DE102020128034A1 - Drive device for a lifting and tipping device - Google Patents

Abstract

The present invention relates to a drive device (10) for a lifting and tipping device (100) with a drive device (20), a carriage (60) and a guide (50) for the carriage (60), the carriage (60) a pivot shaft (62), wherein a gear (40) is provided for temporarily converting a linear movement of the carriage (60) into a pivoting movement of the pivot shaft (62). A traction device (30) is provided for lifting the carriage (60) along the guide (50), the drive device (20) being connected to the traction device (30) via an eccentric drive element (24).

Description

The present invention relates to a drive device for a lifting and tipping device.

A large number of lifting and tipping devices for garbage trucks is already known from the prior art. Lifting and tipping devices are used for lifting and tipping garbage containers to be emptied, in particular garbage cans. A refuse container is moved to a dumping opening of the refuse vehicle by the lifting. The subsequent tipping causes the contents of the refuse container to be emptied through the pouring opening into a collection container of the refuse vehicle.

There are also known lifting and tipping devices that have two separate emptying devices, each for a refuse container. With such lifting and tipping devices, two garbage cans can be emptied independently. Each emptying device has there a lift truck for receiving a garbage container. The lift trucks of two emptying devices can be coupled. Large garbage containers can also be emptied in this way.

In the past, the lifting and tipping functions were often considered separately and performed by two independent drives. In the DE 25 17 247 A1 discloses an electric push and pull device, in particular for lifting and/or tilting loads. the DE 2 146 653 provides separate pressure or lifting cylinders for the lifting movement on the one hand and the tilting movement on the other.

The pamphlets DE 44 17 737 A1 and DE 44 23 718 C1 show devices in which a stationary toothed element, namely the rolling segment, is provided. A cam segment/gear element is provided on the tilting shaft of a lift truck, which, after a certain vertical stroke of the lift truck, engages in the stationary rolling segment, as a result of which a tilting movement is triggered. With these devices, there is a risk that the engagement between the rolling segment and the curve segment will fail, which can lead to damage to the device. Furthermore, both the rolling segment and the curved segment can become soiled by the contents of the refuse container, which can impede or impede the tilting movement.

From the EP 0 358 622 A1 a lifting and tipping device with two stationary chains is known. A lifting truck is moved upwards along the chains to a dumping position by means of two lifting cylinders. The lifting truck has a carriage on each side, which is connected to the chains during the lifting process. Gear wheels of the carriages roll on the chains. The resulting rotation of the gears leads to a tilting movement of the lift truck and the refuse container held on it when the dumping position is reached.

The object of the invention is to provide a more efficient drive device for a lifting and tipping device.

This object is achieved by a drive device according to claim 1.

The drive device for a lifting and tipping device has a drive device, a carriage and a guide for the carriage. The carriage has a pivot shaft, with a gear being provided for temporarily converting a linear movement of the carriage into a pivoting movement of the pivot shaft (pivoting phase).

The drive device has a traction means for lifting the carriage along the guide, the drive device being connected to the traction means via an eccentric drive element.

The process of emptying a refuse container using a lifting and tipping device with a drive device according to the invention can be divided into two phases: first the refuse container is only raised (lifting phase), then it is simultaneously raised and pivoted (pivoting phase). The carriage is also moved further up during the pivoting phase. The swiveling is made possible by the gearbox. Panning requires more force than just lifting. Without an eccentric drive element, the drive device would have to be designed for the pivoting process. In this case it would have too much power for the lifting phase and would be oversized overall, i.e. inefficient. The eccentric drive element makes it possible to provide the required force for the various phases of the emptying process without having to provide an oversized drive device.

The force acting on the traction mechanism is therefore different depending on the orientation of the eccentric drive element. The drive device is preferably connected to the traction means via the eccentric drive element in such a way that the greatest possible force acts on the traction means during the pivoting phase.

The traction device must be robust enough to transfer the forces to the sled. In addition it must be able to transmit the forces both during the lifting phase and during the pivoting phase. In advantageous developments, the traction means is a chain or a belt, in particular a toothed belt. In contrast to a rope, a form-fitting connection to the eccentric drive element is possible with a chain and a toothed belt. Due to the form-fitting connection, the force from the drive device is transmitted reliably and precisely to the carriage, which is particularly beneficial during the pivoting phase.

