JPH0440020Y2 - - Google Patents

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a bearing structure for audio equipment, etc., and particularly to a bearing structure for mounting a vehicle-mounted speaker.

[Prior Art] Generally speaking, the function of a bearing is to support rotating or reciprocating shafts, keeping them in place, and keeping the weight of the shaft and loads acting on the shaft safe. They are roughly divided into two categories: one based on the relative motion between the shaft and the bearing, and the other based on the direction of the load. Those belonging to the former category have relative motion2.
There are bearings whose surfaces slide against each other (sliding bearings) and bearings whose two surfaces move relative to each other (rolling bearings). Bearings belonging to the latter category include bearings that pass through the center of the shaft and receive loads in a direction perpendicular to the shaft (radial bearings); There are bearings (thrust bearings) that receive loads in the direction of the centerline of the shaft.

The various types of bearings listed above have friction, external force, generated heat, wear, seizure, strength, etc. depending on the application.
The structure is such that it satisfies various factors such as lubrication, size, dust, vibration, breakage, cooling, maintenance, and repair to suit each application.

Therefore, if a bearing that satisfies some of the above-mentioned classification functions is required, it is necessary to use a combination of several types of bearings depending on the characteristics of each type of bearing.

Below, examples of bearings that simultaneously satisfy several of the previously disclosed functions will be briefly described.

As a conventional technique, for example, there is a bearing that also serves as a shock absorber disclosed in Japanese Patent Publication No. 36-4852.
This bearing is used on the shaft of a tong, such as a forged manipulator, which is subjected to impact in the front and back and up and down directions during operation, and is intended to prevent the impact from being transmitted to the main body.

FIG. 6 is a longitudinal sectional view of this bearing. This bearing has a side plate 40 fixed to one end of a cylindrical bearing box 39,
Two spiral springs 41 are housed in this bearing box 39 with a cylindrical spacing piece 42 sandwiched therebetween.

Each upper end is fixed to the bearing box 39 with a pin 43, and a bush 44 is fitted inside, and a shaft 45 is fitted inside the bush 44.

Therefore, when the shaft 45 receives an impact in the axial direction, the impact is transmitted to the spiral spring 41 via the collar piece 46 or the bush 44 and the pin 43, and the inner side of the spiral spring 41 moves in the axial direction.

Further, when the shaft 45 receives an impact in the vertical direction, the impact is transmitted to the spiral spring 41 via the bush 44, and the spiral spring 41 deforms to better absorb the impact due to its elasticity.

Further, as another example of the conventional technology, there is a bearing device disclosed in US Pat. No. 2,907,610, which relates to a structure that supports a shaft moving in the longitudinal direction without friction. FIG. 7 is a sectional view of this bearing in a direction perpendicular to its axis.

In the same figure, this bearing is a bearing for supporting a shaft 47 that moves in the length direction, and a casing 48
Inside are opposed holders 49 whose centers are arched outwards, and inside each holder 49 is a respective pulley-like bearing element 50 to facilitate sliding of the shaft 47. These sets are arranged in the axial direction to support the shaft 47 from above and below and from the left and right, and the holder 49 engages with the hole 51 of the casing 48 to prevent its movement in the axial direction. These bearing structures are well known.

On the other hand, for example, the length including the speaker unit
When a stationary enclosure type cabinet with a length of 1 m is mounted on the rear tray of a car, the speaker can be rotated to change the sound field characteristics inside the vehicle by changing the sound emission direction of the speaker. A structure that can be installed is required,
This structure requires, for example, a bearing structure as described above. This type of bearing structure must satisfy at least the following conditions. In other words, (a) Pitch misalignment of the mounting holes for the bearing support frame of the vehicle body is unavoidable in the vehicle body assembly process, so in order to facilitate the assembly of the above-mentioned cabinet onto the vehicle, the bearing itself must be slightly axially misaligned. (b) The bearing itself must have an axial buffering function to prevent axial shocks from being transmitted to the cabinet due to vibrations of the vehicle body after installation; (c) In order to satisfy the so-called audio enjoyment of changing the directivity of sound by rotating the cabinet, it is easy to regulate the rotation angle of the bearing and hold it at a predetermined position within the rotation range. (d) It must have the strength to withstand the load in the direction perpendicular to the axis passing through the axis, such as when a person leans on it for use in a vehicle.

[Problems to be solved by the invention] However, the rotation angle is regulated to such an extent that no lubrication is required, and the gentle rotational movement function and axial buffering function that are essential for speaker enclosures cannot be achieved. Conventionally, there has been no suitable bearing that has a suitable strength and has the function of stopping the cylindrical bearing at a predetermined position within the speaker rotation range and maintaining the speaker angle. If only a single bearing as shown in FIGS. 6 and 7 was used, there was a problem in that several types of bearings had to be used in combination.

