WO2015117632A1

WO2015117632A1 - Conveying device

Info

Publication number: WO2015117632A1
Application number: PCT/EP2014/003301
Authority: WO
Inventors: Michael Freund
Original assignee: Festo Ag & Co. Kg
Priority date: 2014-02-04
Filing date: 2014-12-10
Publication date: 2015-08-13
Also published as: DE102014001406A1

Abstract

Proposed is a conveying device (1) having a conveying carriage (4) which can be driven relative to a base (3) such that it carries out a conveying movement (5) and on which a product support (13) is provided. The product support (13) can be rotated, said product support being in driving connection with the star wheel (25) of a Maltese cross gear mechanism (18), and said star wheel cooperating with a drive wheel (34). During the conveying movement (5) of the conveying carriage (4), the drive wheel (34) can roll over a drive surface (46), which is stationary relative to the base (3), and is thereby actuated to carry out a rotational drive movement (36) which causes the star wheel (25) and the product support (13) to rotate about a rotational angle step.

Description

transport device

The invention relates to a transport device, with a transport carriage, relative to a base to a

Transport movement along a transport path is driven and to which a suitable for carrying and / or holding at least one product to be transported, the transport movement mitmachender product carrier is arranged.

A transport device known from DE 10 2010 022 625 A1 is part of a handling system for handling any products, wherein the products can be repositioned between different locations by means of a transport carriage of the transport device. In the known case, the transport carriage is formed by a telescopic arm of a telescopic arm unit having a plurality of telescopic arms and has article holding means which act as a product carrier and which serve to carry and / or hold one or more products to be transported at least during transport. The product carrier can be, for example, a simple carrier plate or else a gripping device which operates mechanically or on a vacuum base.

As has been shown, the requirement may arise

to provide relocating products at the target location in a different angular orientation than at the point of origin of transport. In this context, the applicant has already internally already considered the idea to mount a product carrier rotatably on the transport carriage and angularly to position as required by means of an electrically or pneumatically activated rotary drive device mitmach the movement of the transport carriage. However, the associated constructive and financial expense is not inconsiderable.

From DE 671462 B, a device for feeding sheets is known in which grippers are used, which are driven by the slotted star wheel of a Maltese cross gear, wherein the star wheel is driven intermittently rotating by a designated as a ratchet drive wheel. A Maltese cross transmission is characterized overall by the fact that it can implement a continuous rotary drive movement in an intermittent output rotary motion.

The invention has for its object to provide a transport device of the type mentioned, which provides a cost-effective, yet simple and precise way to vary the angular orientation of products to be transported.

To solve this problem is provided in conjunction with the features mentioned,

- That the product carrier is rotatable relative to the transport carriage about a transverse to the direction of movement of the transport movement oriented product carrier rotation axis,

- That the transport carriage mitmachende a transmission device is arranged, which has a Maltese cross gear with a driven to an intermittent output rotational movement slotted star wheel and one coupled with the star wheel and its

Output driving motion causing drive wheel has, wherein the product carrier with the star wheel is in Drehantriebsverbin manure,

and in that at least one drive surface fixed relative to the base is arranged next to the transport path of the transport carriage such that the drive wheel is directly or indirectly in drive contact with the drive surface during at least one movement section of the transport movement and rolls on it so that it rotates Drive movement is driven, which causes at least one output rotation step of the star wheel and the motion-coupled product carrier, whereby the rotational position of the product carrier is changed by at least one predetermined angle of rotation step.

In this way, there is an easy way to change the angular orientation of a product during its transport. The rotatably mounted on the transport carriage product carrier allows rotation of the Produktträ gers relative to the transport carriage, so that the Drehwin kellage of the product carrier and thus also that of one or more products arranged on the product carrier can be varied. In this case, the corresponding rotational movement of the product carrier is generated from the relative movement between the transport carriage and a base carrying the transport carriage, so that it is possible to dispense with a separate, separately supplied external energy to be operated rotary drive device. This reduces the energy requirement and also leads to a reduction in the masses to be moved. Significantly responsible for the generation of the rotational movement of the product carrier is located on board the Transportschiit least gear device, which has a known as such Maltese cross gear, the pro- the drive carrier is in drive connection with the multi-slotted star wheel of the Malte- serskreuzgetriebes. The product carrier may in particular be connected in a rotationally fixed manner to an output shaft coaxial with the axis of rotation of the star wheel. The drive torque is thereby generated from the relative movement between the transport carriage and the base that rolls off the drive wheel of the Malte- serskreuzgetriebes also known as ratchet wheel during the transport movement at a base fixed to the drive surface, which is for example a frictional or a can act positive drive contact. It is advantageous that the precision of the interaction between the drive wheel and the drive surface no particularly high demands are made because the output side, an intermittent output rotary motion is generated and an exactly predeterminable angle of rotation step in the rotation of the product carrier is also achieved when repeating transport movements no exactly reproducible driving interaction between the drive surface and the drive wheel can be ensured. A peculiarity of the Maltese cross transmission is that the star wheel maintains a clearly defined rotational position not only at a very specific angular position of the drive wheel, but in a relatively wide Drehwinkelbe ^¬ rich the drive wheel.

