JP6444566B2 - Solenoid actuator - Google Patents

Description

  The present invention relates to a direct acting solenoid actuator.

  Conventionally, a solenoid actuator is used for switching a cam for opening and closing a valve in an automobile engine, so-called “cam shift”. The solenoid actuator for cam shift has a movable part that can move directly, and a pin is attached to the tip of the movable part. A cam lobe is provided on the outer periphery of the cam shaft, and the cam lobe is provided with a cam and a spiral groove. When the camshaft rotates with the tip of the pin fitted in the spiral groove, the cam lobe moves along the axial direction of the camshaft, and the cam of each cylinder is switched.

  Some cam shift solenoid actuators have a pair of movable parts arranged side by side. Such a solenoid actuator for cam shift is required to make the distance between the axes of the pins arranged in parallel to each other smaller than the distance between the axes of the movable parts arranged in parallel to each other. For this reason, the cam shift solenoid actuator is arranged with the pin axis shifted from the axis of the movable part. Patent Document 1 discloses a linear solenoid device in which the axis of a pin is shifted from the axis of a movable part.

JP-A-5-291030

  In the solenoid actuator for cam shift, a pin is passed through a metal housing. The cam shift solenoid actuator can absorb variations in dimensions of parts such as the movable part and the housing by making the arrangement of the pins relative to the movable part and the housing adjustable.

  In the linear solenoid device of Patent Document 1, a substantially spherical portion (pin 34) protrudes from a peripheral surface portion of a base portion of a pin (fuel metering rack 33), and a distal end portion of a movable portion (output shaft 6). The movable portion and the pin are joined by engaging the substantially spherical portion with the groove portion (grooved connecting pipe 31) provided in the groove (see FIG. 1 of Patent Document 1). For this reason, when adjusting the arrangement of the pins with respect to the movable part, the pin axis is inclined with respect to the axis of the movable part with a substantially spherical portion as a fulcrum.

  In general, a cam shift solenoid actuator has a small distance between an outer peripheral portion of a pin and an inner peripheral portion of a through hole formed in a housing. For this reason, in the structure in which the pin arrangement is tilted and the pin arrangement is adjusted as in the linear solenoid device of Patent Document 1, the pin is linearly moved by mechanical interference between the housing and the tilted pin, so-called “twisting”. There is a problem that the motor is hindered or the load on the actuator is increased.

  The present invention has been made to solve the above-described problems, and in a direct acting solenoid actuator that is arranged by shifting the axis of the pin with respect to the axis of the movable part, the pin axis is not inclined. It aims at making pin arrangement adjustable.

The solenoid actuator of the present invention is passed through a coil, and a movable part that can move linearly along the axial direction by energization of the coil, a pin that is arranged with its axis shifted with respect to the movable part, and a tip of the movable part A plate-like joint that joins the base portion of the pin and the pin, the pin is attached to the joint by engagement of the recess provided in the joint and the groove provided in the peripheral surface portion of the pin , The thickness of the part where the pin is attached is thinner than the thickness of the part where the movable part is attached .

  According to the present invention, in a direct acting solenoid actuator that is arranged by shifting the pin axis with respect to the axis of the movable part, the pin arrangement can be adjusted without tilting the pin axis.

It is sectional drawing which shows the principal part of the solenoid actuator which concerns on Embodiment 1 of this invention. FIG. 2A is an explanatory diagram illustrating a state in which the first joint and the first pin according to Embodiment 1 of the present invention are viewed from above. FIG. 2B is an explanatory diagram illustrating a state in which the first joint and the first pin according to Embodiment 1 of the present invention are viewed from the front. FIG. 3A is an explanatory diagram illustrating a state in which the second joint and the second pin according to Embodiment 1 of the present invention are viewed from above. FIG. 3B is an explanatory diagram illustrating a state in which the second joint and the second pin according to Embodiment 1 of the present invention are viewed from the front. In the solenoid actuator which concerns on Embodiment 1 of this invention, it is explanatory drawing which shows the state which enlarged the space | interval between the shafts of a pin. In the solenoid actuator which concerns on Embodiment 1 of this invention, it is explanatory drawing which shows the state which made the space | interval between the shafts of a pin small. It is an enlarged view of the area | region containing the front-end | tip part of a 1st movable part, the boss | hub, a 1st joint, and the root part of a 1st pin in the solenoid actuator which concerns on Embodiment 1 of this invention. It is an enlarged view of the area | region containing the front-end | tip part of a 1st movable part, the boss | hub, a 1st joint, and the root part of a 1st pin in the solenoid actuator used as a comparison object with the solenoid actuator shown in FIG. It is an enlarged view of the area | region containing the front-end | tip part of a 2nd movable part, the boss | hub, a 2nd joint, and the root part of a 2nd pin in the solenoid actuator which concerns on Embodiment 1 of this invention. In the solenoid actuator according to the first embodiment of the present invention, a region including the distal end portion of the first movable portion, the distal end portion of the second movable portion, the boss, the first joint, the second joint, the first pin, the second pin, and the housing. FIG. In the solenoid actuator which concerns on Embodiment 1 of this invention, it is explanatory drawing which shows the state which made the 1st pin into the ON position. In the solenoid actuator which concerns on Embodiment 1 of this invention, it is explanatory drawing which shows the state which made the 2nd pin into the ON position.

