JPH0729220B2 - Brake device for press machine - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a brake device for a press machine. In particular, it is a brake device that can significantly reduce the brake operation time and the brake release operation time.

[0002]

2. Description of the Related Art FIG. 3 shows a general structure of a power press machine. In the figure, 2 is a crankshaft, and its eccentric portion 2e
A slide 4 is connected to the via a connecting rod 3. Rotational power is applied to the crankshaft 2 from the drive shaft 1 via the gear train 5. Also, belt 8
Flywheel 6 driven to rotate by a motor 7 via
Are connected and disconnected from the drive shaft 1 by the clutch device 20.
On the other hand, the drive shaft 1 is braked by the brake device 50.

Therefore, when the brake device 50 is set to the brake release (OFF) operation and the clutch device 20 is engaged (ON), the rotational energy accumulated in the flywheel 6 is transmitted to the drive shaft 1 and the gear train 5 is operated. The slide 4 can be moved up and down via the crankshaft 2 and the connecting rod 3. To stop the slide 4 at a desired stop position such as top dead center, the clutch device 20 is disengaged (OFF) and the brake device 50 is operated.
It is well known that the brake should be operated (ON).

The clutch device 20 includes a solenoid 2
It is turned on by exciting 9S to open the solenoid valve 29 and supplying air of a predetermined pressure P to the air supply port 32B through the air supply pipe 28, and turned off when the solenoid 29S is de-excited and the air pressure is released. On the other hand, the brake device 50 is normally turned on by the urging force of the spring, which excites the solenoid 79S to open the solenoid valve 79, and through the air supply pipe 78 to the predetermined pressure P at 72B.
It is turned off by supplying the above air. Therefore, the solenoid 29S and the solenoid 79S are generally configured to be excited simultaneously.

Although the so-called separate type is shown in FIG. 3, the essence of the so-called combination type in which the clutch device 20 and the brake device 50 are integrally incorporated does not change.

By the way, the brake device 50, for example, in the case of a separate type, has a structure as shown in FIG.
In the figure, the drive shaft 1 is rotatably supported via a bearing 11 mounted on a casing 12 fastened to a frame 10 by bolts, and a brake hub 52 is movable on the drive shaft 1 within a certain range in the axial direction. Is attached to. here,
The brake device 50 includes a brake section 51, a brake actuating means 61, and a brake releasing means 71. The brake portion 51 is formed of the brake hub 52, the friction plate 53, the pressing member 54, and the pressure receiving member 58. Pressing member 5
If the friction plate 53 is sandwiched between the pressure receiving member 58 and the pressure receiving member 58 by moving 4 in the right direction in the figure, the pressure receiving member 58 is fixed to the bolt 72.
Since it is integrated with the cylinder 72 and the frame 10 at A, the brake can be turned on.

The spring 62 performs this brake ON operation.
The brake actuating means 61 comprises a spring support 63 and a spring support 63.
The spring 62 is fitted in the bottomed receiving groove 56 of the pressing member 54, while the spring receiver 63 is integrally attached to the pressure receiving member 58. That is, the pressing member 54 can always be biased to the right in the figure by the biasing force of the spring 62.

Next, the brake releasing means 71 resists the urging force of the spring 62 of the brake operating means 61 and presses the pressing member 54.
Is a means for moving to the left in FIG. 4 to perform an OFF operation. That is, the brake releasing means 71 is the bolt 72A.
Cylinder 72 (pressure receiving member 5) fixed to frame 10 by
8 is also fixed integrally. ), A piston 74 that cooperates with the cylinder 72 to form a cylinder chamber 77, and an air supply means including the air supply pipe 78 and a solenoid valve 79. The piston 74 and the pressing member 54 are integrally connected by a connecting member 76 and a push pin 73 fitted in the through hole 73A. The cylinder chamber 77 is sealed by a seal member 75.

The connecting member 76 is screwed into the flanged nut 55 fixed to the pressing member 54, and the stroke length of the piston 74 is adjusted by adjusting the position of the connecting member 76 in the left-right direction in FIG. Can be adjusted, that is, the stroke of the brake operation can be adjusted.

