JPH0356844Y2 - - Google Patents

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a device that applies a braking load to a rotating shaft of a register or the like, and is used in the field of air conditioning equipment.

[Conventional technology]

Conventional braking means for the rotation shaft of the register, for example, for controlling the rotation of the barrel, are as shown in FIGS. 6a to 6e.
When inserting into the bearing hole of a retainer made of plastic such as ABS and supporting the shaft, there is a thickness d at the base of the barrel shaft.
1 step 21' is formed to form a gap d1 between the opposing barrel outer wall surface and retainer inner wall surface.
, and a shim R (thickness adjustment plate) made of felt having a thickness d2 thicker than the gap d1 or a wave spring shown in FIG. The barrel 2
The rotation relative to the retainer 1 was braked.

[Problem that the invention attempts to solve]

The braking force generation action by the shim 3 attempts to deform the side wall of the barrel 2 and the side wall of the retainer 1 in the directions of arrows F1 and F2, as shown in FIG. The initial setting load continues to decrease. When a felt plate as shown in Figure b is used as a shim, the felt itself is compressively deformed and its initial plate thickness decreases, and as the thickness decreases with each operation, the braking load decreases.

Also, if the retainer or barrel is made of plastic, it will deform due to the effects of heat and time. For example, according to a practical heat resistance test assuming parking during heating and under the scorching sun in midsummer, both the retainer and barrel were made of ABS.
In the case of resin, the load after the heat resistance test was reduced to 25% or less of the initial load.

In the end, in these conventional shaft brakes, if the shim is made of felt, the shim becomes thin, and if the shim does not become deformed and thinned, the gap between the retainer side wall and the barrel side wall will expand and deform, as shown in Figure e. , degradation over time with use of the default load is inevitable;
Also, the factors of the set load are the width of the retainer, the width of the barrel,
It was also difficult to improve the accuracy of load management due to the thickness of the shim.

[Means and actions for solving problems]

The present invention eliminates or improves the above-mentioned drawback of the deterioration over time due to the use of a set load, which could not be avoided in the conventional device due to its configuration.

That is, for example, in a register bearing in which a barrel is assembled to a bearing part provided in a retainer as shown in No. 1A and 1B, the barrel shaft is supported in the retainer bearing hole with a substantially U-shaped plate spring interposed therebetween, and the spring In order to apply braking force to the barrel shaft by the pressure contact force, a bearing hole 31 capable of supporting the barrel shaft and the spring is provided in the bearing portion 3 of the retainer, as shown in FIGS. Further, a spring base support piece 32 and two tip support pieces 33 are formed on the front surface (front side) so that the spring can be freely attached and detached only from the inside surface (back side). 41, the center shaft clamping part 43, and the tip part 42 are approximately U-shaped. 2 cuts S
It is formed to be smaller than the two-way correspondence range D.

When assembling, the spring base 41
into the notch S1 for fitting into the base of the bearing hole, and the spring both tips 42 are slightly expanded against the spring force and inserted into each notch S2, so that the tips 42, 42 of the spring fit into each notch S2, S2. inner surface f
2, the position of the spring is maintained by compressing f2, and then the barrel shaft is inserted while further widening the gap between the two spring shaft clamping parts 43, 43 against the spring force, and The braking force is applied to the barrel shaft by the squeezing action of the U-shaped spring whose rotation is prevented by the respective fitting portions S1 and S2, thereby solving the conventional problems.

〔Example〕

As is clear from FIGS. 3 to 5, the bearing portion 3
has a curved surface with a radius of curvature R, a notch S1 for fitting the spring base on one side, and two notches S1 for fitting the spring tip at a predetermined interval on the other side.
2, S2 was formed.

The cut S1 has a height H1 and a depth L1, and is formed with a base support piece 32 having a length l1 from the back and a width W left on the front surface.

Each of the cuts S2 has a height of H2 and a length of L2, and a tip support piece 33 having a length of 12 from the back and a width of W is left on the front surface.

The spring is vertically symmetrical with respect to the horizontal center line Y-Y, and has an upper and lower curved surface portion 43 with an inner radius of curvature R1, a height H1 portion 41, and a tip portion 42 that widens outward at a tip interval C. The width of the curved surface part is T, and both the base part 41 and the tip part 42 have a width t with a decrease in W on both sides, and have a width dimension that is symmetrical with respect to the center line XX, and a thickness of 0.3. Made of mm spring steel plate.

