JP5458653B2 - Linear bearing assembly - Google Patents

Description

The present invention relates to a linear bearing assembly.

  The cage for linear bearings used in the linear solenoid valve holds the ball in a rollable state with the cage, but this type of cage is made of an injection mold or machining. (For example, see Patent Document 1 and Patent Document 2).

Japanese Utility Model Publication No. 5-1022 Japanese Patent Laid-Open No. 5-126275

However, when the cage shown in Patent Document 1 and Patent Document 2 is manufactured by resin molding, it is a cylindrical part, and it is necessary to slide the mold forming the steel ball holding pocket in the circumferential direction. The mold becomes complicated and the cost increases. Further, when manufacturing by cutting such as a lathe, the processing is complicated and the cost is similarly increased.
The present invention has been made in order to solve the above-described problems. The movable shaft that drives or drives an actuator or the like, and a circumference perpendicular to a cylindrical body arranged coaxially with the movable shaft are equally spaced. The bearing cage (cage) having a bearing ball holding pocket disposed on the bearing, the bearing steel ball held in a rolling manner in the steel ball holding pocket of the cage and in contact with the main shaft, and arranged coaxially with the main shaft An object of the present invention is to provide a linear bearing assembly that has a cylindrical outer ring that comes into contact with the above-described bearing steel ball, and that allows the outer ring and the movable shaft to move slidably .

The invention according to claim 1 for solving the above-mentioned problems is as follows.
A bearing cage molded into a regular polygon;
A substantially rectangular first steel ball holding pocket formed at a corner of each surface of the bearing cage;
A substantially circular second steel ball holding pocket formed on each surface of the bearing cage;
A steel ball holding relief provided close to the first steel ball holding pocket;
A first protrusion formed in the width direction of each surface in the first steel ball holding pocket;
Substantially rectangular second and third protrusions formed in the second steel ball holding pocket in the axial direction of each surface and in the width direction perpendicular to the axial direction;
With
The first protrusion is bent inward with respect to each surface, the second protrusion is bent inward with respect to each surface, and the third protrusion is bent outward with respect to each surface. The steel balls are bent, the steel balls are fitted into the first and second steel ball holding pockets, and the steel balls are rotatably supported by the first to third protrusions.

According to the present invention, since the steel ball holding pockets can be arranged in the plane part and the corner part of the polygonal column, it is possible to arrange the steel balls in a shifted phase. Furthermore, by holding the steel balls using the corners, it is possible to reduce the number of locations where the steel ball holding parts are installed by bending, and the cost is reduced because the structure is simple and easy to manufacture. Can do.
The linear bearing assembly of claim 2, wherein
Since the bearing retainer has the first steel ball retaining pocket and the second steel ball retaining pocket arranged on the outer side in the axial direction of the opposing first steel ball retaining pocket, Since the play of the linear bearing that supports the shaft can be reduced, it is preferable.

According to the present invention, since the steel ball holding pockets can be arranged in the plane part and the corner part of the polygonal column, the phases of the steel balls can be arranged out of phase. In addition, by holding the steel balls using the corners, it is possible to reduce the number of locations where the steel ball holding parts are installed by bending, and the structure is simple and easy to manufacture, reducing costs. Can do.
Furthermore, since the thin plate-shaped polygonal linear bearing assembly by press working is used, the fluid resistance during the movement of the linear bearing assembly can be reduced, so that the responsiveness of the linear solenoid valve can be improved.

