CN112008028A - A clutch for hot die forging press - Google Patents

Abstract

The invention relates to a clutch for a hot die forging press in the technical field of press machine clutch, which comprises a large gear and a crankshaft, wherein the end part of the crankshaft is fixedly connected with a friction disc, a plurality of friction blocks are arranged at the circumferential contact part of the disc surface of the friction disc and the outer end of the large gear, the outer side of the friction disc is provided with a clutch braking structure for axially driving the friction blocks, the clutch braking structure comprises a cylinder and a piston, the cylinder is provided with a conical ring cavity, the two axial sides of the conical ring cavity are provided with a first sealing matching section and a second sealing matching section, the end part of the cylinder is fixedly connected with the large gear, the piston is laterally used for extruding the friction blocks, the end part of the cylinder corresponding to the second sealing matching section is connected with a rotating seat, a buffer cavity is arranged in the rotating seat, the other end of the rotating seat corresponding to the buffer, the side wall of the cylinder is correspondingly provided with a plurality of air inlet and outlet holes, and each radial hole is communicated with the air inlet and outlet holes through a high-pressure hose.

Description

A clutch for hot die forging press

technical field

The invention relates to the technical field of clutches for presses, in particular to a clutch for hot die forging presses.

Background technique

The clutch of the hot die forging press is the core component used to ensure that the press is driven in accordance with the specified frequency in normal operation. The clutches of hot die forging presses are generally floating insert pneumatic friction clutches. Its structure is shown in Figures 1 and 2, including a crankshaft 5 and a large gear 9. The large gear 9 is driven by a driving component. The outer side of the connection between the large gear 9 and the crankshaft 5 is provided with a clutch braking structure to drive the crankshaft 5 to rotate. The braking structure includes a cylinder 2 and a piston 3. The telescopic and inflatable cavity between the cylinder 2 and the piston 3 is a conical annular cavity, and between the cylinder 2 and the piston 3 at both ends of the conical annular cavity, there is a space between the cylinder 2 and the piston 3 that can realize the axial movement of the piston. In the sliding fitting section, the piston 3 is provided with a friction disc 4 on the side of the large gear 9, and the friction disc 4 is provided with a friction block 6 for combining with the large gear 9. The cylinder 2 and the piston 3 are connected to the large gear by bolts. 9; the outside of the piston 3 is provided with an air pressure buffer cavity, the side end of the cylinder is rotatably connected with a rotary joint, and the piston 3 in the circumferential direction of the air pressure buffer cavity is provided with a piston air inlet 301 in communication with the cone annular cavity. The clutch brake structure of this structure controls the electromagnetic air distribution valve when the press needs to act, so that the compressed air enters the conical annular cavity between the cylinder 2 and the piston 3 through the rotary joint through the piston air inlet, and the piston 3 is in the compressed air. Under the action, it moves axially to the friction disc 4 side, and the friction block 6 is pressed between the large gear 9 and the piston 3, so that the clutch is in a combined state, and the large gear 9 drives the crankshaft 5 through the friction block 6 and the friction disc 4. . When the cylinder 2 is exhausted, the piston 3 moves in the opposite direction under the action of the spring force, so that the friction block 6 is disengaged.

In the above clutch structure, since the cylinder 3 rotates with the large gear 9 during operation, the rotary joint is also connected with a pipe joint 1 through a bearing seat, and a bearing is installed between the pipe joint 1 and the bearing seat, and the bearing seat is in operation. Rotating with the rotation of the cylinder 2, the pipe joint 1 is stationary during the working process. The air intake hole 301 opened on the piston 3 enables the compressed air to enter the closed conical annular cavity between the cylinder 3 and the piston 4 through the pipe joint 1 , so as to realize the action of the clutch friction block 6 . The function of this device is relatively simple, because the compressed air can only be taken in and exhausted from the air inlet at the top of the piston 3, and the piston 3 has a large volume, which will cause the air in and out of the clutch to be relatively slow. The speed of the air in and out of the clutch directly affects the working performance of the press, and the slow air intake of the clutch will affect the speed at which the friction block 6 and the friction plate 4 are combined, resulting in insufficient working capacity of the press. The slow air outlet of the clutch will directly affect the braking performance of the hot die forging press, which will cause the press to fail to brake, the braking angle is too large, the temperature of the friction block 6 is too high, and the device cannot cool the friction block.

