阅读说明：本技术 转动传送器 (Rotary conveyor ) 是由 安东·舍勒 沃尔夫冈·格拉夫 于 2015-05-15 设计创作，主要内容包括：本发明涉及一种用于托盘的闭合转动传送器,其具有上回行段和下回行段,它们构成上方和下方的输送轨道,具有将两个回行段相互连接的转向部段,转向元件设置在转向部段中,转向元件与马达相连并且能够由马达驱动,具有在两个回行段中以及在转向部段中无穷转动的牵引元件,牵引元件在转向部段中与转向元件啮合并且由转向元件驱动,具有转动的托盘,其由牵引元件带动并且随着牵引元件转动。第一形状配合或摩擦配合元件固定在托盘的下侧、在转向部段中与设置在该处的、围绕着固定的旋转轴线旋转的第二形状配合或摩擦配合元件产生形状配合或摩擦配合的啮合,其中第一和/或第二形状配合或摩擦配合元件具有在它们相互碰撞时松弛的弹性的缓冲构件。(The invention relates to a closed rotary conveyor for pallets, comprising an upper return section and a lower return section, which form an upper and a lower conveying track, comprising a deflection section which interconnects the two return sections, wherein a deflection element is arranged in the deflection section, which is connected to a motor and can be driven by the motor, comprising traction elements which rotate endlessly in the two return sections and in the deflection section, wherein the traction elements engage with the deflection element and are driven by the deflection element, and comprising a rotating pallet which is moved by the traction elements and rotates along with the traction elements. A first positive-locking or friction-locking element is fixed on the underside of the pallet in the deflecting section in positive-locking or friction-locking engagement with a second positive-locking or friction-locking element arranged there and rotating about a fixed axis of rotation, wherein the first and/or the second positive-locking or friction-locking element has an elastic damping member which relaxes when they collide with one another.)

1. A closed rotary conveyor (1) for pallets (20), which is intended to be used in a closed rotary conveyor

-having an upper (2) and a lower (3) return section, which form an upper and a lower conveyor track (4, 5),

-having a turning section (6) interconnecting the two return sections (2, 3), in which turning sections turning elements (7) are arranged, at least one of which is connected to and can be driven by a motor (8),

-having a traction element (9) that is infinitely rotatable in the upper and lower return sections (2, 3) and in the diverting section (6), which traction element engages with the diverting element (7) in the diverting section (6) and is driven by the diverting element,

-having at least one rotating tray (20) which is entrained by and rotates with the traction element (9),

Wherein at least one first positive or frictional element (30; 130; 230; 330) is fixed on the underside (22) of the pallet (20), which in at least one turning section of the turning section (6) engages in a positive or frictional engagement with at least one second positive or frictional element (50; 350) arranged there, which rotates about a fixed axis of rotation (16), wherein the first and/or the second positive or frictional element (30; 130; 330; 50; 250; 350) has at least one elastic damping means (36; 36, 37; 58), which is relaxed if the first and the second positive or frictional element (30; 130; 330; 50; 350) collide with one another;

Characterized in that the at least one elastic damping member (36; 36, 37) is arranged between the underside (22) of the tray (20) and a rigid member (31) of the first positive-fit or friction-fit element (50; 350), wherein the rigid member (31), but not the at least one damping member (36; 36, 37), is in direct contact with the second positive-fit or friction-fit element (50) in the at least one diverting section (6).

2. Rotary transmitter according to claim 1, characterised in that the second formfitting or friction-fitting element (50; 350) is of disc-or wheel-shaped configuration and the first formfitting or friction-fitting element (30; 130; 330) is in formfitting or friction-fitting engagement with the second formfitting or friction-fitting element (50; 350) in at least one diverting section (6) over an angular range (a) of more than 20 °, preferably more than 35 °, particularly preferably more than 50 °, advantageously more than 60 °, for example 70 °.

3. Rotary transmitter according to claim 1 or 2, characterized in that the first positive or friction fit element (30; 130; 330) is in contact with the second positive or friction fit element (50; 350) over a greater stretch in the direction of rotation (UR) than the corresponding transverse direction (QR) in the at least one diverting section (6).

4. Rotary transmitter according to at least one of the preceding claims, characterized in that the first positive or friction fit element (30; 130; 330) has a concave envelope curve (39) facing the second positive or friction fit element (50; 350) extending in the direction of rotation (UR) of the tray (20), and the second positive or friction fit element (50; 350) has a convex envelope curve (59) facing the first positive or friction fit element (50; 350), preferably an envelope curve (59) corresponding to the concave envelope curve (39) of the first positive or friction fit element (30; 130; 330), wherein the two form-fitting or friction-fitting elements (30; 130; 330) are in form-fitting or friction-fitting engagement on the two envelope curves (39) in the at least one diverting section (6).

