JP2009236173A - Hydraulic control device of wet clutch brake - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a wet clutch brake control device preventing shock on operating a clutch brake without requiring complicated and large hydraulic control circuit and skill of press operation. <P>SOLUTION: The hydraulic control device of the wet clutch brake 10 for selectively operating either a clutch mechanism 15 or a brake mechanism 20 by a clutch cylinder 25 provided between a flywheel W and a crankshaft A to which a rotation power is supplied from an external driving source is provided with a hydraulic cylinder 30 for supplying hydraulic oil to the clutch cylinder 25, a screw/nut mechanism 33 for moving a piston 32 of the hydraulic cylinder 30 forward and backward and a servo motor 38 for rotation control of the screw/nut mechanism 33. As its component only includes the hydraulic cylinder 30 driven by the servo motor 38 basically, a complicated and large hydraulic circuit is not required. The hydraulic control device controls only a rotation quantity of the servo motor 38, skill is not required for the press operation. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a hydraulic control device for a wet clutch brake. For example, the mechanical press is provided with a clutch brake device that controls the operation of the press by transmitting and shutting off the power supplied to the flywheel from an external power source to the crankshaft. The clutch brake device is roughly classified into a dry type and a wet type, and the present invention relates to a hydraulic control device for a wet clutch brake.

A wet clutch brake device such as a mechanical press has better controllability than a dry clutch brake device. Therefore, it is possible to prevent a shock when the clutch or the brake is operated, and to reduce the generated noise. In addition, the apparatus can be made compact, energy can be saved, and the life of the lining of the clutch and brake can be extended. For this reason, a wet clutch brake device may be employed in a mechanical press (see Patent Documents 1 and 2).
Moreover, in a hot forging press that requires high-speed forming, the clutch requires a large torque, but because of the low noise and vibration of the wet clutch brake device, there is a risk of fire due to oil leakage. However, it has recently been adopted.

  A wet clutch brake device in a mechanical press or the like includes a flywheel, a case fixed to the flywheel and rotating together, and a clutch mechanism and a brake mechanism housed in the case. The clutch mechanism and the brake mechanism are controlled by the clutch cylinder and the spring so that only one of them functions. In addition, a hydraulic control circuit is incorporated to drive the clutch cylinder.

  FIG. 3 shows an example of the hydraulic control circuit. This hydraulic control circuit achieves shockless operation by performing oil discharge from the pump in one press cycle and ON / OFF control of various valves in a very short time based on slide position measurement. Therefore, the configuration of the hydraulic equipment is complicated as follows.

First, the basic operation circuit is as follows.
In the figure, reference numeral 101 denotes a high and low pressure dual pump, which supplies pressure oil to two high and low pressure accumulators 102 and 103. The two accumulators 102 and 103 are both hydraulic pressure sources of the clutch cylinder 125, but the low-pressure accumulator 103 is used for driving the clutch piston, and the high-pressure accumulator 102 is used for securing a necessary clutch force.
104 is a logic valve. When the valve is opened, the pressure oil in the accumulator 103 is supplied to the clutch cylinder 125, and when the valve is closed, the supply of the pressure oil is shut off. A pilot control valve 105 opens and closes the logic valve 104.
106 is an electromagnetic on-off valve for the high-pressure accumulator 102, which is opened immediately after the operation of the clutch cylinder 125 by the opening of the logic valve 104 during clutch operation, and supplies high-pressure oil from the high-pressure accumulator 102 to the clutch cylinder 125. The clutch force is secured.
107 is an electromagnetic on-off valve for rapidly releasing the pressure in the clutch cylinder 125, and works simultaneously with the brake signal.