Hereinafter, in order to explain the present invention in more detail, modes for carrying out the present invention will be described with reference to the accompanying drawings.
Embodiment 1 FIG.
FIG. 1 is a cross-sectional view showing a main part of a solenoid actuator according to Embodiment 1 of the present invention. A solenoid actuator 100 according to the first embodiment will be described with reference to FIG.

  In the figure, 1 is a mold part. The mold part 1 is made of a resin such as PPS (Polyphenylene Sulphide). Metal cases 8a and 8b are provided in the mold part 1, and the first coil 2a and the second coil 2b are arranged in parallel in the cases 8a and 8b. The case 8a in which the first coil 2a is accommodated and the case 8b in which the second coil 2b is accommodated are configured as separate members.

  A first movable part 3a is passed through the first coil 2a. The first movable part 3a is constituted by, for example, a movable iron core (hereinafter referred to as “plunger”) or the like, and has a shape in which a substantially rod-like projecting part projects from one end of a substantially cylindrical body part. The first movable portion 3a is linearly movable along the axial direction (the direction along the axis A1 in the figure) by energization of the first coil 2a. The linear motion principle of the first movable part 3a may be any of a so-called “push solenoid”, “self-holding solenoid” or “pull solenoid”.

  A second movable part 3b is passed through the second coil 2b. The 2nd movable part 3b is comprised by the plunger etc., for example, and is a shape where the substantially rod-shaped protrusion part protruded from the one end part of the substantially cylindrical main-body part. The second movable portion 3b is linearly movable along the axial direction (the direction along the axis A2 in the figure) by energization of the second coil 2b. The linear movement principle of the second movable portion 3b may be any of so-called “push solenoid”, “self-holding solenoid”, or “pull solenoid”.

  That is, the axis A1 of the first movable part 3a and the axis A2 of the second movable part 3b are arranged so as to face each other. The linear motion direction of the first movable part 3a and the linear motion direction of the second movable part 3b are set in the same direction.

  The protruding part of the first movable part 3a is passed through a through hole 41a formed in a substantially plate-like part of the boss 4. The protruding part of the second movable part 3b is passed through a through hole 41b formed in a substantially plate-like part of the boss 4. The boss 4 is made of a metal such as SUM or SWCH.

  A substantially plate-like first joint 5a is attached to the tip of the protruding portion of the first movable portion 3a. Specifically, for example, the first joint 5a is made of a non-magnetic material such as SUS, and the tip of the first movable portion 3a is passed through the through hole 51a formed in the first joint 5a. The first joint 5a is fixed to the first movable part 3a by welding or press-fitting the tip of the first movable part 3a into the through hole 51a.

  A substantially plate-like second joint 5b is attached to the tip of the protruding portion of the second movable portion 3b. Specifically, for example, the second joint 5b is made of a nonmagnetic material such as SUS, and the distal end portion of the second movable portion 3b is passed through the through hole 51b formed in the second joint 5b. The second joint 5b is fixed to the second movable portion 3b by welding or press-fitting the tip of the second movable portion 3b into the through hole 51b.

  A root portion of a substantially rod-shaped first pin 6a is attached to the first joint 5a. A root portion of a substantially rod-shaped second pin 6b is attached to the second joint 5b. That is, the first joint 5a joins the tip of the first movable part 3a and the root of the first pin 6a, and the second joint 5b connects the tip of the second movable part 3b and the second pin 6b. It joins the root part. The first pin 6a and the second pin 6b are made of a magnetic material such as SCM, for example.

