JP5416398B2 - Electromagnetic spool valve device - Google Patents

Description

  The present invention relates to an electromagnetic spool valve device including a linear solenoid portion and a spool.

  2. Description of the Related Art Conventionally, an electromagnetic spool valve is known that includes a spool valve whose outer shape is a substantially columnar shape and a solenoid portion that functions as an electromagnetic actuator that drives the spool valve.

  With regard to this type of electromagnetic spool valve, the present applicant has proposed a linear solenoid valve that can further improve the attractive force with respect to the movable core (see, for example, Patent Document 1).

In the linear solenoid valve disclosed in Patent Document 1, an inlet port and an outlet port are formed on the outer periphery of a substantially cylindrical valve body, and the valve body moves along the axial direction. A single spool for switching the communication state and the non-communication state of the inlet port and the outlet port is provided.
JP 2005-286236 A

  By the way, in the linear solenoid valve disclosed in Patent Document 1, for example, the solenoid part (coil) is turned off (non-energized) and on (energized) based on a control signal output from the control device. By controlling the duty ratio, the inlet port and the outlet port are switched to a two-stage state of communication and non-communication, and the hydraulic pressure corresponding to the two-stage switching state is provided so as to be controllable.

  In this case, in the linear solenoid valve disclosed in Patent Document 1, the hydraulic pressure derived from the outlet port is controlled to be switched to a two-stage state by sliding a single spool. There is a demand from the industry to perform switching control in more stages and with higher accuracy.

  Further, even when the multistage switching control of the hydraulic pressure is performed by a plurality of spools, it is required to improve the valve operation responsiveness by suppressing the operation delay of the spool at the hydraulic pressure switching control as much as possible. Is done.

  The present invention has been made in view of the above points, and can switch the hydraulic pressure to a three-stage state with high accuracy using a plurality of spools, and can improve the valve operation responsiveness during the switching control. An object of the present invention is to provide an electromagnetic spool valve device that can be improved.

To achieve the above object, the present invention provides a main body including a valve body having a plurality of ports through which a pressure fluid flows and a housing, a coil provided in the housing and wound around a coil bobbin, A linear solenoid part having a movable core that is attracted to a fixed core under energization, and a series and a coaxial arrangement in the space of the valve body, and also slidable along the space. The first spool includes at least a first annular recess, a second annular recess, and a third annular recess, and the plurality of ports include at least a first inlet port. the second inlet port, a first outlet port, the second comprises an outlet port and a third outlet port, said first spool及A valve mechanism for switching between a communication state and a non-communication state between the plurality of ports in correspondence with a position of the second spool; and a first spring member interposed between the first spool and the second spool And a second spring member interposed between one end of the valve body and the second spool,
An initial valve state in which a small current is supplied to the linear solenoid part in the off state, and an intermediate current larger than the small current is supplied to the linear solenoid part, and the movable core is in an intermediate position. In the 1 lift state, a large current is supplied to the linear solenoid part and the movable core is switched to the second lift state in the displacement end position, respectively. In the off state and the initial valve state of the linear solenoid part, Due to the spring force of the first spring member, the first spool and the second spool are in a non-contact state and a part along the axial direction is overlapped, and the second annular recess of the first spool causes the first 1 inlet port and said first outlet port is led pressure fluid from the first outlet port communicates, wherein the first lift state, the first By the spring force of the first spool against the spring member is displaced to the second spool side, the first spool and the second position next to the spool is in contact, said third of said first spool The first inlet port and the second outlet port are communicated with each other by an annular recess, and pressure fluid is led out from the second outlet port . In the second lift state, the first spool and the second spool are in contact with each other. while maintaining the contact state, the first spool and the second spool, said second spring member positioned next to that against the spring force displaced by integrally predetermined distance toward the one end side of the valve body of The first inlet port and the first outlet port communicate with each other through the first annular recess of the first spool to connect the first outlet port. With the pressure fluid is derived, by the second spool and said second inlet port and said third outlet port, characterized in that the pressure fluid is derived from the third outlet port communicates.

  In the present invention, in the off state where no current is supplied to the linear solenoid part, the movable core is in the original position, and even if a small current is supplied to the linear solenoid part in the off state, the first The spool and the second spool do not displace at all and are set so as to be maintained in the initial valve state. In other words, in the initial valve state, the small current supplied to the linear solenoid unit is set to a minute current that keeps the movable core in the original position and does not operate the first spool and the second spool.

In the OFF state and the initial valve state of the linear solenoid part, the first spring member is in a position where the first spool and the second spool are not in contact with each other and a part along the axial direction is overlapped . The first inlet port and the first outlet port communicate with each other through the second annular recess of one spool, and pressure fluid is led out from the first outlet port. In other words, the first spool and the second spool are pressed toward each other by the spring force of the first spring member interposed between the first spool and the second spool, but are close to each other. The end portion of the first spool and the end portion of the second spool are set at a position where they partially overlap each other.

  In an initial valve state in which a small current is supplied to the linear solenoid part, when an intermediate current larger than the small current is supplied to the linear solenoid part and the movable core is displaced toward the intermediate position, Only one spool slides against the spring force (spring load) of the first spring member and enters the first lift state.

In the first lift state, the first spool is displaced toward the second spool against the spring force of the first spring member, so that the first spool and the second spool come into contact with each other. The first inlet port and the second outlet port communicate with each other through the third annular recess of the first spool, and pressure fluid is led out from the second outlet port. In this case, when the spring load of the first spring member is set smaller than the spring load of the second spring member, only the first spool slides against the spring force of the first spring member, and the second spool Does not slide.

