JP5534695B2 - Crusher - Google Patents

Description

  The present invention relates to a crushing apparatus.

  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 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 enter the material to be crushed. If foreign matter enters, the rotary blade and fixed blade will be damaged. There is a risk that an excessive load is applied to the speed change mechanism that transmits power from the driving machine to the crushing rotor or the driving machine, resulting in damage.

  In view of this, it is conceivable to provide a torque limiter in the coupling portion that connects the crushing rotor and the speed change mechanism so as not to transmit an excessive load from the crushing rotor to the speed change mechanism or the drive 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 speed change mechanism are connected by a plurality of pins is conceivable.

  The torque limiter breaks the pin when the relative rotational torque difference between the output shaft of the speed change mechanism and the rotating shaft of the crushing rotor exceeds the shear strength of the pin, and does not transmit power to the rotating shaft of the crushing rotor. Configured as follows.

  By providing such a torque limiter, it is possible to prevent damage to the rotating blade and the fixed blade, the speed change mechanism, the drive machine, etc. due to the mixing of foreign matter into the object to be crushed. The operation of reconnecting the two members with new pins is necessary and complicated.

  Further, in Patent Document 1, as shown in FIG. 12, 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 object 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 receiving 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 driving machine is stopped, the crushing rotor keeps rotating for a while due to inertia, so that there is a possibility that an excessive load is applied to the transmission and the driving machine itself, resulting in damage.

  In view of the above-described problems, the present invention can prevent the torque limiter from operating when the power of the crushing rotor exceeds the set torque, causing an excessive load to be applied to the transmission mechanism and the drive machine, and preventing the pressure mechanism from being damaged. Even if the pressure supplied to the first oil passage fluctuates, the second oil passage of the supplied hydraulic oil is branched and connected to the first oil passage of the hydraulic oil supplied to the pusher mechanism. By maintaining the specified pressure at a predetermined pressure and preventing the pressure contact force between the friction plate and the pressure plate from decreasing, the risk of seizure and wear due to the heat generated by the friction plate and the pressure plate can be reduced. An object is to provide a crushing device capable of transmission.

In order to achieve the above-mentioned object, the first characteristic configuration of the crushing device according to the present invention is arranged opposite to the rotary blade fixed to the crushing rotor and the rotary blade as described in claim 1 of the claims. The fixed blade cooperates to crush the object to be crushed, a speed change mechanism that transmits power from the drive to the crushing rotor, a pusher mechanism that presses the object to be crushed to the crushing part, and a predetermined flow rate. And a hydraulic circuit that drives the pusher mechanism forward and backward by hydraulic oil supplied from a pressure adjusting mechanism that supplies the hydraulic oil via a switching valve, and a friction plate that is pressed by a pressure mechanism Power is transmitted to the crushing rotor via the pressure plate, and when the power of the crushing rotor exceeds the set torque, a torque limiter that causes the friction plate and the pressure plate to slip is provided between the drive unit and the crushing rotor. The hydraulic circuit, adjusts the second oil passage for supplying hydraulic fluid to the pressurizing mechanism branches connect pressure mechanism to the first oil path for supplying hydraulic fluid to the selector valve, it is supplied to the pressure mechanism to a second oil passage that provided with a pressure reducing valve for adjusting the pressure of the hydraulic fluid, downstream of the branch point of the second oil passage to a upstream side of the switching valve, a torque setting torque of the crushing rotor of the hydraulic oil supplied to the pressure reducing valve A sequence valve is provided that maintains a pressure higher than a predetermined pressure that does not cause slippage between the friction plate and the pressure plate .

  According to the above-described configuration, by incorporating the torque limiter between the driving machine and the crushing rotor, when the power of the crushing rotor exceeds the set torque, the friction plate and the pressure plate slip, and the crushing rotor It is possible to prevent the impact torque from being transmitted to the speed change mechanism and the driving machine. As a result, it is possible to avoid the possibility that the transmission mechanism or the drive machine is damaged due to an abnormal load. When the torque required to rotate the crushing rotor becomes smaller than a predetermined torque, the friction plate and the pressure plate do not slip, and the power of the driving machine is transmitted to the crushing rotor.

  As described above, the transmission and transmission suppression of the power of the driving machine can be automatically switched only by the magnitude of the set torque of the power of the crushing rotor, and the restoration work becomes unnecessary. Furthermore, by changing the pressure contact force between the friction plate and the pressure plate by the pressure mechanism, it is possible to easily adjust the torque that causes the friction plate and the pressure plate to slip.

