EP2411306A1

EP2411306A1 - Sprocket chain drive, in particular having simplified design of wheel bodies

Info

Publication number: EP2411306A1
Application number: EP10711185A
Authority: EP
Inventors: Burkhard Grobbel
Original assignee: Individual
Current assignee: Individual
Priority date: 2009-03-26
Filing date: 2010-03-16
Publication date: 2012-02-01
Also published as: WO2010108816A1

Abstract

The invention relates to a drive chain wheel (A, 100) for a sprocket chain (G) having at least one intermediate body (ZK, 150) mounted in a movable manner that lies in the power transmission path between a rotating wheel body (R, 120) and the driven sprocket chain (G) in the operating state.

Description

Articulated chain drive, in particular with a simplified construction of the wheel body

The invention relates to a drive sprocket for a joint chain, a chain drive chain and a Kettenbecherwerk elevator with such a drive sprocket and a method for driving a joint chain. Furthermore, it relates to a support cam for a drive sprocket.

Articulated chains are used as flexible traction means for transmitting forces. They consist of rigid chain links, which are successively coupled pivotally in joints. The distance between two adjacent joints is referred to as the division of the joint chain. Articulated chains are usually made closed and then run endlessly around at least two wheels. The link chain acts as a drive chain for transmitting mechanical power from one shaft to the other, when one of the two wheels is driven and its rotation is transferred by virtue of the link chain to the other wheel. Another frequently encountered application of articulated chains is that a conveyed material (raw material, components, etc.) is conveyed over a certain distance from the chain or from two or more parallel articulated chains. Such link chains are referred to as conveyor chains.

The drive of articulated chains takes place in most cases by rotating drive sprockets with radially projecting extensions or teeth, which engage in the articulated chain and exert a pulling force on the chain links. The chain can both wrap the drive wheel, that is, at the drive wheel direction reversal of typically 90 ° to 180 ° experience, as well as stretched past the drive wheel, so that the latter engages only along a short distance in the joint chain. A problem with the known Gelenkkettenantrieben is the so-called polygon effect, which arises because the teeth of the drive wheel lie on the corners of a polygon and thus undergoes a periodic fluctuation in a rotation with uniform angular velocity of the effective radial distance of the link chain to the pivot point of the drive wheel. Furthermore, the deviation from the ideal circular shape leads to a relative movement between the Articular chain and the straight force-transmitting here engaging tooth, which leads to high wear due to the effective tensile forces.

In order to improve the interaction of the drive sprockets with the articulated chain, solutions have been proposed in which the teeth engaging in the chain are pivotally mounted about an axis on the wheel body (DE 199 45 921 A1, DE 181 448, DE 159 407). However, the problem remains that the friction during the power transmission causes increased wear of the joint chains.

Against this background, it was an object of the present invention to provide means for driving as low as possible drive of joint chains.

This object is achieved by a drive sprocket according to claim 1, by a chain drive according to claim 22, by a support cam according to claim 29, by a chain bucket elevator according to claim 31, and by a method according to claim 32. Advantageous embodiments are contained in the subclaims.

According to its first aspect, the invention relates to a drive sprocket for a link chain, which comprises the following components: a) A wheel body, which can be rotatably mounted about an axis. For this purpose, the wheel body may, for example, have a hub through which a shaft can be guided, or it may be formed integrally with such a shaft. b) at least one component, which is referred to below as "intermediate body" and which is displaceably mounted relative to the aforementioned wheel body. This storage should also be designed so that the intermediate body comes to lie in the operating state of the drive sprocket (at least temporarily) in the power transmission path from the wheel body to the articulated chain. At least part of the power flow from the wheel body to the articulated chain (preferably the predominant part of about 60-100%) can thus be transmitted from the wheel body via the intermediate body to the articulated chain.

The storage of the intermediate body can take place in virtually any desired way, as long as it is ensured that the intermediate body is in the right place at the right time (that is to say in the force transmission path between the wheel body and the articulated chain).

It is also essential that the displacement of the intermediate body relative to the wheel body. This includes that the intermediate body relative to the wheel body - at least in limits - can move translationally and not (as in the teeth of the known from the prior art drive sprockets) is limited to a purely rotational relative movement. However, the movement of the intermediate body relative to the wheel body optionally also contain rotational components, such rotations are not usually in order a fixed relative to the wheel body axis.

The Verschiebebeweglichkeit of the intermediate body will not be completely arbitrary in the rule, but be determined by stops or the like to certain limits. Furthermore, the displacement movement will usually be limited to a plane perpendicular to the axis of rotation of the wheel body.

The drive sprocket described has the advantage that due to the displacement-movable, "floating" storage of the intermediate body degrees of freedom in the mechanical power transmission chain from the wheel to the articulated chain are obtained, with the help of which the rotation of the wheel body can be kinematically converted into a wear technically favorable movement of the joint chain. In particular, substantially rectilinear movements of the driven chain links can be realized, so that the particularly wear-prone kinking of chain links under force load is largely avoided. Furthermore, wear-prone sliding movements under force load between the articulated chain and the drive sprocket can be avoided or minimized.

As already mentioned, the intermediate body can in principle be stored in virtually any manner. For example, it could be arranged unconnected to the wheel center next to it and be introduced via its own mechanism at the appropriate time into the area of action between the articulated chain and the wheel center. According to a preferred embodiment, however, the intermediate body is (displaceably movable) mounted on the wheel body itself. He is then taken by the rotational movement of the wheel body, which ensures that he always finds himself in the right place of action. Typically, the intermediate body is mounted on the outer circumference of the wheel body. It is particularly preferred if the intermediate body is mounted captive on the wheel body, for example via a suitable linkage, a slotted guide, springs or the like.

The advantageous properties of the drive sprocket would already occur if only a single intermediate body provided or stored on the drive sprocket. Preferably, however, a plurality of N> 1 intermediate bodies is provided which are distributed uniformly over the circumference of the wheel body. With a suitably dimensioned articulated chain, the power transmission can then take place on each driven chain link via such an intermediate body. In general, the plurality of intermediate bodies are formed in such an embodiment substantially similar and stored on the wheel body, but it is theoretically also conceivable to provide differently shaped intermediate body.

The (at least one) mounted on the wheel body intermediate body is preferably relatively by a spring element in a rest position assumed in the unloaded state biased to the wheel body. This ensures that currently not cooperating with the joint chain intermediate body are in a defined position, out of the safe engagement can take place in the joint chain.

In another embodiment of the invention, the intermediate body (at least) on a sensing element which can cooperate in the operating state with an independent of the wheel body, for example fixedly mounted slotted guide. In this way, the intermediate body virtually any movements can be impressed.

