JPH10146538A - Transporting and distributing apparatus of refuse sorting system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a transporting and distributing apparatus for a refuse sorting system which has a mechanism to prevent stoppage by foreign substances. SOLUTION: If an object 54 is inserted between a throwing back rake 26 and a driving body 16, the risk of break is increased. In order to prevent overloading, a first axis 28 is installed in a rocker arm 30 movable on the circumference of a second axis 32 parallel to the first axis 28. A work point at which the first axis 28 comes nearest to a thrusting belt 14 is set on the rocker arm and the rocker arm 30 is fixed and prevented from getting away from the thrusting belt 14 until a prescribed shearing force is generated. In this case, a tangential thrusting force attributed to driving force is generated on the second axis 32 at the time when a turning back end 44 is stopped on the first axis 28 in movement sphere in which the turning back end 44 moves backward in the thrusting direction and the geometric arrangement of these members is so made as to conform the direction of the tangential thrusting force to the direction in which the distance of the first axis 28 and the thrusting belt 14 becomes wide.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a transport and dosing device for a refuse sorting system with a drive moving along a propulsion belt through a crushing device, comprising a throwback rake in the area of the crushing device. The throw-back rake is disposed above the propulsion belt and is pivotally supported about a first axis transverse to the propulsion belt and is driven to oscillate back and forth by a drive, thereby throwing back. At least a majority of the return end of the rake facing the propulsion belt forms a trajectory that moves away from the direction of propulsion of the propulsion belt.

[0002]

2. Description of the Related Art Systems of this kind are known, in particular for acting on the crushing of refuse bags before the refuse to be separated is conveyed to a separating device, whereby the material is shredded and the incoming material is dispensed. The throw-back rake pushes a part of the material, especially a part that has not been sufficiently shredded, back onto the propulsion belt by operation in the reverse direction of the propulsion direction and guides this part again to the working area of the crusher. At the same time, it functions to carry the film material staying in front of the crushing tool into the working area of the crushing device by the operation in the propulsion direction. The dosing is effected on the one hand by a suitable choice of the propulsion speed and, on the other hand, by adjusting the inside dimensions, ie the passage cross section between the trajectory of the return end of the throw-back rake and the propulsion belt. here,
In some cases, coarse objects can be carried on the propulsion belt, which can not be shredded by the crushing tools of the crusher and operates along the retraction rake and the propulsion belt acting in the reversion direction. It can be trapped between the drive and this, at least leading to an overload of the drive, possibly leading to a risk of breakage.

[0003]

SUMMARY OF THE INVENTION Accordingly, it is an object of the present invention to prevent overloading of a driving device, mechanical damage of the device, and stop of the device due to unshredded foreign matter when resistance is generated. To provide a possible overload protection.

[0004]

The above object is achieved by mounting a first axis on a rocker arm movable about a second axis parallel to the first axis, the first axis being propelled by the rocker arm. Set the working position closest to the belt, fix the rocker arm until a preset shear force is generated to prevent the movement away from the propulsion belt, and the first plane including the first axis throws back rake A second plane including a first axis extending perpendicular to the first plane, the return end resting on the first axis in an operating phase counter to the thrust direction When the tangent driving force due to the driving force is generated with respect to the second axis, the direction is geometrically such that the direction corresponds to the direction in which the distance between the first axis and the propulsion belt increases. It is solved by placing.

When the throwing-back action of the throw-back rake is sealed at the free end facing the propulsion belt (referred to as the return end), a reaction to the driving force on the throw-back rake causes a first axial movement. The reaction force generated in the
This acts, on the one hand, as a supporting force in the area of the second axis and, on the other hand, as a tangential driving force for generating a rotational torque around the second axis. When the geometrical positional relationship is selected so that the tangential driving force acts so that the distance between the first shaft and the propulsion belt increases, by appropriately adapting the magnitude of the breaking force to the driving force, This breaking force is smaller than the rotational torque generated by the tangent driving force, and is transmitted by the operation of the rocker arm of the throwback rake generated thereby, so that the object causing the resistance passes below the rake. Lifted off the propulsion belt to be able to. The lifting action of the retraction rake from the propulsion belt causes the rocking arm to act on the rocker arm and move the rocker arm from its operating position at a predetermined level so that the reversion rake can achieve its function. It is executed only when it is done.