  By branch connecting the second oil passage for supplying hydraulic oil to the pressurizing mechanism to the first oil passage for supplying hydraulic oil to the pusher mechanism, it is not necessary to separately provide a hydraulic circuit for the pressurizing mechanism of the torque limiter. Therefore, the hydraulic circuit can be simplified and the cost can be reduced.

Furthermore, since the pressure reducing valve for adjusting the pressure of the hydraulic oil supplied to the pressurizing mechanism is provided in the second oil passage, the friction plate and the pressurizing plate are caused to slip when the power of the crushing rotor exceeds the set torque. As described above, the pressure of the hydraulic oil supplied to the pressurizing mechanism can be adjusted to an appropriate pressure. The hydraulic oil supplied to the pressure reducing valve is upstream of the switching valve and downstream of the branch point of the second oil passage, and the frictional plate and the pressurizing plate do not slip when the torque of the crushing rotor is less than the set torque. Since the sequence valve that maintains the pressure or higher is provided, the pressure of the hydraulic oil supplied to the second oil passage is maintained at a predetermined pressure or higher even if the pressure of the hydraulic oil supplied to the first oil passage fluctuates. Therefore, slippage due to a decrease in the pressure contact force between the friction plate and the pressure plate does not occur without reducing the pressure of the hydraulic oil in the second oil passage, and power can be transmitted stably.

  In addition to the first feature configuration described above, the second feature configuration is pressurized on the downstream side of the pressure reducing valve provided in the second oil passage when the pressure regulating mechanism is unloaded. It is in the point provided with the accumulator which compensates for the pressure drop of the hydraulic fluid supplied to a mechanism.

  According to the above-described configuration, even if the pressure in the first oil passage is reduced when the pressure regulating mechanism is unloaded when the pusher mechanism is switched between forward drive and reverse drive, the hydraulic oil supplied to the second oil passage Since the pressure is maintained at a predetermined pressure or higher, slippage due to a decrease in the pressure contact force between the friction plate and the pressure plate does not occur, and power can be transmitted stably.

  In the third feature configuration, as described in claim 3, in addition to the first or second feature configuration described above, the torque limiter is incorporated in the speed change mechanism, and an output stage gear is provided on the output shaft of the speed change mechanism. The friction plate and the pressure plate are arranged around the axis of the output shaft, and the power is transmitted from the output stage gear to either the friction plate or the pressure plate, and from the other to the output shaft. It is in the point arranged so that motive power may be transmitted.

  According to the above configuration, by incorporating the torque limiter into the speed change mechanism, when the power of the crushing rotor exceeds the set torque, the friction plate and the pressure plate slip, and the power exceeding the set torque from the drive unit is generated. Transmission 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 fourth feature configuration, as described in claim 4, in addition to the third feature configuration described above, the lubricating oil that is rotationally driven by the power from the drive unit and filled in the casing of the transmission mechanism is cooled. It is in the point provided with the pump which circulates and supplies to the torque limiter as oil.

  According to the above-described configuration, the pump that circulates and supplies the lubricating oil filled in the casing of the speed change mechanism to the torque limiter as the cooling oil can be rotationally driven by the power from the drive unit, so that a separate power source is required. The cost can be reduced.

  According to the fifth characteristic configuration, as described in the fifth aspect, in addition to the third or fourth characteristic configuration described above, the leakage of the hydraulic fluid in the hydraulic circuit is used as lubricating oil for the transmission mechanism. This is in that a return flow path is provided for returning excess oil from the inside of the casing to the oil tank of the hydraulic circuit.

  According to the above configuration, since the return flow path is provided, the hydraulic oil supplied to the transmission mechanism can be returned from the casing of the transmission mechanism as surplus oil to the oil tank of the hydraulic circuit. It is possible to prevent the level of the lubricating oil from increasing beyond a predetermined level.

  As described above, according to the present invention, when the power of the crushing rotor exceeds the set torque, the torque limiter is activated, and it is possible to avoid an excessive load on the transmission mechanism and the drive machine and to prevent damage. Even if the pressure supplied to the first oil passage fluctuates, the second oil passage of the supplied hydraulic oil is branched and connected to the first oil passage of the hydraulic oil supplied to the pusher mechanism. By maintaining the specified pressure at a predetermined pressure and preventing the pressure contact force between the friction plate and the pressure plate from decreasing, the risk of seizure and wear due to the heat generated by the friction plate and the pressure plate can be reduced. A crushing device capable of transmission can be provided.