Therefore, the air supply port 7 is provided in the cylinder chamber 77.
If the air of the predetermined pressure P is sent from 2B, the pressurized cross section 74A
Since the (pressurizing cross-sectional area A1) is pressed, the pressing member 54 can be moved to the left in the drawing to turn off the brake against the urging force of the spring 62, that is, the friction plate 53 can press the pressing member 54 and the pressure receiving member 5.
8 and be released. That is, the brake device 50 has a spring-tightened structure that becomes a fail-safe when the air pressure is lost, and is configured to comply with the power press machine structure standard.

That is, in order to speed up the start and stop of the press machine, not only the performance of the clutch device 20 but also the brake device 50 must respond quickly. That is, it is necessary to shorten the time required for stable rotation at the start of the press operation and to quickly stop the press operation when the press operation is stopped. However, in order to speed up the ON operation of the brake device 50, it is preferable that the air pressure P applied to the cylinder chamber 77 is low, but OF
From the viewpoint of speeding up the F operation, the air pressure P is preferably high. Thus, conventionally, the air pressure P supplied to the cylinder chamber 77 is generally determined to be as low as possible within a range in which the brake OFF state can be reliably maintained.

On the other hand, the pressure 2 is set so that the urging force of the spring 62 is constant and the air pressure P is high when the brake is OFF and low when the brake is ON.
A step switching method has been proposed (Japanese Patent Laid-Open No. 60-106700). On the other hand, a multiple spring switching method is also proposed in which the air pressure P is kept constant and two springs are switched (JP-A-60-1).
No. 02299).

[0013]

However, the multiple spring switching system has a complicated structure and is costly. Moreover, with the increasing automation, the packing density of devices in the crown is increasing, which is a disadvantage in terms of space.

On the other hand, in the pressure two-stage switching system, since two sets of air supply means are provided and a switching device is also required, the structure is complicated and the cost is high in this case as well. Indeed, the brake OF
At the time of F, high-speed air is used, so that the speed can be increased. But,
As described above, the low-pressure air cannot be below the value that can reliably hold the brake-off operation, and the exhaust characteristics in the low-pressure region are also poor, so it is impossible to increase the speed when the brake is turned on, and it is possible to further increase the speed. It is no longer applicable to the desired press.

[0015] Here, the object of the present invention is to achieve both the contradictory reduction of the stable rotation time at the start of press operation and the rapid braking at the stop of operation without switching the supply air pressure and the plurality of springs. It is to provide a brake device for a press machine capable of performing the above.

[0016]

SUMMARY OF THE INVENTION According to the present invention, a small recessed portion provided on the side opposite to the cylinder chamber side of a piston and a throttle channel for connecting the recessed portion and the cylinder chamber are provided, and the air pressure in the recessed portion is used. The resisting force is not generated during the brake releasing operation and is generated during the braking operation in the same direction as the biasing force of the spring to achieve the above object.

That is, the present invention is configured so that the brake is operated by the biasing force of the spring and the brake is released against the biasing force of the spring by supplying air pressure to the cylinder chamber consisting of the piston and the cylinder. In a brake device for a press machine, a recess is formed on the opposite side of the piston from the cylinder chamber, and the pressure receiving cross-sectional area of the recess is smaller than and opposite to the pressurizing cross-sectional area of the piston. And the inside of the recess are communicated with each other by a throttle channel.

[0018]

In the present invention, when the press operation is started, when air of a predetermined pressure is supplied to the cylinder chamber from the air supply port of the cylinder forming the brake releasing means, this air pressure and the pressurizing cross-sectional area of the piston are combined. A certain releasing force is generated, and the brake can be turned off against the biasing force of the spring. At this time, the throttle channel does not play a substantial role. That is, no resistance is generated. After the brake is turned off and the clutch is turned on and the drive shaft reaches a stable rotation speed, the air in the cylinder chamber flows through the throttle passage into the recess with a time delay, and the pressure in both the cylinder chamber and the recess is increased. Will be equal.