  According to the present invention, when the valve is displaced from the initial valve state to the first lift state, a small current is supplied to the linear solenoid portion in advance, so that no current is supplied to the linear solenoid portion. Compared with the case where the linear solenoid section is displaced from the off state to the first lift state, the valve can be quickly shifted from the initial valve state to the first lift state, and the delay of the valve operation during switching control is suppressed as much as possible. The valve response (for example, the rising waveform characteristic of the pulse signal when the current value is switched) can be improved.

  Further, when a large current larger than the intermediate current is supplied to the linear solenoid portion and the movable core is displaced toward the displacement end position, the first spool and the second spool are subjected to the spring force of the second spring member. It slides against (spring load) and enters the second lift state.

In the second lift state, the first spool and the second spool are opposed to the spring force of the second spring member while the first spool and the second spool are in contact with each other. The first inlet port and the first outlet port are communicated with each other by the first annular recess of the first spool and pressure fluid is led out from the first outlet port. The second spool communicates with the second inlet port and the third outlet port, and pressure fluid is led out from the third outlet port.

Thus, in the present invention, the first spool includes at least the first annular recess, the second annular recess, and the third annular recess, and the plurality of ports include at least the first inlet port, the second inlet port, A first spool and a second spool , which include one outlet port, a second outlet port, and a third outlet port, and are arranged in series and coaxially in the space portion of the valve body, slide along the space portion as described above. By setting the relative positional relationship, the linear solenoid unit is in an off state and an initial valve state, and includes a first lift state and a second lift state in which an intermediate current and a large current are respectively supplied to the linear solenoid unit. In addition, the pressure of the pressure fluid can be switched and controlled with high accuracy.

  In the present invention, the plurality of ports provided in the valve body may include at least a first inlet port, a second inlet port, a first outlet port, a second outlet port, and a third outlet port.

  In the OFF state and the initial valve state of the linear solenoid portion, the first inlet port and the first outlet port communicate with each other, and pressure fluid is led out from the first outlet port. In the first lift state, the first inlet port and the second outlet port communicate with each other, and pressure fluid is led out from the second outlet port. In the second lift state, the first inlet port and the first outlet port communicate with each other, pressure fluid is led out from the first outlet port, and the second inlet port and the third outlet port communicate with each other. Thus, the pressure fluid is led out from the third outlet port.

  Furthermore, according to the present invention, in the OFF state of the linear solenoid part, the electromagnetic thrust F generated in the linear solenoid part is zero (F = 0), and the spring load L1 of the first spring member and the second spring member The spring load L2 may be set to a relationship of F <L1 <L2. In the OFF state of the linear solenoid portion, the electromagnetic thrust F applied to the movable core is zero, so that no driving force is transmitted to the first spool and the second spool, and the first spool and the second spool are In situ.

  In the initial valve state of the linear solenoid portion, the electromagnetic thrust F0 generated in the linear solenoid portion is set to a relationship of F0 <L1 <L2 which is smaller than the spring load L1 of the first spring member and the spring load L2 of the second spring member. It is good to be done. In the initial valve state of the linear solenoid portion, the electromagnetic thrust F0 generated in the linear solenoid portion is set to be smaller than the spring load L1 of the first spring member and the spring load L2 of the second spring member. The driving force is not transmitted to the second spool, and the first spool and the second spool are in their original positions.

  In the first lift state, the electromagnetic thrust F1 generated in the linear solenoid portion is set to a relationship of L1 <F1 <L2 which is larger than the spring load L1 of the first spring member and smaller than the spring load L2 of the second spring member. Good. In the first lift state, only the first spool can be slid by overcoming the spring load L1 of the first spring member that applies the electromagnetic thrust F1 to the movable core and biases the first spool. Since the electromagnetic thrust F1 is smaller than the spring load L2 of the second spring member, the second spool does not slide and only the first spool slides.

  In the second lift state, when the electromagnetic thrust F2 generated in the linear solenoid portion is set to a relationship of L1 <L2 <F2 which is larger than the spring load L1 of the first spring member and the spring load L2 of the second spring member. Good. In the second lift state, the electromagnetic thrust F2 is applied to the movable core and the spring load L2 of the second spring member is overcome and the first spool and the second spool can be slid integrally.

  According to the present invention, an electromagnetic spool valve device can be obtained that can switch the hydraulic pressure to a three-stage state with high accuracy using a plurality of spools and improve the valve operation responsiveness during the switching control. It is done.

  Next, embodiments of the present invention will be described in detail with reference to the drawings as appropriate. 1 to 4 are longitudinal sectional views along an axial direction of an electromagnetic spool valve device according to an embodiment of the present invention, and FIGS. 5 to 7 are partially enlarged longitudinal sectional views of FIGS. FIG. 8 is an enlarged vertical sectional view along the axial direction of the first spool and the second spool constituting the electromagnetic spool valve device, and FIG. 9 is a longitudinal section along the axial direction of the valve body constituting the electromagnetic spool valve device. It is a surface enlarged view.

  As shown in FIGS. 1 to 4, the electromagnetic spool valve device 10 is formed in a cylindrical shape with a bottom made of, for example, a magnetic metal material, and a housing in which a linear solenoid portion 12 including a linear motion linear solenoid is disposed. 14 and a sleeve-like valve body 18 integrally connected to the housing 14 and provided with a valve mechanism 16 therein. The housing 14 and the valve body 18 function as a main body.

  The housing 14 has a cylindrical portion 14a that is elongated along the axial direction, and is formed at a predetermined interval inside the cylindrical portion 14a and extends substantially parallel to the cylindrical portion 14a and has a short length. The cylindrical yoke 14b is formed, and the cylindrical portion 14a and a bulging portion 14c which is formed at one end of the cylindrical yoke 14b and has a concave portion having a rectangular longitudinal section inside. In this case, the cylindrical portion 14a, the cylindrical yoke 14b, and the bulging portion 14c are integrally formed.