For this reason, the product cost cannot be reduced due to the high cost of the bearing portion, and a support structure for accommodating several types of bearings is required, resulting in a problem that the bearing portion inevitably becomes larger. Also, the above-mentioned 6th
With a single bearing as shown in Fig. 7, when a large resin enclosure is installed in the car body, the amount of thermal expansion and contraction (length) between the car body and the enclosure that occurs due to changes in the temperature inside the car body. There was also a problem in that the above-mentioned functions were deteriorated due to the influence of this difference.

Furthermore, the single bearing structure allows
A speaker bearing structure that satisfies condition (d) has not conventionally existed.

[Means for solving the problem] In order to solve the above problems, the present invention has the following features:
a bearing support frame in which a through hole is formed through which the end of the shaft body passes; a full-circumference sleeve bearing fixed integrally with the bearing support frame with a hollow portion aligned with the through-hole; and the full-circumference sleeve. a shaft body having a shaft portion that is fitted and supported in a hollow portion of the bearing, and a step portion that has a large diameter and is stepped from the shaft portion;
It is rotatably supported in sliding contact with the outer circumferential surface of the full-circumference sleeve bearing, and has a stepped side surface corresponding to the stepped portion of the shaft formed on the inside, and also corresponds to the open end of the full-circumference sleeve bearing. a cylindrical bearing having a flange formed thereon; and a cylindrical bearing having a flange formed thereon; and a cylindrical bearing having a flange formed thereon, and an open end of the flange of the cylindrical bearing and an open end of the periphery sleeve bearing in a state in which the cylindrical bearing is attached to the circumferential sleeve bearing by the shaft; and a first elastic member installed between the stepped side surface of the cylindrical bearing and the stepped portion of the shaft body to elastically engage them. The bearing structure is characterized in that it has a bearing structure consisting of a second elastic member that causes the bearing to move.

[Function] In the bearing structure configured as above,
For example, when the above-mentioned cabinet is mounted on a vehicle, the cylindrical bearing that supports the cabinet is slidable in the axial direction, making it easy to make minute adjustments in the axial direction due to pitch deviation of the bearing mounting hole in the vehicle body. Moreover, the impact in the axial direction can be easily absorbed by the elastic means brought into contact between the cylindrical bearing, the shaft body, and the full-circumference sleeve bearing.

Furthermore, the bearing support frame, the full-circumference sleeve bearing integrated therein, and the shaft body that is fastened and held to the bearing support frame with fastening members such as nuts, maintain sufficient strength against loads in the direction perpendicular to the axis passing through the shaft center. Since the cylindrical bearing is supported by the outer circumferential surface of these full-circumference sleeve bearings and the outer circumferential surface of the shaft body, it has sufficient strength against the above-mentioned loads.

[Example] A preferred example of the present invention will be described in detail based on the drawings.

FIG. 1 is an exploded perspective view showing an embodiment of the bearing structure according to the invention, FIG. Figure 4 is a side view illustrating the engagement between the leaf spring and the rotation-stopping protrusion and rotation-limiting engagement groove provided on the side surface of the bearing support frame, and Figure 5 is the bearing of this invention. FIG. 5A is an enlarged perspective view of the enclosure mounted on the cylindrical bearing.

In the figure, 1 is a bearing support frame, in which a cylindrical full-circumference sleeve bearing 2 is integrally provided so as to be perpendicular to the side surface, and the lower part is bent at a right angle.
Mounting seats 3, 3 for attaching to the vehicle body are arranged there.
Reference numeral 4 denotes a shaft body that is fitted into the inner circumferential surface of the full-circumference sleeve bearing 2. As shown in FIG.
It is formed in a stepped shape, and from the side surface 9 of the second step part 6 there is a protrusion 10 along the outer periphery of the shaft part 7 for regulating the rotation of the cylindrical bearing 12, which will be described later.
10 is provided in a protruding manner, and a keyway 11 is formed in the threaded portion 8 for regulating the rotation of a leaf spring 27, which will also be described later. The cylindrical bearing 12 has a second
As shown in the figure, it is configured to be fitted onto the outer circumferential surfaces of the first step portion 5, second step portion 6, and shaft portion 7 of the shaft body 4 and the outer circumferential surface of the full-circumference sleeve bearing 2. . The stepped side surface 13 of this cylindrical bearing 12
and the side surface 14 of the first step portion 5 of the shaft body 4.
A wave spring washer 15 shown in the figure is disposed between the side surface of a collar 16 protruding in the circumferential direction at approximately the center in the axial direction of the cylindrical bearing 12 and the side surface of the full-circumference sleeve bearing 2. A wave spring washer 17 is provided. Further, as shown in FIG. 3, fan-shaped notches 18, 19, and 20 are formed in the circumferential direction of the collar 16 of the cylindrical bearing 12 over the entire width of the collar 16, The protrusions 10, 10 formed on the shaft body 4 are formed so as to be able to fit and slide into either the fan-shaped cutouts 18 and 19 or 18 and 20. That is, the angle θ ₁ formed by the fan-shaped notches 18 and 19 and the angle θ ₂ formed between 18 and 20 shown in FIG. It is configured to do.

