EP1958918B1 - Load handling device with roller body movement - Google Patents

Description

The present invention relates to a load handling means having the features of the preamble of claim 1.

As a load handling means, for example, side thrusts on industrial trucks are known in which a boom is movably received and guided movably along a guide axis along a guide axis on a side push frame fixedly connected to the industrial truck. In this case, a plurality of rolling elements, usually rollers, provided which store the boom on the side push frame movable and record corresponding bearing forces. Usually, the boom is statically over-determined attached to the side push frame, since the advantages of such storage, namely the exact play-free recording of the boom on the side push frame, the disadvantages of static overdetermination, namely the lack of detectability of bearing forces and associated with a possible tension overcompensated.

For supporting and guiding the boom on the side push frame, roller pairs with parallel roller axles are used inter alia to prevent tilting of the arm about a tilt axis parallel to the roller axes relative to the side push frame. A disadvantage of this configuration is caused by the distance of the rolling points of the axially parallel rollers in the direction of the guide axis restriction of the movement space of the boom relative to the side push frame.

A load handling means having the features of the preamble of claim 1 is known from the document DE 10 2004 007 292 A1 known. In this case, an arrangement of rotating rolling elements replaces the axis-parallel pair of rollers known from the prior art described at the beginning. By the plurality of rotating rolling elements, which roll in a support portion in which the rolling elements under load on both the frame and the load moving component, the load to be absorbed by the support portion can be distributed to a plurality of rolling elements, as always more than two rolling elements in the Support section are located. As a result, with a small surface pressure at the individual rolling elements with a suitable choice of the size dimensions of the rolling elements of the support portion may be formed shorter in the direction of the guide axis than the distance between the pitch points of two axially parallel Wälzrollen according to the prior art described above. Accordingly, the load-moving component can be extended relative to the frame along the guide axis without the bearing and guiding situation of the load-moving component on the frame changes.

By dividing the guide load on a plurality of rolling elements, it is possible to run over the end of the guide track, so that a part of the currently present in the support section rolling elements out of rolling engagement with the guideway passes. As a result, the relative movement path between the load-moving component and the frame along the guide axis relative to the prior art described at the outset can be further extended without the guide of the load-moving component being appreciably impaired on the frame. For short periods, it may be sufficient that only a part of the rolling elements present in the support section is in rolling contact with the guideway. Therefore, for a short time, the end of the guideway can be overrun at least so far that at least half or more of all rolling elements present in the support section continue to be in rolling contact with the guideway.

Furthermore, it can be formed by the division of the guide load on a plurality of rolling elements and the concomitant reduction of the surface pressure on the individual rolling elements with smaller contact surface to the guideway, so that compared to the above-described prior art, a narrower guideway can be used.

With "exit end region" and "entrance end region" of the support section, those regions are designated in which the rolling elements leave the support section after it has passed through or in which they reenter the support section after being returned. The return section ensures that a rolling body, which passes after rolling of the support section except rolling contact with the guide track, is returned to the beginning of the support section to again pass through the support section. The direction of the Wälzkörperdurchgangs by the support portion and the return portion depends on the relative direction of movement between the load movement member and the frame.

A compact guide component which carries the arrangement of rotating rolling elements is formed by the fact that the at least one arrangement of rotating rolling elements at least partially surrounds a molding component having the rolling track on which at least a part of the revolving rolling elements in a relative movement of the frame and load moving component rolls.

A particularly easy assembly with simultaneously defined arrangement of rotating rolling elements is obtained by the fact that the at least one arrangement of rotating rolling elements is at least one Wälzkörperkette. Especially with Wälzkörperketten where the distances between rolling elements by chain links are generally fixed, it may come by different radii of curvature of the Wälzbahn on the mold component to the above-mentioned temporary lifting of rolling elements of the Wälzbahn during circulation.