Regarding the mutual relationship between the bearing hole 31, the spring 4, and the barrel shaft 21, in terms of the width, that is, the axial direction of the barrel shaft, the width T of the curved portion of the spring 4 is equal to the width T of the bearing portion 3, as shown in FIG. 1B. The widths of the base portion 41 and the tip portion 42 of the spring respectively decrease in a curved manner from the curved surface portion to t, and the width of each straight side portion is the same as that of the base support piece 32.
and in contact with the inner surface of the tip support piece 33,
The side surface of the curved spring portion and the front surface of each support piece, that is, the surface of the bearing portion, are shaped to be flush with each other. In addition, the radius of curvature R1 of the inner surface of the spring curved surface, the radius of curvature R2 of the shaft 21, and the radius of curvature R of the curved surface of the bearing part, R1<R
When 2<R and both spring tips are inserted into the respective notches S2 and S2, the gap between the two tips C (Figure 5a) is expanded to a larger gap D (Figure 5b). It was formed like this.

When assembling, insert the spring base 41 into the notch S1 of the bearing and insert each tip 4
2 into each notch S2 from the inside of the bearing part,
The distance C between both ends of the spring is expanded to D, and the fifth
The spring 4 is expanded from the dotted line state to the solid line state as shown in FIG. The spring 4 was self-retained in the bearing hole, and then the barrel shaft 21 was inserted between the spring curved surfaces 43, 43. Spring inner curvature R
1<barrel axis R2, as shown in FIG. 5d, the spring 4 and the shaft 21 are in line contact with contact points P at four approximately equally spaced locations.

FIG. 2 shows the assembled state in an exploded manner, where a indicates the bearing portion, b indicates the spring, and c indicates the barrel shaft. As is clear from c, an inclined surface 21' is provided at the tip of the shaft to facilitate insertion.

The resulting resistor bearing has each spring 4 formed by the spring 4 slightly expanded by the barrel shaft 21.
At the three contact points P positions, the spring 4 was able to apply a pressing braking force to the shaft 21 in a line contact state.

When fitting the spring into the bearing part during the assembly process, it is necessary to use a small spring (width T: 3 to 5 mm, length 10 to 15 mm, height 6 to 10 mm), it can be abutted and supported just by pushing in from one side (inside) as shown by arrow A in Figure 3b, and when pushing in, the distance C between both spring tips 42 and 42 is adjusted to D. Since the spring 4 expands against the force, the fitting state of the spring 4 into the bearing part can be maintained by fitting it into the notch S1 of the base part 41 and clamping the bearing parts of both tips 42, 42, making the work extremely easy. It got easier.

In addition, since the width and height of the spring 4 are symmetrical, there is no need to select the top and bottom when fitting the spring 4 into the bearing 3, and the base 41 and tip 42 are simply fitted into their respective notches. By simply doing this, it was possible to mount it flush with the outer surface (front surface) as shown in Figure 2, resulting in good workability and easy manual work with fingertips.

In addition, when the barrel is attached (the state shown in Fig. 5c), the dimension between the tips 42 and 42 of the spring is in a state D in which the dimension between the tips 42 and 42 is in contact with the inner inner surface f2 of the notch S2.
A state E in which it is in contact with the outer inner surface f1 of the cut S2
The spring force generated causes sliding resistance between the shaft and the spring, but since the dimensions D and E are constant, the dimensional change (E-D) is also constant.
The sliding resistance of the barrel shaft has also stabilized, and the variation in barrel operating load has been reduced.

Also, the contact point P between the spring curved surface and the barrel shaft
Since there was line contact at four approximately equally spaced locations, the barrel shaft could be stably and reliably held in the retainer via the spring.

In carrying out the present invention, the bearing part 3 may be configured separately from the retainer 1 in advance, and the barreled bearing part 3 may be attached to the retainer after the barrel is attached.

In addition, each base support piece 32, tip support piece 33
Even if the notches S1 and S2 are formed in a bridging position between the notches S1 and S2 at the sliding contact position of the barrel shaft, the same effect can be achieved if the width is reduced from the shaft clamping part of the spring to the base part 41 and tip part 42. play.

