JPH0354983Y2 - - Google Patents

Description

[Detailed explanation of the invention] (Industrial field of application) This invention reduces the frictional force of the sliding part during braking.
This invention particularly relates to a wet-type, dual-type brake system that has a boosting action, a so-called servo action, which is fed back as a (+) force to a brake actuator.

(Prior art) In order to press the stator, which is fixed to the brake housing by the rotor spline-fitted to the rotating shaft, against the brake housing by rotating the pressure plate, In a brake device configured such that a ball in a recess is moved to a shallow part of the recess as a result of the above-mentioned rotational operation, the sliding force acting on the pressure plate from the rotor during braking is applied to the pressure plate. A brake device with a servo action configured to assist the above-mentioned rotational operation was first developed in 1982.
No. 80542, Publication No. 15004 of 1983, and Japanese Patent Application Publication No. 1983-
Known as No. 24841.

(Problems to be Solved by the Invention) In the above-mentioned known device, the rotation operation of the pressure plate is performed by rotating each link connected to both pressure plates with a brake rod in the dual type. In the single type, the structure is such that an arm connected to a pressure plate is rotated by a brake rod.

Since such link mechanisms, arms, brake rods, etc. are provided outside the periphery of the pressure plate, the brake equipment unit tends to be large, especially in the case of a single type.
The size is much larger than the braking force that can be obtained.

In the dual type, brake torque acts on the link mechanism and its connecting pins, etc., and because of the play in several places in the connecting parts such as the link mechanism and pins, which are not stationary members, the brake torque is applied at the moment the brake operation starts. There is a problem in that the shocking sliding force becomes a very large impact force that acts on these link mechanisms, connecting pins, etc. Due to the behavior of this actuator, impact pressure is applied to the brake rod via the link mechanism. , so-called shockwaves are occurring.

(Means for Solving the Problems) This invention is proposed in order to solve the above-mentioned conventional problems that the brake device tends to be large and the impact force when applying the brake is large. Its structure consists of a pair of rotors 1 that are fitted onto a rotating shaft so that they can slide in the axial direction and transmit torque and rotate as a unit, and a stator 2 that is disposed between these rotors 1 and 1. The sliding parts 3, 3 are disposed on the rotating shaft 4 facing each other in the brake housing, and a recessed part 8 with a slope facing each other on the opposing surfaces of both the pressure plates 6, 6 is arranged in the rotating direction. A ball 9 is disposed in opposing recesses 8, 8 spaced apart from each other, and between working bosses 11, 11 provided on the peripheral edge of each pressure plate 6, A cylinder mechanism C is provided to push the two working bosses 11, 11, and the pushing moves the two pressure plates 6, 6 in opposite directions so that the ball 9 moves into the shallow recess 8, 8. In this brake device, the cylinder mechanism C moves toward the stationary member 14, thereby widening the gap between the two pressure plates 6, 6 and pressing the sliding parts 3, 3 against the pressure receiving surface of the brake housing. The installed cylinder 12 and the piston anchor flange 1 which abuts the end of the cylinder 12 in the maximum retracted position
7 and a pair of pistons 15, 15 fitted in correspondence with both action boss parts 11, 11, respectively, and the stator 2 is locked to the brake input side member B. It is a brake device that

(Function) Sends hydraulic pressure to the cylinder 12 and both pistons 15,
15, both pressure plates 6,
6 rotate in opposite directions to each other, and the ball 9 moves into the recess 8,
8, move to the shallow side of both pressure plates 6,
6 widens, the sliding parts 3, 3 are pressed against the pressure receiving surface of the brake housing, and a braking force acts on the rotating shaft 4.

The stator 2 in pressure contact with the rotor 1 transmits the frictional force received from the rotor 1 to the brake input side member B, so the sliding portion 3 on the side where the direction in which the piston 15 is projected by hydraulic pressure is the same as the rotational direction of the rotor 1 Then, the above-mentioned frictional force from the brake input side member B is added to generate an even larger braking force, and a servo action is obtained.

In the sliding portion 3 on the side where the protrusion direction of the piston 15 is opposite to the rotational direction of the rotor 1, the brake input side member B to which the frictional force is transmitted causes the piston 15 to be retracted, but the piston anchor flange 17 Since the cylinder 12 contacts the end of the cylinder 12 and receives the above-mentioned frictional force, this frictional force does not weaken the braking force.