In a preferred embodiment, the working position of the rocker arm is determined by a stopper which limits the access of the rocker arm to the propulsion belt, wherein the stopper is used to change the position angle of the rocker arm in the working position with respect to the second axis. Is preferably adjustable.

According to a very simple solution, the breaking force can be set by the load torque of a mass movably supported about a second axis.

[0008] In another preferred embodiment, the breaking force can be set by a spring pressing the rocker arm against the stopper, wherein the spring pressure is preferably adjustable.

It is preferable that the breaking force is set according to the magnitude of an appropriate power that acts so as to return the rocker arm to its operating position after removing the resistive object carried on the propulsion belt. You can continue the work. According to another embodiment, further protection against overload can be achieved if the stopping device is constituted by a break protection element, for example a shear pin. In this case, it is necessary to update the break protection element after the overload prevention is performed. The advantage of this variant is that the working area is inspected when overload protection is performed and the break protection element is updated, whereupon any remaining coarse obstacles can be removed if necessary. it can.

[0010] Since the transport device is put into operation again only after the breaking protection element is updated, the rocker arm leaves the operating position and operates at the same time with a delay time allowing the lifting operation of the rocker arm, and the drive device of the transport device is shut off. It is preferred to mount a possible sensor on the rocker arm.

In order to reduce the frequency of operation, in another preferred embodiment, a cutting plate having a sawtooth-shaped tooth profile and extending in a direction opposite to the propulsion direction is provided at the apex of the return rake. The distance from the first axis increases at the same time as the throw-back rake distance, wherein the tooth profile preferably comprises a cutting tooth surface oriented in the direction of propulsion. This embodiment allows the teeth to penetrate a larger but coarser but severable object at a greater depth during the up and down movement of the retraction rake in the direction of propulsion, eliminating its resistance as well as stopping the device. it can.

In a particularly preferred variant, the crushing device is provided with a cutting tool arranged in such a way that the crushing device proceeds in the chamber orbit into the working trajectory of the throw-back rake and engages with the cutting tooth surface of the throw-back rake. Thereby, for example, the film material can be shredded like scissors.

Furthermore, in another very preferred embodiment, the throw-back rake extends beyond the turn-back position on the propulsive direction side of the reciprocation of the throw-back rake generated by the drive and reciprocating between the two turn positions. The movable area is extended and, when reaching this turn-up position, the throw-back rake is actuated by an adjustable supporting force acting against it in the direction of propulsion.

Thus, when a resistance force exceeding the supporting force is generated at the return end of the throw-back rake, the throw-back rake moves in the propulsion direction and turns around the first axis, whereby the throw-back rake is returned. As the distance between the end and the propulsion belt increases, larger and non-shredable coarse objects can be passed if necessary, thus eliminating the resistive objects. The magnitude of the supporting force is appropriately set according to the type of the substance to be treated, and the power that acts in the propulsion direction by the driving body and increases when the resistance force is generated first exceeds the supporting force and rotates the throwback rake,
If this is not enough, the stopping force is exceeded to reject foreign matter, thereby moving the first shaft away from the propulsion belt and further increasing the distance between the propulsion belt and the throw-back end. This setting is particularly suitable in combination with the break protection element of the rocker arm. If the supporting force is set higher, the rocker arm first turns in the event of resistance, and if this does not achieve the elimination of foreign objects, the throwback rake runs counter to the effect of the supporting force and turns excessively.

In a preferred embodiment, the driving force of the throw-back rake is transmitted to the throw-back rake by a crank mechanism through a connecting rod, and the driving body and the driving device of the crank mechanism preferably have a common drive shaft. is there.

In another preferred embodiment, the drive of the throw-back rake is achieved via a hydraulically reciprocable piston, wherein the hydraulic drive rotates concentrically with the linearly acting piston or first axis. It has a working piston. The hydraulic drive can be located between the rocker arm and the throwback rake.

