CZ139994A3 - Drive for rotary drum as a collecting vessel in refuse collecting vehicles, composting drums or the like - Google Patents

Abstract

A drive is disclosed for a rotating drum useful as a collecting container on refuse collection vehicles, composting drums or the like. The drum has a closed front side with a centrally arranged bearing journal and is rotatably mounted at its opposite, open end by means of a large ball bearing. The inner or outer ring of the large ball bearing is linked to the drum and the open end of the drum may be closed by a lid that can swivel upwards, held on the drum so as to turn therewith, and provided on a truncated cone with a guiding or compacting plate. The large ball bearing has lower and upper bearing supports for supporting the closing lid, its opening cylinder bearing and lid locking arrangement. The lower bearing support (21) is secured by a bolt to the auxiliary frame (3) and the drum (4) is secured by means of driving segments (30, 31, 32) that describe a circular movement, whose length represents a fraction of the circumference of the drum and that engage in the area of a defined circular arc section (b), in a phased manner, the preferably extended roller chain ring (10) at the circumference of the drum. The reference circle of the driving segments (30, 31, 32) is larger than the reference circle of the roller chain ring, toothed wheel (10) or the like to be driven. In a preferred embodiment, the driving unit (16) is mounted on a lower bearing support (21) and is radially adjustable. This driving concept has the advantage of smoothly applying the force required for driving the drum in the area of a circular arc section of the circumference of the drum, so that the bearing and driving elements are less stressed. A simpler, weight-saving embodiment of the rear-side bearing construction and a low-noise drum drive can thus be achieved.

Description

supported by a ball bearing (6). The outer ring (6a) or inner ring (6b) of the bearing (6) is connected to the drum (4) and the open end of the drum (4) is lockable upwardly pivotable relative to the drum (4) by a non-rotatable rear cover (7). on the truncated cone, a guide plate or a compaction plate. The bearing (6) has a lower bearing grip (21) and an upper bearing grip (21a) for receiving the closure cap, receiving its opening cylinder and locking the cap. The lower bearing carrier (21) is fixed by means of a bolt (27) to the subframe (3). The drum (4) has drive segments (30, 31, 32) the length of which is a fraction of the periphery of the drum (4) and which engage in a phase-shifted circumference of the roller chain (10) the drum (4). The pitch circle of the drive segments (30, 31, 32) is larger than the pitch circle of the driven roller chain circuit (10). The drive unit (16) is preferably on the lower bearing carrier (21) and is arranged radially adjustable.

9

garbage collection, composting drums or the like

The invention relates to a rotary drum drive as a collecting pit for garbage trucks, composting drums or the like, wherein the drum has one closed front wall and a central bearing pin thereon, and is rotatably mounted on its opposite open end by a large ball bearing wherein the inner or outer ring of the large ball bearing is connected to the drum and the open end of the drum is closable upwardly pivotal with respect to the drum by a non-rotatable lid having a guide or compression plate formed on the frustoconical cone; rotatable by means of a circular displacement of the driving elements which are engaged with a toothed ring or a fixed roller chain arranged on the circumference of the container or on the outer ring of a large ball bearing, the pitch circle the toothing of the drive elements has a larger diameter than the pitch circle of the driven roller chain, toothing, roller ring or the like, and wherein any points of the drive elements in relation to the rotating drum describe cycloids. The circumference of the eccentric ring, which describes all the points of the drive elements, corresponds exactly to the pitch of the driven roller ring, gear or the like.

