JPH0332833Y2 - - Google Patents

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention mainly relates to the improvement of disc brakes installed in automobiles.

[Conventional technology]

This type of disc brake is prone to a so-called squealing phenomenon in which an abnormal noise is generated due to contact between the disc rotor and the pads during the initial stage of braking or during light braking. This squealing phenomenon occurs because the entire surface of the pad is not pressed against the disc rotor at the same time during braking due to parts processing errors or parts installation errors, but the pad surface area on the leading side is pressed first. is known to occur. Furthermore, it has been confirmed from various experimental results that this squealing phenomenon can be prevented by pressing the pad surface area on the trailing side against the disc rotor first.

Therefore, in view of the above points, conventional disc brakes are equipped with a spring that generates a repulsive force in the direction of separating the leading side of the pad from the disc rotor, as disclosed in Japanese Patent Publication No. 50-28584. Some brake pads are provided with a pad surface area on the trailing side that is pressed against the disc rotor first during braking.

[The problem that the idea attempts to solve]

However, with the conventional structure described above, when a sudden pumping brake operation is performed, the pads are suddenly returned to the direction away from the disc rotor due to the repulsive force of the spring, causing vibration, which may generate other brake noise. It has some problems.

[Means to solve the problem]

In order to solve the above problems, the disc brake of the present invention includes a pair of left and right pads arranged on both sides of the disc rotor, a caliper having a piston that presses the pads against the disc rotor, and a caliper having a pair of left and right pads arranged on both sides of the disc rotor. The present invention is characterized in that it includes a damping force generating means interposed between the two pads for delaying pressure braking on the leading side compared to the trailing side when both pads approach the disc rotor during braking.

[Effect]

According to the above configuration, during braking, the pads on both sides of the disc rotor are pressed against the disc rotor by the pistons of the caliper, thereby performing braking. At this time, the pressure braking caused by the approach of both pads to the disc rotor is delayed on the leading side compared to the trailing side due to the action of the damping force generating means. Therefore, occurrence of the squealing phenomenon can be prevented. In addition, even if a sudden pumping brake operation is performed during the above-mentioned braking, the pads pressing the disc rotor will not suddenly return to the position separated from the disc rotor, so the pads will not vibrate. There is no possibility of another brake noise occurring.

[Embodiment 1] A first embodiment of the present invention will be described in detail below with reference to FIGS. 1 to 3.

In FIG. 1, a pair of left and right pads 2a are located on both sides of the rotor periphery on the front side of the vehicle body from the center of the disc rotor 1, which rotates together with wheels (not shown).
2b are arranged to face each other.

A vehicle body member (knuckle) 3 located on one side of the disc rotor 1 has a pair of upper and lower arm portions 4.
A support member 4 having a support member 4a and a support member 4a (the upper arm portion 4a is not shown) is fixed by a bolt 5 at each fixing portion 4b. The pair of pads 2a and 2b are connected to a pair of upper and lower arm portions 4a and 4b by integrally connected seat plates 6a and 6b, respectively.
4a, and is provided so as to be slidable toward or away from both the left and right sides of the disk rotor 1.

A pair of upper and lower arm portions 4a, 4 of the support member 4
slide holes 4c, 4c are formed in each a, while the caliper 7 arranged to straddle the disc rotor 1 has flanges 7a, 7a at its upper and lower ends.
Slide pins 8, 8 provided on the upper flange 7a (the upper flange 7a is omitted) are inserted into the slide holes 4c, 4c, respectively, so that the pads can be slid laterally in the same way as the pads 2a, 2b. It is configured. This caliper 7 is provided with a piston 9 which is connected to the seat plate 6a of the left pad 2a from the outside on the side where the fixed part 4b of the support member 4 is located, with the disc rotor 1 as a boundary, and the fixed part 4
A pressing portion 7b is formed on the side opposite to b, and is connected to the seat plate 6b of the right pad 2b from the outside. Then, by pushing the piston 9 and the pressing part 7b in opposite directions, the above-mentioned 1.
The pair of pads 2a and 2b are configured to approach or move away from the disk rotor 1, respectively.