  The axis A3 of the first pin 6a is arranged so as to be aligned with the axis A1 of the first movable part 3a, and is shifted from the axis A1 of the first movable part 3a. The axis A4 of the second pin 6b is arranged so as to be aligned with the axis A2 of the second movable part 3b, and is offset from the axis A2 of the second movable part 3b. The distance L1 between the axis A3 of the first pin 6a and the axis A4 of the second pin 6b is set to a different value with respect to the distance L2 between the axis A1 of the first movable part 3a and the axis A2 of the second movable part 3b. ing. In the example of FIG. 1, the interval L1 is set to a value smaller than the interval L2.

  The first pin 6 a is passed through a through hole 71 a formed in the housing 7, and a tip portion projects from the housing 7. The second pin 6 b is passed through a through hole 71 b drilled in the housing 7, and the tip portion projects from the housing 7. The housing 7 is made of a metal such as S25C, for example.

  The first coil 2a, the first movable part 3a, the first joint 5a and the first pin 6a, and the second coil 2b, the second movable part 3b, the second joint 5b and the second pin 6b are with respect to the symmetry axis A5. And is substantially line symmetrical. Mold part 1, first coil 2a, second coil 2b, first movable part 3a, second movable part 3b, boss 4, first joint 5a, second joint 5b, first pin 6a, second pin 6b, housing 7 and cases 8a and 8b constitute the main part of the solenoid actuator 100.

  Hereinafter, the first coil 2a and the second coil 2b may be collectively referred to simply as “coils”. The first movable part 3a and the second movable part 3b may be collectively referred to simply as “movable part”. The first joint 5a and the second joint 5b may be collectively referred to simply as “joint”. The first pin 6a and the second pin 6b may be collectively referred to simply as “pin”.

  The solenoid actuator 100 is used, for example, for cam shift of an automobile engine. That is, when a power source (not shown) energizes the first coil 2a, the first coil 2a functions as an electromagnet, and the first movable portion 3a moves linearly along the axial direction. At this time, the 1st joint 5a and the 1st pin 6a move linearly integrally with the 1st movable part 3a. When a power source (not shown) energizes the second coil 2b, the second coil 2b functions as an electromagnet, and the second movable portion 3b moves linearly along the axial direction. At this time, the second joint 5b and the second pin 6b move linearly integrally with the second movable portion 3b.

  The solenoid actuator 100 includes a position where the distal end portion of the first pin 6a enters a spiral groove (not shown) (hereinafter referred to as “ON position”) and a distal end portion of the first pin 6a due to the direct movement of the first movable portion 3a. Can be switched from a position where it is disengaged from the spiral groove of the cam lobe (hereinafter referred to as “OFF position”). The solenoid actuator 100 can be switched between the ON position and the OFF position of the second pin 6b by the direct movement of the second movable portion 3b.

  FIG. 1 shows a state in which the first pin 6a is in the OFF position and the second pin 6b is in the ON position. As shown in FIG. 1, the protrusion length of the pins 6a and 6b with respect to the housing 7 is longer at the ON position than at the OFF position.

  Next, the detailed structure of the solenoid actuator 100 will be described with reference to FIGS. Hereinafter, an example in which the solenoid actuator 100 is applied to a cam shift of an automobile engine will be mainly described. That is, the solenoid actuator 100 is disposed above the automobile engine. In addition, the solenoid actuator 100 is disposed so that the axes A1 to A4 are along the vertical direction or the axes A1 to A4 are tilted with respect to the vertical direction and the tips of the pins 6a and 6b are directed downward.

  FIG. 2A shows a state in which the first joint 5a and the first pin 6a of the first embodiment are viewed from above. FIG. 2B shows a state in which the first joint 5a and the first pin 6a of Embodiment 1 are viewed from the front.

  As shown in FIG. 2A, the first joint 5a is provided with a U-shaped recess 52a. Further, as shown in FIG. 2B, a groove portion 61a is provided at the root portion of the first pin 6a over the entire circumference of the peripheral surface portion. That is, as for the 1st pin 6a, the site | part which provided the groove part 61a is diameter-reduced with respect to the remaining site | parts. A terminal flange 62a is provided at one end of the groove 61a, and a middle flange 63a is provided at the other end. The end flange part 62a is continuous with the end surface part 64a of the first pin 6a.