On the other hand, the shaft body 4 passes through the cylindrical bearing 12 via the wave spring washers 15 and 17, and the hole 22 of the bearing support frame 1 is opened until the side surface 21 of the shaft portion 7 comes into contact with the side surface of the bearing support frame 1. Inserted into the inner surface,
It is configured to be held in the bearing support frame 1 by tightening a flat washer 23 and a nut 24 to the threaded portion 8 at the tip of the shaft body 4 via a leaf spring 27.

The dimensions of each part are determined so that the wave spring washer 17 is always held without being compressed when the shaft body is fastened. Further, a leaf spring 27 is disposed between the plain washer 23 and the side surface of the bearing support frame 1, and the leaf spring 27 has an upper support rod 25 and a lower support rod 26 extending to equal lengths. The tips of the support rods 25, 26 are bent vertically to form bent portions 28, 28', 29, 29', respectively;
Further, V-shaped engagement protrusions 30 and 31 for engaging with the side surfaces of the bearing support frame 1 are formed on the flat end portions of each of the support rods 25 and 26, respectively.
Furthermore, a shaft body 4 is provided at the center of the leaf spring 27.
A hole 32 into which the threaded portion 8 is fitted is formed, and a pawl 33 that engages with the keyway 11 of the threaded portion 8 formed in the shaft body 4 is formed in a part of this hole in the circumferential direction of the flat surface of the leaf spring 27. It is protruded vertically.

On the other hand, the full circumference sleeve bearing 2 of the shaft support frame 1
On the opposite side, on the circumference centered on the axis,
Engagement protrusion 3 of each support rod 25, 26 of the leaf spring 27
Rotation regulating engagement grooves 34a, 3 that engage with 0, 31
4b, . . . 34'a, 34'b, . . . and the like are arranged at equal angles to the axis and on a circumference equal to the rotation radius of the protrusions 30, 31 of the leaf spring. has been done. Also, vertically downward are bent portions 28, 28', 29, 2 of the support rods 25, 26 of the leaf spring 27.
An inverted V-shaped rotation stopper protrusion 35 is provided within the rotation radius of 9'. As shown in FIG. 4, the side surface 36 of this rotation stopper projection 35 comes into contact with the bent portion 29 of the support rod 26 of the leaf spring 27, and the leaf spring 27 rotates in the direction of the arrow in FIG. In this case, the other side 37 is the bent portion 28 of the support rod 25 of the leaf spring 27.
It is formed so that it comes into contact with. That is, the angle θ ₃ formed by the support rods 25 and 26 of the leaf spring 27 is formed to be equal to the angle formed by the rotation-limiting engagement grooves 34a and 34'a, and the rotation-stopping protrusion 35
and the rotation regulating engagement groove 34a are arranged in a straight line.

In the above configuration, the operation when the bearing structure is used will be described with reference to both FIG. 5 and FIG. 5A. The bearing support frame 1 of this invention matches the mounting holes of the rear side trim part 51 of the vehicle body with the mounting seats 3, 3 of this frame 1, and the bolts 52
(See Figure 2). The enclosure type speaker cabinet 38 has a cylindrical bearing 1 between two bearing supporting frames 1, 1.
2, 12 and is assembled. Note that 53 is a tonneau board. The cabinet 38 is, for example, a half-cylindrical body 38, as shown in FIG. 5A.
a and 38b, which are butted against each other with the cylindrical bearing 12 inside, and are fixed with screws 54 inserted into the hole I on the half cylinder side and the hole RO on the cylindrical bearing 12 side (see Fig. 3).