It is a longitudinal section showing a schematic structure of a linear solenoid valve concerning an embodiment of the invention. FIG. 2 is an enlarged detail view of a main part of the linear bearing assembly of FIG. 1. It is an external view of the linear bearing retainer of FIG. It is an expanded view of a linear bearing retainer. It is sectional drawing of the VV line of FIG. It is sectional drawing of the VI-VI line of FIG. It is sectional drawing of the VII-VII line of FIG. It is a principal part expansion perspective view of the 1st steel ball holding pocket of FIG. It is a principal part expansion perspective view of the 2nd steel ball holding pocket of FIG. (A) is an external view of the linear bearing assembly which concerns on 2nd embodiment. (B) is a development view of the material (a). (A) is an external view of the linear bearing assembly which concerns on 3rd embodiment. (B) is a development view of the material (a). (A) is an external view of the linear bearing assembly which concerns on 4th embodiment. (B) is a development view of the material (a). (A) is an external view of the linear bearing assembly which concerns on 5th embodiment. (B) is a schematic side view of (a). (C) is a development view of the material (a). (A) is an external view of the linear bearing assembly which concerns on 6th embodiment. (B) is a schematic side view of (a). (C) is a development view of the material (a).

An embodiment of a linear solenoid valve of the present invention will be given and described in detail with reference to the accompanying drawings. FIG. 1 is a longitudinal sectional view showing a schematic structure of a linear solenoid valve 10 according to an embodiment of the present invention.
As shown in FIG. 1, the linear solenoid valve 10 includes a pressure regulating valve portion 12 and an electromagnet portion 13. Further, the pressure regulating valve portion 12 includes a valve sleeve 15 and a spool 16, and the valve sleeve 15 has a hole 19 that accommodates a spring 17 in the inner axial direction thereof, and subsequently a large guide that slides and guides the spool 16. A guide hole 20 having a diameter and a guide hole 21 having a small diameter are formed therethrough.

A drain port 22, an output port 23, and a supply port 25 that are opened in the radial direction are sequentially formed on the outer peripheral portion of the valve sleeve 15 corresponding to the guide hole 20, and the guide hole portion of these ports has an annular shape. Each groove is formed.
Also, what is indicated by reference numeral 26 forms a feedback pressure chamber by a spool step, which will be described later, and is closed without communicating with the oil passage. Reference numeral 27 is an open passage for releasing a change in hydraulic pressure in the chamber 29, and reference numeral 28 is an open passage of the spring hole 19.

  The spool 16 includes two land portions 30 and 31 that are in sliding contact with the large diameter guide hole 20 and one land portion 32 that is in sliding contact with the small diameter guide hole 21. The sleeve 15 is formed with an oil passage (not shown) that communicates the output port 23 and the feedback pressure chamber 26. The other large-diameter land portion 30 restricts and communicates the output port 23 and the drain port 22 to restrict the output pressure of the output port 23 to a predetermined pressure or more, and the one large-diameter land portion 31 The supply port 25 and the output port 23 are throttled and communicated, and the supply pressure from the supply port 25 is adjusted to a pressure corresponding to the position of the spool 16 and output as an output pressure from the output port 23.

  Note that these ports and lands are formed in an overlapping manner, and in normal times, the pressure is regulated only by the throttle communication between the supply port 25 and the output port 23. Further, a feedback pressure chamber 26 due to an area difference is formed by one large-diameter land portion 31 and a small-diameter land portion 32 adjacent thereto, and an output pressure is supplied to the chamber 26 from an oil hole (not shown) for feedback pressure. Then, a feedback pressure is applied in the direction in which the spool 16 resists the spring 17. Further, the spool 16 has a spring holding projection 16a at one end and a foot 16b having a predetermined length at the other end.

A screw 19a is formed at a rear end portion of the hole 19 in the valve sleeve 15, and an adjusting bolt 33 is screwed to the screw 19a. A spring 17 is contracted between the adjustment bolt 33 and the spring holding projection 16 a of the spool 16, and the elastic force of the spring 17 is adjusted by rotating the adjustment bolt 33. .
Further, the front end side of the valve sleeve 15 is a flange portion 15a that expands in the outer diameter direction, and the pressure regulating valve portion 12 is fixed to the electromagnet portion 43 by the flange portion 15a.

  On the other hand, the electromagnet portion 13 has a cylindrical core 40 and a coil assembly 41 disposed on the outer periphery of the core 40, and a predetermined current is supplied to the coil assembly 41 via a connector 42. Thus, the electromagnet 43 is configured. Further, the pressure regulating valve portion side of the core 40 is a flange portion 40a, and a shaft 46 is slidably supported in the central hole 44 of the core 40 via a linear bearing assembly 45. One end of the shaft 46 is in contact with the spool 16 of the pressure regulating valve portion 12.