  Here, the attachment of the first pin 6a to the first joint 5a is due to the engagement between the recess 52a and the groove 61a, as indicated by the arrow I in the figure. Therefore, in a state where the first pin 6a is attached to the first joint 5a, the first pin 6a is movable along the depth direction of the recess 52a (the direction along the arrow I in the figure). For this reason, the arrangement of the first pin 6a with respect to the first movable part 3a and the housing 7 can be adjusted, and variations in component dimensions of the first movable part 3a and the housing 7, for example, the housing 7 with respect to the axis A1 of the first movable part 3a. The variation in the position of the through hole 71a can be absorbed.

  Further, the first pin 6a can move in a state where both the axes A1 and A3 are kept parallel without tilting the axis A3 with respect to the axis A1 of the first movable portion 3a. For this reason, it can prevent that the linear motion of the 1st pin 6a is prevented by the prying between the housing 7 and the 1st pin 6a, or the load of the solenoid actuator 100 increases.

  Further, the linear solenoid device of Patent Document 1 has a structure in which the movable portion and the pin are joined by a substantially spherical portion formed at the root portion of the pin. For this reason, spherical processing is required to form a substantially spherical portion, and there is a problem that processing is difficult and manufacturing cost increases. On the other hand, the solenoid actuator 100 according to the first embodiment has a structure in which the first movable portion 3a and the first pin 6a are joined by a substantially plate-like first joint 5a. The substantially plate-like first joint 5a can be easily and inexpensively manufactured by punching or forging a sheet metal, and the manufacturing cost can be reduced.

  The attachment of the second pin 6b to the second joint 5b is the same as the attachment of the first pin 6a to the first joint 5a. That is, as shown in FIG. 3A, the second joint 5b is provided with a U-shaped notch-shaped recess 52b. As shown in FIG. 3B, a groove 61b is provided at the base of the second pin 6b, and an end flange 62b and a middle flange 63b are provided at both ends of the groove 61b. The end flange portion 62b is continuous with the end surface portion 64b of the second pin 6b. The attachment of the second pin 6b to the second joint 5b is due to the engagement between the recess 52b and the groove 61b, as indicated by the arrow II in the figure.

  The shapes of the recesses 52a and 52b are not limited to the U-shaped notch. The recesses 52a and 52b may be, for example, V-shaped cutouts or square cutouts. Further, the shape of the recess 52a related to the first joint 5a and the shape of the recess 52b related to the second joint 5b may be different from each other.

  Further, the grooves 61a and 61b only need to be engageable with the recesses 52a and 52b of the joints 5a and 5b. The grooves 61a and 61b are provided only on a part of the peripheral surface instead of the entire periphery of the peripheral surfaces of the pins 6a and 6b. It may be.

  FIG. 4 shows a state in which the distance L1 between the axes A3 and A4 of the pins 6a and 6b is larger than the state shown in FIG. 5 in the solenoid actuator 100 of the first embodiment. FIG. 5 shows a state in which the distance L1 between the axes A3 and A4 of the pins 6a and 6b is smaller than the state shown in FIG. 4 in the solenoid actuator 100 of the first embodiment.

  As shown in FIGS. 4 and 5, the depth D1 of the recess 52a is set to a value larger than the diameter Φ1 of the portion where the groove 61a of the first pin 6a is provided. The depth D2 of the recess 52b is set to a value larger than the diameter Φ2 of the portion where the groove 61b of the second pin 6b is provided.

  Thereby, while the movement width of the 1st pin 6a along the depth direction of the recessed part 52a can be enlarged, the movement width of the 2nd pin 6b along the depth direction of the recessed part 52b can be enlarged. As a result, the interval L1 between the axes A3 and A4 can be increased as shown in FIG. 4, or the interval L1 between the axes A3 and A4 can be reduced as shown in FIG. 5, and the adjustment width of the interval L1 can be increased. can do.

  In general, the distance L1 between the axes A3 and A4 of the pins 6a and 6b may be changed according to the specifications of an application such as a cam shift mechanism. On the other hand, by setting the depths D1 and D2 of the recesses 52a and 52b to a value larger than the diameters Φ1 and Φ2 of the pins 6a and 6b, even if there is a change in application specifications, The redesign and remanufacturing of 5b are unnecessary, and the change of the interval L1 can be dealt with only by redesigning and remanufacturing the housing 7. That is, it is possible to reduce costs by reducing the man-hours for responding to the specification change.