Schematic diagram of crusher Side view of crushing device Top view of crusher Cross section of transmission Explanatory drawing of the main parts of the torque limiter Side view of transmission according to the present invention (A) is explanatory drawing of the power transmission suppression by a torque limiter, (b) is explanatory drawing of the power transmission by a torque limiter. Illustration of hydraulic circuit (A) is explanatory drawing of a control apparatus, (b) is explanatory drawing of the pump characteristic at the time of forward / backward drive of a pusher mechanism Flow chart for starting control of crusher Flow chart of crushing device stop control Illustration of a conventional crusher

Hereinafter, preferred embodiments of the crushing apparatus 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 pusher mechanism that presses an object to be crushed from the horizontal direction toward the crushing processing unit 10, and the crushing apparatus 1 is controlled in operation by a control device 100 described later.

  The pusher mechanism is configured such that an arm 3a connected to a piston of a hydraulic cylinder 3b that is driven forward and backward by hydraulic oil supplied from a hydraulic pump 52 provided in a hydraulic circuit 60 described later is connected to the rear end of the pusher pusher 3. The board 4 is driven forward and backward in the horizontal direction to press the object to be crushed toward the crushing processing unit 10.

  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 that are parallel to each other at a predetermined pitch are formed in the peripheral portion of the crushing rotor 5, and the blade bodies 6a are bolted to 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 v-shaped grooves 5v are connected to each other. In the fixed blade 7, a v-shaped blade body 7 a at the tip is 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 shape along the rotation trajectory of the rotary blade 6 and has a large number of apertures. The object to be crushed smaller than the opening is dropped from the opening and accommodated in the discharge hopper 9, and the material not passing 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 5 c of the crushing rotor 5.

  Note that the output shaft of the motor M and the input shaft 31 of the speed reduction mechanism 30 may be coupled by a coupling instead of 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 multi-stage gear mechanism and a torque limiter 20 are provided.

  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 configured so that an opening is formed in the center and is loosely inserted into the output shaft 37 via the bearing 38 so that the power of the fourth gear 36 is not directly transmitted to the output shaft 37.

  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. .

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. When the plate 22 is disposed around the axis of the output shaft 37, the friction plate 21 and the pressure plate 22 are pressed against each other at a predetermined pressure by the pressure mechanism 26, and the power on the output shaft 37 side becomes equal to or higher than the set torque, When the friction plate 21 and the pressure plate 22 slip and are less than the set torque, the friction plate 21 and the pressure plate 22 rotate together to transmit power to the output shaft 37.

  As shown in FIG. 5, an annular recess 36 a that can accommodate a plurality of friction plates 21, a pressure plate 22, and a support portion 23 of the pressure plate 22 is formed on one side surface of the fourth gear 36. Is a stopper 25 that holds a plurality of pressure plates 22 and friction plates 21 in an alternately arranged state, and presses the friction plates 21 and the pressure plates 22 in a direction parallel to the axis of the output shaft 37 with a predetermined pressure. A pressure mechanism 26 is provided.

  The friction plate 21 has a tooth portion 21a formed on the inner peripheral side, and is spline-coupled with a groove portion 36b formed on the side wall of the annular recess, 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.

  The pressure plate 22 has a tooth portion 22a formed on the outer peripheral side, and is spline-coupled with a groove portion 23a formed on the side wall of the support portion 23, so that the pressure plate 22 cannot rotate relative to the support portion 23 and is an axis of the output shaft 37. It can move in the direction of the heart.

  The support portion 23 is formed with an opening into which the output shaft 37 can be fitted at the center, a groove portion 23c is formed on the inner peripheral side, and meshes with the groove portion 37c formed around the output shaft 37 to rotate integrally. It is configured as follows.

  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.

  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 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.

  A hydraulic oil passage 37 a for supplying hydraulic oil to the hydraulic chamber 26 a of the pressurizing mechanism 26 is formed in the peripheral portion of the output shaft 37 along a direction parallel to the axis. 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 leaks from the outer peripheral edges of the friction plate 21 and the pressure plate 22 into the casing 39 and is used as lubricating oil for the gear mechanism.

  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.