In addition to the basic circuit described above, an adjustment circuit for improving the controllability of the clutch cylinder is provided.
A throttle 108 controls the pressure release speed of the electromagnetic on-off valve 107.
109 is an electromagnetic on-off valve provided to prevent shock (noise). That is, if the pressure in the clutch cylinder 125 is rapidly released by the electromagnetic on-off valve 107, a sudden brake is activated and a large shock and noise are generated. To prevent this, the electromagnetic on-off valve 107 is turned off by a brake signal. At the same time as the timer is turned on again, the electromagnetic on-off valve 109 is turned off to gradually release the pressure from the circuit.

110 is a valve that controls the flow rate of the electromagnetic on-off valve 109.
111 is a solenoid valve for controlling the flow rate. That is, in order to apply the brake, the pressure oil is extracted from the electromagnetic valve 109, but minute flow control cannot be realized only by the electromagnetic valves 109 and 110. Therefore, the pressure oil is discharged from the electromagnetic valves 109 and 110 while supplying the pressure oil from the electromagnetic valve 111 to the clutch cylinder little by little so as to soften the brake shock.

In addition to the above, a safety countermeasure circuit is also provided to ensure safety and save energy.
112 is an electromagnetic on-off valve provided so that the brake can be operated and safety can be ensured even when the electromagnetic on-off valve 107 malfunctions.
113 is a safety valve provided so that the pressure in the accumulators 102 and 103 does not become abnormally high.
Reference numerals 114 and 115 denote energy saving circuits for unloading and lowering the electric power of the pump drive motor after the pressures of the high and low pressure accumulators 102 and 103 reach the set pressure.

  The hydraulic circuit as described above realizes the operation of the clutch and brake for each press cycle. In the conventional hydraulic control circuit, the pressure of the hydraulic oil supplied to and discharged from the clutch cylinder 125 is the oil pressure. Since it changes slightly depending on the temperature, it is indispensable to add an adjustment circuit as described above and further a safety countermeasure circuit in order to ensure controllability. For this reason, the hydraulic circuit becomes complicated and large. Further, in order to maintain controllability, the management of the oil temperature is important, and it is necessary to adjust the valve in accordance with the oil temperature. Therefore, considerable skill is required for the operation of the press.

JP-A-10-305400 JP 2001-58299 A

  In view of the above circumstances, the present invention provides a wet clutch brake control device that does not require a complicated and large hydraulic control circuit, does not require much skill in operation of the press, and can prevent a shock at the time of clutch brake operation. With the goal.

The hydraulic control device for a wet clutch brake according to a first aspect of the present invention is provided with a clutch mechanism and a brake mechanism between a flywheel to which rotational power is supplied from an external drive source and a crankshaft, and one of them is a clutch cylinder. A hydraulic control device for a wet clutch brake that is selectively operated, a hydraulic cylinder that supplies hydraulic oil to the clutch cylinder, a screw / nut mechanism that moves a piston of the hydraulic cylinder back and forth, and a rotation of the screw / nut mechanism And a servo motor to be controlled.
The hydraulic control apparatus for a wet clutch brake according to a second aspect of the present invention is the relief according to the first aspect, wherein an excessive pressure equal to or higher than a set pressure necessary for the operation of the clutch cylinder is released in an oil passage between the hydraulic cylinder and the clutch cylinder. It is characterized by interposing a valve.
A hydraulic control device for a wet clutch brake according to a third invention is characterized in that, in the first invention, an on-off valve for controlling discharge of hydraulic oil is interposed in an oil passage between the hydraulic cylinder and the clutch cylinder. To do.
The hydraulic control device for a wet clutch brake according to a fourth aspect of the present invention is the hydraulic control device according to the first aspect, wherein a check valve is interposed in an oil passage between the hydraulic cylinder and the hydraulic oil tank. The hydraulic oil is allowed to be supplied to the cylinder, and is prevented from being discharged from the hydraulic cylinder to the hydraulic oil tank.
According to a fifth aspect of the present invention, there is provided a hydraulic control device for a wet clutch brake according to the first aspect, wherein an on-off valve for opening and closing the oil passage is provided in an oil passage between the hydraulic cylinder and a hydraulic pump that supplies hydraulic oil to the hydraulic cylinder. It is characterized by being interposed.
According to a sixth aspect of the present invention, there is provided a hydraulic control device for a wet clutch brake according to the first aspect, wherein an internal pressure sensor that detects an internal pressure of the hydraulic cylinder, a piston position sensor that detects a moving position of a piston of the hydraulic cylinder, and the piston position sensor Calculates the planned internal pressure of the hydraulic cylinder based on the detected movement position of the piston, compares the actual internal pressure detected by the internal pressure sensor, and outputs a drive signal to the servo motor until the actual internal pressure matches the planned internal pressure. A controller having a send-in control function is provided.
The hydraulic control device for a wet clutch brake according to a seventh aspect of the present invention is the hydraulic control apparatus for a wet clutch brake according to the sixth aspect, wherein the controller compares the actual internal pressure detected by the internal pressure sensor during the follow-up control with the planned internal pressure. It has an emergency stop function that outputs a stop signal when the value exceeds.
The hydraulic control device for a wet clutch brake according to an eighth aspect of the present invention is the hydraulic control apparatus for a wet clutch brake according to the sixth aspect, wherein the controller compares the actual internal pressure detected by the internal pressure sensor during the follow-up control with the planned internal pressure, and the actual internal pressure is the planned internal pressure. When it is below the allowable range, it has an error display function that outputs an error display signal.

