JP3304733B2 - Rotating heat sink and drum type brake for braking device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

TECHNICAL FIELD The present invention relates to improvements in rotary heat radiating plate及beauty drum brake such as brake drums or disc rotor for use in a braking device, such as a drum brake or a disc brake, in particular, rotary heat radiating plate The vibration characteristics can be improved, and so-called brake squeal can be reduced.

[0002]

2. Description of the Related Art A drum type brake, which is one of the conventional braking devices, is configured as shown in FIG. 27, and has an inner peripheral surface of a substantially cylindrical brake drum 1 as a rotary heat sink that rotates integrally with wheels. This is a device that performs braking using a frictional force generated when a lining 2a as a friction material of a substantially arc-shaped brake shoe 2 supported on the vehicle body side such as a member contacts the member 1a.

More specifically, this drum type brake has a back plate 3 fixed to the vehicle body side, so that the back plate 3 is located inside the inner peripheral surface 1 a of the brake drum 1. An anchor 4 receiving a braking torque is fixed, and one end side of a pair of brake shoes 2 is swingably attached to the anchor 4. Each of the pair of brake shoes 2 is disposed along the inner peripheral surface 1a of the brake drum 1, and when no braking is performed, the lining 2a fixed to the outer peripheral surface is separated from the inner peripheral surface 1a by a predetermined distance. They face each other at a distance.

A wheel cylinder 5 and a return spring 6 are disposed between opposite ends of the pair of brake shoes 2 at positions opposite to the anchor 4 side. Is supplied, a pair of pistons 5A, 5A,
5B is displaced in the extending direction, whereby the end of the brake shoe 2 opens right and left and is pressed toward the inner peripheral surface 1a,
The lining 2a is pressed against and contacts the inner peripheral surface 1a, and at the contact portion, the rotational force of the brake drum 1 is converted into frictional heat to perform braking.

In such a drum type brake,
When the lining 2a comes into contact with the inner peripheral surface 1a of the brake drum 1 to generate frictional heat, frictional vibrations generated on the frictional surfaces cause the brake drum 1 to vibrate, and the natural vibration of the brake drum 1 is excited. May cause unpleasant brake squeal. Here, an object such as a cylinder or a disk having the same thickness as the general brake drum 1 shown in FIG. ), 3 bar diameter mode (FIG. 28)
(B)), 4-bar diameter mode (see FIG. 28 (c)),
There are eigenmodes exhibiting vibration modes such as a five-node mode (see FIG. 28 (d)) and a six-node mode (see FIG. 28 (e)). In FIG. 27, since the object has a symmetry about an axis extending through the center of the brake drum 1 and extending in a direction perpendicular to the drawing), it is a double root. In addition, "the presence of a double root" means, in addition to one eigenmode as shown in FIGS. 28 (a) to ( e ), another eigenmode having the same shape whose phase is shifted by 1/4 period in the circumferential direction. That is, the modes are considered to exist at the same frequency.

In other words, when the peripheral surface of the brake drum 1 is vibrated while the surface thereof is stationary, the brake drum 1 has a symmetry about the rotation center axis regardless of any position in the circumferential direction. Since it is a certain object, a response mode in which the excitation point is always antinode appears, so it seems that the brake drum 1 has many eigenmodes.
8 (a) to 8 ( e ), it is possible to consider that the axis is rotating with respect to the brake drum 1 by considering the axis along the diameter as indicated by the chain line. Then, in terms of vibration,
A unique mode as shown in FIG. 28 (a) ~ (e) , which <br/> from can be considered as two eigenmodes of eigenmodes same shape shifted by 1/4 period exists, but its Is considered to have a double root.

When the peripheral surface of the brake drum 1 is vibrated while being rotated in the same manner as when the actual drum type brake is braked, the response mode in which the vibration point becomes an antinode is Not as if they were standing still in space.
This is called a space fixed mode. ). The appearance of such a spatial fixed mode means that the antinode of the eigenmode is always the excitation point, so that the mode is excited most efficiently, and the acoustic radiation efficiency is maximized.
It is often the main cause of actual brake squeal.

[0008] Such a phenomenon is not limited to the drum type brake. Even in a disk type brake in which a disk rotor serving as a rotating heat radiating plate which rotates integrally with the wheels is sandwiched by brake pads, the disk rotor does not have the same phenomenon. Since the disk is symmetrical about the rotation center axis, the same phenomenon occurs. As a conventional technique focusing on such a phenomenon, there is one disclosed in Japanese Patent Application Laid-Open No. 56-52633 (first conventional technique) previously proposed by the present applicant. That is, the first prior art is characterized in that at least three or more thick portions are formed at regular intervals in the circumferential direction on the outer peripheral surface of the brake drum. If formed, these thick portions are located at the antinode of one of the two eigenmodes as the three-node mode as shown in FIG. Lowering the resonance frequency, but for the other of the two eigenmodes, FIG.
As shown in (b), since it is located at the node of the mode, it acts as a stiffener and conversely raises the resonance frequency. Then, since the multiple roots are separated and the mode is not in the space fixed mode, the sound radiation efficiency is reduced, and the brake squeal is suppressed. The idea of separating mass roots by adding mass is described in “Papers” in “Transactions of the Japan Society of Mechanical Engineers (C), Vol. 55, No. 512 (1984-4)”.
No.88-0622A ”.

On the other hand, another prior art focusing on the above phenomenon is disclosed in Japanese Utility Model Laid-Open Publication No. 62-89537 (second prior art). That is, the second related art relates to a drum type brake, in which elastic members are interposed at equal intervals at a plurality of concentric circles between a bottom portion of a brake drum and a wheel disk which constitutes a road wheel together with a rim. The feature is that the wheel disc is tightened to the brake drum and the elastic member is pressed, for example, when six elastic members are interposed,
As shown in FIG. 31 (a), these elastic members are located on the antinodes for one of the two eigenmodes as the three-node mode, and act as elastic elements against the vibration of the brake drum to resonate. Although the frequency is increased, the other of the two eigenmodes does not act as an elastic element because it is located at a node of the mode as shown in FIG. 31 (b), so that the resonance frequency does not change. Then, since the multiple roots are separated and the mode is not in the space fixed mode, the sound radiation efficiency is reduced, and the brake squeal is suppressed.

[0010]

Certainly, if the configuration as in the first prior art is adopted, it is possible to separate three-node mode roots by forming, for example, three thick portions at regular intervals. Although it is possible to suppress brake noise to some extent, depending on the number of thick parts formed,
Since the order of the diameter node mode in which the heavy root can be separated is determined, there is also a problem that an unpleasant brake squeal may also occur in the diameter node mode in which the heavy root cannot be separated.

FIG. 30 shows a brake drum having six thick portions formed on the outer peripheral surface according to the first prior art, and FIG.
7 is a graph showing a calculation result of a difference between eigenvalues and a general brake drum 1 as shown in FIG. As can be seen from the result, when the additional mass is six, the diameter is 3
Although multiple roots can be separated for modes that are multiples of 3 such as the knot mode and the 6-node mode, for other orders, multiple roots cannot be separated even if the natural frequency can be reduced.

On the other hand, if the configuration as in the second prior art is adopted, for example, a double root in a three-node mode is separated by interposing six elastic members between the brake drum and the wheel disc at regular intervals. Because you can
Again it is possible to suppress the brake squeal to some extent,
Since the order of the diameter node mode that can separate the heavy root is determined by the number of elastic members to be interposed, there is a problem that unpleasant brake noise may still occur in the diameter node mode that cannot separate the heavy root. .

FIG. 31 shows how the eigenvalues of the diameter node mode are separated by using a drum type brake in which six elastic members are interposed between the brake drum and the wheel disk according to the second conventional technique. 9 is a graph showing a result calculated by the finite element method. As can be seen from this result, when the number of elastic members is six, the roots can be separated in modes that are multiples of 3 such as the three-node mode and the six-node mode, but the natural frequencies of other orders are different. It can be lowered, but not the roots.

That is, in any of the first prior art and the second prior art, when the number of additional masses and elastic members is determined, the order of the separable roots is determined. Here, as described in the above-mentioned paper, the relationship between the number N of the additional masses and the elastic members and the order i of the effective diameter node mode is as shown in Table 1 below. In Table 1, a circle indicates that a double root can be separated. According to Table 1, it can be seen that when two additional masses and two elastic members are used, the effect of improvement can be obtained for all orders, but in practice, the effect is not obtained for higher-order modes. The effect obtained is small, and with two additional masses and two elastic members, the frequency cannot be tuned freely for higher-order modes.

[0015]

[Table 1]

In an actual drum type brake as shown in FIG. 27, the inner peripheral surface 1a of the brake drum 1 is changed due to a difference in operating conditions such as an operating oil pressure of the wheel cylinder 5 and a change with time of the lining 2a. Since the frequency component of the frictional vibration generated between the lining 2a and the lining 2a changes, as long as the vibration can be reduced only for the diameter mode of a specific order as in the prior art described in the above-mentioned publication or article, Even in the situation, the brake squeal cannot be reduced sufficiently.

