compression coil spring 60 can be secured even further (a wide channel cross-sectional area can be secured). Therefore, an even larger amount of oil can be allowed to flow from a wide space to a narrow space.

  According to this modification, the clearance between the annular groove and the compression coil spring can be ensured more easily with a simple processing / configuration (a wide channel cross-sectional area can be ensured). Therefore, a large amount of oil can be flowed from a wide space to a narrow space.

  Further, the concave portion is not annular or spiral (it may not be continuous for one round), but may be a groove (for example, circular arc shape) that is not continuous for one round. In this case, it is only necessary to have a length that allows the wide space S1 and the narrow space S2 to communicate with each other.

  Furthermore, another modified example of the recess will be described with reference to FIG. In the above-described embodiment, the concave portion is configured by the spiral groove 54c. Instead, the concave portion may be configured by the through hole 254c. The through hole 254c is a through hole that penetrates the valve body shaft portion 54a in the radial direction. There may be one or more through holes 254c. In this modification, there are two through-holes 254c and are orthogonal to each other. Since the valve body 54 rotates around its axis, there may be cases where the wide space S1 and the narrow space S2 cannot be properly communicated with each other through the through holes 254c only by extending in one direction. This can be prevented.

  This modification is particularly effective when the gap between the valve body shaft portion 54a and the compression coil spring 60 is very narrow, regardless of whether the gap between the valve body shaft portion 54a and the compression coil spring 60 is wide or narrow. A flow path can be reliably secured between the wide space S1 and the narrow space S2. Therefore, the oil liquid can be flowed from the wide space S1 to the narrow space S2.

  In the above-described embodiment and modification, the first and second flow paths 55a and 52e are used as the inflow path and the outflow path in the same order, but the present invention is not limited to this. Sometimes used as a road.

It is a schematic diagram showing one embodiment of a hydraulic brake device to which an electromagnetic valve according to the present invention is applied. It is sectional drawing which shows the solenoid valve by this invention. (A) is the elements on larger scale showing the circumference of the valve element shown in FIG. 2 (only the end face is shown in the compression coil spring), (b) is the enlarged external view of the compression coil spring shown in FIG. It is. (A) is sectional drawing for demonstrating the action | operation of the solenoid valve by this invention, (b) is sectional drawing for demonstrating the action | operation of the thing without a recessed part in the solenoid valve by this invention. It is a partial expanded sectional view which shows the modification of the solenoid valve by this invention. It is a partial expanded sectional view which shows the modification of the solenoid valve by this invention.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 10 ... Master cylinder, 10a ... 1st output port, 10b ... 2nd output port, 11 ... Brake pedal, 12 ... Reservoir tank, 13 ... Negative pressure type booster, 14 ... Stop switch 21, 22, 31, 32 ... Holding valve 21a, 22a, 31a, 32a, 27, 37 ... check valve, 23, 33 ... pump, 23a ... electric motor, 24, 34 ... built-in reservoir, 25, 26, 35, 36 ... pressure reducing valve, 28, 38 ... Damper, 40 ... control device, 52 ... guide (base), 52c ... guide hole, 52d ... first oil chamber (oil chamber), 52e ... second flow path, 53 ... shaft (movable member), 54 ... valve body, 54a ... Valve body shaft portion, 54b ... Contact portion, 54c ... Spiral groove (recess), 55 ... Seat, 55a ... First flow path, 55b ... Valve seat, compression coil spring ... 60, Electromagnetic coil ... 61, 154c ... Ring , 254c ... through hole, A ... hydraulic brake apparatus, B ... brake actuator, WCfl~WCrr ... wheel cylinder.

