EP0912401A1 - Beschickungs- und dosiervorrichtung für eine müllsortiereinrichtung - Google Patents
Beschickungs- und dosiervorrichtung für eine müllsortiereinrichtungInfo
- Publication number
- EP0912401A1 EP0912401A1 EP97932824A EP97932824A EP0912401A1 EP 0912401 A1 EP0912401 A1 EP 0912401A1 EP 97932824 A EP97932824 A EP 97932824A EP 97932824 A EP97932824 A EP 97932824A EP 0912401 A1 EP0912401 A1 EP 0912401A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- throw
- rocker
- axis
- feeding device
- rake
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B07—SEPARATING SOLIDS FROM SOLIDS; SORTING
- B07C—POSTAL SORTING; SORTING INDIVIDUAL ARTICLES, OR BULK MATERIAL FIT TO BE SORTED PIECE-MEAL, e.g. BY PICKING
- B07C5/00—Sorting according to a characteristic or feature of the articles or material being sorted, e.g. by control effected by devices which detect or measure such characteristic or feature; Sorting by manually actuated devices, e.g. switches
- B07C5/02—Measures preceding sorting, e.g. arranging articles in a stream orientating
Definitions
- the invention relates to a loading and dosing device for a waste sorting device with drivers movable along a conveyor path past a tear-open device, wherein in the area of the tear-open device a throw-back rake is provided which is rotatably supported around a first axis arranged above the conveyor track and crossing the conveyor track can be driven by a drive with a reciprocating movement in such a way that the end of the throw of the throw-back rake facing the conveying path at least largely describes a path moving away from the conveying path in the opposite direction to the conveying direction.
- Such devices are known and are primarily used to tear up garbage bags before the material to be sorted is introduced into the sorting system, so that the material can be dispensed and the material inflow can be metered.
- the throw-back throws back part of the material, especially the part that has not yet been adequately shredded, on the conveyor track when it is moving against the conveying direction in order to guide it again through the area of action of the tearing device.
- it also serves to pull foils jammed in front of the tearing tools into the range of action of the tearing tools during its movement in the conveying direction.
- the metering takes place by a suitable choice of the conveying speed on the one hand and by changing the clear width, ie the passage cross-section, between the path of the throw end of the throw-back rake and the conveying path. It cannot be avoided that occasional Bulky objects arrive on the conveyor track that cannot be shredded by the cutting or tearing tools of the ripping device and are then pinched between the throw-back rake used for the throw-back movement and the drivers moving along the conveyor track, which at least overloads the drive and possibly also brings with it the risk of breakage.
- the object of the invention is to provide an overload protection device which prevents both the overloading of the drive and mechanical damage to the device when resistance occurs, but also prevents the device from becoming blocked by foreign bodies which cannot be comminuted.
- the first axis is mounted on a rocker which is movable about a second axis parallel to the first axis, the rocker is assigned a working position in which the first axis of the conveyor track is closest, the rocker until a predetermined breakaway force occurs in its working position and is prevented from moving away from the conveyor track, a first plane containing the first axis runs through the throwing end of the throw-back rake, a second plane containing the first axis is perpendicular runs to the first level, the geometric arrangement is such that when the throwing end is blocked during the movement phase running against the conveying direction on the first axis, a tangential force resulting from the driving force occurs with respect to the second axis, the direction of which is suitable, the distance between to enlarge first axis and conveyor track , If the throw-back movement of the throw-back rake is blocked at its free end facing the conveyor track - referred to as the throw end - the reaction forces occurring on the first axis in
- this breakaway force is overcome by the torque generated by the tangential force and by the then taking place when the dimensioning of the breakaway force is adapted to the driving force Movement of the rocker of the throw-back rake dragged along and lifted off the conveyor track to such an extent that the object causing the resistance can be moved under the rake. So that the throw-back rake can fulfill its function, this lifting of the throw-off rake from the conveyor track may only occur when the torque exerted on the rocker arm, which moves the rocker arm from its working position, exceeds a predetermined amount.
- the working position of the rocker is determined by a stop limiting its approach to the conveyor track, the stop preferably being adjustable to change the angular position of the rocker in its working position with respect to the second axis.
- the breakaway force can be determined by the load moment of the mass movably mounted about the second axis.
- the breakaway force is determined by a spring pulling the rocker against the stop, the force of the spring preferably being adjustable. It can be advantageous if the breakaway force is determined by the appropriate dimensioning of a force which tends to return the rocker to its working position after removal of the resistance occurring on the conveyor track, so that the loading device can continue to operate.
- the restraint device consists of a break protection device, for example a shear bolt. In such a case, the breakage protection must be replaced after the overload protection has responded.
- the advantage of this variant can be seen in the fact that, after the overload protection has responded, the functional area is checked when the breakage protection is renewed, and any bulky objects that remain can be removed.