The present invention has been made in view of such an unsolved problem of the conventional technology, and it is possible to simultaneously separate a plurality of roots for a plurality of diameter node modes, so that the brake squeal is significantly increased. and its object is to provide a rotary heat radiating plate及beauty drum brake for braking apparatus can be reduced to.

[0018]

SUMMARY OF THE INVENTION In order to achieve the above object, a first aspect of the present invention is a rotary heat radiating device for a braking device which rotates integrally with a wheel and comes into contact with a friction material supported on a vehicle body during braking. in the plate, composed of a plurality of mass stiffness adjuster made to increase or decrease at least one of the mass and stiffness
The same group
The plurality of mass stiffness increasing / decreasing portions included in
The rigidity is equal to each other and is equally spaced in the circumferential direction.
The mass or rigidity of the mass rigidity increasing / decreasing part is
The masses that differ between the groups and are included in the group
The number of the stiffness increasing / decreasing portions was different between the groups .

[0019] The invention according to 請 Motomeko 2, the claim
In the rotary radiator plate for a braking device according to the first aspect,
Said group comprising two said mass stiffness increasing and decreasing parts
And the glue comprising six mass rigidity increasing / decreasing portions.
And the mass, comprising five mass rigidity increasing and decreasing portions
It is composed of a group and four mass rigidity increasing / decreasing units.
And the above group .

[0020]

[0021]

The invention according to claim 3 is the invention according to claims 1 and 2 above.
In the rotating radiator plate for a braking device according to the present invention, the rotating radiator plate for a braking device is a brake drum in a drum type brake, and the mass rigidity increasing / decreasing portion is a thick portion formed on an outer peripheral surface of the brake drum. Or it was made into a thin part.

According to a fourth aspect of the present invention, in the rotary radiator plate for a braking device according to the first and second aspects of the present invention, the rotary radiator plate for the brake device may be a disk rotor in a disk brake. A ventilated rotor having a plurality of bench holes penetrating between an inner peripheral surface and an outer peripheral surface is provided, and the mass rigidity increasing / decreasing portion is a thick portion or a thin portion formed on the inner surface of the bench hole.

[0024]

[0025]

[0026] hand, in order to achieve the above object, claim
The invention according to 5 is a drum type brake having a brake drum that rotates integrally with a wheel, comprising a plurality of elastic members interposed between an outer peripheral surface or a bottom outer surface of the brake drum and a road wheel of the wheel. Group
And a plurality included in the same group.
The elastic members have the same rigidity and the circumferential direction.
Are arranged at equal intervals, and the rigidity of the elastic member is
Different between each group and included in said group
The number of the elastic members was different between the groups.

[0027] The invention according to claim 6 is the above-described claim.
In the drum-type brake according to the fifth aspect, the seven
Said group consisting of said elastic members and six fronts
Said group consisting of said elastic members, and said five
Said group consisting of elastic members and four said bullets
And the above-mentioned group composed of an elastic member .

[0028]

[0029]

[0030] In their invention according to claim 7, in the drum brake is the invention according to the claims 5 and 6,
An annular member is disposed so as to face the outer peripheral surface or the bottom outer surface coaxially with the brake drum, and the elastic member is provided on the outer peripheral surface or the bottom outer surface of the brake drum,
It was interposed between the annular members. In other words, this claim
The invention according to claim 7 is the same as the invention according to claims 5 and 6 , except that the elastic member is interposed not between the brake drum and the road wheel but between the brake drum and the annular member. .

Further, the invention according to claim 8 is a drum type brake according to the invention according to claims 5 and 6 , wherein
A metal cylindrical member is disposed so as to surround the outer peripheral surface coaxially with the brake drum, and a claw portion extending outward is integrally formed at an edge portion of the cylindrical member, and the claw portion has elasticity. The bent claw portion was used as the elastic member by being brought into contact with the outer peripheral surface of the brake drum or the load wheel.

According to the first and second aspects of the present invention, the braking
Multiple mass rigidity increasing / decreasing parts are formed on the rotating heat sink for equipment
The rigidity increase or decrease of the same mass or rigidity in the circumferential direction
Since it is nothing but being arranged at equal intervals , the center of gravity of the entire mass rigidity increasing / decreasing part will be located on the rotation center axis of this rotating heat sink , so the rotating heat sink rotates with the wheel. However, its rotational balance does not collapse. And the system
When the rotating heat sink for motors is rotating, make up each group.
Due to the action of each mass stiffness increasing and decreasing part, only one order
And can separate multiple roots for many orders
From the frequency of frictional vibration generated on the rotating heat sink for the braking device
Even if the components change, almost no double roots appear. Yo
It is extremely unlikely that the fixed space mode will occur during braking
As a result, the sound emission efficiency is also reduced, so that brake squeal is suppressed.

[0033]

[0034]

[0035]

[0036] 請 Motomeko according to third invention, the above claim 1, 2
Is applied to the brake drum of the drum type brake, the mass rigidity increasing and decreasing portion is a thick portion or a thin portion formed on the outer peripheral surface of the brake drum,
The formation of the mass rigidity increasing / decreasing portion is easy. When the thick portion or thin portion is formed on an outer peripheral surface, because the action of the additional mass is most efficiently obtained, the claim 1, 2
Is more reliably exhibited, and the radiation efficiency is also improved.

The invention according to claim 4 is the invention according to claims 1 and 2 above.
The invention according to claim 1 is applied to a ventilated rotor which is one of the disc rotors of a disc brake, wherein the mass rigidity increasing / decreasing portion is a thick portion or a thin portion formed on the inner surface of the ventilated rotor. Therefore, it is easy to form the mass rigidity increasing / decreasing portion. And since the mass rigidity increasing / decreasing part is formed in the ventilated rotor, there is no problem even if the space in which the ventilated rotor is provided has a small space margin.

[0038]

[0039] In the invention according to claim 5 and 6, the center of gravity of the entire elastic member and are located on the axis of rotation of the brake drum, even if the rotating brake drum with a wheel, the The rotation balance does not collapse. And claims
As in the first and second aspects of the invention, when the brake drum rotates,
Are one-piece due to the action of each elastic member constituting each group.
Separate multiple roots for many orders, not just one
The friction vibration generated on the brake drum
Even if the frequency component of motion changes, double roots often appear
Absent. Therefore, the space fixing mode may occur during braking.
Performance becomes very small, and does acoustic emission efficiency decrease?
Therefore , brake squeal is suppressed.

[0040]

[0041]

[0042]

[0043] Also, if the invention according to claim 7, in addition to the effect of the invention according to the claims 5 and 6, it becomes possible to apply even without working against load wheel or the like.

According to the eighth aspect , in addition to the effects of the fifth and sixth aspects , since the elastic member is made of metal, the elastic member can be deteriorated due to frictional heat or the like. Is reduced.

[0045]

Embodiments of the present invention will be described below with reference to the drawings. FIGS. 1 and 2 show a first embodiment of the present invention. In this embodiment, the present invention is applied to a brake drum 1 as a rotary heat radiating plate used for a drum type brake as a braking device. It was done. The overall structure of the drum brake is shown in FIG.
Since the configuration is the same as that of the conventional configuration shown in FIG.

That is, the brake drum 1 of the present embodiment
Is formed in a substantially cylindrical shape as shown in FIG. 1 which is a perspective view thereof, and one end thereof (the side facing rightward in FIG. 1)
It is closed except for a central through-hole 1b and a plurality of bolt holes 1c used for mounting on the wheel side, and the other end is open, and a brake as shown in FIG. A back plate to which a shoe or a wheel cylinder is attached and which is supported on the vehicle body side is provided.

The outer peripheral surface 1d of the brake drum 1 has a shape that is long in the direction along the rotation center axis (the axis passing through the center of the cylindrical shape) of the brake drum 1 and short in the circumferential direction.
A plurality of thick portions 10A and 10 as mass rigidity increasing / decreasing portions
B _2, ..., 10F are formed. In addition, each thick portion 1
0A, 10B _2, ..., 10F is integrated with the cylindrical portion of the brake drum 1, the thick part 10A, 10
The entire brake drum 1 including B ₂ ,..., 10F is cast using a mold, similarly to the conventional brake drum.

The plurality of thick portions 10A, 10B ₂ ,
.., 10F, six thick portions 10B ₂ , 10B ₃ ,
10B ₄ , 10B ₅ and 10B ₆ have the same shape and the mass M _1B , and the four thick portions 10C ₂ , 10C ₃ , 10C ₅ and 10C ₆ have the same shape and the mass M _1C and the four thick portions 10
D ₂ , 10D ₃ , 10D ₄ and 10D ₅ have the same shape and the mass M _1D , and the two thick portions 10E ₂ and 10E ₄ have the same shape and the mass M _1E . And the thick part 1
Assuming that the mass of 0A is M _1A and the mass of the thick portion 10F is M _1F , the relations of the following equations are established between these masses M _{1A to} M _1F .