According to the first invention, the piston advance / retreat amount of the hydraulic cylinder that supplies hydraulic oil to the clutch cylinder is proportional to the rotation amount of the servo motor, so that the necessary pressure is reached if only the actual pressure in the clutch cylinder is detected. Since it is easy to control the rotation amount of the servo motor, the actual pressure of the clutch cylinder can be made to coincide with the planned pressure for each press cycle without affecting the change in the oil temperature. For this reason, the clutch cylinder can be operated by the hydraulic cylinder driven by the servo motor, and the clutch mechanism and the brake mechanism can be selectively operated. In addition, since the component is basically a hydraulic cylinder driven by a servo motor, a complicated and large hydraulic circuit is not required. Furthermore, it is only necessary to control the rotation amount of the servo motor, and it is not necessary to adjust many valves in accordance with the oil temperature.
According to the second invention, the internal pressure of the hydraulic cylinder can be reliably increased to the clutch set pressure set by the relief valve, so that the clutch operation is ensured. Also, by operating the hydraulic cylinder slightly higher than the relief valve set pressure, the hydraulic oil in the hydraulic cylinder can be discharged from the relief valve little by little every clutch operation. If so, it can be replaced with new hydraulic oil, and temperature rise and deterioration of the hydraulic oil can be prevented.
According to the third aspect of the present invention, the pressure in the hydraulic cylinder can be suddenly lowered by opening the on-off valve, and the clutch can be instantaneously switched from the engaged state to the disengaged state. For this reason, since it is not necessary to make the servo motor perform high-speed rotation for retracting the piston at a high speed, a servo motor with a small capacity can be used, and the control device can be made compact.
According to the fourth aspect of the invention, when the piston of the hydraulic cylinder is moved backward, the inside of the hydraulic cylinder tends to become negative pressure. However, since replenishment from the hydraulic oil tank is possible via the check valve, air is sucked into the hydraulic cylinder. Can prevent such obstacles.
According to the fifth aspect of the present invention, if the on-off valve connected to the hydraulic cylinder is opened and the hydraulic pump is driven, the hydraulic oil can be supplied to the hydraulic cylinder as necessary.
According to the sixth aspect of the invention, the additional driving is performed in a state where the actual internal pressure in the hydraulic cylinder does not reach the specified value, so that the actual internal pressure can be surely increased to the specified value. For this reason, even if there is an increase in clutch cylinder stroke or oil leakage due to deterioration over time, the clutch cylinder can be reliably operated.
According to the seventh aspect of the present invention, when the internal pressure of the hydraulic cylinder by the follow-up control exceeds the specified value, the movement of the hydraulic cylinder is urgently stopped, so that an abnormal operation of the clutch cylinder can be prevented.
According to the eighth aspect of the present invention, when the internal pressure of the hydraulic cylinder does not rise sufficiently even after execution of the follow-up control and falls below the allowable range beyond the planned internal pressure, the occurrence of oil leakage or the like can be displayed by displaying an abnormality. Therefore, disasters such as fire can be prevented.