Basically, it is only required of the intermediate body that it lies (somehow) in the force transmission path from the wheel body to the articulated chain. For example, the intermediate body could be just one of several mechanical links which in turn transmit force from the wheel body to the link chain. According to a preferred embodiment, however, the intermediate body has a zone or surface which, in the operating state, can come into direct contact with the joint chain, in particular with the joint of a chain link. Because of this direct contact with the articulated chain and the power transmission that usually takes place, this surface is referred to below as the "chain pressure surface". The mobility of the intermediate body is preferably designed so that no relative movement between the articulated chain and the intermediate body occurs at the chain pressure surface or possibly a rolling movement, which is connected in comparison to sliding movements with a significantly lower wear.

According to one embodiment of the embodiment described above, the intermediate body in addition to an auxiliary stop, which can occur in the operating state in (direct or indirect) contact with the articulated chain, for example to the tab of a chain link. A contact between the articulated chain and the intermediate body can thus take place at least two points, namely the chain pressure surface and the auxiliary stop. Preferably, these two points are applied to the same (driven) chain link, so that the relative position of the intermediate body is invariable to this chain link. This has the advantage that no relative movement between chain link and intermediate body occurs, whereby a significant cause of chain wear and Kettenradverschleiß deleted.

For the transmission of power from the wheel body to the intermediate body, in principle, various implementations are conceivable. It is particularly preferred if the wheel body has at least one tooth, via which in the operating state force (directly or indirectly) can be transmitted from the wheel body to the intermediate body. The term "tooth" in this context is to be understood very generally as designation of a component, a component or a region of the wheel body, through which (s) the flow of power is conducted from the wheel body to the articulated chain. Typically, the tooth is - similar to teeth of conventional drive sprockets - a protruding radially from the circumference of the wheel body and firmly connected to the wheel body projection. Furthermore, a plurality of teeth is typically provided, which are distributed uniformly over the circumference of the wheel body. As a rule, an associated intermediate body will then be mounted on the wheel body for each of these teeth.

In the embodiment described above, the power transmission from the tooth to the intermediate body can be done indirectly, d. H. via further intermediate stations or components. However, it is particularly preferred if the intermediate body has a surface or zone which can come into direct contact with the tooth of the wheel body in the operating state. Due to this contact with the tooth and the typical power transmission, this surface is referred to below as the "tooth pressure surface".

In one embodiment of the invention, in which the intermediate body has both the described tooth pressure surface and the chain pressure surface, these surfaces are preferably arranged so that in the operating state during the power transmission, a torque is applied to the intermediate body. In other words, the force exerted by the tooth on the tooth-pressure surface and the force exerted by the intermediate body on the joint chain force (or its counterforce) in the operating state are not in line, resulting in the mentioned torque. Through this torque, a movement of the intermediate body can be specifically caused, which converts this into a defined position. Such a situation is achieved, for example, when the auxiliary stop (if present) described above applies to the articulated chain. The arrangement of the pressure surfaces will, however, usually be such that the torque described is small, because it should only produce the desired movement of the intermediate body, but have no noticeable effect on the joint chain.

During the transmission of force from the tooth to the intermediate body which is in direct contact with it, there will generally be relative movements between these two components. The occurring wear can be counteracted by a special hardening of the contact surfaces and / or by an interchangeability of the contact surfaces. It is particularly preferred if the tooth and the intermediate body each have rolling surfaces, which can occur in rolling contact in the operating state. In contrast to sliding contacts, such a rolling contact results in less wear of the components involved.

The above-mentioned rolling surfaces on tooth and intermediate body are preferably shaped so that during operation a predetermined desired movement of the intermediate body results. In particular, the shape of the rolling surfaces may be such that the from Moving intermediate body driven chain link of the articulated chain on a substantially straight path, which continues the extension of the load strand of the articulated chain. In this case, a force-loaded bending of the articulated chain is largely avoided, which reduces the joint wear of the articulated chain.

The drive sprocket according to the invention can optionally be designed such that it can be reversed, that is, it can operate in a driving manner in both directions of rotation. For this purpose, the intermediate body preferably has two chain pressure surfaces, of which one can come into contact with the joint chain during operation, depending on the direction of rotation of the wheel body.

Additionally or alternatively, the intermediate body has two tooth-pressure surfaces, one of which can come into contact with a tooth of the wheel body in the operating state depending on the direction of rotation of the wheel body.

As already mentioned, the tooth of the wheel body and / or the intermediate body can preferably be hardened and / or for example made of stainless steel. Additionally or alternatively, these parts can also be interchangeably mounted on the wheel body and thus represent relatively easily renewable wear parts. Furthermore, in a development of the invention, the tooth may be positionally displaceably mounted on the wheel body in order to make the drive sprocket adaptable to a change in the pitch of the articulated chain used (for example due to wear after prolonged operation).

According to a further optional embodiment of the invention, the at least one intermediate body is at least partially disposed in the intermediate space between two axially spaced side walls of the wheel body. The prerequisite for this is, of course, that the wheel body has such a gap and such side walls with a distance in the axial direction. This can be achieved, for example, in that, in the case of a wheel body made of solid material, slots are milled into the radially outer end faces as gaps. By the storage of the intermediate body in a gap a good and safe guidance is achieved on the one hand. This is the better, the greater the percentage area of the intermediate body, which is located in the intermediate space. The bearing of the intermediate body should have a sufficient clearance, so that the intermediate body can still move well according to its task (in a plane perpendicular to the axis of rotation of the wheel body). In addition to safe storage of the intermediate body is a further advantage that the part located in the intermediate space of the intermediate body is protected from contact with the articulated chain and thus less interference is exposed with respect to its movement. In a further development of the above embodiment, the intermediate body has an eye opening through which a transverse bolt (of any cross section) engages with play, wherein the transverse bolt is connected to at least one of the aforementioned side walls of the wheel body. The cross pin ensures by its engagement in the eye opening on the one hand, that the intermediate body is stored safely on the wheel body. If the eye opening is an inner opening in the intermediate body (ie no connection to the edge of the intermediate body) and if the cross bolt is connected to both opposite side walls of the wheel body, the intermediate body is even captivated between the two side walls. The size of the eye opening and the remaining play relative to the cross pin determine and limit the mobility of the intermediate body. With a corresponding dimensioning of the eye opening and the transverse bolt, it can furthermore be achieved that the force flow from the wheel body to the intermediate body takes place via the transverse bolt, in which case the transverse bolt will abut against the edge of the eye opening. By appropriate shaping of the eye opening and cross pin can thereby influence the resulting movement of the intermediate body are taken during its contact with the joint chain. In particular, the configuration may be such that a low-wear rolling motion between the cross pin and intermediate body occurs and the effective radius of the transverse pin (with respect to the axis of rotation) in response to the angular position of the wheel body changed so that a desired or optimal movement of the chain links results ,

In another development of the above embodiment, the intermediate body has at least one thickening which does not fit into the space between the sidewalls of the wheel body. Preferably, the intermediate body such thickening symmetrically on both opposite in the axial direction outer walls. The thickening is preferably arranged so that it can come into contact with the wheel body. Since the thickening can not dive into the gap due to their size, in such a contact typically a force from the wheel body on the thickening (and thus on the intermediate body) exerted, whereby the movement of the intermediate body influence can be taken. Preferably, it is thus ensured with the aid of the thickening that the intermediate bodies assume a defined starting position at the beginning of their contact with the articulated chain.