M _1A > M _1F > M _1E > M _1D > M _1C > M _1B > 0 (1) M _1A = M _1B + M _1C + M _1D + M _1E (2) M _1F = M _1C + M _1E (3) Arrangement position of these thick portions 10A, 10B ₂ ,..., 10F (the arrangement position means the position of the center of gravity of each thick portion).
Is as shown in FIG. 2 which is a cross-sectional view of the central portion in the axial direction of the brake drum 1. That is, the thick portion 10A
And 10F are arranged at positions separated by 180 degrees in the circumferential direction, and based on the position of the center of gravity of the thick portion 10A,
2π / 7 in the counterclockwise direction from the reference position in the circumferential direction.
(Radian:. Hereinafter, the unit of the angle is radian except where stated) thick part 10B ₂ are arranged in a position shifted by, likewise from arrangement position of the thick portion 10B ₂ 2
thick part 10B ₃ is disposed on [pi / 7 shifted position,
… And so on. Thus, seven thick portion of the thick part 10A and the thick part 10B ₂ ~10B ₇ are arranged at equal intervals in the circumferential direction.

Further, with reference to the arrangement position of the thick portion 10A, from the reference position in the circumferential direction in FIG.
Thick portion 10C ₂ is disposed shifted position, the thick portion 1 at a position also shifted by [pi / 3 from the thick portion 10C ₂
0C ₃ is disposed, likewise from the thick portion 10C ₃ [pi /
The thick portion 10F is arranged at a position shifted by 3 and the thick portion 10F is shifted from the thick portion 10F by the same π / 3.
C ₅ is provided, ..., it has become so on. Thus, the thick portion 10A, the thick portion 10C ₂ ~10C ₆ and six thick portions of the thick portion 10F is disposed at equal intervals in the circumferential direction.

Then, with reference to the arrangement position of the thick portion 10A, 2π in the counterclockwise direction in FIG.
/ Thick portion 10D ₂ in the 5 position shifted by is provided, the thick portion 10D ₃ is disposed in well 2 [pi / 5 shifted position from its thick portion 10D _2, has become so on. Thus, the thick portion of the five that the thick portion 10A and the thick portion 10D ₂ ~10D ₅ are arranged at equal intervals in the circumferential direction.

Further, the thick portions 10E ₂ and 10E ₄
Π / 2 in the circumferential direction from each of the thick portions 10A and 10F
It is arranged at the position shifted only. Therefore, the thick portion 10
The _four thick portions A, the thick portions 10E ₂ , 10E ₄ and the thick portion 10F are arranged at equal intervals in the circumferential direction. Then, the mass M _1A of the thick portion 10A, as shown in the above (2), equal to the sum of the mass M _1B ~M _1E, the thick portion 10A is thick portion 10B of the mass M _{1B 1} , the thick portion 10C of the mass M _{1C 1,} the mass M _1D thick portion 10D ₁ and mass M _1E
The thick portion 10E ₁ can be regarded as a thick portion that was integral.

Similarly, since the mass M _1F of the thick portion 10F is equal to the sum of the masses M _1C and M _1E as shown in the above equation (3), the thick portion 10F has a thickness of the mass M _1C . Meat part 10C
₄ and the thick portion 10E ₃ mass M _1E can be regarded as a thick portion which is integrally. From the above, the outer peripheral surface 1d of the brake drum 1, seven thick portion 10B of the mass M _1B spaced at equal intervals in the circumferential direction from the reference line is any diameter ₁ to 1
And 0B _7, the same reference line and six thick portions 10C ₁ ~10C ₆ mass M _1C spaced at equal intervals in the circumferential direction, from the same reference line circumferentially of mass M _1D spaced equidistantly five a thick portion 10D ₁ ~10D _5, four thick portion 10E ₁ ~10E mass M _1E spaced equidistantly from the same reference line in the circumferential direction
₄ is formed.

That is, a total of 22 thick portions are formed on the outer peripheral surface 1d of the brake drum 1, and these thick portions are divided into four groups (10B ₁ to 10B) having the same mass.
_{B 7, 10C 1 ~10C 6,} 10D 1 ~10D 5, 10
E _{1 to} E ₄ ), and the thick portions in each group are arranged at equal intervals in the circumferential direction.
With such a configuration, the outer peripheral surface 1 of the brake drum 1
Even if a large number of thick portions 10A, 10B ₂ ,..., 10F are formed in d, the thick portions having the same mass are arranged at equal intervals in the circumferential direction. 10A,
The center of gravity G of 10B ₂ ,..., 10F as a whole is located on the rotation center axis of the brake drum 1 (in FIG. 2, the axis extends in the direction perpendicular to the drawing through the center of the brake drum 1). Therefore, even if the brake drum 1 rotates at a high speed integrally with the wheels, the rotational balance is not lost.

When the brake drum 1 rotates,
Since the seven thick portion 10B ₁ ～10B ₇ acts as an additional mass, the multiple root for effective diameter 7 Section mode from Table 1 are separated. At the same time, six thick parts 10C
Since ₁ ～10C ₆ acts as an additional mass, the above Table 1
Multiple roots for effectively diameter 3,6,9 Section mode is separated from, since the thick portion 10D ₁ ~10D ₅ five acts as an additional mass, effectively diameter from Table 1 5,10
For the knot mode, the heavy roots are separated and the four thick portions 10E
Since ₁ ～10E ₄ acts as an additional mass, the above Table 1
, Effective roots of 2, 4, 8, 10 node mode are separated.

Therefore, each of the thick portions 10A, 10B ₂ ,.
By acting as an additional mass of 10F, the roots can be separated not only for one order but also for many orders, so that the operating conditions such as wheel cylinder oil pressure and the aging of the lining as a friction material on the brake shoe surface Even if the frequency component of the frictional vibration generated between the inner peripheral surface 1a of the brake drum 1 and the lining changes due to a change or the like, the double root hardly appears. Therefore, even if the inner peripheral surface 1a of the brake drum 1 and the lining come into contact with each other during the braking and the bending vibration is excited, the possibility that the space fixed mode is generated becomes extremely small, and the sound radiation efficiency is reduced. The squeal is suppressed and the noise level is reduced.

In the present embodiment, the thick portion 1 is provided on the outer peripheral surface 1a of the brake drum 1 as a mass rigidity increasing / decreasing portion.
0A to 10F, but those thick portions 10A to 10F
10F can be manufactured simultaneously with the casting of the brake drum 1 body. That is, since the brake drum 1 of the present embodiment can be manufactured by only slightly changing the mold, the manufacturing cost does not significantly increase as compared with the conventional brake drum.

If the thick portions 10A to 10F are formed on the outer peripheral surface 1a of the brake drum 1, the thick portions 10A to 10F are set in the bending vibration mode of the brake drum 1 as shown in FIG. On the other hand, it works efficiently as an additional mass. This means that to achieve the same effect,
Since the minimum thick portion is sufficient, the increase in the weight of the brake drum 1 due to the formation of the thick portion can be minimized, and the increase in unsprung weight can be reduced accordingly.

FIGS. 3 to 6 show a second embodiment of the present invention. In this embodiment, a ventilated rotor 11 as a rotary heat sink used for a disk-type brake as a braking device is used. To which the present invention is applied. Here, as shown in a schematic configuration in cross section in FIG. 3, the disc type brake sandwiches a ventilated rotor 11 as a disc rotor that rotates integrally with a wheel between a pair of brake pads 12, and This is a device that performs braking using a frictional force at a contact portion between the lining 12a as a friction material and the ventilated rotor 11. Specifically, a pair of brake pads 12 are attached to a torque member (not shown) fixed to the vehicle body so as to sandwich the ventilated rotor 11 from both sides. However, the brake pad 12 is supported by a torque member so as to be able to advance and retreat in the axial direction of the ventilated rotor 11 (horizontal direction in FIG. 3), and the torque member has a base 1 facing the back surface of one brake pad 12.
3a, a claw portion 13b facing the back surface of the other brake pad 12, and a connecting portion 13c connecting the base portion 13a and the claw portion 13b.
Are mounted so as to be able to advance and retreat in the axial direction via slide pins and the like. In the base 13 a of the cylinder body 13, a piston 1 capable of pressing the back surface of one of the brake pads 12 toward the ventilated rotor 11 is provided.
4 is formed, and the piston 14 is moved from the master cylinder (not shown) to the cylinder hole 1.
5 is advanced and retracted by the hydraulic pressure supplied to 5.