Depending on the length of the drive surface and the number of existing drive surfaces, the rotational positioning of the product carrier can be influenced individually. If the drive wheel remains in drive contact with a drive surface during a relatively long travel path of the transport path, it can be achieved that the product carrier is rotated by a plurality of rotational angle steps. It can also be several individual, in the transport direction by far mutually arranged drive surfaces may be provided, with which the drive wheel of the Maltese cross gear in the transport movement one after the other comes into drive contact in order to realize a path-dependent spreading of several rotational angle steps. It is also possible to provide only a single drive surface which cooperates with the drive wheel and which can be embodied such that the drive wheel is in driving contact with the drive surface during the entire or only during part of the transport movement.

The drive contact between the drive wheel and the base of the associated drive surface is preferably a direct contact, wherein the drive wheel interacts directly with the drive surface. However, it is also possible to have an embodiment for an indirect drive contact, in which case, for example, a further wheel which is in rotary drive connection with the drive wheel produces the direct drive contact with respect to the base of the stationary drive surface.

Advantageous developments of the invention will become apparent from the dependent claims.

As already indicated, the base is equipped in an advantageous embodiment of the transport device with only a single drive surface cooperating with the drive wheel.

As also already mentioned, a particularly expedient refinement provides that at least one drive surface is designed and arranged such that the drive wheel abuts against the drive surface only during a movement section of the transport movement, which is shorter than the entire transport movement of the transport carriage. rolls and during the remaining sections of the transport movement is out of driving contact with the drive surface. In this case, the drive surface in the direction of movement of the transport movement expediently has a smaller longitudinal extent than the entire transport path.

In particular, when the drive wheel temporarily has no drive contact with a drive surface, it is advantageous if the transmission device in addition to the Maltese cross gear has return means which force the drive wheel in a blocking engagement with the star wheel having basic position when the drive outside drive contact with the at least a drive surface is. A Maltese cross gear is characterized in that the drive wheel in its rotary drive movement alternately in a rotational drive engagement and in a

Blocking engagement with the star wheel is. During a Drehitnahmeeingriff having rotational drive phase, the star wheel is driven by the rotating drive wheel rotationally. While a locking phase having blocking phase still takes place as a rotary drive movement of the drive wheel, but it is in a blocking engagement with the star wheel, so that it is prevented from rotating and is held non-rotatably in the current rotational position. With the help of the return means can now be guaranteed ge that the drive wheel whenever it is not exposed to driving forces, is forced into acting as a basic position blocking engagement, which also has the advantage in addition to a safe non-rotatable fixation of the star wheel and the coupled product carrier, It is ensured that the drive wheel, when it is out of driving contact with the drive surface, is reproducibly turned to a home position, which is the starting point represents for the next upcoming rotary actuation of the product carrier. In this way, tolerance-related deviations in the rotation angle that the drive wheel experiences during its drive contact can be tolerated and compensated. The starting point for the next turning step of the star wheel is always the same basic position of the drive wheel.

A peculiarity of the Maltese cross transmission is that the drive wheel blocks the star wheel not only at a certain rotational position, but constantly during a rotational movement passing through a certain angle of rotation, said rotation angle is referred to as a blocking rotation angle. It is advantageous if the drive wheel by the return means imposed basic position of a middle position of

Blocking angle corresponds. The basic position is thus equidistant from the beginning of the blocking intervention until the end of the blocking intervention.

Preferably, the operating principle of the return means based on a resilient resilient application of the drive wheel, by which the drive wheel is acted upon by a torque in the direction of the basic position, preferably at least approximately constantly in each rotational position of the drive wheel. The restoring torque-inducing actuating force is thus a spring force which, depending on the design of the transmission device, is introduced directly or indirectly into the drive wheel. To realize this, the return means are equipped with suitable spring means.

Preferably, the return means are designed so that they exert the restoring torque on the drive wheel even when the same is in drive contact with a drive surface. Here, however, the restoring torque is effective because it can not develop a return effect on the drive wheel due to the drive contact.

The spring means preferably include a fixed relative to the transport carriage supported and in particular supported on a transmission housing of the transmission device return spring. This return spring is preferably formed by a leg spring, but may also be of a different spring type.

Conveniently, the return means comprise a rotatably mounted return pinion, which is in meshing engagement with the drive wheel and in turn is set in rotation during the rotation of the drive wheel. In this case, the spring means of the return means work expediently indirectly together with the drive wheel by cooperating with the return pinion. The reset pinion expediently has a preferably pin-shaped actuating projection, which is arranged at a distance from the axis of rotation on the return pinion and, during the rotation of the return pinion, orbits on a circular path about the axis of rotation of the return pinion. The spring means are formed so that they constantly act on the actuating projection, wherein they are deflected in the driven rotational movement of the return pinion of the actuating projection, overcoming the spring force. Only when the drive wheel is out of driving contact with the drive surface and thus the reset pinion on the part of the drive wheel torque-free, the effect of the spring means occurs and leads to the provision of the return pinion in a basic position in which the

Basic position of the drive wheel is present.

It is expediently also located between the return pinion and the toothed pinion for engagement with the return pinion. ten drive wheel before a reduction of 2: 1 ago. In this way, the return pinion makes a complete revolution within a 180 ° rotation sequence of the drive wheel. Due to the meshing engagement, the same relative positions between the two toothed wheels are always encountered.

In order to cause the transport movement, is the

Transporter expediently equipped with suitable drive means, which are for example of electrically operated type or by fluid-operated type or combined electro-fluidically actuated type.

The transport device is in particular designed so that the transport carriage can be driven by corresponding drive means to a reciprocating linear transport movement. In this case, a configuration is possible, which enables the drive wheel, in both directions of movement of the transport carriage with the at least one drive surface to get into driving contact. In this way, it can be realized, for example, that the product carrier is rotated in the one direction in the one direction of movement of the transport carriage and in the opposite direction in the opposite direction of movement of the transport carriage.