Against the background of DE 10 2004 007 292 A1 As the closest prior art, it is the object of the present invention to ensure a defined positional relationship between the rolling elements and the molding component, in particular the rolling track on the molding component. For this purpose, the invention provides that the Wälzkörperkette is a lamella chain having guide means which is engaged with guide counterparts on the mold member for guiding the lamella chain on the mold component in the rolling direction. This can be done structurally especially simply by virtue of the fact that at least some of the lamellae, preferably all lamellae, of the lamella chain have a guide lug pointing toward the mold component. The guide nose may be less preferably attached to the slats later. From a production point of view, it is preferred if the guide nose is integrally formed on lamellae of the lamella chain.

In principle, it can be thought that the rolling elements only roll in the support section between the guide track and the roller track, while they are conveyed in the return section substantially without defined contact with a rolling body guide to the entry end of the support section. However, it is preferred that the rolling elements also roll in the return section at least partially on the rolling track, so as to achieve a defined return movement of the rolling elements. For this purpose, the Wälzbahn be formed as an endless closed in Abwälzrichtung web.

Depending on the design of the rolling track, it may in particular occur at different radii of curvature of the rolling track in the direction of rolling, that rolling elements temporarily stand out from the rolling track. However, this leads to unwanted noise and mechanical loads. A sufficient orderly return of the rolling elements can be ensured if at least two thirds of the rotating rolling elements are constantly in rolling contact with the Wälzbahn. For the reasons mentioned above, however, it is preferred that all rotating rolling elements are in touching contact with the rolling track.

Since in most cases the relative movement between the load-moving component and the frame is a linear translatory movement, it is advantageous if the roller track has a straight-line track section associated with the carrying section.

Depending on the load conditions in the support section, it may be necessary that the return section is formed longer than the support section to a Provide the largest possible number of rolling elements in Wälzkörperumlauf. This can be realized by virtue of the fact that the rolling track has a path section assigned to the return section, at least in sections, but preferably completely curvilinear. The curvature of the web section is a curvature in the direction of rolling or Wälzkörperförderrichtung.

The Wälzkörperkette can be easily mounted, if it is a finite chain. Then, however, depending on the shape of the rolling track, the gap between the open ends of the rolling element track during a rolling element revolution may vary. If this is not desired, it is also possible to use an endless rolling element chain closed in the rolling direction.

According to a lamella chain is used as the Wälzkörperkette, since this is dimensioned in Wälzkörperdrehachsenrichtung only slightly larger than the rolling elements themselves and at the same time provides sufficient strength.

A sufficiently movable lamella chain can be obtained by assigning two rolling elements to a rolling element and two rolling elements to a lamination. This applies to each rolling element of the Wälzkörperkette with two adjacent in the chain direction rolling elements, ie in the case of an endless Wälzkörperkette for each rolling element and in the case of a finite Wälzkörperkette for each rolling element except the two end rolling elements.

The most common case of a lamella chain is a lamella chain with two parallel rows of lamellae, between which the rolling elements of the lamella chain are arranged. These lamellae chains are at least sufficiently movable when each rolling element at each longitudinal end of two lamellae and each lamella are associated with two rolling elements. This applies, as described above, again for each rolling element with two adjacent in the chain direction rolling elements. Such lamellae chains are particularly well suited for fixing the position relative to the rolling track when at least a portion of the lamellae of each lamella row has guide lugs, so that at least one section of the rolling lane, preferably the entire rolling lane, of the molding component is located between the guide lugs of lamellae of the two lamellae rows.

The counter-guide means on the mold component can be formed in a very simple manner as a contact surface for the application of guide lugs on this.

Since lamellae of a lamella chain are generally formed as planar components, which are oriented orthogonal to the parallel axes of rotation of the rolling elements of the lamella chain, the at least one contact surface is preferably Angled to the rolling surface of the rolling track.

Then, when the lamella chain is used with the two parallel rows of lamellae, the mold component may have two spaced-apart contact surfaces, each contact surface are assigned guide lugs a lamella array. The abutment surfaces, between which the Wälzbahn runs, preferably enclose an angle with the rolling surface of the Wälzbahn. This angle may be a right angle, or it may be slight, i. 1 ° to 10 °, preferably 2 ° to 5 ° greater than a right angle, so that the attachment of the lamella chain is simplified on the mold component. The enclosed between the contact surface and rolling surface of the rolling angle can therefore be greater than a right angle to usual draft angle.