  FIG. 6 shows the tip of the first movable part 3a, the boss 4, the first joint 5a, and the root part of the first pin 6a in the solenoid actuator 100 of the first embodiment. FIG. 7 shows the tip of the first movable portion 3a ′, the boss 4 ′, the first joint 5a ′, and the root of the first pin 6a ′ in the solenoid actuator 100 ′ to be compared with the solenoid actuator 100 shown in FIG. Is shown.

  As described above, the attachment of the joints 5a and 5b to the movable parts 3a and 3b is by welding or press-fitting. For this reason, the thickness of the joints 5a and 5b is required to be thick enough to withstand welding or press fitting. On the other hand, in general, the cam shift solenoid actuator 100 is disposed above the automobile engine so that the axes A1 to A4 are along the vertical direction. Above the automobile engine, the space between the bonnet is narrow and the axial length of the entire solenoid actuator 100 is required to be as short as possible even in units of millimeters or less. Here, by reducing the thickness of the joints 5a and 5b, the axial length between the boss 4 and the intermediate flange portions 63a and 63b can be shortened, and the axial length of the solenoid actuator 100 as a whole can be shortened.

  Therefore, as shown in FIG. 6, the first joint 5a of the first embodiment has a thickness T1 of a portion where the root portion of the first pin 6a is attached, that is, a portion where the concave portion 52a is provided, and the tip of the first movable portion 3a. It is thinner than the thickness T2 of the part to which the part is attached. Specifically, the 1st joint 5a has the removal part 53a formed by removing the area | region containing the surface part which opposes the boss | hub 4 in the site | part which attaches the 1st pin 6a, and thickness is removed by the removal part 53a. T1 is thinner than the wall thickness T2.

  Thereby, thickness T2 of the site | part which attaches the 1st movable part 3a can be thickened, and it can endure welding or press fit. On the other hand, the thickness T1 of the portion where the first pin 6a is attached can be reduced, the axial length L3 between the boss 4 and the intermediate collar portion 63a can be shortened, and the axial length of the solenoid actuator 100 as a whole can be shortened.

  In FIG. 7, as a comparison object with the solenoid actuator 100 shown in FIG. 6, the thickness T ′ of the first joint 5a ′ is set to a constant value (specifically, a value equivalent to the thickness T2 shown in FIG. 6). A solenoid actuator 100 ′ is shown. The axial length L3 'between the boss 4' and the middle collar portion 63a 'shown in FIG. 7 is longer than the axial length L3 between the boss 4 and the middle collar portion 63a shown in FIG. Therefore, the solenoid actuator 100 of the first embodiment shown in FIG. 6 is more suitable for cam shift than the solenoid actuator 100 ′ to be compared shown in FIG. 7.

  The second joint 5b is configured similarly to the first joint 5a. That is, as shown in FIG. 8, the second joint 5b has a removal portion 53b. Due to the removal part 53b, the thickness T3 of the part to which the second pin 6b is attached is thinner than the thickness T4 of the part to which the first movable part 3a is attached. Thereby, it can endure welding or press fit, and the axial length L4 between the boss | hub 4 and the intermediate collar part 63b can be shortened, and the axial length of the solenoid actuator 100 whole can be shortened.

  FIG. 9 shows the distal end portion of the first movable portion 3a, the distal end portion of the second movable portion 3b, the boss 4, the first joint 5a, the second joint 5b, the first pin 6a, the first pin in the solenoid actuator 100 of the first embodiment. 2 pin 6b and housing 7 are shown.

  As shown in FIG. 9, a substantially cylindrical convex portion 65a is provided at the center of the end surface portion 64a of the first pin 6a. A substantially cylindrical convex portion 65b is provided at the center of the end surface portion 64b of the second pin 6b. Due to the convex portions 65a and 65b, the distance L5 between the boss 4 and the pins 6a and 6b is set to a value smaller than the distance L6 between the boss 4 and the joints 5a and 5b. That is, regardless of the linear movement position of the pins 6a and 6b, the upper ends of the pins 6a and 6b are arranged closer to the boss 4 than the upper ends of the joints 5a and 5b. As a result, the joints 5 a and 5 b do not contact the boss 4 at the OFF position, and the convex portions 65 a and 65 b of the pins 6 a and 6 b contact the boss 4.