In particular, if a change in the rotational position of the product carrier is desired only in one direction of movement of the transport movement, a removal device is expediently associated with the transport carriage, which permits a controlled displacement of the transmission device transversely to the direction of movement of the transport movement in order to selectively position the drive wheel in an operating position or in an inoperative position. In the operating position, the drive wheel is positioned in such a way that it is movement into drive contact with the at least one drive surface. In the inoperative position, the drive wheel is positioned so that it passes by the drive surface at a distance during the transport movement and experiences no drive contact in this respect. The Abrückeinrichtung is preferably a lifting device, which makes it possible to shift the transmission device, in particular including the product carrier for switching between the operating position and the inoperative position in terms of height.

The invention will be explained in more detail with reference to the accompanying drawings. In this show:

Figure 1 is a schematic side view of a preferred

Embodiment of the transport device according to the invention in an initial position of the transport carriage,

Figure 2 shows the transport device of Figure 1 during the

Transport movement of the transport carriage and a drive contact between the drive wheel and with respect to a base fixed drive surface,

3 shows the transport device in an end position of

Transport carriage after completion of the transport movement,

Figure 4 shows the apparent from Figure 1 operating phase in a

Top view ,

Figure 5 shows the apparent from Figure 2 operating phase in a

Top view , FIG. 6 shows the operating phase shown in FIG. 3 in a top view,

Figure 7 is a side view of the transport device in the

Starting position of the transport carriage in the same position of the transmission device positioned in an inoperative position,

FIG. 8 shows the transport device from FIG. 7 during the

Transport movement and while passing the drive wheel on the drive surface without a drive contact,

FIG. 9 shows the end position of the transport carriage with the transmission device still positioned in the inoperative position,

FIG. 10 shows an isometric individual representation of the transmission device,

Figure 11 is a plan view of the transport device in the

Starting position of the transport carriage, wherein for the sake of clarity, only the transmission device and the stationary relative to the base stationary drive surface defining component illustrates and also dash-dotted lines a product carrier and a product arranged thereon are indicated, and

12 shows various further operating phases of the transport device in a representation corresponding to FIG. 11, wherein FIG. 12 shows a transition from a blocking phase into a rotational drive phase, FIG. 13 shows a state during the rotational drive phase, FIG. 14 shows the transition FIG. 15 shows a state in which the drive contact between the drive wheel and the drive surface has been canceled and the product carrier has been rotated by one rotation angle step compared to the initial position of FIG.

The transportation device, designated in its entirety by reference numeral 1, can be used to transport any products, one of which is schematically illustrated at reference numeral 2, between different locations and also to change the spatial orientation during transport. The product or products 2 to be transported are, for example, microtiter plates used in medical technology, which have a plurality of cavities which can be filled or filled with samples to be chemically and / or biologically examined. The range of applications of the transport device 1 is not limited thereto.

In the following, transporting and / or holding a product 2 refers to the simultaneous transporting and / or holding of several products.

The transport device 1 contains a base 3, which may be any base body, for example a frame or a foundation of a machine. At this base 3, a transport carriage 4 is mounted linearly movable, so that it can perform a direction indicated by a double arrow transport movement 5 relative to the base 3. The base 3 expediently contains suitable linear guide means in this context, for example one or more guide rails. NEN, with which the transport carriage 4 is linearly movable in guiding contact.

As part of the transport movement 5 is the transport carriage

4 along a dash-dotted lines indicated transport path 6 movable. By way of example, the transport carriage 4 can be moved between an initial position, which is illustrated in FIGS. 1, 4 and 7, and an end position illustrated in FIGS. 3, 6 and 9. For better distinction, the movement from the initial position to the end position is referred to as the forward movement and the opposite movement is referred to as the rearward movement, without this being intended to be a restriction.

The transport device 1 is equipped with only indicated in Figure 1 drive means 10 to the transport movement

5 cause. The drive means 10 are, in particular, linear drive means. Illustrated is a structure in the manner of a spindle drive with a rotatably mounted on the base 3 and in the axial direction of the transport movement 5 extending drive spindle 7, with a spindle nut 8 is in threaded engagement, which is secured to the transport carriage 4. The drive means 10 also include an electric drive motor 12, which can set the drive spindle 7 in rotation, so that the spindle nut 8 moves along the drive spindle 7 and the transport carriage 4 entrains carrying out the transport movement 5.

The drive means 10 may optionally be, for example, of the electrically actuatable type or by fluid power

be actuated type. However, ischformen or hybrid forms of the drive means 10 are also used. On the transport carriage 4 is a principle arbitrarily designed, in the embodiment plate-like structuring ter product carrier 13 is arranged, which participates in the transport movement 5. By way of example, the product carrier 13 includes an in the use position of the transport device 1 upwardly facing support surface 13a, on which the transportable product Pro 2 is placeable. Without further ado, the product carrier 13 may alternatively or additionally also comprise suitable retaining means, for example one or more clamping or gripping devices.

The product carrier 13 is rotatable relative to the transport carriage 4 about a product carrier rotation axis 14. The product carrier rotation axis 14 extends transversely and in particular rechtwinkeli to the direction of movement of the transport movement 5 and is aligned vertically in the embodiment in the position of use of the transport device 1.