A particularly smooth guiding is obtained by the fact that the at least one contact surface is formed from plastic. Particularly suitable as a low-friction sliding layer, a contact surface made of polytetrafluoroethylene has been found.

Likewise, at least a portion of the rolling elements, but preferably all rolling elements, be supported by a sliding bearing surface made of plastic for rotation about their respective Wälzkörperdrehachse. Again, polytetrafluoroethylene has proven to be a particularly low-friction plastic. Due to the plastic plain bearing surface of the rolling elements and also by the plastic contact surface, the guide with the arrangement of rotating rolling elements of the load handling agent according to the invention receives excellent emergency running properties that allow further operation of the load handling means in the event of failure of a lubricant supply.

Particularly simple can be mounted by a plastic plain bearing surface for rotation part of the rolling elements by the interposition of a plain bearing sleeve on a running in Wälzkörperdrehachserichtung bolt be included. The bolt can, as is known, simultaneously serve to connect the two rows of lamellae.

As already indicated, the load handling agent according to the invention is particularly advantageous as a side thruster. In this case, the above-described frame is a push frame, and the above-described load moving member is a boom movably received on the push frame relative thereto. However, it should not be ruled out that the load handling agent is also suitable for other applications for moving goods, in particular on industrial trucks.

For driving in this preferred embodiment of the present invention to a component of thrust frame and boom, preferably on the boom, at least one drivable drive means and on the other component, preferably on the push frame, a fixedly connected thereto output means may be provided with which the at least one Drive means in driving force transmission engagement, wherein the driving force transmission engagement is in the direction of the guide axis in the longitudinal region of the support portion. Thereby, the durability of the driving force transmission engagement can be ensured. Thus, the above-mentioned arrangement of the driving force transmission engagement in the longitudinal portion of the support portion can prevent an undesired engaging end of the driving force transmission engagement by preventing, for example, a physical separation of driving and driving means by lifting or the like.

Preferably, drive and driven means form a gear made of toothed elements, particularly preferably the drive means is a toothed wheel, which meshes with a toothed rack as the output means. Alternatively, however, it may also be thought to use a friction wheel as drive means, wherein the drive force transmission engagement is then a frictional engagement.

Since the load handling means described above gives a truck special value, independent protection is also sought for trucks with such a load handling means, in particular a side thruster. Such a truck solves the above-mentioned problem.

Although the present invention will be described below essentially by way of example of a side thruster, the invention is not limited to side thrusters, but may be applied to any other load handling means.

Fig. 1

eine perspektivische Darstellung eines Seitenschubgeräts als erfindungsgemäße Ausführungsform eines Lasthandhabungsmittels gemäß der vorliegenden Erfindung,

Fig. 2

eine Seitenansicht des Seitenschubgeräts von Fig. 1,

Fig. 3

eine Schnittansicht entlang der Schnittebene III-III von Fig. 2,

Fig. 4

eine perspektivische Ansicht eines Führungsbauteils umfassend ein Formbauteil mit Wälzbahn und daran abwälzender Lamellenkette,

Fig. 5

eine Draufsicht auf das Führungsbauteil von Fig. 4 und

Fig. 6

eine Schnittansicht entlang der Schnittebene VI-VI von Fig. 5.

The present invention is explained below with reference to an embodiment which is illustrated in the accompanying drawings. It shows:

Fig. 1

3 a perspective view of a side thruster as an embodiment according to the invention of a load handling means according to the present invention,

Fig. 2

a side view of the side thruster of Fig. 1 .

Fig. 3

a sectional view taken along the section plane III-III of Fig. 2 .