Since the torque limiter 20 does not include a pressure release mechanism such as a spring that separates the friction plate 21 and the pressure plate 22 , the torque limiter 20 is pressurized with the friction plate 21 even when the supply of hydraulic oil to the pressure mechanism 26 is stopped. A state in which an appropriate frictional force is applied to the plate 22 is maintained. Adopting the torque limiter 20 as described above in the power transmission control device of the crushing device 1 has the following advantages.

  When the blade body 6 a of the rotary blade 6 is replaced, the supply of hydraulic oil to the hydraulic cylinder 3 b of the pusher pusher 3 is stopped and the electric motor M is stopped. As a result, the supply of hydraulic oil to the torque limiter 20 is stopped, and the pressurizing mechanism 26 does not pressurize the friction plate 21 and the pressurizing plate 22.

  In this state, when the crushing rotor 5 is rotated and the blade body 6a of the rotary blade 6 is replaced, the crushing rotor 5 is heavy, and thus it is difficult to directly rotate it manually. However, since the friction force remains applied to the friction plate 21 and the pressure plate 22, when the input shaft 31 of the speed reduction mechanism 30 is rotated, the rotation of the input shaft 31 is transmitted to the output shaft 37, and the crushing rotor 5 can be easily operated. Can be rotated.

  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. 4, an oil pump 70 is provided outside the casing 39. The oil pump 70 is configured to rotate by the power from the electric motor M and to circulate and supply the lubricating oil filled in the casing 39 of the speed reduction mechanism 30 to the torque limiter 20 as cooling oil. The oil pump 70 sucks in from a discharge port formed on the side surface of the casing 39, circulates and supplies the oil to the oil supply port 37e via the oil supply pipe 48, and cools the friction plate 21 and the pressure plate 22.

The oil pump 70 is not necessarily fixed to the casing 39, but a trochoid pump using a rotation of the input shaft 31 as a power source or a plunger pump is 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 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 a filter for removing dust in the oil is provided in the oil supply pipe 48 from the suction port to the cooling oil passage 37b. 61, other coolers, check valves and the like may be provided as appropriate, and the power source of the oil pump 70 is not limited to the input shaft 31, but may be the rotating shaft 34 or the output shaft 37.

  The hydraulic oil in the hydraulic circuit 60 leaks from the pressurizing mechanism 26 into the casing 39 and is used as cooling oil for the torque limiter 20 and lubricating oil for the speed reduction mechanism 30, and the lubricating oil in the casing 39 is discharged at a predetermined liquid level. The excess oil in the casing 39 is returned to the oil tank 59 of the hydraulic circuit 60 by the return flow path 49. The return flow path 49 is provided with a filter 62 for preventing dust in the oil from flowing into the oil tank 59.

  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. .

  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.

  As described above, when the torque limiter 20 is incorporated between the speed reduction mechanism 30 or between the speed reduction mechanism 30 and the crushing rotor 5, when the power of the crushing rotor 5 exceeds the set torque, as shown in FIG. It is possible to prevent slippage between the friction plate 21 and the pressure plate 22, and to transmit power exceeding the set torque from the electric motor M to the crushing rotor 5.

  Therefore, even if the rotary blade 6 and the fixed blade 7 bite foreign matter, it is possible to avoid the possibility that the speed reduction mechanism 30 is abnormally loaded and damaged, or the load on the motor M is increased and the motor M is damaged.

  When the power of the crushing rotor 5 is smaller than the set torque, as shown in FIG. 7B, the friction plate 21 and the pressure plate 22 are pressed against each other by the pressure mechanism 26, and the power of the electric motor M is transmitted to the crushing rotor 5. Is done.

As described above, the power transmission from the motor M and the transmission suppression can be automatically switched only by the magnitude of the power setting torque of the crushing rotor 5, so that the restoration work becomes unnecessary. Furthermore, by changing the pressure contact force between the friction plate 21 and the pressure plate 22 by the pressure mechanism 26, it is possible to easily adjust the set torque at which the friction plate 21 and the pressure plate 22 slip.