The transport device 1 is permitted with actuating means 15 which are capable of intermittently rotating the product carrier 13 about the product carrier rotation axis 14. These actuating means 15 are designed so that the intermittent rotational movement of the product carrier 13 is derived from the translational relative movement between the transport carriage 4 and the base 3. This eliminates the need for separate, used only for the rotary drive of the product carrier 13 drive measures.

The product carrier rotation axis 14 is defined by a rotatable about its longitudinal axis output shaft 16 of the actuating means 15. This output shaft 16 is preferably formed by the output shaft 17 of a Maltese cross gear 18, with which the transport carriage is equipped. The Maltese cross gear 18 is part of a transport Schiit 4 arranged transmission device 22, which preferably also has special return means 23, whose structure and purpose will be discussed.

The transmission device 22 is arranged on the transport carriage 4 in any desired manner. It can be readily integrated in the transport spouts 4. Appropriately, it has a the movable components at least partially receiving gear housing 24, on which the movable components of the transmission device 22 are mounted. The output shaft 16 projects in particular on an upper side out of the transmission housing 24 and is provided there with the product carrier 13.

Characterized in that the transmission device 22 is arranged on the transport carriage 4, it makes its transport movement 5 with.

The Maltese cross gear 18 contains in a conventional manner a so-called star wheel 25, which is about a coincident with the longitudinal axis of the star wheel 25 axis of rotation 26th

is rotatable. In the preferred position of use of the transport device 1, the axis of rotation 26 of the star wheel 25 is vertically aligned.

Preferably, the aforementioned output shaft 17 is a part of the star wheel 25 or at least rotationally fixed to the

Star wheel 25 attached. In this way, a structure is possible in which the product carrier rotation axis 14 is coaxial with the axis of rotation 26 of the star wheel 25, that is, virtually coincident with this axis of rotation 26.

The star wheel 25 has a plurality of cam slots 27, each radially with respect to the axis of rotation 26th are aligned and which are arranged in a preferably uniform distribution around the axis of rotation 26 around. Each driver slot 27 has an open slot end 28 on the outer end side pointing away from the axis of rotation 26.

The star wheel 25 of the embodiment has four Mitnehmer- slots 27 arranged at angular intervals of 90 ° to each other. Deviating from this, the star wheel 25 but also have a different number of slots.

The star wheel 25 has in the areas which are arranged between in the circumferential direction of the star wheel 25 immediately adjacent cam slots 27, one each

Blocking section 32 on. Each blocking section 32 has a concave locking recess 33 pointing away from the axis of rotation 26. Above and below, the circumferential direction of the starwheel 25 refers to the direction around the axis of rotation 26 of the starwheel 25.

In a direction perpendicular to the axis of rotation 26 next to the star wheel 25 is a drive wheel 34 of the Maltese cross gear 18. The drive wheel 34 is rotatably mounted on the transport carriage 4 or on the gear housing 24 such that it is rotatable about a coincident with its longitudinal axis of rotation 35 that runs parallel to the axis of rotation 26 of the star wheel 25.

The drive wheel 34 is, preferably in both directions, drivable about the axis of rotation 35 to a rotary drive movement 36 indicated by a double arrow. The generation of the drive movement 36 will be explained below. The drive wheel 34 is operatively coupled to the starwheel 25 such that when the rotary drive motion 36 is performed, the starwheel 25 becomes intermittent

Output rotary motion 37 can drive about its axis of rotation 35. In other words, the Maltese cross gear 18, a continuous drive movement 36 of the drive wheel 34 in a stepwise output rotary motion 37 of the star wheel

25 convert.

Responsible for this motion conversion is the type of coupling between the drive wheel 34 and the star wheel 25. Thus, the drive wheel 34 is provided with at least one radially spaced from the axis of rotation 35 arranged driver projection 38 which is concentric with the drive movement 36 on one of the axis of rotation 26th Mitnehmerkreisbahn 42 moves. This is arranged so that each driving lug

38 is able, when passing through the star wheel 25 through the associated open slot end 28 to first retract into one of the drive slots 27 and then extend again. Between the phase of retraction into the driver slot 27 and the phase of extension from the driver slot 27, the slot flank of the driver ^¬ slot 27 is acted upon by the driver projection 38, whereby a torque is introduced into the star wheel 25, which causes a rotation step of the star wheel 25. The operating phase during which a driver projection 38 is located in a driver slot 27 is referred to below as a rotary drive phase. The engagement of the driver projection 38 in a driver slot 27 is a rotational drive engagement, because ultimately the drive wheel 34, the star wheel 25 rotationally takes a piece.

In the embodiment, the drive wheel 34 with two with respect to the rotation axis 35 diametrically opposite Mitnehmervorsprüngen 38 equipped alternately to each other a rotational engagement with each one of

Mitnehmerschlitze 27 can go.

So that the starwheel 25 outside the rotational drive phases maintains a defined rotational position with respect to the transport carriage 4, the drive wheel 34 is also equipped with two arranged at a radial distance from the axis of rotation 35 blocking cam 43, in the circumferential direction of the drive wheel 34, ie in the direction around the rotation axis 35, are arranged at a distance from the driver projections 38. Preferably, the drive wheel 34 has two on opposite sides of the rotation axis 35 placed and in this respect diametrically opposite blocking cam 43, which have radially outwardly a convex blocking surface 44. The blocking surfaces 44 have the same curvature as the concave blocking recesses 33, wherein the blocking recesses 33 and the blocking cams 43 are arranged such that whenever none of the driver projections 38 engages in a driver slot 27, one of the blocking recesses 33 of the axis of rotation 35 of the drive wheel 34 faces and a blocking cam 43 dips positively in this blocking recess 33. This constellation causes a locking engagement between the drive wheel 34 and the star wheel 25 and prevents rotation of the star wheel 25 about its axis of rotation 26. Due to the fact that the