Therefore, when hydraulic pressure is supplied into the cylinder hole 15 during braking, the piston 14 moves to the ventilated rotor 11 side.
Is moved by the piston 14 toward the ventilated rotor 11, and the lining 12 a of the brake pad 12 contacts one surface of the ventilated rotor 11. When the piston 14 further moves toward the ventilated rotor 11, the cylinder body 13 moves in the direction opposite to the moving direction of the piston 14 due to the reaction force of the force pressing the brake pad 12, so that the claw portion 13b Moves to the ventilated rotor 11 side, the other brake pad 12 is pressed by the claw portion 13b and moves to the ventilated rotor 11, and the lining 12a of the brake pad 12 moves to the other side of the ventilated rotor 11. Touch the surface. Since such an operation is performed within a very short time, the ventilated rotor 11 is sandwiched from both sides by the pair of brake pads 12 almost at the same time as the brake pedal is depressed, and braking is performed.

As shown in FIG. 4, which is a perspective view of the ventilated rotor 11, an inner peripheral surface 11a (FIG.
(Not shown) and a plurality of bench holes 11A extending radially so as to penetrate between the outer peripheral surfaces 11d. Also, the inner peripheral surface 11a of the ventilated rotor 11
Hollow cylindrical part 1 coaxially protruding on one surface side
A central through-hole 11b and a plurality of bolt holes 11c used for mounting on the wheel side are formed in the end face of 1B.

As shown in FIG. 5, which is a sectional view of only the left half of the ventilated rotor 11 in the axial direction at the center in the present embodiment, the ventilated rotor 11 has an inner surface of a bench hole 11A. Is the thick part 10
A, 10B ₂ ,..., 10F are formed. The right half not shown in FIG. 5 is omitted because it appears symmetrically to the configuration of the left half in FIG.

FIG. 6 is a cross-sectional view of the left half of the normal ventilated rotor 11 'in which no thick portion is formed at the central portion in the axial direction. FIG. 5 and FIG. as can be seen, the thick portions 10A, 10B _2, ...,
10F is formed by appropriately increasing the thickness of the side surface of the bench hole 11A. And each thick part 1
0A, 10B _2, ..., the mass and arrangement positions of 10F, including also the right half (not shown) is the same as the first embodiment. That is, the thick portions 10A, 10A,
10B _2, ..., 10F and, the thick portion 10 of this embodiment
A, 10B ₂ ,..., 10F have the same mass and arrangement position of the thick portions represented by the same symbols.

With this configuration, also in the disk brake, the thick portions 10A, 10B ₂ ,..., 10F act as additional masses as in the first embodiment. Sometimes the ventilated rotor 11
Even if bending vibration is excited by contact between the lining 12a and the lining 12a, the possibility of occurrence of the space fixed mode is extremely small and the sound radiation efficiency is also reduced, so that brake squeal is suppressed and the noise level is reduced. .

Also in the present embodiment, the thick portions 10A to 10F are formed on the inner surface of the bench hole 11A of the ventilated rotor 11 as mass rigidity increasing / decreasing portions. 10F is bench hall 11
Since it can be manufactured at the same time as the casting of A, the manufacturing cost does not increase as compared with the conventional ventilated rotor, as in the first embodiment. Further, since a thick portion as a mass rigidity increasing / decreasing portion is formed in the ventilated rotor 11 and does not protrude to the outside, there is no problem even if the space in which this is provided is small. In addition, there is no need to change the surrounding design.

FIGS. 7 and 8 show a third embodiment of the present invention. This embodiment is similar to the first embodiment, except that a drum type brake as a braking device is provided. The present invention is applied to a brake drum 1 as a rotating heat sink used. The same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof will not be repeated.

That is, as shown in FIG. 7 which is a perspective view of the outer peripheral surface 1d of the brake drum 1 of this embodiment, and FIG. As in the embodiment, the plurality of thick portions 10H, 10I ₂ , 10
While I ₃ and 10J ₂ is formed, it is different and the number and formation position. That is, in this embodiment, four are thick portion 10H～10J ₂ is formed, the formation position, the thick portion 10H and 10J ₂ is spaced 180 degrees in the circumferential direction, of the thick portion 10J ₂ the gravity center position as a reference, the thick portion 10I ₂ from the reference position to the position shifted by [pi / 3 in FIG. 8 clockwise in the circumferential direction is arranged, [pi 8 counterclockwise from the reference position in the circumferential direction Thick portion 10I ₃ is provided at a position shifted by / 3.

The thick portions 10I ₂ and 10I ₃ have the same shape and a mass of M _1I . Further, assuming that the mass of the thick portion 10H is M _1H and the mass of the thick portion 10J ₂ is M _1J , the relationships of the following equations are established between the masses M _{1H to} M _1J . . M _1H > M _1I > M _1J > 0 (4) M _1H = M _1I + M _1J (5) Mass If there is a relationship between these formulas (4) and (5) in M _{1H to} M _1J , then mass M _1H is the thick part 10I ₁ of mass M _1I and mass M
Since the thick portion 10J ₁ of _1J can be regarded as a thick portion which is integrally on the outer circumferential surface 1d of the brake drum 1,
And any three of the thick portion of the mass M _1I spaced from the reference line at equal intervals in the circumferential direction 10I ₁ ~10I ₁ in diameter, from the same baseline circumferential direction into two masses M _{1 J} spaced equidistantly a thick portion 10J ₁ to 10 J _1, so that is formed.

That is, a total of five thick portions are formed on the outer peripheral surface 1d of the brake drum 1, and these thick portions are composed of two groups (10I _{1 to} 10I ₃ ,
10J _{1 to} 10J ₂ ), and the thick portions in each group are arranged at equal intervals in the circumferential direction. With such a configuration, even if a plurality of thick portions 10H, 10I ₂ , 10I ₃ and 10J ₂ are formed on the outer peripheral surface 1d of the brake drum 1, the thick portions having the same mass are formed in the circumferential direction. It is nothing but being arranged at intervals. Therefore, as in the first embodiment, even when the brake drum 1 rotates at high speed integrally with the wheels, the rotational balance is not lost.

When the brake drum 1 rotates,
Since the three thick portions 10I _{1 to} 10I ₇ act as additional masses, the roots are effectively separated from the above Table 1 for the 3, 6, 9-node mode, and the two thick portions 10J ₁ , 1
Since 0J ₂ acts as an additional mass, multiple roots are effectively separated from the above Table 1 for the 2, 4, 6, 8, 10 node mode. Therefore, similarly to the first embodiment, the multiple roots can be separated for not only one order but many orders, and the brake noise is suppressed and the noise level is reduced.

Further, since the number of the thick portions 10H to 10J ₂ is also four, there are advantages that the mold can be simplified and the increase in unsprung mass can be further suppressed. Other functions and effects are the same as those in the first embodiment. FIGS. 9 to 11 show a fourth embodiment of the present invention. In this embodiment, the present invention is also applied to a brake drum 1 as a rotary heat radiating plate used for a drum type brake as a braking device. Applied. The same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof will not be repeated.

That is, as shown in FIG. 9 which is a perspective view thereof and FIG. 10 which is a cross-sectional view of the central portion in the axial direction, the outer peripheral surface 1d of the brake drum 1 of this embodiment has a mass rigidity increasing / decreasing portion. four thick portion 10P _1, 10P _2, 10Q
₁ and 10Q _2, two thin-walled portion 20A ₁ and 20A ₂ and is formed as a mass stiffness adjuster. And
Its mass thick portion 10P ₁ and 10P ₂ its mass the same shape M _1P, its mass M _1Q is thick portion 10Q ₁ and 10Q ₂ the same shape, the thin-walled portion 20A ₁ and 20A ₂ in the same shape ( mass of the thin portion is the negative mass corresponding to the amount shaved outer circumferential surface 1d) a When M _2A, these mass M _1P, M
Between _1Q and M _2A, so that the following relationship holds the following equation.

M _1P > M _1Q >0> M _2A (6) The six thick portions 10P _{1 to} 10Q ₂ and the thin portions 20A ₁ and 20A ₂ are arranged at equal intervals in the circumferential direction. I have. However, the same mass thick portion 10P ₁ and 10P ₂
Each other, the thick portion 10Q ₁ and 10Q ₂ together, the thin portion 20A
₁ and 20A ₂ each other, so as to face each other across the axis of rotation of the brake drum 1, are disposed 180 degrees apart to the circumferential direction.

With such a configuration, the thick portion 10P ₁
～10Q ₂ and the thin portion 20A _1, 20A ₂ of the center of gravity of the whole G
Is located on the rotation center axis of the brake drum 1,
As in the first embodiment, the brake drum 1
Even if the wheel rotates at high speed integrally with the wheels, the rotational balance is not lost. Here, the equation of motion of the brake drum 1 without forming a thick portion 10P ₁ ~10Q ₂ and thin portions 20A _1, 20A ₂ at ^{all, ([K] -ω 2 [} M]) {x} = {F} ... ... (7) Where K is a rigid matrix, ω is a circular frequency, M is a mass matrix, x is a displacement vector, F is a load (external force), “[]” is a matrix,
“｛｝” Means a vector.

