JPH0724665Y2 - Armature assembly such as electromagnetic clutch - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (Industrial field of application) The present invention relates to an armature assembly used in a friction plate type electromagnetic clutch or electromagnetic brake.

(Prior Art) This type of friction plate type electromagnetic clutch is composed of an armature assembly, which is a rotating part, and a rotor, and a stator, which is a stationary part, as basic elements, and a friction plate type electromagnetic brake is an armature, which is a rotating part. The assembly and the stationary part, the stator, are the basic elements.

For example, taking the friction plate type electromagnetic clutch shown in FIG. 4 as an example, a stator 2 having an exciting coil 1 built-in and fixed to a body or the like, and a lining 3 attached to a rotary shaft on the output side via a key or the like. 4 and an armature assembly which is locked to the rotary shaft 6 on the input side via a key or the like and is arranged to face the rotor 5 with a certain gap G from the lining 3. It is configured. This armature assembly includes an armature 7 arranged to face the rotor 5, an armature hub 8 having a tubular portion locked to the rotary shaft 6 via a key or the like, the armature 7 and the armature hub 8 The armature 7 and the armature hub 8 are each interposed by a disc-shaped spring member 9 alternately connected to the flange portions of the armature 7 and the armature hub 8 along the circumferential direction by fastening shafts such as rivets.

The spring member 9 is curved in a corrugated shape along the circumferential direction in order to give a large spring force.

When the exciting coil 1 is energized, a magnetic flux is generated in the electromagnetic clutch, and the stator 2, the rotor 5, and the armature 7 are generated.
A magnetic circuit is formed between them, and only the armature 7 is attracted to the rotor 5 side and adsorbed to the lining 3 with the disc-shaped spring member 9 bent as shown in FIG. Thus, the rotor 5 and the armature assembly are connected to each other, and the torque is transmitted from the driving side (the rotating shaft 6 in this case) to the driven side (the rotating shaft 4 in this case). When the energization is stopped, the magnetic flux disappears and the bent disk-shaped spring member 9 is restored as shown in FIG. 4 (a), the armature 7 is separated from the lining 3, and the transmission of the torque is interrupted. It

In the friction plate type electromagnetic clutch as described above or in the friction plate type electromagnetic brake (not shown, the rotor portion is omitted from the above structure, the gap G is always constant and the necessary spring force is maintained. If it is not placed, the frictional force and response speed will change and performance will decline. Therefore, it is necessary not only to initialize the gap G to a constant value, but also to satisfy the above requirements even if the lining is worn or the spring member is deformed due to use.

As a means for adjusting the gap G, conventionally, an annular spacer is fitted on the inner peripheral side between the armature and the rotor to adjust the plate thickness and the number of the spacers for fine adjustment, or as disclosed in Japanese Utility Model Publication No. 61-31544. In addition to the above-mentioned spring member, a friction type automatic air gap adjusting device composed of a holding leaf spring, a bush, a sliding pin and the like is provided between the armature and the armature hub.

(Problems to be Solved by the Invention) However, it is not easy to perform the work of forming the wavy shape along the circumferential direction like the spring member 9 in the above-mentioned conventional technique, and the spring member 9 has a constant and uniform shape. It was not easy to apply the spring force.

Further, in the case of the former case described above, there is a problem that the spacer must be detached and adjusted in a disassembled state and the adjustment is complicated, and it is difficult to maintain and maintain a constant gap. is there. In the latter case, the number of parts is large, so assembly and initial setting become complicated, and
There are drawbacks such as difficulty in maintaining and maintaining a constant friction state.

Therefore, the present invention has an object to provide an armature assembly such as an electromagnetic clutch capable of solving the problems of the conventional techniques with an extremely simple structure.