The drive element preferably comprises an eccentrically mounted first gear, the chain or the toothed belt being in engagement with the first gear.

In the past, lifting and tipping devices often had a hydraulic or electrohydraulic drive. With such drives, the forces required for the pivoting phase can easily be provided. A purely electric drive for the lifting and tipping device, on the other hand, reaches its limits in terms of the forces required or it has to be matched to the pivoting phase, in which case it is oversized in the lifting phase. With the eccentric drive element, however, this is different.

The drive device therefore preferably comprises a drive unit in the form of an electric motor. The drive device particularly preferably has no hydraulic components. An electric motor has significant advantages over the hydraulic drives usually installed in garbage trucks. First of all, several components required for a hydraulic drive, such as e.g. hydraulic unit, hose lines, etc., are no longer required. Furthermore, hydraulic medium such as e.g. oil is no longer necessary, which, for example, can leak and lead to environmental pollution. In addition, electric motors are quieter, which reduces the noise pollution of the operating personnel and the environment. The use of an electric motor that is operated with 24 V DC voltage is particularly advantageous, since the electric motor can then be connected directly to the on-board power supply of the garbage truck. The use of the drive unit according to the invention with an electric motor in garbage trucks with an electric drive is also particularly advantageous. There, an electric motor can be operated directly with the energy from the traction battery of the garbage truck, so that no separate energy storage is necessary.

The power transmission from the drive device to the eccentric drive element should be as uniform as possible. The drive device is therefore preferably connected to the drive element via a drive chain or a drive belt, with the drive element comprising a centrally mounted second toothed wheel which meshes with the drive chain. The gears are preferably firmly connected to one another, in particular mortised and/or welded to one another.

In particular, the first gear is preferably arranged eccentrically on the second gear. Particularly preferably, the second gear has an eccentric bore in which the first gear is arranged centrally. Both gears are preferably round.

The first gear can also be an incomplete gear, for example a semi-circular gear. However, the first gear is preferably a complete gear.

The drive chain or the drive belt is preferably closed.

Both the drive chain or the drive belt and the traction mechanism are therefore engaged with the eccentric drive element. In advantageous developments, the traction means runs in a vertical first plane and the drive chain or the drive belt in a vertical second plane, with the two planes running parallel. This reduces the risk of the drive chain or the drive belt and the traction device touching and damaging each other during operation.

The drive device is preferably arranged above or at the upper end of the guide for the carriage. The drive device is particularly preferably connected to the guide.

The eccentric drive element is also preferably arranged above or at the upper end of the guide for the carriage. In this way, the eccentric drive element is in the optimal position in order to pull the carriage upwards by means of the traction means. In addition, the path between the drive device and the eccentric drive element is short, so that, for example, no deflection of the drive chain is necessary. The drive device preferably comprises a rotatably mounted drive gear wheel. The drive chain is then engaged with the drive sprocket.

The drive unit is preferably arranged below the eccentric drive element.

The number of teeth of the first and the second gear is preferably identical. The number of teeth of the drive gear is preferably smaller than those of the first and second gears.

The guide is preferably a linear guide. As a result, complex deflections of the traction mechanism are avoided. The guide is also preferably arranged vertically. The linear guide preferably comprises two parallel round rods. The round rods preferably run vertically. This minimizes the floor space required by the linear guide and, in this way, the installation space required. The round rods are preferably connected by at least one upper connecting web, particularly preferably by an upper and a lower connecting web, as a result of which the linear guide gains in rigidity. The connecting webs are preferably arranged at vertically opposite ends of the rods. The connecting webs also prevent the slide from falling off the rods.

The drive device preferably comprises a frame which can be fixed to the collection container of the garbage truck. The use of such a frame facilitates the fixation since standardized fixation points are usually specified on the collection container. Preferably, the guide and the drive unit are fixed to the frame and the eccentric drive element is rotatably mounted on the frame.