  The cylindrical yoke 14b is, for example, illustrated in which another yoke (not shown) made of a substantially cylindrical body formed separately from the housing 14 is formed on the inner peripheral surface of the bulging portion 14c of the housing 14. You may form so that it may press-fit to the press-fit part which does not.

  The linear solenoid portion 12 includes a coil assembly housed in the housing 14 and a cylindrical yoke 14b formed integrally with the housing 14 on the closed end side of the housing 14 and disposed inside the coil assembly. And a fixed core 20 that is coupled to the open end of the housing 14 and is disposed along the axial direction inside the coil assembly via a predetermined clearance with the cylindrical yoke 14b, and the cylindrical yoke 14b. And a movable core 22 slidably inserted into the fixed core 20.

  In addition, at one end of the fixed core 20 facing the movable core 22 at a predetermined interval, an annular flange having a tapered surface whose outer peripheral surface is gradually reduced in diameter and whose longitudinal section is formed into an acute angle. A portion 20a is provided. The coil assembly includes a coil bobbin 24 formed of a resin material and having flanges at both ends along the axial direction, and a coil 26 wound around the coil bobbin 24.

  Between the housing 14 and the coil 26, a resin sealing body 28 for molding the outer peripheral surface of the coil 26 and the like is provided. The resin sealing body 28 is connected to the coupler portion 30 communicating with the coil 26. It is integrally formed of a resin material continuously. The coupler portion 30 is provided so that a terminal portion 32 of a terminal electrically connected to the coil 26 is exposed.

  A shaft 34 penetrating the central portion of the movable core 22 is fixed, and one end portion (upper end portion) along the axial direction of the shaft 34 is attached to a concave portion of the bulging portion 14 c of the housing 14. The shaft 34 is supported so as to be slidable in the axial direction via the first flat bearing 36 a, and the other end portion (lower end portion) of the shaft 34 is mounted in a through-hole penetrating the center portion of the fixed core 20. It is slidably supported in the axial direction via a flat bearing 36b. In addition, the movable core 22 and the shaft 34 may not be configured separately, and the movable core 22 may be integrally formed including the shaft 34.

  A movable core that displaces integrally with the shaft 34 by adopting a both-end support structure in which both ends of the shaft 34 are slidably supported via the first flat bearing 36a and the second flat bearing 36b. Thus, it is possible to secure 22 straight running characteristics.

  The end surface of the movable core 22 facing the fixed core 20 is made of a nonmagnetic material, and when the energization to the coil 26 is stopped, the movable core 22 remains attracted to the fixed core 20 due to the influence of residual magnetism. A ring body 38 having a function to prevent this (sticking prevention function) is mounted via the shaft 34.

  In this case, an exciting action is generated by turning on a power source (not shown) and causing a current to flow through the coil 26, and the movable core 22 and the shaft 34 are integrally displaced toward the fixed core 20 by the exciting action. The first spool 40 and / or the second spool 42 to be described later can be actuated (advanced / retracted operation).

  The valve mechanism 16 has a first inlet port 44a, a second inlet port 44b, a first outlet port 46a, a second outlet port 46b, a third outlet port 46c, a drain port 48 and a breathing port 50 on one side. The valve body 18 arranged side by side and one end portion of the shaft 34 of the linear solenoid portion 12 abut against each other and are pressed by the shaft 34 so as to be slidable along the space 52 in the valve body 18. The first spool 40 and the second spool 42 are included.

  Note that the breathing port 50 supplies and exhausts air in the housing 14 in response to the advance / retreat operation of the movable core 22. The first inlet port 44a, the second inlet port 44b, the first outlet port 46a, the second outlet port 46b, the third outlet port 46c, the drain port 48 and the breathing port 50 are a plurality of ports through which pressure fluid flows. It functions as.

  The first spool 40 and the second spool 42 are separately formed in a substantially cylindrical shape, and are arranged in series and coaxially in the space 52 of the valve body 18. In this case, as shown in FIG. 8, the maximum outer diameter D2 of the second spool 42 (the outer diameters of the seventh land 60g and the eighth land 60h described later) is the maximum outer diameter D1 of the first spool 40 ( It is set larger than the outer diameter of first to sixth lands 60a to 60f described later (D1 <D2).

  As shown in FIG. 1, when the valve body 18 is mounted on the side wall of another member 54 such as an automobile engine, in the vicinity of each port, each port and the other member 54 are provided. A single seal member 56 is provided for sealing the connecting portion.

  As shown in FIG. 8, the first spool 40 has a long hole 58 that extends along the axial direction and closes at the upper end portion on the linear solenoid portion 12 side and opens at the lower end portion on the second spool 42 side. Is formed. Further, in the vicinity of the upper end portion of the first spool 40 and between a first land 60a and a second land 60b which will be described later, the first spool 40 communicates with the long hole 58 and penetrates in a direction perpendicular to the axial direction. A first communication hole 62a is formed.

  Further, a second communication hole 62b is formed between the lower end of the first spool 40 and a sixth land 60f, which will be described later, and communicates with the long hole 58 and penetrates in a direction orthogonal to the axial direction. In this case, in the first lift state shown in FIG. 3 (described later), the first outlet port 46a, the first communication hole 62a, the long hole 58, the second communication hole 62b, the third communication hole 62c described later, and the drain port. When 48 communicates with each other, the pressure oil on the first outlet port 46 a side can be suitably discharged from the drain port 48.