  Below, the hydraulic circuit 60 and the control apparatus 100 of the crushing apparatus 1 are demonstrated. As shown in FIG. 8, the hydraulic circuit 60 of the crushing device 1 includes a hydraulic pump 52 that supplies hydraulic oil at a predetermined flow rate, a pressure adjusting mechanism 57 that adjusts the pressure of hydraulic oil output from the hydraulic pump 52, and a hydraulic pump. 4 port 3 position and direction control for switching the forward and backward drive of the pusher pusher 3 installed in the supply pipe 51 and the supply pipe 51 as the first oil passage for supplying the hydraulic oil supplied from 52 to the hydraulic cylinder 3b of the pusher pusher 3 A switching valve 53 that is a valve, a sequence valve 54 is provided on the upstream side of the switching valve 53, and a relief valve 63 is provided on the downstream side of the switching valve 53. The sequence valve 54 is configured to maintain hydraulic oil supplied to a pressure reducing valve 50 of a supply pipe 47 described later at a predetermined pressure or higher.

  The relief valve 63 opens when a large load is applied to the pusher pusher 3 due to, for example, a large foreign matter being introduced into the crushing processing unit 10 while the hydraulic cylinder 3b is moving forward, and the pressure in the supply pipe 51 exceeds a predetermined pressure. The hydraulic oil supplied from the hydraulic pump 52 is allowed to escape to the oil tank 59 to protect the hydraulic circuit 60.

Further, the hydraulic circuit 60 includes a supply pipe 47 as a second oil path that is branched from the supply pipe 51 and supplies hydraulic oil to the pressurizing mechanism 26. The supply pipe 47 includes a pressure reducing valve 50 that adjusts the pressure of the hydraulic oil supplied to the pressurizing mechanism 26, a pressure sensor 56 that is installed on the downstream side of the pressure reducing valve 50 and detects the pressure state of the pressurizing mechanism 26, Hydraulic pressure by a switching valve 58 which is a 4-port 2-position direction control valve for switching the pressurization state of the friction plate 21 and the pressurizing plate 22 by the pressure mechanism 26, and a pressure adjusting mechanism 57 at the time of switching between the forward and backward driving of the pusher pusher 3. An accumulator 55 is provided to compensate for the pressure drop of the hydraulic oil in the supply pipe 51 supplied to the pressurizing mechanism 26 when the pump 52 is unloaded.

  The hydraulic pump 52 is an electromagnetic, two-pressure, two-volume control type piston pump that switches the solenoids SOL1 and SOL2 provided in the pressure regulating mechanism 57 on and off in accordance with the operation of the switching valve 53. The pusher pusher 3 is driven forward and backward, and when the pressure of the hydraulic oil supplied to the hydraulic circuit 60 is unnecessary, the unload operation can be performed.

As shown in FIG. 9A, the control device 100 of the crushing device 1 includes signals from the start switch S1 and the stop switch S2, a forward limit switch S3 and a reverse limit switch provided in the hydraulic cylinder 3b of the pusher pusher 3. The signal of S4 and the signal of the pressure sensor 56 provided in the supply pipe 47 are input, and the motor M is controlled to start and stop, and the hydraulic pump 52 that supplies hydraulic oil to the supply pipes 47 and 51 is controlled to start and stop. The solenoid SOL1 and SOL2 of the pressure adjusting mechanism 57 of the hydraulic pump 52 are switched on and off, and the switching valve 53 provided in the first oil passage 51 and the switching valve 58 provided in the second oil passage 47 are controlled. Is configured to do.

  The control device 100 may be provided inside the crushing device 1 or inside a control panel or the like outside the crushing device 1.

  When the crushing device 1 is activated, the hydraulic pump 52 is activated based on the input of the activation switch S1, the switching valve 58 is controlled, the pressurizing mechanism 26 is activated, and the friction plate 21 and the pressurizing plate 22 are brought into pressure contact with each other. M is started, the switching valve 53 is controlled, and the push-pusher 3 is started to move forward and backward.

  As shown in FIG. 9B, when the pusher pusher 3 is driven forward, the solenoids SOL1 and SOL2 of the pressure adjusting mechanism 57 are controlled to be ON, and the discharge from the hydraulic pump 52 is performed at a high pressure and a small flow rate (discharge pressure P2). , The discharge flow rate Q1).

  When the pusher pusher 3 is switched between forward and backward drive, the solenoids SOL1 and SOL2 of the pressure adjusting mechanism 57 are controlled to be OFF, the hydraulic pump 52 is unloaded (discharge pressure P3, discharge flow rate Q2), and the hydraulic circuit The pressure of the hydraulic oil supplied to 60 can be kept low.

  In the case where the pusher pusher 3 is driven backward, the solenoid SOL1 of the pressure adjusting mechanism 57 is controlled to be OFF and the solenoid SOL2 is controlled to be ON, and the discharge from the hydraulic pump 52 is a small pressure and large flow rate (discharge pressure P1, discharge flow rate Q2). .