Fig. 4

a perspective view of a guide member comprising a forming member with Wälzbahn and rolling it off lamellar chain,

Fig. 5

a plan view of the guide member of Fig. 4 and

Fig. 6

a sectional view along the section plane VI-VI of Fig. 5 ,

To explain a side thruster as an inventive embodiment of a lifting device of the present invention is based on the FIGS. 1 and 2 directed. In the FIGS. 1 and 2 is a side thruster generally designated 10. The side thruster 10 includes a side push frame 12, which is fixedly provided on a truck, not shown, as well as on the side push frame 12 relative to this along a direction indicated by the double arrow F guide movable arm 14. The boom 14 can be connected via another scaffold 16 (s , Fig. 2 ) may be connected to a load handling means such as a fork.

The boom 14 has a drive motor 18, on the drive shaft 20, a drive gear closer first gear 22 and a drive motor remote second gear 24 are rotatably provided, which roll on correspondingly associated racks 26 and 28 of the side push frame 12 meshing. By rotation of the gears 22 and 24, driven by the drive motor 18, thus the boom 14 can be moved relative to the side push frame 12 along the double arrow F.

The boom 14 is guided over several rolling rollers on the side push frame 12. A first roller 30 supports the boom 14 on a first formed on the rack 26 roller bearing 32 in the direction of gravity.

Furthermore, on the drive shaft 20, a drive motor-second roller 34 and a drive motor remote third roller 36 are provided relative to the drive shaft 20 rotatable in the vicinity of the gears 22 and 24 and roll on associated roller conveyors 38 and 40, which on the racks 26 and 28 are formed. The second and third rollers 34, 36 support tilting moments about a tilt axis extending parallel to the double arrow F.

Furthermore, a drive-motor-closer first guide member 42 and a drive motor remote second guide member 44 are provided on the boom 14. The guide components 42 and 44 are of identical design, which is why it is sufficient in the following to describe only the first guide member 42 in detail.

The first guide member 42 has a plurality of substantially identical rollers 46 as rolling elements. The rollers 46 are combined to form an endless lamella chain 48.

As in Fig. 1 can be seen, roll the rollers 46 of the lamella chain 48 of the first guide member 42 from a guide rail 50 which is formed on the rack 26 on its side facing away from the toothing side. Likewise, the rollers of the second guide member roll on a guideway 52 of the second rack 28 from. Also on the second rack 28 teeth and guideway 52 are formed on opposite sides.

In Fig. 3 the guide member 42 is shown in section. The lamella chain 48 surrounds a mold component 54, which has a closed circumferential Wälzbahn 56, at the rolling surface 58, the rollers 46 of the lamella chain 48 abut contact and roll in a relative movement of boom 14 and side push frame 12 circumferentially.

The in Fig. 3 shown cross section through the guide member 42 shows that a part of the rotating rollers 46, namely that part which is in contact contact with the guide track 50 forms a support portion T. In this support section T is in the in Fig. 3 shown example, the force acting on the guide member 42 load distributed to a total of six rollers 46, so that each individual roller experiences only a very low surface pressure. The same applies to the surface pressure acting on the guideway 50.

It should be noted that the pitch point W at which the gear wheel 22 is currently rolling on the rack 28, viewed in the guide direction F in the same longitudinal section as the support portion T. This can be prevented that the gear 22 lifts from the rack 28 and out Kämmseingriff device.

By the extension of the support section in the guide direction F can be prevented with the guide member 42 that the boom 14 in the case of a drive, in particular accelerated or delayed drive, tilted about a parallel to the longitudinal direction of the drive shaft 20 tilting axis.

Since it can be temporarily allowed that lie in the guide direction F au-βen rollers 46 of the support section T out of engagement with the guide track 50, the range of movement of the boom 14 relative to the side push frame 12 in the guide direction F over the prior art can be extended.

The mold member 54 has openings to facilitate easy attachment of the guide member 42 over the mold member 54 and to reduce the mass of the guide member 42 to be moved.