D 2 -Analy ⁱⁿ technology

The drive systems of garbage collection vehicles are already known, for example according to AT-P3 362 721, in which the drum engages a pinion by means of a ring gear arranged on the periphery of the drum parallel to the large ball bearing, thereby rotating it. In this embodiment, the rotating vessel is connected to an inner ring of a large ball bearing, the outer ring of which is provided with a box carrier that surrounds it and carries the lid, closure and pinion for drive. Further, EF-PA 0 451 134 describes a garbage truck with a rotating drum as a collection tank, in which the drum is mounted on the outer ring of a large ball bearing. Furthermore, it is known to mount a rotating drum at the rear when fastening the outer ring to a fixed lower beam as described in DE-GM 713 24 10, wherein the closing lid, its opening cylinder and the lid securing are provided by segments on the outer large ball bearing ring. The disadvantage of all these embodiments is that the drive of the drum is effected at one point by means of a pinion acting on the gear ring, thereby generating high local loads and the resulting deformation moments require a strong construction, as already stated, for example, that a large ball bearing has it Freight box carrier. Furthermore, these prior art designs require a planetary gear vlastní for the drive of the gearwheel in order to achieve the desired high gears. A further disadvantage is the generation of high noise, which causes a welded, cast or forged, very inaccurate toothed rim at the perimeter of the container. It is further known from AT-FS 334 S4 to drive a toothed or chain ring which is arranged on the periphery of the drum by means of driving rings which embrace the container over the entire circumference and which perform a cycloid movement relative to the drum. A disadvantage of this arrangement is the fact that high mechanical precision is required, since the storage locations are spaced apart from each other with a slight eccentricity of the drive eccentrics, and in addition a high weight is required in the process; κ puriianecii »· uru — zuum, uteru- surround our eyes and, moreover, still need to be stable in the pressure of x and κ and planetary gearing with eccentric and cyto-toothed gearing is described in —x - ± jjo / oauaie is o o u ... vate o u u u u u o u u o u u u u u u u obv e ee: <o chains, this is mentioned, for example, on page 11 of the Handbuch der Kettentechnik, Arnold und Stolzenberg, 1989, thereby saves toothing of the gear ring. The conventional drive by means of a chain sprocket has, as in the case of a toothed drive. around, here nevyaaau that in trvaiem zaoeru je je jeuen az ave zuoy.

Y-Si-Si describes a string chain dive;

curves segments, utere are uspoiausoy, - ~. -. In parallel and st-er are mounted on lie by rolling. eccentric bearings; support. In addition, the drive has a driven roller chain with a tensioning device, as well as a guide to prevent the chain from being deflected, the curved segments exert an eccentric rotation when the eccentric is rotated. shafts and eccentric supports are circularly displaceable and drive the roller chain by alternating engagement of the spline toothing into the roller chain. FIG. 3 and FIG. 4, in DD 229 468-F3 shown drive arrangement with an eccentric shaft, the eccentric and the corresponding support is formed so that it transmits the circular movement of the cam segments into a translational movement of the chain, two .ví ¹ I \ II metal Yc se gme nvu, jau it is described in au - T u _ - o ilu, but the drive must be blocked because if two curve segments are offset by 18U °, when one segment is in the lowest position, the other segment is in the highest position. Thus, at the same time, both transmission angles are zero, so there are no force X components in the circumferential direction, the drive must stop at this time, making it completely unsuitable for continuous uniform drive of the rotary drum.

SUMMARY OF THE INVENTION It is proposed to provide at least two circular arc-shaped driving elements having drive segments having a fraction of the circumference of the drum over their length and occupying an area of a defined circular arc section as driving elements phase-shifted to a ring gear or a roller chain circuit, a roller circuit or the like in the form of a rolling process, which are driven by at least two known manner uniformly moving shafts thereon in accordance with a number of driving segments of eccentrics arranged therefrom, the radius pitch of the driving segments as is known per se, it is greater by the eccentricity value than the radius of the pitch circle of the roller chain, the toothing or the like. According to a further preferred embodiment of the invention, the shafts of the parallel cranks are optionally synchronized by means of a chain drive, a gear drive, a toothed belt drive, a coupling triangle or the like, the drive having a sliding free bearing in the region of one drive shaft. in the region of the drive shaft coupled to the drive motor, a fixed bearing is provided for radial mobility. By means of this optional measure, the synchronous operation of the drive shafts is ensured, especially at low eccentricities.

The advantage of this drive is that, with a small space requirement, a circumferential force is applied to drive the vessel along the length of the defined circular arc, thereby preventing local overload from acting on the bearing and drive elements. The hitherto heavy box carrier provided in the region of the large ball bearing where it completely surrounds it can now be of a lighter design. ^In addition, this system offers the advantage that the additional, expensive planetary gearing can be eliminated as a front-end upstream of the drum-driven hydraulic motor, since gears of about 1: 100 can be achieved in one stage of the drive according to the invention.

From the point of view of completeness, there are other facts relating to the drive of large drums, which are the reason why the present drive concept is considered to be a substantial further technical improvement. For example, in the case of toothed belt drive, a belt width of about 500 mm is present for commonly transmitted powers and rotational speeds. In addition to the fact that this belt width does not provide any uniform transmission of force, production on the circumferentially arranged toothing for the belt is very costly because high accuracy is required. Drive by a simple chain drive has not proven itself particularly in terms of space requirements, for example in garbage trucks, since additional deflection rollers are required in the area of the drive wheel and the wheel diameters require a specified minimum size to avoid the polygonal effect. However, the space required is not available for vehicles of this type.