Assembling errors caused by the pitch deviation of the mounting holes on the vehicle body side that occur at this time are caused by the fact that the cylindrical bearing 12 is fitted with a wave spring washer 15 for the right direction in FIG. 2, and a wave spring washer 17 for the left direction in FIG. By pressing the bearing 12 against the elasticity of these springs, the bearing 12 can be slid in the axial direction and adjusted. Also, the bearing 12 can be adjusted against the axial impact caused by vibration after assembly in the vehicle body.
As before, the impact can be absorbed by either wave spring washer 15 or 17.
Further, load stress in the vertical direction can be absorbed by the inner and outer circumferences of the full-circumference sleeve bearing 2 and the inner circumferences of the holes in the shaft portion 7 and the cylindrical bearing 12. Note that the sliding of the cylindrical bearing 12 in the axial direction is performed when the shaft body 4 is attached to the nut 24.
The cylindrical bearing 12 is fastened to the side surface of the bearing support frame 1 via the flat washer 23 and the leaf spring 27, so it cannot slide from side to side. It is possible to slide along the outer peripheral surface of the body 4, and at this time, the protrusion 1 of the shaft body 4
0 and 10 slide while being fitted into either the fan-shaped notches 18 and 19 or 18 and 20 formed in the collar 16 of the cylindrical bearing 12.

Furthermore, when the cabinet 38 is assembled, the pawl 33 of the leaf spring 27 is inserted into the keyway 11 of the threaded portion 8 of the shaft body 4.
When engaged, the engagement protrusion 30 of the support rod 25 of the leaf spring 27 is engaged with the rotation regulating engagement groove 34a of the bearing support frame 1, as shown in FIG.
The engagement protrusion 31 of the other support rod 26 is engaged with the rotation restricting engagement groove 34'a, and at the same time, the bent portion 29 of the support rod 26 abuts against the side surface 36 of the rotation prevention protrusion 35. Rotation in the direction of the arrow shown in FIG. 4, that is, in the counterclockwise direction, is restricted and maintained.

That is, this regulation is achieved by the engagement between the protrusion 10 of the shaft 4 and the fan-shaped notches 18 and 19 or 18 and 20 of the flange 16 of the cylindrical bearing 12 through the shaft 4 to the cylindrical bearing 12. and therefore cabinet 3
The rotation angle of 8 is regulated.

Furthermore, when the cabinet 38 is rotated in the indicated direction by a predetermined angle of approximately 22 degrees as shown in FIG. As a result, the protrusion 30 of the support rod 25 of the leaf spring 27 engages with the rotation restriction engagement groove 34b having an angle of about 22° clockwise from the rotation restriction engagement groove 34a, and at the same time, the projection 31 of the support rod 26 slides on the side surface of the bearing support frame by the same angle clockwise from the rotation regulating engagement groove 34'a and engages with the rotation regulating engagement groove 34'b.

Therefore, the shaft body 4 is engaged with the leaf spring 27 at a position of approximately 22 degrees clockwise, and this is transmitted to the cabinet 38 via the cylindrical bearing 12, and the cabinet 38 is rotated clockwise at approximately 22 degrees. It will be locked in a 22° rotated position.

Note that the rotation of the shaft body 4 at this time is caused by the side surface 2 of the shaft portion 7.
1 and the side surface of the bearing support frame 1 and the elasticity of the wave spring washers 15, 17 and the leaf spring 27. The cabinet 38 is rotated clockwise approximately every 22 degrees by engaging the protrusions 30, 31 of the support rods 25, 26 of the leaf spring 27 with the rotation regulating engagement groove array 34 in the same manner as described above. It will be stopped.

As mentioned above, the angle θ ₃ in FIG.
When the cabinet 38 is rotated clockwise by the same amount, the bent portion 28 of the support rod 25 of the leaf spring 27 will move from the side surface 3 of the rotation stopper projection 35 as shown by the two-dot chain line.
7 and makes further rotation of the leaf spring 27 impossible. That is, by stopping the rotation of the leaf spring 27, the clockwise rotation of the shaft body 4 and the cylindrical bearing 12 is also restricted, and therefore the clockwise rotation of the cabinet 38 is restricted. Thereafter, it goes without saying that the cabinet 38 can be rotated in the opposite direction, that is, counterclockwise, in the same manner every 22 degrees until it returns to its initial position.

Furthermore, since the bearing support frame 1, the full-circumference sleeve bearing 2, the shaft body 4, and the fastening members such as nuts have sufficient strength, the cylindrical bearing 12 supported by them passes through the axis. It can maintain sufficient strength against loads in the direction perpendicular to the axis.

According to the embodiment of the present invention described above, the bearing structure can be manufactured easily at low cost without using expensive parts, and is suitable as a bearing structure for assembling a speaker cabinet, which allows the enjoyment of so-called audio to be enjoyed. It is. Furthermore, while making it easier to downsize the bearing part, the three main components of the full-circumference sleeve bearing, the shaft body, and the cylindrical bearing rotate between each other.
Since acting forces such as loads in the axial direction and in the direction perpendicular to the axis are shared, concentrated fatigue of the element due to concentration of acting forces on one part can be prevented.