Next, an embodiment of the present invention will be described with reference to the drawings.
FIG. 2 shows a wet clutch brake in a mechanical press suitable for applying the hydraulic control apparatus of the present invention. First, the configuration of the wet clutch brake will be described with reference to FIG.
Reference numeral F indicates a frame of the mechanical press, and reference numeral A indicates a crank shaft of the mechanical press. Reference numeral S denotes a cylindrical fixing member fixed to the frame F and rotatably supporting one end of the crankshaft A.
A flywheel W is rotatably attached to the outer periphery of the fixed member S. A wet clutch brake 10 is provided between the flywheel W and one end of the crankshaft A to connect and separate them.

The wet clutch brake 10 includes a case 11, and the case 11 is a generally cylindrical member having a top shape, and a base end portion thereof is fixed to the flywheel W. Further, the case 11 is disposed so that the shaft end portion of the crankshaft A is located inside the case 11.
In the case 11, a clutch mechanism 15, a brake mechanism 20, and a clutch cylinder 25 are provided.

The clutch mechanism 15 mainly comprises a rotating member 16 and a clutch plate 17 and is configured as follows.
An outer end portion of a rotating member 16 attached to one end of the crankshaft A is rotatably held on the top portion 11a of the case 11. The rotating member 16 is attached to the crankshaft A so as to be movable in the axial direction of the crankshaft A, although the relative rotation with respect to the crankshaft A is restricted through a spline or the like.
Between the rotating member 16 and the case 11, a plurality of clutch plates 17 are arranged alternately.

The brake mechanism 20 mainly comprises a fixed brake member 21, a shaft brake member 22, and a brake plate 23, and is configured as follows.
One end of the fixing member S is located in the space of the case 11, and a fixed-side brake member 21 whose diameter is increased so as to surround the crankshaft A is provided at one end thereof. A shaft side brake member 22 is provided between the fixed side brake member 21 and the crankshaft A. The shaft-side brake member 22 is attached to the crankshaft A so as to be movable in the axial direction of the crankshaft A although the relative rotation with respect to the crankshaft A is restricted via a spline or the like. . Between the shaft side brake member 22 and the fixed side brake member 21, a plurality of brake plates 23 alternately arranged are arranged.

Next, the clutch cylinder 25 will be described.
In the axial direction of the crankshaft A, a piston 25a slidable along the axial direction of the crankshaft A is provided between the shaft-side brake member 22 and the rotating member 16. A fluid-tightly sealed oil chamber 25b is formed between the piston 25a and the shaft-side brake member 22 side. The oil chamber 25b is connected to a rotary joint 29 attached to one end of the rotating member 16. In addition, an external hydraulic power source is communicated via a communication passage 26 formed inside the rotating member 16. The above-described piston 25a and oil chamber 25b constitute a clutch cylinder 25.

On the other hand, a spring 27 is disposed between the piston 25a and the rotating member 16, and the spring 27 always presses the piston 25a against the brake mechanism 20 side.
For this reason, in a state where oil is not supplied to the oil chamber 25b of the clutch cylinder 25, the piston 25a is urged toward the left in the figure by the spring 27. That is, since it moves toward the shaft side brake member 22, the shaft side brake member 22 and the fixed side brake member 21 are connected by a plurality of brake plates 23, and the rotating member 16 and the case 11 are separated. Is done. In this case, the brake mechanism 20 functions and the clutch mechanism 15 does not function.