Furthermore, the impact brake torque that acts on the stator 2 and the pressure plates 6, 6 from the sliding parts 3, 3 at the moment when the brake operation starts is caused by the piston 15.
And, since it is transmitted to the stationary member 14 through the cylinder 12 fitted with this without any play, the impact of the brake torque becomes much larger due to the play, as in conventional brake devices, and the impact on the actuator is reduced. There is no need to worry about transmitting behavior to the petal system,
Moreover, since this impact is buffered by the brake fluid in the cylinder 12, the brake input side member B
There is no longer any fear that excessive impact force will be applied to the

(Example) Next, an example of this invention will be described.

Figure 1 shows a partially cutaway front view, and Figure 2 shows the X in Figure 1.
-O-X arrow cross section is shown in Fig. 3, Y-Z- of Fig. 1
In the first embodiment shown in the Y cross-section, a pair of sliding parts 3, 3 consisting of a plurality of rotors 1 and stators 2 are provided facing each other in a brake housing (not shown). The rotor 1 is, for example, spline-fitted to the rotating shaft 4 and rotates together, and the stator 2 is connected to the rotor 1,
The notches 5a provided in the extending portions 5 on the peripheral edges of the annular bodies are arranged alternately between the annular bodies and the notches 5a provided in the extending portions 5 of the annular bodies are latched to the pressure plate 6, which is one of the brake input side members B (pressure plate (locked to pin 7 attached to 6).

A pair of annular pressure plates 6, 6 are disposed between the pair of sliding parts 3, 3, and rotate around the rotating shaft 4 mutually along a guide (not shown) provided in the brake housing. Pressure plates 6, 6 are formed so as to be able to rotate by a predetermined angle in opposite directions.

Inside the pressure plates 6, 6, recesses 8, 8 having opposing slopes are provided at intervals in the circumferential direction.
is fitted, and the spacing between both pressure plates 6, 6 is maintained by a spring 10.

Working boss parts 11, 11, which are formed by extending a part of the peripheral edge of each pressure plate 6, 6, are formed to face each other in the rotational direction, and both working boss parts 1
1 and 11, and a cylinder 12 of the cylinder mechanism C is fixed to a stationary member 14 such as a brake housing by a mounting seat 13.

A pair of pistons 15 fitted into the cylinder 12,
15 to the working boss part 1 via a short rod 16.
1, and a piston anchor flange 17 is provided at the tip of the piston 15, and this piston anchor flange 17 comes into contact with the end of the cylinder 12, thereby preventing the piston 12 from retracting after this point. .

Now, assuming that the rotating direction of the rotating shaft 4 is in the direction of the arrow A, when brake fluid is fed into the back chamber 18 of the cylinder C and the pistons 15, 15 are moved to project, the action boss portions 11, 11 move away from each other. The pressure plates 6, 6 rotate in the direction, the ball 9 moves in the direction where the slope of the recess 8 becomes shallower, the distance between the pressure plates 6, 6 is widened, and the rotor 1 and stator 2 are Braking force is applied to the rotor 1 and rotating shaft 4 by the stator 2 and the pressure plate 6, which press against each other and press the sliding parts 3, 3 against the pressure receiving surface of the brake housing, and are prevented from rotating. act.

During this braking action, the stator 2 and the pressure plates 6, 6 both receive torque due to frictional force in the direction of the arrow. On the right side of Fig. 3, the torque due to the frictional force is added to the pushing force of the piston 15 due to the brake fluid, so a much larger braking force is generated on the sliding part 3 on this side (left side in Fig. 2). Positive servo action can be obtained.

On the left side of FIGS. 1 and 3, where the protruding direction of the piston 15 is opposite to the rotational direction of the rotor 1, the torque due to the frictional force causes the piston 15 to retract, and the piston anchor flange 17 is attached to the cylinder 12.
The piston 15 and
The pressure plate 6 and the stator 2 do not rotate in the direction of the arrow A, and the torque is received by the abutment portion, so that the pushing force of the piston 15 is not weakened, and the negative servo action is prevented. , does not occur on the sliding portion 3 on this side (the right side in FIG. 2).

Then, the piston 15,
The braking force due to the pushing action of 15 was doubled.

Brake input side member B where stator 2 is locked
As another example, one using the piston anchor flange 17 of the piston 15 will be described.

Figure 4 shows a partially cutaway front view, and Figure 5 shows the X in Figure 4.
-O-X arrow cross section is shown in Fig. 6, Y-Z- of Fig. 4
In the second embodiment shown in the Y cross-section, the stator 2
The notch 5a of the extending portion 5 is shown locked to the piston anchor flange 17.