Then, the air pressure in the recess is in a direction opposite to the releasing force generated in the piston (in the same direction as the spring biasing force).
Generates resistance. That is, the release force generated in the piston by the air pressure in the cylinder chamber is reduced by subtracting the resistance force generated in the piston by the air pressure in the recess. That is, it is possible to rapidly start up to a stable rotation speed by high pressure, and then the release force generated in the piston due to the air pressure in the cylinder chamber can be set to the minimum value that can hold the brake OFF operation in a stable and reliable manner.

On the other hand, when the press is stopped, the air pressure in the cylinder chamber of the brake releasing means is maintained at its minimum value, so that the braking force due to the biasing force of the spring is quickly generated during exhaust. Moreover, since the air pressure in the recess passes through the throttle passage, it is significantly delayed to the depressurization speed in the cylinder chamber. That is, the air pressure in the recess gives the piston the resistance force in the same direction as the biasing force of the spring. Therefore, the braking operation can be performed rapidly.

[0021]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings. As shown in FIG. 1, this brake device has the same basic structure as the conventional example shown in FIG.
0 is provided so that both the brake release operation and the brake operation can be achieved at high speed without switching the supply air pressure or the spring.

The same or common parts relating to the brake part 51, the brake actuating means 61, and the brake releasing means 71 are designated by the same reference numerals as in the conventional example, and the description thereof will be simplified or omitted.

In FIG. 1, a cylinder chamber 77 is composed of a cylinder 72 and a piston 74 (a pressure section 7 on the right side in FIG. 1) slidably fitted in the cylinder 72 through a seal member 75.
4A). On the other hand, the concave portion 81 forming the quick actuating means 80 is provided on the left side of the piston 74 (on the side opposite to the pressurizing cross section 74A), and the periphery thereof is surrounded by the seal member 83. The pressure receiving cross section of the flat bottom portion of the recess 81 is 74B. In this case, the pressure section 7
When the pressure cross-sectional area of 4A is A1 and the pressure cross-sectional area of the pressure receiving cross-section 74B is A2, A2 <A1.

Further, the cylinder chamber 77 and the recess 81 are communicated with each other by a throttle channel 82. In this embodiment, the piston 7
4 is formed from a small hole having an orifice characteristic. The purpose of the throttle passage 82 is to increase the air pressure in the recess 81 to the pressure in the cylinder chamber 77 after the crankshaft 2 reaches a stable rotation speed when air pressure is applied to the cylinder chamber 77 from the air supply port 72B. When the pressure in the cylinder chamber 77 is released to the atmosphere, the time lag is made equal so that the air pressure in the recess 81 can be maintained until brake braking becomes reliable.

Next, the operation of this embodiment will be described with reference to FIG. In FIG. 2A, the friction plate 5
3 is clamped between the pressing member 54 and the pressure receiving member 58 by the urging force S of the spring 62 to perform a braking operation. At this stage, the piston 74 is pressed to the right inside the cylinder 72. The air pressure in the recess chamber 81 is the atmospheric pressure Po.
Is.

Here, when the air pressure Ph is supplied into the cylinder chamber 77 at the start of the press operation, as shown in (B), the pressure Ph is applied to the pressurizing cross section 74A (pressurizing cross sectional area A1) of the piston 74. Therefore, the release force Fh (= A1 ×
Ph) occurs. This releasing force Fh is the urging force S of the spring.
The piston 74, that is, the pressing member 54 is pushed back to the left side in the figure against the force. At this time, it may be considered that the throttle channel 82 is still substantially inoperative.

Thus, under rapid operation, the piston 74
Is a right side surface of the pressure receiving member 58 (cylinder 7 as shown in FIG. 2C).
When pressed against the left inner surface of 2, the recess 81 is sealed by the seal member 83. That is, the air in the cylinder chamber 77 flows into the recess 81 through the throttle channel 82. That is, both the air pressure in the cylinder chamber 77 and the air pressure in the recess 81 become the pressure Ph after the drive shaft 1 and the crank shaft 2 reach the stable rotation speed.