  Conversely, when oil is supplied to the oil chamber 25b of the clutch cylinder 25, the piston 25a is urged toward the right in the figure by the oil pressure in the oil chamber 25b. That is, since the spring 27 is compressed and moved toward the rotating member 16, the shaft-side brake member 22 and the fixed-side brake member 21 are separated from each other, and a plurality of clutches are provided between the rotating member 16 and the case 11. Connected by the plate 17. In this case, the clutch mechanism 15 functions and the brake mechanism 20 does not function.

  As described above, the wet clutch brake 10 controls the supply / disconnection of the external power supplied from the flywheel W to the crankshaft A by controlling the supply / discharge of hydraulic oil to / from the oil chamber 25b of the clutch cylinder 25. It is possible to control the operation of a mechanical press or the like.

Next, a hydraulic control device for a wet clutch brake will be described.
FIG. 1 is a hydraulic circuit diagram and an electronic circuit diagram showing a hydraulic control device for a wet clutch brake in one embodiment of the present invention.

In the figure, reference numeral 30 denotes a hydraulic cylinder, which includes a cylinder 31 and a piston 32. The piston 32 is configured to be advanced and retracted by a screw / nut mechanism 33. That is, the screw rod 35 is screwed into the nut 34 fixed to the outer end of the piston 32, and the screw rod 35 rotates forward and backward so that the inner end of the piston 32 penetrates deeply into the cylinder 31. It is retracted shallowly. By the advance / retreat operation of the piston 32, the hydraulic oil in the cylinder 31 can be pressurized or returned to a low pressure.
The cylinder 31 of the hydraulic cylinder 30 is communicated with an oil chamber 25b of the clutch cylinder 25 through a communication passage 26 that passes through an oil passage 41 and the rotary joint 29.

A screw rod 35 of the screw / nut mechanism 33 is connected to a speed reducer 37 and a servo motor 38 via a joint 36. Reference numeral 39 denotes a piston position sensor composed of an encoder for detecting the rotation amount of the servo motor 38.
Since the rotation amount of the screw rod 35 is directly proportional to the rotation amount of the servo motor 38, the advance / retreat amount of the piston 32 is also directly proportional to the rotation amount of the servo motor 38. Therefore, the advance / retreat amount of the piston 32 can be accurately grasped by the piston position sensor 39.

  When the servo motor 38 is rotated forward by the above basic circuit and the piston 32 enters the cylinder 31, the hydraulic oil in the cylinder 31 is supplied to the oil chamber 25b of the clutch cylinder 25 and the clutch mechanism 15 is connected. It becomes. On the contrary, when the servo motor 38 is reversed, the piston 32 moves backward in the cylinder 31, and the hydraulic oil in the oil chamber 25 b of the clutch cylinder 25 returns to the cylinder 31. At this time, the piston 25a of the clutch cylinder 25 is pushed by the spring, and the brake mechanism 20 is activated.

The circuit between the hydraulic cylinder 30 and the clutch cylinder 25 is basically as described above, but the following circuit is added.
An oil passage 41 connected to the hydraulic oil tank 40 is provided in the oil passage 41 between the hydraulic cylinder 30 and the clutch cylinder 25, and a relief valve 43 is interposed in the oil passage 42. The relief valve 43 is set so as to release an excessive pressure exceeding a pressure necessary for the operation of the clutch cylinder 25 (hereinafter referred to as a set pressure).

  In other words, since the relief valve 43 is closed until the set pressure is reached, the internal pressure of the hydraulic cylinder 30 can be reliably increased to the clutch set pressure set by the relief valve 43. For this reason, the clutch operation is ensured. Further, by operating the internal pressure of the hydraulic cylinder 30 slightly higher than the relief valve set pressure, the hydraulic oil in the hydraulic cylinder 30 can be discharged little by little from the relief valve 43 each time the clutch is operated. If the operation oil supply from 52 is combined and operated, the operation oil can be replaced with a new operation oil, and the temperature rise and deterioration of the operation oil can be prevented.