Further, if the width of the base 41 and the tip 42 of the spring from the shaft clamping portion is formed into a linear stepped shape by L-shaped notches, it is easy to work and a functional aesthetic appearance can be obtained.

In addition, the shaft clamping part of the spring can be made to have an inner radius of curvature R1 larger than the radius of curvature R2 of the outer periphery of the barrel shaft, or it can be made into a flat plate, and the spring can be assembled at two points above and below the central part of the shaft clamping part of the spring. Even if the braking force is generated through line contact, the desired purpose can be achieved.

In addition, the relationship between the spring and the bearing hole can be adjusted in various ways under the conditions that the spring can be prevented from rotating, can be self-retained at both ends of the spring, and can apply braking force to the barrel shaft with the spring force of the spring. Design changes are possible.

From the above description, it is clear to those skilled in the art that the device of the present invention can be widely applied to bearings that can be braked by the spring pressure of a plate spring, and can be widely applied to rotary shafts with light loads that are manually adjusted for rotation. It should be obvious.

[Effect of idea]

Since the only load factors that brake the rotating shaft are the shaft diameter and the spring, load management is much easier compared to conventional management of retainer width, barrel width, and shim thickness (diameter control is more important than width control). easy to manage).

Since neither the inner circumferential surface of the bearing hole nor the outer circumferential surface of the barrel shaft is subjected to load deformation, the change in operating load over time can be significantly improved by selecting only the spring.

Since braking is performed only by elastic deformation of the spring, three parts of the retainer side wall, barrel side wall, and shim of the conventional device are used.
Compared to elastic deformation braking using members, the tolerance range for ideal dimensions is larger, and manufacturing and management are easier.

Since the spring can be self-retained in the bearing hole, assembly work is easy.

Adjust the operating angle range of the spring to the mating hole (cut S
Since it is regulated by 2), the load usage range can be managed.

[Brief explanation of drawings]

FIG. 1A is a perspective view showing the assembled state of the register of the present invention, and FIG. 1B is a sectional view of the bearing portion of FIG. 1A. FIG. 2 is an exploded perspective view of the bearing section in an assembled state, in which a indicates the bearing section, b indicates the spring, and c indicates the end of the barrel shaft. FIG. 3 shows a bearing part, in which a is a front view and b is a cross-sectional view taken along line bb at a. FIG. 4 shows a spring, in which a is an outside front view and b is a top view. FIG. 5 is an explanatory view of the operation, in which a shows the spring in an unloaded state, b shows the spring attached to the retainer bearing, c shows the barrel assembled, and d shows the spring shows the effect of on the barrel axis. FIG. 6 is an explanatory diagram of a conventional example, in which a is a schematic cross-section, b is a shim made of felt, c is a shim made of a wave spring, and d is a state in which the shim is attached to the barrel shaft.
e indicates the action of the shaft portion. DESCRIPTION OF SYMBOLS 1... Retainer, 2... Barrel, 21... Barrel shaft, 3... Bearing part, 31... Bearing hole, 32...
Base support piece, 33...Tip support piece, 4...Spring, 41...Spring base, 42...Spring tip, 43...Spring shaft clamping part.

Claims (1)

[Claims for Utility Model Registration] 1. Base notch S1 and tip notches S2, S2 for fitting the spring 4 into the bearing part 3
In addition to providing a shaft hole 31 with
Each is formed on the surface of the bearing hole 31, and the base 4
1. Shaft clamping parts 43, 43 and tip parts 42, 42
and a substantially U-shaped spring 4 in which the distance C between the two tip ends is smaller than the corresponding distance D between the inner surfaces f2, f2 of both the tip ends S2, S2,
A rotary shaft braking device that is expanded and fitted into a bearing hole 31 and generates a braking force by spring force on the shaft clamping portions 43, 43 of the spring by inserting the rotary shaft 21. 2 The notches S2, S2 for the tip end are formed on each inner surface f2,
The circuit according to claim 1, wherein f2 imparts a self-retaining action to the tip of the spring 4, and each outer surface f1, f1 regulates the expanded state of the tip of the spring when the rotation shaft is assembled. Dynamic shaft braking device. 3. The rotating shaft braking device according to claim 1, wherein the shaft clamping portion 43 of the spring is a curved surface portion having an inner surface radius of curvature R1 smaller than the rotating shaft radius of curvature R2.