The remaining area of the circumferential lamella chain 48, which does not belong to the straight-line support section T, forms a return section R, which in Fig. 3 is merely indicated. In this return section R, the rolling elements 46, which have just left the support section T, fed this again. The boom 14 moves in Fig. 3 For example, in the direction of the double arrow F up, the rollers 46 of the lamella chain 48 run counterclockwise around the mold member 54 around and roll both on the guide rail 50 of the rack 28 and on the rolling track 56 of the mold member 54 from. The rolling elements 46 occur at the end region 60 of the support section T from this and occur at the end portion 62 again in the support section T. In this case, therefore, the end region 60 forms an exit end region and the end region 62 forms an entry end region of the carrying section T. With a relative movement of the delivery arm 14 in the opposite direction with respect to the side push frame 12, the movement ratios of the rollers 46 are exactly the opposite.

As in Fig. 3 to recognize, the support portion T is assigned a straight Wälzbahnabschnitt 63, while the return section is associated with a curvilinear Wälzbahnabschnitt 65. The Wälzbahnabschnitt 65, in which there are more roles than in the straight track section 63, has different radii of curvature. In its two areas near the end areas 60 and 62 of the support section T, the curvilinear track section 65 is more curved than in the section located between these areas.

In Fig. 4 the guide member 42 is shown in perspective. The lamella chain 48 has two substantially parallel lamellae rows 64 and 66, between which the rollers 46 of the lamella chain 48 are received. At each longitudinal end of a roller 46, this is connected by a bolt 68 with two fins 70. The slats 70 of the two rows of slats 64 and 66 are identical, which facilitates the production of the slat chain 48.

At their edge portions pointing toward the molded component 54, the fins 70 have guide projections 72 protruding toward the molded component 54. This is even better in the plan view of Fig. 5 to recognize.

The roller closer lamellae of the lamella row 64 abut with their guide lugs 72 on a first contact surface 74 of the molded component 54. The system situation for the parallel slat row 66 is identical, so that the rolling track 56 is held with its rolling surface 58 between the respective roll closer slats 70 of the slat rows 64 and 66 positively. The fins 70 are formed by punching so that the guide tabs 72 are integrally formed thereon. This is fine in detail Fig. 5 to recognize.

The cross section of Fig. 6 shows that the peripheral bearing surfaces 74 of the mold member 54 are formed by plastic layers 76 of polytetrafluoroethylene or other plastics with known good sliding properties. It should be noted that the plant situation of the fins 70 both Slat rows 64 and 66 are identical.

The rolling surface 58 includes, when viewed in a direction of rolling at the Abwälzort a roller orthogonal cutting plane 46, with the support surface 74 an angle α, which may be a right angle or may be greater than a right angle to conventional draft angle greater than a right angle, for example 91 ° up to 100 °.

The rollers 46 are mounted with the intermediate arrangement of a plain bearing sleeve 78 on their associated pin 68 for rotation about its roller axis RD. The slide bearing sleeve 78, which provides a radially inner slide bearing surface 78a and a radially outer slide bearing surface 78b, is preferably made of plastic, particularly preferably of the same plastic as the components 76 providing the contact surfaces 74. The guide component is provided by the plastic slide guides provided on the guide component 42 42 very good emergency running properties, if a lubricant supply is interrupted.

With reference to Fig. 5 It should be added that the lamellae 70 have a concave contour 80 between their guide lugs 72, which makes it possible to move the lamellae 70 in spite of the guide system of the guide lugs 72 on the contact surfaces 74 themselves by small radii of curvature near the end regions 60 and 62.

Claims (14)

