JPH0729221B2 - Clutch 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 clutch device for a press machine. In particular, the present invention relates to a clutch device that can significantly reduce both the stable rotation arrival time at the start of press operation and the braking time at the time of operation stop.

[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 clutch device 20 is structured as shown in FIG. 4 in the case of a separate type, for example.
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 clutch hub 22 is mounted so as to be movable within a certain range in the axial direction. .

Functionally, the clutch device 20 is roughly classified into a clutch portion 21 (clutch hub 22, friction plate 23, pressing member 36, pressure receiving member 6B) and clutch operating means 31 (cylinder 32, piston 34). , Cylinder chamber 3
7, the air supply pipe 28, the solenoid valve 29), and FIG.
The clutch release means 38 (the release spring 39 and the like fitted to the pin 39A) shown in FIG. The cylinder 32 and the pressure receiving member 6B are fixed to the flywheel 6 with bolts 32A. Further, 35 is a seal member.

Therefore, if air of a predetermined pressure P is sent from the air supply port 32B into the cylinder chamber 37 of the clutch actuating means 31, the pressurizing cross section 34A (pressurizing cross sectional area A1) is pressed to the left in the figure, so that friction occurs. Flywheel 6 (6B) with plate 22
It is pressed against and the clutch can be turned on. On the other hand, if the pressurized air is withdrawn from the cylinder chamber 37, the clutch release means 3
The biasing force S of the release spring 39 of No. 8 enables the OFF operation.

Here, in order to speed up the start and stop of the press machine, the clutch device 20 must respond quickly as well as the performance of the brake device 50. 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. On the other hand, if press work can be performed with stable rotation from the first punch, it is also effective to improve the quality of being free from the influence of bottom dead center variation due to SPM change. However, in order to speed up the ON operation of the clutch device 20, it is preferable that the air pressure P applied to the cylinder chamber 37 is high, but it cannot be unnecessarily high to ensure the specified torque. Moreover, from the viewpoint of speeding up the OFF operation, it is preferable that the air pressure P is as low as possible. Thus, conventionally, the air pressure P supplied to the cylinder chamber 37 is generally determined to be as low as possible within a range in which the clutch ON state can be reliably maintained and the specified torque can be guaranteed.

[0010]

However, under the present demand for higher speed press machines, the cylinder chamber 37 is a compromise because of the conflicting phenomena of shortening the clutch ON operation time and the clutch OFF operation time.
The conventional method of determining the internal air pressure cannot satisfy the demand at all.

On the other hand, the air pressure supplied into the cylinder chamber 37 is set to a high pressure for the clutch ON operation to shorten the time, and after the crankshaft 2 reaches the stable rotation, that is, in order to ensure the specified torque transmission. A so-called two-stage pneumatic pressure switching system in which the pressure is low is conceivable. However, in this method, two sets of the air supply means (28, 29, etc.) have to be provided and a switching device for them is also required, so that the structure is complicated and the cost is high. Moreover, while the automation has been increasingly automated to increase the device mounting density in the crown, it is disadvantageous in terms of space and practically difficult today.

An object of the present invention is to achieve a press machine capable of achieving both a reduction in the time required for stable rotation at the start of press operation and a rapid braking at the time of operation stop, which are contradictory when the supply air pressure is constant. To provide a clutch device of the.

[0013]

According to the present invention, a small sub-cylinder chamber including a sub-piston opposite to the piston is provided on the opposite side of the cylinder chamber, and both cylinder chambers are connected by a throttle channel, It achieves the purpose. That is, the present invention provides a clutch device of a press machine configured to supply pressurized air to a cylinder chamber formed between a cylinder and a piston to perform a clutch engaging operation, and has a smaller pressure cross-sectional area than the piston. A sub-cylinder chamber including a sub-piston having a pressure cross-sectional area and a sub-cylinder is provided, and the piston and the sub-piston are integrally connected so that the respective pressure cross-sections face each other,
Moreover, the cylinder chamber and the sub-cylinder chamber are communicated with each other through a throttle channel.

[0014]

In the present invention, when air having a predetermined pressure Ph is supplied to the cylinder chamber, the piston moves and the clutch can be turned on. In this case, the air pressure Ph is slightly higher than the air pressure in the case where there is no sub-cylinder necessary for transmitting the specified torque, so that the air pressure Ph can be turned on at high speed. Then, when the crankshaft reaches the stable rotation speed, the air in the cylinder chamber is flowing into the sub-cylinder chamber through the throttle passage, so that the pressure in the cylinder chamber and the pressure in the sub-cylinder become equal pressure Ph. There is. Then, the pressing force F1 determined by the pressure Ph and the pressurizing cross section A1 is generated in the piston, but the reverse pressing force F2 is determined in the sub-piston by the pressure Ph and the pressurizing cross section A2.
Here, since the piston and the sub piston are integrally connected, the substantial pressing force generated in the piston is F (= F1).
-F2). That is, the clutch can be turned on with the pressing force F required to transmit the specified torque. Therefore,
While the clutch ON operation is performed at high speed, the specified torque can be guaranteed after the stable rotation is reached.