In this embodiment, the mounting seat of the bearing support frame was arranged on a member formed by bending the frame at right angles, but it is needless to say that the mounting seat is not limited to this.
For example, a similar effect can be obtained when a flange-like member is formed from a full-circumference sleeve bearing, and the engagement between the cylindrical bearing and the shaft body is based on the engagement between the fan-shaped notch and the protrusion. However, it is needless to say that the invention is not limited to this, and the same effect can be obtained by engaging the hole with a pin or key, for example. Further, although a wave spring washer is used as the buffer member, it is needless to say that the present invention is not limited to this, and the same effect can be obtained even if a buffer member such as a compression coil spring is used.

According to the present invention, even when a large resin enclosure is fastened to the car body, it is possible to absorb the difference in thermal expansion and contraction (length) between the car body and the enclosure that occurs due to changes in the temperature inside the car. can.

[Effects of the invention] As described above, according to the bearing structure of this invention, the cylindrical bearing is slidably supported in the axial direction via the wave spring washer, making it easier to assemble the cabinet. It is possible to easily adjust the position of the shaft, and also to easily absorb shocks in the axial direction. In addition, a leaf spring that rotates together with the shaft body is provided, and a rotation-stopping protrusion that engages with the leaf spring and several rotation-restricting engagement grooves are provided on the side of the bearing support frame. The rotation angle of the shaft body and the cylindrical bearing can be regulated by engagement, and the cabinet can be locked at a desired position within this rotation range via the shaft body and the cylindrical bearing. . Furthermore, by providing sufficient strength to the bearing support frame, all-around sleeve bearing, shaft body, fastening members, etc., there are excellent effects such as maintaining sufficient strength against loads passing through the axis and in the direction perpendicular to the axis. .

[Brief explanation of the drawing]

Fig. 1 is an exploded perspective view showing one embodiment of the bearing structure according to this invention, Fig. 2 is a longitudinal cross-sectional view showing the same assembled state, Fig. 3 is a cross-sectional view taken along the line A--A in Fig. 2, and Fig. 4
The figure is a side view for explaining the engagement between the same leaf spring and the rotation-stopping protrusion and rotation-limiting engagement groove provided on the side surface of the bearing support frame. Figure 5 shows the bearing of this invention. 5A is a perspective view showing an example of use in which an enclosure-type cabinet is used to hold an enclosure-type cabinet;
The figure is a perspective view of a state in which it is assembled into a cabinet cylindrical bearing, Figure 6 is a vertical cross-sectional view showing an example of a conventional bearing that also serves as a shock absorber, and Figure 7 is a vertical cross-sectional view showing another example of a conventional bearing. FIG. 3 is a vertical cross-sectional view. DESCRIPTION OF SYMBOLS 1... Bearing support frame, 2... Full circumference sleeve bearing, 4... Shaft body, 8... Threaded part, 10... Protrusion, 11... Keyway, 12... Cylindrical bearing, 15...
... Wave spring washer, 16... Tsuba, 17... Wave spring washer, 18, 19, 20... Fan-shaped notch, 23...
...Flat washer, 24...Nut, 27...Plate spring, 2
8, 28', 29, 29'...Bending portion, 30, 31
...Engagement protrusion, 33...Claw, 34...Engagement groove row,
35...Protrusion for preventing rotation, 38...Enclosure type speaker cabinet.

Claims (1)

[Claims for Utility Model Registration] A bearing support frame in which a through hole is formed to pass through the end of the shaft, and a full circumference fixed integrally with the bearing support frame with a hollow portion aligned with the through hole. a sleeve bearing; a shaft body having a shaft portion that is fitted and supported in a hollow portion of the full-circumference sleeve bearing; and a stepped portion formed to have a large diameter and a step with the shaft portion; It is rotatably supported in sliding contact with the outer circumferential surface, and has a stepped side surface corresponding to the step of the shaft body formed on the inside, and a collar corresponding to the open end of the full circumference sleeve bearing. a cylindrical bearing; a cylindrical bearing mounted between a flange of the cylindrical bearing and an open end of the full-circumference sleeve bearing when the cylindrical bearing is attached to the full-circumference sleeve bearing by the shaft; a first elastic member that elastically engages the two; and a second elastic member that is installed between the stepped side surface of the cylindrical bearing and the step of the shaft body and elastically engages the two. A bearing structure characterized by having the following.