The wheel body can optionally be constructed of two axially spaced plates, these plates are typically held by spacers on the one hand at the desired axial distance and on the other hand connected to each other. With such a construction of the wheel body of two plates, it is particularly manufacturing technology easy to provide a clearance between two spaced side walls (the plates) in which according to the embodiments of the invention explained above, the intermediate body can be arranged.

In another embodiment of the invention, at least one support cam is arranged on the wheel body in such a way that the support cam in the operating state contacts a chain link of a joint chain that is just entering the drive sprocket before the next intermediate body contacts this chain link. The "next intermediate body" in this context is the intermediate body, which assumes the current angular position of the support cam in the executed revolution as the next intermediate body. The support cam influences the meeting of the chain link with the following intermediate body. In particular, speed components of the movement of chain link and intermediate body facing each other can be reduced in order to soften the inlet of the chain link into the intermediate body and to reduce associated noises.

In a further development of the embodiment described above, the support cam is arranged on the wheel body so that it contacts said incoming chain link at a point in which its pitch circle radius is approximately perpendicular to the extension direction of the load strand of the chain. In such a case, the speed of movement of the support cam is particularly small perpendicular to the extension of the joint chain, resulting in a strongly damped meeting of chain link and support cam.

According to a second aspect, the invention relates to a chain drive comprising a link chain and a cooperating drive sprocket of the type described above. That is, the drive sprocket has a wheel body rotatably mounted about an axis and at least one intermediate body, which is displaceably mounted relative to the wheel body, so that it comes to lie in the operating state in the power transmission path from the wheel body to the articulated chain. Due to the special design of the drive sprocket, such a link chain drive achieves almost wear-free operation.

The concrete kinematic and / or dynamic design of the joint chain drive can be done in different ways. In particular, the articulated chain can be looped around (for example by about 90 ° to about 180 °) around the drive sprocket. Alternatively, however, the drive sprocket may also act as an intermediate drive, engaging a substantially straight piece of the link chain. As will be explained in more detail in connection with the figures are various special Embodiments of the drive sprocket for use in wrap or as an intermediate drive particularly suitable.

According to a preferred embodiment of the joint chain drive whose drive sprocket and articulated chain are coordinated so that a power transmission from the drive sprocket on the articulated chain in the operating state only takes place at a maximum of two chain links simultaneously. Preferably, this power transmission is essentially (i.e., more than 70% of a 360 ° rotation of the wheel) only on a single chain link. In a wrap of the drive sprocket through the articulated chain, this condition can be achieved in that the effective pitch of the drive sprocket (something) is smaller than the ideal pitch circle of the link chain. Behind the first chain links gripped by the drive sprocket, the rest of the chain links are then loosely (unloaded) on the drive sprocket. This has the advantage of wear technology that substantially no kinking of the articulated chain takes place under force load.

According to another embodiment of the joint chain drive, this comprises a stationary link, which cooperates in the operating state with the intermediate body of the drive sprocket. This can in particular take place via a scanning element (for example a roller) arranged on the intermediate body, which moves away from the stationary backdrop. If the drive sprocket is used as an intermediate drive, the link can in particular be shaped so that it causes a possible rectilinear movement of the intermediate body in the direction of the joint chain.

Joint chains are known in different embodiments. In principle, all chains which can be driven by conventional sprockets can also be used in the chain drive according to the invention. However, the use of so-called "bush conveyor chains" (eg according to DIN 8165/8167) is particularly preferred. In these, the hinge point between two chain links by a sleeve or sleeve (which is fixedly connected to the first chain link) and guided through this bush bolt (which is fixedly connected to the second chain link) is realized. The force transmission between two chain links is thus advantageously not at points, but along the line or surface in which contact pin and bush in Buchsenförderketten. Especially with force-loaded relative movements between the chain links, the resulting wear can be minimized in this way.

In the above-described link chain drive, the embodiment of the drive sprocket and bush conveyor chain is preferably selected so that the drive sprocket engages force-transmitting only on those bushes, which are opposite to the direction of movement of the chain at the beginning of the associated chain link. This has the advantage that on the drive sprocket earlier reaching neighboring chain link (whose Bolt through the driven bushing) virtually no traction is transmitted. It can therefore be substantially unloaded and thus bend with little wear.

Preferably, in the above embodiment, a bushing conveyor chain of the "cranked" embodiment is used in which each chain link has a pin between its two parallel tabs at the end of the chain link and a bushing at the (inwardly cranked) beginning of the chain link. In such a cranked Buchsenförderkette can be ensured by the alignment of the chain that all sockets against the pulling direction of the chain are seen at the beginning of the associated chain link. If the Buchsenförderkette, however, is not cranked, but by an alternating sequence of inner chain links (consisting of two parallel tabs with two tab ends fixed therebetween bushings) and outer chain links (consisting of two parallel tabs with at both tab ends fixed between bolts) formed is, only every second socket is at the beginning of the associated chain link. The drive sprocket should then attack only at these sockets.

According to another embodiment of the joint chain drive, the drive sprocket has at least one tooth of the type described above, wherein this tooth can continue to engage between two tabs of a chain link of the joint chain. In this way can be achieved by suitably wide dimensioning of the tooth in addition a side guide of the joint chain. Preferably, in this embodiment, the intermediate body is made narrower (by, for example, 5%) than the tooth to minimize any friction between it and the chain link that may be subject to wear and possibly prevent the tooth from its ideal movement.

The invention further relates to a support cam for the drive sprocket of a link chain, which can favorably influence the running of chain links in the rotating wheel body of the drive sprocket. The support cam may optionally be provided on a drive sprocket of the type discussed above, but may also be used on other drive sprockets. It is characterized in that it comprises a metal body which is arranged on a rotatably mounted about an axis wheel body of the drive sprocket such that it resiliently contacts a running in the drive sprocket chain link. In other words, the metal body is dimensioned (weakly) in the section between its attachment point and the point of contact with the link chain so that it can yield elastically to a typical force load at the point of contact. The support cam can thus act in particular noise dampening on the inlet of a joint chain. It is advantageous in this context that except the metal body no further Additional components or materials to achieve the spring action are necessary, ie the support cam can consist of the metal body in the simplest case only.

The metal body of the support cam described may in particular consist of a C-shaped or L-shaped bent sheet metal. Due to the elongated shape of such body then results in a simple manner, the desired spring property.

The metal body may for example consist of steel, in particular of spring steel, which may be heat treated. Furthermore, support cams are preferably provided on both sides on a wheel body and / or on each tooth of the wheel body. The attachment to the wheel body can be done for example by welding, soldering or screwing.

The invention further relates to a chain bucket elevator with the following components: a) (At least) a joint chain, which is equipped with cups for receiving conveyed. b) A deflection around which the articulated chain is guided so that the free chain sections (Lasttrum, Leertrum) are substantially perpendicular. c) At least one drive sprocket of the type described above, which engages in a free chain portion (of the load strand).