  Further, if the set pressure of the relief valve 43 is adjusted higher, the clutch torque can be increased, so that the stick can be released even when the press slide sticks.

An oil passage 44 is provided between the oil passage 41 between the hydraulic cylinder 30 and the clutch cylinder 25 or between the oil passage 42 connected to the oil passage 41 and the tank 40. The oil passage 44 is provided with an electromagnetic opening / closing valve 45.
If the electromagnetic opening / closing valve 45 is set to the open position, the pressure in the hydraulic cylinder 30 can be suddenly lowered, and the clutch mechanism 15 can be instantaneously switched from the on state to the disconnected state. For this reason, it is not necessary to rotate the servo motor 38 at a high speed so as to retract the piston 32 at a high speed. Therefore, the servo motor 38 having a small capacity can be used, and the control device can be made compact.

When the clutch mechanism 15 is disconnected during normal operation, the servo motor 38 is reversed and the piston 32 is retracted. However, when the retreating speed of the piston 32 cannot catch up, the electromagnetic on-off valve 45 is opened as described above. By switching to the position, the pressure oil in the clutch cylinder 25 can be quickly removed. For this reason, the servo motor 38 does not need to have a large capacity necessary for high-speed retraction.
The electromagnetic on-off valve 45 can also be used to disconnect the clutch mechanism 15 in an emergency such as a malfunction of the servo motor 38.

An electromagnetic on-off valve 52 and a hydraulic pump 53 are interposed in an oil passage 51 between the cylinder 31 of the hydraulic cylinder 30 and the tank 40.
When the electromagnetic on / off valve 52 is set to the open position and the hydraulic pump 53 is driven, the hydraulic oil can be supplied to the hydraulic cylinder 30. The hydraulic circuit from the hydraulic cylinder 30 to the clutch cylinder 25 is basically a closed circuit. However, as described above, it is necessary to replenish the hydraulic oil by discharging the hydraulic oil from the relief valve 43. In order to supplement the replenishment from the valve 55, an electromagnetic opening / closing valve 52 is used. The hydraulic oil supply through the electromagnetic opening / closing valve 52 may be performed at a low pressure, and is used in a state where the clutch cylinder 25 is not operated.

Further, a check valve 55 is interposed in the oil passage 54 between the cylinder 31 of the hydraulic cylinder 30 and the tank 40. The check valve 55 is interposed in a direction that allows hydraulic oil to be supplied to the cylinder 31 of the hydraulic cylinder 30 and prevents discharge from the cylinder 31 to the tank 40.
For this reason, when the piston 32 of the hydraulic cylinder 30 is retracted, the inside of the hydraulic cylinder 30 tends to become negative pressure, but replenishment from the hydraulic oil tank 40 is possible via the check valve 55. For this reason, troubles such as air suction into the hydraulic cylinder 30 can be prevented.

Next, an electronic circuit of the hydraulic cylinder 30 will be described.
Reference numeral 60 denotes a controller, which is a publicly known one composed of a microcomputer or the like. The controller 60 includes a calculation unit 61 and a control unit 62, and detection signals from the internal pressure sensor 65, the slide position sensor 66 and the piston position sensor 39 are input to the calculation unit 61. .

  The internal pressure sensor 65 is a pressure sensor attached to an oil passage that can measure the internal pressure of the hydraulic cylinder 30, for example, the oil passage 41. The slide position detection sensor 66 is a known sensor that can measure the physical position of a slide (not shown) of a mechanical press. The piston position sensor 39 is a sensor for detecting the rotation amount of the servo motor 38 as described above.