  If the distance L5 between the pins 6a, 6b and the boss 4 is larger than the distance L6 between the joints 5a, 5b and the boss 4, the lower end position (ON position) of the linear movement of the pins 6a, 6b is the pin 6a. , 6b is determined by the abutment between the intermediate flange portions 63a, 63b and the housing 7, while the linear motion upper end position (OFF position) of the pins 6a, 6b is determined by the abutment between the joints 5a, 5b and the boss 4. In other words, in such a structure, the dimensional accuracy of the four components of the boss 4, the joints 5a and 5b, the pins 6a and 6b, and the housing 7 affects the variation in the linear motion width.

  On the other hand, by adopting a structure in which the distance L5 between the pins 6a, 6b and the boss 4 is smaller than the distance L6 between the joints 5a, 5b and the boss 4, the lower end position (ON position) of the linear movement of the pins 6a, 6b. Is determined by the contact between the intermediate flange portions 63a and 63b of the pins 6a and 6b and the housing 7, and the upper end position (OFF position) of the linear motion of the pins 6a and 6b is the convex portions 65a and 65b of the pins 6a and 6b. It is determined by contact with the boss 4. That is, in such a structure, the dimensional accuracy of the three parts of the boss 4, the pins 6a and 6b, and the housing 7 affects the variation in the linear motion width. Thus, by reducing the types of parts that affect the variation in the linear motion width of the pins 6a and 6b, the variation in the linear motion width of the pins 6a and 6b can be suppressed.

  In addition, instead of providing the convex portions 65a and 65a on the end surface portions 64a and 64b of the pins 6a and 6b, for example, a structure in which the interval L5 is reduced by increasing the thickness of the end flange portions 62a and 62b may be used. , Variation in the linear motion width of the pins 6a and 6b can be suppressed. However, in the cam shift solenoid actuator 100, it is more preferable to provide the convex portions 65a and 65a as follows.

  That is, the cam shift solenoid actuator 100 rotates and moves the camshaft with the tip ends of the pins 6a and 6b fitted in the spiral grooves of the cam lobe, so that the pins 6a and 6b are large at the ON position. A load is added. In order to withstand this load, it is preferable to harden the pins 6a and 6b by a process such as so-called “quenching”. Usually, the material of the pins 6a and 6b whose hardness is improved by quenching is martensite, that is, a magnetic material. Although it is technically possible to improve the hardness while the pins 6a and 6b are made of a non-magnetic material, it is impractical from the viewpoint of manufacturing cost and the like because it requires treatment such as nitriding, plating or coating. It is.

  Here, when the solenoid actuator 100 fulfills the function of an electromagnet by energizing the coils 2a and 2b, the solenoid actuator 100 is made of a metal that covers the plungers of the movable portions 3a and 3b, the metal boss 4 and the outer peripheral portions of the coils 2a and 2b. A magnetic path is formed by the cases 8a and 8b. When the pins 6a and 6b, which are magnetic bodies, come into contact with the metal boss 4 at the OFF position, the pins 6a and 6b and the boss 4 are electromagnetically connected. As a result, the pins 6a and 6b serve as a magnetic path, and part of the magnetic flux generated by energization of the coils 2a and 2b leaks to the pins 6a and 6b, so that the electromagnetic force is reduced, that is, the responsiveness of the solenoid actuator 100. There is a problem that decreases. In order to prevent this problem, it is required to reduce the contact area between the pins 6a and 6b and the boss 4 at the OFF position.

  By providing the convex portions 65a and 65a on the end surface portions 64a and 64b of the pins 6a and 6b, the interval L5 becomes smaller than the interval L6, and the contact area between the pins 6a and 6b and the boss 4 at the OFF position Can be reduced. As a result, variations in the linear motion width of the pins 6a and 6b can be suppressed, and the efficiency of the solenoid actuator 100 can be prevented from decreasing due to a decrease in electromagnetic force.

  The shape of the convex portions 65a and 65b is not limited to a substantially cylindrical shape. The convex portions 65a and 65b may be, for example, a substantially prismatic shape, a substantially conical shape, a substantially pyramidal shape, or a substantially hemispherical shape. By making the convex portions 65a and 65b into a substantially conical shape, a substantially pyramidal shape, or a substantially hemispherical shape, the contact area between the pins 6a and 6b and the boss 4 at the OFF position can be further reduced.

