JP5238606B2 - Power transmission mechanism and crushing device - Google Patents

Description

  The present invention relates to a power transmission mechanism and a crushing device.

  Conventionally, a crushing device is composed of a rotary blade fixed around a crushing rotor that rotates around a predetermined axis by the power of a driving machine, and a crushing blade that is arranged facing the rotation axis of the crushing rotor. A processing unit is provided, and the crushing processing unit is configured to crush objects to be crushed, such as electrical appliances, building waste materials, and plastics.

  In such a crushing device, foreign matter of hardness or size that cannot be crushed by the rotary blade and fixed blade of the crushing processing unit may be mixed into the material to be crushed, and when such foreign matter reaches the crushing processing unit, There is a risk that the rotating blade and the fixed blade may be damaged, or an excessive load will be applied to the power transmission mechanism such as a speed change mechanism that transmits power from the driving machine to the crushing rotor and the driving machine, resulting in damage to the power transmission mechanism and the driving machine. .

  In view of this, it is conceivable to provide a torque limiter in the coupling portion that connects the crushing rotor and the power transmission mechanism so as not to transmit an excessive load from the crushing rotor to the power transmission mechanism or the driving machine. For example, a torque limiter in which a first member provided at one end of the rotating shaft of the crushing rotor and a second member provided at the power output shaft of the power transmission mechanism are connected by a plurality of pins is conceivable.

  When the relative rotational torque difference between the output shaft of the power transmission mechanism and the rotation shaft of the crushing rotor exceeds the shear strength of the pin, the torque limiter breaks the pin and crushes from the output shaft of the power transmission mechanism. It is comprised so that power may not be transmitted to the rotating shaft of a rotor.

  By providing such a torque limiter, it is possible to prevent damage to the rotating blade and the fixed blade, the power transmission mechanism, the drive machine, etc. due to the mixing of foreign matter into the object to be crushed. The operation of reconnecting the second member with a new pin is necessary and complicated.

  Further, in Patent Document 1, as shown in FIG. 15, a rotary blade 91 fixed around a crushing rotor 90 that rotates around a predetermined axis by the power of a driving machine, and a crushing target in cooperation with the rotary blade 91. A fixed blade 92 that is supported so that it can rotate around an axis parallel to the axis of the crushing rotor 90 by shearing an object, and the fixed blade 92 is fixed in a state where a limit torque that is arbitrarily set for the fixed blade 92 is not applied. A torque limiter 93 is provided that supports and rotates the receiving blade when the limit torque is applied. If foreign matter that cannot be sheared is caught between the rotating blade 91 and the fixed blade 92, the fixed blade 92 rotates excessively. A crushing device capable of releasing the load has been proposed.

  The torque limiter 93 includes a clutch plate 94 fixed integrally with the fixed blade 92, a clutch plate 95 pressed against the clutch plate 94, a disc spring 96 that presses the clutch plates 94, 95, and a pressure contact force by the disc spring 96. An adjustment nut 97 to be adjusted is configured so that a limit torque for relatively rotating the two clutch plates 94 and 95 can be adjusted by tightening the adjustment nut 97.

  If the limit torque is set to a value that is approximately the same as the maximum torque required for shearing the object to be crushed, in a state where the object to be crushed is sheared by the rotary blade 91 and the fixed blade 92, the fixed blade Since such a load does not exceed the limit torque of the torque limiter 93, the posture of the fixed blade is not destroyed.

  If foreign matter that cannot be sheared between the rotary blade 91 and the fixed blade 92 is sandwiched between them, an excessive load exceeding the limit torque of the torque limiter 93 is applied to the fixed blade 92. It rotates to be pushed and releases its load. At that time, the driving machine is stopped to stop the rotation of the crushing rotor, and damage to the rotary blade 91 and the fixed blade 92 is avoided.

JP 2002-79129 A

  However, in the crushing apparatus as described in Patent Document 1 described above, when a small foreign object that cannot be sheared between the rotary blade 91 and the fixed blade 92 is sandwiched between them, the fixed blade 92 is pushed by the rotary blade 91. However, the operation of restoring the rotated fixed blade 92 to its original posture is necessary and complicated.

  In addition, if the foreign object is a large foreign object, it may remain sandwiched between the rotary blade 91 and the fixed blade 92 even if the fixed blade 92 rotates. At that time, even if the drive machine is stopped, the crushing rotor keeps rotating for a while due to inertia, so an excessive load is applied to the power transmission mechanism between the crushing rotor rotating shaft and the drive machine and the drive machine itself. There was a risk of damage to the mechanism and the drive.

  Therefore, according to Japanese Patent Application No. 2009-84055, the applicant of the present application passes a torque limiter that presses the friction plate and the pressure plate with a predetermined pressure contact force, and the required torque on the power transmission shaft side becomes equal to or greater than the set torque. A power transmission mechanism that suppresses power transmission beyond the set torque from the power transmission shaft to the power transmission shaft and transmits power from the power transmission shaft to the power transmission shaft when the required torque on the power transmission shaft side is less than the setting torque. is suggesting.

  However, if it is necessary to manually rotate the input shaft on the drive side of the transmission incorporated in the power transmission mechanism and rotate the power transmitted shaft for maintenance etc. If the power source of the pressurizing mechanism is shut off, the pressure applied by the pressurizing mechanism may drop, and the friction plate and the pressurizing plate may slip to prevent the power transmission shaft from rotating. There was a problem.

  In view of the above-mentioned problems, the present invention transmits power from a power transmission shaft to a power receiving shaft when the power of the device is cut off while avoiding an excessive load on the speed change mechanism or the driving machine. It is an object of the present invention to provide a power transmission mechanism capable of performing the above and a crushing device to which power is transmitted by the power transmission mechanism.

  In order to achieve the above-mentioned object, the first characteristic configuration of the power transmission mechanism according to the present invention is a transmission mechanism for transmitting power from the drive machine to the driven machine as described in claim 1 of the claims. An annular friction plate and a pressure plate are arranged around the shaft center of the power transmission shaft, and either the friction plate or the pressure plate is rotated by the power transmitted from the power transmission shaft. The other is driven to rotate by the frictional force of both plates and transmits power to the power transmission shaft. When the required torque on the power transmission shaft exceeds the set torque, the friction plate and the pressure plate slide. When the torque is lower than the set torque, the friction plate and the pressure plate rotate together to transmit the power to the power transmission shaft. A torque limiter having a pressing mechanism that applies a predetermined pressing force to the pressure plate and the friction plate in a pressure release state in which the pressure contact force between the plate and the friction plate is released is a transmission mechanism or a transmission mechanism and a driven machine. It is in that it is built in between.

  According to the above configuration, when the torque limiter is incorporated between the speed change mechanism or the speed change mechanism and the driven machine, the friction plate and the pressure plate slide and drive when the required torque on the power transmission side exceeds the set torque. When power transmission over the set torque from the machine to the driven machine is avoided and the required torque on the power transmission side becomes less than the set torque, the friction plate and the pressure plate rotate together to transmit power to the power transmission shaft. Become so.

  Therefore, damage to the speed change mechanism and the drive unit due to an abnormally high load can be avoided. When the required torque on the power transmission side is smaller than the set torque, the friction plate and the pressure plate are pressed against each other by the pressure mechanism, and the power of the driving machine is transmitted to the driven machine.