Through the drive sprocket, a low-wear or wear-free intermediate drive can be realized in the ascending load strand of the articulated chain. With the same design of the chain can be achieved in this way a larger delivery height of the chain elevator elevators.

The invention further relates to a method for driving a joint chain with a wheel body. In this method, an intermediate body is arranged in the power transmission path between the wheel body and the articulated chain, which shifts during power transmission relative to the wheel body.

The method relates in general terms to the use of a drive sprocket of the type described above. For further information on the details, advantages and developments of the method, reference is therefore made to the above description.

According to a preferred embodiment of the method, the intermediate body during the power transmission is in contact with a chain link of the articulated chain and shifts so that the chain link moves substantially in a straight line. In the following, the invention will be explained by way of example with the aid of the figures. Showing:

Fig. 1 is a side view of a first drive sprocket according to the invention in the looping operation;

Fig. 2 is a section along the line N-II of Figure 1;

3 shows a section along the line III-III of Figure 1;

4 shows a side view of a second drive sprocket according to the invention in the looping operation, in which the teeth have a greater structural strength;

Figure 5 is a section along the line V-V of Figure 4;

6 shows a section along the line Vl-Vl of Figure 4;

Figure 7 is a side view of a third drive sprocket according to the invention, which is used as an intermediate drive.

Fig. 8 is a section along the line VIII-VIII of Figure 7;

Fig. 9 is a section along the line IX-IX of Figure 7;

10 is a side view of a fourth drive sprocket according to the invention, which can be used as reversi erbarer intermediate drive.

11 is a side view of a fourth drive sprocket according to the invention in the looping operation;

Fig. 12 is a section along the line XII-XII of Figure 11;

Fig. 13 is a separate side view of the intermediate body of Figure 11;

Fig. 14 is a separate front view of the intermediate body of Figure 1 1;

Fig. 15 is a separate side view of the wheel body of Figure 11;

Fig. 16 is a section analog to Figure 12, but with two alternative

Embodiments of support cams are shown;

Fig. 17 is a side view of a fifth drive sprocket according to the invention, which is used as an intermediate drive;

Fig. 18 is a section along the line XVI-XVI of Figure 17;

Fig. 19 is a separate side view of the intermediate body of Figure 17;

Fig. 20 is a separate front view of the intermediate body of Figure 17;

Fig. 21 is a separate side view of the wheel body of Fig. 17;

Fig. 22 is a side view of a sixth invention

Drive sprocket, which is used as an intermediate drive and has a circumferential slotted guide; Figure 23 is a schematic side view of a Kettenbecherwerk-elevators according to the present invention with a lower guide wheel.

Fig. 24 is a schematic side view of a Kettenbecherwerk-elevators according to the present invention without a lower pulley.

In the figures, identical or similar components are given reference numerals that differ by multiples of 100. Furthermore, important components in addition to the reference numerals have letter abbreviations for labeling regardless of the particular embodiment.

Articulated chains are used in many, mostly industrial, processes because of their robustness and relatively low cost. Of particular importance are the chain drives, in which the chain wraps around the sprocket and is thereby driven by it ("drive sprocket"). Furthermore, chains are used to promote goods. However, long conveyor lines result in high tensile forces in the chains due to friction and / or work to be done. The chains are to be dimensioned for this, which makes them heavy and expensive.

The joint chains used must normally be lubricated and are usually subject to considerable wear. Here, the present invention seeks to remedy this situation.

In this regard, FIG. 1 shows in a side view a drive sprocket designated by the reference symbols A and 100 according to a first embodiment of the invention. Furthermore, a part of the driven joint chain G is indicated in the figure.

The link chain G consists in a known manner of a series of individual chain links KG, which are connected at their ends in a joint GE pivotally connected to each other. Between the joints GE extend parallel to each other two tabs KL.

The joint chain drive according to the invention can be used in principle with all types of joint chains together. In the following examples, however, a bushing conveyor chain G is specifically used. In this, the chain joint GE between two chain links KG is formed by: a sleeve-shaped bushing BU, which is fixedly connected to the tabs KL of the first chain link, and by a bolt BL, which guided through this bush BU and fixed with the tabs of the second chain link connected is.

Optionally, the socket may still be surrounded by a roller (not shown). Furthermore, a cranked embodiment of the bush conveyor chain G is assumed, in which the tabs KL of the chain links KG (perpendicular to the plane in FIG. 1) pop up. In this way, each chain link has an end with a long distance of the tabs KL, to which a bolt BL is fixed, and a start with a closer distance of the tabs KL, to which a socket BU is fixed. The chain links can then all be identical. The cranked Buchsenförderkette G is guided with such an orientation to the drive sprocket A that each chain link KG the drive sprocket A in operation first with its socket side (contrary to the direction of movement seen so the "beginning" of the chain link) and then with its bolt side ("end" ) reached.

In conventional drive sprockets with fixed teeth wear of the driven joint chain occurs mainly by the fact that under force load, a relative movement (sliding movement) between the teeth and the chain links and a kinking of the chain links under force. This should be avoided with the drive sprockets according to the invention.

The drive sprocket A shown in Figure 1 has for this purpose initially in a conventional manner a wheel body R and 120, which is rotatably mounted about a rotation axis X. Along its outer circumference, the wheel body evenly distributed radially projecting teeth Z and 110 on. The number or the distance of the teeth Z is selected according to the pitch of the driven joint chain G. Furthermore, the power flow from the wheel body R to the link chain G as usual passes through these teeth.

Unlike usual, the teeth Z in the drive sprocket A, however, do not act directly on the chain links KG, but indirectly via an "intermediate body" ZK or 150. The intermediate bodies ZK are (within limits) freely displaceable or "floating" relative to the wheel body R stored in front of the associated teeth Z. Each intermediate body ZK has the following components:

A substantially radially extending web with a "chain-pressure surface" 151, which at the moment of the drive contact with the chain links KG (more precisely, the outer surface of the chain joint GE) receives and thus transmits the required tensile force on the chain link. This can be recognized by the position marked "P1".

A "tooth pressure surface" W2, which comes into contact with a surface W1 on the associated tooth Z during the force transmission. Since in the illustrated embodiment during this contact a low-wear Rolling motion is executed, the respective surfaces are also referred to as "rolling surfaces" W1, W2.

A substantially tangential Aufsitzsteg 152 on which the bushings BU of the chain links loosely rest when the power transmission is completed (behind position P2).

A body referred to as "carrier" 153, which provides inter alia for storage on the wheel body R.

An auxiliary stop 154 arranged at the end of the carrier 153, which is designed here as a roller.