- the rocker is preferably assigned a sensor which responds with a time delay which allows the rocker to be raised as soon as the rocker leaves the working position and which is suitable for switching off the drive of the loading device.
- the Gearing is preferably provided with cutting flanks pointing in the conveying direction.
- a particularly preferred variant consists in that the tear-open device engages like a comb in the movement path of the throw-back rake and the tear-open device is provided with cutting tools which shearably assign cutting edges of the throw-back rake.
- the tear-open device engages like a comb in the movement path of the throw-back rake and the tear-open device is provided with cutting tools which shearably assign cutting edges of the throw-back rake.
- a further, very advantageous embodiment consists in that the range of motion of the throw-back rake is extended beyond the reversing position in the conveying direction of the oscillating movement of the throw-back rake generated by the drive, which reciprocates between two reversing positions, and that when this reversing position is reached, the throw-back rake is extended by one adjustable supporting force acting on it against the conveying direction.
- the supporting force can be dimensioned so that the force exerted by the drivers in the direction of conveyance and increasing with resistance initially overcomes the supporting force and swivels the throw-back rake and - if this is not sufficient to release the foreign body, the return shark - is overcome and thereby the first axis is removed from the conveyor track and the distance between the conveyor track and the throw-back end is further increased.
- This setting is particularly preferable in connection with a break protection of the swing arm. If the support force is set more strongly, the rocker is pivoted when resistance occurs - and if this does not lead to the release of the foreign body - the throw-back calculation against the effect of Swing out support force.
- An advantageous embodiment consists in that the driving force for the rake rake is transmitted from a crank mechanism to the rake rake via a crank rod, the drive of the drivers and the crank mechanism preferably having a common drive shaft.
- Another expedient embodiment consists in that the throwing rake is driven by a hydraulically reciprocable piston, the hydraulic drive comprising either a linearly movable piston or a piston which can be rotated concentrically to the first axis.
- the hydraulic drive can be arranged between the swing arm and the rake rake.
- an advantageous arrangement consists in that the throwing rake is driven by a hydraulic drive with a reciprocating piston and in the reversing position of the throwing rake in the conveying direction is supported by a spring generating the supporting force.
- the throwing rake is driven by a hydraulic drive with a reciprocating piston and that a lever serves as an abutment of the hydraulic drive, which lever is pivotably mounted on a device part suitable for supporting the reaction force of the drive and via a spring is supported with adjustable spring force on this part of the device, the drive being supported on the lever at a distance from the pivot bearing, so that the supporting force is increased by lever action.
- the resulting tangential force in the area of the first axis theoretically depends on four parameters, namely the angle between the line of action of the driving force transmitted by the crank rod and the connecting line between the support points of the throw-back rake, namely the first axis on the one hand and the throwing end blocked by a resistance on the other hand, then on the length ratio of the sections of the connecting line located on both sides of the action line, also on the angle between the said action line and the plane containing the first and second axes, and finally on the angle between this plane and the called connecting line. It is not a problem for the person skilled in the art, e.g. to check graphically by means of a few parallelograms of forces whether the arrangement provided by him fulfills the condition of providing the required tangential force on the first axis.
- FIG. 1 shows a schematic side view of the area of a loading device for a waste sorting device with the rake-back calculation, with an overload protection designed according to the invention
- FIG. 2 shows a schematic illustration of a first drive variant for generating the oscillating movement of the throw rake similar to FIG. 1,
- FIG. 3 shows a schematic representation of a second drive variant for generating the oscillating movement of the throw-back rake
- FIG. 5 shows a further variant of the drive shown in FIG. 2 seen in the opposite direction at one end of the hydraulically generated oscillating movement of the throw-back rake
- FIG. 6 shows the variant according to FIG. 5 in the approach to an extreme position
- FIG. 7 shows a constructive variant corresponding to FIG. 5 and FIG. 8 this variant in a position corresponding to FIG. 6.
- the loading device shown with a section in FIG. 1 has a conveyor track 14, designed in the manner of a scraper floor and rising towards its discharge end 12, for garbage preferably delivered in bags.
- Carriers 16 are moved along the conveyor track 14 and are suitable for transporting the objects delivered at the lower end of the conveyor track 14 in the direction of conveyance indicated by the arrow 18.
- the drivers 16 are attached to endless chains, which are guided over lower guide rollers 20 and upper guide rollers 22.
- the upper deflection rollers 22 and a crank 24 are continuously driven together by a drive source, not shown.
- the drivers 16 move the delivered items, that is to say preferably garbage bags, through a number of schematically shown tearing tools 17, which extend in the conveying direction and are spaced apart from one another and parallel to one another above the conveying path, and optionally can deflect upwards against the action of a spring force.