1. Load-handling means, in particular for industrial trucks, with a frame (12) and a load movement component part (14), which is accommodated on said frame in such a way that it is capable of relative movement, the load movement component part (14) being guided on the frame (12) by means of a plurality of rolling bodies (30, 34, 36, 46) for the relative movement along a guide axis (F), wherein the plurality of rolling bodies (30, 34, 36, 46) comprises at least one arrangement of circulating rolling bodies (46), with a supporting section (T), in which rolling bodies (46) in the event of a relative movement of the frame (12) and the load movement component part (14) roll along a guide track (50, 52), which is fixedly connected to one component part of the frame (12) and the load movement component part (14), and a rolling track (56), which is fixedly connected to the respective other component part of the frame (12) and the load movement component part (14), and with a return section (R), in which the rolling bodies (46) during the relative movement of the frame (12) and the load movement component part (14) move from an outlet end region (60 or 62) of the supporting section (T) towards its inlet end region (60 or 62), wherein the at least one arrangement of circulating rolling bodies (46) surrounds at least sections of a shaped component part (54), which has the rolling track (56), on which at least some of the circulating rolling bodies (46) roll in the event of a relative movement of the frame (12) and the load movement component part (14), wherein the at least one arrangement of circulating rolling bodies (46) is at least one rolling body chain (48), preferably a continuous rolling body chain (48), characterized in that the rolling body chain (48) is a slat chain (48) which has guide means (72), which engage with opposing guide means (74) on the shaped component part (54) for the purpose of guiding the slat chain (48) on the shaped component part (54) in the rolling direction.
2. Load-handling means according to Claim 1, characterized in that the rolling track (56) is continuous and at least two thirds of the circulating rolling bodies (46), preferably all of the circulating rolling bodies (46), are in touching contact with it.
3. Load-handling means according to Claim 1 or 2, characterized in that the rolling track (56) has a linear track section (63) associated with the supporting section (T).
4. Load-handling means according to one of Claims 1 to 3, characterized in that the rolling track (56) has a track section (65), at least sections of which, but preferably all of which is curvilinear and which is associated with the return section (R).
5. Load-handling means according to one of the preceding claims, characterized in that at least some of the slats (70) of the slat chain (48) has a guide tab (72) pointing towards the shaped component part (54).
6. Load-handling means according to Claim 5, characterized in that the slat chain (48) has two parallel rows of slats (64, 66), between which the rolling bodies (46) of the slat chain (48) are arranged, at least some of the slats (70) of each row of slats (64, 66) having guide tabs (72), so that at least one section of the rolling track (56) of the shaped component part (54) is located between the guide tabs (72) of slats (70) of the two rows of slats (64, 66).
7. Load-handling means according to Claim 5 or 6, characterized in that the shaped component part (54) has at least one resting face (74) for guide tabs (72) to rest thereon.
8. Load-handling means according to Claim 7 incorporating Claim 6, characterized in that the shaped component part (54) has two resting faces (74), which are arranged at a distance from one another, each resting face (74) having associated guide tabs (72) of a row of slats (64, 66).
9. Load-handling means according to Claim 7 or 8, characterized in that the at least one resting face (74) is formed from plastic, in particular from polytetrafluoroethylene.
10. Load-handling means according to one of the preceding claims, characterized in that at least some of the rolling bodies (46), but preferably all of the rolling bodies (46), are mounted by means of a sliding-bearing face (78a, 78b) made from plastic, preferably from polytetrafluoroethylene, so as to rotate about a rolling-body axis of rotation (RD).
11. Load-handling means according to Claim 10, characterized in that at least some of the rolling bodies (46), but preferably all of the rolling bodies (46), are accommodated by means of an intermediate arrangement of a sliding-bearing sleeve (78) on a bolt (68).
12. Load-handling means according to one of the preceding claims, characterized in that the load-handling means is a side-shifting device (10) with a shifting frame (12) as the frame and with an outrigger (14) as the load movement component part.
13. Load-handling means according to Claim 12, characterized in that at least one drivable drive means (22, 24), preferably a gearwheel (22, 24), is provided on one component part of the shifting frame (12) and the outrigger (14), preferably on the outrigger (14), and a driven means (26, 28), preferably a toothed rack (26, 28), is provided on the respective other component part, preferably on the shifting frame (12) and is fixedly connected to it, the at least one drive means (22, 24) being in drive-force-transmitting engagement with the driven means, the drive-force-transmitting engagement lying in the direction of the guide axis (F) in the longitudinal region of the supporting section (T).
14. Industrial truck, characterized in that it has a load-handling means, in particular a side-shifting device (10), according to one of the preceding claims.

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