When a tooth Z engages with the intermediate body ZK lying in front of it during the rotation of the wheel body R at the position P1 in the link chain G, the chain pressing surface 151 comes into contact with the bush BU of a chain link. The in the wheel plane (x, y plane) locally freely movable intermediate body ZK can initially dodge, he turns under the effect of the resulting torque to the (wandering) contact point to the tooth Z. This evasive movement of the intermediate body ZK ends when it abuts with the auxiliary stop 154 on the tabs KL of the contacted chain link. From this point on, the intermediate body ZK assumes a constant position relative to the contacted chain link. During the subsequent power transmission to the chain link, therefore, there is no relative movement (either sliding or rolling) between the intermediate body ZK and the contacted bush BU of the chain link. This minimizes the wear occurring in the contact area.

The rolling surface W1 on the tooth Z follows the kinematically prescribed circular movement about the axis of rotation X. This results in a rolling (rolling) of the rolling surface W1 of the tooth on the tooth-pressure surface W2 of the intermediate body ZK, wherein during the rolling motion, the driving force from the tooth to the Transferring intermediate body. Since only one rolling movement - but no sliding - takes place, the wear is minimal. For further reduction of wear, the rolling surfaces W1, W2 may optionally be designed to be hardened.

The teeth Z may optionally have a pressure projection 11, which carries the rolling surface W1, and a holder 112 for this pressure projection. These components can be separate components from the wheel body R, which are subsequently mounted on the wheel body (for example, screwed tight). This makes it possible to produce the wheel body R from inexpensive material and the particularly loaded tooth components of a cured material, which can also be replaced if necessary. The geometric shape of the rolling surfaces W1, W2 to tooth Z or intermediate body ZK is made so that the kinematically predetermined circular motion of the tooth Z leads to a linear possible further movement of the contacted chain link KG. This has the advantage that the under train load chain links must perform as good as no wear-prone kinking movement.

Once the drive sprocket A has rotated further by about one pitch (i.e., 45 ° in Figure 1), a new tooth engages the wrist chain G, and the previously driving tooth Z and intermediate body ZK are relieved. In Figure 1, this is recognizable by the fact that behind the position P2, the contact between the chain pressure surface 151 of the intermediate body ZK and the articulated chain is lost. The Abknickbewegung the chain links is therefore in the (completely or almost) unloaded condition, whereby the joint wear of the joint chain is minimized. This relief is achieved by a suitable dimensioning of drive sprocket A and joint chain G. According to this dimensioning of the described by the intermediate bodies ZK effective pitch circle is smaller than the ideal pitch circle, which belongs to the division of the joint chain G. Because of their slightly greater distance, the chain links GE thus run slightly ahead of the teeth Z or intermediate bodies ZK of the drive sprocket A. A force transmission to the articulated chain therefore takes place only on the first engaging teeth in the region of the position P1.

In the exemplary embodiment illustrated in FIG. 1, the intermediate bodies ZK are in each case captively fastened to the wheel body R via holding rods 155. The support rods 155 have slots 156 through which a guide pin 121 fixed to the wheel body R projects. Furthermore, stop pins 122 are provided on the wheel body, which limit the pivoting movement of the support rods 155.

Furthermore, at least one (tension) spring 157 is provided for each intermediate body ZK, which is articulated on the one hand in an abutment point 123 on the wheel body R and on the other hand on the intermediate body ZK. By this spring, the intermediate body ZK is biased in the force-free state in a predetermined rest position (see position P3), in which it is optimally positioned for the upcoming engagement in the joint chain G.

It should be noted that the recognizable in the figures parts such as springs, handrails, etc. are usually provided symmetrically on both sides of the wheel body.

The described articulated chain drive has the following advantages: No frictional wear, as the product of frictional force and friction path is zero (limits with respect to load capacity are only possible through the permissible Hertzian pressure depending on material and heat treatment).

The structure is insensitive to dirt (no elaborate gasket required).

Normally no lubrication is required.

Teeth Z and intermediate body ZK are relatively inexpensive realized in stainless materials, the wheel body R can be performed in mild steel.

All types of chains (e.g., gall chains) can be operated wear-free or significantly reduced in wear.

By a suitable adaptation of the rolling surfaces on teeth Z and intermediate bodies ZK, a polygon reduction or a perfect polygon compensation can be achieved.

The pitch of the drive is adaptable to a worn (elongated) chain when positionally variable teeth are used and their radius (or pitch circle) is increased on the wheel body. The teeth Z may be screwed to the wheel body, for example.

In the event of wear, it is no longer necessary to be able to replace the complete drive sprocket; instead, only the intermediate bodies ZK and teeth Z are replaced (if at all).

The wheel body no longer needs a shaft-hub connection, but can be attached directly and permanently to the drive shaft (e.g., by welding). The attachment to the shaft can thus be designed cheaper than a normal sprocket.

In the case of the looping chain drive, the tabs KL of the chain links can be used for support. This is very inexpensive, very simple and very robust.

A drive sprocket A or 200 is shown in FIGS. 4 to 6, which represents a modification of the previously described embodiment. Functionally and structurally, the drive sprocket 200 substantially equals the drive sprocket 100, so that not all details have to be described again. The main difference is that in the wheel body R additional slots 225 are provided, in each of which a pin 258 of an intermediate body ZK engages. The pins are in the slots usually with significant clearance (ie, virtually free) movable and are effectively limited only by stop at the slot ends in their mobility. This realization of a stop makes it possible to give the teeth 210 a higher structural strength. Furthermore, the intermediate bodies ZK are stabilized (and stored captive), since the pin 258 connects their flanks on both sides of the wheel body R.

FIGS. 7 to 9 show a third embodiment of a drive sprocket A or 500, which is designed for use as an intermediate drive. The driven link chain G thus no longer wraps around this wheel, but runs above the wheel substantially straight. The rectilinear movement is to be supported by the drive sprocket 500 as possible without wear and without interference. For this purpose, the drive sprocket 500 is formed substantially similar to the wrap-around drive sprocket 100 described above (identical or similar components to the drive sprocket 100 have references increased by 400). It has the following components:

A wheel body R or 520 with a rotation axis X.

Radially projecting, distributed over the circumference of teeth Z and 510 with pressure projections 51 1 and associated brackets 512, wherein rolling surfaces W1 are provided on the pressure projections.

Intermediate body ZK or 550 with a chain-pressing surface 551, a Aufsitzsteg 552, a carrier 553, and a tooth-pressure surface W2, which cooperates with the rolling surface W1 of the teeth.

On both sides at least one spring 557, which biases the intermediate body in the force-free state in a defined rest position.

The function of these components is substantially similar to the drive sprockets already described, i. H. The teeth Z exert pressure on the intermediate bodies ZK, which they pass on to the joint chain G.

A difference of the drive sprocket 500 is that the intermediate bodies 550 have sensing elements 559 (here in the form of rollers). These act together with a fixed slide guide, which consists in the example shown of two rails S1 and S2. The interaction takes place during the force-transmitting phase and ensures that the intermediate bodies 550 perform substantially only a translation parallel to the direction of extension of the joint chain G (x-direction). As a result, on the one hand force-loaded friction movements between the intermediate bodies 550 and the joint chain G and the teeth are avoided, on the other hand also wear-prone bending movements of the chain under force load. The shaping of the rolling surfaces W1 and W2 of the teeth 510 or of the intermediate bodies 550 can take place such that a rolling contact (without sliding) takes place between these components and / or that a polygonal effect is compensated.