5. Rotary transmitter according to at least one of the preceding claims, characterized in that the first positive-or friction-fit element (30; 130; 330) has at least one sector (40) with three or more teeth (41), for example five or seven or nine or more teeth (41), such as 10 teeth (41), wherein the teeth (41) in the at least one diverting section (6) preferably bear in a positive-fit manner against the second positive-or friction-fit element (50; 350) the above.

6. The rotary transmitter according to at least one of claims 1 to 5, characterized in that the first positive-fit or friction-fit element (330) has a substantially uniformly concave friction-fit surface (342) which bears in a friction-fit manner against the second positive-fit or friction-fit element (350) in the at least one diverting section (6).

7. A rotary conveyor according to at least one of the preceding claims, characterized in that the second positive or frictional element (50; 350) comprises a toothed wheel (51) and an endless chain (55) stretched over the toothed wheel (51; 251).

8. rotary transmitter according to claim 7, characterized in that the tooth (41) of the first positive-fit or friction-fit element (30; 130) and the tooth of the gearwheel (51) are not in contact in the diverting section (6) when form-fitted, but only in contact with the links of the chain (55).

9. Rotary transmitter according to at least one of the preceding claims, characterized in that the second positive or frictional element (250) comprises a gearwheel (251), wherein the at least one elastic damping member (58) is fixedly arranged on its outer circumference and is constructed as a preferably completely encircling toothing.

10. A rotary transmitter according to claim 9, characterized in that the second positive or friction fit element (250) comprises a gear wheel (251) comprising a disc-shaped rigid body (252), preferably of metal, on whose circumferential edge the at least one resilient damping member (58) is provided, in the form of a toothed ring and preferably of polyester-urethane-rubber.

11. Rotary transmitter according to at least one of the preceding claims, characterized in that the at least one elastic damping member (36; 36, 37; 58) consists of an elastic plastic, such as rubber.

12. Rotary conveyor according to at least one of the preceding claims, characterized in that the first elastic damping member (36) is arranged on a front side of the tray (20) seen in the direction of rotation (UR) and the second elastic damping member (37) is arranged on a rear side of the tray (20) seen in the direction of rotation (UR).

13. Rotary conveyor according to at least one of claims 1 to 12, characterized in that the resilient damping member (36) is arranged on a front side of the tray (20) seen in the direction of rotation (UR), the first positive-fit or friction-fit element (30; 130; 330) deflecting upon contact with the second positive-fit or friction-fit element around a rotational axis (35) fixed relative to the tray (20), which rotational axis is arranged on a rear side of the tray (20) seen in the direction of rotation.

14. Rotary transmitter according to at least one of the preceding claims, characterized in that a connecting rod (18) is provided in the at least one diverting section (6), in which a guide element, in particular a roller (23), provided on the pallet (20) is guided such that a counter pressure of the first form-or friction-fit element (30; 130; 330) towards the second form-or friction-fit element (50; 350) is produced in order to form and maintain a form-or friction fit.

15. Rotary transmitter according to at least one of the preceding claims, characterized in that the second positive or friction fit element (50; 350) rotates synchronously with the diverting element (7) and is preferably also driven by the motor (8).

16. Rotary transmitter according to at least one of the preceding claims, characterised in that the second formfitting or friction-fitting elements (50; 350) are arranged between the diverting elements (7) of a diverting section (6), advantageously centrally between these diverting elements (7).

Technical Field

The present invention relates to a rotary conveyor.

Background

Such rotary conveyors have long been known. The workpieces placed on rotating pallets (also called workpiece carriers) are transported in an upper return section from one location to another. The workpieces are, for example, mounting parts for vehicle production, which are transported to the mounting belt by means of a pallet. On reaching the mounting band, these workpieces are removed, for example, by a robot and processed by a production machine. Such rotary conveyors are typically provided in different locations for various applications.

The traction elements, which are usually called endless conveyor chains, rotate in two side sections of the rotating conveyor. They are driven by a motor-driven sprocket wheel, which is arranged in both diverting sections. In the known rotary transmitter described in WO 2004/000698 a1, there is a gear on each side of the tray coupled with a hysteresis coupler or a viscous coupler. The two gears mesh with the respective conveyor chains in the respective side sections. The gear does not rotate when the tray is transported unobstructed, but acts like a rigid pin that carries the tray along. When there is an obstacle (in particular a waiting pallet) hindering further operation, the two toothed wheels do not rotate in this position in the continuous further-operating conveyor chain until the resistance caused by the front pallet is no longer present. In order to be able to drive the pallets in the diverting section also by means of gearwheels, the conveyor chains are in this known device configured in two rows or two channels (or three channels), respectively, wherein the two rows of conveyor chains are each rigidly coupled to one another. The two conveyor chains are each driven by means of a sprocket wheel which, however, engages only in one chain (in the three-channel configuration, both chains) so that one chain remains free. The gears of the pallet, which are coupled with hysteresis or viscous couplings, then enter the chain, which thus continuously meshes with the train of conveyor chains.