Seat plates 6a, 6b of the above pair of pads 2a, 2b
In between, on the upper side, that is, on the leading side of the disc rotor 1, both pads 2 are placed at the time of braking.
A damper 10 is interposed as a damping force generating means for delaying the pressure braking caused by the approaches of the disc rotors 1 and 2b compared to the trailing side.

As shown in FIG. 2, the damper 10 includes a cylinder 11, a first piston 12 fitted inside the cylinder 11 so as to be movable forward and backward, and other components. A second piston 13 is further fitted inside the first piston 12, and a piston compression spring 14 compressed between the closed end 12a of the first piston 12 and the second piston 13 causes the second The piston 13 is urged toward the cylindrical opening end of the first piston 12. A male threaded ring body 15 is screwed onto the inner periphery of the first piston 12 on the open end side, which is fitted into the open end of the cylinder 11.
An annular valve seat 16 is fastened and fixed to a stepped portion on the inner circumference of the valve. A valve body 17 having an orifice 17a penetrated through the center thereof is disposed inside the male threaded ring body 15, and a valve compression spring is received by an inward flange 15a formed at one end of the male threaded ring body 15. 18, the valve seat 16 is biased toward the valve seat 16.

An oil chamber 19 surrounded by the second piston 13 and the valve body 17 in the inner space of the first piston 12, and an oil chamber formed in the inner space of the cylinder 11 and communicating with the oil chamber 19 via the orifice 17a. 20 is filled with oil.

On the other hand, the cylinder 11 and the first piston 12
As shown in FIGS. 2 and 3, support legs 21, 21 are provided protrudingly from the outer circumferential wall of the holder, respectively. Clips 22, 22 are attached to the tips of the support legs 21, 21.
is provided, and the seat plate 6 of each pad 2a, 2b mentioned above is provided.
The damper 10 is mounted between the pads 2a and 2b by clamping the pads a and 6b as shown by the imaginary lines in FIG. Note that the first piston 12
A through hole 12b is formed in the closed end 12a of the cylinder for maintaining the in-cylinder spring mounting space at outside pressure.

In the above configuration, the operation of the disc brake will be explained as follows.

1 and 2 show the positional relationship between the pair of pads 2a, 2b and the damper 10 before braking, that is, in a state where they are separated from the disc rotor 1. When braking is started from this state, the piston 9 and the pressing part 7b of the caliper 7 simultaneously move toward each other, thereby causing the pair of pads 2
a and 2b are pressed against both left and right sides of the disk rotor 1, respectively.

At this time, since a damper 10 is interposed between the leading sides of both pads 2a and 2b, the disk rotor is first
pressed against. That is, when the pads 2a, 2b are brought closer to each other, the cylinder 11 and the first piston 12 of the damper 10, which are attached to the respective seat plates 6a, 6b, are relatively disposed inside the cylinder 11. 12 to enter. The second piston 13 is compressed by the compression spring 14 due to the hydraulic pressure at this time.
The oil chamber 19 in the first piston 12 moves backward against the
is enlarged, and oil flows from the oil chamber 20 in the cylinder 11 toward the oil chamber 19 in the first piston 12. At this time, the oil flows through the orifice 17 of the valve body 17.
Since the pads 2a and 2b pass through a, the flow resistance is large, and the approach of the pads 2a and 2b to the disc rotor 1 on the leading side is delayed accordingly.

On the other hand, when the piston 9 and the pressing part 7b of the caliper 7 are simultaneously moved in opposite directions to release the brake, the cylinder 11 and the first piston 12 of the damper 10 move backward from each other. At this time, the first
From the oil chamber 19 of the piston 2 to the oil chamber 2 of the cylinder 11
Oil flows into the cylinder 11, but not only the orifice 17a of the valve body 17, but also the valve body 17 and the valve that are pushed against the compression spring 18 by the oil pressure at this time. The gap between the seats 16 also serves as an inflow path. Therefore, there is no delay in the movement of the pads 2a, 2b as seen at the start of braking, and the leading and trailing sides of the pads 2a, 2b are separated from the disc rotor 1 almost simultaneously.

The movement of the pads 2a and 2b when the brake is released is not sudden, so even if the braking operation is due to a sudden pumping brake operation, the pads 2a and 2b will vibrate and cause brake noise. No such situation will occur. Furthermore, since this disc brake is configured to include the damper 10 as described above, even if vibration occurs in the pads 2a, 2b for some reason, this vibration can be efficiently absorbed. This prevents the occurrence of noise due to vibration or malfunction.