[0075] When performing a modal analysis on the expression (7), and _{^{([· k ·] -ω 2}} [· m ·]) {λ} = {f i} ...... (8). Here, [ ^· k _· ] and [ ^· m _· ] are diagonal matrices, and [ ^· k _· ] = [φ] ^T [K] [φ] [ ^· m _· ] = [φ] ^T [ M] [φ], [φ] is a modal matrix, and {λ} is a modal coordinate.

The above equation (8) is a non-coupled equation of motion, and can be separated into one single-degree-of-freedom mass-spring system equation for the i-node mode. In other words, the ^{_{(k i -ω 2 m i)}} λ i = 0 ...... (9). Here, the natural frequency ω _i, is _{ω i = (k i / m} i) 1/2 ...... (10).

On the other hand, the thick portion 10P₁-10Q_TwoAnd thin part
20A₁, 20A_TwoOf the brake drum 1 forming the
The equation is ([K] -ω^Two[M + ΔM]) {x} = {F} (11) This equation (11) was approximately obtained by equation (7).
Using the modal matrix [φ] to switch to the i-node mode
分離 k_i−ω^Two(M_i+ Δm_i)｝ Λ_i= 0 (12) Where Δm_i= ｛Φ_i｝^T[ΔM] ｛φ｝. Therefore, the natural frequency ω is determined by the thick portion [ΔM].
_i'Is ω_i'= ｛K_i/ (M_i+ Δm)｝^1/2 …… (13) Therefore, the natural frequency increment Δω_iIs Δω_i= (K_i/ M_i)^1/2− ｛K_i/ (M_i+ Δm_i)｝^1/2 = (K_i/ M_i)^1/2 ｛1-｛｛k_i/ (M_i+ Δm_i)｝ / (K_i/ M_i)｝^1/2＝ = ω₀｛1-1 / (1 + Δm_i/ M_i)^1/2｝ ≒ ω₀(Δm_i/ 2m_i) (14) That is, the eigenmode {φ} is generally known
In this case, the change Δf in the resonance frequency is approximately: Δf = f₀(Δm_i/ 2m) (15) Where f₀Is the original resonance frequency, m is modal
Mass, Δm_i= ｛Φ_i｝ ^T[ΔM] ｛φ_i｝.

As a result of calculating changes in eigenvalues for the two multiple root modes by using the equation (15), in the fourth embodiment, the thick portions 10P _{1 to} 10Q ₂ and the thin portions 20A ₁ , 20A ₂ , it was found that multiple roots could be separated for all nodes. Therefore, the conventional mass adding method of forming three additional masses described in the above publication, the mass adding method according to the fourth embodiment, and the case where the mass ratio is changed in the fourth embodiment are described. When the rate of change of the eigenvalue was calculated by the finite element method for nodes 2 to 6 for each of the above, the results shown in FIG. 11 were obtained. That is, by adopting the configuration of this embodiment having two types of additional masses of three types, the number of the additional masses is six, but the entire range from the node 2 to the node 6 is obtained, despite the fact that the number of the additional masses is six. It can be seen that heavy roots can be separated. In other words, since the roots of a large number of diameter node modes can be separated without forming a large number of additional masses, it is possible to avoid a significant increase in the weight of the brake drum 1 and complexity of the mold, and to reduce the unsprung weight and the production of the mold. There is an advantage that cost is not significantly increased. Further, from the results in FIG. 11, it was found that the rate of change of the eigenvalue of each mode (the degree of separation of the multiple roots) can be changed only by changing the ratio of the masses of the three types of additional masses. Therefore, there is also an advantage that the degree of freedom in arbitrarily setting the resonance frequency for each mode is increased.

Other functions and effects are the same as those of the first embodiment. 12 and 13 show a fifth embodiment of the present invention. In this embodiment, the present invention is also applied to a brake drum 1 as a rotary heat radiating plate used for a drum type brake as a braking device. Applied. The same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof will not be repeated.

That is, as shown in FIG. 12, which is a cross-sectional view of the outer peripheral surface 1d of the brake drum 1 according to the present embodiment in the axial center portion, six thick portions 10R as mass rigidity increasing / decreasing portions. _{1, 10R 2, 10S 1,} 10S 2, 10T
₁ and 10T ₂ and four thin portions 20B ₁ , 20B ₂ , 20C ₁ and 20C ₂ as mass stiffness increasing / decreasing portions are formed.

The thick portions 10R ₁ and 10R ₂ have the same shape and the mass M _1R , and the thick portions 10S ₁ and 10S ₂ have the same shape and the mass M _1S and the thick portions 10T ₁ and 10T _{2.
Has the} same shape, the mass is M _1T , and the thin portions 20B ₁ and 20B
₂ has the same shape, the mass of which is M _2B , and the thin portions 20C ₁ and 20C.
If C ₂ has the same shape and its mass is M _2C , these masses M
_1R, M _1S, M _1T, is between M _2B and M _2C, so that the following relationship holds the following equation.

M _1R , M _1S , M _1T >0> M _2B , M _2C (16) M _1R ≠ M _1S ≠ M _1T ≠ M _2B ≠ M _2C (17) meat portions 10R ₁ ~10T ₂ and the thin portion 20B ₁ ~20C ₂ are arranged at equal intervals in the circumferential direction. However, the thick portions 10R ₁ and 10R _{2 having the} same mass
, Thick portion 10S ₁ and 10S ₂ , thick portion 10T
₁ and 10T ₂ together, as the thin portion 20B ₁ and 20B ₂ each other, the thin-walled portion 20C ₁ and 20C ₂ each other, face each other across the axis of rotation of the brake drum 1, in the circumferential direction 1
They are spaced 80 degrees apart.

With such a configuration, the thick portion 10R ₁
〜１０10T ₂ and the center of gravity G of the thin portion 20B ₁ ２０20C ₂
Is located on the rotation center axis of the brake drum 1,
As in the first embodiment, the brake drum 1
Even if the wheel rotates at high speed integrally with the wheels, the rotational balance is not lost. Here, if there are ten mass rigidity increasing / decreasing parts as in the present embodiment, and all the mass rigidity increasing / decreasing parts are arranged at equal intervals in the circumferential direction, in order to maintain the rotational balance as described above, The following three are conceivable as mass relationships of each mass rigidity increasing / decreasing portion.

All the mass rigidity increasing / decreasing portions have the same mass (one kind of additional mass). Five types of mass stiffness increasing / decreasing parts having different masses are formed five by five.
(Two types of additional cells). Five types of mass stiffness increasing / decreasing portions having different masses are formed two by two, and the mass stiffness increasing / decreasing portions having the same mass are arranged at every π in the circumferential direction (three types of additional masses).

For each of the above arrangement methods, the rate of change of the eigenvalue was calculated by the finite element method, and the result shown in FIG. 13 was obtained. According to this, it can be seen that only in the above case, the multiple roots can be separated for many diameter node modes. Based on this concept, when the total number N of the mass stiffness increasing / decreasing parts N = 4, 6, 8, 9, 10, and 12 was examined for the possibility of separating the multiple roots, the results shown in Table 2 were obtained. In addition, M is the number of types of mass rigidity increasing / decreasing portions, θ is the circumferential arrangement interval (deg) of each mass rigidity increasing / decreasing portion, and i is the order of the diameter node mode.

Based on the results shown in Table 2, the present inventors have determined that the total number N of the mass stiffness increasing / decreasing portions is a non-prime number of 4 or more, and the mass stiffness increasing / decreasing １ ／ of the total number N is different. The mass stiffness increasing / decreasing portion of the same mass
It has been concluded that the multiple roots can be separated for a large number of diameter node modes without disturbing the rotational balance by disposing them so as to face each other with the rotation center axis interposed therebetween at a distance of 0 degrees.

[0087]

[Table 2]

Therefore, even in the configuration of the present embodiment,
Since the roots can be separated for many orders of the nodal modes without breaking the rotational balance, the possibility of the occurrence of the spatial fixed mode is extremely small and the acoustic radiation efficiency is reduced as in the first embodiment. Therefore, brake squeal is suppressed and the noise level is reduced. Moreover, according to the configuration of the present embodiment, the ten thick portions 10R
Since only have to form a _{1 ~10T 2} and the thin portion 20B ₁ ~20C _2, there is an advantage that does not lead to a significant increase in the manufacturing cost of the unsprung weight and mold.

According to Table 2 above, even if the total number N of the thick portions and the thin portions is relatively large, for example, 10 or 12, the arrangement position and the mass thereof can be determined very easily. There is also. That is, if the total number N of the thick portions and the thin portions is selected from a non-prime number of 4 or more, the formation positions of the thick portions and the thin portions are formed at N places equidistantly spaced in the circumferential direction of the outer peripheral surface 1d of the brake drum 1. (Mass stiffness increasing / decreasing portion forming positions) are set, and N / 2 types of thick portions or thin portions having different masses are placed at the N forming positions at the two thick portions opposing each other across the rotation center axis. It is only necessary to form such that the masses of the thin portions are equal.