(Means for Solving the Problems) The gist of the present invention is, in an armature assembly of a friction plate type electromagnetic clutch or electromagnetic brake, a mounting dimension pit Φa centered on the axis of a mounting hole formed in the armature, and a spring. The relational expression between the mounting dimension pitch Φd centered on the axis of the mounting hole formed in the member and the mounting dimension pitch Φh centered on the axis of the mounting hole formed in the armature hub is Φa <Φd = Φh, Φa> Φd = Φh, Φa = Φ
It is set to either d <Φh or Φa = Φd> Φh, and a flat disc-shaped plate spring is used for the spring member, and the spring member is made to have the dimensional difference via the fastening shaft. An armature assembly, such as an electromagnetic clutch, which is connected to an armature and an armature hub, and applies a bending stress to a mounting portion of the spring member to bend the cross section into an arc shape.

(Example) Below, this invention is demonstrated based on the Example shown in figure. As shown in FIG. 2, the armature assembly comprises an armature 11, a disk-shaped spring member 12 and an armature hub 13 as in the conventional case.

However, the spring member 12 is not made of a corrugated plate in advance as in the conventional case, but is made of, for example, a flat thin stainless material of about 0.1 mm.

The armature 11 and the disk-shaped spring member 12 are riveted or screwed into a plurality of mounting holes 11a, 12a (three at 120-degree intervals in the embodiment) which are provided at equal intervals along the circumferential direction. It is fixed by inserting the fastening shaft 14 such as. Further, the disk-shaped spring member 12 and the armature hub 13 are similarly provided at a plurality of positions (60 in the embodiment) which are formed at positions equidistant from the mounting holes 11a and 12a at equal intervals along the circumferential direction. It is fixed by inserting a fastening shaft 15 such as a rivet or a screw into the mounting holes 12b and 13b at three positions which are offset from each other at 120-degree intervals.

The armature 11 has a relief hole 11b for the fastening shaft 15,
The armature hub 13 is provided with escape holes 13b for the fastening shafts 14, respectively. As shown in Fig. 1, the mounting holes are
The mounting dimension pitch Φa centered on the shaft center of the mounting hole 11a,
Mounting dimension pitch Φd centered on the shaft center of the mounting holes 12a, 12b
And the mounting dimension pitch Φh centered on the shaft center of the mounting hole 13b
The relationship is set to one of the following.

Φa <Φd = Φh …… Φa> Φd = Φh …… Φa = Φd <Φh …… Φa = Φd> Φh …… As shown in the above formula, the mounting size of the spring member 12 is the mounting size of the armature 11 against the pitch Φd. Either the pitch Φa or the mounting dimension pitch Φh of the armature hub 13 is set to be slightly larger or smaller, and the spring member 12 is connected to the armature 11 and the armature hub 13 by the fastening shafts 14 and 15.
When they are alternately connected to each other, the outer peripheral surfaces of the fastening shafts 14 and 15 press the inner peripheral surface of the mounting hole of the spring member 12, so that the spring member 12 tries to extend to the outer peripheral side or contracts to the inner peripheral side due to stress. Another stress acts to generate a bending stress whose section is curved in an arc shape as shown in FIG. 3 (b).

For example, as shown in the above formula, the mounting dimension pitch Φ of the spring member 12
If the mounting dimension pitch Φa of the armature 11 to which the spring member 12 is mounted is small with respect to d, the spring member 12 is curved in an arc shape with the armature 11 side as a concave surface, and the mounting dimension of the spring member 12 as in the above formula. When the mounting dimension pitch Φa of the armature 11 is larger than the pitch Φd, the spring member 12 is curved in an arc shape having the armature 11 side as a convex surface.

Also, as in the above formula, the mounting dimension pitch Φd of the spring member 12
When the mounting dimension pitch Φh of the armature hub 13 is larger, the spring member 12 is curved in an arc shape with the armature hub 13 side as a convex surface, and the mounting dimension pitch Φd of the spring member 12 is larger than the mounting dimension pitch Φd of the spring member 12 as shown in the above formula. Dimension pitch Φ
When h is small, the spring member 12 is curved in an arc shape having a concave surface on the armature hub 13 side.

Although the spring member 12 is connected to the armature 11 or the armature hub 13 in a somewhat unreasonable state due to the difference in size, the spring member 12 is temporarily flat as shown in FIG. Mounted.