The known pallet also has working rollers or running wheels on its underside at all four corners, respectively, wherein these running in or on the rails along two return sections which forcibly guide the working rollers and thus protect the pallet. Furthermore, a pawl is arranged below each tray, which pawl is arranged opposite the toothed ring. The pawl forms a positive fit with the chain in the diverting section, thus ensuring a reliable travel of the pallet in the diverting section. But in this configuration the tray cannot be easily removed from the perspective of the operator.

Other constructions are also known from the prior art, which describe solutions for turning trays from an upper to a lower return section in a turning section. In the known configuration, the engagement means provided on the pallet and the correspondingly configured carrier means on the traction element, whose drive is controlled by the signal of the light barrier, have to be synchronized for this purpose. But preferably the steering is effected without interrupting the travel of the pallet. DE 102009056545 a1, for example, shows a solution associated therewith, in which an embodiment with a planetary gear set is described. But this construction is relatively expensive.

Disclosure of Invention

it is therefore an object of the present invention to provide a reliable and cost-effective solution for diverting pallets for delivery from an upper return section to a lower return section and vice versa.

This object is achieved by the features of the following solution.

The advantage of the invention is, in particular, that at least one positive or frictional element is fastened to the underside of the pallet, which, when the pallet is moved into the respective deflection section, engages in a positive or frictional manner with at least one second positive or frictional element, which is arranged in each case and rotates in the at least one deflection section and drives the pallet by means of a positive or frictional fit. When the steering section is moved out of the way, the form fit or friction fit is again cancelled. By being fixed on the pallet, the first form-fitting or friction-fitting element is moved together with the pallet in the at least one diverting section, i.e. does not rotate around itself. According to the invention, the first and/or second positive or friction fit element is/are designed to be elastically flexible. For this purpose, the first and/or second positive or frictional element has at least one elastic damping component. If these two form-fitting or friction-fitting elements touch each other, the first and/or second form-fitting or friction-fitting element may relax. By means of this elastic relaxation, at least one of the two form-fitting or friction-fitting elements is pushed away from the other and is slightly relieved in order then to bear tightly against the other form-fitting or friction-fitting element under the action of a counter-pressure which is generated, for example, by positively guided rollers of the pallet. A strong form fit or friction fit is thus achieved between the two form fit or friction fit elements. Depending on the geometric design of the form-fitting or friction-fitting elements, a relative movement of these elements with respect to one another can be brought about initially (i.e. when the two form-fitting or friction-fitting elements are initially engaged with one another) in the direction of rotation of the tray by elastic relaxation, so that in particular the first form-fitting or friction-fitting element and thus also the tray can be slid into their final position in order to achieve the desired form-fitting or friction-fitting. If a collision occurs between the front edge of the first positive-fit or friction-fit element and the second positive-fit or friction-fit element, a forced jamming and thus mechanical damage of the participating components is avoided by means of the elastic member. Synchronization of the pallet movement with the traction elements is no longer required here.

The invention is further advantageous in that the pallet can be lifted from the upper return section, since no pallets or such like (see above) pointing from inside the traction elements (e.g. conveyor chains) are required to hold the pallet firmly in the diverting section.

According to the invention, if the at least one elastic damping element is arranged on a first form-fitting or friction-fitting element, wherein said damping element is arranged between the underside of the pallet and the rigid component of the second form-fitting or friction-fitting element. In this embodiment, the rigid component is in contact with the second positive or frictional element in the at least one deflection section and is relaxed due to the damping of the at least one elastic damping element when these elements collide with one another.

in particular, it is preferred that a link is provided in the at least one deflecting section, in which link a guide element, in particular a roller, provided on the pallet is positively guided. In the case of the roller, it is moved on the inner side of the connecting rod in such a way that the tray and the first positive or frictional element press against a second positive or frictional element rotating about a fixed axis of rotation, so that the positive or frictional fit is achieved.

It is particularly preferred that the first positive or friction fit element rotates synchronously with the steering element and is preferably also driven by the motor. The first positive-fit or friction-fit element is arranged on an axis on which the deflecting element is also mounted. The structure is easy to implement and low in cost. It also has the effect that the second positive or frictional element can guide the pallet into the diverting section under the co-action of the rollers of the pallet of the track exerting the reaction force moving in this track). The other conveying elements (such as the toothed wheels on the pallets described above, which engage in the conveying chain and are used to effect traction in the upper and lower return sections) can likewise engage with the traction elements, in particular the conveying chain, but preferably do not participate in the conveying of the pallets in the diverting section.

It is particularly preferred that the second form-fitting or friction-fitting element is of disc-like or wheel-like design, while the first form-fitting or friction-fitting element extends over an angular range of more than 20 °, preferably more than 35 °, particularly preferably more than 50 °, for example more than 60 °, for example about 70 °, and that the two form-fitting or friction-fitting elements are in form-fitting or friction-fitting engagement in this angular range in the at least one diverting section. This large angular coverage can be achieved by at least one elastic damping element, which relaxes when the two form-fitting or friction-fitting elements collide with one another and can thus achieve a large contact surface between them, which, after passing beyond the apex, expands continuously from the first form-fitting or friction-fitting element on the one hand as the pallet continues to enter the respective diverting section.