In a throw-back rake that exceeds the supporting force and exceeds the turn-back position and turns excessively in the propulsion direction, the drive of the throw-back rake is performed via a hydraulic drive device having a reciprocating piston. The piston is supported by a spring generating a supporting force at the turn-back position of the side throw-back rake.

In a likewise preferred variant, the drive of the throw-back rake is effected via a hydraulic drive with a reciprocable piston, the lever being used as a support element of the hydraulic drive, which lever is driven It is pivotally mounted on a device part suitable for supporting the reaction force of the device and is supported on this device part via a spring having an adjustable spring pressure, wherein the drive is at a distance from the pivot support of the lever. In this case, so that the supporting pressure is amplified by the action of the lever.

Although different reaction forces are generated in the system according to the selection of the drive mechanism, by appropriately arranging the components constituting the system, the throwing-back operation is obstructed in common with all the modifications. In this case, a tangent driving force is generated on the first shaft, which is necessary for the lifting operation of the rocker arm and generates a rotational torque around the second shaft.

In the crank mechanism described as a preferred variant, the tangential drive generated in the region of the first shaft depends theoretically on four parameters, ie they are the drive transmitted by the connecting rod. Between the line of action and the connection of the support point of the throw-back rake, i.e. one is the angle between the first axis and the other is the return end stopped by the resistor, and The ratio of the lengths of the connection fragments, and also the angle between the line of action and the plane containing the first and second axes, and finally the angle between the plane and the connection. It is difficult for a person skilled in the art to inspect whether the intended arrangement generates the required tangential driving force on the first axis, for example, by graphic analysis using a small number of dynamic parallelograms. It will be understood that it is not.

[0021]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The transport device shown in the partial view of FIG. 1 is formed in the form of a scraper plate and rises towards a discharge end 12, preferably in a bag, for a garbage propulsion belt 1.
4 is provided. A driving body 16 moves along the propulsion belt 14, and is configured to convey an object carried to a lower end of the propulsion belt 14 in a propulsion direction indicated by an arrow 18. The drive 16 is fixed in the form of an endless chain, which operates via a lower turning roller 20 and an upper turning roller 22. The upper diverting roller 22 and the crank 24 are continuously driven by a common driving source (not shown).

The driver 16 is schematically shown in a suitable number, extends in the direction of propulsion, is separated from one another and preferably through a crushing tool 17 arranged on the upper surface of the propulsion belt. The carried object such as a garbage bag is conveyed, and the crushing tool 17 can be retracted upward by a spring pressure as needed. A throwback rake 26 is provided in the area of the crushing tool 17 to loosen the substance and to apply the action of the crushing tool to the coarse object a plurality of times as necessary. Penetration through the gap, and thus crushing by means of, on the one hand, the crushing tool 17 in the illustrated embodiment with a tooth-shaped tooth surface 17a and, on the other hand, appropriately forming the apex 26a of the throwback rake 26 For example, a shearing force suitable for cutting a film material can be formed between the tool 17 and the throw-back rake 26.

The throwback rake 26 is supported above the propulsion belt 14 so as to be movable about a first axis 28 parallel to the axes of the diverting rollers 20 and 22. The first axis 28 is supported on a rocker arm 30 which is on a vertical support member 34 and is supported about a second axis 32 at a distance from and parallel to the axis 28, and includes a support member. Reference numeral 34 designates a part of a frame member of the transport device, which is not shown in detail. The rocker arm 30
The rocker arm 30 is pressed against the adjustable stop 38 in the direction of the propulsion belt 14 by means of a spring 36 with an adjustable spring pressure which abuts on the support member 34 on the other hand, whereby the propulsion belt The working position of the rocker arm 30 and the first shaft 28 which comes closest to the above is set in advance. Stopper 38
Prevents the throwback rake 26 from further approaching the propulsion belt 14. Since the installation position of the stopper 38 is restricted, the operation position can be adjusted by a wire lever 70, which is composed of a wire 72, which is turned from the rocker arm 30 to a turning roller 74 installed on the support member 34. Through to a wire wrapper 76 with fasteners not shown.