The arithmetic unit 61 of the controller 60 can compute the original hydraulic fluid pressure in the cylinder 31 corresponding to the amount of movement of the piston 32 based on the detection signal of the piston position sensor 39, namely the plans pressure P _1.
The control unit 62 has a function of executing follow-up control, emergency stop control, and abnormality display control in addition to basic operation control that is normally performed.

(Basic operation control)
Basic operation control of the clutch cylinder 25 is performed as follows.
When the clutch is operated, the servo motor 38 may continue to rotate normally up to a predetermined position while inputting the position signal of the piston position sensor 39, so that the hydraulic oil having the necessary set pressure can be supplied to the clutch cylinder 25.
When the clutch is disengaged, the servo motor 38 is reversely rotated to retract the piston 32, or in addition to this, the electromagnetic on-off valve 45 is opened to release the pressure in the clutch cylinder 25.

(Follow-up control)
The follow-up control is performed by comparing the planned internal pressure P ₁ calculated by the calculation unit 61 with the actual internal pressure P ₂ of the clutch cylinder 25 detected by the internal pressure sensor 65, and until the actual internal pressure P ₂ matches the planned internal pressure P _1. 38 is a control to send to 38 a drive signal.
When only the basic operation control is performed, the internal pressure of the clutch cylinder 25 may not reach the set pressure with a specified piston stroke. For example, if there is wear of the clutch plate 17 of the clutch mechanism 15 or the brake plate 23 of the brake mechanism 20 or oil leakage from the packing of the hydraulic cylinder 30, the clutch mechanism 15 does not operate at a specified timing. Even in such a case, by the thrust control is automatically executed, in the state in which the actual pressure P ₂ of the hydraulic cylinder 30 does not reach the planned pressure P _1, the piston 32 until the deviation becomes zero thrust Driving is performed. Therefore, it is possible to reliably boost the actual pressure P ₂ on over pressure P _1. Therefore, even if there is an increase in the stroke of the clutch cylinder 25 or oil leakage due to deterioration over time, the operation of the clutch cylinder 25 can be ensured.

(Emergency stop control)
The emergency stop control, while comparing the actual pressure P ₂ and the planned pressure P ₁ in the drive-control with respect to the actual internal pressure P ₂ is planned pressure P _1, the control for outputting a stop signal exceeds a certain value or more is there.
When the actual pressure P ₂ by the control of the is too high, since the emergency stop the movement of the hydraulic cylinder 30, it is possible to prevent abnormal operation of the clutch cylinder 25.

(Abnormal display control)
Moreover, during said drive-control, it does not rise even enough the actual pressure P ₂ by increasing the drive-amount, as compared with the planned pressure P _1, when the deviation d is Shitamawa' above allowable range dp is There is a high possibility that troubles such as oil leakage have occurred in the oil passage from the hydraulic cylinder 30 to the clutch cylinder 25. Therefore, in such a case, a display signal Se is sent to the display unit 63 to display an abnormality indicating the cause of oil leakage or the like. This abnormality display can prevent a fire or the like.

  As described above, according to the hydraulic control device of the present invention, since the delicate pressure of the clutch cylinder 25 can be controlled by controlling the rotation speed of the servo motor 38, flexible clutch control can be easily performed.

  In addition, the conventional technology basically employs a control system that turns on and off by measuring the slide position of the valve installed in the hydraulic unit, so a reduction in controllability due to changes in oil temperature is inevitable. However, in the present invention, since the actual pressure in the clutch cylinder 25 is directly controlled, the pressure controllability in the clutch cylinder 25 is not deteriorated due to a change in the oil temperature or the like.

  Furthermore, a hot forging press clutch that requires high-speed forming requires a large torque and uses high-pressure oil, so oil leakage is likely to occur. However, in the present invention, the hydraulic circuit is simple, so there is a possibility of oil leakage itself. In addition, if there is an oil leak, a small amount of oil leak can be detected immediately, so that it is possible to prevent a disaster such as a fire.