SUMMARY OF THE INVENTION

Aiming at the problems in the prior art that the clutch structure of the hot die forging press has poor brake clutch action sensitivity and slow heat dissipation and cooling of the friction block, the present invention provides a clutch for a hot die forging press. The improvement of the structure realizes the quick in and out of the compressed air to improve the flexibility of the clutch action.

The object of the present invention is achieved in this way, a clutch for a hot die forging press includes a large gear and a crankshaft, the large gear is rotatably connected to the outer periphery of the end of the crankshaft, the end of the crankshaft is fixedly connected with a friction disc, the A number of friction blocks are arranged at the contact position between the disk surface of the friction disk and the outer end of the large gear in the circumferential direction, and the outer side of the friction disk is provided with a clutch brake structure for axially driving the friction block. The cylinder and the piston of the ring cavity, characterized in that, between the cylinder and the piston on the two axial sides of the conical ring cavity, there are axially sliding sealing and matching sections 1 and 2, and the sealing and matching sections correspond to each other. The end of the cylinder is fixedly connected with the large gear in the circumferential direction, the piston side corresponding to the first sealing and matching section is used to squeeze the brake friction block, and the end of the cylinder corresponding to the second sealing and matching section is connected with a rotating seat, so One end of the rotary seat is fixedly connected to the end of the cylinder in the circumferential direction, a buffer cavity is arranged in the rotary seat, and the other end of the rotary seat corresponding to the buffer cavity is provided with a central hole, and a bearing seat is fixed in the central hole, and the bearing seat is fixed in the central hole. A pipe joint is rotatably connected in the bearing seat through the bearing shaft. A seal is arranged between the pipe joint and the bearing seat and between the bearing seat and the central hole of the rotating seat. A number of air inlet and outlet holes are correspondingly arranged on the side wall of the cylinder, and each radial hole is in sealing communication with the air inlet and outlet holes through a high-pressure hose respectively.

In the clutch brake structure of the press of the present invention, the air intake structure at the top of the piston is improved to enter the air into the buffer cavity through the rotating seat, and then the buffer cavity is arranged along the outer side of the cylinder to form a plurality of high-pressure hoses to form an air intake channel to communicate with each other. Intake and exhaust are realized in the working cavity of the piston and the cylinder. By setting an external channel, it is convenient to set up multiple intake pipelines, increase the speed and flow of the intake and exhaust flow, reduce the braking angle and clutch angle of the clutch, and improve the The sensitivity of clutch and brake improves the precision of press operation.

In order to ensure the fitting installation between the pipe joint, the bearing seat and the rotating seat, the outer circumference of the bearing seat is fitted and sleeved with the central hole of the rotating seat, and a seal is provided, and the outer circumference of the bearing seat is provided with a contact with the rotating seat. By the fixed flange 1, the center of the bearing seat is provided with a shaft hole, the two ends of the shaft hole and the outer circumference of the pipe joint are respectively installed with bearings, and there is a seal between the inner end of the bearing seat and the outer circumference of the pipe joint A cover, the sealing cover is sleeved on the outer circumference of the pipe joint with a gap, and is fixed to the end of the bearing seat by several screws in the circumferential direction, and a sealing ring is arranged between the inner circumference of the sealing cover and the pipe joint.

In order to facilitate the rapid cooling of the friction block, the rotating seat is also provided with a blast hole in the circumferential direction, the blast hole is connected with a blower, and the center of the piston corresponding to the center of the rotating seat is provided with a ventilation hole communicated with the blast hole, The vent communicates along the hollow ring between the inner side of the piston and the outer side of the friction disc and blows air to the friction block for cooling.

In order to ensure the smooth flow of the blast through the air, the large gear is also provided with several ventilation holes in the circumferential direction close to the friction block.

Further, the pipe joint protrudes from the outer side of the bearing seat, and the outer periphery of the extended end is provided with a flange ring, and a wind cover is installed between the flange ring and the rotating seat, and the wind cover corresponds to the position of the blowing hole. With air inlet.

In order to limit the axial moving force distance between the piston and the cylinder, a guide copper sleeve is arranged between the cylinder and the piston corresponding to the second sealing and matching section, the guide copper sleeve is fixedly embedded with the cylinder, and the piston and the guide The copper sleeve is slidably matched, the matching section of the piston is provided with a step that is limited and abutted against the guide copper sleeve, and a sealing ring is arranged between the outer periphery of the step and the cylinder.