Further, even in the configuration of the present embodiment, the rate of change of the eigenvalue (separation degree of multiple roots) of each mode can be changed only by changing the mass ratio of the additional mass. FIG. 14 is a view showing a sixth embodiment of the present invention. In this embodiment, a configuration similar to that of the fifth embodiment is replaced by a disk-type device as in the second embodiment. This is applied to the ventilated rotor 11 of the brake.

That is, the ventilator according to the present embodiment
On the inner surface of the benchhole 11 of the rotor 11
A total of six mass rigidity increasing / decreasing parts so that they are equally spaced
Thick part 10U as₁, 10U_Two, 10V₁, 10V
_TwoAnd thin part 20D₁, 20D _TwoAre formed, and each
Thick part 10U₁-10V_TwoAnd thin part 20D₁, 20D
_TwoOf those that oppose each other across the rotation center axis,
Amount. Therefore, the ventilator of this embodiment
In Table 2, N = 6 and M =
This corresponds to the case of 3.

For this reason, even in the configuration of the present embodiment, since multiple roots can be separated for a large number of diameter node modes without deteriorating the rotational balance, the spatial roots can be separated as in the first embodiment. Since the possibility of the occurrence of the fixed mode becomes extremely small and the sound radiation efficiency is also reduced, the brake noise is suppressed and the noise level is reduced.
Moreover, in the present embodiment, since the total number of the thick portion and the thin portion is set to six, which is relatively small, the bench hole 11A
Since there is no large resistance to the airflow flowing from the inner peripheral surface 11a side to the outer peripheral surface 11d side, there is an advantage that stable cooling performance can be maintained as compared with the configuration of the second embodiment.

In each of the above embodiments, the thick portion or the thin portion is provided to increase or decrease the mass of the brake drum 1 or the ventilated rotor 11 at a predetermined circumferential position. As described with reference to FIG. 29, the rigidity may be increased or decreased in order to separate the heavy root. Therefore, instead of the structure for increasing or decreasing the mass described in each of the above embodiments, the rigidity may be reduced. May be adopted as the mass rigidity increasing / decreasing section. However, in reality, the thick portion and the thin portion described in each of the above embodiments have an effect of increasing and decreasing the mass at the formation position and also increasing and decreasing the rigidity. In other words, considering the ratio of the thickness of the thick portion or the thin portion to the width in the circumferential direction, if the thickness is increased relative to the width, the effect of increasing or decreasing the mass increases, and the width increases relative to the thickness. Then, the effect of increasing or decreasing the rigidity is increased.

However, increasing or decreasing only the rigidity without changing the mass is technically troublesome and not advantageous in terms of cost. It is most desirable that both the mass and the rigidity be appropriately increased or decreased by forming a portion and appropriately selecting the thickness and width thereof. In this case, as can be seen from the above equation (13), an increase in mass has an effect of lowering the resonance frequency, and an increase in rigidity has an effect of increasing the resonance frequency. Tuning can be performed more finely.

FIGS. 15 to 17 show a seventh embodiment of the present invention. FIG. 15 is a sectional view (upper half) along the axis of a drum brake according to the present invention, and FIG. FIG. 3 is a cross-sectional view of the brake drum 1 at a central portion in the axial direction. The same components as those in the above-described embodiments and the conventional drum-type brake are denoted by the same reference numerals, and redundant description will be omitted.

That is, the brake drum 1 is mounted on the road wheel 12 comprising the rim 12A and the wheel disc 12B.
Integrally with the hub 13 via a hub bolt 13a, so that the brake drum 1 rotates integrally with the wheels. Note that a tire (not shown) is held on the outer peripheral surface of the rim 12A, and the tire and the road wheel 12 form a wheel. The hub 13 is rotatably supported by an axle housing 15 via a bearing 14.
The back plate 3 is fixed to 5.

Then, the outer peripheral surface 1d of the brake drum 1
And between the inner peripheral surface of the wheel disc 12B of the road wheel 12 and at six locations equally spaced in the circumferential direction,
The elastic members 30A ₁ , 3 made of six rubber-like elastic bodies are arranged concentrically around the rotation center axis of the brake drum 1.
0A ₂ , 30B ₁ , 30B ₂ , 30C ₁ , 30C ₂
It is interposed in a radially compressed state. Each elastic member 30A ₁ ~30C ₂ is being bonded to the outer circumferential surface 1d of the brake drum 1, the wheel disc 12 during assembly
B is pressed into the inner peripheral surface to be in a compressed state.

Although each of the elastic members 30A _{1 to} 30C ₂ is made of the same elastic material, the two elastic members 30A ₁
And 30A ₂ is formed in the same shape (maximum), another two resilient members 30B ₁ and 30B ₂ are formed in the same shape (Min), the remaining two resilient member 30C ₁ and 30C ₂
Are formed in the same shape (medium). Then, the elastic member 30A ₁ and 30A ₂ is provided at a position opposite sides of the rotational center axis of the brake drum 1, the elastic member 30B
₁ and 30B ₂ is provided at a position opposite sides of the rotational center axis of the brake drum 1, the elastic member 30C ₁ and 30
C ₂ is provided at a position facing the rotation center axis of the brake drum 1.

That is, in the present embodiment, two types of elastic members having different stiffness are provided two by two, and a total of six elastic members 30A _{1 to} 30C ₂ are arranged at equal intervals in the circumferential direction, two resilient members 30A ₁ and 30 equal
A ₂ , 30B _1, 30B ₂ , 30C _1, and 30C ₂ are located at positions opposing each other across the rotation center axis of the brake drum 1, and elastic members adjacent in the circumferential direction have different rigidities.

With such a configuration, the elastic members 30A _{1 to} 30C ₂ having the same rigidity are located opposite to each other with the rotation center axis of the brake drum 1 interposed therebetween (in other words, the elastic members 30A _{1 to} 30C having the same rigidity). ₂ is 180 ° on a concentric circle
The elastic members 30A _{1 to} 3A
0C ₂ overall center of gravity, will be located on the axis of rotation of the brake drum 1, the brake drum 1 is also rotated at a high speed, never rotation balance collapses.

On the other hand, when the eigenmode of the configuration of the present embodiment was calculated by the finite element method, the result shown in FIG. 17 was obtained. In FIG 17, the horizontal axis represents the number of nodes diameter section mode, the vertical axis represents the rate of change of the eigenvalue shows the calculation results for the two changing the rigidity ratio of the elastic member 30A ₁ ~30C ₂ . As a comparative example, the calculation result of the change rate of the eigenvalue according to the above-described second related art is also displayed.

According to this calculation result, by adopting the configuration of the present embodiment having two types of elastic members, three types of elastic members 30A _{1 to} 30C ₂ are provided in spite of the fact that the number is six. It can be seen that multiple roots can be separated throughout the range from 2 to 6 nodes in diameter. That is, even if the number of the elastic members is not extremely increased, there is an advantage that the roots of the diameter node mode of many orders can be separated and the production cost does not increase significantly.

Further, from the results shown in FIG. 17, only by changing the rigidity ratio of the three types of elastic members 30A _{1 to} 30C ₂ ,
It has been found that the rate of change of the eigenvalue of each mode (the degree of separation of multiple roots) can also be changed. Therefore, there is also an advantage that the degree of freedom in arbitrarily setting the resonance frequency for each mode is increased. 18 and 19 are views showing an eighth embodiment of the present invention. FIG. 18 is a cross-sectional view (upper half) along the axis of the drum brake, and FIG. 19 is a perspective view of the brake drum 1. is there. The same components as those in the above-described embodiments and the conventional drum-type brake are denoted by the same reference numerals, and redundant description will be omitted.

[0104] That is, in this embodiment, has a seventh elastic member 30A ₁ ~30C ₂ as in the embodiment of, the elastic member 30A ₁ ~30C _2, the bottom of the brake drum 1 1e is interposed between the outer surface and the side surface of the wheel disk 12B opposed thereto. Also in the present embodiment, the elastic member 30A ₁ ~30C ₂ disposed coaxially about the central axis of rotation of the brake drum 1, the two elastic members 30A ₁ and 30A ₂ is formed in the same shape (maximum),
Another two resilient members 30B ₁ and 30B ₂ are formed in the same shape (Min), the remaining two resilient member 30C ₁ and 30C ₂ are formed in the same shape (moderate), the elastic member 30A ₁ and 30A ₂ is provided at a position opposite sides of the rotational center axis of the brake drum 1, the elastic member 30B ₁ and 30B ₂ is provided at a position opposite sides of the rotational center axis of the brake drum 1, the elastic member 30C ₁ and 30C ₂
Are provided at positions facing each other across the rotation center axis of the brake drum 1.