On the other hand, when the clutch is off, the air pressure Ph in the cylinder chamber is released to the atmosphere. Then, the pressure in the cylinder chamber is reduced to atmospheric pressure Po, but the pressure in the sub-cylinder chamber remains as the residual pressure P due to the orifice effect of the throttle passage. Therefore, the pressing force F1 of the piston disappears, but the backward pressing force F2 of the sub-piston is in good health. Therefore, together with the biasing force S of the release spring, the piston is forcibly biased in the clutch OFF direction. Therefore, the clutch OFF operation can be performed at a much higher speed than the case where the clutch is released only by the biasing force S of the release spring.

[0016]

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, the present clutch device has the same basic configuration as that of the conventional example shown in FIG. 4, and is provided with a quick actuating means 40 for performing both the clutch ON operation and the clutch OFF operation.
Speeding up without switching air pressure, shortening the time required to reach stable rotation at the start of press operation, and braking device 5 at the time of operation stop
It is configured so that quick braking by 0 can be promoted. Of course, after reaching the stable rotation, the specified torque can be automatically guaranteed.

The same or common parts relating to the clutch portion 21, the clutch actuating means 31, and the clutch releasing means 38 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 37 includes a piston 34 axially slidably fitted through a cylinder 32 and a seal member 35 (an end surface on the right side in FIG.
It is formed between A). On the other hand, the quick operating means 40
The sub-cylinder chamber 47 that forms the sub-cylinder chamber 47 and the sub-cylinder 42 that is integral with the cylinder 32 and the sub-piston 44 (the left end surface in FIG.
It is formed between B). Then, the piston 34 and the sub-piston 44 are integrally connected by a connecting means composed of a bush 38 and a bolt 39 slidable in the through hole 33 of the cylinder 32. Pressure section 34A and pressure section 44
The direction is opposite to B.

Here, the pressure cross-sectional area of the pressure cross-section 34A is A
1, the pressure cross-sectional area of the pressure cross-section 44B is A2, A
1 >> A2. Further, the relationship between the pressurizing cross-sectional areas A1 and A2 is that the pressing force of the piston 34 required to transmit the specified torque in the conventional structure is F to the left in FIG. When the air pressure in the chamber 37 is P, F = P × A1 = Ph (A1-A
2) << Ph × A1 is selected to hold.

In order to establish such a relationship, the cylinder chamber 37 and the sub-cylinder chamber 47 are communicated with each other by the throttle passage 41. The throttle channel 41 in this embodiment is
A gap is formed between the inner diameter of the through hole 33 and the outer diameter of the bush 38, and this gap is supplied with air of pressure Ph into the cylinder chamber 37 to cause the clutch to operate and the crankshaft 2 to rotate stably. It is determined that the orifice action is exerted so that the internal pressures of both the chambers 37 and 47 of the cylinder chamber 37 and the sub-cylinder chamber 47 become the same pressure Ph when the pressure reaches the pressure. The pressure in both chambers 37 and 47 in the clutch-off state is the atmospheric pressure Po.

Next, the operation of this embodiment will be described with reference to FIG. At the start of the press operation, when the air pressure Ph is supplied into the cylinder chamber 37, the pressing force Fh determined by the product of the pressure cross-sectional area A1 and the pressure Ph is applied to the piston 34 as shown in FIG. 2 (A). Occur. This pressing force Fh is larger than the pressing force F required to transmit the specified torque. That is, while the conventional structure operates the clutch ON with the pressing force F, the speed can be extremely increased. At this stage, the throttle channel 41 is not yet substantially in operation, and the piston 34 is in the leftward direction (C
LCH indicates the clutch ON position. ), The air pressure in the sub-cylinder chamber 47 is substantially equal to the atmospheric pressure Po.

By the time the crankshaft 2 reaches stable rotation, air is introduced into the sub-cylinder chamber 47 from the cylinder chamber 37 through the throttle passage 41. In other words, when the stable rotation is reached, the pressure in the cylinder chamber 37 is Ph as shown in (B), but the pressure in the sub-cylinder chamber 47 is Po.
To Ph. As a result, both chambers 37 and 47 are
The pressure becomes Ph. In this case, a leftward pressing force F1 (= A1 × Ph) is generated in the piston 34, and the sub piston 44
A rightward pressing force F2 (= A2 × Ph) is generated at. As a result, the substantial pressing force applied to the piston 34 is F (= F
1-F2).