A lever 40 is connected to the throw-back rake 26 and performs a common rotation operation about the first axis 28. The lever is connected to the crank 24 via a connecting rod 42, and the propulsion belt of the throw-back rake 26 is provided. Return end 44 facing 14
Draws a trajectory such that at least a large part of the rake moves backward in the propulsion direction and moves away from the propulsion belt, so that the throw-back rake 26 traces a predetermined area in a reciprocating operation.

The apex 26a retreats somewhat from the return end 44.
A round cutting plate 46 is mounted on the top, and its position is
a is adjustable along and extends counter to the propulsion direction 18, the surface facing the propulsion belt 14 is formed with saw-toothed teeth 48, the teeth 48 of which extend from the first shaft 28. The distance increases with increasing distance from a plane that includes the first axis and extends through the return end 44.
The tooth 48 has a cutting tooth surface 50 facing the propulsion direction,
This can achieve the aforementioned shearing action in conjunction with the crushing tooth surface 17a.

FIG. 1 shows a plastic tank 52 which, when moved in the propulsion direction,
In particular, it is understood that the cutting is performed by the cutting tooth surface 50 with increasing depth in the reciprocating operation of the throw back rake in the propulsion direction.

On the propulsion belt 14 below the cutting plate 46, an object 54 that cannot be shredded by a crushing tool
Exists. This object 54 is used for the return rake 26
During the backward movement, the rake 26 is sandwiched between the apex 26a and the driving body 16 and hinders the further operation of the throw-back rake 26.

Since the driving force acting on the throw-back rake 26 via the connecting rod 42 is considerably increased, the reaction force applied to both ends of the throw-back rake 26 is correspondingly increased, and accordingly, it is generated and the first The tangential drive force acting in the area of the axis 28 of the second axis 32 and producing a rotational torque about the second axis 32 is also increased,
, The rocker arm 30 can be turned counterclockwise in FIG. by this,
The throwback rake 26 retracts from the area of the propulsion belt 14, opening the path for the object 54, further reducing the tangential drive force acting on the first shaft 28 and causing the spring 36 to move the rocker arm 3.
0 is again pressed against the stopper 38, and the throwback rake 26 returns to its movable position again.

FIG. 1 shows a variant of the arrangement described above in dashed lines, in which the support member 34 ′ is arranged behind the shaft 28, rather than in front of the shaft 28 in the direction of propulsion. Here, rocker arm 30 'requires traction, not propulsion, however, tangential drive on first shaft 28 acts in the required direction.

Instead of supplying the driving force to the system consisting of the throwback rake 26 and the rocker arm 30 from the outside, the driving force can also be generated inside the system without changing the principle functional system. As a first example of this type of change, FIG.
Also shown is a linear operating hydraulic motor 56 comprising a fixed rod 56b, which hydraulic motor is arranged between the throwback rake 26 and the rocker arm 30.

FIG. 3 shows a hydraulic rotary drive device 58 arranged coaxially with the first shaft 28, for example, an arc-shaped chamber 58a arranged coaxially with the shaft 28,
A piston 58b, also formed in an arc shape inside, is installed so as to be capable of reciprocating rotational movement.

FIG. 4 shows a modification of that of FIG. 3, in which the working position of the rocker arm 30 is fixed by a break protection element instead of the stopper 38.
It comprises a connector 60 arranged on the rocker arm 30 and a connector 62 joined thereto.
Numeral 2 is arranged on a console 39 fixed on a support member 34 so as to be adjustable in height. Each of the couplings 60 and 62 has the same hole disposed at the operation position of the rocker arm, and a shear pin 64 can be disposed therein, and the shear pin is formed by a predetermined breaking pressure. Destroyed thereby rocker arm 3
0 is designed to allow the operation of rising from a predetermined operation position. However, it is also possible to exclude the shear pin 64 and use the wire lever 70 to adjust the working position.

FIGS. 5 to 8 show an embodiment which consists of two very preferred arrangements, which, during the normal operation of the device of the throwback rake 26, between the two turning positions. The reciprocating motion of the rake does not fully utilize its operating capacity, and the return end 44 is moved away from the propulsion belt 14 so that it is thrown back beyond the turning position on the propulsion direction side shown in FIG. The rake 26 can move in other areas in its normal operation beyond the supporting forces limiting movement in the resistance position. The advantages of this method and the setting of the supporting force are as described above.