The first positive or friction fit element and the second positive or friction fit element preferably have a larger contact path in the direction of rotation than in the transverse direction. In other words, the effective contact length (in the circumferential direction) is greater than the contact width in this embodiment. In this case, the pallet is guided in a reliable form-fitting or friction-fitting manner over a long distance in the deflecting section.

In a particularly preferred embodiment, the first positive-locking or friction-locking element has a concave envelope curve, which extends in the direction of rotation of the pallet, facing away from the second positive-locking or friction-locking element. It is also preferred that the second positive or friction fit element has a convex envelope curve, which is preferably configured to correspond to the concave envelope curve of the first positive or friction fit element. The concave envelope curve of the first positive-fit or friction-fit element preferably extends over this or the abovementioned angular range.

In the case of a friction fit, the two form-fitting or friction-fitting elements are in friction-fitting engagement in the diverting section on the envelope curves. The friction fit can be achieved over the entire envelope curve or, if the configuration of the friction fit surfaces is not uniform, only in a specific region coinciding with the envelope curve, while other regions lie outside the envelope curve and no friction fit can be achieved.

The concave course of the first positive-locking or friction-locking element and the convex course of the second positive-locking or friction-locking element enable the pallet to be removed from the upper return path in a simple manner.

The first positive-locking or friction-locking element preferably has at least one sector with three or more teeth (for example five or seven or nine or more teeth, for example 10 teeth), which bear against the second positive-locking or friction-locking element in at least one deflection section, preferably in a positive-locking manner. Advantageously, the second positive or friction element is designed as a gear for this purpose. The concave envelope curve mentioned above is in this case defined by the tooth tips of the teeth of the first positive-fit or friction-fit element. Since the synchronization of the first and second positive or friction fit elements can be omitted, the toothing of the first positive or friction fit element can be brought into engagement with the toothing of the second positive or friction fit element in different scenarios. The foremost tooth of the first positive-locking or friction-locking element can, for example, collide with a gearwheel (for example, the second positive-locking or friction-locking element) and, if an elastic component is provided on the first positive-locking or friction-locking element, the elastic component is forced to move upward when the latter is driven from the upper return path to the lower return path and the tray is slid forward or backward in the circumferential direction until the teeth of the first and second positive-locking or friction-locking elements are properly meshed with one another and form the final positive lock. However, this form fit also already occurs when the pallet fit is driven precisely into the deflecting section, with more and more tooth pairs meshing with one another as the pallet continues to be driven forward. As the pallet continues to move forward and thus performs a rotational movement, it forms a positive fit with the subsequent teeth of the two positive-fit or friction-fit elements until all the teeth of the first positive-fit or friction-fit element mesh with the second positive-fit or friction-fit element.

According to a variant, the first positive-fit or friction-fit element comprises a friction-fit surface that is substantially uniformly concave, i.e. without teeth, but with a concave surface of constant radius. The concave envelope curve coincides here with the concave friction interface. In the diverting section, it then rests with a friction fit on a second positive or friction fit element, which preferably has a uniformly convex friction fit surface corresponding to the concave friction fit surface of the first positive or friction fit element. The concave and convex enveloping curves preferably extend concentrically about an axis about which the second positive or friction fit element rotates. In this case, the flexibility of the elastic component also enables a friction fit over the entire surface between the two form-fitting or friction-fitting elements. As the pallet continues to move forward in the turning section, the overall frictional engagement surface increases until it reaches a maximum level. The counter-pressure pressing the pallet against the second positive or friction fit element is preferably generated by rollers of the pallet, which are themselves positively guided in the deflection section.

According to a variant, the first positive-fit or friction-fit element can also be of corrugated or toothed design with the formation of the friction fit, so that no continuous surface contact is produced between the two positive-fit or friction-fit elements with a pure friction fit. According to one variant, the first positive-locking or friction-locking element has a uniformly concave friction-locking surface which bears in a friction-locking manner against the tooth tips of the gear wheel as the second positive-locking or friction-locking element.

In a further variant, the first positive-fit or friction-fit element has a partial engagement, i.e. in particular has two or more teeth and in particular a concave surface. Correspondingly, the second positive or friction fit element has a corresponding opposite side. The force transmission based on the form fit is produced overall.

In a particularly preferred embodiment, the second positive or frictional element comprises a toothed wheel on which an endless chain is wound. The first form-fitting or friction-fitting element is then in form-fitting or friction-fitting contact with the gearwheel or endless chain. The chain stretched over the gear (preferably similar or even identical to a commercially standard wheel chain) is a very inexpensive wear element and can be regarded as a force-receiving and therefore wear-receiving part.

for the form fit, the toothing of the first form-fitting or friction-fitting element (preferably three or more toothings, which preferably form a concave envelope curve and extend within this or the abovementioned angular range) engages in a form-fitting manner in the intermediate space formed by the links of the tensioned chain. It is particularly preferred that the teeth of the first and second positive or friction elements do not touch each other here. In other words, the teeth of the first positive-fit or friction-fit element bear only against the links of the tensioned chain. The toothing of the first and second positive or friction elements is advantageously flattened for this purpose. The wear load is here essentially located on the chain link, which, as described above, can be replaced in the simplest manner when required.