Blocking cam 43 at its blocking surface 44 have the same curvature as the blocking recesses 33, the drive wheel 34 is able to run through the execution of the drive movement 36 individual blocking phases, in each of which one of the blocking cam 43 passes while maintaining the blocking engagement on the facing blocking recess 33 , In this case, the blocking cam 43 first emerges at one end in the blocking axis facing the axis of rotation 35. Recess 33, to selbige then after returning a certain angle of rotation, which is referred to as blocking rotation angle, extend again from said blocking recess 33. At any time, as long as a blocking cam 43 is only partially immersed in the associated blocking recess 33, the star wheel 25 is prevented from further rotation or blocked. Thus, the drive movement 36 contains not only the already mentioned rotational drive phases but also two blocking phases, which are characterized by a blocking engagement with the

Mark the star wheel 25. The blocking phase extends over the mentioned blocking rotation angle.

When the drive wheel 34 performs the rotary continuous drive motion 36, enter alternately

Mitnehmervorsprung 38 with a cam slot 27 in the rotary driving engagement and a blocking cam 43 with a

Blocking recess 33 in a blocking engagement. This results in that the rotary drive movement 36 of the drive wheel 34 is converted into the intermittent output rotary motion 37 of the star wheel 25, the peculiarity is that the star wheel 25 is blocked during its downtime by the drive wheel 34 non-rotatably.

By the product carrier 13 is coupled to the star wheel 25, preferably in that the product carrier 13 is rotatably connected to the output shaft 16 of the star wheel 25, the product carrier 13 performs the same intermittent rotational movement as the star wheel 25. This causes the Rotary position of the product carrier 13 at each rotational drive phase changed by a predetermined angle of rotation step. The rotation carried out by the product carrier 13 during a rotational drive phase, which is limited to a rotational angle step, is indicated by an arrow in the drawing at 45. A special feature of the transport device 1 is the way in which the drive movement 36 of the drive wheel 34 is generated. As can also be seen in particular from FIGS. 4 to 6, at least one drive surface 46 arranged stationary with respect to the base 3 is located alongside the transport path 6 of the transport carriage 4 This drive surface 46 is placed so that the drive wheel 34 of the Maltese cross gear 18 comes to rest against it and rolls off when the transport carriage 4 executes the transporting movement 5. The rolling of the drive wheel 34 on the drive surface 46 causes the drive movement 36, which is thus produced without a separate drive means. The responsible for the generation of the transport movement 5 drive means 10 indirectly also call the drive movement 36 of the drive wheel 34.

The rolling contact between the drive wheel 34 and the drive surface 46 fixed relative to the base 3, which causes the rotary drive of the drive wheel 34, will also be referred to below as the drive contact.

In a non-illustrated embodiment of the transport device 1, the drive contact is present during the entire transport movement 5. This has the consequence that the drive wheel 34 continuously rotates during the entire transport movement 5 and causes a gradual rotation of the star wheel 25 and the product carrier 13.

In many applications, however, it will be required that the product carrier 13 is rotated at the transition between the starting position and the end position of the transport carriage 4 only by a predetermined angle of rotation step. For such an application, the transport device of the embodiment is designed, in which the drive wheel 34 only during a limited movement section of the transport movement 5, which is shorter than the entire

Transport movement 5 between the initial position and the end position of the TransportSchlittens 4, with the drive surface 46 is in drive contact and rolls on it. Apart from this limited movement portion of the transport movement, the drive wheel 34 is disengaged from the drive surface 46 and experiences so far from the outside no drive torque.

It is quite possible to cause in the transport movement 5 in at least one direction of transport a plurality of rotational angle steps of the product carrier 13, which are spread further in time than would be the case with an uninterrupted rotation of the drive wheel 34. For this purpose, it is sufficient to arrange a plurality of drive surfaces 46 at a distance from each other along the transport path 6, so that the drive wheel 34 with these multiple drive surfaces 46 in the transport movement 5 laterally engages in succession and is not driven in the intervening times.

The embodiment shows an advantageous embodiment of the drive surface 46 as a linear toothing 46a with a plurality of in the direction of the transport movement 5 consecutive teeth. The toothed drive surface 46 is in particular part of a stationary relative to the base 3 arranged rack 47th

The drive wheel 34 in turn has a counter drive surface 48 rolling on the drive surface 46 during the drive contact, which is formed by a radially outwardly oriented peripheral surface of the drive wheel 34 and which in the exemplary embodiment is realized in the form of a drive toothing 48a. In this way, the drive contact manifests itself between the drive wheel 34 and the drive surface 46 in a meshing engagement of the drive toothing 48a and the linear toothing 46a. The result is a slip-free introduction of a drive movement 36 causing driving force into the drive wheel 34 during the transport movement 5.

In one embodiment, not shown, the drive contact is a purely frictional contact. Here, both the drive surface 46 and the mating drive surface 48 are preferably formed as untoothed friction surfaces.