[0105] Changing the site to be interposed in this way the elastic member 30A ₁ ~30C _2, it is possible to obtain the same effect as in the above-described seventh embodiment. 20 and 21
FIG. 20 is a view showing a ninth embodiment of the present invention, FIG. 20 is a perspective view of the brake drum 1, and FIG.
FIG. It is to be noted that the same components as those in the above-described embodiments are denoted by the same reference numerals, and the description thereof will not be repeated.

That is, in the present embodiment, a short cylindrical metal annular member 32 is disposed coaxially with the brake drum 1 so as to surround the outer peripheral surface 1d thereof, and the outer peripheral surface 1d and the annular member 32 are provided. An elastic member 30 is provided between the elastic member 30 and the inner peripheral surface.
It is interposed the A ₁ ~30C _2. The elastic member 30
A ₁ ~30C _2, by being pressed into the outer circumferential surface 1d of the brake drum 1 in a state of being adhered to the inner peripheral surface of the annular member 32 so as to interposed in a compressed state between their outer circumferential surfaces 1d and the annular member 32 It has become.

The outer diameter of the annular member 32 is determined by the rim 12A of the road wheel 12 surrounding the annular member 32.
And the inner diameter of the wheel disc 12B. Therefore, the annular member 32 is
And no contact. In addition, the elastic members 30A _{1 to} 3A
The shape of 0C ₂ arrangement relationship is the same as the seventh embodiment.

Even with such a configuration, the elastic members 30A _{1 to} 30C interposed between the outer peripheral surface 1d and the annular member 32 can be used.
₂ exhibits the same operation as in the seventh embodiment, so that the same operation and effect as in the seventh embodiment can be obtained. Moreover, if the present embodiment, processing such as, for example, road wheels 12 in order to dispose the elastic member 30A ₁ ~30C ₂ is no unnecessary. Therefore, even if the inner diameter of the road wheel 12 is changed as a result of, for example, replacing the wheels by the user of the vehicle, there is no need for special processing or the like, which is advantageous in terms of cost. There is an advantage that it can be easily applied to

In the ninth embodiment, the annular member 32 surrounds the outer peripheral surface 1d of the brake drum 1.
However, the present invention is not limited to this, and a thin plate-shaped ring member as an annular member is disposed coaxially with the brake drum 1 so as to face the outer surface of the bottom 1e thereof.
An elastic member 30A is provided between the outer surface of the bottom 1e and the ring member.
The _{1 ~30C 2} may be interposed.

FIGS. 22 to 24 show a tenth embodiment of the present invention. FIG. 22 is a perspective view of the brake drum 1, and FIG.
It is to be noted that the same components as those in the above-described embodiments are denoted by the same reference numerals, and the description thereof will not be repeated. That is, in the present embodiment, there is provided a belt 34 made of a thin steel plate as an annular member having a diameter slightly larger than the outer diameter of the brake drum 1, and an inner surface of the belt 34 and an outer peripheral surface 1 d of the brake drum 1 are formed. during, six elastic member 30D ₁ ~30F ₂ is turned so as to be interposed in a compressed state.

Specifically, the elastic member 30D₁~ 30F_Two
Is a belt 34 detached from the brake drum 1
As shown in FIG. 24 which is a front sectional view of
Adhesion is made at six locations at equal intervals in the circumferential direction of the inner peripheral surface of the
Elastic member 3 which is fixed
0D₁And 30D_Two, 30E₁And 30E_Two, 30F ₁
And 30F_TwoForm a group, and each group
Are made of the same elastic material
However, each group is made of a different elastic material. Ma
Each elastic member 30D₁~ 30F_TwoThe thickness of the brake
As shown in FIG.
Than the outer peripheral surface 1d of the brake drum 1 indicated by a two-dot chain line
It is dimensioned to enter slightly inside. Therefore,
Elastic member 30D₁~ 30F_TwoWith the belt 34 fixed
When assembled to the brake drum 1, FIG. 22 and FIG.
As shown, the belt 34 is attached to each elastic member 30D.₁~ 30
F_TwoBetween the two, a tensile force is applied between them.
It will be almost flat.

Even with such a configuration, the elastic members 30D _{1 to} 30F ₂ interposed between the outer peripheral surface 1d and the belt 34.
Exerts the same effect as that of the seventh embodiment, so that the same operation and effect as those of the seventh embodiment can be obtained, and the cost can be reduced similarly to the ninth embodiment. It is advantageous and has the advantage that it can be easily applied to existing drum brakes.

Further, since the belt 34 made of a thin steel plate is used, the weight of the brake drum 1 can be reduced as compared with the ninth embodiment, and the moment of inertia of the wheels is unnecessarily increased. There is an advantage that brake squeal can be prevented without affecting power performance such as acceleration performance. FIGS. 25 and 26 show an eleventh embodiment of the present invention.
FIG. 25 is a sectional view of a drum type brake. It is to be noted that the same components as those in the above-described embodiments are denoted by the same reference numerals, and the description thereof will not be repeated.

That is, in the present embodiment, a metal ring 36 as a cylindrical member having a diameter slightly larger than the outer diameter of the brake drum 1 is provided. same length six claw portion 36A ₁ ~36C ₂ of spaced equidistantly, are formed integrally so as to extend outwardly from the edge portion. Also, the other edge portion of the ring 36, the claw portions 36A ₁ identical to a formation position of ～36C ₂ from its edge portion so as to extend outwardly length of six claw portion 36D ₁ ~36F ₂ is integrally Is formed. However, the claw portion 36D ₁ ~36F _2, the claw portion 36A ₁
It is slightly shorter than the ~36C _2.

Claw portions 36A ₁ to 36A formed on one edge portion
36C ₂ are claw portions 36A ₁ and 36A _2, 36B ₁ and 36B ₂ that face each other across the central axis of the ring 36, 36C
₁ and 36C ₂ form a group, respectively, the claw portions constituting each group are formed in the same width dimension, but a different width dimensions between the groups. Similarly, the pawl portion 36D ₁ ~36F ₂ also, the claw portions 36D ₁ and 36D ₂ facing each other across the central axis of the ring 36, 36E ₁ and 36
E ₂ , 36F _1, and 36F ₂ each form a group, and the claws forming each group have the same width, but have different widths between the groups.

The claws 36A _{1 to} 36C ₂ are bent in a substantially U-shaped cross section so that the tip ends enter the inside of the ring 36. Also, the claws 36D _{1 to} 36F
₂ is that the base end on the ring 36 side is the ring 36
Is bent at an obtuse angle so as to slightly rise outward in the radial direction, and its tip is bent at substantially 90 ° so as to face radially inward of the ring 36.

Then, as shown in FIG.
It is interposed between the inner peripheral surface of the outer circumferential surface 1d and the wheel disc 12B of the brake drum 1, this time, the claw portions 36A ₁ ~36C ₂ bent in a substantially U-shaped, the bent portion the state toward the vehicle width direction inner side, together with the tip portion abuts on the outer circumferential surface 1d to the extent that C-shape is crushed, the pawl portion 36D ₁ ~36F ₂ is bent portion on the base end side is substantially flat Wheel disc 12B to the extent
It comes into contact with the inner peripheral surface.

Thus, the claws 36A _{1 to} 36F ₂ are
It will be substantially used as an elastic member in the present invention. With the above configuration, each of the claws 36A ₁ to 36A ₁ to
Since the size of the 36F ₂ is set as described above, the center of gravity of the entire their claw portions 36A ₁ ~36F _2, the brake drum 1
Will be located on the rotation center axis of. Therefore, even if the brake drum 1 rotates at a high speed integrally with the wheels, the rotational balance is not lost.

The pawl portions 36A _{1 to} 36F ₂ have the same rigidity in the above-mentioned groups because the width dimensions thereof are adjusted, but the rigidity is different between the respective groups. Elastic member 30A ₁ in the form of
～30C ₂ and can be substantially regarded as the same. Therefore, the same function and effect as those of the seventh embodiment can be obtained.

In this embodiment, since the elastic member is realized by a metal spring instead of a rubber-like elastic body,
There is an advantage that the possibility that the elastic member is degraded by frictional heat generated at the time of braking or the like is extremely small, and the durability is improved. Further, the elastic because the claw portions 36A ₁ ~36F ₂ that member to the formation is integral with the ring 36, the rubber-like elastic member outer peripheral surface 1d and the annular member as the first 7-10 embodiment of There is also an advantage that there is no need to adhere to the inner peripheral surface of the P. 32, and there is no need for labor and time for adhesion and positioning during manufacturing, thereby improving efficiency.