  As shown in FIG. 8, the lower end of the first spool 40 faces the lower end of the second spool 42, and a recess 64 is provided so that the lower end can come into contact therewith. Further, a third communication hole 62c is formed in the side wall of the hollow portion 64 so as to be able to communicate with the second communication hole 62b of the first spool 40 and penetrates in a direction orthogonal to the axial direction of the second spool 42. The Further, the second spool 42 is formed with a stepped through hole 66 that communicates with the recessed portion 64 and penetrates along the axial direction.

  Further, as shown in FIG. 1, the valve mechanism portion 16 is disposed so as to face the end surface of the second spool 42 and closes the space portion 52 of the valve body 18, the first spool 40 and the first spool 40. The first spring member 70 is interposed between the two spools 42 and the second spring member 72 is interposed between the second spool 42 and the cap member 68. The cap member 68 functions as one end of the valve body 18. Further, a seal ring 74 is provided on the outer peripheral surface of the cap member 68 through a circular groove to hold the mounting portion liquid-tight or air-tight, and the cap member 68 is press-fitted into the hole of the valve body 18. Is done.

  In this case, the spring load (spring constant) L2 of the second spring member 72 is set larger than the spring load (spring constant) L1 of the first spring member 70 (L1 <L2).

  In the present embodiment, the first spring member 70 and the second spring member 72 each formed of a coil spring have been described. However, the present invention is not limited to this. Any biasing member that biases (applies pressing force) the first spool 40 and the second spool 42 may be used.

  The first inlet port 44a and the second inlet port 44b are respectively connected to a hydraulic power source (pressure fluid supply source) (not shown) such as a hydraulic pump through a supply oil passage, and the first to third outlet ports 46a to 46c. Is connected to a hydraulic operating part of a hydraulic device (not shown) via an output oil passage, and the drain port 48 is connected to a reservoir tank (not shown). In the present embodiment, the pressure oil is used for explanation. However, the present invention is not limited to this, and for example, a pressure fluid including compressed air or the like can be used as the working medium.

  As shown in FIG. 8, the outer peripheral surface of the first spool 40 is composed of an annular protrusion that is bulged by a predetermined length in the radially outward direction, from the linear solenoid portion 12 side toward the cap member 68 side. The first to sixth lands 60a to 60f are sequentially formed along the axial direction with a predetermined interval. The first to sixth lands 60a to 60f have the same outer diameter, and constitute the maximum outer diameter D1 of the first spool 40.

  In this case, a first annular recess 76a that connects the first inlet port 44a and the first outlet port 46a is formed between the second land 60b and the third land 60c adjacent to each other of the first spool 40. (See the second lift state in FIG. 4). In addition, a second annular recess 76b that allows the first inlet port 44a and the first outlet port 46a to communicate with each other is formed between the third land 60c and the fourth land 60d adjacent to each other of the first spool 40 (see FIG. (Refer to the linear solenoid portion OFF state in FIG. 1).

  Further, a third annular recess 76c that allows the first inlet port 44a and the second outlet port 46b to communicate with each other is formed between the fourth land 60d and the fifth land 60e adjacent to each other of the first spool 40 (see FIG. (Refer to the first lift state in FIG. 3). Furthermore, a fourth annular recess 76d for communicating the second outlet port 46b and the drain port 48 is formed between the fifth land 60e and the sixth land 60f adjacent to each other of the first spool 40 (see FIG. No. 4 second lift state). Furthermore, a fifth annular recess 76e for communicating the second outlet port 46b and the drain port 48 is formed between the sixth land 60f and the lower end of the first spool 40 (the linear solenoid portion of FIG. 1). See off state).

  A recess 64 that extends by a predetermined length along the axial direction is formed at the upper end of the second spool 42 adjacent to the first spool 40, and one end of the first spring member 70 is formed on the inner wall surface of the recess 64. The other end of the first spring member 70 is engaged with the side wall of the sixth land 60f of the first spool 40. In this case, the inner diameter of the recessed portion 64 of the second spool 42 is set larger than the outer diameter of the lower end portion of the first spool 40, and the lower end portion of the first spool 40 compresses the first spring member 70. However, it is inserted along the recessed portion 64 of the second spool 42 and is provided so as to be in contact with the bottom wall 64a of the recessed portion 64 (see FIGS. 6 and 7).

  On the outer peripheral surface of the second spool 42, as shown in FIG. 8, the seventh land 60g and the eighth land 60h which are wide along the axial direction are formed to bulge outward in the radial direction. A sixth annular recess 76f that allows the second inlet port 44b and the third outlet port 46c to communicate with each other is formed between the seventh land 60g and the eighth land 60h and substantially at the center of the second spool 42 (see FIG. (Refer to the second lift state in FIG. 4).

  On the inner wall of the valve body 18, as shown in FIG. 9, a first annular projecting portion 78 a that protrudes toward the space portion 52 and is wide along the axial direction, and second to seventh portions that are narrow along the axial direction. The annular projecting portions 78b to 78g are formed, respectively, and the first to seventh annular projecting portions 78a to 78g are sequentially arranged at a predetermined interval from the linear solenoid portion 12 side toward the cap member 68 side.

  As described above, since the maximum outer diameter D1 of the first spool 40 and the maximum outer diameter D2 of the second spool 42 are set to be different, the difference in the maximum outer diameter (D1 <D2) is accommodated. The inner diameters of the first to seventh annular protrusions 78a to 78g provided in the space 52 of the valve body 18 are also set to be different from each other. That is, as shown in FIG. 9, the inner diameter d1 of the first to fifth annular projecting portions 78a to 78e that are close to the housing 14 side with the substantially central portion of the valve body 18 as a base point is from the substantially central portion to the cap member 68 side. It is set smaller than the inner diameter d2 of the adjacent sixth annular protrusion 78f and seventh annular protrusion 78g (d1 <d2).