In the case of the friction fit, the friction fit surface of the first positive-fit or friction-fit element is located on the chain link projecting over the tooth tips of the gear. In the event of excessive wear, only the chain needs to be replaced.

It is of course also possible to provide, for example, two or more side-by-side gears which are arranged transversely to the conveying direction and which engage with one (depending on the width) or more first form-fitting elements.

It is particularly preferred that the second positive or friction fit element comprises a gearwheel having at least one elastic, preferably completely circumferential, outer circumferential section of a tooth-like projection as an elastic damping means. If the first form-fitting or friction-fitting element comes into contact with the elastic damping member, the latter relaxes and at the same time exerts a pressure on the first form-fitting or friction-fitting element, which facilitates the form-fitting or friction-fitting. In the case of a gear wheel designed in this way, if the chain is tight (see above), it is pressed into the elastic damping element when it encounters the first positive or friction fit element. If the first positive-fit or friction-fit element has a sector extending in a concave manner (see above), the toothing of this sector is particularly preferably not in contact with the toothing of the gear wheel, neither at the start of the mutual engagement nor at the complete positive-fit.

According to a particularly advantageous embodiment, the second positive or friction element comprises a toothed wheel comprising a rigid disk, preferably made of metal, on the circumferential edge of which a toothed ring made of an elastic material, preferably polyester-urethane-rubber, is provided. Corresponding rubbers are commercially available, for example under the name Vulkollan. An advantage of this embodiment is that the main components of the second formfitting or friction-fitting element can be made of steel and only on the outer circumference must be provided with a toothed rubber or elastic material. After wear of the ring gear, it can be easily replaced, for example with a radial expansion of about 10mm up to its tooth tip. The disk can have a smooth circumferential edge or circumferential fixing grooves or toothed projections, for example, wherein in all of these embodiments an elastic material is provided on the circumferential side. If the chain is stretched over the toothed ring and the first positive-locking or friction-locking element has at least one tooth segment as described above, the teeth of the first and second positive-locking or friction-locking elements preferably do not touch.

In general, it is preferred that the material of the at least one elastic damping element is an elastic plastic, for example a rubber-based or elastic material.

Preferably, the second positive or friction fit element is arranged between the diverting elements in the diverting section, advantageously centrally between these diverting elements. These positions are easy to access because there is relatively much free space between the diverting elements. Furthermore, the central arrangement also prevents the pallet from warping, so that the pallet is smoothly turned in the turning section.

In a further embodiment, at least two elastic damping elements are arranged on the underside of the tray, wherein a first elastic damping element is arranged on the front side of the tray as seen in the direction of rotation and a second elastic damping element is arranged on the rear side of the tray as seen in the direction of rotation. A wobbling movement of the first positive-fit or friction-fit element may therefore occur if the first positive-fit or friction-fit element is moved toward the second positive-fit or friction-fit element (possibly also pressed away upward), and if a subsequent positive fit (for example by a positive-fit interlaced sliding of the teeth of the two positive-fit or friction-fit elements) may also be set back during the further forward movement of the pallet. Thus, two form-fitting or friction-fitting elements in at least one diverting section can be matched to one another.

In all the described embodiments, it is advantageous if on both sides of the deflecting section, in each case, a preferably semicircular connecting rod is provided, along which the rollers of the pallet run, for the purpose of achieving a form-fit or friction-fit, a counter pressure is applied. This ensures a simple and effective guidance of the pallet roller or pallet wheel into the diverting section, which guidance achieves a counter-pressure of the pallet towards the second positive-locking or friction-locking element. By means of the driven second form-fitting or friction-fitting element, the entrainment of the pallet is achieved due to the form-fitting or friction-fitting between the two form-fitting or friction-fitting elements.

The traction elements are preferably designed as drive chains and the deflection elements as chain wheels.

Drawings

The invention is explained in detail below with the aid of the figures. Like reference numbers indicate identical or functionally identical elements.