Then, due to the relationship between the air pressure Ph in the recess 81 and the pressure receiving cross section 74B (pressure receiving cross sectional area A2), a resistance force F2 in the same direction as the urging force S of the spring 62 is generated in the piston 74. In this case, a releasing force F1 is generated in the piston 74, which is determined by the air pressure P in the cylinder chamber 77 and the pressure cross-sectional area A1. Here, the substantial brake release force F is (F
1-F2). This releasing force F resists the urging force S and can stably maintain the brake releasing operation.

Next, when the press operation is stopped, as shown in (D), air is released to release the air pressure in the cylinder chamber 77 to the atmosphere. The pressure in the cylinder chamber 77 becomes the atmospheric pressure Po. Then, the release force F1 applied to the pressure section 74A
But the recess 81 is sealed and the throttle channel 82 is removed.
Since the flow inside is restricted, the air pressure inside the recess 81 remains as a residual pressure P substantially equal to the pressure Ph, and a resistance force F22 substantially equal to the resistance force F2 still exists. The resistance force F22 is in the same direction as the urging force S of the spring 62 as described above. Therefore, the brake operation time can be significantly shortened as compared with the case of only the urging force S.

However, according to this embodiment, the recess 81
And a throttle passage 82 that communicates the recess 81 and the cylinder chamber 77 is provided, and by applying a slightly higher air pressure Ph than in the conventional case, the resistance force F2 is not generated during the brake release operation. Since it is configured to be generated only when the brake is operated, both the stable rotation arrival time when the press operation starts and the braking time when the press stops can be significantly reduced.

Further, it is only necessary to apply one kind of air pressure Ph in the cylinder 72 and it is not necessary to switch between the two springs, and a recess 81 is simply provided inside the piston 74 and a through hole (82) is formed in the piston 74. Since the rapid actuating means 80 can be formed only by providing (), the structure is simple, stable operation is possible, and the cost is low. Moreover, there is no need to upsize the entire braking device.

In the above embodiment, the friction plate 53 is a single plate type and the clutch device 20 is a separate type. However, this can be implemented as it is as a multiple plate type or a combination type.

[0033]

As described above, according to the present invention, since a recess having a small pressure receiving cross-sectional area is provided on the opposite side of the cylinder chamber of the piston, and both of them are communicated with each other by the throttle passage, a slightly higher air flow rate is achieved. A resistance force in the same direction as the urging force of the spring can be generated only during the braking operation after the pressure is applied to achieve the rapid brake releasing operation. Therefore, the time required to reach stable rotation at the start of the press operation and the time required for reliable braking when the press is stopped can be greatly reduced.

[Brief description of drawings]

FIG. 1 is a side sectional view showing an embodiment of the present invention.

FIG. 2 is a diagram for similarly explaining the operation.

FIG. 3 is a diagram for explaining the configuration of a press machine.

FIG. 4 is a side sectional view showing a conventional brake device.

[Explanation of symbols]

 1 Drive shaft 2 Crankshaft 4 Slide 6 Flywheel 10 Frame 20 Clutch device 50 Braking device 51 Brake part 52 Brake hub 53 Friction plate 54 Pressing member 55 Collar nut 56 Receiving groove 58 Pressure receiving member 61 Brake operating means 62 Spring 63 Spring receiving 71 Brake Release Means 72 Cylinder 72B Air Supply Port 73 Push Pin 73A Through Hole 74 Piston 74A Pressurized Cross Section (Pressurized Cross Section A1) 74B Pressure Received Cross Section (Pressure Received Cross Section A2) 75 Sealing Member 76 Connecting Member 77 Cylinder Chamber 79 Solenoid 80 Rapid actuation means 81 Recessed portion 82 Restricted flow passage 83 Seal member

Claims (1)

[Claims] 1. A press machine configured to perform a brake operation by an urging force of a spring and to release a brake against the urging force of the spring by supplying air pressure to a cylinder chamber composed of a piston and a cylinder. In the brake device, the recess is formed on the opposite side of the piston from the cylinder chamber, and the pressure receiving cross-sectional area of the recess is formed to be smaller than and opposite to the pressurizing cross-sectional area of the piston. A brake device for a press machine, characterized in that and are communicated with each other through a throttle channel.