  FIG. 10 shows a state where the first pin 6a is in the ON position in the solenoid actuator 100 of the first embodiment. FIG. 11 shows a state where the second pin 6b is in the ON position in the solenoid actuator 100 of the first embodiment.

  As shown in FIG. 10, when the first pin 6 a is in the ON position, the intermediate flange portion 63 a of the first pin 6 a is sandwiched between the first joint 5 a and the housing 7. Thereby, the vibration of the 1st pin 6a in an ON position can be suppressed. That is, the earthquake resistance of the solenoid actuator 100 can be improved.

  As shown in FIG. 11, when the second pin 6 b is in the ON position, the intermediate flange portion 63 b of the second pin 6 b is sandwiched between the second joint 5 b and the housing 7. Thereby, the vibration of the 2nd pin 6b in an ON position can be suppressed. That is, the earthquake resistance of the solenoid actuator 100 can be improved.

  The application of the solenoid actuator 100 is not limited to the cam shift of an automobile engine. The solenoid actuator 100 can be used for any application as long as it is a general linear actuator. Moreover, the solenoid actuator 100 may have one each of the coils 2a and 2b, the movable parts 3a and 3b, the joints 5a and 5b, and the pins 6a and 6b, or three or more of each. The number of these members may be any number depending on the application of the solenoid actuator 100.

  Further, the shape of the joints 5a and 5b may be a substantially plate shape as shown in FIGS. 1 to 11, and may not be a strict plate shape. The meaning of the term “plate shape” described in the claims of the present application is not limited to a strict plate shape, but includes such a substantially plate shape.

  As described above, the solenoid actuator 100 according to the first embodiment is passed through the coils 2a and 2b, and is movable with the movable portions 3a and 3b that are linearly movable along the axial direction when the coils 2a and 2b are energized. Pins 6a and 6b arranged with their axes shifted relative to the parts 3a and 3b, and plate-like joints 5a and 5b that join the distal ends of the movable parts 3a and 3b and the roots of the pins 6a and 6b. The pins 6a and 6b are attached to the joints 5a and 5b by engagement between the recesses 52a and 52b provided in the joints 5a and 5b and the grooves 61a and 61b provided in the peripheral surface portions of the pins 6a and 6b. Thereby, the arrangement of the pins 6a and 6b with respect to the movable parts 3a and 3b and the housing 7 can be adjusted without tilting the axes A3 and A4 of the pins 6a and 6b with respect to the axes A1 and A2 of the movable parts 3a and 3b. Variations in the dimensions of parts such as the movable parts 3a and 3b and the housing 7 can be absorbed. Further, a substantially spherical portion is unnecessary for joining the movable parts 3a, 3b and the pins 6a, 6b, and the plate-like joints 5a, 5b can be easily and inexpensively manufactured by punching or forging a sheet metal. Therefore, the manufacturing cost of the solenoid actuator 100 can be reduced.

  In addition, the depth D1 of the recess 52a provided in the first joint 5a is set to a value larger than the diameter Φ1 of the portion where the groove 61a of the first pin 6a is provided, and is provided in the second joint 5b. The depth D2 of the recess 52b is set to a value larger than the diameter Φ2 of the portion where the groove 61b of the second pin 6b is provided. Thereby, the adjustment width | variety of the space | interval L1 between axis | shafts A3 and A4 of pin 6a, 6b can be enlarged. As a result, even when the interval L1 is changed due to a change in the specification of the application, it is not necessary to redesign and remanufacture the joints 5a and 5b, and the number of man-hours for responding to the specification change can be reduced.

  Further, in the joints 5a and 5b, the thickness T1 of the portion to which the pins 6a and 6b are attached is thinner than the thickness T2 of the portion to which the movable parts 3a and 3b are attached. Thereby, it is possible to endure welding or press-fitting by increasing the thickness T2 of the portion to which the movable parts 3a and 3b are attached, and the solenoid actuator 100 by reducing the thickness T1 of the portion to which the pins 6a and 6b are attached. The overall axial length can be shortened.

  The movable portions 3a and 3b are passed through the boss 4, and the interval L5 between the pins 6a and 6b and the boss 4 is set to a value smaller than the interval L6 between the joints 5a and 5b and the boss 4. As a result, the types of components that affect the variation in the linear motion width of the pins 6a and 6b are reduced, and the variation in the linear motion width of the pins 6a and 6b can be suppressed.