In order to keep the design effort as low as possible, it is expedient if the drive wheel 34 is in direct drive contact with the drive surface 46 in order to receive its drive torque. It is, however, quite possible, particularly when a displacement and / or force transmission ^¬ reduction is desired to provide at least one standing in rotary drive connection with the drive wheel 34 further wheel, then the driving wheel reaches only an indirect contact with the drive surface 46, meanwhile, switching 34 ,

Preferably, the transport carriage 4 by means of the drive means 10 to a reciprocating linear transport movement 5 can be driven. In this case, the drive wheel 34 can come into driving contact with the at least one drive surface 46 during the forward movement as well as during the opposite rearward movement, in order to rotate the product carrier 13. For example, the product carrier 13 in the forward movement in the clockwise direction and in the reverse movement can be rotated counterclockwise, so that when the transport carriage 4 returns to the starting position, it has a already occupied before execution of the transport movement 5 basic position. The drive wheel 34 is therefore in a preferred embodiment of the transport device 1 able to come in both directions of movement of the transport carriage 4 with the at least one drive surface 46 in drive contact to cause a rotational movement of the product carrier 13 in opposite directions of rotation.

It is particularly advantageous if the transport device 1, which emerges in particular from FIGS. 7 to 9, has an equipment which makes it possible to select, if at all and, if so, in which direction of movement of the transport carriage 4 the drive wheel 34 has a drive contact at least one drive surface 46 is received.

This Abrückeinrichtung 52 allows a demand-based displacement of the transmission device 22 transversely to the direction of movement of the transport movement 5 to position the drive wheel 34 either in an operative operating position or in an inoperative inoperative position. In the effective operating position shown in FIGS. 1 to 3, the drive wheel 34 can, as described above, come into drive contact with the at least one drive surface 46 during the transport movement 5. In the non-operating position shown in FIGS. 7 to 9, the drive wheel 34 assumes such a position that it can not come into driving contact with this drive surface 46 when passing by the drive surface 46 and consequently also experiences no drive torque. As a result, the current rotational position of the product carrier 13 remains unchanged.

It is thus possible to provide, for example, an operation of the transport device, in which the product carrier 13 only in the forward movement is rotated by at least one rotation step, while he remains in the backward movement in this rotational position. Ultimately, this results in a function similar to a rotary indexing table, which is further indexed in the same direction in each forward transport movement 5.

An embodiment of the take-off device 52 has proved to be particularly advantageous as a lifting device 52a. The indicated in Figure 7 by a double arrow Abrückbewegung 53 is in this case a lifting movement, which is oriented in particular in the preferred position of use of the transport device 1 vertically.

The Abirückbewegung 53 may alternatively but for example also be a sideways movement in the plane of the transport movement 5 and / or a pivoting movement.

If the drive wheel 34 has no drive contact with a drive surface 46, vibrations of the transport device 1 may possibly cause the rotational position of the drive wheel 34 to change unintentionally. Even if this is due to the fact that the blocking engagement with the star wheel 25 is ensured during a not insignificant blocking ^¬ rotation angle, the rotational locking of the star wheel 25 and consequently of the product carrier 13 is not canceled, but in the course of time such a changed rotational position of the Drive wheel 34 sum up that the desired accuracy of the clocked output rotary motion 37 can not be guaranteed. This problem can also be due to the fact that due to manufacturing tolerances, the effective length of the drive surface 46 is not accurate enough to cause a Drehwinkel- Step of the star wheel 25 required rotation angle of the drive wheel 34 is tuned.

In order to prevent such impairments, the transmission device 22 is equipped with the reset center 23 already mentioned above. These return means 23 are characterized by the fact that they always force the drive wheel 34 into a rotationally angular basic position which has a blocking engagement with the starwheel 25 when the drive wheel 34 is out of drive contact with the at least one drive surface 46. Such a basic position of the drive wheel 34 is apparent from the figure 11.

The desired and by the return means 23 also guaranteed basic position of the drive wheel 34 is preferably characterized by the fact that it is a middle position of the above-described blocking rotation angle. The angle of rotation by which the drive wheel 34, starting from the basic position in the clockwise or counterclockwise direction must be rotated to cancel the blocking engagement is at least substantially equal.

In principle, the return means 23 can cooperate directly with the drive wheel 34. Also, the drive wheel 34 may be directly equipped with corresponding return means 23 itself. However, a design is considered more advantageous in which the return means 23 are separate components with respect to the drive wheel 34. This applies to the embodiment. All embodiments of the return means 23 are expediently equipped with spring means 54 which provide the restoring force required for the restoring operation to be explained. In the exemplary embodiment, the return means 23 comprise a return pinion 55 which is rotatable about a rotational axis 56 which coincides with its longitudinal axis relative to the transport carriage 4 or to the gearbox housing 24. The axis of rotation 56 extends parallel to the axes of rotation 26, 35 of the star wheel 25 and the drive wheel 34th

The reset pinion 55 has a circumferential outer toothing 57, which is constantly engaged with a concentrically around the rotation axis 35 extending around the coupling teeth 58 of the drive wheel 34. The coupling toothing 58 is preferably an external toothing. If the mating drive surface 48 of the drive wheel 34 is formed as a drive toothing 48a, the coupling toothing 58 is expediently formed directly by this drive toothing 48a, so that a single toothing of the drive wheel 34 is sufficient to co-operate with the drive surface 46 and with the reset pinion 55.

A rotation of the drive wheel 34 always has a direct rotation of the return pinion 55 about its axis of rotation 56 result.

The reset pinion 55 is expediently provided with an actuating projection 62 projecting in the axial direction of the axis of rotation 56. During the rotation of the return pinion 55, the actuating projection 62 passes through a circular path 63 indicated by dash-dotted lines about the axis of rotation 56 as the center.