  In this way, it is possible to automatically switch between driving power transmission or power transmission suppression based only on whether the required torque on the power transmitted shaft side is larger or smaller than the set torque, and complicated recovery Work becomes unnecessary. Furthermore, by changing the pressure contact force between the pressure plate and the friction plate by the pressure mechanism, it is possible to easily adjust the set torque for suppressing the power transmission when the pressure plate and the friction plate slide.

  Furthermore, when it is necessary to rotate the power transmission shaft for maintenance work, etc., even if the pressure contact state between the pressure plate and the friction plate by the pressure mechanism is released, the pressure mechanism and friction plate Since a predetermined pressing force is applied to the plate and the contact state is maintained, the rotation of the power transmission shaft can be transmitted to the power transmitted shaft side.

  In the second characteristic configuration, as described in claim 2, in addition to the first characteristic configuration described above, the predetermined pressing force applied to the pressure plate and the friction plate by the pressing mechanism is based on the pressing mechanism. The pressure is less than the pressure contact force, and is set to be equal to or greater than the minimum pressure contact force necessary for transmitting the power on the power transmission shaft side to the power transmitted shaft side in the pressure release state.

  According to the above-described configuration, the predetermined pressing force applied to the pressure plate and the friction plate by the pressing mechanism is necessary for transmitting the power on the power transmission shaft side to the power transmitted shaft side in the pressure release state. Since the pressure is set to be equal to or greater than the minimum pressure contact force, a relatively small force, for example, a manual rotation force of the power transmission shaft can be reliably transmitted to the power transmitted shaft side.

  In the third feature configuration, as described in claim 3, in addition to the first or second feature configuration described above, an input shaft to which power from the driving machine is transmitted and power to the driven machine are transmitted. The output stage gear is rotatably provided on the output shaft of the speed change mechanism having a gear mechanism for transmitting power from the input shaft to the output shaft, and the friction plate and the pressure plate are connected to the shaft of the output shaft. Power is transmitted from the gear of the output stage to either the friction plate or the pressure plate via the first engagement portion, and the second engagement portion is connected to the support portion that rotates integrally with the output shaft from the other. It is arrange | positioned so that motive power may be transmitted via this, and it exists in the point by which the pressurization mechanism and the press mechanism are provided in the support part.

  According to the above configuration, the power on the power transmission shaft side is arranged so that power is transmitted from the gear of the output stage to the friction plate or pressure plate, and is transmitted from the pressure plate or friction plate to the output shaft. When the required torque on the output shaft side as the power transmission shaft exceeds the torque for driving the gear of the output stage with the pressure plate and the friction plate being in pressure contact with each other, the friction plate and the pressure plate slide. Therefore, it is possible to avoid a possibility that an abnormal load is applied to the gears of the multiple-stage gear mechanism that transmits power from the input shaft to the output shaft and the gears are damaged, or that the load on the drive machine is increased and the drive machine is damaged.

  In addition, when the pressure plate is disengaged from the pressure plate and the friction plate, a predetermined pressure is applied to the pressure plate and the friction plate by the pressure mechanism to maintain the contact state. The rotation of the shaft can be transmitted to the power transmitted shaft side.

  In the fourth feature configuration, as described in claim 4, in addition to the third feature configuration described above, the pressure plate and the friction plate are pressed between the pressure member and the support portion by the pressure mechanism. A pressing mechanism is provided, and the pressing mechanism is configured to apply a predetermined pressing force to the pressing member in a pressure release state in which the pressing force to the pressing member by the pressing mechanism is released. is there.

  A predetermined pressing force is applied to the pressing member by the pressing mechanism in a state where the pressing force to the pressing member by the pressing mechanism is released. Both the pressing mechanism and the pressing mechanism can press or press the pressing plate and the friction plate via a common member called a pressing member, and a simple structure can be realized.

  The fifth characteristic configuration is that, as described in the fifth aspect, in addition to the third or fourth characteristic configuration described above, the pressing mechanism is configured by an elastic body.

  According to the above configuration, since the pressing mechanism is configured by an elastic body, it is possible to absorb variations in pressing force due to dimensional tolerances such as the pressure plate and the friction plate to some extent, and less than the pressure contact force by the pressure mechanism. Thus, it is possible to easily obtain a predetermined pressing force that is equal to or greater than the minimum pressure contact force required to transmit the power on the power transmission shaft side to the power receiving shaft side in the pressure release state.

  In the sixth feature configuration, as described in claim 6, in addition to any of the third to fifth feature configurations described above, the pressing mechanism includes a support portion by a position holding portion formed in the support portion. The position is relatively maintained with respect to.

  According to the above-described configuration, when the friction plate and the pressure plate slip, it is possible to prevent the occurrence of a situation in which the pressing mechanism follows and slides in the circumferential direction. The risk of this can be reduced.

  In the seventh feature configuration, as described in claim 7, in addition to any one of the third to sixth feature configurations described above, the pressing mechanism is changed from the opening formed in the support portion to the pressurizing mechanism. It is inserted so as to be in contact with each other, and is configured to give a predetermined pressing force by the cover of the opening.

  According to the above configuration, the pressing mechanism is inserted so as to contact the pressure mechanism from the opening formed in the support portion, and is configured to apply a predetermined pressing force by the cover of the opening. It becomes possible to finely adjust the pressing force.

  The characteristic configuration of the crushing device according to the present invention is, as described in claim 9 of the claims, a power transmission mechanism including any one of the first to seventh characteristic configurations described above, and a driving machine. The power is transmitted to the rotating shaft of the crushing rotor.

  In the eighth feature configuration, in addition to any one of the third to seventh feature configurations described above, the annular recess formed on the gear side surface of the output stage has a plurality of features. The friction plate and the pressure plate are accommodated alternately, the inner periphery of either the friction plate or the pressure plate and the side wall of the annular recess are engaged by the first engagement portion, and the other is supported. And the second engaging portion.

  A friction plate and a pressure plate that constitute a torque limiter can be arranged in an annular recess formed on the side surface of the gear of the output stage. Furthermore, friction can be achieved by arranging a plurality of friction plates and pressure plates alternately. The pressure contact surface between the plate and the pressure plate can be increased, and the limit torque at which the friction plate and the pressure plate start to slide can be increased even with a relatively small pressure contact force by the pressure mechanism. The same torque as the limit torque due to the pressure contact between the pair of friction plates and the pressure plate can be generated by a plurality of small diameter friction plates and pressure plates, so the torque limiter can be made compact and the speed change mechanism Can be miniaturized.

  According to the above-described configuration, even when a foreign object is caught in the crushing rotor of the crushing device, if an abnormally high load exceeding the power transmitted from the driving machine is generated thereby, the friction plate of the torque limiter and While the pressure plate rotates relatively, the breakage of the blade of the crushing rotor, the drive machine, and the power transmission mechanism from the drive machine to the crushing rotor can be avoided by an abnormally high load. When the power is cut off, the power can be transmitted from the input shaft on the driving machine side to the power receiving shaft.

  As described above, according to the present invention, transmission of power from the power transmission shaft to the power transmission shaft is avoided when the power of the device is interrupted while avoiding an excessive load on the speed change mechanism or the drive machine. It is now possible to provide a power transmission mechanism capable of transmitting power and a crushing device that is powered by the power transmission mechanism.