  Further, one end of the shaft 46 is in contact with the foot portion 16 b of the spool 16, and cooperates with the spool 16 by the operation of the plunger 48. A plunger 48 is integrally fixed to the other end (right end in FIG. 1) of the shaft 46, and the plunger 48 can be attracted by the electromagnet 43 and move in the axial direction.

FIG. 2 is a schematic view showing the structure of the linear bearing assembly 45 according to the first embodiment used in the linear solenoid valve 10. The linear bearing assembly 45 includes a bearing cage 50 and the bearing cage. And a steel ball 51 to be fitted to the 50.
In this embodiment, the linear bearing assembly 45 needs to secure the outer diameter of the shaft 46 to φ4 mm and the inner diameter of the core 40 to φ7 mm according to the requirements of the electromagnetic force characteristics of the linear solenoid valve 10. Is determined to be φ1.5 mm.

  Moreover, since it is desirable that the number of the steel balls 51 arranged in one row in the radial direction of the shaft 46 is larger from the viewpoint of durability, it is the maximum number that can be arranged in the linear solenoid valve 10 according to the present embodiment. 7 pieces are arranged in one row, and are arranged evenly every 360/7 degrees, and as shown in FIG. 2, four rows of linear bearings, that is, linear bearings indicated by reference numerals 52 to 55 are provided in the radial direction. Yes.

  Furthermore, the linear bearing generally uses a method of shifting the angular phase of the balls arranged in different rows for the purpose of reducing the shakiness of the shaft. In the linear bearing assembly 45 of this embodiment, as shown in FIG. Further, the linear bearings 52 to 54 are provided in the same phase, and the phase is shifted by 360/14 degrees so that the steel balls of the linear bearing 55 are disposed between the steel balls of the linear bearings 52 to 54. It is shifted.

FIG. 3 is an outline view showing a schematic structure of the bearing cage 50, and FIG. 4 is a development view.
As shown in FIG. 3, the bearing cage 50 is formed of a stainless steel thin plate, for example, a plate thickness of 0.15 mm into a regular heptagon.
As shown in FIG. 4, the material 60 before the bearing cage 50 is formed into a regular heptagon is divided so that the strips 60 a to 60 g have uniform widths.
The linear bearing 52 is formed with substantially rectangular steel ball holding pockets (first steel ball holding pockets) 61a to 61g for fitting the steel balls 51 to the strips 60a to 60g.

  The steel ball holding pockets 61a to 61g are formed in openings whose long sides are oriented in the circumferential direction (vertical direction in FIG. 4) around the corner 69 (see FIG. 5) between the strips 60a to 60g, As shown in FIG. 5, a pair of substantially rectangular protrusions 65a to 65g (first protrusions) are opposed to the steel ball holding pockets 61a to 61g in the long side direction of the steel ball holding pockets 61a to 61g. The steel ball 51 is held in a rotatable state by being bent diagonally inwardly to a size that does not contact the steel ball 51. Therefore, the steel ball 51 has a function of holding the steel ball 51 and prevents the steel ball 51 from falling off.

Further, as shown in FIGS. 6 and 8, in the steel ball holding pockets 61a to 61g, the length A formed by the corners 69 of the bent portions of the strips 60a to 60g is made larger than the diameter B of the steel ball 51. The steel ball 51 is formed so as to be small, and the steel ball 51 can be held in a rotatable state by preventing the steel ball 51 from falling off to the outer diameter side.
Furthermore, when the steel ball 51 is fitted to the steel ball holding pockets 61a to 61g in the linear bearing 52, it is necessary to be deformed in the axial direction and escape, so the steel ball holding pockets 61a to 61g include the steel balls. Steel ball pressing reliefs 66a to 66g (see FIG. 4) are formed in the vicinity of the holding pockets 61a to 61g. Therefore, the steel ball holding pockets 61a to 61g include the steel ball holding reliefs 66a to 66.