  As described above, the pressure of the hydraulic oil supplied to the hydraulic circuit 60 fluctuates during forward and backward driving of the pusher pusher 3 and switching thereof. However, as described above, the accumulator 55 is provided to supply the pressure to the pressurizing mechanism 26. Since the pressure of the hydraulic oil in the supply pipe 51 is compensated, the power contact can be stably transmitted without fluctuation of the pressure contact force between the friction plate 21 and the pressure plate 22.

  When the crushing apparatus 1 is stopped, the switching valve 53 is controlled to stop the operation of the push-in pusher 3, the electric motor M is stopped, and then the switching valve 58 is controlled to stop the pressurizing mechanism 26. .

Furthermore, the control device 100 detects the pressurization state by the pressurization mechanism 26 based on the output of the pressure sensor 56 at the time of start-up, and prohibits the start of the electric motor M when it deviates from the predetermined pressurization state. pressurized flatly state by pressurizing mechanism 26 detects based on the output of the sensor 56, is configured to stop the motor M deviates from a predetermined pressure.

  The starting control of the crushing apparatus 1 will be described based on the flowchart shown in FIG. When the activation switch S1 is turned on (SA1), the control device 100 activates the hydraulic pump 52 to supply hydraulic oil to the hydraulic circuit 60 (SA2). Next, in order to operate the torque limiter 20, the switching valve 58 is controlled, and supply of hydraulic oil to the pressurizing mechanism 26 of the torque limiter 20 is started (SA3).

When the pressure in the supply pipe 47 to the pressure sensor 56 detects a predetermined pressure (YES at SA 4), the torque limiter 20 is a capable power transmission state, the electric motor M to rotate the crushing rotor 5 Is started (SA5).

When the crushing rotor 5 is rotated by the power of the electric motor M, the switching valve 53 is controlled to drive the push-in pusher 3 forward (SA6). If the pressure in the supply pipe 47 detected by the pressure sensor 56 is a predetermined pressure (YES in SA7), the forward pusher 3 is driven forward until the forward limit switch S3 is turned on (NO in SA8). to continue.

When the forward limit switch S3 is turned on (YES in SA8), the switching valve 53 is controlled to drive the pusher pusher 3 backward (SA9). Here, if the pressure the pressure is given in the supply pipe 47 to the pressure sensor 56 detects (YES at SA10), to a retracted limit switch S 4 is ON (NO at SA11), the push pusher 3 reverse drive Continue. ON retreat limit switch S 4 Then (YES at SA11), and it controls the switching valve 53 is advanced driving the push pusher 3 (SA6).

When the pressure in the supply pipe 47 detected by the pressure sensor 56 in steps SA4, SA7, and SA10 described above is not a predetermined pressure, the pressurization state of the friction plate 21 and the pressure plate 22 by the pressurizing mechanism 26 is a predetermined pressure. Since it deviates from the pressure state, the motor M is stopped (SA12), the hydraulic pump 52 is stopped (SA13), the occurrence of an abnormality is reported (SA14), and the start control is terminated.

  Next, stop control of the crushing apparatus 1 will be described based on the flowchart shown in FIG. When the stop switch S2 is turned on (YES in SB1), the control device 100 controls the switching valve 53 to stop driving the pusher pusher 3 (SB2), and stops the motor M to stop the rotation of the crushing rotor 5. In step SB3, the switching valve 58 is controlled to release the pressurization state of the friction plate 21 and the pressure plate 22 of the torque limiter 20 so that the torque limiter 20 does not transmit power (SB4). The hydraulic pump 52 that supplies hydraulic oil to the engine is stopped (SB5), and the stop control is terminated.

  As described above, when the crushing device 1 is started, the pressurizing mechanism 26 is operated to securely press the friction plate 21 and the pressurizing plate 22, and then the motor M is started. 26, the friction plate 21 and the pressure plate 22 are always in a predetermined pressure state while the crushing device 1 is activated, and the rotating blade 6 and the fixed blade 7 bit the foreign matter. As long as the situation where the power of the crushing rotor 5 exceeds the set torque does not occur, the friction plate 21 and the pressure plate 22 do not slip, and seizure due to heat generation or damage due to wear can be reduced.