Although FIG. 2 shows a mechanical press as an example of application of the present invention, the control device of the present invention can be applied to a clutch cylinder having a structure other than the wet clutch brake device 10 shown in the present drawing.
Moreover, the wet clutch brake control apparatus of this invention is not restricted to a mechanical press, If it is a machine which uses a wet clutch brake control apparatus, it can apply also to machines, such as a cutting machine and a forging mill.

It is the hydraulic circuit diagram and electronic circuit diagram which show the hydraulic control apparatus of the wet clutch brake in one Embodiment of this invention. It is structure explanatory drawing of the wet clutch brake to which the hydraulic control apparatus of this invention is applied. It is explanatory drawing of the hydraulic control circuit of the conventional wet clutch brake.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Wet clutch brake 15 Clutch mechanism 20 Brake mechanism 25 Clutch cylinder 30 Hydraulic cylinder 31 Cylinder 33 Screw / nut mechanism 38 Servo motor 39 Piston position sensor 43 Relief valve 45 Electromagnetic on-off valve 52 Electromagnetic on-off valve 55 Check valve 60 Controller 61 Calculation part 62 Control unit

Claims (8)

A hydraulic control device for a wet clutch brake in which a clutch mechanism and a brake mechanism are provided between a flywheel to which rotational power is supplied from an external drive source and a crankshaft, and either one is selectively operated by a clutch cylinder. There,
A hydraulic cylinder for supplying hydraulic oil to the clutch cylinder;
A screw / nut mechanism for moving the piston of the hydraulic cylinder back and forth;
A hydraulic control device for a wet clutch brake, comprising: a servomotor for controlling rotation of the screw / nut mechanism. The wet clutch brake according to claim 1, wherein a relief valve for releasing an excessive pressure not less than a set pressure necessary for the operation of the clutch cylinder is interposed in an oil passage between the hydraulic cylinder and the clutch cylinder. Hydraulic control device. 2. The hydraulic control device for a wet clutch brake according to claim 1, wherein an on-off valve for controlling discharge of hydraulic oil is interposed in an oil passage between the hydraulic cylinder and the clutch cylinder. A check valve is interposed in the oil passage between the hydraulic cylinder and the hydraulic oil tank,
2. The wet clutch brake according to claim 1, wherein the check valve allows hydraulic oil to be supplied to the hydraulic cylinder and prevents discharge from the hydraulic cylinder to the hydraulic oil tank. 3. Hydraulic control device. 2. The hydraulic pressure of the wet clutch brake according to claim 1, wherein an opening / closing valve for opening and closing the oil passage is interposed in an oil passage between the hydraulic cylinder and a hydraulic pump that supplies hydraulic oil to the hydraulic cylinder. Control device. An internal pressure sensor for detecting an internal pressure of the hydraulic cylinder;
A piston position sensor for detecting a movement position of a piston of the hydraulic cylinder;
The servo motor calculates the planned internal pressure of the hydraulic cylinder based on the movement position of the piston detected by the piston position sensor and compares the actual internal pressure detected by the internal pressure sensor until the actual internal pressure matches the planned internal pressure. 2. The hydraulic control device for a wet clutch brake according to claim 1, further comprising a controller having a follow-up control function for sending a drive signal to the wet clutch brake. The controller has an emergency stop function that compares the actual internal pressure detected by the internal pressure sensor during the follow-up control with the planned internal pressure, and outputs a stop signal when the actual internal pressure exceeds the planned internal pressure. The hydraulic control device for a wet clutch brake according to claim 6. The controller compares the actual internal pressure detected by the internal pressure sensor during the follow-up control with the planned internal pressure, and outputs an abnormality display signal when the actual internal pressure is below the allowable range with respect to the planned internal pressure. The hydraulic control device for a wet clutch brake according to claim 6, further comprising an abnormality display function.

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