- the rake rake 26 is mounted above the conveyor track 14 so as to be movable about a first axis 28 parallel to the axes of the deflection rollers 20 and 22.
- This first axis 28 is mounted on a rocker arm 30, which in turn is mounted at a distance from this first axis 28 about a second axis 32 parallel to it on a vertical support 34 which is part of a frame construction of the charging device, not shown in detail.
- the rocker 30 is pulled by an adjustable spring force on the one hand on this rocker 30 and on the other hand on the support 34 spring 36 in the pivoting direction towards the conveyor track 14 against an adjustable stop 38, whereby a maximum approach of the conveyor track working position of the rocker 30 and the first axis 28 is predetermined.
- the stop 38 prevents the throw-back rake 26 from approaching the conveyor track 14 further. Since the setting range of this stop 38 is limited, the working position can additionally be set by means of a cable 70 which comprises a cable 72 which extends from the rocker 30 via a the support 34 arranged deflection roller 74 is guided to a cable winch 76 which is not shown with a ratchet.
- a lever 40 which in turn is connected to the crank 24 via a crank rod 42 in such a way that the throw-back rake 26 sweeps in a swinging movement a sector in which the throw end 44 of the throw-back rake 26 facing the conveyor track 14 is at least largely one describes the path away from the conveyor track against the conveying direction.
- curved blades 46 are attached to the tines 26a, the position of which can be adjusted along the tines 26a and which extend counter to the conveying direction 18 and have sawtooth-like teeth 48 on their side facing the conveyor path 14, the distance from which the first axis 28 increases with increasing distance from a plane containing the first axis 28 and placed through the throwing end 44.
- the toothing 48 is provided with cutting flanks 50 which point in the conveying direction and which, in cooperation with the flanks of the fangs 17a, can exert the above-mentioned heavy effect.
- Fig. 1 denotes a plastic canister, wherein it can be seen that this canister 52, when it is moved in the conveying direction, is cut into by the cutting flanks 50 with increasing depth of penetration, in particular in the stroke of the throw-back rake running in the conveying direction.
- FIG. 1 A variant of the arrangement described is shown in broken lines in FIG. 1, in which — with respect to the conveying direction — the support 34 ′ is not arranged in front of, but behind the first axis 28.
- the rocker arm 30 ' is not subjected to pressure, but to tension, but the tangential force acting on the first axis 28 also acts here in the desired direction.
- the driving force can also be generated within this system without changing the principle of operation.
- a linearly acting hydraulic motor 56 with a cylinder 56a and an actuating rod 56b is shown as the drive source in FIG. 2, this hydraulic motor being arranged between the return rake 26 and the rocker 30.
- FIG. 3 schematically shows a hydraulic rotary drive 58 arranged concentrically to the first axis 28, for example with an arcuate chamber 58a arranged concentrically to the axis 28, in which an equally arcuate piston 58b can be rotated back and forth.
- FIG. 4 shows a variant of FIG. 3, in which the working position of the rocker 30 instead of a stop 38 is determined by a break protection.
- This comprises a bracket 60 attached to the rocker 30 and an associated bracket 62 which is height-adjustable on a bracket 39 attached to the support 34.
- the tabs 60 and 62 are each provided with congruent holes in the working position of the rocker 30, in which a shear pin 64 can be arranged, which is dimensioned so that it is destroyed by the predetermined breakaway force and thereby the rocker 30 into one it releases lifting movement from the given working position.
- a shear pin 64 can be arranged, which is dimensioned so that it is destroyed by the predetermined breakaway force and thereby the rocker 30 into one it releases lifting movement from the given working position.
- 5 to 8 show two examples of a very advantageous measure, which consists in the fact that the swinging movement of the rake carried out by the rake rake 26 between two reversing positions during normal operation of the device does not exhaust its movement possibility, but that the movement shown in FIG. 1, the reverse position shown in the conveying direction, beyond the throw-back rake 26, after overcoming a supporting force limiting its movement in this reversing position during normal operation, can still cover a sector in which the throwing end 44 moves away from the conveyor track 14.
- the advantage of this measure and the dimensioning of the supporting force have already been explained in the introduction.
- FIG. 5 and 6 show a hydraulic drive unit 80 which generates a linear movement and which is arranged between the rake rake 26 and the support 34.
- the situation corresponding to FIG. 1 is shown, in which the throw-back calculation is in the reversing position in the conveying direction.
- the piston 82 bears against a spring 84, which in this position opposes the further piston movement of the supporting force.
- the non-crushable foreign body 86 moved on the conveyor track 14 by the driver 16 transmits a force directed in the conveying direction to the cutting blade 46 and thus to the throw-back rake 26 because the foreign body 86 is located between the Cutting blade 46 and the conveyor track 14 jammed.