The described (quasi) noise-free intermediate drive provides the ideal implementation of the rotational movement of the drive shaft of a motor in a linear, polygonwirkungsfreie movement of the chain.

Figure 10 shows a drive sprocket A and 600, which can be used as a reversible intermediate drive for link chains G. Basically, its structure is similar to the drive sprocket 500 described above, wherein identical or similar components have been increased by 100 reference numerals.

In order to enable the drive of the link chain G in both directions, the teeth Z and 610 of the drive sprocket 600 on two opposing rolling surfaces W1 and W1 'on. These may alternatively cooperate with corresponding tooth pressure surfaces W2 and W2 'on the intermediate body ZK or 650. For this purpose, the intermediate body 650 encompasses the tooth 610 in a clip-like manner with one end of its carrier 653.

Furthermore, two opposing chain pressure surfaces 651 and 651 'are provided on the intermediate body 650, between which a Aufsitzsteg 652 is located. Depending on the direction of rotation of the wheel body R, one or the other of these chain pressure surfaces comes into force-transmitting contact with the chain links.

Further, again on each intermediate body 650, a sensing element 659 is provided, which is guided in a stationary slide guide consisting of two rails S1 and S2. In the example shown, this link guide is slightly bent in order to counteract the risk of slipping of the joints of the intermediate bodies 650. The infeed and outfeed of rails S1, S2 are curved to reduce the speed of the chains in the y-direction and to minimize shock and noise.

Finally, a tension spring 657a and a compression spring 657b are provided, which are articulated on one side in points 623, 624 on the wheel body R and on the other hand on the intermediate body 650. These springs serve to bias the intermediate body in a defined rest position.

As already mentioned, parts such as springs, handrails, rails etc. are generally provided symmetrically on both sides of the wheel body. FIGS. 11 to 15 show a further embodiment of a drive sprocket A or 300 around which a link chain G is guided in the looping operation. The basic operation is similar to the first drive sprocket 100, wherein the same or similar components by 200 increased reference numerals.

The drive sprocket 300 has a wheel body R or 320 with radially projecting teeth Z and 310, wherein this wheel body is shown separately in FIG. 15 for better visibility (together with a section along the line S-S). In the region of each tooth Z, an intermediate body ZK or 350 is provided and arranged on the wheel body R so that it (in limits) is freely movable in the xy plane. A side view and a front view of an intermediate body ZK are shown separately in Figures 13 and 14.

The drive sprocket 300 differs from previous embodiments in that the wheel body R consists of two plates (or sidewalls RW1 and RW2) spaced axially (i.e., in the direction of the rotation axis X) and enclosing therebetween a clearance ZR (see cross-sectional view of Fig. 12). The two side walls RW1 and RW2 can be identical and can be cut out, for example, from a sheet metal plate of suitable thickness. Their axial distance they get by spacers (not shown), which are typically arranged in the space ZR in the vicinity of the axis of rotation X.

In the area of the teeth Z, the gap ZR between the two side walls RW1 and RW2 is used to accommodate there a part of the intermediate body ZK. By a sufficiently large clearance in the axial direction, the mobility of the intermediate body ZK can be ensured in the xy plane, while simultaneously cause the side walls RW1 and RW2 lateral stabilization of the position of the intermediate body. Thus, a guide of the intermediate body ZK is achieved in a simple manner, which ensures a robust behavior when engaging an intermediate body in the joint chain G. In particular, the side walls RW1 and RW2 protect the intermediate body ZK from coming into contact with the link plates KL of a chain link and thereby being disturbed in its trajectory. In contact with the joint GE of an incoming chain link is only a chain-pressure surface 351 on the front side of the intermediate body ZK. In the example shown, this chain-printing surface 351 is formed (inter alia) by a thickening 352 (in the direction of the axis of rotation X). In the region of the thickening 352, the intermediate body is too wide for immersion in the intermediate space ZR between the side walls RW1, RW2 of the wheel body. At certain stations of the rotational movement (eg P1 in FIG. 11), the thickenings 352 therefore rest on the end faces of the side walls RW1 and RW2, whereby a further support and guidance of the intermediate body ZK is effected and these in particular receive a defined starting position when engaging in the articulated chain G.

The intermediate bodies ZK can be cut in a simple manner from a sheet material of suitable strength. The thickenings 352 can then be attached to the cut sheet metal parts z. B. are fixed by welding. Advantageously, the part of the intermediate body ZK produced in this way is subsequently hardened.

As can be seen in particular from the separate illustration in FIG. 13, the intermediate bodies ZK have an inner (completely closed) eye opening AO. Through this eye opening, a transverse pin QB is guided during assembly of the drive sprocket A, which is then connected to the two side walls RW1 and RW2 of the wheel body R (eg by welding). As a result, on the one hand, the intermediate body ZK is captively mounted on the wheel body R, on the other hand takes place via the transverse pin QB the power transmission from the wheel body R to the intermediate body ZK.

The aforementioned power transmission takes place in the contact area between the transverse pin QB and the eye opening AO. The contacting surfaces are in turn designed as rolling surfaces W1 on the transverse pin QB or W2 on the intermediate body ZK and shaped so that the desired movement of the intermediate body ZK is established during the power transmission and the rotation of the drive sprocket. Further control of the movement of the intermediate body ZK via sensing elements, which are realized here by axially projecting from both sides of the intermediate body rollers 359. In the area of entry into a joint chain G and in the power transmission zone, these rollers 359 come into contact with guide slots S1 and S2 mounted in a stationary manner (on both sides) next to the wheel body R, whereby the intermediate body ZK experiences a forced guidance. The expert can determine the optimum shaping of the guide slots S1 and S2 theoretically or by simple tests in accordance with the predetermined target criteria (eg a straight movement of the articulated chain G in the drive region).

The drive sprocket 300 has the advantage that it can be manufactured in a simple manner with few individual parts, while at the same time ensuring an extremely robust operating behavior. In particular, the essential components, i. H. the wheel body R and the intermediate body ZK, simply cut out of sheets and mounted in a few steps. This makes it possible to use the entire drive sprocket as a wearing part.

In the figures support cams 330 are further recognizable, which in pairs between successive teeth Z of the wheel body R on both sides axially outward are arranged projecting. The support cams 330 are typically made of hardened steel and positioned to contact a chain link entering the drive sprocket A before the subsequent intermediate body ZK contacts that chain link. In FIG. 11, this can be recognized by the support cam 330 located in the upper vertex position P1. The pitch circle radius of the support cam 330 (starting from the rotation axis X) is approximately perpendicular to the load strand of the link chain G in this position. The support cam 330 strikes the chain link in this position due to its positioning at a low speed in the y direction typically moved down in negative y-direction. The clash of chain link and support cam 330 is therefore relatively quiet. After its contact with the chain link, the support cam 330 imprints the speed of the wheel body R on the chain link, so that the chain link is synchronized for the contact that occurs shortly thereafter with the next intermediate body ZK and this contact is also noise-dampened.