  Accordingly, the inner diameter of the valve body 18 is formed so as to increase from the small diameter to the large diameter from the linear solenoid portion 12 side toward the cap member 68 side, thereby cutting the space portion 52 from the large diameter side and the first. Assembling work (described later) of the spool 40, the second spool 42, and the like can be easily performed. Further, as shown in FIGS. 5 and 9, the second spool 42 is located at a portion adjacent to the fifth annular projecting portion 78 e provided in the space portion 52 of the valve body 18 when the linear solenoid portion 12 is in the OFF state. An annular step 80 that functions as a stopper is provided by abutting the upper end of each.

  The electromagnetic spool valve device 10 according to the present embodiment is basically configured as described above. Next, its operation and effects will be described.

First, the assembly work of the electromagnetic spool valve device 10 will be described.
The inner diameter of the inner wall of the valve body 18 is formed so as to increase from a small diameter to a large diameter from the linear solenoid portion 12 side toward the cap member 68 side, and as shown in FIG. 10, from the large diameter side opening portion 18a of the valve body 18. After loading the first spool 40 and the first spring member 70 along the space 52, and subsequently loading the second spool 42 and the second spring member 72, respectively, the cap member 68 is press-fitted, and the large diameter The side opening 18a is closed.

  In this case, one end portion of the second spool 42 engaged with the first spring member 70 abuts on an annular stepped portion 80 formed at a substantially central portion of the inner wall of the valve body 18 (see the broken line in FIG. 10), and the space It is positioned at a predetermined position in the part 52. Therefore, even if the first spool 40 is in a free state to some extent in the space 52 when assembled, the second spool 42 is held at a position in contact with the annular stepped portion 80 by the pressing force of the second spring member 72. As a result, the assembling work becomes easy and the assembling property can be improved.

  In addition, the small-diameter side opening 18b of the valve body 18 is obtained by crimping the thin end portion of the linear solenoid portion 12 configured in advance inward (see FIGS. 1 to 4), so that the valve body 18 and the housing 14 are connected. They are joined together and closed.

Next, the operation of the electromagnetic spool valve device 10 will be described.
When the linear solenoid portion 12 is not energized, as shown in FIG. 1, since no electromagnetic force (electromagnetic thrust) of the linear solenoid portion 12 is generated (electromagnetic thrust F = 0), the first spool 40 is The second spool 42 is pressed toward the first spool 70 by the spring force (L2) of the second spring member 72 while being pressed toward the linear solenoid portion 12 by the spring force (L1) of the spring member 70. The upper end portion of the second spool 42 is in contact with the annular stepped portion 80 and the upward displacement is restricted.

  Therefore, in the OFF state of the linear solenoid portion 12, as shown in FIG. 1, the first inlet port 44a and the first outlet port 46a are connected by the second annular recess 76b formed on the outer peripheral surface of the first spool 40. In a state of communication, the pressure oil introduced from the first inlet port 44a is supplied to the other member 54 via the second annular recess 76b and the first outlet port 46a (OUT1).

  At the same time, when the linear solenoid portion 12 is in the OFF state, as shown in FIG. 1, the first spool 40 and the second spool are positioned so that the lower end portion of the first spool 40 and the upper end portion of the second spool 42 overlap each other. 42 is set. Accordingly, the second outlet port 46 b is in communication with the drain port 48 via the fifth annular recess 76 e of the first spool 40, and the pressure oil remaining in the second outlet port 46 b is discharged from the drain port 48. .

  In the OFF state of the linear solenoid portion 12 shown in FIG. 1, the eighth land 60h formed on the outer peripheral surface of the second spool 42 and the seventh annular projecting portion 78g of the valve body 18 come into contact with each other, and the second inlet port 44b The third outlet port 46c is not in communication.

  Thus, in the OFF state of the linear solenoid part 12, the spring load L1 of the first spring member 70 is set smaller than the spring load L2 of the second spring member 72, and the electromagnetic thrust F of the linear solenoid part 12 is set. Is zero and smaller than the spring load L1 of the first spring member 70, the movable core 22 is in the uppermost original position (F <L1 <L2, F = 0).

  Subsequently, a predetermined small current (such as a driver (not shown) that is controlled by a control signal derived from the control mechanism and supplies the current to the coil 26 to energize the coil 26) by a current value switching device (not shown). For example, by supplying a very small current) to the linear solenoid unit 12, the linear solenoid unit 12 enters the initial valve state. In this initial valve state, as shown in FIG. 2, the first spool 40 and the second spool 42 are not displaced even when a small current is supplied to the linear solenoid portion 12 in the off state. The initial state of the valve, which is the same valve position as the OFF state of the linear solenoid unit 12, is maintained.

  That is, in the initial valve state, a small current is supplied to the linear solenoid portion 12 and a minute electromagnetic thrust F0 is generated by the coil 26. The electromagnetic thrust F0 is generated by the spring load L1 of the first spring member 70 and the first load. The relationship is set such that F0 <L1 <L2 which is smaller than the spring load L2 of the two spring members 72. Therefore, in the initial valve state of the linear solenoid portion 12, the electromagnetic thrust F0 generated in the linear solenoid portion 12 is smaller than the spring load L1 of the first spring member 70 and the spring load L2 of the second spring member 72. Therefore, the driving force is not transmitted to the first spool 40 and the second spool 42, and the first spool 40 and the second spool 42 are in the same manner as in the OFF state of the linear solenoid portion 12. The position is set such that the lower end portion of the first spool 40 and the upper end portion of the second spool 42 overlap.

  Subsequently, the current value (I) is switched by a current value switching device (not shown), and a predetermined intermediate current larger than the small current is supplied to the linear solenoid unit 12 (see FIG. 11), whereby the linear solenoid unit 12 is supplied. Is in the first lift state. In this first lift state, as shown in FIG. 3, the movable core 22 is attracted toward the fixed core 20 by the electromagnetic force (electromagnetic thrust F1) proportional to the current value flowing through the coil 26, and the movable core 22. Stops at an intermediate position.