In order to improve the structure of the contact part between the piston and the friction block, the friction block is provided with an outer gear ring that guides movement in the circumferential direction of the outer side of the piston, the outer circumference of the outer gear ring is matched with an inner gear ring, and the inner gear ring and the outer gear ring are provided. Axial guide fit, the inner gear ring and the circumference of the cylinder and the large gear are fixed by a number of bolts, the outer gear ring and the cylinder are circumferentially provided with a number of lead screws, and the outer ring gear corresponding to the lead screws is provided with a number of screw holes in the circumference A through hole is provided in the corresponding circumferential direction of the cylinder to facilitate the passage of the lead screw, the position of the lead screw extending out of the cylinder is provided with a return spring and a compression nut, and a washer is arranged between the compression nut and the return spring.

Description of drawings

FIG. 1 is a schematic structural diagram of a clutch of a hot die forging press in the prior art.

FIG. 2 is a partial enlarged view of part A in FIG. 1 .

Fig. 3 is a schematic structural diagram of the clutch for a hot die forging press of the present invention.

FIG. 4 is a partial enlarged view of part B in FIG. 3 .

Among them, 1 pipe joint; 2 cylinder; 3 piston; 301 air inlet; 302 air outlet 4 friction disc; 5 crankshaft; 6 friction block; 7 sealing ring; 8 reset parts; 9 large gears; 10 rotating seat; 1001 buffer cavity ; 1002 radial hole; 1003 blast hole; 11 guide copper sleeve; 12 high pressure hose; 13 lead screw; 14 return spring; 15 outer ring gear; 16 inner gear ring; 17 ventilation holes; ; 20 sealing caps.

Detailed ways

As shown in Figures 3 and 4, it is a clutch for a hot die forging press of the present invention, comprising a large gear 9 and a crankshaft 5, the large gear 9 is rotatably connected to the outer periphery of the end of the crankshaft 5, and the end of the crankshaft 5 is fixedly connected with a friction disc 4. A number of friction blocks 6 are provided at the contact position between the disk surface of the friction disk 4 and the outer end of the large gear 9, and the outer side of the friction disk 4 is provided with a clutch brake structure for axially driving the friction block 6. The clutch brake structure includes: The cylinder 2 and the piston 3 have a conical ring cavity, the axial sliding seal fitting section 1 and the seal fitting section 2 are arranged between the cylinder 2 and the piston 3 on both axial sides of the conical ring cavity, and the sealing fitting section 1 corresponds to The end of the cylinder 2 is fixedly connected with the large gear 9 in the circumferential direction, the piston 3 corresponding to the first sealing and matching section is used to squeeze the clutch friction block 6 laterally, and the end of the cylinder 2 corresponding to the second sealing and matching section is connected with a rotating seat 10, which rotates One end of the seat 10 is fixedly connected with the end of the cylinder 2 by several screws. A buffer cavity 1001 is provided in the rotary seat 10. The other end of the rotary seat 10 corresponding to the buffer cavity 1001 is provided with a central hole, and a bearing seat 19 is fixed in the central hole. In the bearing seat 19, a pipe joint 1 is rotatably connected through the bearing shaft. Seals are provided between the pipe joint 1 and the bearing seat 19 and between the bearing seat 19 and the central hole of the rotary seat 10. The rotary seat 10 is provided with several The radial holes 1002 communicate with the buffer cavity 1001 respectively. The side wall of the cylinder 2 is correspondingly provided with a number of air inlet and outlet holes. The pipe joint enters the conical ring cavity through the buffer cavity 1001 and the high-pressure hose 12 to realize the axial movement of the piston 3 .

In order to ensure the fitting installation between the pipe joint 1, the bearing seat 19 and the rotating seat 10, the outer circumference of the bearing seat 19 is fitted with the central hole of the rotating seat 10, Flange 1, the flange 1 and the rotary seat are fixedly connected by a number of screws, a sealing ring is provided between the bearing seat 19 on the inner side of the flange 1 and the rotary seat 10; the center of the bearing seat 19 is provided with a shaft hole, and the shaft hole two Bearings are respectively installed between the end and the outer circumference of the pipe joint 1, and a sealing cover 20 is arranged between the inner end of the bearing seat 19 and the outer circumference of the pipe joint 1. The circumference is fixed by several screws, and a sealing ring is provided between the inner circumference of the sealing cover 20 and the pipe joint 1 .