- the pressure on the piston 82 increases to such an extent that the spring 84 is compressed and the return rake 26 pivots further in the conveying direction until the cutting blade 46 releases the foreign body 86. If the available swiveling range of the throw-back rake 26 is not sufficient to release the foreign body 86, the further increasing pressure will overcome the breakaway force of the rocker 30 and, in the manner described, swiveling the rocker 30 up the cross section between the cutting blade 46 and the conveyor track 14 enlarge further.
- the setting can also be selected such that the rocker arm 30 is pivoted first and then the throw-back rake 26 is optionally also pivoted.
- FIGS. 7 and 8 show a variant of the construction according to FIGS. 5 and 6, wherein the piston rod 88 does not act on the support 34, but on a lever 92 which is pivotably mounted on the support 34 at 90 and which has a pull rod 94 engages through the support 34, the spring 84 being loaded between the end of the pull rod 94 and the support 34 when the throwing rake 26 is loaded in the conveying direction under pressure.
- the translation effect of the lever 92 can be used, for example, by making the articulation point of the piston rod 88 adjustable on the lever 92.
Landscapes
- Refuse Collection And Transfer (AREA)
- Crushing And Pulverization Processes (AREA)
- Branching, Merging, And Special Transfer Between Conveyors (AREA)
- Control And Other Processes For Unpacking Of Materials (AREA)
- Combined Means For Separation Of Solids (AREA)
- Sorting Of Articles (AREA)
- Discharge Of Articles From Conveyors (AREA)
- Framework For Endless Conveyors (AREA)
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19628276 | 1996-07-12 | ||
DE19628276A DE19628276A1 (de) | 1996-07-12 | 1996-07-12 | Beschickungs- und Dosiervorrichtung für eine Müllsortiereinrichtung |
PCT/EP1997/003733 WO1998002356A1 (de) | 1996-07-12 | 1997-07-12 | Beschickungs- und dosiervorrichtung für eine müllsortiereinrichtung |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0912401A1 true EP0912401A1 (de) | 1999-05-06 |
EP0912401B1 EP0912401B1 (de) | 2000-06-07 |
Family
ID=7799738
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP97932824A Expired - Lifetime EP0912401B1 (de) | 1996-07-12 | 1997-07-12 | Beschickungs- und dosiervorrichtung für eine müllsortiereinrichtung |
Country Status (6)
Country | Link |
---|---|
EP (1) | EP0912401B1 (de) |
JP (1) | JP3959105B2 (de) |
AT (1) | ATE193690T1 (de) |
DE (2) | DE19628276A1 (de) |
ES (1) | ES2146478T3 (de) |
WO (1) | WO1998002356A1 (de) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN102700787A (zh) * | 2012-06-27 | 2012-10-03 | 长沙中联重科环卫机械有限公司 | 破袋机和破袋方法 |
CN106986076B (zh) * | 2017-04-21 | 2024-04-09 | 河南中烟工业有限责任公司 | 一种烟梗开包机自动开口机构 |
CN108499459B (zh) * | 2018-05-30 | 2023-11-24 | 潍坊新希望六和饲料科技有限公司 | 一种实验室用粉碎料混合机 |
CN112407700B (zh) * | 2020-12-22 | 2024-01-02 | 山西易通环能科技集团有限公司 | 一种用于农村垃圾处理的大件垃圾分离转运装置及方法 |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4323952C2 (de) * | 1993-07-16 | 1995-07-27 | Benno Gasner | Vorrichtung zur Beschickung einer Müllsortiereinrichtung mit dem Inhalt von Müllsäcken |
-
1996
- 1996-07-12 DE DE19628276A patent/DE19628276A1/de not_active Withdrawn
-
1997
- 1997-07-11 JP JP18706697A patent/JP3959105B2/ja not_active Expired - Fee Related
- 1997-07-12 WO PCT/EP1997/003733 patent/WO1998002356A1/de active IP Right Grant
- 1997-07-12 EP EP97932824A patent/EP0912401B1/de not_active Expired - Lifetime
- 1997-07-12 DE DE59701851T patent/DE59701851D1/de not_active Expired - Lifetime
- 1997-07-12 ES ES97932824T patent/ES2146478T3/es not_active Expired - Lifetime
- 1997-07-12 AT AT97932824T patent/ATE193690T1/de not_active IP Right Cessation
Non-Patent Citations (1)
Title |
---|
See references of WO9802356A1 * |
Also Published As
Publication number | Publication date |
---|---|
WO1998002356A1 (de) | 1998-01-22 |
JP3959105B2 (ja) | 2007-08-15 |
DE59701851D1 (de) | 2000-07-13 |
ES2146478T3 (es) | 2000-08-01 |
DE19628276A1 (de) | 1998-01-22 |
ATE193690T1 (de) | 2000-06-15 |
EP0912401B1 (de) | 2000-06-07 |
JPH10146538A (ja) | 1998-06-02 |
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