Schematic of the crushing device according to the invention Side view of the crushing device according to the invention Plan view of the crushing device according to the invention Plan sectional view of the power transmission mechanism according to the present invention Explanatory drawing of the main part of the power transmission mechanism External view of power transmission mechanism according to the present invention Explanatory drawing of hydraulic oil passage and cooling oil passage (A) is explanatory drawing of the control part at the time of normal, (b) is explanatory drawing of the vibration which a vibration sensor detects. (A) is explanatory drawing of the power transmission of the motive power by a torque limiter, (b) is explanatory drawing of the transmission suppression by a torque limiter. (A) is explanatory drawing of the fall of the rotation speed in the predetermined time by the biting of a foreign material, (b) is explanatory drawing of the fall of the rotation speed in the predetermined time by the biting of a high load to be crushed. Illustration of power transmission by pressurization mechanism Illustration of power transmission by pressing mechanism (A) is explanatory drawing of the procedure which incorporates a pressing mechanism, (b) is explanatory drawing of the support part incorporating a pressing mechanism. Explanatory drawing of the press mechanism by another embodiment Illustration of a conventional crusher

Hereinafter, preferred embodiments of a power transmission mechanism, a power transmission control device, and a crushing device to which power is transmitted by the power transmission mechanism according to the present invention will be described.
As shown in FIG. 1 to FIG. 3, the crushing device 1 includes a receiving hopper 2 that inputs an object to be crushed such as electrical appliances, building waste, and plastic, and a crushing process that crushes the object to be crushed that has been input to the receiving hopper 2. The crushing apparatus 1 is provided with a processing unit 10 and a push-in pusher 3 that presses the object to be crushed from the horizontal direction toward the crushing processing unit 10. .

  The pusher pusher 3 is connected to the rear end of the pusher pusher 3 by an arm 3a connected to a piston of a hydraulic cylinder which is expanded and contracted by pressure oil from a hydraulic pump (not shown), and slides on and off the base plate 4. Driven freely.

  The crushing processing unit 10 is disposed below the receiving hopper 2 and has a tip V-shaped rotary blade 6 fixed to a groove formed in the circumferential direction on the peripheral surface of the crushing rotor 5 that rotates around a predetermined axis. The crushing rotor 5 includes a tip V-shaped fixed blade 7 which is opposed to the rotation axis 5c of the crushing rotor 5 and meshes with the rotary blade 6 to shear and crush the object to be crushed.

  A large number of V-shaped grooves 5v parallel to each other at a predetermined pitch are formed in the peripheral portion of the crushing rotor 5, and the blade body 6a is bolted to each of the plurality of mounting seats 6b formed in the grooves 5v. It is fastened. Each rotary blade 6 is arranged in a zigzag shape when those provided in adjacent grooves 5v are connected to each other at the apex thereof. The fixed blade 7 has a tip V-shaped blade body 7 a fastened with a bolt to a mounting seat 7 b provided at the end of the base 4 along the axial direction of the crushing rotor 5.

  In the lower part of the crushing processing unit 10, a screen mechanism 8 for selectively passing the object to be crushed to a predetermined size or less by the rotary blade 6 and the fixed blade 7, and a discharge for receiving the object to be crushed that has passed the screen mechanism 8. A hopper 9 is provided.

  The screen mechanism 8 is formed of a punching metal that is curved in an arc along the rotation trajectory of the rotary blade 6 and has a large number of openings. Of the objects to be crushed by the crushing processing unit 10, The object to be crushed smaller than the opening falls from the opening and is accommodated in the discharge hopper 9, and what does not pass through the opening is crushed again by the rotary blade 6 and the fixed blade 7.

  An electric motor M as a driving machine is fixed to a gantry below the crushing device 1, and a speed reduction mechanism 30 as a speed change mechanism is fixed to a mounting gantry 12 a as an example of a support body assembled to one side 11 a of the main body frame 11. . The pulley 13 attached to the output shaft of the motor M and the pulley 15 attached to the input shaft 31 of the speed reduction mechanism 30 are connected by the V belt 14, and the power of the motor M is shifted to a predetermined rotational speed by the speed reduction mechanism 30. Then, it is configured to be output from the output shaft 37 and transmitted to the rotating shaft 5c of the crushing rotor 5 as a driven machine.

  Note that the output shaft of the motor M and the input shaft 31 of the speed reduction mechanism 30 may be coupled by coupling instead of being coupled by the V belt 14 via the pulleys 13 and 15.

  As shown in FIG. 4, the speed reduction mechanism 30 transmits power from the input shaft 31 to which power from the motor M is transmitted, an output shaft 37 that transmits power to the crushing rotor 5, and power from the input shaft 31 to the output shaft 37. A power transmission mechanism is configured by including a plurality of gear mechanisms and a torque limiter 20.

  The multi-stage gear mechanism includes a first gear 32 formed on the peripheral surface of the input shaft 31, a second gear 33 meshing with the first gear 32, a rotating shaft 34 inserted through the second gear 33, A third gear 35 formed on the peripheral surface of the rotating shaft 34 and a fourth gear 36 that meshes with the third gear 35 are configured. The fourth gear 36 is formed with an opening in the center and is fitted into the output shaft 37 via a bearing 38.

  The input shaft 31 is supported by bearings 40 and 41 fixed to the inner wall of the casing 39, both ends of the rotating shaft 34 are supported by bearings 42 and 43, and both ends of the output shaft 37 are supported by bearings 44 and 45. . A vibration sensor 101 is installed in the bearing 45 at an appropriate position where the vibration of the output shaft 37 can be detected.

  In the torque limiter 20, friction materials are attached to both surfaces, and an annular friction plate 21 that rotates with transmission power from the rotating shaft 34, and an annular pressurization that transmits power to the output shaft 37 with frictional force between the friction plates 21. The plate 22 is arranged around the shaft center of the output shaft 37, and the friction plate 21 and the pressure plate 22 slide when the required torque on the output shaft 37 side is equal to or higher than the set torque. The pressure plate 22 is configured to include a pressure mechanism 26 that presses the pressure plate 22 against the friction plate 21 so that the pressure plate 22 rotates integrally to transmit power to the output shaft 37. In the present embodiment, the rotating shaft 34 is a power transmission shaft, and the output shaft 37 is a power transmitted shaft.

  More specifically, as shown in FIG. 5, an annular surface that can accommodate a plurality of friction plates 21, a pressure plate 22, and a support portion 23 of the pressure plate on one side surface of the fourth gear 36 that is an output stage gear. A concave portion 36 a is formed, and the support portion 23 includes a stopper 25 that holds the plurality of pressure plates 22 and the friction plates 21 in an alternately aligned state, and the friction plates 21 and the pressure plates 22 with respect to the axis of the output shaft 37. A pressurizing mechanism 26 that presses in a direction parallel to the pressure is provided.

  The tooth portion 21a formed on the inner peripheral side of the friction plate 21 and the groove portion 36b formed on the side wall of the annular recess are spline-coupled so that the friction plate 21 cannot rotate relative to the fourth gear 36 and the shaft of the output shaft 37 It can move in the direction of the heart. That is, the first engaging portion is constituted by the tooth portion 21a and the groove portion 36b. The first engagement portion is not limited to the spline connection, and may be a key structure in which the key groove and the key are engaged.

  The tooth portion 22a formed on the outer peripheral side of the pressure plate 22 and the groove portion 23a formed on the side wall of the support portion 23 are spline-coupled, so that the pressure plate 22 cannot rotate relative to the support portion 23 and is output shaft 37. It is possible to move in the axial direction. That is, the tooth portion 22a and the groove portion 23a constitute a second engagement portion. The second engagement portion is not limited to the spline connection, and may be a key structure in which the key groove and the key are engaged.

  Further, the support portion 23 is formed with an opening in which the output shaft 37 can be inserted in the center, and the groove portion 37c formed around the output shaft 37 and the groove portion 23c formed on the inner periphery of the support portion are engaged with each other. And is configured to rotate.