Claims (6)

A base body (52) having a guide hole (52c) formed thereon;
A movable member (53) capable of reciprocating along the central axis direction in the guide hole;
An electromagnetic coil (61) that forms a magnetic field when energized and moves the movable member within the guide hole according to the energized state;
A valve body (54) provided at one end of the movable member;
The valve body has a valve seat (55b) that closes the open end of the guide hole on the side facing the valve body, and contacts and separates the valve body, and is opened and closed when the valve body contacts and separates from the valve seat. A sheet (55) having a flow path (55a);
An oil chamber (52d) formed by the guide hole and the sheet and into which oil liquid flows from the first flow path;
A second flow path (52e) that opens in the oil chamber and is provided in the base body and through which the oil in the oil chamber flows out;
A compression coil spring (60) interposed in the oil chamber so as to surround the valve body between the seat and the movable member, and an electromagnetic valve (50),
The valve body includes a valve body shaft portion (54a) that extends in the axial direction at one end of the movable member, and an abutment that is provided at the tip of the valve body shaft portion and contacts the valve seat. And a concave portion (54c, 154c, 254c) extending from one side in the radial direction to the other side that is the opposite side is formed on the valve body shaft portion,
The concave portion is composed of a spiral groove (54c) formed in a spiral shape on the outer wall surface of the valve body shaft portion,
The electromagnetic valve characterized in that the winding direction of the spiral groove and the winding direction of the compression coil spring are the same. A base body (52) having a guide hole (52c) formed thereon;
A movable member (53) capable of reciprocating along the central axis direction in the guide hole;
An electromagnetic coil (61) that forms a magnetic field when energized and moves the movable member within the guide hole according to the energized state;
A valve body (54) provided at one end of the movable member;
The valve body has a valve seat (55b) that closes the open end of the guide hole on the side facing the valve body, and contacts and separates the valve body, and is opened and closed when the valve body contacts and separates from the valve seat. A sheet (55) having a flow path (55a);
An oil chamber (52d) formed by the guide hole and the sheet and into which oil liquid flows from the first flow path;
A second flow path (52e) that opens in the oil chamber and is provided in the base body and through which the oil in the oil chamber flows out;
A compression coil spring (60) interposed in the oil chamber so as to surround the valve body between the seat and the movable member, and an electromagnetic valve (50),
The valve body includes a valve body shaft portion (54a) that extends in the axial direction at one end of the movable member, and an abutment that is provided at the tip of the valve body shaft portion and contacts the valve seat. And a concave portion (54c, 154c, 254c) extending from one side in the radial direction to the other side that is the opposite side is formed on the valve body shaft portion,
The concave portion is composed of a spiral groove (54c) formed in a spiral shape on the outer wall surface of the valve body shaft portion,
The electromagnetic valve according to claim 1, wherein a groove width of the spiral groove is equal to or larger than a clearance between lines of the compression coil spring when the electromagnetic valve is in an open state.   3. The electromagnetic valve according to claim 1, wherein an angle of the spiral groove is the same as an angle of a winding of the compression coil spring when the electromagnetic valve is in an open state.   4. The solenoid valve according to claim 1, wherein a pitch of the spiral groove is the same as a pitch of the compression coil spring when the solenoid valve is in an open state. 5.   5. The spiral groove according to claim 1, wherein the spiral groove is opposed to a gap portion between the compression coil springs when the electromagnetic valve is in an open state in a radial direction over the entire circumference. Characteristic solenoid valve. A base body (52) having a guide hole (52c) formed thereon;
A movable member (53) capable of reciprocating along the central axis direction in the guide hole;
An electromagnetic coil (61) that forms a magnetic field when energized and moves the movable member within the guide hole according to the energized state;
A valve body (54) provided at one end of the movable member;
The valve body has a valve seat (55b) that closes the open end of the guide hole on the side facing the valve body, and contacts and separates the valve body, and is opened and closed when the valve body contacts and separates from the valve seat. A sheet (55) having a flow path (55a);
An oil chamber (52d) formed by the guide hole and the sheet and into which oil liquid flows from the first flow path;
A second flow path (52e) that opens in the oil chamber and is provided in the base body and through which the oil in the oil chamber flows out;
A compression coil spring (60) interposed in the oil chamber so as to surround the valve body between the seat and the movable member, and an electromagnetic valve (50),
The valve body includes a valve body shaft portion (54a) that extends in the axial direction at one end of the movable member, and an abutment that is provided at the tip of the valve body shaft portion and contacts the valve seat. And a concave portion (54c, 154c, 254c) extending from one side in the radial direction to the other side that is the opposite side is formed on the valve body shaft portion,
The recess is composed of a plurality of annular grooves (154c) parallel to each other formed in an annular shape on the outer wall surface of the valve body shaft portion,
The pitch of the annular groove is the same as the pitch of the compression coil spring when the solenoid valve is in an open state.

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