Similarly, steel ball holding pockets (first steel ball holding pockets) 62a to 62g and 63a to 63g for fitting the steel balls 51 to the strips 60a to 60g are also formed in the linear bearings 53 and 54. The ball holding pockets 62a to 62g and 63a to 63g are similarly provided with protrusions 65a to 65g on the linear bearing 52, and steel ball pressing reliefs 66a to 66g.
In the developed view shown in FIG. 4, the reference numerals of the protrusions 65a to 65g formed on the linear bearings 53 and 54 are omitted.

  On the other hand, as shown in FIG. 4, the linear bearing 55 has steel ball holding pockets (second steel ball holding pockets) 64a to 64g having substantially circular openings for fitting the steel balls 51 to the strips 60a to 60g. The steel ball holding pockets 64a to 64g are formed with a pair of substantially rectangular projections 67a to 67g (second projections) and 68a to 68g (second projections) in the axial direction and in the width direction orthogonal to the axial direction. Three protrusions) are formed.

  As shown in FIGS. 7 and 9, the projections 67a to 67g are bent inward in the axial direction with respect to the respective surfaces of the strip plates 60a to 60g, and the projections 68a to 68g are each surface of the strip plates 60a and 60g. Is bent inward in the width direction. In this case, the protrusions 67a to 67g and the protrusions 68a to 68g have their tip portions made smaller than the outer diameter of the steel ball 51 to prevent the steel ball 51 from falling off, and the outer diameter of the steel ball 51 does not come into contact. Steel ball retainers (protrusions 67a to 67g and protrusions 68a to 68g) in a state where the assembly has been completed in a state where the steel balls 51 are in contact with the dimensions, that is, the inner peripheral surface of the central hole 44 of the shaft 46 and the core 40 (see FIG. 1) The steel ball 51 has a function of holding the steel ball 51 in a rotatable manner by bending it diagonally to such a size that it floats from above.

Next, the molding and assembly sequence of the linear bearing assembly 45 will be described.
The case where it shape | molds to the bearing cage 50 shown in FIG. 3 is demonstrated. First, in order to form a thin plate of stainless steel material, for example, a plate thickness of 0.15 mm into a regular heptagon, a material 60 is formed in a rectangular shape as shown in FIG.
Here, as described above, the size of the material 60 is the same as that of the bearing cage 50 in which the outer diameter of the shaft 46 in the linear solenoid valve 10 is 4 mm, the inner diameter of the core 40 is 7 mm, and the diameter of the steel ball 51 is 1.5 mm. Since it is formed, the size of the material 60 shown in FIG. 4 shows an enlarged state about 2.5 times the actual size.

Next, after forming the material 60 into a shape shown in FIG. 4 by press working, the material 60 shown in FIG. 3 is formed into a bearing cage 50 having a regular heptagon shape by pressing.
In FIG. 3, detailed reference numerals given to the steel ball holding pockets 61 to 64, the protrusions 65, 67, and 68, and the steel ball holding relief 66 are omitted.
Then, the steel balls 51 are fitted into the steel ball holding pockets 61 to 64 formed in the bearing cage 50 and assembled so as to be rotatable.

According to the linear bearing assembly 45 according to the first embodiment of the present invention, since the steel ball holding pockets can be arranged in the plane part and the corner part of the polygonal column, the steel balls can be arranged out of phase. Is possible.
In the linear bearing assembly 45 according to the embodiment, the phase is shifted by only one row, but it goes without saying that the arrangement can be easily changed as necessary.
Furthermore, by holding the steel balls using the corners of the linear bearing assembly 45, it is possible to reduce the number of installation locations of the steel ball pressing parts by bending, and the structure is simple and the manufacture is facilitated. .
In the first embodiment, the steel ball holding pocket 64 has a steel ball presser, that is, the projections 67a, 67a, and 68a, 68a are each set as two sets in the circumferential direction, and the set is bent inward. Although another set is provided by bending outward, at least two protrusions 67a, 67a, and 68a, 68a (steel ball pressers) may be provided as a set, and one or more sets may be provided on the inside and outside.