Wherein:

Fig. 1 shows a rotary conveyor with a diverting section in a partial perspective view;

Fig. 2 shows a turning section with a tray shown in perspective;

3 fig. 33 3 shows 3 a 3 diverting 3 section 3 according 3 to 3 a 3 first 3 embodiment 3( 3 section 3 a 3- 3 a 3 in 3 fig. 32 3) 3 in 3 a 3 side 3 sectional 3 view 3, 3 with 3 a 3 tray 3 and 3 a 3 first 3 form 3- 3 fitting 3 or 3 friction 3- 3 fitting 3 element 3; 3

FIG. 4 shows the tray of FIG. 3 in a perspective bottom view;

FIG. 5 shows the tray of FIGS. 3 and 4 in a side cross-sectional view (taken along B-B of FIG. 4);

Fig. 6 shows a diverting section according to a second embodiment in a sectional side view, with a tray and a first form-fitting or friction-fitting element;

FIG. 7 shows the tray of FIG. 6 in a perspective bottom view;

FIG. 8 shows the tray of FIGS. 5 and 6 in a side cross-sectional view;

Fig. 9 shows a third exemplary embodiment of a deflecting section with a tray and a first positive or friction-fit element in a side sectional view;

FIG. 10 shows the tray of FIG. 9 in a perspective bottom view;

Fig. 11 shows the tray of fig. 9 and 10 in a cross-sectional side view;

Fig. 12 shows a diverting section according to a fourth embodiment in a sectional side view, with a tray and a first form-fitting or friction-fitting element;

FIG. 13 shows the tray of FIG. 12 in a perspective bottom view; and

Fig. 14 shows the tray of fig. 12 and 13 in a side sectional view.

Detailed Description

Fig. 1 shows, in a particular sectional view from above, a rotary conveyor 1 with an upper return section 2 and a lower return section 3, which together form an upper conveying track 4 and a lower conveying track 5 for pallets 20 travelling in sequence. The upper and lower return portions 2, 3 are connected at their two end faces by a substantially semicircular deflecting portion 6. Two guide rails 14 and 15, which are arranged parallel to one another, extend in the upper and lower return sections 2 and 3, respectively. The guide rails 14 of the upper circuit section 2 each extend above the guide rails 15 of the lower circuit section 3, wherein the pair of guide rails 14, 15 are connected by means of the struts of the rack 13. The guide rails 14 of the upper circuit section 2 and the guide rails 15 of the lower circuit section 3 are each connected by a connecting rod 18 arranged in the deflecting section 6. The rotary conveyor 1 thus has two side sections 17 in which an endless rotation of the tray 20 is realized in each case.

In the diverting section 6, in each side section 17 there is also provided a diverting element 7 in the form of a sprocket wheel, which are fixed to a common shaft 10, which shaft 10 defines an axis of rotation 16. The shaft 10 is driven by a motor 8 and an intermediate transmission 11. The endless traction element 9, which here is in the form of a three-channel endless chain, thus extends in each side section 17 and carries a tray 20 which rotates endlessly in the rotary conveyor 1. As shown in fig. 4, the trays 20 have for this purpose toothed wheels 25 which are supported on the side walls 24 in the region of both lateral sides of each tray 20. These gears 25 are coupled with hysteresis couplers 26, respectively, which are provided on the other side of each side wall 24. Such a hysteresis coupler is described in document WO 2004/000698 a 1. If no unusual load is applied to the gear wheels 25, these do not rotate in the traction element 9, but are responsible for traction of the pallet 20. If an obstruction (e.g., a stationary tray 20) occurs, the gear 25 begins to rotate and the tray 20 does not continue to move. Other conventional couplings, such as friction couplings, can of course also be applied instead of the hysteresis coupling 26.

In order to provide a smooth running of the pallet 20 in the rails 14, 15 and the connecting rods 18, they have rollers 23 on the underside 22 of the four corner regions, respectively (see for example fig. 4).

The invention relates to the switching of a pallet 20 in a turnaround section by means of a form fit or friction fit between two form fit or friction fit elements, wherein a first such element is arranged on the underside 22 of the pallet 20 and a second such element is arranged in at least one, preferably two turnaround sections 6.

A first embodiment of a first form-fitting or friction-fitting element is shown in fig. 2 to 5. It is arranged in the middle of the underside 22 of the tray 20 and comprises a rigid member 31 which is elongate and extends in the direction of rotation UR of the tray 20. The rigid component 31 has a sector 40, which has nine teeth here, which form a concave envelope curve 39 with a constant radius. It is also possible to apply sectors 40 with a different number of teeth 41 (instead of nine teeth), for example sectors 40 with three, six, eight or ten teeth 41. The nine teeth 41 here form an angular range a of approximately 70 °. The connection to the underside 22 of the tray 20 is effected by two cylindrical, elastic damping elements 36, 37, wherein the damping element 36 is arranged on the front side of the tray 20 in the direction of rotation UR and the damping element 37 is arranged on the rear side facing away from the direction of rotation UR. The two damping members 36, 37 are fixed to the carrier plate or base plate 31 by means of fixing means 33, such as screws, and are arranged in recesses of the first rigid member 31 directed towards the underside 22 of the tray 20, wherein these damping members 36, 37 are fixed to the rigid member 31 by means of threaded journals (not shown). The fixing of the first form-fitting or friction-fitting element 30 on the tray 30 is achieved in that a gap 38 is present between the rigid component 31 and the underside 22 of the tray 20, so that the rigid component 31 can be deflected upwards due to the elasticity of the damping components 36, 37 when a pressure force occurs in the direction of the underside 22 of the tray 20.

the damping elements 36, 37 are made of rubber, for example, and are polyester-urethane rubber. Such rubbers are marketed, for example, under the name Vulkollan. It is important here that the modulus of elasticity of the damping members 36, 37 is significantly lower than the modulus of elasticity of the rigid body 31.