FIGS. 5 and 6 show a hydraulic operating unit 80 for producing a linear movement, which is arranged between the throw-back rake 26 and the support member 34. The situation corresponding to FIG. 1 is shown, in which the throwback rake is in a turning position on the propulsion direction side. Here, a piston 82 is connected to a spring 84, which in this position provides an opposing support for further piston movement. The driving body 1 on the propulsion belt 14
Since the non-shredable foreign matter 86 driven by 6 is sandwiched between the cutting plate 46 and the propulsion belt 14,
The driving force directed to the propulsion direction is transmitted to the cutting plate 46 and thus the throw-back rake 26. As a result, the pressure on the piston 82 increases, the spring 84 contracts, and the rake 26 is thrown back again in the propulsion direction until the cutting plate releases the foreign matter 86. Throwback rake 26
If the usable swivel area is insufficient, the further increasing pressure exceeds the breaking pressure of the rocker arm 30 and the rocker arm 30 swings as described above, so that the passage between the cutting plate 46 and the propulsion belt 14 is performed. The surface expands further.

By appropriately setting the dimensions, the rocker arm 30 is first turned, and then the rake 2
It is also possible to select a setting for turning the wheel 6.

FIGS. 7 and 8 show a modification of the arrangement of FIGS. 5 and 6, wherein the piston rod 88 is pivotally supported at 90 on the support member 34 instead of on the support member 34. To the support member 34 by means of a lever rod 94, wherein the end of the lever rod 94 and the support member 34 when the throw-back rake 26 is loaded in the propulsion direction. Pressure is applied to the spring 84 between them. In this configuration, for example, the turning point of the piston rod 88 is
By making it adjustable above, the shifting action of the lever 92 can be used.

[Brief description of the drawings]

FIG. 1 is a schematic side view showing a portion provided with a throw-back rake of a transport device for a refuse sorting system, which is provided with an overload prevention device according to the present invention.

FIG. 2 is a schematic diagram showing an example of the configuration of a first drive device for generating a reciprocating motion of a throwback rake similar to FIG. 1;

FIG. 3 is a schematic diagram showing a second driving device configuration example for generating a reciprocating motion of a throwback rake.

FIG. 4 shows a stopping device having a shear pin shape.

FIG. 5 is another configuration example of the driving device shown in FIG. 2;
It is disposed at one end of a reciprocating motion of a throwback rake generated by hydraulic pressure when viewed from the opposite direction.

FIG. 6 is a modification of FIG. 5, showing the approach to a pole.

FIG. 7 is a structural modification of the one in FIG. 5;

8 at a position corresponding to that of FIG.
FIG.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 10 Conveying device 12 Discharge end 14 Propulsion belt 16 Driver 17 Crushing tool 17a Crushing tooth surface 20,22 Turning roller 24 Crank 26 Throw-back rake 26a Vertex 28 First shaft 30,30 'Rocker arm 32 Second shaft 34,34 'Supporting member 36 Spring 38 Stopper 39 Console 40 Lever 42 Connecting rod 44 Return end 46 Cutting plate 48 Teeth 50 Cutting tooth surface 52 Tank 54 Object 56 Hydraulic motor 56a Cylinder 56b Fixed rod 58 Rotary drive 58a Chamber 58b Piston 60, 62 Connection Tool 64 Shear pin 70 Wire lever 72 Wire 74 Deflection roller 76 Wire wrapping tool 80 Operation unit 82 Piston 84 Spring 86 Foreign matter 88 Piston rod 92 Lever 94 Lever rod

Claims (20)