  The pressurizing mechanism 26 includes an annular cylinder portion formed in the support portion 23, and an annular piston 26a and a piston 26a disposed in the cylinder portion and movable in a direction parallel to the axis of the output shaft 37 in the axial direction. And a hydraulic chamber 26b for injecting hydraulic oil to be operated. That is, the piston 26a serves as a pressure member that presses the pressure plate and the friction plate.

  A groove is provided on the peripheral surface of the piston 26a along the peripheral surface, and seal members 26c and 26d are inserted into the groove. The hydraulic chamber 26b is kept oil tight by these seal members 26c and 26d.

  The output shaft 37 is formed in a cylindrical shape in which the rotating shaft 5c of the crushing rotor 5 can be fitted at the center, and a hydraulic oil passage 37a for supplying hydraulic oil to the hydraulic chamber 26b of the pressurizing mechanism 26 is an axial center on the periphery. It is formed along the direction parallel to. Hydraulic oil is supplied from the outside of the torque limiter 20 through the hydraulic oil passage 37a into the hydraulic chamber 26b, and the pressure plate 22 and the friction plate 21 are moved by moving the piston 26a in a direction parallel to the axis of the output shaft 37. It will be pressed.

  Further, the output shaft 37 is formed with a cooling oil passage 37b for supplying cooling oil to the joint portion between the friction plate 21 and the pressure plate 22 from the gap 27 between the inner side wall of the annular recess 36a and the support portion 23. The supplied cooling oil is configured to leak into the casing 39 from the outer peripheral edges of the friction plate 21 and the pressure plate 22.

  The hydraulic oil and the cooling oil are respectively supplied from oil supply ports 37 d and 37 e provided in the casing 39. Since the output shaft 37 rotates relative to the casing 39, in order to supply the working oil and the cooling oil to the working oil passage 37a and the cooling oil passage 37b, the oil supply grooves 37f and 37g are provided over the entire circumference of the output shaft 37. Is formed. The hydraulic oil and cooling oil supplied from the supply ports 37d and 37e are supplied to the hydraulic oil passage 37a and the cooling oil passage 37b from the oil supply grooves 37f and 37g, respectively.

  As shown in FIG. 7, the cooling oil is supplied by circulating the cooling oil accumulated in the casing 39 by the oil pump 60. The hydraulic oil is supplied through a supply pipe 47 branched from a pressure oil supply pipe 51 that causes the hydraulic cylinder 3 b of the push-in pusher 3 to advance and retreat by the hydraulic pump 52. By providing the pressure reducing valve 50 in the hydraulic oil supply piping 47 and changing the hydraulic oil supply pressure to the pressurizing mechanism 26, the pressure contact force between the pressure plate 22 and the friction plate 21 can be easily changed. The supply pipes 47 and 51 are appropriately provided with a relief valve and a sequence valve (not shown).

  By the way, when exchanging the blade body 6a of the rotary blade 6 of the crushing rotor 5, it is necessary to rotate the crushing rotor 5. However, since the crushing rotor 5 is heavy, it is difficult to directly rotate it manually. is there.

  Therefore, the input shaft 31 that is the power transmission shaft is manually rotated, and the output shaft 37 that is the power transmission shaft is rotated using the gear mechanism provided in the power transmission mechanism, that is, the crushing rotor with a small force. It is conceivable to rotate the motor 5, but during such replacement work, for the sake of safety, the hydraulic oil is supplied to the hydraulic cylinder 3 b of the pusher pusher 3, the hydraulic oil is supplied to the torque limiter 20, and the motor M is supplied. The power supply is stopped.

  Then, the pressurization mechanism 26 of the torque limiter 20 enters a pressure release state in which the friction plate 21 and the pressurization plate 22 are not pressurized with a predetermined pressure contact force. In such a pressure release state, the input shaft 31 is rotated. However, the friction plate 21 and the pressure plate 22 slip, and the output shaft 37 does not rotate and the crushing rotor 5 cannot be rotated.

  Therefore, as shown in FIGS. 11 and 12, the torque limiter 20 is in a state in which the pressure contact force 28 between the pressure plate 22 and the friction plate 21 by the pressure mechanism 26 is released, and the torque limiter 20 is in friction with the pressure plate 22. A pressing mechanism 80 that applies a predetermined pressing force 81 to the plate 21 is provided.

  The predetermined pressing force 81 applied to the pressure plate 22 and the friction plate 21 by the pressing mechanism 80 is less than the pressing force 28 by the pressing mechanism 26, and the power on the power transmission shaft 31 side is driven by the pressure release state. It is set to be equal to or greater than the minimum pressure contact force required for transmission to the transmitted shaft 37 side. It is set to a pressure contact force that can transmit torque applied to the input shaft to the driven-side output shaft when the drive-unit-side input shaft is manually rotated.

  Therefore, even when the pressure is released, the friction plate 21 and the pressure plate 22 are kept in contact with each other and an appropriate frictional force is applied. When the input shaft 31 of the speed reduction mechanism 30 is manually rotated, the input is performed. The rotation of the shaft 31 is transmitted to the output shaft 37, and the crushing rotor 5 can be easily rotated.

  Specifically, the pressing mechanism 80 is positioned between the pressurizing mechanism 26 and the support portion 23, and the position thereof is held relative to the support portion 23 by a position holding portion 23 d formed on the support portion 23. The pressure mechanism 26 is composed of an elastic body that presses the piston 26 a toward the pressure plate 22 and the friction plate 21. The position holding part is not limited to being formed on the support part, but may be formed on the piston.

  A procedure for incorporating the pressing mechanism 80 into the support portion 23 will be described with reference to FIGS. The members such as the bolt 25a, the support portion 23 other than the pressing mechanism 80, the friction plate 21, and the pressure plate 22 shown in FIGS. Only the cross section of the part is shown.

  As shown in FIG. 13 (a), the support portion 23 can insert a part of the pressing mechanism 80 into the bottom portion of the cylinder portion where the annular piston 26a constituting the pressurizing mechanism 26 is arranged, A plurality of counterbore as a position holding portion 23d that holds the relative position of the portion 23 and the pressing mechanism 80 are formed on a concentric circle.

  First, the pressing mechanism 80 is inserted into each of the plurality of position holding portions 23d formed on the support portion 23, and then the piston 26a is disposed so as to contact the pressing mechanism 80, and the pressure plate 22 and the friction plate 21 are moved. A predetermined number of sheets are alternately arranged.

  At this time, the tooth portion 22a formed on the outer peripheral side of the pressure plate 22 and the groove portion 23a formed on the side wall of the support portion 23 are spline-coupled so that the pressure plate 22 cannot be rotated relative to the support portion 23. Become.

  On the other hand, although the friction plate 21 is movable in the circumferential direction, the tooth portion 21a and the fourth gear formed on the inner peripheral portion of the friction plate 21 when the support portion 23 is fitted into the output shaft 37 later. Assembling while aligning the positions of the respective tooth portions 21a of the respective friction plates 21 in the circumferential direction by using a positioning jig (not shown) so that the groove portions 36b formed on the side walls of the 36 annular recesses can be smoothly coupled. .

  As shown in FIG. 13B, after a predetermined number of pressure plates 22 and friction plates 21 are arranged on the support portion 23, the stopper 25 is fixed to the support portion 23 with bolts 25a. As a result, a predetermined pressing force 81 is generated by the pressing mechanism 80 on the pressure plate 22 and the friction plate 21. In this state, it is difficult to relatively rotate the tooth portion 21a of the friction plate 21 in the circumferential direction, and it is difficult to couple the tooth portion 21a to the groove portion 36b of the fourth gear 36. Therefore, a positioning jig is used. It is.

