JPS641545Y2 - - Google Patents

Description

[Detailed explanation of the idea] This invention relates to disc brakes.

2. Description of the Related Art Conventionally, a disc brake is known in which a carrier that guides and supports a caliper is integrally formed with a nut of a vehicle. In this disc brake, a piston is housed in a carrier integrally formed with the nut of the vehicle, and in one of a pair of legs facing both sides of the disc and connected by a bridge part spanning the outer circumference of the disc. A caliper is formed in one of the pair of legs with a pair of through holes spaced apart in the rotational direction of the disk and extending in the axial direction of the disk. A pair of guide shafts (slide pins) are fitted into guide portions that are formed on the carrier to face each other, guide and support the pair of pads, and receive brake torque, and are screwed into the guide portions so as to extend in the axial direction of the disk, The pad is slidably attached in the axial direction of the disk, and is pressed against one side of the disk by the piston provided on one leg of the caliper, and the reaction force generated at this time causes the caliper to be pressed against the piston. The other pad is brought into pressure contact with the other side of the disk by the other leg.

However, in conventional disc brakes, the pitch between the pair of guide shafts attached to the carrier is equal to the pitch between the pair of through holes formed in the caliper, so the brake torque generated during braking causes the carrier to When deformed, this braking torque is applied to the caliper via the guide shaft and this guide shaft, which tends to reduce the mounting strength of the guide shaft to the carrier, easily damage the guide shaft, and damage the caliper to the carrier. There were drawbacks such as the sliding movement being hindered.

This idea was made in view of the above circumstances,
The pair of guide shafts provided in the carrier and the pair of through holes provided in the caliper have circular cross sections, and the diameter of the through holes is made larger than the diameter of the guide shaft, and the pitch between the pair of guide shafts is The pitch is set to be smaller than the pitch between the pair of through holes, and both guide shafts are brought into contact with the inner surface of the through hole on the sides that are close to each other, and the inner surface of the through hole on the opposite side from the guide shaft abutting inner surface and the guide By forming a gap between the guide shaft and the caliper that allows the guide shaft to move, no brake torque is applied to the guide shaft and caliper.
It is an object of the present invention to provide a disc brake which has sufficient mounting strength of a guide shaft and sufficient strength of the guide shaft, improves braking performance, and further increases durability.

An embodiment of this invention will be described below based on the drawings. In FIG. 1, reference numeral 1 denotes a carrier integrally formed in the knuckle of the vehicle, and guide portions 3 and 4 are formed on the carrier 1 so as to be spaced apart from each other in the direction of rotation of the disk 2 and face each other. A pair of pads 5 and 6, which are provided on opposite surfaces of the disk 2, are guided and supported by these guide portions 3 and 4 so as to be movable in the axial direction of the disk 2. The guide portions 3 and 4 are configured such that the braking torque generated by the pads 5 and 6 when the disc 2 is braked can be received by the guide surfaces 3a and 4a.
Further, in the guide parts 3 and 4, a bolt 8 inserted into the sleeve 7 and a bolt 10 inserted into the sleeve 9 are provided.
The sleeves 7 and 9 are fitted to the end surfaces of the guide portions 3 and 4 so as to extend in the axial direction of the disk 2, respectively, and have inner diameters slightly larger than the outer diameters of the sleeves 7 and 9, respectively. hole 1
1 and 12 and are screwed in.
Here, the sleeve 7 and the bolt 8 constitute a guide shaft 18, and the sleeve 9 and the bolt 10 constitute a guide shaft 14. Note that the sleeves 7 and 9 have the same dimensions.

Further, a caliper 15 is slidably attached to the carrier 1. This caliper 15 faces both sides of the disk 2 via pads 5 and 6,
A piston 17a is housed in one leg 17 of a pair of legs 17 and 18 connected by a bridge part 16 that spans the outer circumference of the disk 2, and a piston 17a is housed in this one leg 17 in the rotational direction of the disk 2. A pair of through holes 19 and 20 having a circular cross section are formed which are spaced apart and extend in the axial direction of the disk 2, and these through holes 19 and 20 are slidably fitted into the sleeves 7 and 9, respectively. be. In addition,
The inner diameters of the through holes 19 and 20 are the same. Further, the pitch A between the pair of guide shafts 13 and 14 is set smaller than the pitch B between the pair of through holes 19 and 20. That is, the diameters of the through holes 19 and 20 are larger than the outer diameters of the sleeves 7 and 9 by α as shown in FIG. 2, respectively.