In this second embodiment, the frictional force acting on the stator 2 during braking is transmitted directly from the piston anchor flange 17 to the cylinder 12.

In any of the above embodiments, the pistons 15, 15 of the cylinder 12 fixed to the stationary member 14 are
This is a structure in which a braking operation is performed by rotating the pressure plates 6, 6 by a protruding action by the brake fluid.

Therefore, the impactful brake torque that acts on the stator 2 and the pressure plates 6, 6 from the sliding parts 3, 3 at the moment when the brake operation starts is applied to the piston 15 and the cylinder 12 in which it is fitted.
is transmitted to the stationary member 14 through
2. Excessive impact force does not act on the brake input side member B such as the pressure plate 6, and there is no backlash.

Even when the rotating direction of the rotating shaft 4 is opposite to the direction of the arrow A in the illustrated example, the same servo action as described above can be obtained, and the vehicle to which this brake device is applied can move forward. A large braking force can be obtained in both cases.

(Effects of the invention) As mentioned above, the brake device according to this invention has the following features:
A cylinder 12 and a piston 1 constitute a cylinder mechanism C that pushes both pressure plates 6, 6.
5, 15, the cylinder 12 is the stationary member 1
4, and the pistons 15, 15 are provided with a piston anchor flange 17 that abuts the end of the cylinder 12 at the maximum retracted position.
In the sliding portion 3 on the side where the protruding direction of the rotor 1 is the same as the rotating direction of the rotor 1, the brake input side member B is subjected to a servo action due to the frictional force that the stator 2 and the pressure plate 6 receive from the rotor 1. , a large braking force is obtained, and when the piston 15 is retracted by the frictional force in the sliding portion 3 on the opposite side, the piston anchor flange 17 is attached to the cylinder 12.
As a result, the frictional force is received by the cylinder 12, and the negative servo force is not transmitted to the brake input side member B, and a large braking force is generated overall due to the positive servo force.

The impact brake torque that acts on the stator 2 and the pressure plates 6, 6 from the sliding parts 3, 3 at the moment when the braking action starts is caused by the piston 15 and the
Since the impact is transmitted to the stationary member 14 through the cylinder 12 fitted with the cylinder 12 without any play, the impact is magnified due to the play in various parts, such as in conventional brake devices using brake rods and link mechanisms. This fear has been eliminated by this invention, and wear and tear on the brake-side input member B has been reduced, and there has been no knock-back on the link mechanism, brake rod, brake pedal, etc. due to the above-mentioned impact.

[Brief explanation of the drawing]

The figures show an embodiment of this invention, and FIGS. 1 and 4 are partially cutaway front views of the brake device in each embodiment, and FIGS. 2 and 5 are respectively shown in FIGS.
X-O-X cross-sectional view in the figure, Figure 3, Figure 6
The figures are Y-Z-Y arrow sectional views in FIGS. 1 and 4, respectively. 1... Rotor, 2... Stator, 3... Sliding part, 4... Rotating shaft, 6... Pressure plate,
8... Recessed part, 9... Ball, 11... Working boss part, 12... Cylinder, 15... Piston, 17
... Piston anchor flange, B ... Brake input side member, C ... Cylinder mechanism.

Claims (1)

[Claims for Utility Model Registration] (1) Consisting of a plurality of rotors that are fitted onto a rotating shaft so that they can slide in the axial direction and transmit torque and rotate as one, and a stator that is disposed between these rotors. A pair of sliding parts are disposed on the rotating shaft facing each other in the brake housing, and recessed parts with opposing slopes are provided at intervals in the rotational direction on the opposing surfaces of both pressure plates. A cylinder mechanism is provided between both of the action bosses provided at the peripheral edge of the pressure plate, and a cylinder mechanism for pushing the action bosses is provided between the two action bosses provided on the peripheral edge of the pressure plate. As a result, both pressure plates are rotated in opposite directions, and the ball moves to the shallower direction of the recess, thereby widening the gap between both pressure plates and bringing the sliding part closer to the pressure-receiving surface of the brake housing. In the brake device, the cylinder mechanism has a cylinder attached to a stationary member, and a piston anchor flange that abuts the end of the cylinder at the maximum retracted position, and is fitted in correspondence with both action boss parts. 1. A brake device comprising a pair of pistons, the stator being locked to a brake input side member. (2) The brake device according to claim 1, wherein the brake input side member to which the stator is locked is a pressure plate. (3) The brake device according to claim 1, wherein the brake input side member to which the stator is locked is a piston.