  The pressing mechanism 80 is preferably an elastic body such as a coiled compression spring. The elastic body is not limited to a coiled compression spring, but may be a disc spring, a leaf spring, or other known springs, but those having a small spring constant are preferable.

  For example, when 10 friction plates and 10 pressure plates are alternately stacked, even if the dimensional tolerance between the friction plate 21 and the pressure plate 22 is ± 0.1 mm, the maximum is +2 mm when the total 20 plates are stacked. -2mm and a total error of 4mm may occur.

  Even in such a case, by configuring the pressing mechanism 80 with an elastic body such as a compression spring, the pressing force is less than the pressing force by the pressing mechanism 26 regardless of the dimensional tolerance between the friction plate and the pressing plate, This is because it is easy to achieve a predetermined pressing force that is equal to or greater than the minimum pressure contact force required to transmit the power on the power transmission shaft 31 side to the power transmitted shaft 37 side in the released state.

  In the above-described embodiment, a portion of the pressing mechanism 80 can be inserted into the bottom of the cylinder portion of the support portion 23, and the position holding portion 23d that holds the relative position of the support portion 23 and the pressing mechanism 80. As described above, the structure in which the piston 26a constituting the pressurizing mechanism 26 is disposed after the pressing mechanism 80 is inserted into the support portion 23 has been described. A time-consuming assembly operation using a positioning jig is required.

  Therefore, as shown in FIG. 14, the piston 26a, the plurality of pressure plates 22 and the friction plate 21 are arranged in this order on the support portion 23 in which the opening 23e is formed, and the stopper 25 is fixed. 80 may be inserted and the cover lid 23f may be fixed with bolts 23g.

  In this case, at the stage where the pressure plate 22 and the friction plate 21 are assembled in the support portion 23 and the stopper 25 is fixed, no pressing force is applied to the pressure plate 22 and the friction plate 21. 21a can be easily moved in the circumferential direction.

  In this state, the support portion 23 is fitted into the output shaft 37, the groove portion 36b formed in the side wall of the annular recess of the fourth gear 36 and the tooth portion 21a of the friction plate 21 are coupled, and then the pressing mechanism is opened from the opening 23e. 80 is inserted and the cover 23f is fixed with the bolt 23g.

  If comprised in this way, it is not necessary to use the jig for positioning, and the assembly operation | work of the torque limiter incorporating the press mechanism can be advanced very smoothly.

  Further, even after the pressure plate 22 and the friction plate 21 are incorporated into the support portion 23, fine adjustment of the pressing force 81 can be easily performed by sandwiching a shim between the cover lid 23f and the pressing mechanism 80.

  Further, with this configuration, the position holding function of the pressing mechanism 80 can be realized by the opening 23e formed in the support portion 23, and the pressing mechanism 80 can be stably held in position.

  In FIG. 13, a protrusion is formed in a portion of the cover lid 23 f that comes into contact with the pressing mechanism 80 so that the protrusion amount can be adjusted. If there is a spring, there is no need to provide a protrusion or sandwich a shim.

  In the above-described embodiment, the case where the elastic body constituting the pressing mechanism is a spring has been described. However, the elastic body is not limited to a spring but may be an elastomer, a resin, or the like. In this case as well, a material having an appropriate elastic modulus may be adopted in consideration of dimensional tolerances such as a friction plate and a pressure plate.

  The pressing mechanism is not limited to an elastic body and may be a rigid body. For example, a bolt or the like that mechanically pressurizes the piston 26a to press the friction plate and the pressure plate may be screwed to the inner wall of the support portion 23, or a columnar rigid body is fitted to the counterbore as the position holding portion 23d. May be included.

  Further, the pressing mechanism is constituted by a separate hydraulic mechanism driven by a battery or the like, the piston 26a is pressurized with pressure oil supplied from the separate hydraulic mechanism, and the friction plate and the pressure plate are pressurized. The pressure contact force may be less than the minimum pressure contact force and greater than the minimum pressure contact force.

  Furthermore, you may provide the press mechanism mentioned above between the pressure plate 22 and the piston 26a which pressurizes the friction plate 21, and the plate which opposes the piston 26a. For example, a counterbore can be formed by forming a counterbore on the pressure surface of the piston 26a, a spring held by the counterbore, and pressing the plate by the spring.

  As shown in FIG. 6, the casing 39 is formed such that the upper edge portion 39a and the lower edge portion 39b are symmetrical with respect to the center line CL, and the interval gradually decreases from the one end side 39c to the other end side 39d. On the center line CL, the axis of the first gear 32 in the input stage, that is, the axis of the input shaft 31, the axis of the rotary shaft 34, and the axis of the fourth gear 36 in the output stage, that is, the output shaft 37. It is comprised by the shape in which an axial center is located.

  One end side 39c and the other end side 39d of the casing 39 are formed so as to be connected to the inner side from the end portions of the upper edge portion 39a and the lower edge portion 39b with convex curved surfaces directed outward. An attachment portion 46 for attaching the speed reduction mechanism 30 to the attachment base 12a is formed in the vicinity of the end portion of the edge portion 39b, and a bolt hole is formed in the attachment portion 46.

  As shown in FIG. 7, an oil pump 60 is provided outside the casing 39, and the cooling oil leaked and accumulated in the casing 39 by the oil pump 60 is sucked from a discharge port formed on the side surface of the casing 39, and an oil supply pipe 48 is provided. The friction plate 21 and the pressure plate 22 are cooled by being circulated and supplied to the oil supply port 37e.

  The oil pump is not necessarily fixed to the casing 39, but a trochoid pump using a rotation of the input shaft 31 as a power source and a plunger pump are preferable from the viewpoint of reducing the power cost.

  When employing a trochoid pump, the inner gear fixed to the input shaft 31 and the inside of the outer rotor may be rotated to repeat the suction and discharge processes. When employing a plunger pump, What is necessary is just to comprise so that the process of suction | inhalation and discharge may be repeated by the relative rotation of the cam fixed to the input shaft 31, and the casing 39. FIG. In any case, it is only necessary that the oil accumulated in the casing 39 is circulated through the cooling oil passage 37 b as cooling oil and supplied to the joint between the friction plate 21 and the pressure plate 22.

  The oil discharge port in the casing 39 may be provided at an appropriate position on the side surface of the casing 39, and the oil supply pipe 48 from the suction port to the cooling oil passage 37b is appropriately provided with a filter, a cooler, a check valve, and the like. The power source of the oil pump 60 is not limited to the input shaft 31 and may be the rotating shaft 34 or the output shaft 37. The cooling oil is also used as a lubricating oil for the gear mechanism. Further, it is preferable that the casing 39 is provided with an overflow pipe 49 so that the cooling oil accumulated inside is discharged at a predetermined liquid level.

  One end side of the rotating shaft 5c of the crushing rotor 5 is fitted to the output shaft 37 of the speed reduction mechanism 30, and the other end side is supported by the bearing 16 attached to the mounting base 12b assembled to the other side portion of the main body frame 11. . A vibration sensor 102 is installed on the bearing 16 at an appropriate position where vibration of the rotating shaft 5c of the crushing rotor 5 can be detected.