In order to facilitate the rapid cooling of the friction block 6, the rotating seat 10 is also provided with a blowing hole 1003 in the circumferential direction, and the blowing hole 1003 is connected with a blower, and the center of the piston 3 corresponding to the center of the rotating seat 10 is provided with a ventilation hole 1003. Port 302, the ventilation port 302 is communicated along the hollow ring between the inner side of the piston 3 and the outer side of the friction disc 4 and blows air to the friction block 6 for cooling; in order to ensure the smooth flow of the blast air, the large gear 9 is also set close to the circumferential direction of the friction block 6. There are a number of ventilation holes 17; in order to prevent the wind, the pipe joint 1 extends out of the bearing seat 19, and the outer periphery of the extension end is provided with a flange ring, and a wind cover 18 is installed between the flange ring and the rotating seat 10, and the wind cover 18 is provided with an air inlet at the position corresponding to the air blowing hole 1003, and the air inlet is used to communicate with the blower. In the friction block blast cooling structure of this embodiment, the blast air flows through the blast hole 1003 and the air vent into the annular space between the piston and the friction disc, and blows directly to the neutral position between the friction blocks 6 and then from the ventilation The hole 17 discharges the other side of the large gear 9, and the airflow is forced to cool the friction block during the neutral process of the friction block, so as to promote the rapid cooling of the friction block 6. It is blown away in time to reduce the wear of the friction block and finally improve the life of the friction block 6 .

In order to limit the axial moving force distance between the piston 3 and the cylinder 2, a guide copper sleeve 11 is provided between the cylinder 2 and the piston 3 corresponding to the second sealing and matching section. The guide copper sleeve 11 is fixedly embedded with the cylinder 2, and the piston 3 It is slidingly matched with the guide copper sleeve 11, the matching section of the piston 3 is provided with a step that is limited and abutted with the guide copper sleeve 11, and a sealing ring is arranged between the outer periphery of the step and the cylinder 2. When the guide copper sleeve 11 abuts, the piston reaches the right limit position, at this time, the clutch is released, and the friction block is in the non-clutch state. When moving, the other end of the piston gradually presses against the friction block 6 to brake the large gear, and the friction block fits with the large gear, thereby transmitting torque through 4, and finally driving the crankshaft to rotate.

In order to improve the structure of the contact part between the piston 3 and the friction block 6, the friction block 6 is provided with an outer gear ring 15 for guiding movement in the outer circumferential direction of the piston 3, and the outer ring gear 15 is provided with an inner gear ring 16 on the outer circumference. The ring gear 15 is axially guided and matched. When the piston 3 moves to the left, it pushes the outer ring gear 15 to move to the left along the guide teeth, so as to squeeze the friction block 6 through the outer ring gear 15, and the inner gear 16 and the cylinder 2 and the large The circumference of the gear 9 is fixed by a number of bolts, the outer ring gear 15 and the cylinder 2 are provided with a number of lead screws 13 in the circumference, the outer ring gear 15 corresponding to the lead screw 13 is provided with a number of screw holes in the circumference, and the cylinder 2 is provided in the circumference direction to facilitate the passage of the lead screw 13 The part of the lead screw 13 protruding from the outside of the cylinder 2 is provided with a return spring 14 and a compression nut, and a washer is arranged between the compression nut and the return spring. When the conical ring cavity is exhausted, the piston 3 moves to the right under the action of the return spring 14, so that the step at the other end of the piston 3 at the sealing and matching section 2 abuts against the guide copper sleeve 11. The braking of the friction block 6 is released, and the large gear 9 can continue to drive the crankshaft 6 to rotate, so as to realize the normal operation of the press.

In the clutch brake structure of the press of the present invention, the air intake structure at the top of the piston 3 is improved to enter the buffer chamber 302 through the pipe joint 1, and then enter the piston 3 through the buffer chamber 302 along the multiple high-pressure hoses 12 arranged outside the cylinder 2. Intake and exhaust are realized in the working cavity of cylinder 2. This external intake channel is convenient to set up multiple intake pipes, increase the speed and flow of intake and exhaust flow, and reduce the braking angle and clutch angle of the clutch. , to improve the sensitivity of clutch and braking, and improve the accuracy of press operation; at the same time, an additional blast channel is added to realize forced cooling of friction block 6 and waste chip blowing, reduce friction block 6 wear and prolong the life of friction block .