According to a further advantageous embodiment of the invention, the drive unit can be provided in its own gearbox, which is directly screwable to the ball bearing of a large ball bearing. However, it is also possible to mount the drive unit, preferably driven by one or two hydraulic motors, directly to the inner ring or outer ring of a large ball bearing, or to form one large ball bearing ring as a housing for receiving drive shafts with eccentrics. By means of the described embodiment, a closed circuit ⁷ siiovj driving and reaction forces on the vehicle frame so that the remaining forces are not transferred. According to a further preferred embodiment of the invention, it would be possible to form the drive unit at the same time as a connecting member of the upper and lower bearing of the large tower surrounding the large ball ball bearing. For this reason, the entire bearing box box beam can be omitted.

Another advantageous embodiment or use of the invention shows the continuous possibility of drive by means of linearly moving toothed racks, tensioned roller chain rods and the like. This is a special case of propulsion, that is to say with an infinite radius of the container, thus creating a direct movable element.

BRIEF DESCRIPTION OF THE DRAWINGS

The invention is explained in more detail below with reference to the drawing.

FIG. 1 is a schematic side view of a drive on a garbage truck. Fig. 2 shows a construction of a garbage truck with the rotating drum lifted in plan view. Fig. 3 shows a rear view of such a vehicle. Xa o'r. 4 shows the drive unit in detail and FIG. 5 shows a section through the drive according to the invention. Giant. G and FIG. 7 show further variants of the drive. and FIG. b shows an embodiment in which the mounting of the drive shafts is carried out directly in the outer ring of a large ball bearing. FIG. 9 shows an embodiment in which a plurality of driving elements are used. X and FIG. 10 shows a structure in the form of a vascular toothing. 11 and 12 are kinematic diagrams of a drive according to the invention. X and FIG. 13 shows a further bearing arrangement on a subframe of a vehicle. X and FIG. 14 shows a drive train with a drive shaft coupling for synchronous operation. and ⁱⁿ FIG. 15 shows the same drive train in section. and ⁱⁿ Fig. 16 illustrates a linear drive pinion when using a coupling gear. Fig. 17 shows the eccentric adjustment of the eccentric according to the invention. and ⁱⁿ Fig. 1S illustrates the kinematic connection and the toothing geometry give cycloid. 19 and 20 show variants of the transmission elements. FIG. 21 shows the control of the synchronous operation of the drive shafts by means of a coupling triangle. and ⁱⁿ FIG. 22 to FIG. 2S are shown in engagement situation poison notlivých stages on the basis of computer simulation for a complete revolution of the eccentric shafts.

Embodiments of the invention

As can be seen from FIG. 1, a drum 4, which serves as a collection container, is rotatably mounted on the garbage collection vehicle 1 having the vehicle frame 2. A bearing pin 5 is provided on the front face of the drum 4. In the open, rear region, the drum 4 is rotatably supported by a large ball bearing 6. The rear cover 2 is mounted pivotable upwardly via the hydraulic cylinder 15. the housing 2 carries a truncated cone-shaped portion 7a having a spiral worm plate 14 for conveying and compacting garbage. On the inner wall of the drum 4 is further provided a helical sheet 13 for conveying the rubbish to the front area of the drum 4. To drive the drum 4 there is a toothed ring or roller chain 10 in which the drive unit 16 engages. Figure 2 is a top view of the rear of the vehicle. The drive unit 16 is mounted directly on the lower bearing carrier 21 of the large ball bearing 6 and in this embodiment has three drive segments 30, 31. 32.

In the rear region, the subframe 3 is connected to a bracket 3a on which the lower bearing carrier 21 is pivotably mounted in a defined region about a vertical and horizontal axis. By means of a centering plate which is connected via a bolt 27 to the two pins 25, 26, which are themselves welded to the bracket 3a of the subframe 3, the large ball bearing 6 is held axially firmly, the lower bearing carrier 21 being simultaneously supported by two sliding bearings. In the rear region, there are also locks 12, 12a of the rear cover 2, which are connected to the lower bearing carrier via brackets 19, 20.