  Thus, by fixing the speed reduction mechanism 30 to the mounting base 12a, it is not necessary to separately provide a support for the speed reduction mechanism 30, and the installation space is reduced, and the output shaft 37 of the speed reduction mechanism 30 and the crushing rotor 5 can be reduced. Positioning of the rotary shaft 5c can be easily performed. Moreover, since one end side of the rotating shaft 5c of the crushing rotor 5 is fitted to the output shaft 37 and the rotating shaft 5c can be supported by the bearing 45 of the speed reduction mechanism 30, the number of parts can be reduced by reducing the number of bearings. I can plan.

  Since the speed reduction mechanism 30 has a symmetrical shape on the upper edge 39a side and the lower edge 39b side with respect to the center line CL, the speed reduction mechanism 30 is rotated 180 degrees around the center line CL, and is attached to the mounting base 12a with the upper edge 39a as the bottom surface. Therefore, it can be provided on any side portion of the main body frame 11.

  The output shaft 37 is configured by a hollow shaft that fits and supports the rotating shaft 5c of the crushing rotor 5, and a key groove 37h formed in the hollow portion of the output shaft 37 and a key groove formed at the end of the rotating shaft 5c. It is configured to be key-linked.

  As shown in FIG. 8A, the control panel is provided with a control unit 100. Based on the signals input from the start switch S1 and the stop switch S2, the control unit 100 starts and stops the electric motor M, starts and stops the hydraulic pump 52 that supplies hydraulic oil to the supply pipes 47 and 51, Based on the inputs of the forward switch S3 and the reverse switch S4 provided in the hydraulic cylinder 3b, the direction switching valve 53 is controlled to control the forward and backward movement of the pusher pusher 3.

  A signal from the filter unit 103 is input to the control unit 100. The filter unit 103 includes a differential filter that extracts only high-frequency components from the vibrations of the output shaft 37 and the rotating shaft 5 c of the crushing rotor 5 detected by the vibration sensors 101 and 102. Output signals of the vibration sensors 101 and 102 are input to the filter unit 103. As illustrated in FIG. 8B, the filter unit 103 extracts the high frequency component 55 from the outputs from the vibration sensors 101 and 102 and outputs the high frequency component 55 to the control unit 100. In the present embodiment, the vibration sensors 101 and 102 and the filter unit 103 serve as a state detection unit.

  The control unit 100 is configured to determine that the torque limiter 20 is activated when the high frequency component extracted by the filter unit 103 exceeds a predetermined threshold value set in advance.

  The slip between the friction plate and the pressure plate of the torque limiter generated when the rotary blade 6 and the fixed blade 7 bite foreign matter is, for example, a few tens of milliseconds, and when the foreign matter bite state is resolved, the torque limiter It automatically returns to the power transmission state. However, if there is a large foreign object or a plurality of foreign objects, the foreign object may be caught many times and the rotary blade 6 and the fixed blade 7 may be damaged.

  In addition, the required torque on the power transmission side exceeds the set torque for a moment when a foreign object is caught between the rotary blade 6 and the fixed blade 7, but then the foreign object is caught between the rotary blade and the fixed blade. Even if the crushing rotor stops rotating in a state, if the required torque on the power transmission side becomes less than the set torque, the torque limiter automatically returns to the power transmission state and the drive machine and transmission mechanism are damaged. There is also a risk.

  Even in such a case, when the control unit 100 determines that the torque limiter 20 has been operated based on a signal from the state detection unit that detects the operation of the torque limiter 20, the control unit 100 stops the electric motor M, so The power supply is stopped, and the rotary blade 6 and the fixed blade 7 can be prevented from being damaged.

  The control unit 100 does not need to stop the electric motor M every time it determines that the torque limiter 20 has been activated. Even if it is a hard foreign object, it can be crushed by the rotary blade 6 and the fixed blade 7, or if it is a small foreign object, it passes through the gap between the rotary blade 6 and the fixed blade 7 and falls to the screen mechanism 8, so the torque within a predetermined time The motor M may be controlled to stop when the limiter operation count exceeds the set count. For example, when it is determined that the torque limiter 20 has been operated five times or more in 5 seconds, the electric motor M is stopped.

  As shown in FIG. 7, the cooling oil is supplied by circulating the cooling oil accumulated in the casing 39 by the oil pump 60. The hydraulic oil may be supplied by being branched from a hydraulic oil supply pipe 51 that causes the hydraulic cylinder 3 b of the pusher pusher 3 to advance and retreat by the hydraulic pump 52.

  By providing the pressure reducing valve 50 in the hydraulic oil supply piping 47 and changing the hydraulic oil supply pressure to the pressurizing mechanism 26, the pressure contact force between the pressure plate 22 and the friction plate 21 can be easily changed. The supply pipes 47 and 51 are appropriately provided with a relief valve and a sequence valve (not shown).

  The operation of the crushing apparatus 1 will be described with reference to FIGS. 7, 8 (a), and 9 (a). When the start switch S <b> 1 provided on the control panel is pressed, the control unit 100 starts the hydraulic pump 52 to supply hydraulic oil to the pressurizing mechanism 26 of the torque limiter 20 and rotates the crushing rotor 5. Start M. When the stop switch S2 is pressed, the direction switching valve 53 is controlled to move the pusher pusher 3 to the retracted position, the electric motor M is stopped, and hydraulic oil is supplied to the pressurizing mechanism 26 of the torque limiter 20. Stop.

  When the hydraulic pump 52 is activated, the control unit 100 supplies hydraulic oil to the supply pipe 51 and operates the pusher pusher 3. When the forward limit switch S3 and the backward limit switch S4 provided in the hydraulic cylinder 3b are pressed, the direction switching valve 53 is controlled to switch the operating direction of the hydraulic cylinder 3b.

  The power of the motor M is input to the input shaft 31 of the speed reduction mechanism 30 and transmitted to the fourth gear 36 and the friction plate 21 of the output stage via the gear mechanism, and is pressed against the friction plate 21 by the pressurizing mechanism 26 at a predetermined pressure. Is transmitted to the pressure plate 22 and output from the output shaft 37, and the crushing rotor 5 rotates.

  Torque required to rotate the crushing rotor 5 as shown in FIG. 9 (b) when the crushing processing unit 10 is bitten by a foreign object having a hardness or size that cannot be crushed by the rotary blade 6 and the fixed blade 7. May increase momentarily and become larger than the torque for rotating the fourth gear 36.

  As described above, when the required torque of the output shaft 37 becomes equal to or larger than the torque limiter set torque set to a value larger than the output torque of the electric motor M, the friction plate 21 and the pressure plate 22 slip. As described above, when the required torque of the output shaft 37 becomes equal to or higher than the set torque, the friction plate 21 and the pressure plate 22 slide relative to each other, and damage to each gear of the speed reduction mechanism 30 can be avoided.

  The set torque is set to a value corresponding to an impact force that is transiently generated when foreign matter is caught in the crushing processing unit 10, and is set to, for example, 3 to 4 times the output torque of the electric motor M.

  When the state in which foreign matter is caught in the crushing processing unit 10 continues, the torque is lowered to a torque lower than the transiently generated impact force, so that the sliding state of the friction plate 21 and the pressure plate 22 is eliminated, and the friction plate 21 A situation in which the pressure plate 22 is burned is avoided.

  When the control unit 100 detects that the vibration of the vibration sensors 101 and 102 detected by the filter unit 103 exceeds a predetermined threshold value set in advance, the control unit 100 determines that the torque limiter 20 is activated and is incorporated in the pusher pusher 3. The supply of hydraulic oil to the hydraulic cylinder 3b and the electric motor M are stopped.