Here, the pressing force F is equal to the pressing force (F) generated when the ideal air pressure P is applied to transmit the specified torque into the cylinder chamber 37 in the conventional structure.
That is, the clutch ON operation itself is performed at a high speed by generating a large pressing force Fh by the pressure Ph, but after the crankshaft 2 reaches stable rotation, the pressing force F that ensures the transmission of the specified torque can be automatically adjusted.

On the other hand, when stopping the press operation,
As shown in (C), the air in the cylinder chamber 37 is opened to the atmosphere. Then, the air pressure in the cylinder chamber 37 quickly becomes the atmospheric pressure Po, but in this case also, the throttle channel 41 exerts an orifice action. Therefore, the sub-cylinder chamber 4
Since the residual air pressure P in the air inside 7 is substantially equal to Ph, the sub-piston 44 continues to have F22 substantially equal to the rightward pressing force F2. Therefore, in the conventional structure, the cylinder chamber 37 is opened to the atmosphere and the release spring 39 is released.
In the present invention, the clutch OFF operation is positively performed by the pressing force F2 in addition to the urging force S of the spring 39 in comparison with the conventional urging force S of the spring 39. The clutch can be turned off at a very high speed.

Therefore, according to this embodiment, the sub-piston 44 and the sub-cylinder 4 having the small pressurizing cross-sectional area A2 are provided.
2 is provided, and the sub-piston 44 is integrally connected to the piston 34 so that both pressurizing cross sections 34A and 44B are in opposite directions, and the cylinder chamber 37 and the sub-cylinder chamber 47 are provided. Since the throttle passage 41 is communicated with the throttle passage 41, a high pressing force Fh enables high-speed clutch ON operation, and after the crankshaft 2 reaches stable rotation, the pressing torque F can ensure transmission of a specified torque. During the clutch off operation, in addition to the biasing force S of the release spring 39, the residual pressure P in the sub-cylinder chamber 47 positively biases the sub-piston 44, that is, the piston 34, so that only the conventional release spring 39 is used. Compared with this, the clutch OFF operation can be performed at a much higher speed. Therefore, both the stable rotation arrival time at the start of the press operation and the braking time at the press stop can be automatically and significantly shortened.

Further, since the sub-cylinder 42 also serves as a part of the cylinder 32 which is indispensable for this apparatus, and the sub-piston 44 is also small in size, the structure is simple and stable operation is possible, and the cost is low. Moreover, there is no need to upsize the entire clutch device.

Furthermore, since the air supplied into the cylinder chamber 37 may have one kind of pressure Ph, the air supply means (28, 29).
Etc.) can be used as they are without modification.

In the above embodiment, the friction plate 23 is a single plate type and the brake device 50 is a separate type, but this can be implemented as it is as a multiple plate type or a combination type.

[0029]

As described above, according to the present invention, a sub-cylinder chamber including a sub-cylinder and a sub-piston having a small pressurizing cross section is provided, and the sub-piston is integrated with the piston so that the pressurizing cross-sectional area faces the piston. In addition, since both cylinder chambers are connected to each other and both cylinder chambers are communicated with each other by the throttle passage, the clutch ON operation can be speeded up and the specified torque can be automatically guaranteed after the crankshaft reaches stable rotation. The clutch-off operation can be performed at high speed with significantly reduced time. Therefore, the time required to reach stable rotation at the start of the press operation and the time until the 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 general press machine.

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

FIG. 5 is a diagram for explaining a clutch releasing means.

[Explanation of symbols]

 1 Drive Shaft 2 Crankshaft 4 Slide 6 Flywheel 10 Frame 20 Clutch Device 21 Clutch Part 22 Clutch Hub 23 Friction Plate 28 Air Supply Pipe 29 Solenoid Valve 31 Clutch Actuating Means 32 Cylinder 32B Air Supply Port 34 Piston 34A Press Section (Pressurization) Cross-sectional area A1) 35 Seal member 36 Pressing member 37 Cylinder chamber 38 Clutch release means 39 Release spring 39A pin 40 Rapid actuation means 41 Throttling flow passage 42 Sub-cylinder 44 Sub-piston 44B Pressurized cross-section (pressurized cross-sectional area A2) 47 Sub Cylinder chamber 50 Brake device

Claims (1)

[Claims] 1. A clutch device of a press machine configured to supply pressurized air to a cylinder chamber formed between a cylinder and a piston to perform a clutch engagement operation, the clutch device having a smaller pressure cross-sectional area than the piston. A sub-cylinder chamber including a sub-piston having a pressure cross-sectional area and a sub-cylinder is provided, and the piston and the sub-piston are integrally connected so that the respective pressure cross-sections face each other,
A clutch device for a press machine, wherein the cylinder chamber and the sub-cylinder chamber are communicated with each other through a throttle passage.