As a result, the piston 17a receives oil pressure from a mass cylinder (not shown) and moves to the arrow C in FIG.
When moving in the direction, one of the pads 5 will touch the disk 2.
The caliper 15 moves in the direction of arrow D in the figure due to the reaction force generated at this time, and the other pad 6 presses against the other side of the disk 2, thereby causing the rotating disk 2 to move. Brake.
During this braking, a braking force is applied to the guide portion 4 of the carrier 1 in the direction of arrow E in FIG. As a result, the guide portion 4 is slightly displaced in the direction of arrow E. However, before this displacement, there are gaps between the inner circumferential surface of the through hole 20 and the outer circumferential surface of the sleeve 9, and between the inner circumferential surface of the through hole 19 and the outer circumferential surface of the sleeve 7, as shown in FIGS. 1 and 2, respectively. Right side of sleeve 9, Figures 1 and 2
Since there is a gap α on the left side of the sleeve 7 in the figure, the caliper 15 will not be dragged in the direction of arrow E in FIG. 1 until the displacement amount of the guide portion 4 reaches 2α. No braking force is applied to the caliper 15 in the direction of arrow E shown in FIG. Therefore, in this case, the guide shafts 13 and 14 only need to support the weight of the caliper 15 and guide its sliding movement, so great strength is not required.
This means that a relatively thin material with lower strength than the conventional material may be used. In addition, even if the guide shafts 13 and 14 support the weight of the caliper 15 and guide its movement as described above, the sleeves 7 and 9 do not fit into the sleeve fitting hole.
1 and 12 and tightened to the carrier 1 by the bolts 8 and 10, the bolts 8 and 10 will not loosen due to weakening of the mounting strength.

In addition, if the guide part 4 is displaced by 2α or more,
Guide shafts 13, 14 and these guide shafts 13, 1
A braking force is applied to the caliper 15 via the carrier 1, but if the pitches A and B are set appropriately, this will not happen. Even if the amount of deformation of the caliper guide part is outside the range equivalent to twice the gap α, the force that further deforms the carrier 1 in addition to the deformation within the twice the gap α is applied to the guide shaft. and caliper 15, so when the brake is applied, the guide shaft and caliper 15
The brake torque applied to this type of brake is significantly reduced compared to conventional pin slide type disc brakes.
Further, since the sleeves 7 and 9 are fitted into the sleeve fitting holes 11 and 12 as described above, the bolts 8 and
No unreasonable force is applied to the attachment portions of the guide shafts 13 and 14 to the carrier 1, so that the attachment portions of the guide shafts 13 and 14 to the carrier 1 do not come loose. Then, when the oil pressure applied to the piston 17a is lowered, the caliper 15 moves in the direction of arrow C in FIG. 1 and returns to its original position.

In the above embodiment, the guide shaft is composed of a bolt and a sleeve, but the guide shaft is not limited to this, and may be composed of only a bolt.

As explained above, according to this invention, the cross sections of the pair of guide shafts provided in the carrier and the pair of through holes provided in the caliper are circular, and the diameter of the through holes is made larger than the diameter of the guide shaft. the diameter is large, the pitch between the pair of guide shafts is set smaller than the pitch between the pair of through holes, and both guide shafts are brought into contact with the inner surface of the through hole on the sides close to each other, and the pitch between the pair of guide shafts is set smaller than the pitch between the pair of through holes. Since a gap is formed between the guide shaft and the inner surface on the opposite side to the guide shaft abutting inner surface, which is a space in which the guide shaft can move, Braking torque is not applied to the guide shaft and caliper within a range equivalent to twice the gap formed between the inner surface of the through hole opposite to the guide shaft abutting inner surface and the guide shaft, and (b) this range Even outside, in addition to deforming the carrier within an amount equivalent to twice the gap, the force that deforms the carrier is only applied to the guide shaft and caliper, so the brake torque applied to the guide shaft and caliper is the same as in the conventional case. C. Since the guide shaft is in contact with the inner surface of the through hole, vibration of the caliper can be prevented without the need for special elastic bushings, etc. (d) Since the guide shaft has sufficient mounting strength to the carrier and the guide shaft has sufficient strength, and the sliding movement of the caliper against the carrier is not hindered, braking performance is improved and durability is greatly increased. To increase.

[Brief explanation of drawings]

FIG. 1 is a partially cutaway plan view showing an embodiment of this invention, and FIG. 2 is a partially cutaway sectional view taken in the direction of the arrows in FIG. 1...Carrier, 2...Disk, 7,9...
Sleeve, 8, 10... Bolt, 11, 12...
Sleeve fitting hole, 13, 14... Guide shaft, 15
... Caliper, 17, 18... Leg, 17a...
Piston, 19, 20...through hole.

Claims (1)

[Scope of Claim for Utility Model Registration] 1. A carrier that is provided in a non-rotating part of the vehicle on one side of the disc and receives brake torque,
provided spaced apart in the rotational direction of the disk,
A pair of guide shafts extending in the axial direction of the disk are fixed, and a pair of through holes are provided in a caliper in which a piston is housed in one of a pair of leg portions that straddle the outer periphery of the disk and are opposed to both surfaces of the disk, In a disc brake in which the guide shaft is slidably fitted into the through hole and the caliper is slidably supported by the carrier in the axial direction of the disk, the cross section of the guide shaft and the through hole is circular. At the same time, the diameter of the through-hole is made larger than the diameter of the guide shaft, the pitch between the pair of guide shafts is set smaller than the pitch between the pair of through-holes, and both guide shafts are connected to the through-hole on the sides adjacent to each other. A disk that is brought into contact with an inner surface of a hole, and a gap is formed between the guide shaft and the inner surface of the through hole opposite to the guide shaft abutting inner surface, which is a space in which the guide shaft can move. brake. 2. The guide shaft comprises a bolt and a sleeve fitted to the bolt, and the sleeve is fitted into a sleeve fitting hole provided on an end face of the carrier. Disc brake described in item 1.