  That is, the displacement of the movable core 22 and the shaft 34 is transmitted to the first spool 40, and the first spool 40 approaches the second spool 42 side against the spring force (L 1) of the first spring member 70. The first spool 40 is displaced in the direction, and the lower end portion of the first spool 40 comes into contact with the bottom portion 64a of the hollow portion 64 of the second spool 42, so that the displacement is regulated (see FIG. 6).

  Therefore, as shown in FIG. 3, the third land 60c of the first spool 40 and the third annular protrusion 78c of the valve body 18 come into contact with each other, and the communication state between the first inlet port 44a and the first outlet port 46a is established. The valve position is switched to a state where the first inlet port 44a and the second outlet port 46b communicate with each other by the third annular recess 76c formed on the outer peripheral surface of the first spool 40. As a result, the pressure oil introduced from the first inlet port 44a is supplied to the other member 54 via the third annular recess 76c and the second outlet port 46b (OUT2).

  At the same time, as shown in FIG. 6, the second communication hole 62 b of the first spool 40 and the third communication of the second spool 42 at the overlapping portion of the lower end portion of the first spool 40 and the upper end portion of the second spool 42. The hole 62c wraps in a substantially horizontal direction. Therefore, as shown in FIG. 3, the first outlet port 46 a passes through the first communication hole 62 a, the long hole 58, the second communication hole 62 b, and the third communication hole 62 c of the second spool 42. As a result, the pressure port remains in communication with the drain port 48, and the pressure oil remaining in the first outlet port 46a is suitably discharged from the drain port 48.

  In the first lift state in which the current value (I) is switched from the small current in the initial valve state and a predetermined intermediate current larger than the small current is supplied to the linear solenoid unit 12, the spring load of the first spring member 70 Since the electromagnetic thrust F1 larger than L1 and smaller than the spring load L2 of the second spring member 72 is generated in the linear solenoid part 12, the movable core 22 stops at the intermediate position (L1 <F1 <L2). Therefore, only the first spool 40 can be pressed and displaced by the electromagnetic thrust F1 generated in the linear solenoid portion 12, but the second spool 42 cannot be pressed and displaced.

  As a result, in the first lift state, only the first spool 40 is displaced and abuts against the second spool 42 to restrict the displacement, and the second spool 42 is still in its original position.

  In the present embodiment, when the valve is displaced from the initial valve state to the first lift state, a small current is supplied to the linear solenoid unit 12 in advance, so that no current is supplied to the linear solenoid unit 12. Compared with the case where the linear solenoid section 12 is not displaced from the off state (see FIG. 1) to the first lift state (see FIG. 3), the initial valve state can be quickly shifted to the first lift state. The valve operation responsiveness can be improved by suppressing the delay of the valve operation during the control as much as possible.

  In other words, in this embodiment, the linear solenoid unit 12 does not directly shift from the off state (see FIG. 1) to the first lift state (see FIG. 3) of the linear solenoid unit 12, and the off state and the By providing a preparation stage (valve initial state) for supplying a minute current to the linear solenoid unit 12 between the first lift state and the first lift state, as shown in FIG. As a good one, the valve operation responsiveness can be improved.

  Next, the current value (I) is switched and controlled by a current value switching device (not shown), and a predetermined large current larger than the intermediate current is supplied to the linear solenoid unit 12 (see FIG. 11). The second lift state is established. In the second lift state, as shown in FIG. 4, the movable core 22 is further attracted toward the fixed core 20 by the electromagnetic force (electromagnetic thrust F2) proportional to the current value flowing to the coil 26, and the movable core 22 stops at the lowermost position (displacement end position).

  That is, further displacement of the movable core 22 and the shaft 34 is transmitted to the second spool 42 through the first spool 40, and the first spool 40 and the second spool 42 resist the spring force (L 2) of the second spring member 72. Thus, they are integrally displaced in a direction approaching toward the cap member 68 side.

  Therefore, as shown in FIG. 4, the fourth land 60d of the first spool 40 and the fourth annular protrusion 78d of the valve body 18 come into contact with each other, and the communication state between the first inlet port 44a and the second outlet port 46b is established. The valve position is switched to a state where the first inlet port 44a and the first outlet port 46a communicate with each other by the first annular recess 76a formed on the outer peripheral surface of the first spool 40. At the same time, the second inlet port 44b and the third outlet port 46c are in communication with each other through a sixth annular recess 76f formed on the outer peripheral surface of the second spool 42.

  As a result, the pressure oil introduced from the first inlet port 44a is supplied to the other member 54 via the first annular recess 76a and the first outlet port 46a (OUT1), and from the second inlet port 44b. The introduced pressure oil is supplied to the other member 54 via the sixth annular recess 76f and the third outlet port 46c (OUT3).

  The second outlet port 46 b is in communication with the drain port 48 via a fourth annular recess 76 d formed on the outer peripheral surface of the first spool 40, and the pressure oil remaining in the second outlet port 46 b is discharged from the drain port 48. Are preferably discharged.

  In this case, as shown in FIG. 7, the upper end surface of the second spool 42 and the side wall surface of the sixth land 60 f formed on the lower end side of the first spool 40 are set to substantially the same height H. Therefore, the flow of the pressure oil from the second outlet port 46b to the drain port 48 can be made smooth.

  Further, as shown in FIG. 7, the second spool 42 is provided with a stepped through hole 66 penetrating along the axial direction, so that a gap between the lower end of the second spool 42 and the cap member 68 is provided. Can be suitably discharged from the drain port 48 via the stepped through hole 66, the second communication hole 62b, and the third communication hole 62c.