  In the embodiment described above, the bearing 38 between the fourth gear 36 and the output shaft 37 has not been described in detail. However, the foreign material is caught in the crushing rotor 5, so that the friction plate 21 and the pressure plate 22 of the torque limiter 20 When slipping occurs, the bearing 38 slides with the fourth gear 36 and the output shaft 37. 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 characteristics of the cooling oil, the lubricating oil, and the hydraulic oil are not particularly specified. However, since the hydraulic oil supplied to the pressurizing mechanism is slightly leaked into the transmission mechanism, the gear lubricating oil, friction It is preferable to use a mission oil in which an extreme pressure additive is added to an oil having a kinematic viscosity VG of about 32 to 68 so that it can be used as a cooling oil for the plate and the pressure plate.

  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 If it is less than that, it is sufficient if it has a pressurizing mechanism that presses the pressurizing plate against the friction plate so that the friction plate and the pressurizing plate rotate integrally to transmit power to the power receiving shaft.

  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 torque limiter has been described. However, the number of friction plates and pressure plates is appropriately selected according to the electric motor, the transmission 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.

  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: Pusher pusher 3b: Hydraulic cylinder 4: Base 5: Crushing rotor 6: Crushing rotor 7: Fixed blade 8: Screen mechanism 9: Discharge hopper 10: Crushing processing unit 11: Main body frame 20 : Torque limiter 21: Friction plate 22: Pressurizing plate 23: Supporting part 26: Pressurizing mechanism 26 a: Piston 26 b: Hydraulic chamber 30: Speed change mechanism (deceleration mechanism)
31: Input shaft 37: Output shaft 47: Second oil passage (supply piping)
49: Return passage 50: Pressure reducing valve 51: First oil passage (supply pipe)
52: hydraulic pump 53: switching valve 54: sequence valve 55: accumulator 56: pressure sensor 57: pressure regulating mechanism 58: switching valve 59: oil tank 60: hydraulic circuit 70: oil pump 100: controller M: drive motor (electric motor) )
CL: Center line

Claims (5)

A crushing processing unit for crushing an object to be crushed by cooperation between a rotary blade fixed to the crushing rotor and a fixed blade arranged opposite to the rotary blade;
A transmission mechanism for transmitting power from the drive to the crushing rotor;
A pusher mechanism for pressing an object to be crushed into a crushing processing unit;
A hydraulic circuit that drives the pusher mechanism forward and backward by hydraulic oil supplied via a switching valve from a pressure regulating mechanism that supplies hydraulic oil at a predetermined flow rate;
A crushing device comprising:
A torque limiter that transmits the power to the crushing rotor via the friction plate and the pressure plate pressed by the pressurizing mechanism and causes the friction plate and the pressure plate to slip when the power of the crushing rotor exceeds the set torque, Prepare between the drive and crushing rotor,
The hydraulic circuit is connected to the first oil passage for supplying hydraulic oil from the pressure adjusting mechanism to the switching valve with a second oil passage for supplying hydraulic oil to the pressurizing mechanism. The second oil passage is supplied to the pressurizing mechanism. that provided with a pressure reducing valve for adjusting the pressure of the hydraulic fluid, downstream of the branch point of the second oil passage to a upstream side of the switching valve, a torque setting torque of the crushing rotor of the hydraulic oil supplied to the pressure reducing valve A crushing apparatus provided with a sequence valve that maintains a predetermined pressure or higher so that no slippage occurs between the friction plate and the pressure plate .   The crushing apparatus according to claim 1, further comprising an accumulator that compensates for a pressure drop of hydraulic fluid supplied to the pressurizing mechanism when the pressure regulating mechanism is unloaded, on a downstream side of the pressure reducing valve provided in the second oil passage.   The torque limiter is incorporated in the speed change mechanism, and the gear of the output stage is rotatably fitted to the output shaft of the speed change mechanism, and the friction plate and the pressure plate are arranged around the axis of the output shaft. The crushing apparatus according to claim 1 or 2, wherein power is transmitted to one of the friction plate and the pressure plate, and the power is transmitted from the other to the output shaft.   The crushing apparatus according to claim 3, further comprising a pump that is rotationally driven by power from a driving machine and circulates and supplies the lubricating oil filled in the casing of the speed change mechanism as a cooling oil to the torque limiter. Leakage amount of the operating oil in the hydraulic circuit is used as a lubricating oil of the transmission mechanism, wherein the casing in claim 3 or 4 return flow path is provided for feeding back the excess oil to the oil tank of the hydraulic circuit of the transmission mechanism Crushing equipment.

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