When the armature 11 is attracted to the rotor side (stator side in the case of an electromagnetic brake) by energizing the exciting coil, the cross section of the mounting portion of the spring member 12 is given by the dimensional difference as shown in FIG. 3B. The armature 11 is bent in an arc shape more than the bending stress applied to the armature 11 as in the conventional case described above.
Torque is transmitted by frictional conduction of the lining and.

Further, when the energization is stopped, the armature 7 is separated by the restoring force of the spring member 12 and the transmission of the torque is interrupted, but the spring member 12 is restored to the curved state due to the bending stress imparted by the dimensional difference, It does not restore to the initial flat state shown in FIG. 3 (a), but returns to a state in which a slight spring force is held.

Furthermore, for example, when the armature 7 is brought into a limit state in which the armature 7 is brought into contact with the lining surface of the rotor 5 by the restored spring member 12, the bending state by the bending stress given by the above-mentioned dimensional difference is set. When the lining wears while the suction and separation operations are repeated, the curved portion of the spring member 12 protrudes by the amount of wear and the gap is automatically adjusted by the amount of wear of the lining.

Even if the armature 7 is set to the limit of contact with the lining surface of the rotor 5 as described above, the spring member
The bending stress applied to 12 is a local and small spring force, and since there is inertia on the load side, the rotor 5 and the armature 7 do not rotate together, and there is no hindrance to the operation of the clutch and the brake.

(Effect of the Invention) As is apparent from the above-described embodiment, in the present invention, the disk-shaped spring member that constitutes the armature assembly together with the armature and the armature hub is formed into a flat plate shape,
The armatures and the armature hubs, to which the spring members are alternately mounted along the circumferential direction, are provided with a dimensional difference in the mounting dimension pitch so as to locally apply bending stress that bends in an arc shape.

As a result, it is possible to provide a spring member that is easier to manufacture and has less variation in spring force than a conventional spring member that is curvedly formed in a wave shape along the conventional circumferential direction.

Further, if the bending state is set by the bending stress applied to the spring member so that the armature comes into a limit state in which the armature comes into contact with the lining surface of the rotor by the spring member, when the lining is worn, the spring member is The curved portion is pushed out and the gap is automatically adjusted by the wear of the lining.

[Brief description of drawings]

FIG. 1 is a plan view showing a mounting dimension pitch relationship of an armature assembly according to an embodiment of the present invention, FIG. 2 is an exploded perspective view of the armature assembly, and FIG. 3 is a longitudinal sectional view of an essential part showing an operating state of the armature assembly. FIG. 4 and FIG. 4 are longitudinal sectional views of a general friction plate type electromagnetic clutch. [Explanation of symbols] 11 …… Armature 12 …… Disc-shaped spring member 13 …… Armature hub 14,15 …… Fastening side 11a, 12a, 12b, 13b …… Mounting hole 11b, 13a… Escape hole Φa… … (Armature) mounting dimension pitch Φd …… (spring member) mounting dimension pitch Φh …… (armature hub) mounting dimension pitch

Claims (1)

[Scope of utility model registration request] 1. An armature, an armature hub, and a disk-shaped spring member interposed between the armature and the armature hub and alternately connected to the armature and the armature hub by fastening shafts along the circumferential direction. In an armature assembly for a friction plate type electromagnetic clutch or electromagnetic brake, the mounting dimension pitch Φa around the shaft center of the mounting hole formed in the armature and the shaft center of the mounting hole formed in the spring member are set. The relational expression between the mounting dimension pitch Φd about the center and the mounting dimension pitch Φh about the axis of the mounting hole formed in the armature hub is Φa <Φd = Φh, Φ
a> Φd = Φh, Φa = Φd <Φh, Φa = Φd> Φh
Which is set to any one of the above, a flat disc-shaped leaf spring is used for the spring member, and the spring member is connected to the armature and the armature hub having the dimensional difference via the fastening shaft, An armature assembly, such as an electromagnetic clutch, characterized in that a bending stress is applied to a mounting portion of a spring member so that a cross section thereof is curved in an arc shape.