The already mentioned spring means 54 are based on the one hand stationary with respect to the transport carriage 4 and on the other hand on the actuating projection 62 from. The spring means 54 act on the actuating projection 62 constantly in a direction perpendicular to the axis of rotation 56 in the direction of a plane 11 apparent rest position. In the rest position, the spring means 54 engage the actuating projection 62 such that no torque is exerted on the reset pinion 55. A deflection of the return pinion 55 from the rest position in one or the other direction of rotation immediately causes a tensioning of the spring means 54 with the effect that a restoring torque builds up, which has a tendency to turn the return pinion 55 back to the rest position.

The return means 23 are designed so that the rest position of the return pinion 55 coincides with the above-mentioned basic position of the drive wheel 34. Thus, if the drive wheel 34 is angularly deflected from the basic position, there is also a corresponding angular displacement of the return pinion 55, so that the return means 23 constantly strive to turn the drive wheel 34 into the basic position by means of the return pinion 55 and to hold it there.

To be particularly advantageous, it has proven to design the spring means 54 in the form of a leg spring 64, which is the case in the embodiment. The leg spring 64 has a fastening end 64a fixed to the transmission housing 24 or otherwise stationary with respect to the transport carriage 4 and a spring-elastically pivotable and free-ending leg section 64b projecting from the attachment end 64a. The pivoting plane, in which the leg section 64b is pivotable during resilient deformation, extends at right angles to the axis of rotation 56 of the return pinion 55.

With one of its two leg surfaces of the elastically pivotable leg portion 64b is constantly on the actuating projection 62 at. When the operating projection 62 along due to the drive movement 36 of the drive wheel 34 along travels around the circular path 63, the leg portion 64b is deflected according to arrow 65, wherein an increasing resilient spring force F builds up, which generates by the interaction with the operating projection 62 a torque which tends to turn the return pinion 55 back to the rest position.

The flexibility of the spring means 54, however, is sufficient to allow the actuating projection 62 a complete circulation of the circular path 63. Consequently, the drive means 36 of the drive wheel 34 is not obstructed by the return means 23.

The spring means 54 can only cause a return operation when the drive wheel 34 is not in driving contact with the drive surface 46. In the moment in which the drive contact is released, eliminating the drive wheel 34 acting on external driving force, so that the return means 23 are able to rotate the drive wheel 34 to the normal position. Which sense of direction the rotational movement occurring has depends on which rotational position the drive wheel 34 or the reset pinion 55 is currently located. The rotating return movement can therefore take place both clockwise and counterclockwise.

Conveniently, between the outer teeth 57 of the return pinion 55 and the coupling teeth 58 of the drive wheel 34 before a reduction of 2: 1, which has the consequence that the return pinion performs a full rotation within a 180 ° rotational sequence of the drive wheel 34.

FIGS. 11 to 15 show various successive operating phases of the transport device 1. In the figure 11, the transport carriage 4 is in the starting position, at the same time the drive wheel 34 assumes the basic position in which it is held resiliently resilient by the return means 23. The reset pinion 55 is in the rest position.

Starting from the initial position of the transport spouts 4 is linearly displaced by the drive means 10, so that the drive wheel 34 according to FIG 12 after returning a certain distance with the drive surface 46 engages or in drive contact. As a result, the drive wheel 34 is rotated in accordance with arrow 66, which rotational movement is also transmitted to the reset pinion 55 by the meshing engagement, which consequently in turn rotates according to arrow 67. In this case, the actuating projection 62 traverses the circular path 63 and deflects the leg portion 64b of the leg spring 64 as indicated by arrow 65.

In the operating phase of FIG. 12, one of the driver projections 38 is just about to engage in one of the driver slots 27. Since one of the blocking cam 43 is still in blocking engagement with one of the blocking recesses 33, the rotational position of the star wheel 25 and the product carrier 13 has not changed at this time.

In the operating phase shown in FIG. 13, the drive wheel 34 continues to run on the drive surface 46, wherein it has rotated by 90 ° in comparison to the basic position. The starwheel 25 has gone through until then relative to the starting position a rotation angle of 45 °. The same applies to the product carrier 13.

In the operating phase of FIG. 14, the drive wheel has reached almost the end of the drive surface and the towards engaging in a driver slot 27 driver projection 38 is just about to emerge from the respective driver slot 27. In this case, the other of the two blocking cam 43 is already in blocking engagement with a further blocking recess 33, so that the rotational position of the star wheel 25, which was previously rotated by 90 °, is blocked again.

The leg section 64b, which has experienced its maximum deflection in the operating phase of FIG. 13, follows the actuating projection 62 of the return pinion 55 rotating in the direction of the rest position according to arrow 68.

A rotation cycle with a rotation angle step of the product carrier 13 is terminated when, according to FIG. 15, the drive wheel 34 is no longer in driving contact with the drive surface 46. Here now takes the drive wheel 34 again a basic position and the reset pinion 55 its rest position.

The basic position assumed by the drive wheel 34 after leaving the drive contact, which is also present in the end position of the transport carriage 4, differs from the basic position of the drive wheel 34 assumed in the starting position of the transport carriage by a position rotated by 180 °. The star wheel 25 and the product carrier 13 have thereby rotated by 45 °.

If at the time of canceling the drive contact between the drive wheel 34 and the drive surface 46, the drive wheel 34 take a deviating from the basic position Drehposi ^¬ tion, immediately the return means 23 are effective and cause an immediate return to the normal position. In this way, no undefined intermediate positions occur during operation of the transport device 1 in the Maltese cross gear 18. The transmission device 22 is thus in a defined operating state at every moment. The Maltese cross gear 18 always initializes itself with respect to the basic position as soon as the driving forces introduced by the contact with the drive surface 46 are eliminated.