Figure 16 shows in a section similar to Figure 12 (i.e., along the line XII-XII of Figure 11) two alternative embodiments of support cams SN1 and SN2. The basic function of this support cam is the same as that of the support cam 330 in Figure 12, d. H. the damping of the entry of a chain link KG in the drive sprocket. The illustrated support cams SN1, SN2 consist of an L-shaped (SN1) or C-shaped (SN2) metal body, which can be produced by edges of a metal sheet. The metal body is fixed to the wheel body R, for example, by welding or by screw (s) (not shown). To stabilize the distance between the side walls RW1 and RW2 of the wheel body, a spacer sleeve DH is preferably inserted between these walls.

The support cams SN1 and SN2 are preferably made of spring steel, which may additionally be heat treated. Due to their "light" shape and the choice of material is achieved that they can yield elastically in a contact with a chain link KG (slightly).

The described support cams SN1, SN2 can be used in various embodiments of drive sprockets. In particular, conventional drive sprockets can hereby be executed or retrofitted.

In Figures 17 to 21, another embodiment of a drive sprocket A and 700 is shown, which transmits the above-described for the drive sprocket 300 new design features on an intermediate drive.

In principle, it is again the case that a wheel body R or 720 rotatably mounted about an axis X has radially projecting teeth Z and 710, respectively Intermediate body ZK or 750 drivingly engage in a stretched joint chain G. As with the drive sprocket 300, the wheel body R consists of two sidewalls RW1 and RW2 (see Fig. 18) defining therebetween a clearance ZR in which the intermediate bodies ZK are (partially) arranged. The intermediate bodies for this purpose in turn have eye openings AO, through which a transverse pin QB is guided, which is fixed axially at both ends to the teeth Z of the side walls RW1 and RW2. Furthermore, the intermediate bodies ZK have thickenings 752 in the axial direction, the chain pressure surfaces 751 of which come into contact with the joints GE of the chain and can be seated on the end faces of the side walls RW1 and RW2. The power transmission from the transverse pin QB on the intermediate body ZK is again via rolling surfaces W1 and W2 on the cross pin QB and the intermediate bodies ZK.

For additional guidance further sensing elements are provided, here in the form of axially on both sides of the intermediate bodies arranged rollers 759. These rollers come in the region of the chain engagement with the guide rails S1 and S2 in touch. In order to keep those intermediate bodies, which are not in contact with the articulated chain G, in a defined position, the intermediate bodies are further biased by springs 757 into a rest position. The springs 757 are typically provided on both sides of the wheel body R.

FIG. 22 shows a further drive sprocket A or 800 for an intermediate drive, which represents a modification of the drive sprocket 700 described above. The difference is that the stationary slotted guides or rails S1 and S2 are designed and extended in such a way that they provide a defined position of the intermediate bodies during the entire rotation in cooperation with the cam rollers 859 on the intermediate bodies ZK or 850. In this way can be dispensed with the attachment of spring elements.

FIG. 23 illustrates the use of a drive sprocket A according to the invention as an intermediate drive in a chain elevator elevator 1000. In the elevator at least one articulated chain G is provided with cups B for the vertical conveyance of goods. At its highest point, the link chain G is guided around a guide wheel KR1. At the lowest point, the link chain is deflected by a wheel KR2.

According to the invention, a drive sprocket A (for example according to the embodiments of FIGS. 7 to 10) is turned on in the upward-facing load strand of the articulated chain G in order to effect an additional drive at an intermediate level. As a result, the enormous tensile forces acting due to the weight of the chains, the cup, as well as the loading of the cup B in such elevators, evenly distributed and their tips are reduced. Furthermore, it is advantageous that in the upper sprocket KR1, where the chain links buckle, the tensile load between the chain links significantly reduced and the joint wear is thus reduced. Due to the intermediate drive A and the possible reduction of the (maximum) tensile forces, it is also possible to use a lighter articulated chain G and / or to realize larger delivery heights.

As can be seen from FIG. 23, a slight bending of the articulated chain G is provided at the point of engagement of the drive sprocket A in order to press the articulated chain G securely into the toothing with a (small) radial force component. Of course, it is also possible to provide two or more drive sprockets A as intermediate drives.

Figure 24 shows a modified embodiment of a Kettenbecherwerk- elevators 2000, in which, in contrast to Figure 1 1, the lower guide wheel KR2 is omitted.

Claims

claims

A drive sprocket (A, 100, 200, 300, 500, 600, 700, 800) for a link chain (G), comprising: a) a wheel body (R) rotatably mounted about an axis (X); b) at least one intermediate body (ZK, 150, 250, 350, 550, 650, 750, 850), which is displaceably mounted relative to the wheel body so that it comes to lie in the operating state in the power transmission path from the wheel body to the articulated chain.

Second drive sprocket (A, 100, 200, 300, 500, 600, 700, 800) according to claim 1, characterized in that the intermediate body (ZK, 150, 250, 350, 550, 650, 750, 850) on the wheel body (R) - preferably captive - is stored.

3. drive sprocket (A, 100, 200, 300, 500, 600, 700, 800) according to claim 2, characterized in that a plurality of intermediate bodies (ZK, 150, 250, 350, 550, 650, 750, 850) are present is uniformly distributed over the circumference of the wheel body (R) are arranged.

4. drive sprocket (A, 100, 200, 300, 500, 600, 700, 800) according to claim 2 or 3, characterized in that the intermediate body (ZK, 150, 250, 350, 550, 650, 750, 850) is biased by a spring element (157, 257, 557, 657a, 657b, 757) in a rest position.

5. drive sprocket (A, 300, 500, 600, 700, 800) according to at least one of the preceding claims, characterized in that the intermediate body (ZK, 350, 550, 650, 750, 850) a scanning element (359, 559, 659, 759, 859), which can cooperate in the operating state with a slotted guide (S1, S2).

6. drive sprocket (A, 100, 200, 300, 500, 600, 700, 800) according to at least one of the preceding claims, characterized in that the intermediate body (ZK, 150, 250, 350, 550, 650, 750, 850 ) a chain printing surface (151, 251, 351, 551, 651, 651 ', 751, 851), which can come into direct contact with the articulated chain (G) in the operating state.

7. drive sprocket (A, 100, 200) according to claim 6, characterized in that the intermediate body (ZK, 150, 250) additionally an auxiliary stop (154, 254), which in the operating state in direct contact with the articulated chain (G) can occur.

8. drive sprocket (A, 100, 200, 300, 500, 600, 700, 800) according to at least one of the preceding claims, characterized in that the wheel body (R) at least one tooth (Z, 110, 210, 310, 510, 610, 710, 810), via which in the operating state force can be transmitted from the wheel body (R) to the intermediate body (ZK, 150, 250, 350, 550, 650, 750, 850).