[Embodiment 2] In this embodiment, the damper interposed between the leading sides of the pads 2a and 2b is configured as shown in FIG. 4, and the other configuration shown in FIG. Since this is the same as the embodiment, the explanation thereof will be omitted.

The damper 10' shown in FIG. 4 is composed of a cylinder 24, a first piston 25 fitted into the cylinder so as to be able to move forward and backward, and other components.

The first piston 25 has a closed portion 25a at one end, and an opening at the other end has a rod insertion hole 26a in the center.
It is closed by a lid body 26 having a. on the other hand,
The cylinder 24 has a closing portion 24a at one end, and a second piston 27 located inside the cylinder 24 and protruding from the center of the closing portion 24a has a rod portion 27a.
passes through the rod insertion hole 26a of the lid 26,
The head portion 27b is in sliding contact within the first piston 25. Inside the first piston 25, there are two oil chambers 2 partitioned by the head portion 27b.
8 and 29 are formed, and each oil chamber 28 and 29 is filled with oil.

The head portion 27b of the second piston 27 includes:
An orifice 30 and a valve mechanism 31 are formed, whereby both the oil chambers 28 and 29 communicate with each other. The valve mechanism 31 is configured by disposing a floating valve 33 on the oil chamber 28 side of an oil passage 32 formed through the head portion 27b, and the floating valve 33 is freely movable by a cap 34 having an oil passage 34a. is maintained.

FIG. 4 shows the relative positional relationship between the cylinder 24 and the first piston 25 before braking, with the pair of pads 2a and 2b separated from the disc rotor 1. When braking is started from this state, the cylinder 24 and the first piston 25 move toward each other. At this time, oil flows from the oil chamber 28 through the orifice 30 to the oil chamber 29 side,
The valve mechanism 31 moves the idle valve 33 to the oil passage 3 by hydraulic pressure.
2 is closed, the area of the pads 2a and 2b on the leading side is delayed in movement.

On the other hand, in the case of brake release in which oil flows from the oil chamber 29 to the oil chamber 28, the idle valve 33 opens the oil passage 32 due to the hydraulic pressure at this time, so the resistance when the oil flows in is small. Therefore, the separation movement between the cylinder 24 and the first piston 25 is performed quickly, and there is no delay in the movement of the pads 2a, 2b on the leading side.

Incidentally, the dampers 10 and 10' shown in the first and second embodiments are merely illustrative of two structures, and it goes without saying that there is no particular limitation on the specific structure of the dampers. be.

[Effect of idea]

As described above, the disc brake of the present invention includes a pair of left and right pads arranged on both sides of a disc rotor, a caliper having a piston that presses the pads against the disc rotor, and a caliper interposed between the pair of pads, This structure includes damping force generating means for delaying pressure braking on the leading side compared to the trailing side when both pads approach the disc rotor during braking.

Therefore, even if braking is performed by sudden pumping brake operation, the squealing phenomenon can be prevented without causing a situation where the pads vibrate and generate other brake noise. Furthermore, even if vibration occurs in the pad for some reason, this vibration can be efficiently absorbed, making it highly practical.

[Brief explanation of the drawing]

1 to 3 show an embodiment of the present invention. FIG. 1 is a partially cutaway front view showing an embodiment of the present invention. FIG. 2 is a longitudinal sectional view of the damper shown in FIG. 1. FIG. 3 is a side view of the damper. FIG. 4 is a longitudinal sectional view of a damper showing another embodiment of the present invention. 1 is the disc rotor, 2a and 2b are the pads, 4
is a support member, 4a is an arm portion, 4b is a fixed portion, 6
a, 6b are seat plates, 7 is a caliper, 7b is a pressing part,
8 is the slide pin, 9 is the piston, 10, 10'
is a damper (damping force generating means).

Claims (1)

[Scope of utility model registration request] A pair of left and right pads arranged on both sides of the disc rotor, a caliper having a piston that presses the pads against the disc rotor, and a caliper interposed between the pair of pads to allow the pads to approach the disc rotor during braking. and a damping force generating means for delaying pressure braking on the leading side compared to the trailing side.