  In the second lift state in which the current value (I) is switched from the intermediate current in the first lift state and a predetermined large current greater than the intermediate current is supplied to the linear solenoid part 12, the spring of the first spring member 40 An electromagnetic thrust F2 that is larger than the load L1 and larger than the spring load L2 of the second spring member 42 is generated in the linear solenoid part 12, so that the movable core 22 stops at the lowest end position (displacement end position) ( L1 <L2 <F2). Therefore, the first spool 40 and the second spool 42 can be pressed almost simultaneously by the electromagnetic thrust F2 generated by the linear solenoid portion 12 to be integrally displaced.

  As a result, in the second lift state, the electromagnetic thrust F2 generated by the linear solenoid portion 12 resists the spring loads L1, L2 of the first spring member 70 and the second spring member 72, respectively, and the first spool 40 and the first By displacing the two spools 42 coaxially, the first inlet port 44a and the first outlet port 46a communicate with each other, and the second inlet port 44b and the third outlet port 46c communicate with each other. The pressure oil can be supplied to the other member 54 through the first outlet port 46a (OUT1) and the third outlet port 46c (OUT3).

  As described above, in this embodiment, the linear solenoid unit 12 is in the off state (see FIG. 1) and the initial valve state (see FIG. 2), and the first lift state in which the intermediate current is supplied to the linear solenoid unit 12 (see FIG. 3). ) And the second lift state (see FIG. 4) in which a large current is supplied to the linear solenoid section 12 can be reliably switched with high accuracy.

  Next, FIG. 13 shows the positional relationship between the first spool 40 and the second spool 42 that are controlled to be switched to the three-stage state.

  As shown in FIG. 13A, in the OFF state and the initial valve state of the linear solenoid portion 12, the first spool 40 and the second spool 42 are not in contact with each other due to the spring force of the first spring member 70. It is set at a position where ends close to each other along the axial direction overlap. In other words, the first spool 40 and the second spool 42 are pressed away from each other by the spring force of the first spring member 70 interposed between the first spool 40 and the second spool 42. The end portion of the first spool 40 and the end portion of the second spool 42 that are close to each other are set to overlap each other.

  Next, as shown in FIG. 13B, in the first lift state, the first spool 40 is displaced toward the second spool 42 against the spring force of the first spring member 70. The position is set such that the first spool 40 and the second spool 42 are in contact with each other. In this case, since the spring load L1 of the first spring member 70 is set to be smaller than the spring load L2 of the second spring member 72, only the first spool 40 slides against the spring force of the first spring member 70. The second spool 42 does not slide.

  Further, as shown in FIG. 13 (c), in the second lift state, the first spool 40 and the second spool 42 are held while the first spool 40 and the second spool 42 are in contact with each other. It is set at a position that is integrally displaced by a predetermined distance toward one end of the valve body 18 against the spring force of the second spring member 72.

  As described above, in the present embodiment, the first spool 40 and the second spool 42 arranged in series and coaxially are set in the positional relationship as described above, whereby the OFF state of the linear solenoid portion 12 and the initial valve state are set. In this state, the pressure of the pressure fluid can be switched and controlled with high accuracy in three stages consisting of a first lift state and a second lift state in which an intermediate current and a large current are respectively supplied to the linear solenoid unit 12.

  Moreover, in this embodiment, as FIG. 1-4 shows, the common single drain port 48 is provided with respect to three ports consisting of the 1st-3rd outlet ports 46a-46c. Therefore, the number of the drain ports 48 can be reduced as compared with a normal case (if there are three output ports, there are two or more drain ports).

  Further, in the present embodiment, as shown in FIG. 7, the lower end portion of the first spool 40 and the upper end portion of the second spool 42 arranged coaxially in the space portion 52 of the valve body 18 are overlapped. Therefore, the axial length of the drain port 48 can be shortened, and the axial dimension of the valve body 18 can be further shortened.

  In this embodiment, the current value (I) energized to the linear solenoid unit 12 by a current value switching device (not shown) is sequentially switched to a small current, an intermediate current, and a large current (see FIG. 11). However, the present invention is not limited to this. For example, as shown in FIG. 12, the current value (I) can be switched from a small current in the initial valve state to a large current in the second lift state. is there. Contrary to the above, in the direction of decreasing the current value (I) energized to the linear solenoid section 12, for example, switching from large current to intermediate current and small current sequentially, or from large current to suddenly small current. Can be switched. Thus, in the present embodiment, the current value (I) energized to the linear solenoid unit 12 by a current value switching device (not shown) is freely switched between three current values of a small current, an intermediate current, and a large current. be able to.

  Next, FIG. 14 shows a comparative example in which the hydraulic pressure can be switched in three stages as in the present embodiment. In this comparative example, the hydraulic pressure is increased by combining two solenoid valves, which are a three-port two-position solenoid valve 100 (hereinafter referred to as a three-way valve 100) and a two-port two-position solenoid valve 110 (hereinafter referred to as a two-way valve 110). Switching control is performed in three stages.

  Schematically explaining the operation of the valve device according to the comparative example, in FIG. 14A, the pressure oil is derived only from OUT1 of the three-way valve 100 by turning off the three-way valve 100 and the two-way valve 110, respectively. I am letting. In FIG. 14B, pressure oil is derived only from OUT2 of the three-way valve 100 by turning on the three-way valve 100 and turning off the two-way valve 110. In FIG. 14C, the pressure oil is led out from OUT1 of the three-way valve 100 by turning off the three-way valve 100 and turning on the two-way valve 110, and at the same time OUT3 of the two-way valve 110. Pressure oil is derived from

  As described above, in the comparative example in which the two solenoid valves of the three-way valve 100 and the two-way valve 110 are combined and controlled to switch the hydraulic pressure to a three-stage state, two solenoid valves are used (two solenoid parts are also included). However, there is a problem that the valve body is increased in size and weight, and the cost is increased.