9. drive sprocket (A, 100, 200, 300, 500, 600, 700, 800) according to claim 8, characterized in that the intermediate body (ZK, 150, 250, 350, 550, 650, 750, 850) a tooth -Pressure surface (W2, W2 '), which can come into direct contact with the tooth (Z, 110, 210, 310, 510, 610, 710, 810) of the wheel body (R) in the operating state.

10. drive sprocket (A, 100, 200, 300, 500, 600, 700, 800) according to claim 6 and 9, characterized in that the tooth pressure surface (W2, W2 ') and the chain pressure surface (151, 251, 351, 551, 651, 651 ', 751, 851) are arranged so that in the operating state during the power transmission, a torque on the intermediate body (ZK, 150, 250, 350, 550, 650, 750, 850) is exerted.

Drive sprocket (A, 100, 200, 300, 500, 600, 700, 800) according to at least one of claims 8 to 10, characterized in that the tooth (Z, 110, 210, 310, 510, 610, 710, 810) and the intermediate body (ZK, 150, 250, 350, 550, 650, 750, 850) each Wälzflächen (W1, W1 ', W2, W2'), which in the operating state in Wälzkontakt can occur to transmit power from the wheel body (R) on the intermediate body (ZK, 150, 250, 350, 550, 650, 750, 850).

12 drive sprocket (A, 100, 200, 300, 500, 600, 700, 800) according to claim 11, characterized in that the rolling surfaces (W1, W1 ', W2, W2') are shaped so that a predetermined desired movement of the intermediate body (ZK, 150, 250, 350, 550, 650, 750, 850) in the operating state.

13. drive sprocket (A, 600) according to at least one of the preceding claims, characterized in that the intermediate body (ZK, 650) has two chains - pressure surfaces (651 a, 651 b), of which in the operating state depending on the direction of rotation of the wheel body (R ) can come into contact with the articulated chain (G).

14. drive sprocket (A, 600) according to at least one of the preceding claims, characterized in that the intermediate body (ZK, 650) has two tooth pressure surfaces (W2, W2 '), of which in the operating state depending on the direction of rotation of the wheel body (R ) can come into contact with the tooth (Z, 610) of the wheel body (R).

15. Drive sprocket (A, 100, 200, 300, 500, 600, 700, 800) according to at least one of the preceding claims, characterized in that the tooth (Z, 110, 210, 310, 510, 610, 710, 810) and / or the intermediate body (ZK, 150, 250, 350, 550, 650, 750, 850) interchangeable and / or positionally adjustable on the wheel body (R) are mounted.

16, drive sprocket (A, 300, 700, 800) according to at least one of the preceding claims, characterized in that the intermediate body (350, 750, 850) at least partially in the intermediate space (ZR) between two axially spaced side walls (RW1, RW2) of the wheel body (R) is arranged.

17, drive sprocket (A, 300, 700, 800) according to claim 16, characterized in that the intermediate body (350, 750, 850) has an eye opening (AO) through which a transverse pin (QB) engages with play, which with at least one side wall (RW1, RW2) of the wheel body (R) is connected.

18. drive sprocket (A, 300, 700, 800) according to at least one of claims 16 to 17, characterized in that the intermediate body (350, 750, 850) at least one thickening (352, 752, 852), which is not in the intermediate space (ZR) fits, wherein the thickening preferably gives the intermediate body a defined position when engaging in the articulated chain.

19, drive sprocket (A, 300, 700, 800) according to at least one of the preceding claims, characterized in that the wheel body (R) of two axially spaced plates (RW1, RW2) is constructed.

20, drive sprocket (A, 300) according to at least one of the preceding claims, characterized in that at least one support cam (330, SN1, SN2) on the wheel body (R) is arranged such that it contacts a running in the drive sprocket chain link (KG) before the next intermediate body (350) contacts the chain link.

21, drive sprocket (A, 300) according to claim 20, characterized in that the support cam (330, SN1, SN2) the chain link (KG) contacted at a point in which its associated pitch circle radius approximately perpendicular to the direction of the load strand of Joint chain (G) is.

22. A chain drive comprising a joint chain (G) and a drive sprocket (A, 100, 200, 300, 500, 600, 700, 800) cooperating therewith according to at least one of claims 1 to 21.

23. A chain drive according to claim 22, characterized in that the articulated chain (G) is looped around the drive sprocket (A, 100, 200, 300), or that the drive sprocket (A, 500, 600, 700, 800) engages as an intermediate drive in a substantially straight running piece of the link chain (G).

24. A chain drive according to at least one of claims 22 to 23, characterized in that the drive sprocket (A, 100, 200, 300, 500, 600, 700, 800) and the link chain (G) are dimensioned so that a power transmission from Drive sprocket on the link chain in the operating state only at a maximum of two chain links (KG).

25. A chain drive according to at least one of claims 22 to 24, characterized in that a stationary link (S1, S2) is present, which cooperates in the operating state with the intermediate body (ZK, 350, 550, 650, 750, 850).

26. Joint chain drive according to at least one of claims 22 to 25, characterized in that the articulated chain (G) is a bush conveyor chain.

27. Articulated chain drive according to claim 26, characterized in that the drive sprocket (A, 100, 200, 300, 500, 600, 700, 800) acts force-transmitting only on such sockets (BU), seen against the pulling direction of the chain at the beginning of the associated chain link (KG) lie.

28 joint chain drive according to at least one of claims 22 to 27, characterized in that the drive sprocket (A, 100, 200, 300, 500, 600, 700, 800) at least one tooth (Z, 110, 210, 310, 510, 610, 710, 810), which can engage in each case between two tabs (KL) of a chain link (KG).

29 supporting cam (SN1, SN2) for the drive sprocket (A, 300) of a link chain (G), in particular for a drive sprocket (A, 300) according to at least one of claims 1 to 21, characterized in that the support cam (SN1, SN2) has a metal body which is arranged on a about an axis (X) rotatably mounted wheel body (R) such that it resiliently contacts a running in the drive sprocket chain link (KG).

30. support cam (SN1, SN2) according to claim 29, characterized in that the metal body consists of a C-shaped or L-shaped bent sheet metal.

31. Kettenbecherwerk elevator (1000, 2000), comprising a) a cup (B) equipped with articulated chain (G); b) a deflection (KR1) about which the articulated chain (G) is guided so that the free chain portions are substantially perpendicular; c) at least one drive sprocket (A) according to at least one of claims 1 to 21, which engages in a free chain portion.

32. A method for driving a joint chain (G) with a rotating wheel body (R), characterized in that in Kraftübertragu ngsweg between the wheel body (R) and the joint chain (G) an intermediate body (ZK, 150, 250, 350, 550 , 650, 750, 850), which shifts relative to the wheel body (R) during power transmission.

33. The method according to claim 32, characterized in that the intermediate body (ZK, 150, 250, 350, 550, 650, 750, 850) during the power transmission in contact with a chain link (KG) of the joint chain (G) is and moves so that the chain link moves in a substantially straight line.