As can be seen in fig. 2 and 3, the first positive-locking or friction-locking element 50 is in a positive-locking state with the second positive-locking or friction-locking element in the deflection section 6. The second positive or friction element 50 comprises according to the first embodiment a gear wheel 51, which is arranged centrally on the shaft 10 between the two steering elements 7 and is driven synchronously with these steering elements. A chain 55 is stretched over this gear, which preferably has little or no play. Such a chain 55 can be, for example, a conventional wheel chain. The upper side of the links of the chain 55 form a convex envelope curve 59.

When the pallet 20 is driven, for example, from the upper return section 2 into the turnaround section 6, the foremost tooth section 41 of the segment teeth 40 of the first positive-fit or friction-fit element 30 either reaches directly into the intermediate space between the two chain links or collides with a chain link of the chain 55. The resulting forces on the rigid structure bar 31 are blocked in particular by the damping element 36, and damage to the involved components is thus avoided. In the event of such a collision, the tray 20 is slid forward or backward over a short distance until the toothed segment 40 is in form-fitting engagement with the toothed wheel 51.

The toothing 41 of the sector gear 40 preferably does not contact the toothing of the toothed wheel 51 during the entire travel of the pallet 20 in the turning section 6. I.e. a form fit is established between the teeth 41 and the chain 55. This also applies to the other embodiments of fig. 6-8 and 9-11. The toothing of the first and second positive or friction elements is preferably flattened here.

the counter-pressure pressing the first positive or friction fitting element 30 against the second positive or friction fitting element 50 and maintaining this pressed state is here exerted by the connecting rod 18, which is a positive guide for the rollers 23 of the pallet. The tray 20 is thus held on such a rail, establishing the above-mentioned form fit (as will also be explained below as a friction fit).

In the form-fitting state shown (also as in the second and third exemplary embodiments, see below), the contact path in the direction of rotation UR is greater than the contact path in the transverse direction QR (see fig. 4). That is, the effective contact length as viewed in the circumferential direction UR is greater than the contact width in the transverse direction QR.

Even if the foremost tooth segment 41 already forms a positive fit with the gearwheel 50 and the chain 55 (i.e. does not collide with the links of the chain 55) when the pallet 20 is driven into the turnaround section 6, the rigid member 31 is deflected upwards until the first tooth segment 41 crosses the apex. As the tray continues to advance, the situation shown in fig. 2 and 3 then results, wherein in fig. 2 the floor or carrier plate 21 of the tray 20 is shown in a transparent manner for the sake of clarity.

It is also noted here that, as can be seen in fig. 2, a cover 12 is provided before the deflection element 7 on the side of the deflection section 6 facing away from the motor 8. It can also be seen in fig. 4 that, on the underside 22 of the tray 20, on both sides of the first positive or friction-fit element 50, there are provided dry-running blocking pins 29 which, when moving in the opposite direction to a stop (not shown) which can be moved out of the upper reversing segment 2, block the tray 20, wherein the two toothed wheels 25 start to rotate when the traction element 9 continues to move.

In fig. 6-8 a second embodiment of the first formfitting or friction-fitting element 130 is shown, whereas the second formfitting or friction-fitting element 50 is identical to the second formfitting or friction-fitting element of the first embodiment. The cross-sections of the cross-sectional views of fig. 6 and 8 correspond to the cross-sections of the cross-sectional views of the first embodiment. The first positive or friction fit element 150 also has a rigid component 131 here, which is connected to the underside 22 of the tray 20 by a front elastic damping component 36, as in the first exemplary embodiment. In the second embodiment, the rear fixation of the rigid member 131 is different. A double-walled bearing body 34 is provided, to which the rigid component 131 is pivotably articulated about a horizontal axis of rotation 35. If the foremost tooth 41 of the sector gear 40 hits an obstacle, i.e. the gear wheel 51 of the tight chain 55, the rigid member 131 can deflect around its axis of rotation towards the underside 22 of the tray. Furthermore, the mechanism for establishing a form fit between the two form-fitting or friction-fitting elements 130, 50 is also the same as in the first embodiment.

A third embodiment of the first and second formfitting or friction-fitting elements 230, 250, not claimed, is shown in fig. 9-11. In this embodiment, the first form-fitting or friction-fitting element 230 has no resilient cushioning member, but only a rigid member 231, which is fixed (e.g., welded) to the underside 22 of the tray 20. The rigid member 231 has a toothed segment 40 extending in the direction of rotation UR, facing away from the underside of the tray 20, which here also has nine teeth 41, the tips of which define an enveloping curve 39. The angular range a swept by the toothed sector 40 is here likewise about 65 °.