Claims

claims

1. Transport device, with a transport carriage (4) which is drivable relative to a base (3) to a transport movement (5) along a transport path (6) and on which a for carrying and / or holding at least one product to be transported (2 ) suitable, the transport movement (5) mitmachender product carrier (13) is arranged, characterized

- That the product carrier (13) relative to the transport carriage (4) about a transversely to the direction of movement of the transport movement (5) aligned product carrier axis of rotation (14)

is rotatable,

- that on the transport carriage (4) a transport movement (5) mitmachende gear means (22) is arranged, which via a Maltese cross gear (18) with an intermittent output rotational movement (37) drivable slotted star wheel (25) and one with the star wheel ( 25) coupled and the output rotational movement (37) causing drive wheel (34), wherein the product carrier (13) with the star wheel (25) is in rotary drive connection,

- And that at least one with respect to the base (3) stationary drive surface (46) is arranged in such a way next to the transport path (6) of the transport carriage (4) that the drive wheel (34) at least during at least one movement section of the transport movement (5) directly or indirectly is in drive contact with the drive surface (46) and rolls on it, so that it is driven to a rotary drive movement (36), the at least one output rotation step of the star wheel (25) and the motion coupled therewith Pro Duct carrier 13) causes, whereby the rotational position of the product carrier (13) by at least a predetermined angle of rotation - step is changed.

2. Transport device according to claim 1, characterized in that the base (3) only a single with the drive wheel (34) cooperating drive surface (46).

3. Transport device according to claim 1 or 2, characterized in that the at least one drive surface (46) is designed and arranged such that the drive wheel (34) only during a movement step of the transport movement (5), which is shorter than the entire transport movement ( 5) of the transport carriage (4), rolls on the drive surface (46) and otherwise out of driving contact with the drive surface (46).

4. Transport device according to one of claims 1 to 3, characterized in that the at least one drive surface (46) in the direction of movement of the transport movement (5) has a smaller longitudinal extent than the entire transport path (6).

5. Transport device according to one of claims 1 to 4, characterized in that the drive wheel (34) in its rotational drive movement (36) alternately in the rotary driving engagement with the star wheel (25) stationary rotational drive phase and in blocking engagement with the star wheel (25) standing Locking phase passes through, wherein the transmission device (22) comprises return means (23) which force the drive wheel (34) in a basic position having a blocking engagement with the starwheel (25) when the drive wheel (34) out of driving contact with the at least one drive surface (46 ) stands .

6. Transport device according to claim 5, characterized in that the drive wheel (34) is rotated when passing through a blocking phase by a blocking rotation angle, wherein the basic position of the drive wheel (34) is a middle position of the blocking rotation angle.

7. Transport device according to claim 5 or 6, characterized in that the return means (23) have spring means (54) which act on the drive wheel (34) yielding a torque in the direction of the basic position and the drive wheel (34) in the normal position as long as it is out of drive contact with the drive surface (46).

8. Transport device according to claim 7, characterized in that the spring means (54) a stationary with respect to the transport carriage (4), in particular on a transmission housing (24) of the transmission device (22) supported return spring included, in particular as a leg spring (64) is.

9. Transport device according to claim 7 or 8, characterized in that the drive wheel (34) has a concentrically about its axis of rotation (35) extending around coupling teeth (58), wherein the return means (23) has a rotatably mounted, with the coupling toothing (58 ) in meshing engagement return pinion (55) which in turn is rotated by the drive rotational movement (37) of the drive wheel (34) in turn, wherein the spring means (54) cooperate with the return pinion (55).

10. Transport device according to claim 9, characterized in that the return pinion (55) has a rotational movement of the return pinion (55) about its axis of rotation (56) encircling actuating projection (62) to which the Fe dermittel (54) constantly acting to exert a torque, which tends to rotate with the return pinion (55) meshing drive wheel (34) to its normal position.

11. Transport device according to claim 9 or 10, characterized in that between the return pinion (55) and the coupling toothing (58) of the drive wheel (34) a reduction of 2: 1 is present.

12. Transport device according to one of claims 1 to 11, characterized in that the drive surface (46) by a linear toothing (46 a) is formed and the drive wheel (34) during the drive contact with this linear toothing (46 a) in engagement drive toothing (48a).

13. Transport device according to one of claims 1 to 12, characterized in that it is equipped with drive means (10) for generating the transport movement (5) of the transport carriage (4).

14. Transport device according to one of claims 1 to 13, characterized in that the transport carriage (4) to a reciprocating linear transport movement (5) is drivable.

15. Transport device according to claim 14, characterized in that the drive wheel (34) is able to come in both directions of movement of the transport carriage (4) with the at least one drive surface (46) in drive contact.

16. Transport device according to one of claims 1 to 15, characterized in that the transport carriage (4) designed in particular as a lifting device

Abrückeinrichtung (52) is assigned, which allows a controlled displacement of the transmission device (22) transversely to the direction of movement of the transport movement (5), such that the drive wheel (34) either in the transport movement (5) in driving contact with the drive surface (46 ) reaching effective operating position or in the transport movement (5) not in driving contact with the drive surface (46) reaching inoperative position

is positionable.

17. Transport device according to one of claims 1 to 16, characterized in that the product carrier rotation axis (14) coaxial with the axis of rotation (26) of the star wheel (25).