The carriage can be moved along the linear guide, preferably between a pick-up position and an emptying position. In the pick-up position, a refuse container to be emptied can be attached to the carriage or to a component attached thereto, in particular the lift truck. The carriage is then moved into the emptying position by the drive device. The waste container is first lifted and then tilted. In the emptying position, the contents of the refuse container can fall into a collection container, in particular that of a refuse vehicle, in particular through a pouring opening.

Ropes, chains and other traction devices can be open or closed. If they are open, they have two ends; if they are closed, they have no ends. In advantageous developments, the traction mechanism is open and has a tight strand and a slack strand, with a first end of the traction mechanism being connected to the carriage at a first attachment point. In this way, no complex deflection for the traction mechanism is required on the carriage. The section of the traction means that is responsible for the power transmission is referred to as the load strand, that is to say it runs here from the drive element to the carriage.

The traction means is preferably attached to the first attachment point by means of a joint, in particular rotatable about an axis of rotation that runs perpendicular to the first plane. As a result, movements of the traction device can be better compensated for during operation.

The carriage preferably has a housing. The housing protects the transmission from environmental influences, especially from dirt and moisture. In the area of the first attachment point, the housing of the carriage is preferably tapered and particularly preferably has a recess open to the top on both sides. At the first end of the traction means, two legs are preferably provided, which run parallel. The legs are arranged on both sides outside of the housing and each have a bore. The housing also has a hole. A link rod is arranged in the three bores. Alternatively, an eyebolt could also be provided on the housing, with which the first end of the traction means is connected.

A second end of the traction means is preferably connected to the guide. In particular, the second end is connected to the guide in such a way that it is stationary. The second end can be connected to the guide in a simple manner. The second end is particularly preferably attached to the lower connecting web.

Coming from the drive element, the tight strand runs essentially downwards. Deviations from a purely vertical course result from the shape and movement of the drive element. The tight strand is preferably guided between the drive element and the first end by a first guide unit. The first guide unit preferably has at least two guide gears, in particular exactly two guide gears, between which the traction means is guided. As a result, the section of the load strand running below the first guide unit runs vertically or at least more vertically than the section of the load strand running above the first guide unit, largely independently of the movement and shape of the drive element. This leads to a more even upward movement of the carriage and thus prevents it from jamming. The first guide unit is preferably arranged vertically above the first attachment point on the carriage.

Coming from the drive element, the slack side runs essentially downwards. Deviations from a purely vertical course result from the shape and movement of the drive element. To reduce vibrations, the slack side is advantageously guided by a second guide unit between the drive element and the second end. The second guide unit preferably has at least two guide teeth Vessels on, in particular exactly two guide gears, between which the traction means is guided.

A rotary encoder, in particular a multiturn rotary encoder, which engages with the traction means, is preferably provided for detecting a jammed displacement unit (carriage). In the event of jamming, the traction device does not move, which can be determined using the rotary encoder.

A deflection element for the slack side is preferably arranged on the guide, in particular on the lower connecting web. Coming from the second guide unit, the slack side first runs downwards and is deflected by the deflection element, preferably by 180°, so that it runs upwards before it is attached to the lower connecting web with the second end. In this way, the descent can be controlled, otherwise a jammed moving unit, for example, cannot be reliably detected.

The deflection element preferably comprises at least one sliding piece, in particular a U-shaped sliding piece, on which the slack side is guided. Alternatively, the deflection element can comprise two or more deflection rollers.

In the area of the slack side, a chain tensioning device is preferably provided to compensate for play. The chain tensioning device is preferably part of the deflection element and is particularly preferably located in the lower part of the deflection element.

The carriage preferably has a gear with at least two interacting gear parts for converting the linear movement of the carriage into a rotary movement of one of the gear parts, in which at least one of the interacting gear parts can be blocked by a blocking part.

The gear part, which is rotated, is preferably connected or can be connected to the lifting carriage of the lifting and tipping device and then, in the case of a rotary movement, leads to a tipping movement of the lifting carriage.

Due to the transmission, only a single drive device is required for both the linear movement of the carriage and the tilting movement of the truck. The shifting of the transmission is particularly simple and reliable, since it is done automatically by the blocking part. In particular, it is provided that a blocking of the blockable transmission part causes the transmission to switch from a passive to an active mode. In the passive mode, the gear parts do not move relative to each other. In the active mode, a relative movement takes place between the gear parts, as a result of which the linear movement of the carriage is converted into a rotary movement of the rotatable gear part or a tilting movement of the lifting carriage. In particular, it is provided that in the active mode one of the transmission parts does not move relative to the linear guide.