21. ^In FIG. 3 is a rear view of a drive according to the invention. As can be seen here, the large ball bearing 2 each has a one-piece lower bearing carrier 22 and an upper bearing carrier 21a which embrace the large ball bearing 6 in the form of a circular arc from above and below and extending up to approximately the horizontal center of the drum 4. the carrier 21 and the upper bearing carrier 21a (fy) are connected to each other by an outer ring oa. For example, the shaped tubular frame 2S or 23 serves to cover the rear part, possibly also as a holder for the cover plates. ^'T aspount ..i ozxsov 1 IU u *. , aseoi 1 j * - ', jjec <jpc * tr> í, ρ. the oil driving unit 16 is insulated; hydraulic actuator immot or emi / · x- o. and π ecxsegmene) o 0, u 1, o - ρ ixuo u. zuexra - bar length

About the chain vine or toothed ring. Fig. 4 shows a detailed view of the drive according to the invention. The film segments 20, d1, 32 are engaged with a roller chain circuit 10 arranged on the periphery of the drum 4 and non-rotatably embracing it. The two eccentric drive shafts 34, 05 carry eccentrics α, 27, 26, which in this example operate in phase offset of 120 °. The drive unit 16 has its own housing 16a, which can be fastened to a vertically arranged lateral surface of the lower bearing gripper 21 and the upper bearing gripper 21a via a longitudinal bore 30 ± 2 ^{in the} free corner area. while the roller chain ID has a radius 31, the drive segments 10, 31, 22 have a larger radius 22. This difference is given by 22-31 + e. where e is the eccentricity value of the eccentrics 36, 37. 33. 32 perform a circular displacement, each arbitrary point of the drive segments 30, 31, 32 describing an identical circular path with a radius e.

^'T and FIG. 3 is a sectional view of the embodiment of Fig. 4. The housing 16a of the driving unit 16 is thereby immediately fixing the lower bearing support 21, the upper bearing carrier optionally via spacing objhneš 2LA.

41, 42. The drive shafts 34, 35 are mounted in the housing 16a in a rolling manner and are actuated by the ...

Claims (1)

In this case the circuit 10 of the roller chain 10 is connected to the drum 4 without slip by means of a chain carrier 10a. 6 and 7 show further embodiments of the drive. As already mentioned, it is also possible to connect the outer ring 43a of the large ball bearing 4.3 to the drum 4. The inner ring 43 is thereby rigidly connected to the lower bearing carrier 21 and to the upper bearing carrier 21a. The outer ring 43a has a toothed ring 44 into which the drive segments 30, 31, 32 engage, as can be seen from FIG. 6. FIG. 7 shows a variant in which the drive unit 10 is screwed to a large ball bearing 54 by means of a In this embodiment, the inner ring 54b has a spur gear 55 into which the drive segments 30, 31, 32 again engage in phase-displacement. FIG. S shows a particularly space-saving design in which the outer ring 6a forms a large ball bearings 6 at the same time bearings for the drive shafts 56, 56a. The drive shafts 56, 56a are rotatably supported by roller bearings 57, 58 and are rotated by the oil hydraulic drive motor 17 and the spline shafts 56, 56b. The drive segments 30, 31, 32 take up space in the roller chain into separate The rollers 60 disposed on the periphery of the container, the rollers 60, which are mounted on the roller ring carrier 6c, can have a sliding bearing 61 or a rolling bearing. In the embodiment of FIG. 8, the pin 59 is formed simultaneously as an axis for the rollers 22. However, the roller ring formed from the rollers 60 can also be arranged separately from ^and parallel to the large ball bearing 2 '. it can be seen that more than three drive segments can also be provided. The drive segments 65 shown in FIG. 66, 67, 68 are connected via eccentrics 63 and roller bearings 64 to the drive shafts 34, 35 and can be made very narrow and space-saving, since more drive segments 65, 66, 67, 66 are always engaged. The chain or roller chain is fixed to the drum 4 by means of a spring washer 62. As will be explained below, the transmission angle of the drive also increases with the number of drive segments 65, 66, 67, 58 provided. FIG. 10 shows an embodiment of a vascular toothing. The teeth of the drive segments 70, 71, 72 are arranged on a straight line, but the pitch circle radius 82 is nevertheless maintained, thereby ensuring engagement along the entire teeth of the drive segments T1, 71, 72 into the ring gear 74. FIG. 11 schematically illustrates a drive function with three drive segments 30, 31, 32. As can be seen, each of the three drive segments 30, 31, 32 engages along a circular arc t>. the circular arc b of the drive segments 30, 31, 32 with the pitch circle radius 82 practically rolls in relative motion around the circumference of the circle with the pitch circle radius 81 of the roller chain circle 10. The eccentricity δ must be adjusted according to the form in such a way that each tooth of the drive segments 30, 31, 32, when rotating the drive shafts 34, 35, 56, 56a, accurately engages in the gap between the gear ring teeth or the chain 10 of the roller chain. 11. Because the degree of overlap is relatively high due to the parallelogram effect, or a good transmission angle can be achieved, the drive segments 30, 31, 32 can be made relatively short, so that the