Claims (7)

1. A clutch for a hot die forging press, comprising a large gear and a crankshaft, the large gear is rotatably connected to the outer periphery of the end of the crankshaft, the end of the crankshaft is fixedly connected with a friction disk, and the disk surface of the friction disk is connected to the large gear. A number of friction blocks are arranged at the contact part of the outer end in the circumferential direction, and the outer side of the friction disc is provided with a clutch brake structure for axially driving the friction blocks. The clutch brake structure includes a cylinder and a piston with a conical ring cavity, It is characterized in that, between the cylinder and the piston on the two axial sides of the conical ring cavity, there are axially sliding seal matching section 1 and sealing matching section 2, and the cylinder end corresponding to the sealing matching section 1 is circumferentially aligned with the cylinder end. The large gear is fixedly connected, the piston side corresponding to the first sealing and matching section is used to squeeze the brake friction block, and the end of the cylinder corresponding to the second sealing and matching section is connected with a rotating seat, and one end of the rotating seat is circumferentially connected to the side. The ends of the cylinder are fixedly connected, the rotating seat is provided with a buffer cavity, the other end of the rotating seat corresponding to the buffer cavity is provided with a central hole, a bearing seat is fixed in the central hole, and the bearing seat rotates through the bearing shaft A pipe joint is connected, and a sealing member is arranged between the pipe joint and the bearing seat and between the bearing seat and the central hole of the rotating seat, and the rotating seat is provided with a number of radial holes which are respectively communicated with the buffer cavity. A plurality of air inlet and outlet holes are correspondingly arranged on the side wall of the cylinder, and each radial hole is in sealing communication with the air inlet and outlet holes through a high-pressure hose respectively. 2 . The clutch for a hot die forging press according to claim 1 , wherein the outer periphery of the bearing seat is fitted and sleeved with the central hole of the rotating seat, and a sealing member is provided, and the outer periphery of the bearing seat is provided with a seal. 3 . There is a flange that is abutted against the rotating seat, the center of the bearing seat is provided with a shaft hole, the two ends of the shaft hole and the outer circumference of the pipe joint are respectively installed with bearings, and the inner end of the bearing seat and the outer circumference of the pipe joint are respectively installed. A sealing cover is arranged therebetween, the sealing cover is sleeved on the outer circumference of the pipe joint and fixed to the end of the bearing seat by several screws in the circumferential direction, and a sealing ring is arranged between the inner circumference of the sealing cover and the pipe joint. 3 . The clutch for a hot die forging press according to claim 1 , wherein the rotary seat is further provided with a blower hole in the circumferential direction, the blower hole is communicated with a blower, and the piston corresponds to the rotary seat. 4 . The center is provided with a vent communicating with the blowing hole, the vent communicates along the hollow ring between the inner side of the piston and the outer side of the friction disc and blows air to the friction block for cooling. 4 . The clutch for a hot die forging press according to claim 3 , wherein the large gear is further provided with several ventilation holes in the circumferential direction close to the friction block. 5 . 5 . The clutch for a hot die forging press according to claim 3 , wherein the pipe joint protrudes from the outer side of the bearing seat, and the outer periphery of the protruding end is provided with a flange ring, and the flange ring is connected with the rotating An air hood is installed between the seats, and the air hood is provided with an air inlet at a position corresponding to the air blowing hole. 6 . The clutch for a hot die forging press according to claim 1 , wherein a guide copper sleeve is provided between the cylinder and the piston corresponding to the second sealing and matching section, and the guide copper sleeve is fixedly embedded in the cylinder. 7 . The piston is slidably matched with the guide copper sleeve, the matching section of the piston is provided with a step that is limited and abutted with the guide copper sleeve, and a sealing ring is arranged between the outer periphery of the step and the cylinder. 7 . The clutch for a hot die forging press according to claim 1 , wherein the outer circumference of the friction block corresponding to the piston is provided with an outer ring gear for guiding movement, and the outer circumference of the outer ring gear is matched with an inner gear ring. 8 . , the inner gear ring is axially guided and matched with the outer gear ring, the inner gear ring and the circumference of the cylinder and the large gear are fixed by a number of bolts, the outer gear ring and the cylinder are provided with a number of lead screws in the circumference direction, and the lead screws The corresponding outer ring gear is provided with a number of screw holes in the circumferential direction, and the corresponding circumferential direction of the cylinder is provided with through holes for the passage of the lead screw. A washer is provided between it and the return spring.

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