The gear parts are preferably a rack and a gear wheel.

The drive device preferably includes a controller that is connected to the drive device. The control can also be formed by a common control of the lifting and tipping device. In this case, the drive device has a connection element for an external control, for example part of a plug-in coupling system.

Also disclosed is a lifting and tipping device with at least one emptying device, the emptying device having at least one drive device. The drive device is preferably a drive device as described above. The emptying device preferably has at least one lift truck for receiving a refuse container. The truck is preferably connected to a transmission part of the transmission. A rotary movement of the gear part then leads to a tilting movement of the truck.

A garbage truck with a lifting and tipping device according to the above description is also disclosed.

The lifting and tipping device preferably has two emptying devices according to the above description, which are arranged next to one another in the area of a pouring opening of a collection container of the garbage truck. Accordingly, each emptying device has its own drive device.

The emptying devices can be operated separately (single dump). However, they can also be actuated by the controller in such a way that they can be moved together (synchronism). For this purpose, the emptying devices can include sensors which report the position of the carriages to the controller. The synchronization of both sides when emptying four-wheel containers is preferably monitored by multi-turn rotary encoders that are in engagement with the traction mechanism. The control compares the positions and corrects any discrepancies.

• 1 eine Rückansicht einer erfindungsgemäßen Hub-Kipp-Vorrichtung;
• 2 eine Seitenansicht im Schnitt der Hub-Kipp-Vorrichtung der 1 mit einem Schlitten in einer Ruheposition;
• 3 eine Seitenansicht der Hub-Kipp-Vorrichtung der 1 mit dem Schlitten in einer Aufnahmeposition;
• 4 eine Seitenansicht der Hub-Kipp-Vorrichtung der 1 mit dem Schlitten in einer Schaltposition;
• 5 eine Seitenansicht der Hub-Kipp-Vorrichtung der 1 mit dem Schlitten in einer Entleerposition.

The invention is illustrated and explained below by way of example with reference to the drawings. It shows:

• 1 a rear view of a lifting and tipping device according to the invention;
• 2 a side view in section of the lifting and tipping device 1 with a carriage in a rest position;
• 3 a side view of the lifting and tipping device 1 with the carriage in a pickup position;
• 4 a side view of the lifting and tipping device 1 with the carriage in a shift position;
• 5 a side view of the lifting and tipping device 1 with the carriage in an emptying position.

The one in the 1 The lifting and tipping device 100 shown comprises two emptying devices 102, each with a lifting truck 110 for lifting and tipping refuse containers 130, the lifting truck 110 being arranged on a pivot shaft 62. Each lifting carriage 110 has a receiving comb 112 and an abutment element 114 . Each emptying device 102 is associated with a retaining element (not shown). The emptying devices 102 are arranged side by side on a collection container of a garbage truck (both not shown). The lifting and tipping device 100 includes a controller that is not shown.

Due to the side view, only one of the emptying devices 102 is visible. The lifting takes place along the Y-axis and the tilting around the X-axis of a Cartesian coordinate system, with the Z-axis of the coordinate system running parallel to the direction of travel of the garbage truck. The emptying devices 102 are identical in construction, but are arranged mirrored on a YZ plane running through the middle of the garbage truck. In the following, therefore, only those in the 2 until 5 visible emptying device 102 described in detail.

The emptying device 102 has a drive device 10 . The drive device 10 has a guide 50 with two parallel rods as guide rods 54 for a carriage 60 . The rods run vertically, i.e. parallel to the Y-axis. The guide 50 has two connecting webs 52, 53 at vertically opposite ends, which connect the round rods to one another. The guide 50 is attached to a frame 120 (see 1 ) which is fixed to the collection container of the garbage truck.

The carriage 60 has a housing 64 with guide holes for the rods. Radial bearings are arranged in the guide bores in such a way that the carriage 60 can be moved linearly along the round rods.