  If the rotary blade 6 and the fixed blade 7 are bitten and the rotation of the crushing rotor 5 stops, the required torque of the output shaft 37 becomes less than the torque limiter set torque, and the friction plate 21 and the pressure plate 22 slip. Even if the motor does not occur, the electric motor M is stopped by the control unit 100, so that it is possible to avoid the subsequent damage to the rotary blade 6 and the fixed blade 7 and the damage to each gear of the electric motor M and the speed reduction mechanism 30. .

  As described above, if the torque limiter is incorporated between the speed change mechanism or the speed change mechanism and the driven machine, and the torque required to rotate the power transmission side is equal to or greater than the set torque, the friction plate and the pressure plate Slipping, it is possible to suppress the transmission of power beyond the set torque from the drive machine to the driven machine.

As described above, since the power transmission suppression and transmission of the driving machine can be automatically switched only by the magnitude of the required torque on the power transmitted shaft side with respect to the set torque, the restoration work becomes unnecessary. Furthermore, by changing the pressure contact force between the pressure plate and the friction plate by the pressure mechanism, the set torque when the pressure plate and the friction plate slide can be easily adjusted.

  The vibration sensor only needs to be able to detect the vibration of the output shaft of the speed reduction mechanism 30 that is a speed change mechanism or the rotation shaft of the driven machine connected to the output shaft, and either one of the bearing portions of the output shaft 37 of the speed reduction mechanism 30. Alternatively, it can be attached near the output shaft of the speed reduction mechanism 30.

  In the above-described embodiment, a control device is provided that includes a state detection unit configured by a vibration sensor and a filter unit, and a control unit that determines that the torque limiter is activated when the output of the filter unit exceeds a predetermined threshold. However, the present invention is not limited to one using a vibration sensor for the state detection unit.

  For example, the state is detected by a torque sensor (strain gauge type) attached to the output shaft of the speed change mechanism or the rotation shaft of the driven machine connected to the output shaft, and a filter unit (differential filter) that extracts high-frequency components from the output of the torque sensor You may comprise a part. Also in this case, the control unit determines that the torque limiter is activated when the output of the filter unit exceeds a predetermined threshold value.

  Further, the state detection unit may be configured by an encoder that detects the rotational speeds of the input shaft and the output shaft of the speed change mechanism. Based on the output of the encoder, the control unit determines that the torque limiter has been activated when the ratio between the rotational speeds of the input shaft and the output shaft within a predetermined time exceeds a predetermined threshold.

  For example, the rotation speed Na (rpm) of the input shaft and the rotation speed Nb (rpm) of the output shaft detected by the encoder within a predetermined time are not slipped on the friction plate and the pressure plate of the torque limiter. In the case of, it shows the same value. However, when the rotary blade and the fixed blade bite foreign matter, the input shaft, the rotational speed Na (rpm), and the output shaft rotational speed Nb (rpm) are slightly shifted or uneven rotation occurs. The control unit determines that the torque limiter is activated when the absolute value of the ratio Na / Nb or the difference (Na−Nb) between the rotational speeds of the input shaft and the output shaft within a predetermined time exceeds a predetermined threshold value.

  Furthermore, the state detection unit may be configured by an encoder that detects the rotation speed of the output shaft of the transmission mechanism. The control unit determines that the torque limiter is activated based on the output of the encoder when the rate of decrease in the rotation speed of the output shaft exceeds a predetermined threshold within a predetermined time.

  For example, when the rotary blade and the fixed blade bite foreign matter, the required torque on the power transmission shaft side on the driven machine side instantaneously exceeds the set torque and the torque limiter operates. At this time, as shown in FIG. 10A, the output of the encoder is reduced by Nc (rpm) at a predetermined time t (sec). If the rotation speed reduction rate Nc / t at this time exceeds a predetermined threshold value, it is determined that the torque limiter has been activated.

  However, in the case of an object to be crushed, such as a bundle of magazines, the rotational speed of the output shaft decreases by Nd (rpm) at a predetermined time t (sec) as shown in FIG. The required torque on the driven gear side on the driven machine side does not exceed the set torque, and the torque limiter does not operate.

  Thus, based on the output of the encoder, if the rate of decrease in the output shaft rotation speed exceeds a predetermined threshold within a predetermined time, it can be determined that the output shaft rotation speed is decreased due to the biting of foreign matter, It is possible to reliably detect that the torque limiter has been activated.

  The specific configuration of the encoder is not particularly limited, and is configured with a gear attached to the shaft end and a laser sensor that detects gear teeth, a gear attached to the shaft end, and gear teeth. What is necessary is just to convert the rotation of a rotating shaft into a pulse signal and to detect it, such as an electromagnetic pickup sensor that detects the above.

  Regardless of which state detection unit described above is used, the control unit detects not only the operation of the torque limiter and controls the electric motor M to stop, but also a foreign object between the rotary blade and the fixed blade. The electric motor M may be controlled to be stopped by detecting that the rotation of the crushing rotor has stopped in a state where the electric motor M is bitten.

  When a vibration sensor or a torque sensor is used, the lower limit threshold value of the sensor output is appropriately set, and the control unit may determine that the rotation of the crushing rotor has stopped when the sensor output is equal to or lower than the lower limit threshold value.

  Even when the encoder is used, the control unit may determine that the rotation of the crushing rotor has stopped by detecting that the sensor output is equal to or lower than the lower limit threshold value, or that the rotation of the input shaft or the output shaft has stopped. .

  Furthermore, it is preferable that the determination of the rotation stop of the crushing rotor by the control unit is performed within a predetermined time (for example, several seconds) after detecting the operation of the torque limiter.

  Even when the crushing rotor stops rotating due to foreign matter biting, the required torque on the power transmission side becomes less than the set torque and the torque limiter automatically returns to the power transmission state, the electric motor M or Breakage of the speed reduction mechanism 30 can be avoided reliably.

  In the embodiment described above, the bearing 38 between the fourth gear 36 and the output shaft 37 has not been described in detail, but the friction plate 21 and the pressure plate 22 of the torque limiter 20 are caused by foreign matter or the like being caught in the crushing rotor 5. When the relative rotation occurs between the first gear 36 and the fourth gear 36, the fourth gear 36 and the output shaft 37 also rotate relative to each other. Therefore, an appropriate sliding bearing or rolling bearing is used from the viewpoint of cost and durability. For example, a solid lubricant dispersion type sintered multilayer bearing can be suitably used.

  In the above-described embodiment, the first gear 32 and the third gear 35 are configured such that teeth are formed on the peripheral portion of the rotation shaft, but may be inserted through the respective rotation shafts. The number of gears included in the speed reduction mechanism 30 is not limited to this.

  In the above-described embodiment, the pressure plate provided on the output shaft side is provided on the gear side of the output stage, and the pressure plate is pressed against the friction plate with the friction material pasted on both sides by the pressurization mechanism. The configuration in which power is transmitted from the gear of the stage to the friction plate and power is transmitted from the pressure plate to the output shaft has been described, but the pressure plate provided on the gear side of the output stage is provided on the output shaft side, It is possible to transmit power from the gear of the output stage to the pressurizing plate and to transmit power from the friction plate to the output shaft by press-contacting the friction plate to which the friction material is attached. Good.