[Claims] A transport device (10) for a refuse sorting system comprising a drive (16) moving along a propulsion belt (14) through a crushing device (17), the crushing device (17). And a return rake (26) disposed in the area of the propulsion belt (14) so as to be pivotable about a first axis (28) traversing the propulsion belt (14). Supported, and the throw-back rake can be driven to oscillate back and forth by a drive, whereby at least a majority of the return end (44) of the throw-back rake (26) facing the propulsion belt (14). Forms a trajectory that moves away from the propulsion belt (14) in a direction opposite to the propulsion direction (18), and the first axis (28) is parallel to the first axis (28). Lockable about the axis of the Arm (30)
Mount on the rocker arm (30), set the working position of the first shaft (28) closest to the propulsion belt (14), and fix the rocker arm (30) until a preset shear force is generated. A tangential driving force caused by the driving force is prevented when the return end (44) stops on the first shaft (28) in the operation phase going backward in the propulsion direction by preventing the operation of moving away from the propulsion belt (14). Geometrically arranged so as to occur with respect to the second axis (32) and whose direction corresponds to the direction in which the distance between the first axis (28) and the propulsion belt (14) increases; A conveying device characterized by the above-mentioned. 2. The transport device according to claim 1, wherein the working position of the rocker arm is determined by a stopper that limits the approach of the rocker arm to the propulsion belt. 3. The device according to claim 1, wherein the stop is adjustable to change the position angle of the rocker arm in the operating position with respect to the second axis. Transport device. 4. The transport device according to claim 1, wherein the breaking pressure is set by a load torque of a mass movably supported around the second axis. . 5. A rocker arm (30) with a stopper (3).
4. The conveying device according to claim 1, wherein the breaking pressure is set by a spring that presses against the sheet. 6. The transport device according to claim 5, wherein the pressure of the spring is adjustable. 7. The conveying device according to claim 1, wherein the breaking pressure is set by a breaking protection element. 8. A sensor arranged to operate with a delay time allowing the lifting operation of the rocker arm (30) at the same time as the rocker arm (30) leaves the working position and to shut off the drive of the transport device (10). (3
8. The transport device according to claim 7, wherein the transport device is attached to (0). 9. An apex (26) of a throw-back rake (26).
a) has sawtooth teeth (48) in the propulsion direction (1);
8) A cutting plate (46) extending backwards from 8), the distance from the first axis (28) increasing with the distance from the throwback rake (26). 9. The transport device according to any one of 1 to 8. 10. The transport device according to claim 9, wherein the teeth (48) have cutting tooth surfaces (50) oriented in the direction of propulsion. 11. A crushing device (17) cuts disposed so as to enter a motion path of a throw-back rake (26) into a chamber shape and to engage with a cutting tooth surface (50) of the throw-back rake (26). The transport device according to claim 10, comprising a tool (17a). 12. The throw-back rake (26) movable beyond the turn-back position on the side of the propulsion direction (18) of the reciprocating movement of the throw-back rake (26) generated by the driving device and reciprocating between the two turn-back positions. Extending the area and arriving at this turn-up position, wherein the throw-back rake (26) is actuated by an adjustable bearing force (84) acting against the direction of propulsion (18). 1
12. The transfer device according to any one of claims 11 to 11. 13. The transport device according to claim 1, wherein the driving force of the throw-back rake (26) is transmitted to the throw-back rake (26) by a crank mechanism (24) via a connecting rod (42). . 14. The transport device according to claim 13, wherein the drive of the drive body and the drive of the crank mechanism have a common drive shaft. 15. The transport device according to claim 12, wherein the throw-back rake (26) is driven by a hydraulically reciprocable piston. 16. The transport device according to claim 15, wherein the hydraulic drive comprises a piston that moves linearly. 17. The hydraulic drive (58) includes a first shaft (2).
The transporting device according to claim 15, further comprising a piston (58b) that rotates coaxially with the piston (8). 18. The transport device according to claim 16, wherein the hydraulic drive is arranged between the rocker arm and the throw-back rake. 19. A hydraulic drive (8) comprising a piston (82) capable of reciprocating the drive of a throw-back rake (26).
The piston (82) is supported by a spring (84) that generates a supporting force at a turn-back position on the thrust direction side of the throw-back rake (26). Transport device. 20. The drive of the throw-back rake (26) is carried out via a hydraulic drive (80) having a reciprocable piston, and a lever (9) is used as a support element of the hydraulic drive.
2), this lever being pivotally mounted on a device part (34) suitable for supporting the reaction force of the drive and via a spring (84) having an adjustable spring pressure; 20. The transport device according to claim 19, wherein the drive (80) is supported at a distance from the pivot support of the lever (92).