The drive device 10 also has a drive device 20 (see FIG 2 ) for moving the carriage 60 along the guide 50. The drive device 20 is connected to the controller and includes a drive unit 22 (see FIG 3 ) in the form of an electric motor. The drive unit 22 is fixed to the frame 120 and drives a rotatably mounted drive gear 25 (see FIG 2 ). A closed drive chain 23 which meshes with the drive gear 25 is arranged on the drive gear 25 . The drive device 10 further includes an eccentric drive member 24 having a first gear 26b and a second gear 26a. The second gear 26a is rotatably mounted on the frame 120 about a second axis of rotation D2.

The second sprocket 26a meshes with the drive chain 23. As shown in FIG. The drive chain 23 thus connects the drive gear 25 to the second gear 26a so that rotation of the drive gear 25 is transmitted to the second gear 26a.

The first gear 26b is eccentrically fixed to the second gear 26a. There is therefore no relative movement between the gear wheels 26a,b. Rather, when the second gear 26a rotates, the first gear 26b is moved on a circular path K about the second axis of rotation D2.

The drive device 10 also includes a traction mechanism 30 in the form of an open chain (see FIG 2 ). The chain has a first end 32 and a second end 34 . The first end 32 is connected to the carriage 60 at a first attachment point 36 . The chain runs in a vertical first plane and is laid over the first sprocket 26b such that it engages the first sprocket 26b. The first gear 26b thus also runs essentially in the first plane. The second gear 26a, like the drive chain 23 and the drive gear 25, runs in a vertical second plane, the two planes running parallel. The planes are perpendicular to the X-axis.

The chain has a tight side 31 and a slack side 33 . The load strand 31 runs between the first gear wheel 26b and the first end 32. The load strand 31 runs from the first gear wheel 26b to a first guide unit 70. The first guide unit 70 has two guide gear wheels 72a, b, whose axes of rotation are parallel to the X-axis and run parallel to each other. The first guide unit 70 is arranged vertically above the first attachment point 36 in every possible position of the carriage. The tight strand 31 runs between the guide gears 72a, b and is guided by them. From there, the tight strand 31 runs to the first attachment point 36. The The chain is rotatably attached to the carriage 60 by means of a joint 37 about an axis of rotation D3 parallel to the X-axis.

A rotary encoder 59 is provided on the upper connecting web 52 . The rotary encoder 59 includes a gear wheel which is in engagement with the load strand 31 . As a result, the gear wheel of the rotary encoder 59 rotates when the tightening strand 31 is moved up or down. The rotary encoder 59 also includes a sensor for detecting a rotation of the gear, which is connected to the controller of the lifting and tipping device 100 . If the carriage 60 jams on the guide 50 or if the traction mechanism 30 jams itself, the gear wheel of the rotary encoder 59 stops rotating. The controller records this fact and can thus determine that there is a fault. The controller can then deactivate the drive device 20, for example.

The rotary encoder 59 can also be used for the synchronism of both emptying devices 102 . The controller can use the two rotary encoders 59 of the emptying devices 102 to detect the speed at which the load strands 31 are actually moving. If the speed differs from one another, the controller can control the drive devices 20 of the emptying devices 102 in such a way that the speeds are adapted to one another again.

The slack side 33 runs between the first gear 26b and the second end 34. Coming from the first gear 26b, the slack side 33 runs to a second guide unit 80. The second guide unit 80 has two guide gears 82a,b, whose axes of rotation are parallel to the X-axis and run parallel to each other. The slack side 33 runs between the guide gears 82a, b and is guided by them. The slack side 33 then runs vertically downwards along the frame 120 and outside the guide 50 , first past the upper connecting web 52 and then past the lower connecting web 53 .

A deflection element 56 (see FIG 3 ) arranged for the slack side 33. The deflection element 56 has three sliders 58a,b,c (see FIG 2 ) that guide the slack side 33 and deflect it by 180°. The second end 34 of the traction mechanism is connected to the lower connecting web 53 at a second attachment point 38 .

A chain tensioning device is provided in the area of the slack side to compensate for play. The middle slider 58b can be changed in position relative to the outer counterparts 58a,c. In this way, the slack side 33 and thus the entire chain can be more or less tensioned.