  Further, the pins 6a and 6b are made of a magnetic material, and the distance L5 between the pins 6a and 6b and the boss 4 is formed by the convex portions 65a and 65b provided on the end surface portions 64a and 64b at the roots of the pins 6a and 6b. Is set to a value smaller than the distance L6 between the joints 5a, 5b and the boss 4. Thereby, while using the pins 6a and 6b whose hardness is improved by quenching, variation in the linear motion width of the pins 6a and 6b is suppressed, and the pins 6a and 6b and the boss 4 are electromagnetically connected to reduce the electromagnetic force. Can be suppressed.

  Further, the pins 6a and 6b are passed through the housing 7, and by the direct movement of the movable portions 3a and 3b, the flange portions (the intermediate flange portions 63a and 63b) provided on the pins 6a and 6b are connected to the joints 5a and 5b and the housing. 7 between. Thereby, the vibration of the pins 6a and 6b at the ON position can be suppressed, and the earthquake resistance of the solenoid actuator 100 can be improved.

  The movable parts 3a and 3b have a first movable part 3a and a second movable part 3b arranged in parallel with the directions of the axes A1 and A2 being aligned, and the pins 6a and 6b are connected to each other with an axis A3. , A4, the first pin 6a and the second pin 6b arranged in parallel, and the joints 5a and 5b include a first joint 5a that joins the first movable part 3a and the first pin 6a to each other. The second movable part 3b and the second joint 5b for joining the second pin 6b are provided. Thereby, the solenoid actuator 100 for cam shift can be obtained.

  In the present invention, any component of the embodiment can be modified or any component of the embodiment can be omitted within the scope of the invention.

  The solenoid actuator of the present invention can be used, for example, for a cam shift of an automobile engine.

  DESCRIPTION OF SYMBOLS 1 Mold part, 2a 1st coil, 2b 2nd coil, 3a 1st movable part, 3b 2nd movable part, 4 boss, 5a 1st joint, 5b 2nd joint, 6a 1st pin, 6b 2nd pin, 7 Housing, case 8a, 8b, 41a, 41b through hole, 51a, 51b through hole, 52a, 52b recess, 53a, 53b removal part, 61a, 61b groove part, 62a, 62b end flange part, 63a, 63b middle flange part, 64a , 64b end face part, 65a, 65b convex part, 71a, 71b through hole, 100 solenoid actuator.

Claims (6)

A movable part that is passed through the coil and is linearly movable along the axial direction by energization of the coil;
A pin arranged with its axis shifted with respect to the movable part;
A plate-like joint that joins the tip of the movable part and the root of the pin;
The pin is attached to the joint by the engagement of the recess provided in the joint and the groove provided in the peripheral surface portion of the pin ,
The solenoid is a solenoid actuator characterized in that a thickness of a portion to which the pin is attached is thinner than a thickness of a portion to which the movable part is attached . The movable part has a first movable part and a second movable part arranged in parallel with the directions of the axes of each other,
The pin has a first pin and a second pin that are arranged side by side so that the directions of their axes are aligned,
The joint includes a first joint that joins between the first movable part and the first pin, and a second joint that joins between the second movable part and the second pin,
The depth of the concave portion provided in the first joint is set to a value larger than the diameter of the portion where the groove portion of the first pin is provided,
2. The solenoid actuator according to claim 1, wherein a depth of the concave portion provided in the second joint is set to a value larger than a diameter of a portion of the second pin where the groove portion is provided. The movable part is passed through a boss,
The solenoid actuator according to claim 1, wherein a distance between the pin and the boss is set to be smaller than a distance between the joint and the boss. The pin is made of a magnetic material,
By the convex portion provided on an end face of the root portion of the pin, according to claim 3, wherein the distance between said pin and said boss characterized in that it is set to a value smaller than the spacing between the joint and the boss Solenoid actuator. The pin is passed through the housing;
The solenoid actuator according to claim 1, wherein a flange provided on the pin is sandwiched between the joint and the housing by the linear movement of the movable part. The movable part has a first movable part and a second movable part arranged in parallel with the directions of the axes of each other,
The pin has a first pin and a second pin that are arranged side by side so that the directions of their axes are aligned,
The joint includes a first joint that joins between the first movable part and the first pin, and a second joint that joins between the second movable part and the second pin. Item 10. The solenoid actuator according to Item 1.

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