  In contrast, in the present embodiment, the first spool 40 and the second spool 42 are arranged in series and coaxially in a single main body (a combined body of the housing 14 and the valve body 18), By adopting a configuration in which the first spring member 70 and the second spring member 72 having different spring loads are provided, the overall size and weight of the apparatus can be reduced as compared with the comparative example. Cost can be reduced.

  In the present embodiment, three outlet ports including the first to third outlet ports 46a to 46c are provided. However, another outlet port (not shown) is increased to provide four outlet ports. It may be.

It is a longitudinal cross-sectional view along the axial direction of the electromagnetic spool valve apparatus which concerns on embodiment of this invention. It is a longitudinal cross-sectional view which shows the valve initial state in which the small current was supplied to the said linear solenoid part from the OFF state of the linear solenoid part shown in FIG. FIG. 3 is a longitudinal sectional view showing a first lift state in which an intermediate current is supplied to the linear solenoid portion from the initial valve state of the linear solenoid portion shown in FIG. 2 and the valve position is switched. It is a longitudinal cross-sectional view which shows the 2nd lift state from which the large current was supplied to the said linear solenoid part from the 1st lift state shown in FIG. 3, and the valve position was switched. FIG. 2 is a partially enlarged longitudinal sectional view showing a superimposed portion of a first spool and a second spool constituting the electromagnetic spool valve device in an OFF state of a linear solenoid portion shown in FIG. 1. FIG. 4 is a partially enlarged longitudinal sectional view showing an overlapped portion of a first spool and a second spool in the first lift state shown in FIG. 3. FIG. 5 is a partially enlarged longitudinal sectional view showing an overlapping portion of a first spool and a second spool in the second lift state shown in FIG. 4. It is a longitudinal cross-sectional enlarged view along the axial direction of the 1st spool which comprises the said electromagnetic spool valve apparatus, and a 2nd spool. It is a longitudinal cross-sectional enlarged view along the axial direction of the valve body which comprises the said electromagnetic spool valve apparatus. It is a longitudinal cross-sectional view which shows the state which assembled | attaches a 1st spool and a 2nd spool with respect to the said valve body. FIG. 6 is a characteristic diagram in which a linear solenoid unit in an off state is sequentially switched and supplied to current values including a small current, an intermediate current, and a large current. FIG. 5 is a characteristic diagram in which the linear solenoid unit in the off state is supplied by switching from a small current to a large current value. (A) is a partially omitted longitudinal sectional view showing the positional relationship between the first spool and the second spool in the OFF state and the initial valve state of the linear solenoid part, and (b) is the first spool and the first spool in the first lift state. FIG. 4C is a partially omitted longitudinal sectional view showing the positional relationship between the two spools, and FIG. 6C is a partially omitted longitudinal sectional view showing the positional relationship between the first spool and the second spool in the second lift state. (A)-(c) is a circuit block diagram of the valve apparatus which concerns on a comparative example, respectively.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Electromagnetic spool valve apparatus 12 Linear solenoid part 14 Housing 16 Valve mechanism part 18 Valve body 20 Fixed core 22 Movable core 26 Coil 34 Shaft 40 1st spool 42 2nd spool 44a 1st inlet port 44b 2nd inlet port 46a 1st outlet port 46b 2nd outlet port 46c 3rd outlet port 52 Space part 68 Cap member 70 1st spring member 72 2nd spring member

Claims (1)

A main body including a valve body having a plurality of ports through which pressure fluid flows and a housing;
A linear solenoid portion provided in the housing and having a coil wound around a coil bobbin, and a movable core that is attracted to a fixed core under an energization action on the coil;
The first and second spools are disposed in series and coaxially in the space of the valve body, and are slidably disposed along the space.
The first spool includes at least a first annular recess, a second annular recess, and a third annular recess,
The plurality of ports include at least a first inlet port, a second inlet port, a first outlet port, a second outlet port, and a third outlet port,
A valve mechanism that switches between a communication state and a non-communication state between the plurality of ports corresponding to the positions of the first spool and the second spool;
A first spring member interposed between the first spool and the second spool;
A second spring member interposed between one end of the valve body and the second spool;
With
An initial valve state in which a small current is supplied to the linear solenoid part in the off state, and an intermediate current larger than the small current is supplied to the linear solenoid part, and the movable core is in an intermediate position. Switching control is performed between a first lift state and a second lift state in which a large current is supplied to the linear solenoid portion and the movable core is at a displacement end position;
And in the off state and valve initial state of the linear solenoid portion, the position next to the spring force and the first spool and the second spool portion along the axial direction is superimposed with a non-contact state of the first spring member The first inlet port communicates with the first outlet port by the second annular recess of the first spool, and pressure fluid is led out from the first outlet port ;
In the first lift state, the first spool is displaced toward the second spool against the spring force of the first spring member, so that the first spool and the second spool are in contact with each other. And the first annular port communicates with the second outlet port by the third annular recess of the first spool, and pressure fluid is led out from the second outlet port ,
In the second lift state, the first spool and the second spool resist the spring force of the second spring member while maintaining the state where the first spool and the second spool are in contact with each other. The valve body is integrally displaced by a predetermined distance toward one end side of the valve body, and the first inlet port and the first outlet port are communicated with each other by the first annular recess of the first spool. The electromagnetic fluid characterized in that pressure fluid is led out from the outlet port, and pressure fluid is led out from the third outlet port through communication between the second inlet port and the third outlet port by the second spool. Spool valve device.

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