The second positive or friction fit element 250 according to the third embodiment is not a gear wheel made of solid material, but rather has an internal rigid body 252 in the form of a disk or toothed ring with smooth edges, made of steel or aluminum. A resilient damping element 58, in the form of a completely circumferential toothed ring and in particular made of polyester-urethane rubber, is arranged on the circumferential edge of the rigid body 252. The rigid body 252 and the toothed ring-shaped cushioning member 58 together constitute a gear 251. The chain 55 is stretched again over a toothed annular damping element 58.

When the tray 20 is driven into the turning section 6, the teeth of the toothed cushioning members 58 are pressed by the foremost teeth 41 of the rigid members 231, while applying the reaction force of the rigid members 58 to the tray 20. By the elastic relaxation of the damping member 58 and by the guiding of the tray 20 into the connecting rod 18 of the respective diverting section 6, the tray 20 is reliably guided through the diverting section by the form fit of the two form-fitting or friction-fitting elements 230, 250.

Fig. 12-14 show a fourth embodiment, in which a friction fit is established between the first and second formfitting or friction-fitting elements 330, 350 in comparison with the previous embodiments. For this purpose, the first positive or friction fit element 330 differs from the first positive or friction fit element 130 (the elastic damping member 36, which is pivoted about the axis of rotation 35) in that, instead of the toothed segment 40 on the rigid member 331, it has a uniformly concave friction fit surface 343, which in a side view also has the shape of the enveloping curve 39. The angular range a swept by the toothed sector 40 is here likewise about 65 °. The second positive or friction fit element 350 has a rigid body 352 with a convex friction fit surface 353 corresponding to the concave friction fit surface 343.

when the concave friction engagement surface 343 hits the convex friction engagement surface 353, the front edge 344 of the rigid member 331 is loaded and squeezed until full surface friction is achieved between the two friction engagement surfaces 343, 353. The counterpressure is also defined here by the link 18 in the deflecting section 6, which guides the rollers 23 of the pallet 20. By applying an inwardly directed force to the tray 20 via the connecting rod 18, the tray 20 is pressed outwards during the friction fit, so that a reliable guidance of the tray 20 is achieved overall in the diverting section.

The invention generally brings the two form-fitting or friction-fitting elements into contact with one another without damage, because of the clearance caused by the at least one elastic damping element, without the contact between the two form-fitting or friction-fitting elements being lost there (advantageously by the action of the connecting rod 18).

According to a further alternative, which is not shown, the at least one elastic damping element is arranged on the underside of the tray and is in direct contact with the second positive or frictional element in at least one deflection section. For this purpose, according to a fourth embodiment, the concave friction counterface can have a rubber layer with a thickness of a few millimeters, for example. It is also possible that the sector gear 40 according to the first to third embodiments is made of rubber (like the cushion member 58 of the toothed ring shape).

According to an embodiment which is likewise not shown, it is also possible to provide a circumferential rubber layer on the rigid body 351 (fig. 12 to 14) of the second disc-shaped form-fitting or friction-fitting element 350, which constitutes a uniformly convex friction-fitting surface 353. A corresponding concave frictional engagement surface is provided here on the first form-fitting or frictional engagement element 330, which may be free of the damping element 36.

Although it is preferable to use rubber as the material of the elastic buffer member. In some embodiments, however, the elastic damping element can also be embodied as a spring or the like. For convenience and robustness, it is of course preferred to apply rubber.

the invention is illustrated in detail below with the aid of examples. The particulars of the different embodiments can be combined with each other in order to obtain new embodiments, which belong to the present invention. Furthermore, the invention also comprises variants falling within the claims.

List of reference marks

1 rotating conveyor

2 upper return section

3 lower return section

4 upper conveying track

5 lower conveying track

6 turning section

7 steering element

8 Motor

9 traction element

10 shaft

11 speed variator

12 cover

13 shelf

14 guide rail

15 guide rail

16 axis of rotation

17 side section

18 connecting rod

20 tray

21 bottom plate

22 underside of tray

23 roller

24 side wall

25 Gear

26 hysteresis coupler

29 stop pin

30 first form-fitting or friction-fitting element

31 rigid member

32 of concave part

33 fixing device

34 bearing body

35 axis of rotation

36 buffer component

37 buffer member

38 gap

39 concave envelope curve

40 tooth fan

41 tooth system

50 second formfitting or friction-fitting element

51 Gear

55 chain

58 elastic buffer component (toothed ring)

59 convex envelope curve

130 first form-fitting or friction-fitting element

131 rigid member

230 first form-fitting or friction-fitting element

231 rigid member

250 second formfitting or friction-fitting element

251 gear

252 rigid body

330 first form-fitting or friction-fitting element

331 rigid member

343 concave friction mating surface

344 front edge

350 second formfitting or friction-fitting element

352 rigid body

353 raised friction mating surface