10 to 14 are schematic structural views according to the second to sixth embodiments of the linear bearing assembly 45. In FIGS. 10 to 14, the same components as those of FIG. Detailed description will be omitted. 10 to 14, the illustration of the steel ball 51 is omitted.
In FIG. 10, the material 60 is formed into a regular heptagon, and a steel ball holding pocket 63 is provided on each surface at symmetrical positions in the axial direction, and the steel ball holding pocket 64 is disposed outside the steel ball holding pocket 63. A linear bearing assembly 70 is shown.

In FIG. 11, the material 60 is formed into a regular heptagon, and a steel ball holding relief 66 and steel ball holding pockets 63 and 64 are arranged in this order on each surface to form a set, and two sets of these are provided in the same direction. A bearing assembly 75 is shown.
In FIG. 12, the material 60 is formed into a regular heptagon, and a steel ball holding pocket 64 is provided on each surface at symmetrical positions in the axial direction, and the steel ball holding pocket 63 is arranged outside the steel ball holding pocket 64. A linear bearing assembly 80 is shown.

In FIG. 13, the material 60 is formed into a regular pentagon, and a steel ball holding pocket 63 is provided on each surface at symmetrical positions in the axial direction, and the steel ball holding pockets 63, 64 are respectively formed outside the steel ball holding pocket 63. A linear bearing assembly 85 is shown.
A body 85 is shown.
FIG. 14 shows a linear bearing assembly 90 in which the material 60 is formed into a regular pentagon, and the arrangement of the steel ball holding pockets is the same as FIG.

In the linear solenoid valve 10 according to the present embodiment, by using the linear bearing assembly 45, the plunger 48 held by the shaft 46 moves slidably with respect to the core 40, and the electromagnetic generated by the electromagnet portion 13. The force is transmitted to the spool 16 of the pressure regulating valve portion 12, and the spool 16 can be operated by electromagnetic force.
In the embodiment, the spool 16 moves in the axial direction relative to the valve sleeve 15, and the pressure of the output port 23 is adjusted by adjusting the flow of the fluid flowing in from the supply port 25 and the fluid discharged from the drain port 22. Is adjusted.

DESCRIPTION OF SYMBOLS 10 Linear solenoid valve 12 Pressure regulating valve part 13 Electromagnet part 15 Valve sleeve 16 Spool 22 Drain port 23 Output port 25 Supply port 45, 70, 75, 80, 85, 90 Linear bearing assembly 46 Shaft 47 Coil case 48 Plunger 50 Bearing holding 51 Steel ball 52-55 Linear bearing 60 Material 61-64 Steel ball holding pocket
65, 67, 68 Protrusion 66 Steel ball holding relief

Claims (2)

A bearing cage molded into a regular polygon;
A substantially rectangular first steel ball holding pocket formed at a corner of each surface of the bearing cage;
A substantially circular second steel ball holding pocket formed on each surface of the bearing cage;
A steel ball holding relief provided close to the first steel ball holding pocket;
A first protrusion formed in the width direction of each surface in the first steel ball holding pocket;
Substantially rectangular second and third protrusions formed in the second steel ball holding pocket in the axial direction of each surface and in the width direction perpendicular to the axial direction;
With
The first protrusion is bent inward with respect to each surface, the second protrusion is bent inward with respect to each surface, and the third protrusion is bent outward with respect to each surface. A linear bearing assembly characterized by bending, fitting steel balls into the first and second steel ball holding pockets, and rotatably supporting the steel balls by the first to third protrusions. The linear bearing assembly of claim 1, wherein
The linear bearing holder is characterized in that the first steel ball holding pocket and the second steel ball holding pocket are respectively arranged outwardly in the axial direction of the opposing first steel ball holding pocket. Bearing assembly.

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