  That is, in the torque limiter, the annular friction plate and the pressure plate are arranged around the axis of the power transmission shaft, and either the friction plate or the pressure plate is rotationally driven by the transmission power from the power transmission shaft, The other is driven to rotate by the frictional force of both plates to transmit power to the power-transmitted shaft. When the required torque on the power-transmitted shaft exceeds the set torque, the friction plate and the pressure plate slide, and the set torque When the pressure is less than the pressure plate, the pressure plate presses against the friction plate so that the friction plate and the pressure plate rotate integrally to transmit power to the power transmission shaft, and the pressure plate and the friction plate by the pressure mechanism Any configuration including a pressing mechanism that applies a predetermined pressing force to the pressure plate and the friction plate in a pressure release state in which the pressure contact force is released is sufficient.

  In any case, when the power of the crushing rotor exceeds the set torque, slippage occurs between the friction plate and the pressure plate, and transmission of power exceeding the set torque from the driving machine to the crushing rotor can be suppressed. As a result, it is possible to avoid a possibility that the gear of the transmission mechanism is damaged due to an abnormal load.

  In the embodiment described above, the case where the torque limiter 20 is incorporated in the speed reduction mechanism 30 has been described. However, the torque limiter 20 is located outside the speed reduction mechanism 30 and between the output shaft 37 and the rotating shaft 5 c of the crushing rotor 5. Further, although the speed reduction mechanism is described as an example of the speed change mechanism, the speed change mechanism of the present invention can also be applied to the speed increase mechanism.

  In the embodiment described above, the case where the torque limiter 20 is a so-called wet multi-plate type torque limiter has been described. However, the number of friction plates and pressure plates is appropriately selected according to the electric motor, the speed change mechanism, the crushing rotor, and the like. The In that case, it is not always necessary to use a plurality of sheets, and a single sheet may be used. Further, the torque limiter may be a dry torque limiter, and the pressure contact force between the friction plate and the pressure plate can be adjusted by air pressure, the expansion / contraction force of the spring, or the like.

  Each of the above-described embodiments is an example of the present invention, and the present invention is not limited by the description. The specific configuration of each part can be appropriately changed and designed within the range where the effects of the present invention are exhibited. Needless to say.

1: Crushing device 2: Receiving hopper 3: Pushing pusher 3a: Arm 3b: Hydraulic cylinder 4: Base 5: Driven machine (crushing rotor)
5c: Rotating shaft 5v: Groove 6: Rotating blade 6a: Blade 6b: Mounting seat 7: Fixed blade 7a: Blade 7b: Mounting seat 8: Screen mechanism 9: Discharge hopper 10: Crushing processing unit 11: Main body frame 11a: One side 12a: support (mounting base)
12b: Support (mounting base)
13: Pulley 14: V belt 15: Pulley 16: Bearing 20: Torque limiter 21: Friction plate 21a: Tooth portion 22: Pressure plate
22a: tooth portion 23: support portion 23a: groove portion 23c: groove portion 23d: position holding portion 23e: opening 23f: cover lid 23g: bolt 25: stopper 25a: bolt 26: pressurizing mechanism 26a: piston 26b: hydraulic chamber 26c: seal member 26d: seal member 27: gap 28: pressure contact force 30: speed change mechanism (deceleration mechanism)
31: Input shaft 32: Gear mechanism (first gear)
33: Gear mechanism (second gear)
34: Rotating shaft (power transmission shaft)
35: Gear mechanism (third gear)
36: Gear mechanism (fourth gear)
36a: annular recess 36b: groove 37: power transmission shaft (output shaft)
37a: hydraulic oil passage 37b: cooling oil passage 37c: groove portion 37d: oil supply port 37e: oil supply port 37f: oil supply groove 37g: oil supply groove 37h: key groove 38: bearing 39: casing 39a: upper edge portion 39b: lower edge portion 39c : One end side 39d: the other end side 40: bearing 41: bearing 42: bearing 43: bearing 44: bearing 45: bearing 46: mounting portion 47: supply pipe 48: oil supply pipe 49: overflow pipe 50: pressure reducing valve 51: supply pipe 52: Hydraulic pump 53: Directional switching valve:
55: high frequency component 60: oil pump 80: pressing mechanism 81: pressing force 90: crushing rotor 91: rotary blade 92: fixed blade 93: torque limiter 94: clutch plate 95: clutch plate 96: disc spring 97: adjusting nut 100: Control unit 101: Vibration sensor 102: Vibration sensor 103: Filter unit M: Driver (electric motor)
CL: Center line

Claims (9)

A power transmission mechanism including a speed change mechanism that transmits power from the driving machine to the driven machine,
An annular friction plate and a pressure plate are arranged around the axis of the power transmission shaft, and either the friction plate or the pressure plate is driven to rotate by the transmission power from the power transmission shaft, and the other is the friction between both plates. It is arranged to be driven to rotate by force and transmit power to the power transmission shaft. When the required torque on the power transmission shaft side exceeds the set torque, the friction plate and the pressure plate slide, and when the torque is less than the set torque, the friction plate A pressure mechanism that presses the pressure plate against the friction plate so that the pressure plate rotates as a unit and power is transmitted to the power transmission shaft, and the pressure contact force between the pressure plate and the friction plate by the pressure mechanism is released In the released pressure release state, a torque limiter having a pressing mechanism that applies a predetermined pressing force to the pressure plate and the friction plate is assembled between the speed change mechanism or the speed change mechanism and the driven machine. Filled-in and the power transmission mechanism.   The predetermined pressing force applied to the pressure plate and the friction plate by the pressing mechanism is less than the pressure contact force by the pressing mechanism, and transmits the power on the power transmission shaft side to the power receiving shaft side in the pressure release state. The power transmission mechanism according to claim 1, wherein the power transmission mechanism is set to be equal to or greater than a minimum pressure contact force required for the operation.   An output stage gear is provided on the output shaft of the speed change mechanism having an input shaft for transmitting power from the drive machine, an output shaft for transmitting power to the driven machine, and a gear mechanism for transmitting power from the input shaft to the output shaft. And a friction plate and a pressure plate are arranged around the axis of the output shaft, and power is output from the gear of the output stage to either the friction plate or the pressure plate via the first engagement portion. The pressure mechanism and the pressing mechanism are provided on the support portion, and are arranged so that power is transmitted from the other side to the support portion that rotates integrally with the output shaft via the second engagement portion. The power transmission mechanism described.   A pressure mechanism is provided between the pressure member that presses the pressure plate and the friction plate by the pressure mechanism, and the support portion, and the pressure mechanism releases the pressure when the pressure force applied to the pressure member by the pressure mechanism is released. The power transmission mechanism according to claim 3, wherein the power transmission mechanism is configured to apply a predetermined pressing force to the pressure member in a state.   The power transmission mechanism according to claim 3 or 4, wherein the pressing mechanism is made of an elastic body.   The power transmission mechanism according to any one of claims 3 to 5, wherein the pressing mechanism is held at a position relative to the support portion by a position holding portion formed on the support portion.   The pressing mechanism is configured to be fitted and inserted so as to come into contact with the pressurizing mechanism from an opening formed in the support portion, and configured to apply a predetermined pressing force by a cover of the opening. Power transmission mechanism.   A plurality of friction plates and pressure plates are accommodated alternately in the annular recess formed on the side surface of the gear of the output stage, and the inner periphery of either the friction plate or the pressure plate and the annular recess are The power transmission mechanism according to any one of claims 3 to 7, wherein the side wall is engaged by the first engagement portion, and the other is engaged by the support portion and the second engagement portion.   A crushing apparatus in which the power transmission mechanism according to any one of claims 1 to 8 is incorporated, and the power from the driving machine is transmitted to the rotating shaft of the crushing rotor.

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