The carriage 60 also has a gear 40 for converting the linear movement of the carriage 60 into a tilting movement of the lift truck 110 . The gear 40 comprises two interacting gear parts, namely a toothed rack 42 and a gear wheel 44. The toothed rack 42 and gear wheel 44 mesh with one another in every position of the carriage 60. The rack 42 runs vertically. The pivot shaft 62 connects to the gear wheel 44 , the gear wheel 44 being designed as a spur gear of the pivot shaft 62 . The pivot shaft 62 is in several parts. The axis of rotation D1 of the transmission gear 44 and the pivot shaft 62 is parallel to the X-axis. The lifting carriage 110 is arranged on the pivot shaft 62 . Gear wheel 44, pivot shaft 62 and truck 110 are connected to one another in a torque-proof manner, so that rotation of the gear wheel 44 automatically causes the truck 110 to tilt.

In 2 the carriage 60 is in a lower rest position. The carriage 60 is moved into this position when the garbage truck is to be moved and there is no garbage container 130 to be emptied for a short time. For example, this position is approached when the garbage truck is on the way to the unloading point.

In 3 the carriage 60 is in the pick-up position. A refuse container 130 can be arranged on the lift truck 110 in the pick-up position. Now the drive unit 22 is activated, whereupon the drive gear 25 is rotated. The drive chain 23 transmits this movement to the second gear wheel 26a, which then rotates about the axis of rotation D2. The first gear wheel 26b is thereby moved on a circular path about the axis of rotation D2 and in the process moves the traction means 30, the chain, with it. This movement results in the carriage 60 being moved upwards along the guide 50 . In this way, the carriage 60 reaches the in 4 switch position shown. In this position, the rack 42 of the gear 40 comes into contact with the upper connecting bar 52 . The upper connecting web 52 blocks further upward movement of the toothed rack 42.

However, the carriage 60 is moved further, as a result of which the gear wheel 44 rolls on the toothed rack 42 and in the process rotates about its own axis of rotation D1. The pivot shaft 62 is also rotated with the gear wheel 44 and the lift truck 110 is tilted. The truck 110 thus performs a combined upward and pivoting movement.

The circular path of the first gear wheel 26b changes the lever arm, which determines the torque necessary for lifting the carriage 60, continuously. In other words, the tractive force that can be transmitted to the traction means 30 and the carriage 60 and their speed increase as a result of the eccentric drive element 24 with a constant torque. The lever arm is controlled by the geometry and the movement of the eccentric drive element 24 in such a way that the maximum tensile force is achieved for the combined lifting/pivoting movement.

The drive unit 22 remains activated until the carriage 60 has arrived at an emptying position (see FIG 5 ). In this emptying position, garbage can fall out of the garbage container 130 through a pouring opening (not shown) into the collection container of a garbage truck.

The drive unit 22 is then activated again, with its direction of rotation being reversed. As a result, the drive element 24 also rotates in the opposite direction and the carriage 60 moves downwards due to gravity. The rack 42 is spring loaded so that it initially maintains its position as the carriage 60 moves downward. The toothed rack 42 is thus in contact with the upper connecting web 52 until the carriage is again in the switching position (see Fig 4 ) has arrived. As a result, the gear wheel 44 again rolls off the toothed rack 42, but in the opposite direction. Characterized the pivot shaft 62, the lift truck 110 and the garbage container 130 are pivoted back. From the switching position, the carriage 60 moves further down until it has again reached the pick-up position.

To assist in emptying the trash can 130, the trash can 130 may be shaken. Here the drive element 24 is rotated several times in one direction and the other, starting from the emptying position.

Reference List

10

drive device

20

drive device

22

drive unit (motor)

23

drive chain

24

eccentric drive element

25

drive gear

26a,b

gear

30

traction means

31

load strand

32

first end

33

slack side

34

second end

36

first attachment point

37

joint

38

second attachment point

40

transmission

42

rack

44

gear wheel

50

guide

52

upper connecting bar

53

lower connecting bar

54

guide rods

56

deflection element

58a,b,c

slider

59

encoder

60

Sleds

62

pivot shaft

64

Housing

70

first leadership unit

72a,b

guide gear

80

second leadership unit

82a,b

guide gear

100

Lift-tilt device

102

emptying device

110

pallet truck

112

pick-up comb

114

abutment element

120

frame

130

trash can

D1

Axis of rotation of the gear wheel 44

D2

Axis of rotation of the second gear 26a

D3

Axis of rotation of the joint 37

K

circular path

QUOTES INCLUDED IN DESCRIPTION

This list of documents cited by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent Literature Cited