In the seventh to tenth embodiments,
Although the elastic member in the present invention is a rubber-like elastic body,
The present invention is not limited to this, and may be a metal elastic member as in the eleventh embodiment, or
It may be an elastic member made of synthetic resin. The arrangement pattern of the elastic members is not limited to the seventh to eleventh embodiments. That is, the thick part and the thin part in the first to sixth embodiments are made to correspond to the elastic member, and the relation of the mass of the thick part and the thin part is replaced with the relation of the rigidity of the elastic member. The arrangement pattern of the thick part and the thin part in the first to sixth embodiments can be applied as it is to the arrangement pattern of the elastic member, and the same operation and effect as those of the first to sixth embodiments can be obtained. It is done.

Further, the number of the elastic members is not limited to six, but may be five or less or seven or more.

[0123]

As described above, according to the present invention,
One order without breaking the rotational balance of the rotating heat sink
Not only separate multiple roots for many orders
As a result, the vibration of the rotary radiator plate is further reduced and brake squeal can be suppressed, so that there is an effect that the noise level can be reduced.

In particular , the invention according to claim 3 does not cause a significant increase in the weight and manufacturing cost of the brake drum as the rotary heat sink, and also improves the heat radiation efficiency and the cooling performance of the rotary heat sink. There is also the effect of doing.

The invention according to claim 4 does not cause a significant increase in the manufacturing cost of the ventilated rotor as the rotary radiator plate, and does not allow a space for the ventilated rotor to be disposed. Even if it is small, it can be easily installed, so there is no need to change the surrounding design.
No.

Further, according to the fifth and sixth aspects of the present invention, the rotation balance of the brake drum is not lost.
Separate multiple roots for many orders instead of just one
It can be, because can suppress brake noise vibration of the rotary heat radiating plate is further reduced, the effect there Ru of reducing the noise level.

According to the seventh aspect of the invention, there is no need for any processing of the road wheel or the like, which is advantageous in terms of cost and can be easily applied to the current drum type brake. There is also. Further, according to the invention of claim 8 , there is an effect that the durability is improved and the efficiency is improved by eliminating the trouble of bonding and positioning at the time of manufacturing.

[Brief description of the drawings]

FIG. 1 is a perspective view of a brake drum according to a first embodiment.

FIG. 2 is a cross-sectional view of the brake drum according to the first embodiment at a central portion in the axial direction.

FIG. 3 is a cross-sectional view illustrating a configuration of a disc brake.

FIG. 4 is a perspective view of a ventilated rotor.

FIG. 5 is a sectional view of a ventilated rotor according to a second embodiment at an axially central portion.

FIG. 6 is a sectional view of a conventional ventilated rotor at a central portion in the axial direction.

FIG. 7 is a perspective view of a brake drum according to a third embodiment.

FIG. 8 is a cross-sectional view at a central portion in the axial direction of a brake drum according to a third embodiment.

FIG. 9 is a perspective view of a brake drum according to a fourth embodiment.

FIG. 10 is a cross-sectional view of a brake drum according to a fourth embodiment at a central portion in the axial direction.

FIG. 11 is a graph illustrating the operation and effect of the fourth embodiment.

FIG. 12 is a cross-sectional view of a brake drum according to a fifth embodiment at a central portion in the axial direction.

FIG. 13 is a graph illustrating the operation and effect of the fifth embodiment.

FIG. 14 is a sectional view of a brake drum according to a sixth embodiment at a central portion in the axial direction.

FIG. 15 is a sectional view of a drum type brake according to a seventh embodiment.

FIG. 16 is a cross-sectional view of a brake drum according to a seventh embodiment at a central portion in the axial direction.

FIG. 17 is a graph illustrating the operation and effect of the seventh embodiment.

FIG. 18 is a sectional view of a drum brake according to an eighth embodiment.

FIG. 19 is a perspective view of a brake drum according to an eighth embodiment.

FIG. 20 is a perspective view of a brake drum according to a ninth embodiment.

FIG. 21 is a sectional view of a brake drum according to a ninth embodiment at a central portion in the axial direction.

FIG. 22 is a perspective view of a brake drum according to a tenth embodiment.

FIG. 23 is a sectional view of a brake drum according to a tenth embodiment at a central portion in the axial direction.

FIG. 24 is a sectional view of a belt according to a tenth embodiment.

FIG. 25 is a sectional view of a drum type brake according to an eleventh embodiment.

FIG. 26 is a perspective view of a ring according to the eleventh embodiment.

FIG. 27 is a sectional view showing a configuration of a general drum type brake.

FIG. 28 is an explanatory diagram of a specific mode of the brake drum.

FIG. 29 is a conceptual diagram illustrating the action of separating a heavy root according to the first conventional technique.

FIG. 30 is a graph showing a change rate of an eigenvalue in the first related art.

FIG. 31 is a conceptual diagram illustrating the action of separating heavy roots according to the second conventional technique.

FIG. 32 is a graph showing a change rate of an eigenvalue in the second conventional technique.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 Brake drum (rotating heat sink) 1a Inner peripheral surface 1d Outer peripheral surface 1e Bottom part 2 Brake shoe 2a Lining (friction material) 10A to 10V ₂ Thick part (mass rigidity increasing / decreasing part) 11 Ventilated rotor (rotating heat sink) 11a the inner peripheral surface 11d outer peripheral surface 11A bench hole 12 brake pads 12a lining (friction member) 20A ₁ ~20D ₂ thin portion (mass stiffness adjuster) 30A ₁ ~30F ₂ elastic member 32 annular member 34 belt (annular member) 36 ring ( Cylindrical member) 36A _{1 to} 36F ₂ claw (elastic member)

──────────────────────────────────────────────────続 き Continuation of front page (56) References JP-A-58-5032 (JP, A) JP-A-57-208329 (JP, A) JP-A-61-290241 (JP, A) JP-A-58-208 200827 (JP, A) Fully open sho 59-107344 (JP, U) Fully open sho 55-34577 (JP, U) Fully open sho 62-89537 (JP, U) (58) Fields investigated (Int. ⁷ , DB name) F16D 65/10 F16D 65/12

Claims (8)

(57) [Claims] 1. A wheel and rotating integrally with and at the time of braking contact with the friction material supported on the vehicle body side brake device for a rotating heat sink mass and a plurality of mass formed by increasing or decreasing at least one of the rigid Glue composed of rigidity increasing / decreasing part
Group, and multiple groups included in the same group
The number of the mass stiffness increasing / decreasing portions is such that the mass and the stiffness are different from each other.
Are equally and circumferentially equally spaced, said mass
The mass or stiffness of the stiffness increasing / decreasing part differs between the above groups.
Of the mass rigidity increasing / decreasing unit included in the group.
Number rotary heat radiating plate for a braking device which is characterized that you have different between the respective groups. 2. The method according to claim 1 , wherein said mass rigidity increasing / decreasing portion comprises :
Consisting of the group and the six mass rigidity increasing / decreasing units
From the group and the five mass stiffness increasing / decreasing units
Said group comprising and four said mass rigidity increasing / decreasing parts
The rotary heat radiating plate for a braking device according to claim 1 , further comprising: the group comprising: 3. The rotary radiator plate for a braking device is a drum type.
The brake drum in the brake, said mass rigidity
The increasing / decreasing portion has a thickness formed on the outer peripheral surface of the brake drum.
The rotating heat radiating plate for a braking device according to claim 1 or 2 , wherein the rotating heat radiating plate is a thick portion or a thin portion . 4. The rotating radiator plate for a braking device is a disk.
Of the disk rotor in the type brake, the inner peripheral surface and
A bench formed with multiple bench holes penetrating between the outer peripheral surfaces
Wherein the mass rigidity increasing / decreasing portion is
A thick portion or a thin portion formed on the inner surface of the bench hole
The rotary heat radiating plate for a braking device according to claim 1 or 2, wherein: 5. A brake drum which rotates integrally with a wheel.
A drum brake having the brake drum
Of the outer peripheral surface or bottom outer surface of the
Group consisting of multiple elastic members interposed between
Have multiple and multiple
The elastic members have the same rigidity and are circumferentially equal.
The elastic members are arranged at equal intervals, and the rigidity of the elastic member
Different between groups, before being included in said group
The number of elastic members should be different between each group.
And a drum type brake. 6. The device according to claim 6 , wherein said elastic member comprises seven said elastic members.
A group and the group comprising the six elastic members.
A loop and the glue comprising five of the elastic members.
Loop and the glue comprising the four elastic members.
The drum type brake according to claim 5, comprising: 7. An outer peripheral surface coaxial with said brake drum.
Or if an annular member is arranged so as to face the bottom outer surface,
In addition, the elastic member may be connected to the outer peripheral surface of the brake drum or
Is interposed between the bottom outer surface and the annular member.
A drum brake according to claim 5 or claim 6. 8. An outer peripheral surface coaxial with said brake drum.
A metal cylindrical member to surround the
And an externally extending claw portion at the edge of the cylindrical member.
Formed, and bend the claw part to generate elastic force.
Of the bent claw portion on the outer peripheral surface of the brake drum or
Abuts on the road wheel as the elastic member
A drum type brake according to claim 5 or 6, wherein the drum type brake is used.
Ki.