• DE 2517247 A1 [0004]
• DE 2146653 [0004]
• DE 4417737 A1 [0005]
• DE 4423718 C1 [0005]
• EP 0358622 A1 [0006]

Claims (22)

Drive device (10) for a lifting and tipping device (100) with a drive device (20), a carriage (60) and a guide (50) for the carriage (60), the carriage (60) having a pivot shaft (62) having a gear (40) for temporarily converting a linear movement of the carriage (60) into a pivoting movement of the pivot shaft (62), characterized by a traction means (30) for lifting the carriage (60) along the guide (50), wherein the drive device (20) is connected to the traction means (30) via an eccentric drive element (24). Drive device (10) after claim 1 , characterized in that the traction means (30) is a chain or a belt, in particular a toothed belt. Drive device (10) after claim 2 , characterized in that the drive element (24) comprises an eccentrically mounted first gear (26b), wherein the chain or the toothed belt with the first gear (26b) is in engagement. Drive device (10) according to one of the preceding claims, characterized in that the drive device (20) comprises a drive unit (22) in the form of an electric motor. Drive device (10) according to one of the preceding claims, characterized in that the drive device (20) is connected to the drive element (24) via a drive chain (23) or a drive belt, the drive element (24) having a centrally mounted second gear wheel (26a ) which is engaged with the drive chain (23). Drive device (10) after claim 5 , characterized in that the first gear (26b) is arranged eccentrically on the second gear (26a). Drive device (10) according to one of Claims 5 or 6 , characterized in that the traction means (30) run in a vertical first plane and the drive chain (23) or the drive belt in a vertical second plane, the two planes running parallel. Drive device (10) according to one of the preceding claims, characterized in that the drive device (20) and/or the drive element (24) is arranged above or at the upper end of the guide (50) for the carriage (60). Drive device (10) according to one of Claims 4 until 8th , characterized in that the drive unit (22) is arranged below the drive element (24). Drive device (10) according to one of the preceding claims, characterized in that the guide (50) is a linear guide. Drive device (10) according to one of the preceding claims, characterized by a frame (120), the guide (50) and the drive unit (22) being fastened to the frame (120) and the eccentric drive element (24) being fastened to the frame (120 ) is rotatably mounted. Drive device (10) according to one of the preceding claims, characterized in that the traction means (30) is open and has a tight strand (31) and a slack side (33), with a first end (32) of the traction means (30) on a first Attachment point (36) is connected to the carriage (30). Drive device (10) after claim 12 , characterized in that the traction means (30) is attached to the first attachment point (36) by means of a joint (37). Drive device (10) after claim 12 or 13 , characterized in that the carriage (60) has a housing (64), wherein the housing (64) in the region of the first attachment point (36) is tapered. Drive device (10) according to one of the preceding claims, characterized in that a second end (34) of the traction means (30) is connected to the guide (50). Drive device (10) according to one of Claims 12 until 15 , characterized in that the tight side (31) between the drive element (24) and the first end (36) is guided by a first guide unit (70) and/or the slack side (33) between the drive element (24) and the second end (34) by a second Guide unit (80) is performed. Drive device (10) after Claim 16 , characterized in that at least one of the guide units (70, 80) comprises at least two guide gears (72a, b, 82a, b), between which the traction means (30) is guided. Drive device (10) according to any one of the preceding claims, characterized in that net that a deflection element (56) for the traction means (30) is provided on the guide (50). Drive device (10) after Claim 18 , characterized in that the deflection element (56) has at least one slider (58a, b, c) or at least two deflection rollers. Drive device (10) according to one of Claims 12 until 19 , characterized in that a chain tensioning device is provided in the region of the slack side (33). Lifting and tipping device (100) with at least one emptying device (102), wherein the emptying device (102) has at least one drive device (10) according to one of the preceding claims. Garbage truck with a lifting and tipping device (100) according to Claim 21 .

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